CN113090440A - 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
CN113090440A
CN113090440A CN202110395049.1A CN202110395049A CN113090440A CN 113090440 A CN113090440 A CN 113090440A CN 202110395049 A CN202110395049 A CN 202110395049A CN 113090440 A CN113090440 A CN 113090440A
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pump turbine
water
theoretical
turbine
flow
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CN202110395049.1A
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CN113090440B (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 at present, 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, so that serious associated accidents occur. The invention comprises the following steps: 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 water 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 turbine runner.
Background
With the gradual improvement of the requirement of users on the operation stability of 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 the unit and checking the operation 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 totally immersed in water, the corresponding sensors of the parts exposed in the air of the pump turbine runner can not be utilized to carry out targeted detection and measurement like other parts of the pump turbine, so that no direct and reliable method can detect out the damage condition of the pump turbine runner, 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 water pump turbine runner is damaged or not cannot be judged according to the change of the external characteristics of a water pump turbine so as to cause serious associated accidents at present, and provides a method for detecting the damage of the water 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 unitt；
Water turbine with water pump according to output/input force of pumped storage unitDetermining theoretical output/input force P of the pumped storage unit under corresponding working conditions according to the theoretical relation curve of the stroke change of the servomotort；
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 unittP；
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 servomotortS；
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 differencestTAnd theoretical lift HtP；
Calculating an actual efficiency value according to the stored output/input force information, the water head and lift information of the water pump turbine and the 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 pump turbine 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 coefficient of damage efficiency of a 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;
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 head/lift of the pump turbine, combines the problem that the efficiency of the pump turbine is reduced because the parts and the components of the embedded part of the pump turbine, the water guide mechanism, the water guide bearing of the rotating part, the rotating wheel and the like are broken down, and the reason that the output of the unit is reduced because the parts and the components of the embedded part of the pump turbine, the water guide mechanism, the water guide bearing of the rotating part, the rotating wheel and the like and the generator are broken down, introduces the flow reduction evaluation index of the pump turbine to eliminate the possibility that the water guide bearing of the rotating part of the generator motor and the pump turbine is broken down, and simultaneously introduces the water head of the pump turbine under the power generation working condition of the pumped storage unit and the water head/lift reduction evaluation index of the pump turbine under the pumping working condition to discharge the embedded The method comprises the steps of concentrating the fault position of a unit on a rotating wheel of a water turbine, selecting the output/input force, the flow and the head/lift of the water pump turbine on external characteristics according to the phenomenon that the energy conversion capacity of the water pump turbine is greatly reduced when the rotating wheel of the water pump turbine is damaged and has a fault, taking the actual efficiency of the water pump turbine calculated according to the parameters as an evaluation object, comparing the actual efficiency with corresponding theoretical values under the working condition, calculating the difference between the theoretical value and the actual measurement value of the characteristic quantity in a mode of corresponding to the damage judgment coefficients of a plurality of groups of rotating wheels of the water pump turbine with different characteristic quantities, and finally judging whether the rotating wheel of the water pump turbine has the damage and fault 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 turbine;
FIG. 4 is a theoretical relation 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 water pump turbine servomotor;
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 combination of the flow of the pumping condition of the pump turbine and the inlet force variation;
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 the variation of the water head of the pump turbine with the difference between the water levels upstream and downstream;
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 unitt；
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 turbinet；
Storage along with water pumping according to water pump turbine power generation working condition/water pumping working condition flowTheoretical flow Q of water pump turbine under corresponding working condition is determined by theoretical relation curve of output/input force change of energy unittP；
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 servomotortS；
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 differencestTAnd theoretical lift HtP；
Calculating an actual efficiency value according to the stored output/input force information, the water head and lift information of the water pump turbine and the 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 coefficient of damage efficiency of a 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;
and step five, judging whether the turbine runner has a fault 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 turbine; the actual flow value is measured by a flow measuring device of the water turbine.
Other steps are the same as those 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 force/input force of the pumped storage unittThe 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, may be slightly higher than the theoretical efficiency 11 (as indicated by point 12), and may also be 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: 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 servomotortThe 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 the servomotor stroke measuring equipment of the water pump and the water turbine. 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 force value obtained by the pumped-storage unit actually measured should fluctuate around the theoretical force value 31, which may be slightly lower than the theoretical force value 31 (as indicated by point 33) or slightly higher than the theoretical force value 31 (as indicated by point 32), but the fluctuation range is small. 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 energy conversion capability of the pump turbine 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 pumped-storage group actually measures 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 the fluctuation range is small. Of course, the actual force value obtained by the actual measurement of the pumped-storage group may also be equal to the theoretical force 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 of the pumped storage unit without the damage of the runner under the same guide vane opening, that is, under 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 unittPThe 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 runner of the pump-turbine 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 servomotortSThe 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 this 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 condition flow 71 and the theoretical pumping condition flow 81, and may be slightly lower than the theoretical power generation condition flow 71 and the theoretical pumping condition flow 81 (as shown by points 73 and 83), or may be slightly higher than the theoretical power generation condition flow 71 and the theoretical pumping 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 necessarily smaller than the value of the theoretical pumping condition flow 81, and a sufficiently large flow difference value must occur 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 differencestTAnd theoretical lift HtPThe 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 the pump turbine runner takes place the breakage phenomenon, the change of flood peak and lift reflection on electricity generation operating mode 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, the higher the lift, and conversely, the lower the lift. Once the runner blade of the pump turbine is damaged, the energy conversion capability of the water 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:
ζ1＝C1-Δη
therein, ζ1Is the determination coefficient of the efficiency of the damage of the water pump turbine runner, C10.01 is a constant, Δ η ═ ηt-ηmL 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, etamActual 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, PeIs the actual output/input force, eta, of the pumped storage unit under the corresponding operating conditioneIs the actual efficiency of the generator motor under the corresponding operating condition, ρ is the density of water, g is the acceleration of gravity, QmIs the actual flow rate, H, of the water turbine of the water pump corresponding to the operating conditionmIs 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:
ζ2＝C2-δ
therein, ζ2Is 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, C20.05 is a constant, Δ P ═ Pt-PeI 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, PtThe 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: and in the fourth step, a flow judgment coefficient determined according to a theoretical relation curve of the flow of the pump turbine under the power generation condition/pumping condition of the pump turbine along with the change of the output/input of the pumped storage unit is obtained, and the method specifically comprises the following steps:
Figure BDA0003018213960000091
in the formula, ζ3Is 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, C30.015 is a constant;
wherein,
Figure BDA0003018213960000093
in the formula,. DELTA.QPThe 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 QP＝Qm-QtP；
For the pumping condition: delta QP＝QtP-Qm；
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 servomotor stroke comprises the following steps:
ζ4＝ω-C4
in the formula, ζ4The 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 water pump turbine is pressed to generate power under the corresponding working condition/pump waterThe relative deviation between the theoretical flow of the pump turbine and the actual flow of the pump turbine determined by the theoretical relation curve of the working condition flow along with the change of the stroke of the servomotor C40.012 is a constant, Δ QSThe 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 QS＝Qm-QtS；
For the pumping condition: delta QS＝QtS-Qm；
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, ζ5Is the determination coefficient of the damaged water head of the water pump turbine runner, C50.005 is a constant which is,
Figure BDA0003018213960000102
the relative deviation between the theoretical water head and the actual water head of the pump turbine, delta H, is determined according to the theoretical relation curve that the water head/lift of the pump turbine changes along with the difference between the water heads of the upstream and the downstream under the working condition of power generationT＝|Hm-HtTAnd | 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 is thirteen: the step four of obtaining the pump turbine runner damage lift determination coefficient comprises the following steps:
ζ6＝γ-C6
in the formula, ζ6Is 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, C60.05 is a constant,. DELTA.HP＝|HtP-HmThe I is the difference between the theoretical lift and the actual lift 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 pump turbine and the water heads of the upstream and the downstream under the working condition of pumping water;
the other steps are the same as those in one to twelve embodiments.
The specific implementation mode is fourteen: 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 water pump turbine runner breakage determination coefficient meets zeta1≥0∧ζ2≥0∧ζ3≥0∧ζ4≥0∧ζ5≥0∧ζ6And if not, indicating that the damage fault of the water pump turbine runner does not occur.
The other steps are the same as those in one to thirteen embodiments.

Claims (9)

1. A method for detecting damage of a water 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 corresponding working condition of the information collected in the step one, and determining through the following mode:
determining water pump water under corresponding working conditions according to theoretical relation curve of water pump turbine efficiency along with output/input force change of pumped storage unitTheoretical efficiency η of the turbinet；
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 turbinet；
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 unittP；
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 servomotorts；
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 differencestTAnd theoretical lift HtP；
Calculating an actual efficiency value according to the stored output/input force information, the water head and lift information of the water pump turbine and the 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 pump turbine 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 coefficient of damage efficiency of a 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;
and step five, judging whether the turbine runner has a fault according to the judgment coefficient of the step four.
2. The method of claim 1 for inspecting a hydroturbine runner for breakage, wherein: 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 turbine; the actual flow value is measured by a flow measuring device of the water turbine.
3. A method of inspecting a pump turbine runner for breakage as claimed in claim 2 or 1, wherein: the step four of obtaining the pump turbine runner damage efficiency judgment coefficient comprises the following steps:
ζ1＝C1-Δη
therein, ζ1Is the determination coefficient of the efficiency of the damage of the water pump turbine runner, C1The value of 0.01 is a constant, delta eta is the difference between the theoretical efficiency and the actual efficiency of the pump turbine determined according to the theoretical relation curve of the pump turbine efficiency changing along with the output force/input force of the pumped storage unit under the corresponding operating working condition, and eta ismActual efficiency of the water pump turbine corresponding to the operating condition;
for the power generation working condition:
Figure FDA0003018213950000021
for the pumping condition:
Figure FDA0003018213950000022
wherein, PeIs the actual output/input force, eta, of the pumped storage unit under the corresponding operating conditioneIs the actual efficiency of the generator motor under the corresponding operating condition, ρ is the density of water, g is the acceleration of gravity, QmIs the actual flow rate, H, of the water turbine of the water pump corresponding to the operating conditionmIs the actual head/lift of the water turbine of the water pump corresponding to the operating condition.
4. The method of claim 3, wherein the method comprises the steps of: 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:
ζ2＝C2-δ
therein, ζ2Is the determination coefficient of the output/input force of the damaged runner of the pump turbine,
Figure FDA0003018213950000023
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, C20.05 is a constant, Δ P ═ Pt-PeI 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, PtThe 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.
5. The method of claim 4, wherein the method comprises the steps of: and in the fourth step, a flow judgment coefficient determined according to a theoretical relation curve of the flow of the pump turbine under the power generation condition/pumping condition of the pump turbine along with the change of the output/input of the pumped storage unit is obtained, and the method specifically comprises the following steps:
Figure FDA0003018213950000024
in the formula, ζ3The 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 FDA0003018213950000035
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, C30.015 is a constant;
wherein,
Figure FDA0003018213950000031
in the formula,. DELTA.QPThe 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 QP＝Qm-QtP；
For the pumping condition: delta QP＝QtP-Qm。
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 damage of the water pump turbine according to the theoretical relation curve of the flow of the water 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:
ζ4＝ω-C4
in the formula, ζ4The 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 FDA0003018213950000032
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, C40.012 is a constant, Δ QSIs corresponding to the movementThe 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 operating condition;
for the power generation working condition: delta QS＝Qm-QtS；
For the pumping condition: delta QS＝QtS-Qm。
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 FDA0003018213950000033
in the formula, ζ5Is the determination coefficient of the damaged water head of the water pump turbine runner, C50.005 is a constant which is,
Figure FDA0003018213950000034
the relative deviation between the theoretical water head and the actual water head of the pump turbine, delta H, is determined according to the theoretical relation curve that the water head/lift of the pump turbine changes along with the difference between the water heads of the upstream and the downstream under the working condition of power generationT＝|Hm-HtTAnd | 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, wherein the method comprises the steps of: the step four of obtaining the pump turbine runner damage lift determination coefficient comprises the following steps:
ζ6＝γ-C6
in the formula, ζ6Is a pump turbine runner damage lift determination coefficient,
Figure FDA0003018213950000041
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, C60.05 is a constant,. DELTA.HP＝|HtP-HmAnd | is the difference between the theoretical lift and the actual lift 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 pump turbine and the water heads of the upstream and the downstream under the water pumping working condition.
9. The method of claim 8, wherein the step of inspecting the runner of the pump turbine for breakage comprises: 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 water pump turbine runner breakage determination coefficient meets zeta1≥0∧ζ2≥0∧ζ3≥0∧ζ4≥0∧ζ5≥0∧ζ6And if not, indicating that the damage fault of the water pump turbine runner does not occur.
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