CN107191308B - A kind of prediction technique of mixed flow pump turbine complete characteristic curve - Google Patents
A kind of prediction technique of mixed flow pump turbine complete characteristic curve Download PDFInfo
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- CN107191308B CN107191308B CN201710611029.7A CN201710611029A CN107191308B CN 107191308 B CN107191308 B CN 107191308B CN 201710611029 A CN201710611029 A CN 201710611029A CN 107191308 B CN107191308 B CN 107191308B
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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
- F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
- F03B11/008—Measuring or testing arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
- F03B13/06—Stations or aggregates of water-storage type, e.g. comprising a turbine and a pump
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- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- 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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Abstract
The invention discloses a kind of prediction techniques of mixed flow pump turbine complete characteristic curve, including：In conjunction with the characteristics of actual measurement method for complete characteristic curves of reversible pump turbine, the internal character analysis of description flow omnicharacteristic and torque omnicharacteristic is corrected；The unit parameter for counting characteristic operating point on different specific speed method for complete characteristic curves of reversible pump turbine, establishes the dominant functional relation between the unit parameter of each characteristic operating point and pump turbine optimum operating condition specific speed and relative opening of guide vane；The unit parameter of each characteristic operating point under different guide vane openings is obtained according to above-mentioned dominant functional relation, so that it is determined that the undetermined coefficient in modified internal character analysis, obtains the prediction complete characteristic curve of arbitrary specific speed pump turbine.The complete characteristic curve error very little that this method is predicted, therefore when carrying out rotary wheel model experiment, only a few features operating mode can be tested, model test process is accelerated in guidance.
Description
Technical field
The present invention relates to Hydraulic Design fields, and in particular to a kind of prediction side of mixed flow pump turbine complete characteristic curve
Method.
Background technology
With the sustained and rapid development of China's economic society, power grid peak-valley difference increasingly increases, peak modulation capacity deficiency gradually at
In order to restrict the outstanding problem of China's power system development.And hydroenergy storage station is being solved as a kind of outstanding peak regulation tool
The peak regulation pressure and improve intelligent grid operation that certainly the consumption problem, nuclear power large-scale grid connection of wind-powered electricity generation extensive development are brought
Effect in terms of flexibility and safety can not be substituted.
However, being different from conventional hydropower station, hydroenergy storage station change working is rapid, start and stop are frequent, in addition water pump water wheels
The special bidirectional flow-through characteristic of machine so that the more conventional power station of Calculations of Hydraulic Transient in hydroenergy storage station is much more complex, from
And threaten the safety and stability in power station.Therefore, under the background of China's hydroenergy storage station Large scale construction, research water-storage electricity
The intrinsic characteristic of Hydraulic Transient of standing process, has a very important significance the safe and stable operation in power station.
The four-quadrant complete characteristic curve of pump turbine is the key element for studying hydroenergy storage station Hydraulic Transient process.
But feasibility study and concept phase in power station often lack phase since model test is not carried out or prototype is also unselected
The complete characteristic curve answered brings many difficulties to the Preliminary design of hydroenergy storage station, and applies mechanically close specific speed unit
Complete characteristic curve, in fact it could happen that the concept phase, which respectively adjusts, protects parameter and is satisfied by design requirement, and when skill applies the review of stage prototype,
Certain adjust protects the exceeded situation of parameter, causes error larger.Therefore, how accurately pre- before pump turbine is selected
Method for complete characteristic curves of reversible pump turbine is surveyed, with the transient process in preliminary analysis hydroenergy storage station unit and pressure pipeline, guidance
Engineering design becomes important research direction.
Lack the feelings of method for complete characteristic curves of reversible pump turbine for hydroenergy storage station feasibility study and concept phase
Condition, when carrying out the calculating of hydroenergy storage station Calculations of Hydraulic Transient, it is common practice to apply mechanically head, single-machine capacity and specific speed
Similar method for complete characteristic curves of reversible pump turbine.However, using the meter of pump turbine runner complete characteristic curve similar in specific speed
Although calculation result and the result of calculation of prototype runner complete characteristic curve are similar on waveform, calculating extreme value difference is larger, causes
Or pipe design intensity is bigger than normal when Preliminary design, investment is caused to increase；Pipe design intensity is less than normal, and there are accident wind
Danger.Therefore, this way for applying mechanically method for complete characteristic curves of reversible pump turbine similar in head, single-machine capacity and specific speed cannot be accurate
Instruct the Preliminary design of engineering in ground.
Invention content
The technical problem to be solved by the present invention is to existing hydroenergy storage station Calculations of Hydraulic Transient computational methods, because of set
The method for complete characteristic curves of reversible pump turbine similar in head, single-machine capacity and specific speed causes error larger, cannot accurately refer to
The problem of leading engineering Preliminary design.
In order to solve the above-mentioned technical problem, the technical solution adopted in the present invention is to provide a kind of mixed flow pump turbine
The prediction technique of complete characteristic curve, includes the following steps：
In conjunction with actual measurement method for complete characteristic curves of reversible pump turbine the characteristics of, correct description flow omnicharacteristic and torque omnicharacteristic it is interior
Characteristic analytic theory；
The unit parameter for counting characteristic operating point on different specific speed method for complete characteristic curves of reversible pump turbine, establishes each feature work
Dominant functional relation between the unit parameter and pump turbine optimum operating condition specific speed and relative opening of guide vane of condition point；
The unit parameter of each characteristic operating point under different guide vane openings is obtained according to above-mentioned dominant functional relation, so that it is determined that
Undetermined coefficient in modified internal character analysis obtains the prediction complete characteristic curve of arbitrary specific speed pump turbine.
In the above-mentioned technical solutions, the calculation of the internal character analysis of flow omnicharacteristic and torque omnicharacteristic is described
Specially：
When pump turbine stable operation under hydraulic turbine condition and pump operating condition, pass through the stream to stream interface among runner
Fast triangle is analyzed, and the relationship between flow, rotating speed and the torque when pump turbine stable operation, Yi Jiliu are obtained
Relationship between amount, rotating speed and head；
By introducing unit speed, specific discharge and units of torque, above-mentioned relation formula is converted, description stream is just obtained
Measure the internal character analysis of omnicharacteristic and torque omnicharacteristic.
In the above-mentioned technical solutions, unit speed is introducedSpecific discharge
Units of torque M '1=M/D1 3H, hydraulic turbine condition efficiency etaT=1-STQT 2/ H=1-STQ1′2D1 4With pump operating condition efficiency etaP=(1+
SPQ1′2D1 4)-1, then specific discharge of the pump turbine in hydraulic turbine condition and pump operating condition stable operation, unit speed and
Relationship between units of torque is：
M′1T=αTQ′1T 2-βTQ′1Tn′1T
M′1P=-αPQ′1P 2+βPQ′1Pn′1P
aTn′1TQ′1T-bTn′1T 2+cTQ′1T 2=1
-aPn′1PQ′1P+bPn′1P 2-cPQ′1P 2=1
According to actual measurement complete characteristic curve feature, the operating point that specific discharge is zero in complete characteristic curve, specific torque
And be not zero, therefore above-mentioned formula is modified to：
M′1T=αTQ′1T 2-βTQ′1Tn′1T+γT
M′1P=-αPQ′1P 2+βPQ′1Pn′1P+γP
Wherein, subscript T represents hydraulic turbine condition, i.e. centripetal flow operating mode；Subscript P represents pump operating condition, i.e. centrifugal flow
Operating mode；n′1、Q′1With M '1Respectively unit speed, specific discharge and units of torque；η is hydraulic efficiency；N, Q and M is respectively water
Pump turbine rotating speed, flow and axle power square；D1For runner diameter；H is head or lift；S is loss coefficient；αT、βT、γT、aT、
bT、cTFor with unit geometric parameter and the relevant coefficient of hydraulic turbine condition parameter；αP、βP、γP、aP、bP、cPFor with unit geometric parameters
Number and the relevant coefficient of pump operating condition parameter.
When in the above-mentioned technical solutions, by the fundamental equation of pump turbine and to hydraulic turbine condition at runner
The analysis of flow velocity triangle obtains pump turbine under hydraulic turbine condition when stable operation, between flow, rotating speed and torque
Relational expression is：
There are following relationships for torque and shaft power when due to hydraulic turbine condition：
Simultaneous above-mentioned formula, the relational expression that can be obtained between flow, rotating speed and head are：
Wherein, subscript 1,2 respectively represents runner inlet and outlet；γ is fluid severe；G is acceleration of gravity；It is wide etc. relevant with stream interface among hydraulic turbine condition runner import and export flow angle and runner import and export
Coefficient；b1And b2Respectively represent guide vane height and outlet of rotary wheel axis plane projection width；α1And β2Respectively guide vane outlet stream angle and
Outlet of rotary wheel flow angle；The π of ω=2 n/60 are angular velocity of rotation；R is stream interface radius；P is shaft power.
Stream when in the above-mentioned technical solutions, according to the fundamental equation of pump turbine and to pump operating condition at runner
The analysis of fast triangle, flow, rotating speed when obtaining pump operating condition stable operation and the relationship between torque are：
Relationship between flow, rotating speed and head is：
Wherein, b is and pump operating condition runner import and export flow angle and the wide equal geometric parameters of runner import and export centre stream interface
With the relevant coefficient of duty parameter；For outlet of rotary wheel intermediate flow radius surface under pump operating condition.
In the above-mentioned technical solutions, when pump turbine stable operation under hydraulic turbine condition and pump operating condition, according to
The moment of momentum theorem, the fundamental equation that pump turbine can be obtained are respectively：
Wherein, subscript T, P respectively represents hydraulic turbine condition and pump operating condition；Subscript 1,2 respectively represents runner import and goes out
Mouthful；VuFor the circumferential components of mass flow absolute velocity.
The analysis of flow velocity triangle when in the above-mentioned technical solutions, by hydraulic turbine condition at runner, can obtain：
Above-mentioned formula is substituted into formulaIn, can obtain above-mentioned hydraulic turbine condition down-off,
Relational expression between rotating speed and torque；Wherein, VmFor flow rate on axial surface；U is runner peripheral speed.
The present invention has the following advantages：
(1) the characteristics of combining actual measurement method for complete characteristic curves of reversible pump turbine, has modified description flow omnicharacteristic and torque is entirely special
The internal character analysis of property；
(2) unit parameter of characteristic operating point on different specific speed method for complete characteristic curves of reversible pump turbine can be calculated, is tied
Modified internal character analysis is closed, it can be achieved that before pump turbine is selected, accurately predicts the complete of pump turbine
Characteristic curve；The complete characteristic curve of prediction can be used for the Preliminary design of ancillary works, be the operational safety of hydroenergy storage station
Design considerations is provided, tradition is overcome to apply mechanically method for complete characteristic curves of reversible pump turbine error similar in head, single-machine capacity and specific speed
Larger deficiency；
(3) due in the case of the unit parameter of known all characteristic operating point collection, being predicted using this method
Complete characteristic curve error very little, therefore when carrying out rotary wheel model experiment, only a few features operating mode can be tested, it instructs
Accelerate model test process.
Description of the drawings
Fig. 1 is a kind of prediction technique flow chart of mixed flow pump turbine complete characteristic curve in the present invention；
Fig. 2 is the flow velocity triangle that hydraulic turbine condition runner is imported and exported in the present invention；
Fig. 3 is each characteristic operating point distribution on most excellent aperture line in the present invention；
Fig. 4 is the relationship between the unit parameter and optimal specific speed of characteristic operating point O points in the present invention；
Fig. 5 is O in the present inventioniRelationship between the relative unit parameter and relative opening of guide vane of point set；
Fig. 6 is that the complete characteristic curve of actual measurement and theoretical prediction in the present invention compares；
Fig. 7 is the transient process comparison based on prototype omnicharacteristic and prediction omnicharacteristic in the present invention.
Specific implementation mode
In order to solve existing hydroenergy storage station Calculations of Hydraulic Transient computational methods, because apply mechanically head, single-machine capacity with
And method for complete characteristic curves of reversible pump turbine similar in specific speed causes error larger, cannot accurately instruct asking for engineering Preliminary design
Topic.The present invention proposes a kind of prediction technique of mixed flow pump turbine complete characteristic curve, is stablized in runner using flow
The speed triangle of flowing establishes the mathematical model of description pump turbine omnicharacteristic, and combines each feature on complete characteristic curve
The unit parameter of operating mode point set and specific speed and the statistical relationship of guide vane opening, to realize method for complete characteristic curves of reversible pump turbine
Theoretical prediction.
The present invention is described in detail with specific implementation mode with reference to the accompanying drawings of the specification.
An embodiment of the present invention provides a kind of prediction techniques of mixed flow pump turbine complete characteristic curve, as shown in Figure 1,
Include the following steps：
S1, when pump turbine stable operation under hydraulic turbine condition and pump operating condition, by stream interface among runner
Flow velocity triangle analyzed, obtain the relationship between flow, rotating speed and the torque when pump turbine stable operation, and
Relationship between flow, rotating speed and head.
S2, unit speed, specific discharge and units of torque are introduced, it is complete to convert the relational expression in step S1 to description flow
The internal character analysis of characteristic and torque omnicharacteristic, and actual measurement complete characteristic curve feature is combined, correct internal character analysis.
The unit parameter of characteristic operating point, establishes each spy on S3, statistics different specific speed method for complete characteristic curves of reversible pump turbine
Levy the dominant functional relation between the unit parameter and pump turbine optimum operating condition specific speed and relative opening of guide vane of operating point.
S4, based on modified internal character analysis in step S2, and under the different guide vane openings obtained according to step S3
The unit parameter of each characteristic operating point then can determine the undetermined coefficient in modified internal character analysis in step S2, to
Obtain the prediction complete characteristic curve of arbitrary specific speed pump turbine.
The realization principle of above-mentioned steps S1 is specific as follows：
When pump turbine stable operation under hydraulic turbine condition and pump operating condition, according to the moment of momentum theorem, can be derived from
The fundamental equation (Eulerian equation) of pump turbine is respectively：
Wherein, subscript T represents pump turbine operating mode, i.e. centripetal flow operating mode；Subscript P represents pump turbine operating mode,
That is centrifugal flow operating mode；Subscript 1,2 respectively represents runner inlet and outlet；M is axle power square；γ is fluid severe；Q is to enter to turn
Flow in wheel；VuR is velocity moment；VuFor the circumferential components of mass flow absolute velocity；R is stream interface radius；H is head or raises
Journey；η is hydraulic efficiency；ω is angular velocity of rotation；G is acceleration of gravity.
Analyzed by the flow velocity triangle to stream interface among hydraulic turbine condition runner shown in Fig. 2, can by formula (1) and
V in formula (2)u1And Vu2It is written as：
Wherein, Vm1And Vm2Respectively runner inlet and outlet flow rate on axial surface；b1And b2Respectively guide vane height and runner goes out
Mouth axis plane projection width；α1And β2Respectively guide vane outlet stream angle and outlet of rotary wheel flow angle.
Formula (5) and formula (6) are substituted into formula (1), can be obtained：
Simultaneously as there are following relationships for torque and shaft power when the hydraulic turbine：
Wherein, P is shaft power；The π of ω=2 n/60 are angular velocity of rotation；N is rotating speed.
Simultaneous formula (7) and formula (8), can obtain：
Formula (7) and formula (9) are respectively flow, rotating speed and torque of the pump turbine in hydraulic turbine condition stable operation
Between relationship and flow, rotating speed and head between relationship.Flow velocity when similarly, by analyzing pump operating condition at runner
Triangle, it is also possible to obtain the relationship between flow, rotating speed and torque of the pump turbine in pump operating condition stable operation, with
And the relationship between flow, rotating speed and head.Then the fundamental equation of pump turbine can be exchanged into：
Wherein,For among hydraulic turbine condition runner import and export flow angle and runner import and export
The wide equal geometric parameters of stream interface and the relevant coefficient of duty parameter；B be with pump operating condition runner import and export flow angle and runner into,
The intermediate stream interface in outlet is wide to wait geometric parameters and the relevant coefficient of duty parameter；For stream interface among outlet of rotary wheel under pump operating condition half
Diameter；ηT=(HT-STQT 2)/HT=1-STQT 2/HTFor hydraulic turbine condition efficiency；ηP=HP/(HP+SPQP 2)=(1+SPQP 2/HP)-1For
Pump operating condition efficiency；S is loss coefficient.
The realization principle of above-mentioned steps S2 is specific as follows：
Since complete characteristic curve is unit specific discharge, unit force under different guide vane openings under characterization steady running condition
The cluster curve of correlation between square and unit speed, therefore introduce unit speedSpecific dischargeUnits of torque M '1=M/D1 3H、ηT=1-STQT 2/ H=1-STQ1′2D1 4And ηP=(1+SPQ1′2D1 4
)-1, formula (10) is substituted into formula (13), can be converted：
M′1T=αTQ′1T 2-βTQ′1Tn′1T (14)
M′1P=-αPQ′1P 2+βPQ′1Pn′1P (15)
aTn′1TQ′1T-bTn′1T 2+cTQ′1T 2=1 (16)
-aPn′1PQ′1P+bPn′1P 2-cPQ′1P 2=1 (17)
According to actual measurement complete characteristic curve feature, the operating point that specific discharge is zero in complete characteristic curve, specific torque
And be not zero, therefore formula (14) and formula (15) should be modified to：
M′1T=αTQ′1T 2-βTQ′1Tn′1T+γT (18)
M′1P=-αPQ′1P 2+βPQ′1Pn′1P+γP (19)
Wherein, n '1For unit rotating speed (r/min)；D1 is runner diameter (m)；H is head or lift (m)；Q′1For unit stream
It measures (m3/s)；M′1For unit torque (Nm)；αT、βT、γT、aT、bT、cTIt is to join with geometric parameter and pump turbine operating mode
The relevant coefficient of number；αP、βP、γP、aP、bP、cPIt is and geometric parameter and the relevant coefficient of pump turbine duty parameter.
Formula (16) and formula (17) determine centripetal flow operating mode (Q ' respectively1T> 0) and centrifugal flow operating mode (Q '1P< 0) when
Flow omnicharacteristic；Torque when formula (18) and formula (19) determine pump turbine operating mode and pump turbine operating mode respectively is entirely special
Property.Formula (16)~formula (19) is to describe the mathematical model of pump turbine omnicharacteristic, also referred to as modified internal character analysis reason
By.
Due in above-mentioned each equation only there are three undetermined coefficient, as long as three spies in known corresponding operating mode area
Sign point unit parameter, convolution (16) to (19) can determine above-mentioned undetermined coefficient, to theoretical prediction complete characteristic curve.
The realization principle of above-mentioned steps S3 is specific as follows：
Every characteristic curve can regard the curve that each characteristic operating point of one timing of guide vane opening is formed by connecting paragraph by paragraph as,
Therefore, as long as the unit parameter of energy each characteristic point of Accurate Prediction, in conjunction with the mathematical model of the description complete characteristic curve of step S2, just
It can the theoretical complete characteristic curve for drawing pump turbine.Fig. 3 show point of characteristic operating point on most excellent aperture line (τ=1)
Cloth.
Wherein, point C represents high-efficiency point in pump operating condition area I；Point B1 is that pump operating condition area I brakes area's II intersection points with water pump,
Its specific discharge is zero；Point A is that water pump brakes area II and hydraulic turbine condition area III intersection points, unit speed zero；Point O is represented
Optimal operating condition point in pump turbine operating mode area III, generating efficiency highest；Point R is runaway speed point, and specific torque is
Zero；Point B2 is the intersection point that pump turbine brakes area IV and the pump condition area V that turns one's coat, specific discharge zero.Due under each aperture
There is features described above point, to form complete characteristic curve characteristic operating point collection Ci、B1i、Ai、Oi、Ri、B2i(i represents guide vane opening
Serial number).
The pump turbine model runner complete characteristic curve sample that 10 sets of specific speeds differ greatly is collected, unit head exists
Between 100~700m, cover high, medium and low drop, using each characteristic operating point unit parameter of Least Square Regression Analysis with most
Excellent operating mode specific speed nS(parameter of comprehensive characterization pump turbine characteristic) and relative opening of guide vane τ (τ=Ω/Ω0, Ω0It represents
Guide vane opening when generating efficiency highest) functional relation.Fig. 4 show the O points unit parameter that regression analysis obtains, and (unit turns
Speed, specific discharge and specific torque) functional relation between optimum operating condition specific speed.Fig. 5 show what regression analysis obtained
OiFunctional relation between point set relative unit parameter and relative opening of guide vane.
The governing equation of foundation is as follows：
n′1Oi=(75.4688+0.0782nS)×(-0.0742τ2+0.4353τ+0.6402) (20)
Q′1Oi=0.0855nS 1.6707×(-0.2243τ2+1.2241τ-0.0005) (21)
M′1Oi=0.1401nS 1.5870×(-0.4410τ2+1.4661τ-0.0267) (22)
Using same method, other characteristic operating point collection unit parameters and optimum operating condition specific speed and guide vane can be established
The functional relation of relative opening degree.
The embodiment of the present invention is specifically implemented as follows：
The optimum operating condition specific speed of certain known hydroenergy storage station unit is nS=83.1 (mkW), according to the present invention
The comparison of the complete characteristic curve that content and principle are predicted and actual measurement complete characteristic curve is as shown in Figure 6.It can be seen from the figure that
The complete characteristic curve variation tendency that theoretical prediction and actual measurement are drawn is almost the same, and also maintains in small guide vane higher consistent
Property.
Also with prediction complete characteristic curve and prototype complete characteristic curve respectively to " two machines send out nominal output, dash forward simultaneously
Removal of load, guide vane normal switching-off " operating mode is calculated, and obtained tune protects Parameters variation process such as Fig. 7, adjusts the extreme value pair for protecting parameter
Table 1 for example than result.From Fig. 7 and table 1 as can be seen that method proposed by the present invention it is more traditional apply mechanically head, single-machine capacity and
The way error smaller of the close unit complete characteristic curve of specific speed, can effectively improve concept phase hydroenergy storage station waterpower
The computational accuracy of transient process provides important data supporting for the Preliminary design in power station.
1 removal of load operating mode difference runner characteristic comparing result of table
The present invention is suitable for feasibility study and the Calculations of Hydraulic Transient of concept phase hydroenergy storage station calculates, tool
Body is, under prototype complete characteristic curve unknown situation, manages arbitrary specific speed mixed-flow type method for complete characteristic curves of reversible pump turbine
By prediction, be hydroenergy storage station aqueduct structure design, the arrangement of hydraulic structure, unit and spiral case strength check and
Power station stable operation etc. provides information and foundation.
The present invention is not limited to above-mentioned preferred forms, anyone structure change made under the inspiration of the present invention,
The technical schemes that are same or similar to the present invention are each fallen within protection scope of the present invention.
Claims (7)
1. a kind of prediction technique of mixed flow pump turbine complete characteristic curve, which is characterized in that include the following steps：
In conjunction with the characteristics of actual measurement method for complete characteristic curves of reversible pump turbine, the internal characteristic of description flow omnicharacteristic and torque omnicharacteristic is corrected
Analytic theory；
The unit parameter for counting characteristic operating point on different specific speed method for complete characteristic curves of reversible pump turbine, establishes each characteristic operating point
Unit parameter and pump turbine optimum operating condition specific speed and relative opening of guide vane between dominant functional relation；
The unit parameter of each characteristic operating point under different guide vane openings is obtained according to above-mentioned dominant functional relation, so that it is determined that correcting
Internal character analysis in undetermined coefficient, obtain the prediction complete characteristic curve of arbitrary specific speed pump turbine.
2. the method as described in claim 1, which is characterized in that the internal character analysis of description flow omnicharacteristic and torque omnicharacteristic
Theoretical calculation is specially：
When pump turbine stable operation under hydraulic turbine condition and pump operating condition, pass through the flow velocity three to stream interface among runner
It is angular to be analyzed, it obtains relationship and flow between flow, rotating speed and the torque when pump turbine stable operation, turn
Relationship between speed and head；
By introducing unit speed, specific discharge and units of torque, above-mentioned relation formula is converted, it is complete just to obtain description flow
The internal character analysis of characteristic and torque omnicharacteristic.
3. method as claimed in claim 2, which is characterized in that introduce unit speedSpecific dischargeUnits of torque M '1=M/D1 3H, hydraulic turbine condition efficiency etaT=1-STQT 2/ H=1-STQ1 ′2D1 4And water
Pump condition efficiency etaP=(1+SPQ1 ′2D1 4)-1, then unit of the pump turbine in hydraulic turbine condition and pump operating condition stable operation
Relationship between flow, unit speed and units of torque is：
According to actual measurement complete characteristic curve feature, the operating point that specific discharge is zero in complete characteristic curve, specific torque is not
It is zero, therefore above-mentioned formula is modified to：
Wherein, subscript T represents hydraulic turbine condition, i.e. centripetal flow operating mode；Subscript P represents pump operating condition, i.e. centrifugal flow operating mode；
n′1、Q′1With M '1Respectively unit speed, specific discharge and units of torque；η is hydraulic efficiency；N, Q and M is respectively water pump water wheels
Machine rotating speed, flow and axle power square；D1For runner diameter；H is head or lift；S is loss coefficient；αT、βT、γT、aT、bT、cTFor
With unit geometric parameter and the relevant coefficient of hydraulic turbine condition parameter；αP、βP、γP、aP、bP、cPFor with unit geometric parameter and water
The relevant coefficient of pump condition parameter.
4. method as claimed in claim 3, which is characterized in that by the fundamental equation of pump turbine and to the hydraulic turbine
The analysis of flow velocity triangle when operating mode at runner obtains pump turbine under hydraulic turbine condition when stable operation, and flow turns
Speed and torque between relational expression be：
There are following relationships for torque and shaft power when due to hydraulic turbine condition：
Simultaneous above-mentioned formula, the relational expression that can be obtained between flow, rotating speed and head are：
Wherein, subscript 1,2 respectively represents runner inlet and outlet；γ is fluid severe；G is acceleration of gravity；It is wide etc. relevant with stream interface among hydraulic turbine condition runner import and export flow angle and runner import and export
Coefficient；b1And b2Respectively represent guide vane height and outlet of rotary wheel axis plane projection width；α1And β2Respectively guide vane outlet stream angle and
Outlet of rotary wheel flow angle；The π of ω=2 n/60 are angular velocity of rotation；R is stream interface radius；P is shaft power.
5. method as claimed in claim 3, which is characterized in that according to the fundamental equation of pump turbine and to plugman
The analysis of flow velocity triangle when condition at runner obtains the pass between flow, rotating speed and the torque when pump operating condition stable operation
System is：
Relationship between flow, rotating speed and head is：
Wherein, b is and pump operating condition runner import and export flow angle and the wide equal geometric parameters of runner import and export centre stream interface and work
The relevant coefficient of condition parameter；For outlet of rotary wheel intermediate flow radius surface under pump operating condition.
6. method as described in claim 4 or 5, which is characterized in that when pump turbine is in hydraulic turbine condition and pump operating condition
When lower stable operation, according to the moment of momentum theorem, the fundamental equation that pump turbine can be obtained is respectively：
Wherein, subscript T, P respectively represents hydraulic turbine condition and pump operating condition；Subscript 1,2 respectively represents runner inlet and outlet；Vu
For the circumferential components of mass flow absolute velocity.
7. method as claimed in claim 4, which is characterized in that flow velocity triangle when by hydraulic turbine condition at runner
Analysis, can obtain：
Above-mentioned formula is substituted into formulaIn, above-mentioned hydraulic turbine condition down-off, rotating speed can be obtained
Relational expression between torque；Wherein, VmFor flow rate on axial surface；U is runner peripheral speed.
Priority Applications (1)
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| CN112487733B (en) * | 2020-11-27 | 2022-06-28 | 长江勘测规划设计研究有限责任公司 | Method and system for calculating adjustment guarantee value of axial flow through-flow type turbine unit |
| CN113833593A (en) * | 2021-08-26 | 2021-12-24 | 长江勘测规划设计研究有限责任公司 | Method for quantifying maintenance period of vertical coaxial two-stage mixed-flow water turbine under high-water-head and sediment-rich condition |
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| CN113987802B (en) * | 2021-10-28 | 2023-04-11 | 华中科技大学 | Calculation method and system for characteristic coefficients of water pump turbine |
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