CN113239511B - Circulating water system optimization method based on permanent magnet regulation and mechanical ventilation - Google Patents
Circulating water system optimization method based on permanent magnet regulation and mechanical ventilation Download PDFInfo
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Abstract
The invention provides a circulating water system optimization method based on permanent magnet regulation and mechanical ventilation, which comprises the steps of setting the permanent magnet regulation initial opening of a permanent magnet regulation circulating water pump and the initial opening number of fans of a mechanical ventilation cooling tower, and establishing a power consumption characteristic model of the permanent magnet regulation circulating water pump, a heat exchange characteristic model of a condenser, a heat exchange and power consumption characteristic model of the mechanical ventilation cooling tower and an influence model of back pressure of a steam turbine on the power of the steam turbine; and (3) taking the maximum actually increased power of the steam turbine as a target function, optimizing the target function by utilizing a genetic algorithm, and finishing the optimization of the circulating water system by obtaining the corresponding permanent magnet regulation opening of the circulating water pump and the number of the started fans of the mechanical ventilation cooling tower when the maximum value of the target function is obtained. The invention comprehensively analyzes the influence factors of the economy of the circulating water system, the analyzed factors fit the actual production, the optimization effect is better, and the running mode of the circulating water system is more economical.
Description
Technical Field
The invention relates to the field of water system circulation optimization, in particular to a circulating water system optimization method based on permanent magnet regulation and mechanical ventilation.
Background
The cold end system of the thermal power plant mainly comprises a low-pressure cylinder of a steam turbine, a condenser and a circulating cooling water system, is an important auxiliary system of the thermal power generating unit, and has important influence on the economy of the steam turbine. The change of the backpressure of the condenser can cause the change of the heat consumption and the power generation power of the steam turbine, the ideal specific enthalpy of the steam turbine can be reduced and the power generation power can be increased by improving the vacuum of the condenser, and the backpressure of the condenser is closely related to the operating characteristics of each subsystem of a cold end system. The circulating water system is a pipeline and equipment forming circulating water flow, an optimal operation mode of the circulating water system is researched, and a circulating water system optimization module is developed, so that the circulating water system optimization module has very important significance for improving the vacuum of a condenser, further realizing energy conservation and consumption reduction and improving the operating economy of a unit.
The existing method for optimizing the circulating water system of the thermal power generating unit only considers the scheduling optimization of a circulating water pump: under the condition that the flow of new steam of a unit and the inlet temperature of circulating water are constant, the flow of the circulating water is increased, the pressure of a condenser is reduced, the power generation power of a steam turbine is increased, and the heat consumption is reduced; the increase of the circulating water amount causes the increase of the power consumption of the circulating pump and the increase of the power consumption. The circulating water amount is the optimal circulating water amount only when the difference between the increment of the power generation power of the steam turbine and the increment of the power consumption of the circulating water pump is maximum. Therefore, most circulating water optimization methods achieve the optimization of the circulating water flow rate only by changing the operation mode of the circulating water pump group. However, when the flow of the circulating water is analyzed and optimized, the inlet temperature of the circulating water is regarded as quantitative, and the influence of the cooling tower on the inlet temperature of the circulating water is not considered. If the natural draft cooling tower is adopted to cool the circulating water, the error is relatively small, but the influence of the cooling tower on the inlet temperature of the circulating water is huge when the mechanical draft cooling tower is adopted, and the influence factor must be considered.
An industrial circulating cooling water system optimization method based on an annual average cooling energy efficiency ratio and optimized operation is provided in Chinese patent CN106251079A disclosed in 2016, 12, 21, a concept of the annual average cooling energy efficiency ratio and the annual average cooling energy efficiency ratio of a circulating cooling water system is provided, and a calculation formula is given; the method has the advantages that the different energy consumption indexes under a plurality of working conditions in a certain environment of the circulating cooling water system are calculated and contrastively analyzed, so that the design and operation level of the industrial circulating cooling water system is improved; however, in the method, under the condition of assuming a certain inlet water temperature of the cooling water system, three general evaluation indexes of water pump efficiency, power consumption power and cooling energy efficiency ratio are calculated, the optimization method only considers the influence of the number of running water pumps and the working condition on the circulating water system, and the consideration factor is single; the default water inlet temperature of the cooling water system is certain, and the water inlet temperature is not in accordance with the actual production; therefore, the method has a certain optimization effect, but the optimization effect is not ideal.
Disclosure of Invention
The invention aims to overcome the defect of poor optimization effect caused by single and ideal consideration factors when the circulating water system is optimized in the prior art, and provides the circulating water system optimization method based on permanent magnet regulation and mechanical ventilation.
In order to solve the technical problems, the technical scheme of the invention is as follows:
the invention provides a circulating water system optimization method based on permanent magnet regulation and mechanical ventilation, which comprises the following steps:
a circulating water system optimization method based on permanent magnet regulation and mechanical ventilation is characterized by comprising the following steps:
s1: acquiring current operating condition data of the thermal power generating unit, parameters of a mechanical ventilation cooling tower and a characteristic report of a permanent magnet regulation circulating water pump;
s2: setting the permanent magnet regulation initial opening of the permanent magnet regulation circulating water pump and the initial starting number of fans of the mechanical ventilation cooling tower;
s3: establishing a power consumption characteristic model of the permanent magnet regulation circulating water pump, and calculating and obtaining the water yield of the permanent magnet regulation circulating water pump and the total power consumption of the permanent magnet regulation circulating water pump when the permanent magnet regulation initial opening degree of the permanent magnet regulation circulating water pump is obtained according to the characteristic report of the permanent magnet regulation circulating water pump;
s4: establishing a condenser heat exchange characteristic model, setting the assumed water inlet temperature of a condenser, utilizing the current operation condition data of the thermal power unit and the water outlet quantity of the permanent magnet adjusting circulating water pump, and calculating the water outlet temperature of the condenser and the end difference of the condenser;
s5: establishing a heat exchange characteristic model of the mechanical ventilation cooling tower, and calculating the water outlet temperature of the mechanical ventilation cooling tower according to the water outlet temperature of the condenser and the parameters of the mechanical ventilation cooling tower;
s6: comparing the difference value between the outlet water temperature of the mechanical ventilation cooling tower and the supposed inlet water temperature of the condenser, if the difference value is smaller than a preset threshold value, balancing the water temperatures of the mechanical ventilation cooling tower and the condenser, and executing the step S7; otherwise, substituting the outlet water temperature of the mechanical ventilation cooling tower calculated in the step S5 as the assumed inlet water temperature of the condenser into the condenser heat exchange characteristic model in the step S4, repeating the steps S4-S5 until the water temperatures of the mechanical ventilation cooling tower and the condenser are balanced, and executing the step S7;
s7: establishing a power consumption characteristic model of the mechanical ventilation cooling tower, and calculating the total power consumption of the mechanical ventilation cooling tower;
s8: establishing an influence model of the back pressure of the steam turbine on the power of the steam turbine, and calculating the micro-boost power of the steam turbine;
s9: calculating the actual increased power of the steam turbine according to the total power consumption of the permanent magnet regulation circulating water pump, the turbine micro-increased power and the total power consumption of the mechanical ventilation cooling tower, optimizing the objective function by utilizing a genetic algorithm by taking the maximum actual increased power of the steam turbine as an objective function, outputting the permanent magnet regulation opening of the permanent magnet regulation circulating water pump and the number of the opened fans of the mechanical ventilation cooling tower corresponding to the maximum value of the objective function, and finishing the optimization process;
the circulating water system based on permanent magnet regulation and mechanical ventilation operates for a preset time T according to the optimization result of the last optimization process 0 Thereafter, the steps S1-S9 are repeated to perform the next stage of optimization calculation.
Preferably, in S1, the data of the current operating condition of the thermoelectric generation unit includes the current power of the turbine, the exhaust gas volume of the turbine, the exhaust back pressure of the turbine, the specific enthalpy of the turbine exhaust, the specific enthalpy of the condenser condensed water, and the ambient temperature and humidity at the air inlet of the mechanical draft cooling tower.
Preferably, in S3, the water outlet amount D of the permanent magnet regulation circulation water pump when the permanent magnet regulation circulation water pump is at the permanent magnet regulation initial opening degree is obtained w And the total power consumption P of the permanent magnet adjusting circulating water pump pump The specific method comprises the following steps:
when the permanent magnet adjusting circulating water pump leaves a factory, a characteristic report is attached, wherein the characteristic report comprises a relation curve chart among the lift, the power, the efficiency and the flow of the permanent magnet adjusting circulating water pump at a rated rotating speed. And fitting the curve to obtain a relational expression of each parameter relative to the flow change. The variable speed regulation of the permanent magnet regulation circulating water pump means that under the condition that a pipeline characteristic curve is not changed, the characteristic curve of the pump is changed by changing the rotating speed, so that the working point of the pump is changed. When the variable rotating speed performance test is not carried out in the characteristic report of the permanent magnet regulation circulating water pump, the characteristics of each parameter after the rotating speed is changed can be obtained by deduction according to the proportional rate principle;
establishing a permanent magnet regulation circulating water pump characteristic equation according to a permanent magnet regulation circulating water pump rotating speed ratio z corresponding to the permanent magnet regulation initial opening degree O of the permanent magnet regulation circulating water pump, wherein the permanent magnet regulation circulating water pump rotating speed ratio z comprises the following steps:
the relation equation of the head and the flow of the permanent magnet regulation circulating water pump is as follows:
the permanent magnet adjusting circulating water pump pipeline resistance characteristic equation:
the relation equation of the shaft power and the flow of the permanent magnet regulation circulating water pump is as follows:
wherein H is the head of the permanent magnet adjusting circulating water pump, and the unit is meter; q. q.s v The flow of the circulating water pump is regulated by permanent magnet, and the unit is ton/hour; h f1 Is the pipeline resistance in meters; h st Is a still water pipe with the unit of meter,
is the pipeline resistance coefficient; z is the rotation speed ratio; h 0 、A 1 、A 2 、A 3 、A 4 Fitting each order coefficient for a polynomial of the water pump lift and flow at a rated rotating speed; b is 1 、B 2 、B 3 Fitting each order coefficient for a polynomial of the water pump power and the flow at the rated rotating speed;
the parallel equation of the n permanent magnet adjusting circulating water pumps at the same rotating speed is as follows:
the parallel equation and the permanent magnet adjusting circulating water pump pipeline resistance characteristic equation under the same rotating speed of the n water pumps are combined to obtain the parallel operation working point (Q) of the circulating water pumps And are ，H And are ) And then the actual working point (Q) of the single permanent magnet regulation circulating water pump is obtained And are /n，H And are ) And then the water outlet quantity D of the circulating water pump is adjusted by the permanent magnet w ＝Q And are And the total power consumption of the permanent magnet adjusting circulating water pump is as follows:
in actual operation, the flow and the lift of the working point of the permanent magnet adjusting circulating water pump can be obtained through test and measurement, and the static water pipe H is obtained through fitting st And coefficient of resistance of pipe
The operating working point of the permanent magnet adjusting circulating water pump is the intersection point of the characteristic curve of the permanent magnet adjusting circulating water pump and the characteristic curve of the pipeline, and the operating working point of the single pump can be obtained by combining the two modes. The working point of the parallel connection of the permanent magnet regulation circulating water pumps is obtained by firstly obtaining a characteristic curve of the parallel connection of the water pumps according to the principle that the lift is constant and the flow is superposed, then obtaining an intersection point with a pipeline resistance curve, and obtaining the operating working point of the corresponding single pump from the characteristic curve of the single pump after the parallel connection of the lift is obtained.
Preferably, in S4, the specific process of calculating the condenser outlet water temperature is:
setting the assumed water inlet temperature of the condenser as t w1 Then the temperature t of the outlet water of the condenser w2 Comprises the following steps:
t w2 ＝t w1 +Δt
wherein, delta t is the temperature rise of the number in the condenser, and the unit is centigrade; h is c The specific enthalpy of the steam turbine exhaust steam is kilojoule/kilogram; h' c Specific enthalpy of condensed water of the condenser is expressed in kilojoule/kilogram; d w The water outlet quantity of the circulating water pump is regulated by permanent magnets, and the unit is ton/hour; d c Is the exhaust volume of the steam turbine in tonIn terms of hours.
Preferably, in S4, the specific process of calculating the condenser end difference δ t is as follows:
wherein, delta t is the temperature rise of the number in the condenser, and the unit is centigrade; a. the c The total heat transfer area of the condenser is expressed in square meters; k c The overall heat transfer coefficient of the condenser; e is the natural logarithm.
Preferably, in the step S5, the outlet water temperature τ of the mechanical draft cooling tower is calculated w2 The specific process comprises the following steps:
water inlet temperature tau of mechanical draft cooling tower w1 ＝t w2 Assuming that the mechanical draft cooling tower effluent temperature is
Establishing an Simpson approximate formula of a Merkel enthalpy difference equation:
i m ＝(i 1 +i 2 )/2
characteristic number A lambda
Wherein c is the specific heat of the cooling water and has the unit of kilojoule/(kilogram Kelvin); k is the influence coefficient of evaporation on heat; i.e. i 1 、i m And i 2 Respectively including the enthalpy value of air entering the mechanical ventilation cooling tower, the enthalpy value of air in an average state and the enthalpy value of air discharged from the mechanical ventilation cooling tower, wherein the unit is kilojoule/kilogram; i ″) 1 、i″ m And i ″) 2 Respectively the water outlet temperature tau of the mechanical draft cooling tower w1 Corresponding saturated air enthalpy value and average water temperature
Corresponding saturated air enthalpy value and outlet water temperature of mechanical draft cooling tower
The corresponding enthalpy value of saturated air is kilojoule/kilogram; a is a characteristic coefficient of the filler, and lambda is a gas-water ratio; t is the temperature of air entering the mechanical draft cooling tower, and the unit is centigrade; phi is the relative humidity of the air; p ″) v Is the saturated steam partial pressure in Pa; p is a radical of a Is atmospheric pressure in pascals; t is the time-humid air temperature, and the unit is centigrade;
if the difference between the cooling number and the characteristic number satisfies the preset precision, the water outlet temperature tau of the mechanical draft cooling tower w2 Equal to the assumed temperature of the water outlet of the mechanical draft cooling tower
Otherwise, adopting dichotomy iterative approximation until the difference between the cooling number and the characteristic number meets the preset precision, and taking the assumed temperature of the mechanical draft cooling tower effluent corresponding to the preset precision as the mechanical draft cooling tower effluent temperature tau w2 。
In this process, the cooling number is a parameter representing the cooling capacity, the value of which is related to the external meteorological conditions and not to the configuration and type of the mechanical draft cooling tower itself; the characteristic number is the characteristic number of the mechanical ventilation cooling tower, reflects the cooling capacity of the mechanical ventilation cooling tower, is related to the structure and the performance of the water spraying filler and the flow of water and air, and is given by a manufacturer or a research institution as a constant coefficient of the heat dissipation characteristic.
Preferably, in S7, the total power consumption P of the mechanical draft cooling tower is calculated fan The specific process comprises the following steps:
establishing a ventilation resistance equation of the mechanical ventilation cooling tower:
wherein H f2 The unit is the ventilation resistance of a mechanical ventilation cooling tower, and is Pa; k j Resistance coefficients of all parts of the mechanical ventilation cooling tower are obtained; v j The unit of the air flow rate of each part of the mechanical draft cooling tower is meter/second; rho m The average density of air in the mechanical ventilation cooling tower is expressed in kilogram/cubic meter;
establishing a full pressure equation of a fan of the mechanical ventilation cooling tower:
H＝f(Q)
wherein H is the total pressure of a fan of the mechanical draft cooling tower, and the unit is Pa; q is the fan flow of the mechanical draft cooling tower, and the unit is cubic meter per second;
combining a ventilation resistance equation and a fan full pressure equation of the mechanical ventilation cooling tower to obtain a fan flow Q of the mechanical ventilation cooling tower, and obtaining the fan power consumption P of the mechanical ventilation cooling tower corresponding to Q from a power characteristic curve of the mechanical ventilation cooling tower; then the process of the first step is carried out,
mechanical draft coolingTotal tower power consumption P fan And (NP), wherein N is the number of the fans of the mechanical draft cooling tower which are started initially.
Preferably, in S8, the turbine micro-boost power Δ P is calculated t The specific method comprises the following steps:
calculating turbine micro-boost power delta P t The specific method comprises the following steps:
ΔP t ＝f 1 (P t ，P k )
t s ＝t w1 +Δt+δt
P k ＝P s
wherein, P t The current power of the steam turbine is megawatt; p k Is the exhaust back pressure of the steam turbine, and the unit is Pa; t is t s The saturation temperature of steam in a condenser is given in centigrade; p s Is t s The corresponding saturation pressure in pa; t is t w1 The assumed water inlet temperature of the condenser is given in centigrade; delta t is the temperature rise of the number in the condenser, and the unit is centigrade; δ t is condenser end difference, and the unit is centigrade.
Preferably, in S9, the objective function is specifically:
max P t +ΔP t -P fan -P pump
wherein, P t The current power of the steam turbine is megawatt; delta P t The micro-power increase of the steam turbine is realized, and the unit is megawatt; p fan The total power consumption of the mechanical draft cooling tower is megawatt; p pump The total power consumption of the circulating water pump is regulated by the permanent magnet, and the unit is megawatt.
Preferably, in S9, the specific method for optimizing the objective function by using the genetic algorithm is as follows:
setting the initial opening degree of the permanent magnet regulation circulating water pump and the initial opening number of fans of the mechanical ventilation cooling tower as an initial generation population, and solving an objective function by using the initial generation population;
and judging whether population iteration is finished, if not, updating the initial population, solving the objective function until the iteration is finished, and outputting the corresponding permanent magnet regulation opening degree of the circulating water pump and the number of the fans of the mechanical ventilation cooling tower when the objective function is the maximum value.
Methods for updating the primary population include chromosome crossing and mutation of the primary population.
Compared with the prior art, the technical scheme of the invention has the beneficial effects that:
setting the permanent magnet regulation initial opening degree of a permanent magnet regulation circulating water pump and the initial opening number of fans of a mechanical ventilation cooling tower, comprehensively considering the combined action of the permanent magnet regulation circulating water pump and the fans of the mechanical ventilation cooling tower on a circulating water system, establishing a steam turbine back pressure-to-steam turbine power influence model, a condenser heat exchange characteristic model, a permanent magnet regulation circulating water pump power consumption characteristic, a mechanical ventilation cooling tower heat exchange and power consumption characteristic model, and calculating corresponding data, namely comprehensively analyzing influence factors of the economy of the circulating water system, wherein the analyzed factors are fit with the actual production; and finally, taking the actual power increase of the steam turbine as a maximum value as an objective function, updating the permanent magnet adjusting opening of the permanent magnet adjusting circulating water pump and the number of the fans of the mechanical ventilation cooling tower to optimize the objective function by utilizing a genetic algorithm until population iteration is completed, and obtaining the maximum value of the objective function, wherein the permanent magnet adjusting opening of the permanent magnet adjusting circulating water pump and the number of the fans of the mechanical ventilation cooling tower correspond to each other, so that the optimization effect is better, and the running mode of the circulating water system is more economic.
Drawings
Fig. 1 is a flowchart of a method for optimizing a circulating water system based on permanent magnet regulation and mechanical ventilation according to an embodiment of the present invention.
Detailed Description
The drawings are for illustrative purposes only and are not to be construed as limiting the patent;
for the purpose of better illustrating the embodiments, certain features of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product;
it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
The technical solution of the present invention is further described below with reference to the accompanying drawings and examples.
Examples
The embodiment provides a method for optimizing a circulating water system based on permanent magnet regulation and mechanical ventilation, and as shown in fig. 1, the method comprises the following steps:
a circulating water system optimization method based on permanent magnet regulation and mechanical ventilation is characterized by comprising the following steps:
s1: acquiring current operating condition data of the thermal power generating unit, parameters of a mechanical ventilation cooling tower and a characteristic report of a permanent magnet regulation circulating water pump;
s2: setting the permanent magnet adjusting initial opening of the permanent magnet adjusting circulating water pump and the initial number of the fans of the mechanical ventilation cooling tower;
s3: establishing a power consumption characteristic model of the permanent magnet regulation circulating water pump, and calculating and obtaining the water yield of the permanent magnet regulation circulating water pump and the total power consumption of the permanent magnet regulation circulating water pump when the permanent magnet regulation initial opening degree of the permanent magnet regulation circulating water pump is obtained according to the characteristic report of the permanent magnet regulation circulating water pump;
s4: establishing a condenser heat exchange characteristic model, setting the assumed water inlet temperature of a condenser, utilizing the current operation condition data of the thermal power unit and the water outlet quantity of the permanent magnet adjusting circulating water pump, and calculating the water outlet temperature of the condenser and the end difference of the condenser;
s5: establishing a heat exchange characteristic model of the mechanical ventilation cooling tower, and calculating the water outlet temperature of the mechanical ventilation cooling tower according to the water outlet temperature of the condenser and the parameters of the mechanical ventilation cooling tower;
s6: comparing the difference value between the outlet water temperature of the mechanical ventilation cooling tower and the supposed inlet water temperature of the condenser, if the difference value is smaller than a preset threshold value, balancing the water temperatures of the mechanical ventilation cooling tower and the condenser, and executing the step S7; otherwise, substituting the outlet water temperature of the mechanical ventilation cooling tower calculated in the step S5 as the assumed inlet water temperature of the condenser into the condenser heat exchange characteristic model in the step S4, repeating the steps S4-S5 until the water temperatures of the mechanical ventilation cooling tower and the condenser are balanced, and executing the step S7;
s7: establishing a power consumption characteristic model of the mechanical ventilation cooling tower, and calculating the total power consumption of the mechanical ventilation cooling tower;
s8: establishing an influence model of the back pressure of the steam turbine on the power of the steam turbine, and calculating the micro-boost power of the steam turbine;
s9: and calculating the actual increased power of the steam turbine according to the total power consumption of the permanent magnet regulation circulating water pump, the turbine micro-increased power and the total power consumption of the mechanical ventilation cooling tower, optimizing the objective function by utilizing a genetic algorithm by taking the maximum actual increased power of the steam turbine as the objective function, outputting the permanent magnet regulation opening of the permanent magnet regulation circulating water pump and the number of the opened fans of the mechanical ventilation cooling tower corresponding to the maximum value of the objective function, and finishing the optimization process.
The circulating water system based on permanent magnet regulation and mechanical ventilation operates for a preset time T according to the optimization result of the last optimization process 0 Thereafter, the steps S1-S19 are repeated to perform the next stage of optimization calculation. In this embodiment, the time T is preset 0 ＝10min。
And in S1, the current operating condition data of the thermoelectric generator set comprises the current power of the turbine, the exhaust volume of the turbine, the exhaust back pressure of the turbine, the exhaust specific enthalpy of the turbine, the specific enthalpy of condensed water of the condenser and the ambient temperature and humidity at the air inlet of the mechanical draft cooling tower.
In the step S3, obtaining the water outlet quantity D of the permanent magnet regulation circulating water pump when the permanent magnet regulation circulating water pump is in the permanent magnet regulation initial opening degree w And the total power consumption P of the permanent magnet adjusting circulating water pump pump The specific method comprises the following steps:
when the permanent magnet adjusting circulating water pump leaves a factory, a characteristic report is attached, wherein the characteristic report comprises a relation curve chart among the lift, the power, the efficiency and the flow of the permanent magnet adjusting circulating water pump at a rated rotating speed. And fitting the curve to obtain a relational expression of each parameter relative to the flow change. The variable speed regulation of the permanent magnet regulation circulating water pump means that under the condition that a pipeline characteristic curve is not changed, the characteristic curve of the pump is changed by changing the rotating speed, so that the working point of the pump is changed. When the variable rotating speed performance test is not carried out in the characteristic report of the permanent magnet regulation circulating water pump, the characteristics of each parameter after the rotating speed is changed can be obtained by deduction according to the proportional rate principle;
establishing a permanent magnet regulation circulating water pump characteristic equation according to a permanent magnet regulation circulating water pump rotating speed ratio z corresponding to the permanent magnet regulation initial opening degree O of the permanent magnet regulation circulating water pump, wherein the permanent magnet regulation circulating water pump rotating speed ratio z comprises the following steps:
the relation equation of the head and the flow of the permanent magnet regulation circulating water pump is as follows:
the permanent magnet adjusting circulating water pump pipeline resistance characteristic equation:
the relation equation of the shaft power and the flow of the permanent magnet regulation circulating water pump is as follows:
wherein H is the head of the permanent magnet adjusting circulating water pump, and the unit is meter; q. q.s v The flow of the circulating water pump is regulated by permanent magnet, and the unit is ton/hour; h f1 Is the pipeline resistance in meters; h st Is a still water pipe with the unit of meter,
is the pipeline resistance coefficient; z is the rotation speed ratio; h 0 、A 1 、A 2 、A 3 、A 4 Fitting each order coefficient for a polynomial of the water pump lift and flow at a rated rotating speed; b is 1 、B 2 、B 3 Fitting each order coefficient for a polynomial of the water pump power and the flow at the rated rotating speed;
the parallel equation of the n permanent magnet adjusting circulating water pumps at the same rotating speed is as follows:
the parallel equation and the permanent magnet adjusting circulating water pump pipeline resistance characteristic equation under the same rotating speed of the n water pumps are combined to obtain the parallel operation working point (Q) of the circulating water pumps And are ，H And are ) Go forward and go forwardTo obtain the actual working point (Q) of the single permanent-magnet regulation circulating water pump And are /n，H And are ) And then the water outlet quantity D of the circulating water pump is adjusted by the permanent magnet w ＝Q And are And the total power consumption of the permanent magnet adjusting circulating water pump is as follows:
in actual operation, the flow and the lift of the working point of the permanent magnet adjusting circulating water pump can be obtained through test and measurement, and the static water pipe H is obtained through fitting st And coefficient of resistance of pipe
The operating working point of the permanent magnet adjusting circulating water pump is the intersection point of the characteristic curve of the permanent magnet adjusting circulating water pump and the characteristic curve of the pipeline, and the operating working point of the single pump can be obtained by combining the two modes. The working point of the parallel connection of the permanent magnet regulation circulating water pumps is obtained by firstly obtaining a characteristic curve of the parallel connection of the water pumps according to the principle that the lift is constant and the flow is superposed, then obtaining an intersection point with a pipeline resistance curve, and obtaining the operating working point of the corresponding single pump from the characteristic curve of the single pump after the parallel connection of the lift is obtained.
In S4, the specific process of calculating the condenser outlet water temperature is:
setting the assumed water inlet temperature of the condenser as t w1 Then the temperature t of the outlet water of the condenser w2 Comprises the following steps:
t w2 ＝t w1 +Δt
wherein, delta t is the temperature rise of the number in the condenser, and the unit is centigrade; h is c The specific enthalpy of the steam turbine exhaust steam is kilojoule/kilogram; h' c Specific enthalpy of condensed water of the condenser is expressed in kilojoule/kilogram; d w The water outlet quantity of the circulating water pump is regulated by permanent magnets, and the unit is ton/hour; d c The unit is the exhaust volume of the steam turbine and is ton/hour.
In S4, the specific process of calculating the condenser end difference δ t is:
wherein, delta t is the temperature rise of the number in the condenser, and the unit is centigrade degree; a. the c The total heat transfer area of the condenser is expressed in square meters; k c The overall heat transfer coefficient of the condenser; e is the natural logarithm.
In S5, calculating the water outlet temperature tau of the mechanical draft cooling tower w2 The specific process comprises the following steps:
water inlet temperature tau of mechanical draft cooling tower w1 ＝t w2 Assuming that the mechanical draft cooling tower effluent temperature is
Establishing an Simpson approximate formula of a Merkel enthalpy difference equation:
i m ＝(i 1 +i 2 )/2
characteristic number A lambda
Wherein c is the specific heat of the cooling water and has the unit of kilojoule/(kilogram Kelvin); k is the influence coefficient of evaporation on heat; i.e. i 1 、i m And i 2 Respectively including the enthalpy value of air entering the mechanical ventilation cooling tower, the enthalpy value of air in an average state and the enthalpy value of air discharged from the mechanical ventilation cooling tower, wherein the unit is kilojoule/kilogram; i ″) 1 、i″ m And i ″) 2 Respectively the water outlet temperature tau of the mechanical draft cooling tower w1 Corresponding saturated air enthalpy value and average water temperature
Corresponding saturated air enthalpy value and outlet water temperature of mechanical draft cooling tower
The corresponding enthalpy value of saturated air is kilojoule/kilogram; a is a characteristic coefficient of the filler, and lambda is a gas-water ratio; t is the temperature of air entering the mechanical draft cooling tower, and the unit is centigrade; phi is the relative humidity of the air; p ″) v Is the saturated steam partial pressure in Pa; p is a radical of a Is atmospheric pressure in pascals; t is the time-humid air temperature, and the unit is centigrade;
if the difference between the cooling number and the characteristic number satisfies the preset precision, the water outlet temperature tau of the mechanical draft cooling tower w2 Equal to the assumed temperature of the water outlet of the mechanical draft cooling tower
Otherwise, adopt twoIterative approximation by a component method until the difference between the cooling number and the characteristic number meets the preset precision, and taking the assumed temperature of the mechanical draft cooling tower effluent corresponding to the preset precision as the mechanical draft cooling tower effluent temperature tau w2 。
In this process, the cooling number is a parameter representing the cooling capacity, the value of which is related to the external meteorological conditions and not to the configuration and type of the mechanical draft cooling tower itself; the characteristic number is the characteristic number of the mechanical ventilation cooling tower, reflects the cooling capacity of the mechanical ventilation cooling tower, is related to the structure and the performance of the water spraying filler and the flow of water and air, and is given by a manufacturer or a research institution as a constant coefficient of the heat dissipation characteristic.
In the step S7, the total power consumption P of the mechanical draft cooling tower is calculated fan The specific process comprises the following steps:
establishing a ventilation resistance equation of the mechanical ventilation cooling tower:
wherein H f2 The unit is the ventilation resistance of a mechanical ventilation cooling tower, and is Pa; k is j Resistance coefficients of all parts of the mechanical ventilation cooling tower are obtained; v j The unit of the air flow rate of each part of the mechanical draft cooling tower is meter/second; rho m The average density of air in the mechanical ventilation cooling tower is expressed in kilogram/cubic meter;
establishing a full pressure equation of a fan of the mechanical ventilation cooling tower:
H＝f(Q)
wherein H is the total pressure of a fan of the mechanical draft cooling tower, and the unit is Pa; q is the fan flow of the mechanical draft cooling tower, and the unit is cubic meter per second;
combining a ventilation resistance equation and a fan full pressure equation of the mechanical ventilation cooling tower to obtain a fan flow Q of the mechanical ventilation cooling tower, and obtaining the fan power consumption P of the mechanical ventilation cooling tower corresponding to Q from a power characteristic curve of the mechanical ventilation cooling tower; then the process of the first step is carried out,
total power consumption P of mechanical ventilation cooling tower fan NP where N is mechanical draft cooling tower windThe number of the machine is initially started.
In the step S8, the turbine micro-boost power delta P is calculated t The specific method comprises the following steps:
calculating turbine micro-boost power delta P t The specific method comprises the following steps:
ΔP t ＝f 1 (P t ，P k )
t s ＝t w1 +Δt+δt
P k ＝P s
wherein, P t The current power of the steam turbine is megawatt; p k Is the exhaust back pressure of the steam turbine, and the unit is Pa; t is t s The saturation temperature of steam in a condenser is given in centigrade; p s Is t s The corresponding saturation pressure in pa; t is t w1 The assumed water inlet temperature of the condenser is given in centigrade; delta t is the temperature rise of the number in the condenser, and the unit is centigrade; δ t is condenser end difference, and the unit is centigrade.
In S9, the objective function is specifically:
max P t +ΔP t -P fan -P pump
wherein, P t The current power of the steam turbine is megawatt; delta P t The micro-power increase of the steam turbine is realized, and the unit is megawatt; p fan The total power consumption of the mechanical draft cooling tower is megawatt; p pump The total power consumption of the circulating water pump is regulated by the permanent magnet, and the unit is megawatt.
In S9, the specific method for optimizing the objective function by using the genetic algorithm is as follows:
setting the initial opening degree of the permanent magnet regulation circulating water pump and the initial opening number of fans of the mechanical ventilation cooling tower as an initial generation population, and solving an objective function by using the initial generation population;
and judging whether population iteration is finished, if not, updating the initial population, solving the objective function until the iteration is finished, and outputting the corresponding permanent magnet regulation opening degree of the circulating water pump and the number of the fans of the mechanical ventilation cooling tower when the objective function is the maximum value.
Methods for updating the primary population include chromosome crossing and mutation of the primary population.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. A circulating water system optimization method based on permanent magnet regulation and mechanical ventilation is characterized by comprising the following steps:
s1: acquiring current operating condition data of the thermal power generating unit, parameters of a mechanical ventilation cooling tower and a characteristic report of a permanent magnet adjusting circulating water pump;
s2: setting the permanent magnet regulation initial opening of the permanent magnet regulation circulating water pump and the initial starting number of fans of the mechanical ventilation cooling tower;
s3: establishing a power consumption characteristic model of the permanent magnet regulation circulating water pump, and calculating and obtaining the water yield of the permanent magnet regulation circulating water pump and the total power consumption of the permanent magnet regulation circulating water pump when the permanent magnet regulation initial opening degree of the permanent magnet regulation circulating water pump is obtained according to the characteristic report of the permanent magnet regulation circulating water pump;
s4: establishing a condenser heat exchange characteristic model, setting the assumed water inlet temperature of a condenser, utilizing the current operation condition data of the thermal power unit and the water outlet quantity of the permanent magnet adjusting circulating water pump, and calculating the water outlet temperature of the condenser and the end difference of the condenser;
s5: establishing a heat exchange characteristic model of the mechanical ventilation cooling tower, and calculating the water outlet temperature of the mechanical ventilation cooling tower according to the water outlet temperature of the condenser and the parameters of the mechanical ventilation cooling tower;
s6: comparing the difference value between the outlet water temperature of the mechanical ventilation cooling tower and the supposed inlet water temperature of the condenser, if the difference value is smaller than a preset threshold value, balancing the water temperatures of the mechanical ventilation cooling tower and the condenser, and executing the step S7; otherwise, substituting the outlet water temperature of the mechanical ventilation cooling tower calculated in the step S5 as the assumed inlet water temperature of the condenser into the condenser heat exchange characteristic model in the step S4, repeating the steps S4-S5 until the water temperatures of the mechanical ventilation cooling tower and the condenser are balanced, and executing the step S7;
s7: establishing a power consumption characteristic model of the mechanical ventilation cooling tower, and calculating the total power consumption of the mechanical ventilation cooling tower;
s8: establishing an influence model of the back pressure of the steam turbine on the power of the steam turbine, and calculating the micro-boost power of the steam turbine;
s9: and calculating the actual increased power of the steam turbine according to the total power consumption of the permanent magnet regulation circulating water pump, the turbine micro-increased power and the total power consumption of the mechanical ventilation cooling tower, optimizing the objective function by utilizing a genetic algorithm by taking the maximum actual increased power of the steam turbine as the objective function, outputting the permanent magnet regulation opening of the permanent magnet regulation circulating water pump and the number of the opened fans of the mechanical ventilation cooling tower corresponding to the maximum value of the objective function, and finishing the optimization process.
2. The optimization method for the circulating water system based on the permanent magnet regulation and the mechanical ventilation as claimed in claim 1, wherein the data of the current operation condition of the thermoelectric generation set in the S1 includes current power of a turbine, exhaust capacity of the turbine, exhaust back pressure of the turbine, specific enthalpy of exhaust steam of the turbine, specific enthalpy of condensed water of a condenser and ambient temperature and humidity at an air inlet of a mechanical ventilation cooling tower.
3. The optimization method for a recirculating water system based on PMT and mechanical ventilation as claimed in claim 2, wherein in S3, obtaining the output D of the PMT recirculating water pump at the PMT initial opening w And the total power consumption P of the permanent magnet adjusting circulating water pump pump The specific method comprises the following steps:
establishing a permanent magnet regulation circulating water pump characteristic equation according to a permanent magnet regulation circulating water pump rotating speed ratio z corresponding to the permanent magnet regulation initial opening degree O of the permanent magnet regulation circulating water pump, wherein the permanent magnet regulation circulating water pump rotating speed ratio z comprises the following steps:
the relation equation of the head and the flow of the permanent magnet regulation circulating water pump is as follows:
the permanent magnet adjusting circulating water pump pipeline resistance characteristic equation:
the relation equation of the shaft power and the flow of the permanent magnet regulation circulating water pump is as follows:
wherein H is the head of the permanent magnet adjusting circulating water pump, and the unit is meter; q. q.s v The flow of the circulating water pump is regulated by permanent magnet, and the unit is ton/hour;
is the pipeline resistance in meters; h st Is a still water pipe with the unit of meter,
is the pipeline resistance coefficient; z is the rotation speed ratio; h 0 、A 1 、A 2 、A 3 、A 4 Fitting each order coefficient for a polynomial of the water pump lift and flow at a rated rotating speed; b is 1 、B 2 、B 3 Fitting each order coefficient for a polynomial of the water pump power and the flow at the rated rotating speed;
the parallel equation of the n permanent magnet adjusting circulating water pumps at the same rotating speed is as follows:
parallel equation and permanent magnet regulation circulating water pump pipeline under same rotating speed of simultaneous n water pumpsResistance characteristic equation to obtain parallel operation working point (Q) of circulating water pump And are ，H And are ) And then the actual working point (Q) of the single permanent magnet regulation circulating water pump is obtained And are /n，H And are ) And then the water outlet quantity D of the circulating water pump is adjusted by the permanent magnet w ＝Q And are And the total power consumption of the permanent magnet adjusting circulating water pump is as follows:
4. the optimization method for the circulating water system based on the permanent magnet regulation and the mechanical ventilation as claimed in claim 3, wherein in the step S4, the specific process of calculating the condenser outlet water temperature is as follows:
setting the assumed water inlet temperature of the condenser as t w1 Then the temperature t of the outlet water of the condenser w2 Comprises the following steps:
t w2 ＝t w1 +Δt
wherein, delta t is the temperature rise of the number in the condenser, and the unit is centigrade; h is a total of c The specific enthalpy of the steam turbine exhaust steam is kilojoule/kilogram; h' c Specific enthalpy of condensed water of the condenser is expressed in kilojoule/kilogram; d w The water outlet quantity of the circulating water pump is regulated by permanent magnets, and the unit is ton/hour; d c The unit is the exhaust volume of the steam turbine and is ton/hour.
5. The optimization method for the circulating water system based on the permanent magnet regulation and the mechanical ventilation as claimed in claim 4, wherein in the step S4, the specific process of calculating the condenser end difference δ t is as follows:
wherein the content of the first and second substances,delta t is the temperature rise of the number in the condenser, and the unit is centigrade; a. the c The total heat transfer area of the condenser is expressed in square meters; k c The overall heat transfer coefficient of the condenser; e is the natural logarithm.
6. The optimization method for a circulating water system based on permanent magnet regulation and mechanical ventilation as claimed in claim 5, wherein in S5, the outlet water temperature τ of the mechanical ventilation cooling tower is calculated w2 The specific process comprises the following steps:
water inlet temperature tau of mechanical draft cooling tower w1 ＝t w2 Assuming that the mechanical draft cooling tower effluent temperature is
Establishing an Simpson approximate formula of a Merkel enthalpy difference equation:
i m ＝(i 1 +i 2 )/2
characteristic number A lambda
Wherein c is the specific heat of the cooling water and has the unit of kilojoule/(kilogram Kelvin); k is the influence coefficient of evaporation on heat; i.e. i 1 、i m And i 2 Respectively including the enthalpy value of air entering the mechanical ventilation cooling tower, the enthalpy value of air in an average state and the enthalpy value of air discharged from the mechanical ventilation cooling tower, wherein the unit is kilojoule/kilogram; i ″) 1 、i″ m And i ″) 2 Respectively the water outlet temperature tau of the mechanical draft cooling tower w1 Corresponding saturated air enthalpy value and average water temperature
Corresponding saturated air enthalpy value and outlet water temperature of mechanical draft cooling tower
The corresponding enthalpy value of saturated air is kilojoule/kilogram; a is a characteristic coefficient of the filler, and lambda is a gas-water ratio; t is the temperature of air entering the mechanical draft cooling tower, and the unit is centigrade; phi is the relative humidity of the air; p ″) v Is the saturated steam partial pressure in Pa; p is a radical of a Is atmospheric pressure in pascals; t is the time-humid air temperature, and the unit is centigrade;
if the difference between the cooling number and the characteristic number satisfies the preset precision, the water outlet temperature tau of the mechanical draft cooling tower w2 Equal to the assumed temperature of the water outlet of the mechanical draft cooling tower
Otherwise, adopting dichotomy iterative approximation until the difference between the cooling number and the characteristic number meets the preset precision, and taking the assumed temperature of the mechanical draft cooling tower effluent corresponding to the preset precision as the mechanical draft cooling tower effluent temperature tau w2 。
7. The optimization method for a circulating water system based on permanent magnet regulation and mechanical ventilation as claimed in claim 6, wherein in S7, the total power consumption P of the cooling tower of the mechanical ventilation is calculated fan The specific process comprises the following steps:
establishing a ventilation resistance equation of the mechanical ventilation cooling tower:
wherein the content of the first and second substances,
the unit is the ventilation resistance of a mechanical ventilation cooling tower, and is Pa; k j Resistance coefficients of all parts of the mechanical ventilation cooling tower are obtained; v j The unit of the air flow rate of each part of the mechanical draft cooling tower is meter/second; rho m The average density of air in the mechanical ventilation cooling tower is expressed in kilogram/cubic meter;
establishing a full pressure equation of a fan of the mechanical ventilation cooling tower:
H＝f(Q)
wherein H is the total pressure of a fan of the mechanical draft cooling tower, and the unit is Pa; q is the fan flow of the mechanical draft cooling tower, and the unit is cubic meter per second;
combining a ventilation resistance equation and a fan full pressure equation of the mechanical ventilation cooling tower to obtain a fan flow Q of the mechanical ventilation cooling tower, and obtaining the fan power consumption P of the mechanical ventilation cooling tower corresponding to Q from a power characteristic curve of the mechanical ventilation cooling tower; then, the total power consumption P of the mechanical draft cooling tower fan And (NP), wherein N is the number of the fans of the mechanical draft cooling tower which are started initially.
8. According to claim7, the method for optimizing the circulating water system based on permanent magnet regulation and mechanical ventilation is characterized in that in S8, the micro-boost power delta P of the turbine is calculated t The specific method comprises the following steps:
ΔP t ＝f 1 (P t ，P k )
t s ＝t w1 +Δt+δt
P k ＝P s
wherein, P t The current power of the steam turbine is megawatt; p k Is the exhaust back pressure of the steam turbine, and the unit is Pa; t is t s The saturation temperature of steam in a condenser is given in centigrade; p s Is t s The corresponding saturation pressure in pa; t is t w1 The assumed water inlet temperature of the condenser is given in centigrade; delta t is the temperature rise of the number in the condenser, and the unit is centigrade; δ t is condenser end difference, and the unit is centigrade.
9. The optimization method for a circulating water system based on permanent magnet regulation and mechanical ventilation as claimed in claim 8, wherein in the step S9, the objective function is specifically:
max P t +ΔP t -P fan -P pump
wherein, P t The current power of the steam turbine is megawatt; delta P t The micro-power increase of the steam turbine is realized, and the unit is megawatt; p fan The total power consumption of the mechanical draft cooling tower is megawatt; p pump The total power consumption of the circulating water pump is regulated by the permanent magnet, and the unit is megawatt.
10. The method for optimizing a circulating water system based on permanent magnet regulation and mechanical ventilation according to claim 9, wherein in S9, the specific method for optimizing the objective function by using the genetic algorithm is as follows:
setting the initial opening degree of the permanent magnet regulation circulating water pump and the initial opening number of fans of the mechanical ventilation cooling tower as an initial generation population, and solving an objective function by using the initial generation population;
and judging whether population iteration is finished, if not, updating the initial population, solving the objective function until the iteration is finished, and outputting the corresponding permanent magnet regulation opening degree of the circulating water pump and the number of the fans of the mechanical ventilation cooling tower when the objective function is the maximum value.
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