CN105404748A - Stability judging method for water feeding pump working point - Google Patents

Abstract

The present invention discloses a stability judging method for a water feeding pump working point. The method comprises: fitting a water feeding pump pressure head; carrying out fitting calculation on a condensate pump pressure head; carrying out resistance calculation on a working point of a water supply system; calculating a rotating speed of a water feeding pump; carrying out stability judgment on the water feeding pump working point in order to judge whether the water feeding pump can stably operate under different load working conditions of the water supply system. The method is simple and easy to operate, can provide the basis for calculating a water feeding pump working condition point and judging whether the water feeding pump can stably operate under different load working conditions of the water supply system, and also can be used for guiding optimal designs of the water supply system and the water feeding pump.

Description

A kind of feed pump stabilization of operating point method of discrimination

Technical field

The invention belongs to Steam Power Equipment water supply system technical field, more specifically, relate to a kind of feed pump stabilization of operating point method of discrimination, for the calculating of feed pump working point under different load operating mode and the differentiation of stability, thus instruct design and the optimization of water supply system and feed pump.

Background technology

In Steam Power Equipment, water supply system is used for solidifying water condenser condenses got off, and is transported to incessantly in steam generator.Feed pump occupies critical role in water supply system, as the main power source of secondary circuit, plays the function of assure feed water supercharging, and its characteristic directly decides security and the operation stability of water supply system.Along with the rapid increase of net capacity, different seasons and daytime night load difference increase, regulating units is more and more difficult to the change meeting network load, large-sized unit participate in peak regulation also imperative.Therefore, except requiring unit and have good heat-economy under declared working condition, also require there is heat-economy high as far as possible when sub-load.By changing the feed pump method of operation, as adopted varying number feed pump to run during different load, or reduce speed of feedwater during underload, by reducing the wasted work of feed pump to improve heat-economy during unit underload.In addition, power station unit is when start and stop or feed pump fault, and need to switch different feed pumps and run, when handoff procedure and stable operation, feed pump can be in different duties.

In order to ensure the economy that water supply system is run and safe reliability, under various possibility operating condition, feed pump must safe operation continuously and stably.For the feed pump that performance curve is hump shape, if feed pump driving force and water supply system pipe resistance characteristics match bad, surge or the phenomenon that flies may be there is in feed pump, pump stream flow can periodically change on a large scale repeatedly, can leaf destruction be caused time serious, affect the safe handling of feed pump.Therefore, need to give enough attention to surge phenomenon in feed pump and water supply system designing.The design of usual feed pump can meet the stability and safety of water supply system under declared working condition and run, but when running on the lower load, due to factors such as the reduction of feedwater flow, the changes of steam generator operational factor, may surge be there is in feed pump, and also lack in water supply system and feed pump design at present a kind of fast effectively and the higher analytical approach of precision can feed pump during different load operating mode be differentiated in stable operation.

Summary of the invention

For above defect or the Improvement requirement of prior art, the invention provides a kind of feed pump stabilization of operating point method of discrimination, comprise the matching of feed pump pressure head, condensate pump pressure head the Fitting Calculation, water supply system working point drag evaluation, feed pump running speed calculates, and feed pump working point operation stability differentiates, under its object is to differentiate water supply system different load operating mode, can feed pump stable operation.

For achieving the above object, the invention provides a kind of feed pump stabilization of operating point method of discrimination, it is characterized in that, comprise the steps:

(1) according to condensate pump pressure head Δ P _cpcalculating formula matching is carried out to condensate pump flow-head test point data, obtains condensate pump pressure head fitting coefficient with wherein, ρ _cpfor flowing through the fluid density of condensate pump, G _cpfor condensate pump flow;

(2) condenser pressure P is obtained _con, condensate pump flow G _cp, flow through the fluid density ρ of condensate pump _cp, pressure differential deltap P before and after feed-regulating valve _v, steam generator operating pressure P _sG, feedwater flow G _fwwith the fluid density ρ flowing through feed pump _p;

(3) according to condensate pump flow G _cpwith the fluid density ρ flowing through condensate pump _cp, calculate condensate pump pressure head Δ P _cp;

(4) according to condenser pressure P _conwith condensate pump pressure head Δ P _cp, calculate feed pump intake pressure P _in=P _con-Δ P _p1-Δ P _g1+ Δ P _cp, wherein, Δ P _p1for feed pump inlet ductwork flow pressure drop, Δ P _g1for condenser is to the heavy position pressure drop of feed pump centreline space;

(5) according to pressure differential deltap P before and after feed-regulating valve _vwith steam generator operating pressure P _sG, calculate feed pump top hole pressure P _out=Δ P _p2+ Δ P _v+ Δ P _g2+ P _sG, wherein, Δ P _p2for feed pump export pipeline flow pressure drop, Δ P _g2for feed pump exports to heavy position pressure drop between steam generator entrance;

(6) according to feed pump intake pressure P _inwith feed pump top hole pressure P _out, calculate feed pump inlet outlet pressure differential Δ P=P _out-P _in, and calculate the first correction feed pump inlet outlet pressure differential Δ P further ₊feed pump inlet outlet pressure differential Δ P is revised with second _-, wherein, first revises feed pump inlet outlet pressure differential Δ P ₊refer to the feed pump inlet outlet pressure differential after considering Pipe interference allowance, the controlling dead error upper limit, condensate pump and the feed pump pressure head fitness bias upper limit, second revises feed pump inlet outlet pressure differential Δ P _-refer to the feed pump inlet outlet pressure differential after considering controlling dead error lower limit, condensate pump and feed pump pressure head fitness bias lower limit;

(7) according to feed pump pressure head Δ P _fpcalculating formula matching is carried out, in conjunction with feedwater flow G to feed pump flow-head test point data _fw, flow through the fluid density ρ of feed pump _p, feed pump inlet outlet pressure differential Δ P, first revises feed pump inlet outlet pressure differential Δ P ₊feed pump inlet outlet pressure differential Δ P is revised with second _-, calculate feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-be respectively:

${\mathrm{\α}}_p=\frac{-\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_1{\mathrm{\ρ}}_p(\frac{\tilde{k}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\ρ}}_p}-\mathrm{\Δ}P)}}{2{\tilde{k}}_1{\mathrm{\ρ}}_p},$

${\mathrm{\α}}_{p+}=\frac{-\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1+}{\mathrm{\ρ}}_p(\frac{{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\ρ}}_p}-{\mathrm{\ΔP}}_{+})}}{2{\tilde{k}}_{1+}{\mathrm{\ρ}}_p}$ With

${\mathrm{\α}}_{p-}=\frac{-\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1-}{\mathrm{\ρ}}_p(\frac{{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\ρ}}_p}-{\mathrm{\ΔP}}_{-})}}{2{\tilde{k}}_{1-}{\mathrm{\ρ}}_p},$

Wherein, with for feed pump pressure head fitting coefficient, G _fpfor feed pump flow, with be the first correction feed pump pressure head fitting coefficient, with be the second correction feed pump pressure head fitting coefficient, m _fpfor running the quantity of feed pump;

(8) judge whether following condition is set up:

$\frac{{\tilde{k}}_2}{m_{fp}}{\mathrm{\&alpha;}}_p+\frac{2{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}},$

$\frac{{\tilde{k}}_{2+}}{m_{fp}}{\mathrm{\&alpha;}}_{p+}+\frac{2{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}}$ And

$\frac{{\tilde{k}}_{2-}}{m_{fp}}{\mathrm{\&alpha;}}_{p-}+\frac{2{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}},$

Be that feed pump steady-state operation stabilization of operating point is described, otherwise illustrate that feed pump steady-state operation working point is unstable.

Preferably, in described step (7), single curve matching or many curves are carried out to feed pump flow-head test point data, when the match value of all testing sites that single curve matching obtains and the deviation of trial value all less time, adopt single curve matching; When the match value of the testing site that single curve matching obtains and trial value exist relatively large deviation, adopt many curves.

Preferably, when adopting single curve matching, ${\tilde{k}}_{1+}={\tilde{k}}_{1-}={\tilde{k}}_1,{\tilde{k}}_{2+}={\tilde{k}}_{2-}={\tilde{k}}_2,$ ${\tilde{k}}_{3+}={\tilde{k}}_{3-}={\tilde{k}}_3.$

Preferably, when employing two curves, the calculating formula of two groups of feed pump pressure heads is obtained respectively:

${\mathrm{\&Delta;P}}_{fp1}=k_{11}{\mathrm{\&rho;}}_p{\mathrm{\&alpha;}}_p^2+k_{12}{\mathrm{\&alpha;}}_p{G}_{fp}+\frac{k_{13}{G}_{fp}^2}{{\mathrm{\&rho;}}_p}$ With

${\mathrm{\&Delta;P}}_{fp2}=k_{21}{\mathrm{\&rho;}}_p{\mathrm{\&alpha;}}_p^2+k_{22}{\mathrm{\&alpha;}}_p{G}_{fp}+\frac{k_{23}{G}_{fp}^2}{{\mathrm{\&rho;}}_p},$

Wherein, Δ P _fp1be the first feed pump pressure head, Δ P _fp2be the second feed pump pressure head, k ₁₁, k ₁₂and k ₁₃be the fitting coefficient of the first matched curve, be designated as first group of fitting coefficient, k ₂₁, k ₂₂and k ₂₃be the fitting coefficient of the second matched curve, be designated as second group of fitting coefficient;

Concrete approximating method is as follows: process feed pump flow-lift test figure, obtains one group of data point wherein, for feed pump volume flow ratio, Q is feed pump volume flow, Q _rfor the volume flow that feed pump operating point for design is corresponding, for feed pump lift ratio, H is feed pump lift, H _rfor the lift that feed pump operating point for design is corresponding; According to order from small to large, rejects data point one by one, until according to remaining data point according to expression formula when the relative deviation of the feed pump pressure head value that the matched curve that matching obtains is calculated and test head value is less than 1%, obtain first group of fitting coefficient k ₁₁, k ₁₂and k ₁₃, matched curve is now designated as the first matched curve, and corresponding data point is designated as first data point, in first data point minimum value be designated as remaining data point is designated as second group of data point, by second group of data point according to expression formula matching obtains the second matched curve, adjusts in second group of data point maximal value corresponding pressure head value, makes the second matched curve and the first matched curve exist inside there is intersection point, and calculate according to the second matched curve the deviation of corresponding pressure head and the pressure head of this data point is less than 1%, and the horizontal ordinate of this intersection point is designated as obtain second group of fitting coefficient k ₂₁, k ₂₂and k ₂₃;

Feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-computing method as follows:

(A1) get ${\tilde{k}}_1=k_{11},{\tilde{k}}_2=k_{12},{\tilde{k}}_3=k_{13},{\tilde{k}}_{1+}=k_{11},{\tilde{k}}_{2+}=k_{12},{\tilde{k}}_{3+}=k_{13}$ And ${\tilde{k}}_{1-}=k_{11},$ ${\tilde{k}}_{2-}=k_{12},{\tilde{k}}_{3-}=k_{13};$

(A2) α is calculated _p, α _p+and α _p-;

(A3) calculate $\frac{v}{{\mathrm{\&alpha;}}_p}=\frac{G_{fw}}{m_{fp}{\mathrm{\&rho;}}_p{Q}_R{\mathrm{\&alpha;}}_p}$ And judge $\frac{v}{{\mathrm{\&alpha;}}_p}>{\left(\frac{v}{{\mathrm{\&alpha;}}_p}\right)}_0$ Whether set up, be, by the α that step (A2) calculates _pvalue as end value, otherwise to get recalculate α _p, and by this α _pvalue as end value; Calculate and judge whether set up, be, by the α that step (A2) calculates _p+value as end value, otherwise to get recalculate α _p+, and by this α _p+value as end value; Calculate and judge whether set up, be, by the α that step (A2) calculates _p-value as end value, otherwise to get recalculate α _p-, and by this α _p-value as end value.

Preferably, first feed pump inlet outlet pressure differential Δ P is revised ₊feed pump inlet outlet pressure differential Δ P is revised with second _-be respectively:

Δ P ₊=Δ P+ Δ P _{δ, V}+ (Δ P _{sg, pc+}+ Δ P _{sg, L+}+ Δ P _{δ, fp+}+ Δ P _{δ, cp+})+ε (Δ P _p1+ Δ P _p2) and

ΔP _-＝ΔP-ΔP _δ,V+(ΔP _sg,pc-+ΔP _sg,L-+ΔP _δ,fp-+ΔP _δ,cp-)，

Wherein, Δ P _{δ, V}for feed-regulating valve controlling dead error, Δ P _{sg, pc+}for the vapor pressure overgauge that power controlling dead error causes, Δ P _{sg, L+}for the vapor pressure overgauge that steam generator water level control dead band causes, Δ P _{δ, fp+}the maximal value of the difference of trial value and match value during for carrying out matching to feed pump flow-head test point data, Δ P _{δ, cp+}the maximal value of the difference of match value and trial value during for carrying out matching to condensate pump flow-head test point data, ε is that pressure-drop in pipeline calculates allowance, Δ P _{sg, pc-}for the vapor pressure minus deviation that power controlling dead error causes, Δ P _{sg, L-}for the vapor pressure minus deviation that steam generator water level control dead band causes, Δ P _{δ, fp-}the minimum value of the difference of trial value and match value during for carrying out matching to feed pump flow-head test point data, Δ P _{δ, cp-}the minimum value of the difference of match value and trial value during for carrying out matching to condensate pump flow-head test point data.

In general, the above technical scheme conceived by the present invention compared with prior art, there is following beneficial effect: propose a kind of method for differentiating water supply system typical condition operation stability, the method is simple and easy to use, can can the foundation of stable operation as calculating feed pump operating point and differentiation feed pump under water supply system different load operating mode, also can be used to guide the optimal design of water supply system and feed pump.

Accompanying drawing explanation

Fig. 1 is the feed pump stabilization of operating point method of discrimination process flow diagram of the embodiment of the present invention.

Embodiment

In order to make object of the present invention, technical scheme and advantage clearly understand, below in conjunction with drawings and Examples, the present invention is further elaborated.Should be appreciated that specific embodiment described herein only in order to explain the present invention, be not intended to limit the present invention.In addition, if below in described each embodiment of the present invention involved technical characteristic do not form conflict each other and just can mutually combine.

As shown in Figure 1, the feed pump stabilization of operating point method of discrimination of the embodiment of the present invention comprises the steps:

(1) according to condensate pump pressure head Δ P _cpcalculating formula adopt least square method to carry out matching to condensate pump flow-head test point data, obtain condensate pump pressure head fitting coefficient with wherein, ρ _cpfor flowing through the fluid density of condensate pump, G _cpfor condensate pump flow;

(2) condenser pressure P is obtained _con, condensate pump flow G _cp, flow through the fluid density ρ of condensate pump _cp, pressure differential deltap P before and after feed-regulating valve _v, steam generator operating pressure P _sG, feedwater flow G _fwwith the fluid density ρ flowing through feed pump _p;

(3) according to condensate pump flow G _cpwith the fluid density ρ flowing through condensate pump _cp, calculate condensate pump pressure head Δ P _cp;

(4) according to condenser pressure P _conwith condensate pump pressure head Δ P _cp, calculate feed pump intake pressure P _in=P _con-Δ P _p1-Δ P _g1+ Δ P _cp, wherein, for feed pump inlet ductwork flow pressure drop, λ _1ifor the i-th segment pipe friction factor before feed pump, L _1ifor the i-th segment pipe length before feed pump, G _1ifor the i-th segment pipe fluid flow before feed pump, d _1ifor the diameter of the i-th segment pipe before feed pump, ρ _1ifor the density of fluid in the i-th segment pipe before feed pump, ζ _1jfor the shock resistance part form drag coefficient of jth before feed pump, G _1jfor the shock resistance part fluid flow of jth before feed pump, d _1jfor the diameter of the shock resistance part interface pipe of jth before feed pump, ρ _1jfor flowing through the density of a jth shock resistance part fluid before feed pump, Δ P _g1=g Σ (ρ _1iΔ H _1i) for condenser is to the heavy position pressure drop of feed pump centreline space, g is acceleration of gravity, Δ H _1ifor the potential difference of the i-th segment pipe before feed pump;

Wherein, ${\mathrm{\&lambda;}}_{1i}=\left\{\begin{array}{cc}\frac{64}{\frac{4}{{\mathrm{\&pi;d}}_{1i}}\frac{G_{1i}}{{\mathrm{\&eta;}}_{1i}}}& 0<\left(\frac{4}{{\mathrm{\&pi;d}}_{1i}}\frac{G_{1i}}{{\mathrm{\&eta;}}_{1i}}\right)<2320\\ \frac{0.3164}{{\left(\frac{4}{{\mathrm{\&pi;d}}_{1i}}\frac{G_{1i}}{{\mathrm{\&eta;}}_{1i}}\right)}^{0.25}}& 2320\&le;\left(\frac{4}{{\mathrm{\&pi;d}}_{1i}}\frac{G_{1i}}{{\mathrm{\&eta;}}_{1i}}\right)\&le;{10}^5\\ 0.0032+\frac{0.221}{{\left(\frac{4}{{\mathrm{\&pi;d}}_{1i}}\frac{G_{1i}}{{\mathrm{\&eta;}}_{1i}}\right)}^{0.237}}& {10}^5\&le;\left(\frac{4}{{\mathrm{\&pi;d}}_{1i}}\frac{G_{1i}}{{\mathrm{\&eta;}}_{1i}}\right)\&le;3\&times;{10}^6\end{array}\right.,$ η _1ifor the kinetic viscosity of fluid in the i-th segment pipe before feed pump.

Δ P _p1calculating principle be, when there being many parallel pipelines before feed pump, only the pipeline of is wherein calculated.

(5) according to pressure differential deltap P before and after feed-regulating valve _vwith steam generator operating pressure P _sG, calculate feed pump top hole pressure P _out=Δ P _p2+ Δ P _v+ Δ P _g2+ P _sG, wherein, for feed pump export pipeline flow pressure drop, λ _2ifor the i-th segment pipe friction factor after feed pump, L _2ifor the i-th segment pipe length after feed pump, G _2ifor the i-th segment pipe fluid flow after feed pump, d _2ifor the diameter of the i-th segment pipe after feed pump, ρ _2ifor the density of fluid in the i-th segment pipe after feed pump, ζ _2jfor the shock resistance part form drag coefficient of jth after feed pump, G _2jfor the shock resistance part fluid flow of jth after feed pump, d _2jfor the diameter of the shock resistance part interface pipe of jth after feed pump, ρ _2jfor flowing through the density of a jth shock resistance part fluid after feed pump, Δ P _g2=g Σ (ρ _2iΔ H _2i) weigh position pressure drop, Δ H for feed pump exports between steam generator entrance _2ifor the potential difference of the i-th segment pipe after feed pump;

Wherein, ${\mathrm{\&lambda;}}_{2i}=\left\{\begin{array}{cc}\frac{64}{\frac{4}{{\mathrm{\&pi;d}}_{2i}}\frac{G_{2i}}{{\mathrm{\&eta;}}_{2i}}}& 0<\left(\frac{4}{{\mathrm{\&pi;d}}_{2i}}\frac{G_{2i}}{{\mathrm{\&eta;}}_{2i}}\right)<2320\\ \frac{0.3164}{{\left(\frac{4}{{\mathrm{\&pi;d}}_{2i}}\frac{G_{2i}}{{\mathrm{\&eta;}}_{2i}}\right)}^{0.25}}& 2320\&le;\left(\frac{4}{{\mathrm{\&pi;d}}_{2i}}\frac{G_{2i}}{{\mathrm{\&eta;}}_{2i}}\right)\&le;{10}^5\\ 0.0032+\frac{0.221}{{\left(\frac{4}{{\mathrm{\&pi;d}}_{2i}}\frac{G_{2i}}{{\mathrm{\&eta;}}_{2i}}\right)}^{0.237}}& {10}^5\&le;\left(\frac{4}{{\mathrm{\&pi;d}}_{2i}}\frac{G_{2i}}{{\mathrm{\&eta;}}_{2i}}\right)\&le;3\&times;{10}^6\end{array}\right.,$ η _2ifor the kinetic viscosity of the fluid in the i-th segment pipe after feed pump.

Δ P _p2calculating principle be, when there being many parallel pipelines after feed pump, only the pipeline of is wherein calculated.

(6) according to feed pump intake pressure P _inwith feed pump top hole pressure P _out, calculate feed pump inlet outlet pressure differential Δ P=P _out-P _in, and calculate the first correction feed pump inlet outlet pressure differential Δ P further ₊feed pump inlet outlet pressure differential Δ P is revised with second _-be respectively:

Δ P ₊=Δ P+ Δ P _{δ, V}+ (Δ P _{sg, pc+}+ Δ P _{sg, L+}+ Δ P _{δ, fp+}+ Δ P _{δ, cp+})+ε (Δ P _p1+ Δ P _p2) and

ΔP _-＝ΔP-ΔP _δ,V+(ΔP _sg,pc-+ΔP _sg,L-+ΔP _δ,fp-+ΔP _δ,cp-)，

Wherein, Δ P _{δ, V}for feed-regulating valve controlling dead error, Δ P _{sg, pc+}for the vapor pressure overgauge that power controlling dead error causes, Δ P _{sg, L+}for the vapor pressure overgauge that steam generator water level control dead band causes, Δ P _{δ, fp+}the maximal value of the difference of trial value and match value during for carrying out matching to feed pump flow-head test point data, Δ P _{δ, cp+}the maximal value of the difference of match value and trial value during for carrying out matching to condensate pump flow-head test point data, ε is that pressure-drop in pipeline calculates allowance, Δ P _{sg, pc-}for the vapor pressure minus deviation that power controlling dead error causes, Δ P _{sg, L-}for the vapor pressure minus deviation that steam generator water level control dead band causes, Δ P _{δ, fp-}the minimum value of the difference of trial value and match value during for carrying out matching to feed pump flow-head test point data, Δ P _{δ, cp-}the minimum value of the difference of match value and trial value during for carrying out matching to condensate pump flow-head test point data;

Particularly, first revises feed pump inlet outlet pressure differential refers to the feed pump inlet outlet pressure differential after considering Pipe interference allowance, the controlling dead error upper limit, condensate pump and the feed pump pressure head fitness bias upper limit, and second revises feed pump inlet outlet pressure differential refers to the feed pump inlet outlet pressure differential after considering controlling dead error lower limit, condensate pump and feed pump pressure head fitness bias lower limit.

Further, the vapor pressure overgauge Δ P that causes of power controlling dead error _{sg, pc+}with the vapor pressure minus deviation Δ P that power controlling dead error causes _{sg, pc-}be respectively:

${\mathrm{\&Delta;P}}_{sg,pc+}=P_{sg,p_0+\mathrm{\&delta;}}-P_{sg,p_0}$ With

${\mathrm{\&Delta;P}}_{sg,pc-}=P_{sg,p_0-\mathrm{\&delta;}}-P_{sg,p_0},$

Wherein, for the vapor pressure that the power controlling dead error upper limit is corresponding, for the vapor pressure that power control target value is corresponding, for the vapor pressure that power controlling dead error lower limit is corresponding;

The vapor pressure overgauge Δ P that steam generator water level control dead band causes _{sg, L+}with the vapor pressure minus deviation Δ P that steam generator water level control dead band causes _{sg, L-}be respectively:

${\mathrm{\&Delta;P}}_{sg,L+}=P_{sg,L_0+\mathrm{\&delta;}}-P_{sg,L_0}$ With

${\mathrm{\&Delta;P}}_{sg,L-}=P_{sg,L_0-\mathrm{\&delta;}}-P_{sg,L_0},$

Wherein, for the vapor pressure that steam generator water level control deadband upper limit is corresponding, for the vapor pressure that steam generator water level control desired value is corresponding, for the vapor pressure that steam generator water level control deadband lower limit is corresponding.

(7) according to feed pump pressure head Δ P _fpcalculating formula least square method is adopted to carry out matching, in conjunction with feedwater flow G to feed pump flow-head test point data _fw, flow through the fluid density ρ of feed pump _p, feed pump inlet outlet pressure differential Δ P, first revises feed pump inlet outlet pressure differential Δ P ₊feed pump inlet outlet pressure differential Δ P is revised with second _-, calculate feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-, wherein, with for feed pump pressure head fitting coefficient, G _fpfor feed pump flow;

Particularly, first revises feed pump normalization rotating speed refers to the feed pump normalization rotating speed after considering Pipe interference allowance, the controlling dead error upper limit, condensate pump and the feed pump pressure head fitness bias upper limit, and second revises feed pump normalization rotating speed refers to the feed pump normalization rotating speed after considering controlling dead error lower limit, condensate pump and feed pump pressure head fitness bias lower limit.

Further, single curve matching or many curves are carried out to feed pump flow-head test point data, when the match value of all testing sites that single curve matching obtains and the deviation of trial value all less (as being less than 1%), adopt single curve matching; When the match value of the testing site that single curve matching obtains and trial value exist relatively large deviation (as being greater than 1%), adopt many curves.

When adopting single curve matching, obtain feed pump pressure head fitting coefficient with and then obtain feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-be respectively:

${\mathrm{\&alpha;}}_p=\frac{-\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_1{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-\mathrm{\&Delta;}P)}}{2{\tilde{k}}_1{\mathrm{\&rho;}}_p},$

${\mathrm{\&alpha;}}_{p+}=\frac{-\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{+})}}{2{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p}$ With

${\mathrm{\&alpha;}}_{p-}=\frac{-\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{-})}}{2{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p},$

Wherein, ${\tilde{k}}_{1+}={\tilde{k}}_{1-}={\tilde{k}}_1,{\tilde{k}}_{2+}={\tilde{k}}_{2-}={\tilde{k}}_2,{\tilde{k}}_{3+}={\tilde{k}}_{3-}={\tilde{k}}_3,$ M _fpfor running the quantity of feed pump.

When employing two curves, obtain the calculating formula of two groups of feed pump pressure heads respectively:

${\mathrm{\&Delta;P}}_{fp1}=k_{11}{\mathrm{\&rho;}}_p{\mathrm{\&alpha;}}_p^2+k_{12}{\mathrm{\&alpha;}}_p{G}_{fp}+\frac{k_{13}{G}_{fp}^2}{{\mathrm{\&rho;}}_p}$ With

${\mathrm{\&Delta;P}}_{fp2}=k_{21}{\mathrm{\&rho;}}_p{\mathrm{\&alpha;}}_p^2+k_{22}{\mathrm{\&alpha;}}_p{G}_{fp}+\frac{k_{23}{G}_{fp}^2}{{\mathrm{\&rho;}}_p},$

Wherein, Δ P _fp1be the first feed pump pressure head, Δ P _fp2be the second feed pump pressure head, k ₁₁, k ₁₂and k ₁₃be the fitting coefficient of the first matched curve, be designated as first group of fitting coefficient, k ₂₁, k ₂₂and k ₂₃be the fitting coefficient of the second matched curve, be designated as second group of fitting coefficient.

Concrete approximating method is as follows: process feed pump flow-lift test figure, obtains one group of data point wherein, for feed pump volume flow ratio, Q is feed pump volume flow, Q _rfor the volume flow that feed pump operating point for design is corresponding, for feed pump lift ratio, H is feed pump lift, H _rfor the lift that feed pump operating point for design is corresponding; According to order from small to large, rejects data point one by one, until according to remaining data point according to expression formula when the relative deviation of the feed pump pressure head value that the matched curve that matching obtains is calculated and test head value is less than 1%, obtain first group of fitting coefficient k ₁₁, k ₁₂and k ₁₃, matched curve is now designated as the first matched curve, and corresponding data point is designated as first data point, in first data point minimum value be designated as remaining data point is designated as second group of data point, by second group of data point according to expression formula matching obtains the second matched curve, adjusts in second group of data point maximal value corresponding pressure head value, makes the second matched curve and the first matched curve exist inside there is intersection point, and calculate according to the second matched curve the deviation of corresponding pressure head and the pressure head of this data point is less than 1%, and the horizontal ordinate of this intersection point is designated as obtain second group of fitting coefficient k ₂₁, k ₂₂and k ₂₃;

When employing two curves, feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-computing method as follows:

(A1) get ${\tilde{k}}_1=k_{11},{\tilde{k}}_2=k_{12},{\tilde{k}}_3=k_{13},{\tilde{k}}_{1+}=k_{11},{\tilde{k}}_{2+}=k_{12},{\tilde{k}}_{3+}=k_{13}$ And ${\tilde{k}}_{1-}=k_{11},$ ${\tilde{k}}_{2-}=k_{12},{\tilde{k}}_{3-}=k_{13};$

(A2) calculate

${\mathrm{\&alpha;}}_p=\frac{-\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_1{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-\mathrm{\&Delta;}P)}}{2{\tilde{k}}_1{\mathrm{\&rho;}}_p},$

${\mathrm{\&alpha;}}_{p+}=\frac{-\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{+})}}{2{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p}$ With

${\mathrm{\&alpha;}}_{p-}=\frac{-\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{-})}}{2{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p},$

(A3) calculate and judge whether set up, be, by the α that step (A2) calculates _pvalue as end value, otherwise to get recalculate ${\mathrm{\&alpha;}}_p=\frac{-\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_1{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-\mathrm{\&Delta;}P)}}{2{\tilde{k}}_1{\mathrm{\&rho;}}_p},$ And by this α _pvalue as end value; Calculate and judge whether set up, be, by the α that step (A2) calculates _p+value as end value, otherwise to get recalculate ${\mathrm{\&alpha;}}_{p+}=\frac{-\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{+})}}{2{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p},$ And by this α _p+value as end value; Calculate and judge whether set up, be, by the α that step (A2) calculates _p-value as end value, otherwise to get recalculate ${\mathrm{\&alpha;}}_{p-}=\frac{-\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{-})}}{2{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p},$ And by this α _p-value as end value.

(8) judge whether following condition is set up:

$\frac{{\tilde{k}}_2}{m_{fp}}{\mathrm{\&alpha;}}_p+\frac{2{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}},$

$\frac{{\tilde{k}}_{2+}}{m_{fp}}{\mathrm{\&alpha;}}_{p+}+\frac{2{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}}$ And

$\frac{{\tilde{k}}_{2-}}{m_{fp}}{\mathrm{\&alpha;}}_{p-}+\frac{2{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}},$

Be that feed pump steady-state operation stabilization of operating point is described, otherwise illustrate that feed pump steady-state operation working point is unstable.

Those skilled in the art will readily understand; the foregoing is only preferred embodiment of the present invention; not in order to limit the present invention, all any amendments done within the spirit and principles in the present invention, equivalent replacement and improvement etc., all should be included within protection scope of the present invention.

Claims (5)

1. a feed pump stabilization of operating point method of discrimination, is characterized in that, comprises the steps:

(1) according to condensate pump pressure head Δ P _cpcalculating formula matching is carried out to condensate pump flow-head test point data, obtains condensate pump pressure head fitting coefficient with wherein, ρ _cpfor flowing through the fluid density of condensate pump, G _cpfor condensate pump flow;

(2) condenser pressure P is obtained _con, condensate pump flow G _cp, flow through the fluid density ρ of condensate pump _cp, pressure differential deltap P before and after feed-regulating valve _v, steam generator operating pressure P _sG, feedwater flow G _fwwith the fluid density ρ flowing through feed pump _p;

(3) according to condensate pump flow G _cpwith the fluid density ρ flowing through condensate pump _cp, calculate condensate pump pressure head Δ P _cp;

(4) according to condenser pressure P _conwith condensate pump pressure head Δ P _cp, calculate feed pump intake pressure P _in=P _con-Δ P _p1-Δ P _g1+ Δ P _cp, wherein, Δ P _p1for feed pump inlet ductwork flow pressure drop, Δ P _g1for condenser is to the heavy position pressure drop of feed pump centreline space;

(5) according to pressure differential deltap P before and after feed-regulating valve _vwith steam generator operating pressure P _sG, calculate feed pump top hole pressure P _out=Δ P _p2+ Δ P _v+ Δ P _g2+ P _sG, wherein, Δ P _p2for feed pump export pipeline flow pressure drop, Δ P _g2for feed pump exports to heavy position pressure drop between steam generator entrance;

(6) according to feed pump intake pressure P _inwith feed pump top hole pressure P _out, calculate feed pump inlet outlet pressure differential Δ P=P _out-P _in, and calculate the first correction feed pump inlet outlet pressure differential Δ P further ₊feed pump inlet outlet pressure differential Δ P is revised with second _-, wherein, first revises feed pump inlet outlet pressure differential Δ P ₊refer to the feed pump inlet outlet pressure differential after considering Pipe interference allowance, the controlling dead error upper limit, condensate pump and the feed pump pressure head fitness bias upper limit, second revises feed pump inlet outlet pressure differential Δ P _-refer to the feed pump inlet outlet pressure differential after considering controlling dead error lower limit, condensate pump and feed pump pressure head fitness bias lower limit;

(7) according to feed pump pressure head Δ P _fpcalculating formula matching is carried out, in conjunction with feedwater flow G to feed pump flow-head test point data _fw, flow through the fluid density ρ of feed pump _p, feed pump inlet outlet pressure differential Δ P, first revises feed pump inlet outlet pressure differential Δ P ₊feed pump inlet outlet pressure differential Δ P is revised with second _-, calculate feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-be respectively:

${\mathrm{\&alpha;}}_p=\frac{-\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_2{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_1{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-\mathrm{\&Delta;}P)}}{2{\tilde{k}}_1{\mathrm{\&rho;}}_p},$

${\mathrm{\&alpha;}}_{p+}=\frac{-\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2+}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{+})}}{2{\tilde{k}}_{1+}{\mathrm{\&rho;}}_p}$ With

${\mathrm{\&alpha;}}_{p-}=\frac{-\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}+\sqrt{{\left(\frac{{\tilde{k}}_{2-}{G}_{fw}}{m_{fp}}\right)}^2-4{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p(\frac{{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}^2}{{\mathrm{\&rho;}}_p}-{\mathrm{\&Delta;P}}_{-})}}{2{\tilde{k}}_{1-}{\mathrm{\&rho;}}_p},$

Wherein, with for feed pump pressure head fitting coefficient, G _fpfor feed pump flow, with be the first correction feed pump pressure head fitting coefficient, with be the second correction feed pump pressure head fitting coefficient, m _fpfor running the quantity of feed pump;

(8) judge whether following condition is set up:

$\frac{{\tilde{k}}_2}{m_{fp}}{\mathrm{\&alpha;}}_p+\frac{2{\tilde{k}}_3}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}},$

$\frac{{\tilde{k}}_{2+}}{m_{fp}}{\mathrm{\&alpha;}}_{p+}+\frac{2{\tilde{k}}_{3+}}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}}$ And

$\frac{{\tilde{k}}_{2-}}{m_{fp}}{\mathrm{\&alpha;}}_{p-}+\frac{2{\tilde{k}}_{3-}}{m_{fp}^2}\frac{G_{fw}}{{\mathrm{\&rho;}}_p}<\frac{2{\mathrm{\&Delta;P}}_{p2}}{G_{fw}},$

Be that feed pump steady-state operation stabilization of operating point is described, otherwise illustrate that feed pump steady-state operation working point is unstable.

2. feed pump stabilization of operating point method of discrimination as claimed in claim 1, it is characterized in that, in described step (7), single curve matching or many curves are carried out to feed pump flow-head test point data, when the match value of all testing sites that single curve matching obtains and the deviation of trial value all less time, adopt single curve matching; When the match value of the testing site that single curve matching obtains and trial value exist relatively large deviation, adopt many curves.

3. feed pump stabilization of operating point method of discrimination as claimed in claim 2, is characterized in that, when adopting single curve matching, ${\tilde{k}}_{1+}={\tilde{k}}_{1-}={\tilde{k}}_1,{\tilde{k}}_{2+}={\tilde{k}}_{2-}={\tilde{k}}_2,{\tilde{k}}_{3+}={\tilde{k}}_{3-}={\tilde{k}}_3.$

4. feed pump stabilization of operating point method of discrimination as claimed in claim 2, is characterized in that, when employing two curves, obtain the calculating formula of two groups of feed pump pressure heads respectively:

${\mathrm{\&Delta;P}}_{fp1}=k_{11}{\mathrm{\&rho;}}_p{\mathrm{\&alpha;}}_p^2+k_{12}{\mathrm{\&alpha;}}_p{G}_{fp}+\frac{k_{13}{G}_{fp}^2}{{\mathrm{\&rho;}}_p}$ With

${\mathrm{\&Delta;P}}_{fp2}=k_{21}{\mathrm{\&rho;}}_p{\mathrm{\&alpha;}}_p^2+k_{22}{\mathrm{\&alpha;}}_p{G}_{fp}+\frac{k_{23}{G}_{fp}^2}{{\mathrm{\&rho;}}_p},$

Wherein, Δ P _fp1be the first feed pump pressure head, Δ P _fp2be the second feed pump pressure head, k ₁₁, k ₁₂and k ₁₃be the fitting coefficient of the first matched curve, be designated as first group of fitting coefficient, k ₂₁, k ₂₂and k ₂₃be the fitting coefficient of the second matched curve, be designated as second group of fitting coefficient;

Concrete approximating method is as follows: process feed pump flow-lift test figure, obtains one group of data point wherein, for feed pump volume flow ratio, Q is feed pump volume flow, Q _rfor the volume flow that feed pump operating point for design is corresponding, for feed pump lift ratio, H is feed pump lift, H _rfor the lift that feed pump operating point for design is corresponding; According to order from small to large, rejects data point one by one, until according to remaining data point according to expression formula when the relative deviation of the feed pump pressure head value that the matched curve that matching obtains is calculated and test head value is less than 1%, obtain first group of fitting coefficient k ₁₁, k ₁₂and k ₁₃, matched curve is now designated as the first matched curve, and corresponding data point is designated as first data point, in first data point minimum value be designated as remaining data point is designated as second group of data point, by second group of data point according to expression formula matching obtains the second matched curve, adjusts in second group of data point maximal value corresponding pressure head value, makes the second matched curve and the first matched curve exist inside there is intersection point, and calculate according to the second matched curve the deviation of corresponding pressure head and the pressure head of this data point is less than 1%, and the horizontal ordinate of this intersection point is designated as obtain second group of fitting coefficient k ₂₁, k ₂₂and k ₂₃;

Feed pump normalization speed alpha _p, first revise feed pump normalization speed alpha _p+feed pump normalization speed alpha is revised with second _p-computing method as follows:

(A1) get ${\tilde{k}}_1=k_{11},{\tilde{k}}_2=k_{12},{\tilde{k}}_3=k_{13},{\tilde{k}}_{1+}=k_{11},{\tilde{k}}_{2+}=k_{12},{\tilde{k}}_{3+}=k_{13}$ And ${\tilde{k}}_{1-}=k_{11},$ ${\tilde{k}}_{2-}=k_{12},{\tilde{k}}_{3-}=k_{13};$

(A2) α is calculated _p, α _p+and α _p-;

(A3) calculate and judge whether set up, be, by the α that step (A2) calculates _pvalue as end value, otherwise to get recalculate α _p, and by this α _pvalue as end value; Calculate and judge whether set up, be, by the α that step (A2) calculates _p+value as end value, otherwise to get recalculate α _p+, and by this α _p+value as end value; Calculate and judge whether set up, be, by the α that step (A2) calculates _p-value as end value, otherwise to get recalculate α _p-, and by this α _p-value as end value.

5. the feed pump stabilization of operating point method of discrimination according to any one of Claims 1-4, is characterized in that, first revises feed pump inlet outlet pressure differential Δ P ₊feed pump inlet outlet pressure differential Δ P is revised with second _-be respectively:

Δ P ₊=Δ P+ Δ P _{δ, V}+ (Δ P _{sg, pc+}+ Δ P _{sg, L+}+ Δ P _{δ, fp+}+ Δ P _{δ, cp+})+ε (Δ P _p1+ Δ P _p2) and

ΔP _-＝ΔP-ΔP _δ,V+(ΔP _sg,pc-+ΔP _sg,L-+ΔP _δ,fp-+ΔP _δ,cp-)，

Wherein, Δ P _{δ, V}for feed-regulating valve controlling dead error, Δ P _{sg, pc+}for the vapor pressure overgauge that power controlling dead error causes, Δ P _{sg, L+}for the vapor pressure overgauge that steam generator water level control dead band causes, Δ P _{δ, fp+}the maximal value of the difference of trial value and match value during for carrying out matching to feed pump flow-head test point data, Δ P _{δ, cp+}the maximal value of the difference of match value and trial value during for carrying out matching to condensate pump flow-head test point data, ε is that pressure-drop in pipeline calculates allowance, Δ P _{sg, pc-}for the vapor pressure minus deviation that power controlling dead error causes, Δ P _{sg, L-}for the vapor pressure minus deviation that steam generator water level control dead band causes, Δ P _{δ, fp-}the minimum value of the difference of trial value and match value during for carrying out matching to feed pump flow-head test point data, Δ P _{δ, cp-}the minimum value of the difference of match value and trial value during for carrying out matching to condensate pump flow-head test point data.