CN113090440B - Method for detecting damage of water pump turbine runner - Google Patents

Method for detecting damage of water pump turbine runner Download PDF

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Publication number
CN113090440B
CN113090440B CN202110395049.1A CN202110395049A CN113090440B CN 113090440 B CN113090440 B CN 113090440B CN 202110395049 A CN202110395049 A CN 202110395049A CN 113090440 B CN113090440 B CN 113090440B
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pump turbine
water
theoretical
flow
turbine
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CN113090440A (en
Inventor
范寿孝
赵越
李友平
赵英男
郭全宝
孙永新
黎辉
刘智良
张金伟
邵国辉
徐用良
赵伟
明宏林
苏文涛
郭彦峰
韩东邑
明亮
董宇
刘登峰
王润鹏
许彬
贺婷婷
任玉堂
吴喜东
贺儒飞
曹卫华
崔金声
郑程
陈章煜
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Hadong National Hydroelectric Power Equipment Engineering Technology Research Central Co ltd
Harbin Electric Machinery Co Ltd
Peak and Frequency Regulation Power Generation Co of China Southern Power Grid Co Ltd
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Hadong National Hydroelectric Power Equipment Engineering Technology Research Central Co ltd
Harbin Electric Machinery Co Ltd
Peak and Frequency Regulation Power Generation Co of China Southern Power Grid Co Ltd
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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
    • 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
    • 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
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/10—Machines or engines of reaction type; Parts or details peculiar thereto characterised by having means for functioning alternatively as pumps or turbines
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/26—Devices for measuring efficiency, i.e. the ratio of power output to power input
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/80—Diagnostics
    • 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)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Control Of Water Turbines (AREA)
  • Hydraulic Turbines (AREA)

Abstract

A method for detecting damage of a water pump turbine runner relates to the field of water turbine fault detection. The invention aims to solve the problem that whether a water pump turbine is damaged or not can not be judged according to the change of the external characteristics of the water pump turbine at present, so that serious associated accidents occur. The invention includes: acquiring the actual information of the related quantity of stable operation of the water pump turbine under the power generation working condition and the water pumping working condition; acquiring a theoretical value of the correlation quantity of the acquired information under a corresponding working condition; acquiring a serious damage judgment coefficient of the pump turbine according to the acquired theoretical value and actual value; the serious damage judgment coefficient of the water pump turbine comprises six judgment coefficients; and judging whether the turbine runner has serious faults or not according to the judgment coefficient. The invention detects the fault of the damage of the water pump turbine runner.

Description

Method for detecting damage of water pump turbine runner
Technical Field
The invention belongs to the field of water turbine fault detection, and particularly relates to a method for detecting damage of a water pump and water turbine runner.
Background
Along with the gradual improvement of the operating stability requirements of users on the pump turbine, the guarantee that the main components of the pump turbine, particularly giant and large-scale pump turbines, are in a normal working state becomes an important index for guaranteeing the safe and stable operation of a unit and checking the operating state of the unit.
The pump turbine runner is used as an energy conversion component of the pump turbine and is a core element of the pump turbine. Because the pump-turbine runner is completely immersed in water, the corresponding sensors can not be installed on the parts exposed in the air like other parts of the pump-turbine for targeted detection and measurement, so that a direct and reliable method for detecting the damage condition of the pump-turbine runner is unavailable, and then a worker can not know whether the pump-turbine runner is damaged according to the change of the external characteristics of the pump-turbine, thereby causing serious associated accidents.
Disclosure of Invention
The invention aims to solve the problem that whether a pump turbine runner is damaged or not cannot be judged according to the change of the external characteristics of the pump turbine so as to cause serious associated accidents at present, and provides a method for detecting the damage of the pump turbine runner.
A method for detecting damage of a water pump turbine runner comprises the following specific processes:
acquiring actual upstream and downstream water level values, actual pumped storage output/input force values, actual water head values, actual lift information values, actual servomotor stroke values and actual flow values of a water pump turbine stably operating under a power generation working condition and a pumping working condition;
step two, obtaining a theoretical value of the correlation quantity under the corresponding working condition of the information collected in the step one, and determining through the following mode:
determining theoretical efficiency eta of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the water pump turbine efficiency along with the change of the output force/input force of the pumped storage unit t ；
Determining theoretical output/input force P of the pumped storage unit under corresponding working conditions according to a theoretical relation curve of output/input force of the pumped storage unit along with stroke change of a servomotor of a water pump water turbine t ；
Determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the flow of the water pump turbine under the power generation working conditions/the water pumping working conditions along with the change of the output force/the input force of the water pumping energy storage unit tP ；
Determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the flow of the water pump turbine under the power generation working conditions/water pumping working conditions along with the change of the stroke of the servomotor tS ；
Determining theoretical head H of water pump turbine under corresponding working condition according to theoretical relation curve of water pump turbine head/lift along with change of upstream and downstream water level differences tT And theoretical lift H tP ；
Calculating an actual efficiency value according to the stored output/input force information, the water head and lift information of the water pump and the water turbine and flow information in combination with the gravity acceleration, the efficiency of the power generation motor under the power generation working condition and the pumping working condition of the pumping energy storage unit and the density of water;
step four, acquiring a damage judgment coefficient of the water turbine of the water pump according to the actual value obtained in the step one, the theoretical value obtained in the step two and the actual efficiency value obtained in the step three;
the pump turbine breakage determination coefficient includes: determining the coefficient of the damage efficiency of the water pump turbine runner; judging the coefficient of output/input force of the damaged runner of the pump turbine; the flow judgment coefficient is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/pumping working condition of the pump turbine along with the change of the output force/input force of the pumping energy storage unit when the runner of the pump turbine is damaged; determining a flow determination coefficient according to a theoretical relation curve of the flow of the water pump turbine along with the change of the stroke of the servomotor when the water pump turbine runner is damaged; determining coefficient of a damaged water head of a water pump turbine runner; determining coefficient of pump turbine runner damage lift;
and step five, judging whether the turbine runner has a fault according to the judgment coefficient of the step four.
The invention has the beneficial effects that:
the invention comprehensively analyzes the comprehensive change conditions of the efficiency of the pump turbine, the output/input force of the pumped storage unit, the flow of the pump turbine and the water head/lift of the pump turbine, the reason for the efficiency reduction of the combined water pump and turbine can be that part sleeves and components of the embedded part, the water distributor, the water guide bearing and the runner of the rotating part of the water pump and turbine are failed, and the reason of the output reduction of the unit can be two parts of the faults of the embedded part of the pump turbine, the water distributor, the water guide bearing, the runner and other parts and components of the rotating part of the pump turbine and the generator, the possibility of the faults of the generator motor and the water guide bearing of the rotating part of the pump turbine is eliminated by introducing the flow reduction evaluation index of the pump turbine, meanwhile, the possibility that the water pump turbine embedded part and the water distributor have faults is discharged by introducing the grade index of the water pump turbine head reduction under the water pumping condition without the change of the water pump turbine head under the power generation condition of the water pumping energy storage unit, the parts of the unit with the faults are concentrated on the rotating wheel of the water turbine, and based on the phenomenon that the capability of the pump turbine for energy conversion is greatly reduced when the pump turbine runner is damaged and fails, selecting the output/input force, flow and water head/lift of the water pump turbine on the external characteristics, calculating the actual efficiency of the water pump turbine according to the parameters as an evaluation object, and comparing the characteristic quantity with corresponding theoretical values under the working condition, calculating the difference between the characteristic quantity theoretical value and an actual measured value in a mode of corresponding to the damage judgment coefficients of the multiple groups of water pump turbine rotating wheels with different characteristic quantities, and finally judging whether the water pump turbine rotating wheels have damage faults or not according to judgment rules. The invention enables the worker to know whether the water pump turbine is damaged or not according to the change of the external characteristics of the water pump turbine, thereby avoiding the occurrence of serious associated accidents.
Drawings
FIG. 1 is a theoretical relation curve of the working condition efficiency of a pump turbine along with the output change of a pumped storage unit;
FIG. 2 is a theoretical relation curve of the working condition efficiency of a water pump and a water turbine along with the input force change of a pumped storage unit;
FIG. 3 is a theoretical relationship curve of the output of the pumped storage unit under the power generation working condition along with the change of the stroke of the servomotor of the water pump and the water turbine;
FIG. 4 is a theoretical relationship curve of the change of the water pumping working condition inlet force of the water pumping energy storage unit along with the stroke of the servomotor of the water pump water turbine;
FIG. 5 is a theoretical relationship curve of the water pump turbine generating condition flow random group output variation;
FIG. 6 is a theoretical relationship curve of the random set of inflow force changes of the flow rate under the water pumping condition of the pump turbine;
FIG. 7 is a theoretical relationship curve of the flow of the water pump turbine under the power generation working condition along with the stroke change of the servomotor;
FIG. 8 is a theoretical relationship curve of the flow of the water pump turbine under the water pumping condition along with the change of the stroke of the servomotor;
FIG. 9 is a theoretical relationship curve of variation of a pump turbine head with difference between upstream and downstream water levels;
fig. 10 is a theoretical relationship curve of the pump turbine lift varying with the difference between the water levels upstream and downstream.
Detailed Description
The first embodiment is as follows: the method for detecting the damage of the water pump turbine runner comprises the following specific processes:
acquiring actual upstream and downstream water level values, actual pumped storage output/input force values, actual water head values, actual lift information values, actual servomotor stroke values and actual flow values of a water pump turbine stably operating under a power generation working condition and a pumping working condition;
step two, obtaining a theoretical value of the correlation quantity under the corresponding working condition of the information collected in the step one, and determining through the following mode:
determining theoretical efficiency eta of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the water pump turbine efficiency along with the change of the output force/input force of the pumped storage unit t ；
Determining theoretical output/input force P of the pumped storage unit under corresponding working conditions according to a theoretical relation curve of output/input force of the pumped storage unit along with stroke change of a servomotor of a water pump turbine t ；
Determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the flow of the water pump turbine under the power generation working conditions/the water pumping working conditions along with the change of the output force/the input force of the water pumping energy storage unit tP ；
Determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the flow of the water pump turbine under the power generation working conditions/water pumping working conditions along with the change of the stroke of the servomotor tS ；
Determining theoretical head H of water pump turbine under corresponding working condition according to theoretical relation curve of water pump turbine head/lift along with change of upstream and downstream water level differences tT And theoretical lift H tP ；
Calculating an actual efficiency value according to the stored output/input force information, the water head and lift information of the water pump and the water turbine and flow information in combination with the gravity acceleration, the efficiency of the power generation motor under the power generation working condition and the pumping working condition of the pumping energy storage unit and the density of water;
step four, obtaining a damage judgment coefficient of a water pump turbine runner according to the actual value obtained in the step one, the theoretical value obtained in the step two and the actual efficiency value obtained in the step three;
the pump turbine breakage determination coefficient includes: determining the coefficient of the damage efficiency of the water pump turbine runner; judging the coefficient of output/input force of the damaged runner of the pump turbine; the flow judgment coefficient is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/pumping working condition of the pump turbine along with the change of the output force/input force of the pumping energy storage unit when the pump turbine runner is damaged; the flow judgment coefficient is determined according to a theoretical relation curve of the flow of the water pump turbine generator/pumping working condition along with the change of the stroke of the servomotor when the water pump turbine runner is damaged; determining coefficient of a damaged water head of a water pump turbine runner; determining coefficient of damaged lift of a water pump turbine runner;
and step five, judging whether the rotating wheel of the water turbine fails according to the judgment coefficient of the step four.
The second embodiment is as follows: the actual water head value of the water turbine of the water pump in the first step is obtained through water head measuring equipment of the water turbine; the actual value of the lift is obtained by lift measuring equipment; the actual servomotor stroke value is obtained through servomotor stroke measuring equipment of a water pump and a water turbine; the actual flow rate value is measured by a flow measuring device of the water turbine.
Other steps are the same as in the first embodiment.
The third concrete implementation mode: determining theoretical efficiency eta of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the water pump turbine efficiency changing along with the output/input of the pumped storage unit t The method comprises the following steps:
as shown in fig. 1 and fig. 2, when the pump-turbine operates stably under a certain working condition, a theoretical relationship curve 10 of the pump-turbine working condition efficiency random group output change and a theoretical relationship curve 20 of the pump-turbine working condition efficiency random group input change can be determined according to the upstream and downstream water levels at the moment, and then, theoretical efficiency values 11 and 21 of the pump-turbine working condition and the pump working condition can be determined respectively according to the output and input values of the pump-storage unit (generator motor) under the power generation working condition and the pump working condition.
In this embodiment, for the operating mode of power generation, when the pump turbine operates normally, the theoretical efficiency value of the operating mode of the turbine is equivalent to the actual efficiency value obtained by real-time measurement in the operating process of the unit. That is, the actual efficiency value obtained by actual measurement of the turbine operating conditions fluctuates around the theoretical efficiency 11, and may be slightly higher than the theoretical efficiency 11 (as indicated by point 12) or slightly lower than the theoretical efficiency 11 (as indicated by point 13), but the fluctuation range is small. Of course, the actual efficiency value obtained from actual measurements of the turbine operating conditions may also be equal to the theoretical efficiency 11. Once the runner of the pump turbine is damaged, the energy conversion capability of the pump turbine is greatly reduced. The efficiency reflected on the working condition of the water turbine is that the actual efficiency of the working condition of the water turbine is greatly reduced compared with the theoretical efficiency. At the moment, the value of the actual efficiency point 14 of the pump-turbine is certainly smaller than the value of the theoretical efficiency 11, and a large enough efficiency difference value is certainly generated between the theoretical efficiency and the actual efficiency of the pump-turbine;
for the working condition of pumping water, when the water pump turbine normally operates, the theoretical efficiency value of the working condition of the water pump should be equivalent to the actual efficiency value obtained by real-time measurement in the operation process of the unit. That is, the actual efficiency value obtained from actual measurement of the water pump operating conditions should fluctuate around the theoretical efficiency 21, either slightly above the theoretical efficiency 21 (as shown at point 22) or slightly below the theoretical efficiency 21 (as shown at point 23), but with a small fluctuation range. Of course, the actual efficiency value obtained from actual measurements of the water pump operating conditions may also be equal to the theoretical efficiency 21. Once the runner of the pump turbine is damaged, the energy conversion capability of the water pump is greatly reduced. The efficiency of the water pump is reflected in that the actual efficiency of the water pump is much lower than the theoretical efficiency. The value of the actual efficiency point 24 of the water pump must be smaller than the value of the theoretical efficiency 21, and a sufficiently large efficiency difference must occur between the theoretical efficiency and the actual efficiency of the pump turbine.
The other steps are the same as those in the first or second embodiment.
The fourth concrete implementation mode is as follows:determining theoretical output/input force P of the pumped storage unit under corresponding working conditions according to a theoretical relation curve of output/input force of the pumped storage unit along with stroke change of the water pump turbine servomotor t The method comprises the following steps:
as shown in fig. 3 and 4, when the pump turbine stably operates under a certain working condition, a theoretical relationship curve 30 of the output of the pumped storage unit under the power generation working condition along with the change of the stroke of the water pump turbine servomotor and a theoretical relationship curve 40 of the input of the pumped storage unit under the pumping working condition along with the change of the stroke of the water pump turbine servomotor are determined according to the upstream and downstream water levels. The actual servomotor stroke of the water turbine under the working condition can be measured in real time through servomotor stroke measuring equipment of the water turbine of the water pump. And then according to the servomotor stroke of the water pump turbine under the working condition, the theoretical output value 31 of the pumped storage unit under the power generation working condition and the theoretical input value 41 of the pumped storage unit under the pumped storage working condition can be determined.
In this embodiment, for the power generation condition, when the pump turbine operates normally, the theoretical output value of the pumped storage unit should be equivalent to the actual output value of the pumped storage unit obtained by real-time measurement in the unit operation process. That is, the actual output value obtained by actual measurement of the pumped-storage group should fluctuate around the theoretical output value 31, which may be slightly lower than the theoretical output value 31 (as indicated by point 33) or slightly higher than the theoretical output value 31 (as indicated by point 32), but with a small fluctuation range. Of course, the actual measured output value of the pumped-storage group may be equal to the theoretical output value 31. Once the runner of the pump turbine is damaged, the capability of the pump turbine for energy conversion is greatly reduced. The ability of the pumped storage unit to convert water energy into electric energy is greatly reduced, and the same output force can be generated only by consuming more water than when the runner is not damaged. This means that the output of the pumped storage unit is much smaller than that of the pumped storage unit without the damage of the runner under the same opening degree of the guide vane, that is, under the same servomotor stroke. At the moment, the actual output force 34 of the pumped storage unit is certainly smaller than the theoretical output force value 31, and a large enough output force difference value is certainly generated between the theoretical output force and the actual output force of the pumped storage unit;
for the pumping working condition, when the pump turbine operates normally, the theoretical input value of the pumping energy storage unit is equivalent to the actual input value of the pumping energy storage unit obtained by real-time measurement in the unit operation process. That is, the actual input value obtained by the actual measurement of the pumped-storage group should fluctuate around the theoretical input value 41, which may be slightly lower than the theoretical output value 41 (as indicated by point 43) or slightly higher than the theoretical output value 41 (as indicated by point 42), but with a small fluctuation range. Of course, the actual input value obtained by the actual measurement of the pumped-storage group may also be equal to the theoretical input value 41. Once the pump turbine runner is damaged, the ability of the pump storage unit to convert electric energy into hydraulic energy is greatly reduced, and the same hydraulic energy can be generated only by consuming more electric energy than when the runner is not damaged. This means that the input force of the pumped storage unit is much smaller than that when the runner is not damaged at the same guide vane opening, that is, at the same servomotor stroke. The actual force input 44 of the pumped-storage group must be smaller than the theoretical force input 41, and a sufficiently large force input difference must occur between the actual force input and the actual force input of the pumped-storage group.
The other steps are the same as those in one of the first to third embodiments.
The fifth concrete implementation mode: determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the water pump turbine power generation working condition/water pumping working condition flow changing along with the output/input force of the water pumping energy storage unit tP The method comprises the following steps:
as shown in fig. 5 and 6, when the pump turbine is operating stably, a theoretical relationship curve 50 of the flow rate of the pump turbine changing with the output of the group and a theoretical relationship curve 60 of the flow rate of the pumping condition changing with the input of the group can be respectively determined according to the water levels of the upstream and the downstream. Then, according to the output value of the pumped storage unit, the theoretical power generation flow 51 of the pump turbine can be determined; and the theoretical pumping flow 61 of the pump turbine can be determined according to the input value of the pumping energy storage unit.
In this embodiment, for the power generation condition, when the pump turbine operates normally, the theoretical power generation flow value of the pump turbine should be equivalent to the actual power generation flow value obtained by real-time measurement in the unit operation process. That is, the actual generated current value obtained by the actual measurement of the pump turbine should fluctuate around the theoretical generated current amount 51, and may be slightly lower than the theoretical generated current amount 51 (as indicated by a point 53) or slightly higher than the theoretical generated current amount 51 (as indicated by a point 52), but the fluctuation range is small. Of course, the actual generated flow value obtained by the actual measurement of the pump turbine may be equal to the theoretical generated flow 51. Once the pump turbine runner is damaged, the capacity of the pump turbine for energy conversion is greatly reduced, and the actual power generation flow of the pump turbine under the working condition is much larger than the theoretical power generation flow. At this time, the value of the actual power generation flow point 54 of the pump turbine is certainly larger than the value of the theoretical power generation flow 51, and a sufficiently large flow difference value is certainly generated between the theoretical power generation flow and the actual power generation flow of the turbine;
for the pumping condition, when the pump turbine operates normally, the theoretical pumping flow value of the pump turbine should be equivalent to the actual pumping flow value obtained by real-time measurement in the operation process of the unit. That is, the actual pumping flow value obtained by the actual measurement of the pump turbine should fluctuate around the theoretical pumping flow 61, which may be slightly lower than the theoretical pumping flow 61 (as indicated by point 63) or slightly higher than the theoretical pumping flow 61 (as indicated by point 62), but the fluctuation range is small. Of course, the actual pumping flow value obtained by the actual measurement of the pump turbine may be equal to the theoretical pumping flow 61. Once the runner of the pump-turbine is damaged, the energy conversion capability of the pump-turbine is greatly reduced, and the actual pumping flow of the pump-turbine under the working condition is greatly reduced compared with the theoretical pumping flow. At this time, the value of the actual pumping flow point 64 of the pump turbine must be smaller than the value of the theoretical pumping flow 61, and a sufficiently large flow difference must occur between the theoretical pumping flow and the actual pumping flow.
The other steps are the same as those in one of the first to fourth embodiments.
The sixth specific implementation mode: determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the water pump turbine power generation working condition/water pumping working condition flow along with the change of the stroke of the servomotor tS The method comprises the following steps:
as shown in fig. 7 and 8, when the pump turbine is stably operated, a theoretical relationship curve 70 of the flow of the pump turbine under the power generation condition varying with the stroke of the servomotor and a theoretical relationship curve 80 of the flow of the pump turbine under the water pumping condition varying with the stroke of the servomotor are respectively determined according to the water levels of the upstream and the downstream. And respectively determining the theoretical power generation working condition flow 71 and the theoretical water pumping working condition flow 81 of the pump turbine according to the servomotor stroke value of the pump turbine.
In the embodiment, when the pump turbine operates normally, the theoretical flow value of the pump turbine is equivalent to the actual flow value obtained by real-time measurement in the operation process of the unit. That is, the actual flow value obtained by actual measurement of the pump turbine fluctuates around the theoretical power generation operating condition flow 71 and the theoretical pumping operating condition flow 81, may be slightly lower than the theoretical power generation operating condition flow 71 and the theoretical pumping operating condition flow 81 (as shown by points 73 and 83), and may also be slightly higher than the theoretical power generation operating condition flow 71 and the theoretical pumping operating condition flow 81 (as shown by points 72 and 82), but the fluctuation range is very small. Of course, the actual flow value obtained by the actual measurement of the pump turbine may be equal to the theoretical power generation condition flow 71 and the theoretical pumping condition flow 81. Once the runner of the pump turbine is damaged, the energy conversion capability of the pump turbine is greatly reduced.
The flow reflected on the pump turbine is as follows: for the power generation working condition, the flow rate of the actual power generation working condition is much larger than that of the theoretical power generation working condition. At this time, the value of the actual power generation condition flow point 74 of the pump turbine is certainly larger than the value of the theoretical power generation condition flow 71, and a sufficiently large flow difference value is certainly generated between the theoretical power generation condition flow and the actual power generation condition flow of the pump turbine;
for the water pumping working condition, the flow rate of the actual water pumping working condition is reduced greatly compared with the flow rate of the theoretical water pumping working condition. At this time, the value of the actual pumping condition flow point 84 of the pump turbine is certainly smaller than the value of the theoretical pumping condition flow 81, and a sufficiently large flow difference value is certainly generated between the theoretical pumping condition flow and the actual pumping condition flow of the pump turbine.
The other steps are the same as those in one of the first to fifth embodiments.
The seventh embodiment: determining the theoretical head H of the water pump turbine under the corresponding working condition according to the theoretical relation curve of the head/lift of the water pump turbine along with the change of the upstream and downstream water level differences tT And theoretical lift H tP The specific process comprises the following steps:
the pumped storage unit operates stably under a certain working condition, which means that the upstream and downstream water levels and the head/lift of the pump turbine are determined at the moment, and a theoretical relation curve 90 of the head of the pump turbine changing along with the upstream and downstream water level difference and a theoretical relation curve 100 of the lift changing along with the upstream and downstream water level difference can be determined according to the upstream and downstream water levels, as shown in fig. 9 and 10. And then according to the difference value of the water levels of the upper part and the lower part under the working condition, the theoretical water head 91 and the theoretical lift 101 of the water turbine of the water pump under the working condition can be determined.
In this embodiment, in case pump turbine runner takes place damaged phenomenon, the change that flood peak and lift reflection are on the operating mode of generating electricity and the operating mode of drawing water is different: for the working condition of power generation, the energy level contained in the water body represented by the water head is not changed, so that the water head is not obviously changed no matter whether the runner of the pump turbine is damaged or not. That is, the actual water head value obtained by the actual measurement of the pump turbine should be equal to the theoretical water head 91, may be slightly lower than the theoretical water head 91 (as shown by a point 93), and may be slightly higher than the theoretical water head 91 (as shown by a point 92), but the fluctuation range is very small;
for the pumping condition, the lift of the water pump is the direct reflection of the energy conversion capability of the water pump. The stronger the energy conversion capability of the water pump is, the higher the lift is, and conversely, the lower the lift is. Once the runner blades of the pump turbine are damaged, the energy conversion capability of the pump is greatly reduced. The actual lift is much lower than the theoretical lift, which is reflected in the lift of the water pump. At this time, the value of the actual head point 104 of the pump turbine must be smaller than the value of the theoretical head 101, and a sufficiently large head difference value must occur between the theoretical head and the actual head of the pump turbine.
The other steps are the same as those in one of the first to sixth embodiments.
The specific implementation mode is eight: the step four of obtaining the pump turbine runner damage efficiency judgment coefficient comprises the following steps:
ζ 1 ＝C 1 -Δη
therein, ζ 1 Is the determination coefficient of the efficiency of the damage of the water pump turbine runner, C 1 =0.01 is a constant, Δ η = | η t -η m L is the difference between the theoretical efficiency and the actual efficiency of the pump-turbine determined according to the theoretical relation curve of the change of the efficiency of the pump-turbine along with the output/input force of the pumped storage unit under the corresponding operating condition, eta m Actual efficiency of the water pump turbine corresponding to the operating condition;
for the power generation working condition:
Figure BDA0003018213960000081
for the pumping condition:
Figure BDA0003018213960000082
wherein, P e Is the actual output/input force, eta, of the pumped storage unit under the corresponding operating condition e Is the actual efficiency of the generator motor under the corresponding operating condition, ρ is the density of water, g is the gravitational acceleration, Q m Is the actual flow, H, of the water turbine of the water pump corresponding to the operating condition m Is the actual head/lift of the water turbine of the water pump corresponding to the operating condition.
The other steps are the same as those in one of the first to seventh embodiments.
The specific implementation method nine: the fourth step of obtaining the judgment coefficient of the output force/the input force of the damage of the water pump turbine runner comprises the following steps:
ζ 2 ＝C 2 -δ
therein, ζ 2 Is the determination coefficient of the output/input force of the damaged runner of the pump turbine,
Figure BDA0003018213960000083
the relative deviation between the theoretical output/input force and the actual output/input force of the pump turbine is determined according to the theoretical relation curve of the output/input force of the pumped storage unit along with the stroke change of the servomotor of the pump turbine under the corresponding working condition, C 2 =0.05 is a constant, Δ P = | P t -P e I is the difference between the theoretical output/input force and the actual output/input force of the pump turbine determined according to the theoretical relation curve of the output/input force of the pumped storage unit along with the change of the stroke of the servomotor of the pump turbine under the corresponding operating condition, P t The theoretical output/input force of the pumped storage unit under the corresponding working condition is determined according to a theoretical relation curve of the output/input force of the pumped storage unit along with the stroke change of the servomotor of the water pump water turbine.
The other steps are the same as those in the first to eighth embodiments.
The detailed implementation mode is ten: the fourth step of obtaining a flow judgment coefficient determined according to a theoretical relation curve of the flow of the pump turbine rotating wheel damage under the power generation working condition/the pumping working condition of the pump turbine along with the change of the output/input of the pumped storage unit comprises the following specific steps:
Figure BDA0003018213960000091
in the formula, ζ 3 Is a water pump turbine runner damage flow determination coefficient,
Figure BDA0003018213960000092
the relative deviation between the theoretical flow and the actual flow of the pump turbine is determined according to the theoretical relation curve of the change of the flow of the pump turbine under the power generation working condition/the pumping working condition along with the output/input force of the pumping energy storage unit under the corresponding working condition, C 3 =0.015 is a constant;
wherein the content of the first and second substances,
Figure BDA0003018213960000093
in the formula,. DELTA.Q P The difference between the theoretical flow and the actual flow of the pump turbine is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/pumping working condition along with the change of the output force/input force of the pumping energy storage unit under the corresponding operating working condition;
for the power generation condition: delta Q P ＝Q m -Q tP ；
For the pumping condition: delta Q P ＝Q tP -Q m ；
The other steps are the same as those in one of the first to ninth embodiments.
The concrete implementation mode eleven: the fourth step of obtaining the flow judgment coefficient determined by the damage of the water pump turbine runner according to the theoretical relation curve of the water pump turbine power generation working condition/water pumping working condition flow along with the change of the stroke of the servomotor comprises the following steps:
ζ 4 ＝ω-C 4
in the formula, ζ 4 The flow rate judgment coefficient is determined according to a theoretical relation curve of the flow rate of the pump turbine along with the change of the stroke of the servomotor when the pump turbine is damaged,
Figure BDA0003018213960000094
the relative deviation between the theoretical flow of the pump-turbine and the actual flow of the pump-turbine is determined according to the theoretical relation curve of the flow of the pump-turbine under the power generation working condition/water pumping working condition along with the change of the stroke of the servomotor under the corresponding working condition, C 4 =0.012 is constant, Δ Q S The difference between the theoretical flow of the pump turbine and the actual flow of the pump turbine is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/water pumping working condition along with the change of the stroke of the servomotor under the corresponding operating working condition;
for the power generation working condition: delta Q S ＝Q m -Q tS ；
For the pumping condition: delta Q S ＝Q tS -Q m ；
The other steps are the same as in one of the first to tenth embodiments.
The specific implementation mode twelve: the step four of obtaining the determination coefficient of the damaged water head of the water pump turbine runner comprises the following steps:
Figure BDA0003018213960000101
in the formula, ζ 5 Is the determination coefficient of the damaged water head of the water pump turbine runner, C 5 =0.005 is a constant number,
Figure BDA0003018213960000102
the relative deviation delta H between the theoretical water head and the actual water head of the pump turbine is determined according to a theoretical relation curve of the variation of the water head/lift of the pump turbine along with the difference of water levels between the upstream and the downstream under the working condition of power generation T ＝|H m -H tT And l is the difference between the theoretical water head and the actual water head of the pump turbine determined according to a theoretical relation curve of the variation of the water head/lift of the pump turbine along with the difference between the water heads of the upstream and the downstream under the power generation working condition.
The other steps are the same as in one of the first to eleventh embodiments.
The specific implementation mode thirteen: the step four of obtaining the pump turbine runner damage lift determination coefficient comprises the following steps:
ζ 6 ＝γ-C 6
in the formula, ζ 6 Is a pump turbine runner damage lift determination coefficient,
Figure BDA0003018213960000103
the relative deviation between the theoretical lift and the actual lift of the pump turbine is determined according to a theoretical relation curve that the water head/lift of the pump turbine changes along with the difference between the water heads of the pump turbine and the water heads of the upstream and the downstream under the condition of pumping water, C 6 =0.05 constant,. DELTA.H P ＝|H tP -H m The water pump turbine theoretical lift is determined according to a theoretical relation curve of the variation of the water pump turbine head/lift along with the water level difference between the upstream and the downstream under the water pumping working condition;
the other steps are the same as those in one to twelve embodiments.
The specific implementation mode fourteen are as follows: and in the step five, judging whether the turbine runner fails according to the judgment coefficient in the step four, wherein the method comprises the following steps:
when the coefficient of the pump turbine wheel breakage determination meets zeta 1 ≥0∧ζ 2 ≥0∧ζ 3 ≥0∧ζ 4 ≥0∧ζ 5 ≥0∧ζ 6 And if not, indicating that the damage fault of the water pump turbine runner does not occur.
The other steps are the same as in one of the first to thirteenth embodiments.

Claims (8)

1. A method for detecting damage of a pump turbine runner is characterized by comprising the following specific steps:
acquiring an actual value of water level of upstream and downstream water pumps and turbines which stably run under a power generation working condition and a pumping working condition, an actual value of pumped storage output/input force, an actual value of a water head of the water pump and turbine, an actual value of a lift, an actual value of a stroke of an actual servomotor and an actual value of flow;
step two, obtaining a theoretical value of the correlation quantity under the working condition corresponding to the information collected in the step one, and determining through the following mode:
determining theoretical efficiency eta of the water pump turbine under corresponding working conditions according to the theoretical relation curve of the water pump turbine efficiency changing along with the output/input of the pumped storage unit t ；
Determining theoretical output/input force P of the pumped storage unit under corresponding working conditions according to a theoretical relation curve of output/input force of the pumped storage unit along with stroke change of a servomotor of a water pump water turbine t ；
Determining theoretical flow Q of the water pump turbine under corresponding working conditions according to a theoretical relation curve of the flow of the water pump turbine under the power generation working conditions/the water pumping working conditions along with the change of the output force/the input force of the water pumping energy storage unit tP ；
Determining theoretical flow Q of the water turbine of the water pump under corresponding working conditions according to a theoretical relation curve of the flow of the water turbine of the water pump under the power generation working conditions/water pumping working conditions along with the change of the stroke of the servomotor ts ；
Determining water under corresponding working conditions according to a theoretical relation curve of water pump turbine head/lift along with changes of upstream and downstream water level differencesTheoretical head H of water pump turbine tT And theoretical lift H tP ；
Calculating an actual efficiency value according to output/input force information of the pumped storage unit, water head and lift information of a water pump turbine and flow information in combination with gravity acceleration, the efficiency of a power generation motor under the power generation working condition and the pumping working condition of the pumped storage unit and the density of water;
step four, acquiring a damage judgment coefficient of the water turbine of the water pump according to the actual value obtained in the step one, the theoretical value obtained in the step two and the actual efficiency value obtained in the step three;
the pump turbine breakage determination coefficient includes: determining the coefficient of the damage efficiency of the water pump turbine runner; judging the coefficient of output/input force of the damaged runner of the pump turbine; the flow judgment coefficient is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/pumping working condition of the pump turbine along with the change of the output force/input force of the pumping energy storage unit when the pump turbine runner is damaged; determining a flow determination coefficient according to a theoretical relation curve of the flow of the water pump turbine along with the change of the stroke of the servomotor when the water pump turbine runner is damaged; determining coefficient of a damaged water head of a water pump turbine runner; determining coefficient of pump turbine runner damage lift;
step five, judging whether the turbine runner fails according to the judgment coefficient of the step four:
when the coefficient of the pump turbine wheel breakage determination meets zeta 1 ≥0∧ζ 2 ≥0∧ζ 3 ≥0∧ζ 4 ≥0∧ζ 5 ≥0∧ζ 6 And if the detected value is more than or equal to 0, the water pump turbine runner breakage fault is generated, otherwise, the water pump turbine runner breakage fault is not generated.
2. The method of claim 1 for inspecting a hydroturbine runner for breakage, wherein: in the first step, the actual water head value of the water turbine of the water pump is obtained through water head measuring equipment of the water turbine; the actual value of the lift is obtained by lift measuring equipment; the actual servomotor stroke value is obtained through servomotor stroke measuring equipment of a water pump turbine; the actual flow value is measured by a flow measuring device of the water turbine.
3. A method of testing for breakage of a pump turbine runner according to claim 2 or 1, wherein: the step four of obtaining the damage efficiency judgment coefficient of the water pump turbine runner comprises the following steps:
ζ 1 ＝C 1 -Δη
therein, ζ 1 Is the determination coefficient of the efficiency of the pump turbine runner damage, C 1 =0.01 is constant, Δ η is the difference between the theoretical efficiency and the measured efficiency of the pump turbine determined according to the theoretical relationship curve of the pump turbine efficiency changing with the output/input of the pumped storage unit under the corresponding operating condition, η m Actual efficiency of the water pump turbine corresponding to the operating condition;
for the power generation condition:
Figure FDA0003990141430000021
for the pumping condition:
Figure FDA0003990141430000022
wherein, P e Is the actual output/input force, eta, of the pumped storage unit under the corresponding operating condition e Is the actual efficiency of the generator motor under the corresponding operating condition, ρ is the density of water, g is the gravitational acceleration, Q m Is the actual flow rate, H, of the water turbine of the water pump corresponding to the operating condition m Is the actual head/lift of the water turbine of the water pump corresponding to the operating condition.
4. A method of verifying a pump turbine runner breakage as claimed in claim 3, wherein: the fourth step of obtaining the judgment coefficient of the output force/the input force of the damage of the water pump turbine runner comprises the following steps:
ζ 2 ＝C 2 -δ
therein, ζ 2 Is a determination coefficient of the output/input force of the damage of the water pump turbine runner,
Figure FDA0003990141430000023
the relative deviation between the theoretical output/input force and the actual output/input force of the pump turbine is determined according to the theoretical relation curve of the output/input force of the pumped storage unit along with the stroke change of the servomotor of the pump turbine under the corresponding working condition, C 2 =0.05 is a constant, Δ P = | P t -P e I is the difference between the theoretical output/input force and the actual output/input force of the pump turbine determined according to the theoretical relation curve of the output/input force of the pumped storage unit along with the change of the stroke of the servomotor of the pump turbine under the corresponding operating condition, P t The theoretical output/input force of the pumped storage unit under the corresponding working condition is determined according to a theoretical relation curve of the output/input force of the pumped storage unit along with the stroke change of the servomotor of the water pump turbine.
5. The method of claim 4, wherein the method comprises the steps of: the fourth step of obtaining a flow judgment coefficient determined according to a theoretical relation curve of the flow of the pump turbine rotating wheel damage under the power generation working condition/the pumping working condition of the pump turbine along with the change of the output/input of the pumped storage unit comprises the following specific steps:
Figure FDA0003990141430000031
in the formula, ζ 3 The flow determination coefficient is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/pumping working condition of the pump turbine along with the change of the output force/input force of the pumping energy storage unit when the runner of the pump turbine is damaged,
Figure FDA0003990141430000032
the relative deviation between the theoretical flow and the actual flow of the pump turbine is determined according to the theoretical relation curve of the change of the flow of the pump turbine under the power generation working condition/the pumping working condition along with the output/input force of the pumping energy storage unit under the corresponding working condition, C 3 =0.015 is a constant;
wherein the content of the first and second substances,
Figure FDA0003990141430000033
in the formula,. DELTA.Q P The difference between the theoretical flow and the actual flow of the pump turbine is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/pumping working condition along with the change of the output force/input force of the pumping energy storage unit under the corresponding operating working condition;
for the power generation working condition: delta Q P ＝Q m -Q tP ；
For the pumping condition: delta Q P ＝Q tP -Q m 。
6. The method of claim 5, wherein the method comprises the steps of: the fourth step of obtaining the flow judgment coefficient determined by the pump turbine damage according to the theoretical relation curve of the flow of the pump turbine under the power generation working condition/water pumping working condition along with the change of the stroke of the servomotor comprises the following steps:
ζ 4 ＝ω-C 4
in the formula, ζ 4 The flow rate judgment coefficient is determined according to a theoretical relation curve of the flow rate of the pump turbine along with the change of the stroke of the servomotor when the pump turbine is damaged,
Figure FDA0003990141430000034
the relative deviation between the theoretical flow of the pump turbine and the actual flow of the pump turbine is determined according to the theoretical relation curve of the flow of the pump turbine under the power generation working condition/water pumping working condition along with the change of the stroke of the servomotor under the corresponding working conditions, C 4 =0.012 is a constant, Δ Q S The difference between the theoretical flow of the pump turbine and the actual flow of the pump turbine is determined according to a theoretical relation curve of the flow of the pump turbine under the power generation working condition/water pumping working condition along with the change of the stroke of the servomotor under the corresponding operating working condition;
for the power generation working condition: delta Q S ＝Q m -Q tS ；
For the pumping condition: delta Q S ＝Q tS -Q m 。
7. The method of claim 6, wherein the method comprises the steps of: the step four of obtaining the determination coefficient of the damaged water head of the water pump turbine runner comprises the following steps:
Figure FDA0003990141430000035
in the formula, ζ 5 Is the determination coefficient of the damaged water head of the water pump turbine runner, C 5 =0.005 is a constant number which,
Figure FDA0003990141430000036
the relative deviation delta H between the theoretical water head and the actual water head of the pump turbine is determined according to a theoretical relation curve of the variation of the water head/lift of the pump turbine along with the difference of water levels between the upstream and the downstream under the working condition of power generation T ＝|H m -H tT And | is the difference between the theoretical water head and the actual water head of the pump turbine determined according to a theoretical relation curve of the variation of the water head/lift of the pump turbine along with the difference between the water heads of the upstream and the downstream under the power generation working condition.
8. The method of claim 7 for inspecting a hydroturbine runner for breakage, wherein: the step four of obtaining the pump turbine runner damage lift determination coefficient comprises the following steps:
ζ 6 ＝γ-C 6
in the formula, ζ 6 Is a pump turbine runner damage lift determination coefficient,
Figure FDA0003990141430000041
the relative deviation between the theoretical lift and the actual lift of the pump turbine is determined according to a theoretical relation curve that the water head/lift of the pump turbine changes along with the difference between the water heads of the pump turbine and the water heads of the upstream and the downstream under the condition of pumping water, C 6 =0.05 is a constant,. DELTA.H P ＝|H tP -H m I is the theoretical lift of the pump turbine determined according to the theoretical relation curve of the variation of the pump turbine head/lift with the upstream and downstream water level differences under the condition of pumping waterDifference from the actual head.
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