CN112983579A - Cold end system of thermal power plant and efficiency optimization method thereof - Google Patents

Cold end system of thermal power plant and efficiency optimization method thereof Download PDF

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CN112983579A
CN112983579A CN202110256508.8A CN202110256508A CN112983579A CN 112983579 A CN112983579 A CN 112983579A CN 202110256508 A CN202110256508 A CN 202110256508A CN 112983579 A CN112983579 A CN 112983579A
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pressure
steam
entropy
condenser
low
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CN112983579B (en
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严俊杰
符悦
刘明
王进仕
邢秦安
刘继平
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Xian Jiaotong University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D13/00—Combinations of two or more machines or engines
    • F01D13/02—Working-fluid interconnection of machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/003—Arrangements for measuring or testing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
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Abstract

The invention discloses a cold end system of a thermal power plant and an efficiency optimization method thereof. The design step comprises the steps of reading main parameter information of a relevant unit, obtaining data such as steam turbine exhaust steam quantity, steam turbine extraction steam quantity, steam turbine exhaust steam enthalpy value and the like, then selecting the type of a multi-pressure condenser, and obtaining the system design with the optimal efficiency of a cold end system of the thermal power plant according to the type selection of the condenser; the invention can obtain the optimal design of the cold end system when the power generation power is maximum under the condition of fixed economic cost, thereby improving the economy of the thermal power plant.

Description

Cold end system of thermal power plant and efficiency optimization method thereof
Technical Field
The invention belongs to the field of cold end design of a thermal power plant, and particularly relates to a cold end system of the thermal power plant and an efficiency optimizing method thereof.
Background
Global electrification is accelerated, power consumption is strongly increased, primary energy is used as a main power for power production, and nearly 70% of primary energy is used for power production. The coal-fired power generation efficiency is further improved in the prior art, and the development of unit energy conservation and consumption reduction is vigorously carried out, so that the coal-fired power generation system has very important significance for economic development. According to the basic principles of thermodynamics, the efficiency of a coal-fired power plant is determined by the average heat absorption temperature and the average heat release temperature of the thermodynamic cycle of coal-fired power generation. Therefore, in order to improve the utilization of fuel, coal-fired power generation technology is developed in the direction of high-parameter and large-capacity. Besides improving the hot end parameters of the coal-fired generator set, improving the performance of the cold end of the power station is also an effective means for improving the efficiency of the coal-fired power station. Under the condition that most of the existing units adopt the multi-pressure condenser, the research on a cold end system adopting the multi-pressure condenser is developed on the basis of the principle of minimum entropy production, and an optimization design scheme with minimum irreversible loss of the cold end system is explored.
Disclosure of Invention
In order to improve the efficiency of the thermal power plant, the invention aims to provide a cold end system of the thermal power plant and an efficiency optimizing method thereof.
In order to achieve the purpose, the invention adopts the following technical scheme:
a cold end system of a thermal power plant comprises a low-pressure turbine stage group 1, a low-pressure turbine exhaust pipeline 2, a multi-pressure condenser 3, a cold source 4, a circulating water pump 5, a condensate pump 6 and a low-pressure regenerative heater 7;
the low-pressure turbine stage group 1 is provided with n steam outlets, the multi-pressure condenser 3 consists of n steam chambers with different pressures, the number of the steam chambers is 3-i, i is 1-n, the low-pressure turbine stage group 1 is provided with n steam outlets, the steam outlet of the low-pressure turbine stage group 1 is connected with the steam inlet of each steam chamber of the multi-pressure condenser 3 through a corresponding pipeline 2-i, the outlet of a condensed water chamber of the steam chamber 3-i in the multi-pressure condenser 3 is connected with the inlet of a condensed water chamber of the next steam chamber 3- (i +1), the outlet of the condensed water of the last steam chamber 3-n is connected with the inlet of the cooled water of the cold source 4, the outlet of the cooled water of the cold source 4 is connected with the inlet of the cooled water of the first steam chamber 3-1 through a circulating water pump 5, the outlet of the condensed water well of the last steam chamber 3-n is connected with the inlet of the condensed water pump 6, a water supply outlet of the condensate pump 6 is connected with a water supply inlet of the low-pressure regenerative heater 7, and a steam outlet of the low-pressure turbine stage group 1 is connected with a steam inlet of the low-pressure regenerative heater 7;
cooling water flows into the multi-pressure condenser 3 after being boosted by the circulating water pump 5 from the cold source 4, the cooling water absorbs heat in the multi-pressure condenser 3, the cooling water absorbs heat in the steam chamber 3-i, then flows into the next steam chamber 3- (i +1) to absorb heat, and then flows into the cold source 4 to release heat;
the steam in each steam chamber in the multi-pressure condenser 3 is radiated to cooling water to form condensed water, the condensed water in the steam chamber 3-i is collected in the condensed water chamber and then flows to the next steam chamber 3- (i +1), the condensed water in the last steam chamber 3-n flows to the low-pressure regenerative heater 7 after being pressurized by the condensed water pump 6, and exchanges heat with the steam in the low-pressure turbine stage group 1 in the low-pressure regenerative heater 7.
The cold source 4 is a cooling tower or lake water or seawater.
The multi-pressure condenser 3 is longitudinally arranged, each steam chamber of the multi-pressure condenser is provided with a single flow path, and condensed water among the steam chambers is connected in series.
The flow direction of the cooling water and the condensed water in the multi-pressure condenser 3 is from the steam chamber 3-i of the multi-pressure condenser to the next steam chamber 3- (i + 1).
The efficiency optimization method of the cold end system of the thermal power plant is a method for maximizing the generating power of the cold end system, applies the entropy production minimization principle, adopts a genetic algorithm to carry out multi-parameter optimization of the cold end system, and comprises the following steps:
step 1: obtaining the boundary condition of cold end system design, and obtaining the steam pressure, steam flow and steam enthalpy value of the low-pressure turbine stage group 1 at the inlet of the cold end system; obtaining the water supply pressure, water supply flow and water supply enthalpy value of a low-pressure regenerative heater 7 at the outlet of the cold end system, and the ambient temperature and pressure;
step 2: determining an optimized target, and selecting the optimized number of steam chambers;
and step 3: establishing a mathematical model of an optimization function, establishing an entropy production model of each component of the cold end system, and minimizing the total entropy production of the cold end system
Figure BDA0002968441260000031
As an objective function of cold end system optimization, a specific entropy production minimization model is established as follows:
total entropy production of cold end systems
Figure BDA0002968441260000032
The sum of the entropy products for each component:
Figure BDA0002968441260000033
in the formula:
Figure BDA0002968441260000034
is the entropy production of the low pressure turbine stage group, kW;
Figure BDA0002968441260000035
is the entropy production of the pipeline, kW;
Figure BDA0002968441260000036
is the entropy production of a multi-pressure condenser, kW;
Figure BDA0002968441260000037
is the entropy production of the circulating water pump, kW;
Figure BDA0002968441260000038
is the entropy production of the condensate pump, kW;
Figure BDA0002968441260000039
the entropy production of the low-pressure regenerative heater is kW;
1) the entropy yield of the low pressure turbine stage set is calculated by equation (2):
Figure BDA0002968441260000041
in the formula:
Figure BDA0002968441260000042
mass flow of the low-pressure turbine is kg/s; s1,outIs the entropy value of the fluid at the outlet of the low pressure turbine stage group, kJ/(kg. K); s1,inIs the entropy value of the fluid at the inlet of the low pressure turbine stage group, kJ/(kg. K);
the isentropic efficiency of each level of the low-pressure turbine in the cold end system is constant, so that the entropy of the low-pressure turbine part can be obtained by checking a water vapor enthalpy entropy table according to the pressure and enthalpy values of an inlet and an outlet:
the enthalpy value of the exhaust port of the low-pressure turbine stage group is calculated by the following formula:
h1,out＝h1,in-ηs(h1-h1s,out) (3)
in the formula: h is1,inAnd h1,outRespectively the enthalpy values of the steam inlet and the steam outlet of the low-pressure steam turbine stage group, kJ/kg; etasIsentropic efficiency,%; h is1s,outThe constant entropy enthalpy value of the outlet of the low-pressure turbine stage group is kJ/kg;
2) considering the pressure loss of the pipeline, a calculation model of the entropy production of the pipeline is calculated by the formula (5):
p2-i,out＝p2-i,in-Δp2-i (4)
Figure BDA0002968441260000043
Figure BDA0002968441260000044
in the formula:
Figure BDA0002968441260000045
mass flow in the pipeline, kg/s; p is a radical of2-i,inIs the pressure of the fluid at the inlet of the pipeline, MPa; p is a radical of2-i,inIs the pressure of the fluid at the outlet of the pipeline, MPa; Δ p is the pressure loss of the pipe, MPa; s2-i,outThe entropy value of the fluid at the outlet of the pipeline is obtained by checking a water vapor enthalpy entropy table according to the pressure and the enthalpy value at the outlet of the pipeline, and kJ/(kg.K); s2-i,inThe entropy value of the fluid at the pipeline inlet is obtained by checking a water vapor enthalpy entropy table according to the pressure and the enthalpy value of the pipeline inlet, and kJ/(kg.K) is obtained;
3) considering the pressure loss inside the multi-pressure condenser in the cold end system, the entropy production of the multi-pressure condenser is calculated by an equation (7), the entropy production of the multi-pressure condenser is the sum of the entropy production of n steam chambers in the multi-pressure condenser, wherein the entropy production of each steam chamber is calculated by an equation (8):
Figure BDA0002968441260000051
Figure BDA0002968441260000052
Figure BDA0002968441260000053
in the formula:
Figure BDA0002968441260000054
is the heat exchange capacity of each steam chamber in the condenser, kW;
Figure BDA0002968441260000055
is the mass flow of each steam chamber of the condenser
Figure BDA0002968441260000056
kg/s；h3-iChecking a water vapor enthalpy entropy table, namely kJ/kg for the enthalpy value of saturated water corresponding to the steam pressure in a steam chamber of a condenser; t is3-i,hotIs the steam saturation temperature, K, of each steam chamber in the condenser;
Figure BDA0002968441260000057
is the mass flow of cooling water, kg/s; c. CcwIs the specific heat capacity of the cooling water in the condenser, kJ/(kg. K); t is3-i,cw,inIs the inlet water temperature of the cooling water in each steam chamber in the condenser, K; t is3-i,cw,outThe outlet water temperature K of cooling water in each steam chamber in the condenser; lambda is the flow resistance coefficient on the cooling water side of the condenser; rhocwIs the density of cooling water in the steam chamber of the condenser in kg/m3；T3-i,cwIs the water temperature of the cooling water, K; a. the3-iIs the area of the steam chamber of the condenser, m2；d3-iThe inner diameter of a cooling water pipe in a steam chamber of the condenser is m; l is3-iThe length of a cooling water pipe in a steam chamber of the condenser is m;
4) the entropy production of the circulating water pump is calculated by equation (10):
Figure BDA0002968441260000058
in the formula: scw,outIs the entropy value of the fluid at the outlet of the circulating water pump, kJ/(kg.K); scw,inIs the entropy value of the fluid at the inlet of the circulating water pump, kJ/(kg. K);
5) the entropy yield of the condensate pump is calculated by equation (11):
Figure BDA0002968441260000059
in the formula:
Figure BDA0002968441260000061
mass flow of the condensate pump is kg/s; s6,outThe entropy value of the fluid at the outlet of the condensate pump is kJ/(kg.K); s6,inIs the entropy value of the fluid at the inlet of the condensate pump, kJ/(kg. K);
entropy values of inlets and outlets of the condensate pump and the circulating water pump are obtained by table lookup of pressures and enthalpy values of the inlets and outlets, an enthalpy value of an outlet of the pump is determined by a pump power equation,
Figure BDA0002968441260000062
in the formula:
Figure BDA0002968441260000063
is the input power of the pump, kW;
Figure BDA0002968441260000064
is the mass flow of the working medium in the pump, kg/s; delta PpumpIs the pressure change in the pump, kPa; rhopumpIs the density of the working medium in the pump, kg/m3；ηpumpIs the efficiency of the pump,%; h ispump,outIs the enthalpy value of the outlet of the pump, kJ/kg; h ispump,inIs the enthalpy at the pump inlet, kJ/kg.
6) The entropy production of the low-pressure regenerative heater is calculated by equation (13):
Figure BDA0002968441260000065
in the formula:
Figure BDA0002968441260000066
is the heat exchange capacity in the low-pressure regenerative heater, kW; t is7,hotIs the steam saturation temperature, K;
Figure BDA0002968441260000067
the mass flow of the feed water in the low-pressure regenerative heater is kg/s; c. C7,coldIs the specific heat capacity of the feed water in the low-pressure regenerative heater, kJ/(kg.K); t is7,cold,inIs the inlet water temperature of the feed water in the low-pressure regenerative heater, K; t is7,cold,outIs the outlet water temperature of the feed water in the low-pressure regenerative heater, K;
and 4, step 4: carrying out multi-parameter optimization, wherein the variable of the multi-parameter optimization is the steam quantity entering each steam chamber of the multi-pressure condenser
Figure BDA0002968441260000068
Area A of each steam chamber of the condenser3-1,A3-2,…,A3-nAnd the flow rate of the circulating water
Figure BDA0002968441260000069
The objective function of multi-parameter optimization is that the total entropy production of the cold end system is minimized, the multi-parameter optimization mode adopts a genetic algorithm, the feasible solutions which can be selected in the variable range are traversed, then the total entropy production of the cold end system is obtained, the total entropy production values of the cold end system of each solution are compared, the feasible solution corresponding to the minimum entropy production value is found, and the solution is the optimal efficiency of the cold end system of the thermal power plant.
The population scale of the genetic algorithm is 150-250, the number of the individuals of the previous generation in each generation is 2-5, the cross probability is 0.6-0.8, and the iteration generation number is 150-300.
Compared with the prior art, the invention has the following advantages:
(1) the influence among all parts of the cold end is considered in detail, and the cold end system of the thermal power plant with the highest efficiency is obtained from the system level;
(2) the method utilizes a genetic algorithm to carry out multi-parameter optimization on the cold end system, minimizes the entropy product as a target function, and reduces the irreversible loss in the system design from the second law of thermodynamics.
Drawings
FIG. 1 is a schematic diagram of the cold end system of the present invention.
FIG. 2 is a flow chart of the efficiency optimization method of the present invention.
Fig. 3 is a diagram illustrating the relationship among boundary conditions, variables and optimization objectives of the cold end system of the thermal power plant and the efficiency optimization method thereof.
Fig. 4 is a comparison chart of the results of the cold end optimization and the reference working condition of the embodiment of the thermal power plant cold end system and the efficiency optimization method thereof.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1, the cold end system of the thermal power plant of the present invention is composed of a low pressure turbine stage group 1, a low pressure turbine exhaust pipe 2, a multi-pressure condenser 3, a cold source 4, a circulating water pump 5, a condensate pump 6 and a low pressure regenerative heater 7; the low-pressure turbine stage group 1 is provided with n steam outlets, the multi-pressure condenser 3 consists of n steam chambers with different pressures, the number of the steam chambers is 3-i, i is 1-n, the low-pressure turbine stage group 1 is provided with n steam outlets, the steam outlet of the low-pressure turbine stage group 1 is connected with the steam inlet of each steam chamber of the multi-pressure condenser 3 through a corresponding pipeline 2-i, the outlet of a condensed water chamber of the steam chamber 3-i in the multi-pressure condenser 3 is connected with the inlet of a condensed water chamber of the next steam chamber 3- (i +1), the outlet of the condensed water of the last steam chamber 3-n is connected with the inlet of the cooled water of the cold source 4, the outlet of the cooled water of the cold source 4 is connected with the inlet of the cooled water of the first steam chamber 3-1 through a circulating water pump 5, the outlet of the condensed water well of the last steam chamber 3-n is connected with the inlet of the condensed water pump 6, a water supply outlet of the condensate pump 6 is connected with a water supply inlet of the low-pressure regenerative heater 7, and a steam outlet of the low-pressure turbine stage group 1 is connected with a steam inlet of the low-pressure regenerative heater 7; cooling water flows into the multi-pressure condenser 3 after being boosted by the circulating water pump 5 from the cold source 4, the cooling water absorbs heat in the multi-pressure condenser 3, the cooling water absorbs heat in the steam chamber 3-i, then flows into the next steam chamber 3- (i +1) to absorb heat, and then flows into the cold source 4 to release heat; the steam in each steam chamber in the multi-pressure condenser 3 is radiated to cooling water to form condensed water, the condensed water in the steam chamber 3-i is collected in the condensed water chamber and then flows to the next steam chamber 3- (i +1), the condensed water in the last steam chamber 3-n flows to the low-pressure regenerative heater 7 after being pressurized by the condensed water pump 6, and exchanges heat with the steam in the low-pressure turbine stage group 1 in the low-pressure regenerative heater 7.
In a preferred embodiment of the present invention, the cold source 4 is a cooling tower or lake water or seawater.
In a preferred embodiment of the present invention, the multi-pressure condenser 3 is arranged longitudinally, each steam chamber of the multi-pressure condenser has a single flow path, and the condensed water between the steam chambers is connected in series.
In a preferred embodiment of the invention, the flow direction of the cooling water and the condensed water in the multi-pressure condenser 3 is from the steam chamber 3-i of the multi-pressure condenser to the next steam chamber 3- (i + 1).
As shown in fig. 2, the efficiency optimization method for the cold end system of the thermal power plant, which is provided by the invention, is a method for maximizing the generating power of the cold end system, and adopts a genetic algorithm to optimize the cold end system with multiple parameters by applying an entropy production minimization principle, and comprises the following steps:
step 1: obtaining the boundary condition of cold end system design, and obtaining the steam pressure, steam flow and steam enthalpy value of the low-pressure turbine stage group 1 at the inlet of the cold end system; obtaining the water supply pressure, water supply flow and water supply enthalpy value of a low-pressure regenerative heater 7 at the outlet of the cold end system, and the ambient temperature and pressure;
step 2: determining an optimized target, and selecting the optimized number of steam chambers;
and step 3: establishing a mathematical model of an optimization function, establishing an entropy production model of each component of the cold end system, and minimizing the total entropy production of the cold end system
Figure BDA0002968441260000091
As an objective function of cold end system optimization, a specific entropy production minimization model is established as follows:
total entropy production of cold end systems
Figure BDA0002968441260000092
The sum of the entropy products for each component:
Figure BDA0002968441260000093
in the formula:
Figure BDA0002968441260000094
is the entropy production of the low pressure turbine stage group, kW;
Figure BDA0002968441260000095
is the entropy production of the pipeline, kW;
Figure BDA0002968441260000096
is the entropy production of a multi-pressure condenser, kW;
Figure BDA0002968441260000097
is the entropy production of the circulating water pump, kW;
Figure BDA0002968441260000098
is the entropy production of the condensate pump, kW;
Figure BDA0002968441260000099
the entropy production of the low-pressure regenerative heater is kW;
1) the entropy yield of the low pressure turbine stage set is calculated by equation (2):
Figure BDA00029684412600000910
in the formula:
Figure BDA00029684412600000911
mass flow of the low-pressure turbine is kg/s; s1,outIs the entropy value of the fluid at the outlet of the low pressure turbine stage group, kJ/(kg. K); s1,inIs the entropy value of the fluid at the inlet of the low pressure turbine stage group, kJ/(kg. K);
the isentropic efficiency of each level of the low-pressure turbine in the cold end system is constant, so that the entropy of the low-pressure turbine part can be obtained by checking a water vapor enthalpy entropy table according to the pressure and enthalpy values of an inlet and an outlet:
the enthalpy value of the exhaust port of the low-pressure turbine stage group is calculated by the following formula:
h1,out＝h1,in-ηs(h1-h1s,out) (3)
in the formula: h is1,inAnd h1,outRespectively the enthalpy values of the steam inlet and the steam outlet of the low-pressure steam turbine stage group, kJ/kg; etasIsentropic efficiency,%; h is1s,outThe constant entropy enthalpy value of the outlet of the low-pressure turbine stage group is kJ/kg;
2) considering the pressure loss of the pipeline, a calculation model of the entropy production of the pipeline is calculated by the formula (5):
p2-i,out＝p2-i,in-Δp2-i (4)
Figure BDA0002968441260000101
Figure BDA0002968441260000102
in the formula:
Figure BDA0002968441260000103
mass flow in the pipeline, kg/s; p is a radical of2-i,inIs the pressure of the fluid at the inlet of the pipeline, MPa; p is a radical of2-i,inIs the pressure of the fluid at the outlet of the pipeline, MPa; Δ p is the pressure loss of the pipe, MPa; s2-i,outThe entropy value of the fluid at the outlet of the pipeline is obtained by checking a water vapor enthalpy entropy table according to the pressure and the enthalpy value at the outlet of the pipeline, and kJ/(kg.K); s2-i,inThe entropy value of the fluid at the pipeline inlet is obtained by checking a water vapor enthalpy entropy table according to the pressure and the enthalpy value of the pipeline inlet, and kJ/(kg.K) is obtained;
3) considering the pressure loss inside the multi-pressure condenser in the cold end system, the entropy production of the multi-pressure condenser is calculated by an equation (7), the entropy production of the multi-pressure condenser is the sum of the entropy production of n steam chambers in the multi-pressure condenser, wherein the entropy production of each steam chamber is calculated by an equation (8):
Figure BDA0002968441260000111
Figure BDA0002968441260000112
Figure BDA0002968441260000113
in the formula:
Figure BDA0002968441260000114
is the heat exchange capacity of each steam chamber in the condenser, kW;
Figure BDA0002968441260000115
is the mass flow of each steam chamber of the condenser
Figure BDA0002968441260000116
kg/s；h3-iChecking a water vapor enthalpy entropy table, namely kJ/kg for the enthalpy value of saturated water corresponding to the steam pressure in a steam chamber of a condenser; t is3-i,hotIs the steam saturation temperature, K, of each steam chamber in the condenser;
Figure BDA0002968441260000117
is the mass flow of cooling water, kg/s; c. CcwIs the specific heat capacity of the cooling water in the condenser, kJ/(kg. K); t is3-i,cw,inIs the inlet water temperature of the cooling water in each steam chamber in the condenser, K; t is3-i,cw,outThe outlet water temperature K of cooling water in each steam chamber in the condenser; lambda is the flow resistance coefficient on the cooling water side of the condenser; rhocwIs the density of cooling water in the steam chamber of the condenser in kg/m3；T3-i,cwIs the water temperature of the cooling water, K; a. the3-iIs the area of the steam chamber of the condenser, m2；d3-iThe inner diameter of a cooling water pipe in a steam chamber of the condenser is m; l is3-iThe length of a cooling water pipe in a steam chamber of the condenser is m;
4) the entropy production of the circulating water pump is calculated by equation (10):
Figure BDA0002968441260000118
in the formula: scw,outIs the entropy value of the fluid at the outlet of the circulating water pump, kJ/(kg.K); scw,inIs the entropy value of the fluid at the inlet of the circulating water pump, kJ/(kg. K);
5) the entropy yield of the condensate pump is calculated by equation (11):
Figure BDA0002968441260000119
in the formula:
Figure BDA00029684412600001110
mass flow of the condensate pump is kg/s; s6,outThe entropy value of the fluid at the outlet of the condensate pump is kJ/(kg.K); s6,inIs the entropy value of the fluid at the inlet of the condensate pump, kJ/(kg. K);
entropy values of inlets and outlets of the condensate pump and the circulating water pump are obtained by table lookup of pressures and enthalpy values of the inlets and outlets, an enthalpy value of an outlet of the pump is determined by a pump power equation,
Figure BDA0002968441260000121
in the formula:
Figure BDA0002968441260000122
is the input power of the pump, kW;
Figure BDA0002968441260000123
is the mass flow of the working medium in the pump, kg/s; delta PpumpIs the pressure change in the pump, kPa; rhopumpIs the density of the working medium in the pump, kg/m3；ηpumpIs the efficiency of the pump,%; h ispump,outIs the enthalpy value of the outlet of the pump, kJ/kg; h ispump,inIs the enthalpy at the pump inlet, kJ/kg.
6) The entropy production of the low-pressure regenerative heater is calculated by equation (13):
Figure BDA0002968441260000124
in the formula:
Figure BDA0002968441260000125
is the heat exchange capacity in the low-pressure regenerative heater, kW; t is7,hotIs the steam saturation temperature, K;
Figure BDA0002968441260000126
the mass flow of the feed water in the low-pressure regenerative heater is kg/s; c. C7,coldIs the specific heat capacity of the feed water in the low-pressure regenerative heater, kJ/(kg.K); t is7,cold,inIs the inlet water temperature of the feed water in the low-pressure regenerative heater, K; t is7,cold,outIs the outlet water temperature of the feed water in the low-pressure regenerative heater, K;
and 4, step 4: carrying out multi-parameter optimization, wherein the variable of the multi-parameter optimization is the steam quantity entering each steam chamber of the multi-pressure condenser
Figure BDA0002968441260000127
Area A of each steam chamber of the condenser3-1,A3-2,…,A3-nAnd the flow rate of the circulating water
Figure BDA0002968441260000128
The objective function of multi-parameter optimization is that the total entropy production of the cold end system is minimized, the multi-parameter optimization mode adopts a genetic algorithm, the feasible solutions which can be selected in the variable range are traversed, then the total entropy production of the cold end system is obtained, the total entropy production values of the cold end system of each solution are compared, the feasible solution corresponding to the minimum entropy production value is found, and the solution is the optimal efficiency of the cold end system of the thermal power plant.
In the genetic algorithm, the population scale is 150-250, the number of the previous generation individuals in each generation is 2-5, the cross probability is 0.6-0.8, and the iteration generation number is 150-300.
As shown in fig. 3, the boundary condition of the implementation of the present invention is that, under the condition that the unit parameters and the environmental parameters are constant, the amount of steam entering each steam chamber of the multi-pressure condenser is adjusted by considering the local change of the cold end system
Figure BDA0002968441260000131
Area A of each steam chamber of the condenser3-1,A3-2,…,A3-nAnd the flow rate of the circulating water
Figure BDA0002968441260000132
And performing multi-parameter optimization, wherein the change of the parameters can cause the change of the pressure of the condenser, so that the entropy of each component of the cold end system is obtained, and the optimization function of the method is the minimum of the total entropy of the cold end system.
As an example of the present invention, table 1 lists the main parameters and main environmental information of the coal-fired power plant in the example;
TABLE 1 Main parameters and Main environmental information of coal-fired Power plants
Figure BDA0002968441260000133
As shown in FIG. 4, the cold end entropy production of the reference working condition of the thermal power plant is 105.61kW/K, the cold end entropy production optimized by adopting a single-pressure condenser is 103.92kW/K, the cold end entropy production optimized by adopting a double-pressure condenser is 102.23kW/K, and the cold end entropy production optimized by adopting a four-pressure condenser is 101.45 kW/K. The research shows that: the cold end adopting the single-pressure condenser is optimized, so that the entropy production of the cold end is reduced by 1.68kW/K, and the efficiency is improved by 0.13%; for a cold end system adopting the double-pressure condenser, compared with the optimized cold end adopting the single-pressure condenser, the entropy production of the cold end is reduced by 1.69kW/K, and the efficiency is improved by 0.14% compared with the reference design working condition; for a cold end system adopting a four-pressure condenser, compared with an optimized cold end adopting a single-pressure condenser, the entropy production of the cold end is reduced by 2.47kW/K, and the efficiency is improved by 0.15% compared with the reference design working condition;
the invention adopts a genetic algorithm to carry out multi-parameter optimization on the condenser area, the steam inlet quantity and the circulating water quantity of the condenser, and combines the second law of thermodynamics to reduce the loss in the system, thereby improving the efficiency of the coal-fired power plant.

Claims (6)

1. A thermal power plant cold end system characterized by: the system is composed of a low-pressure turbine stage group (1), a low-pressure turbine exhaust pipeline (2), a multi-pressure condenser (3), a cold source (4), a circulating water pump (5), a condensate pump (6) and a low-pressure regenerative heater (7);
the low-pressure steam turbine stage group (1) is provided with n steam outlets, the multi-pressure condenser (3) consists of n steam chambers with different pressures, the number is 3-i, i is 1-n, the low-pressure steam turbine stage group (1) is provided with n steam outlets, the steam outlet of the low-pressure steam turbine stage group (1) is connected with the steam inlet of each steam chamber of the multi-pressure condenser (3) through a corresponding pipeline (2-i), the outlet of a condensed water chamber of the steam chamber 3-i in the multi-pressure condenser (3) is connected with the inlet of a condensed water chamber of the next steam chamber 3- (i +1), the outlet of a cooled water of the last steam chamber 3-n is connected with the inlet of a cooled water of a cold source (4), the outlet of the cooled water of the cold source (4) is connected with the inlet of the cooled water of the first steam chamber 3-1 through a circulating water pump (5), the outlet of the condensed water of the last steam chamber 3-n is connected with the inlet of a condensed water pump (6), a water supply outlet of the condensate pump (6) is connected with a water supply inlet of the low-pressure regenerative heater (7), and a steam outlet of the low-pressure turbine stage set (1) is connected with a steam inlet of the low-pressure regenerative heater (7);
cooling water is boosted by a circulating water pump (5) from a cold source (4) and then flows into a multi-pressure condenser (3), the cooling water absorbs heat in the multi-pressure condenser (3), the cooling water absorbs heat in a steam chamber 3-i, then flows into the next steam chamber 3- (i +1) to absorb heat, and then flows into the cold source (4) to release heat;
steam in each steam chamber in the multi-pressure condenser (3) is heated to cooling water to form condensed water, the condensed water in the steam chamber 3-i is collected in the condensed water chamber and then flows to the next steam chamber 3- (i +1), the condensed water in the last steam chamber 3-n is pressurized by the condensed water pump (6) and then flows to the low-pressure regenerative heater (7), and the condensed water and the steam in the low-pressure turbine stage group (1) exchange heat in the low-pressure regenerative heater (7).
2. A thermal power plant cold end system according to claim 1, wherein: the cold source (4) is a cooling tower or lake water or seawater.
3. A thermal power plant cold end system according to claim 1, wherein: the multi-pressure condenser (3) is longitudinally arranged, each steam chamber of the multi-pressure condenser is provided with a single flow path, and condensed water among the steam chambers is connected in series.
4. A thermal power plant cold end system according to claim 1, wherein: the flow direction of the cooling water and the condensed water in the multi-pressure condenser (3) is from the steam chamber 3-i of the multi-pressure condenser to the next steam chamber 3- (i + 1).
5. A method for optimizing the efficiency of a cold end system of a thermal power plant as claimed in claim 1, characterized in that: the method for maximizing the generating power of the cold end system utilizes the entropy production minimization principle and adopts a genetic algorithm to optimize the cold end system in multiple parameters, and comprises the following steps:
step 1: obtaining the boundary condition of cold end system design, and obtaining the steam pressure, the steam flow and the steam enthalpy value of the low-pressure turbine stage group (1) at the inlet of the cold end system; obtaining the water supply pressure, water supply flow, water supply enthalpy value and environmental temperature and pressure of a low-pressure regenerative heater (7) at the outlet of the cold end system;
step 2: determining an optimized target, and selecting the optimized number of steam chambers;
and step 3: establishing a mathematical model of an optimization function, establishing an entropy production model of each component of the cold end system, and minimizing the total entropy production of the cold end system
Figure FDA0002968441250000021
As an objective function of cold end system optimization, a specific entropy production minimization model is established as follows:
total entropy production of cold end systems
Figure FDA0002968441250000022
The sum of the entropy products for each component:
Figure FDA0002968441250000031
in the formula:
Figure FDA0002968441250000032
is the entropy production of the low pressure turbine stage group, kW;
Figure FDA0002968441250000033
is the entropy production of the pipeline, kW;
Figure FDA0002968441250000034
is the entropy production of a multi-pressure condenser, kW;
Figure FDA0002968441250000035
is the entropy production of the circulating water pump, kW;
Figure FDA0002968441250000036
is the entropy production of the condensate pump, kW;
Figure FDA0002968441250000037
the entropy production of the low-pressure regenerative heater is kW;
1) the entropy yield of the low pressure turbine stage set is calculated by equation (2):
Figure FDA0002968441250000038
in the formula:
Figure FDA0002968441250000039
mass flow of the low-pressure turbine is kg/s; s1,outIs the entropy value of the fluid at the outlet of the low pressure turbine stage group, kJ/(kg. K); s1,inIs the entropy value of the fluid at the inlet of the low pressure turbine stage group, kJ/(kg. K);
the isentropic efficiency of each level of the low-pressure turbine in the cold end system is constant, so that the entropy of the low-pressure turbine part can be obtained by checking a water vapor enthalpy entropy table according to the pressure and enthalpy values of an inlet and an outlet:
the enthalpy value of the exhaust port of the low-pressure turbine stage group is calculated by the following formula:
h1,out＝h1,in-ηs(h1-h1s,out) (3)
in the formula: h is1,inAnd h1,outRespectively the enthalpy values of the steam inlet and the steam outlet of the low-pressure steam turbine stage group, kJ/kg; etasIsentropic efficiency,%; h is1s,outThe constant entropy enthalpy value of the outlet of the low-pressure turbine stage group is kJ/kg;
2) considering the pressure loss of the pipeline, a calculation model of the entropy production of the pipeline is calculated by the formula (5):
p2-i,out＝p2-i,in-Δp2-i (4)
Figure FDA00029684412500000310
Figure FDA00029684412500000311
in the formula:
Figure FDA00029684412500000312
mass flow in the pipeline, kg/s; p is a radical of2-i,inIs the pressure of the fluid at the inlet of the pipeline, MPa; p is a radical of2-i,inIs the pressure of the fluid at the outlet of the pipeline, MPa; Δ p is the pressure loss of the pipe, MPa; s2-i,outThe entropy value of the fluid at the outlet of the pipeline is obtained by checking a water vapor enthalpy entropy table according to the pressure and the enthalpy value at the outlet of the pipeline, and kJ/(kg.K); s2-i,inThe entropy value of the fluid at the pipeline inlet is obtained by checking a water vapor enthalpy entropy table according to the pressure and the enthalpy value of the pipeline inlet, and kJ/(kg.K) is obtained;
3) considering the pressure loss inside the multi-pressure condenser in the cold end system, the entropy production of the multi-pressure condenser is calculated by an equation (7), the entropy production of the multi-pressure condenser is the sum of the entropy production of n steam chambers in the multi-pressure condenser, wherein the entropy production of each steam chamber is calculated by an equation (8):
Figure FDA0002968441250000041
Figure FDA0002968441250000042
Figure FDA0002968441250000043
in the formula:
Figure FDA0002968441250000044
is the heat exchange capacity of each steam chamber in the condenser, kW;
Figure FDA0002968441250000045
is the mass flow of each steam chamber of the condenser
Figure FDA0002968441250000046
kg/s；h3-iChecking a water vapor enthalpy entropy table, namely kJ/kg for the enthalpy value of saturated water corresponding to the steam pressure in a steam chamber of a condenser; t is3-i,hotIs the steam saturation temperature, K, of each steam chamber in the condenser;
Figure FDA0002968441250000047
is the mass flow of cooling water, kg/s; c. CcwIs the specific heat capacity of the cooling water in the condenser, kJ/(kg. K); t is3-i,cw,inIs the inlet water temperature of the cooling water in each steam chamber in the condenser, K; t is3-i,cw,outThe outlet water temperature K of cooling water in each steam chamber in the condenser; lambda is the flow resistance coefficient on the cooling water side of the condenser; rhocwIs the density of cooling water in the steam chamber of the condenser in kg/m3；T3-i,cwIs the water temperature of the cooling water, K; a. the3-iIs the area of the steam chamber of the condenser,m2；d3-ithe inner diameter of a cooling water pipe in a steam chamber of the condenser is m; l is3-iThe length of a cooling water pipe in a steam chamber of the condenser is m;
4) the entropy production of the circulating water pump is calculated by equation (10):
Figure FDA0002968441250000051
in the formula: scw,outIs the entropy value of the fluid at the outlet of the circulating water pump, kJ/(kg.K); scw,inIs the entropy value of the fluid at the inlet of the circulating water pump, kJ/(kg. K);
5) the entropy yield of the condensate pump is calculated by equation (11):
Figure FDA0002968441250000052
in the formula:
Figure FDA0002968441250000053
mass flow of the condensate pump is kg/s; s6,outThe entropy value of the fluid at the outlet of the condensate pump is kJ/(kg.K); s6,inIs the entropy value of the fluid at the inlet of the condensate pump, kJ/(kg. K);
entropy values of inlets and outlets of the condensate pump and the circulating water pump are obtained by table lookup of pressures and enthalpy values of the inlets and outlets, an enthalpy value of an outlet of the pump is determined by a pump power equation,
Figure FDA0002968441250000054
in the formula:
Figure FDA0002968441250000055
is the input power of the pump, kW;
Figure FDA0002968441250000056
is the mass of the working medium in the pumpFlow rate, kg/s; delta PpumpIs the pressure change in the pump, kPa; rhopumpIs the density of the working medium in the pump, kg/m3；ηpumpIs the efficiency of the pump,%; h ispump,outIs the enthalpy value of the outlet of the pump, kJ/kg; h ispump,inIs the enthalpy at the pump inlet, kJ/kg.
6) The entropy production of the low-pressure regenerative heater is calculated by equation (13):
Figure FDA0002968441250000057
in the formula:
Figure FDA0002968441250000058
is the heat exchange capacity in the low-pressure regenerative heater, kW; t is7,hotIs the steam saturation temperature, K;
Figure FDA0002968441250000059
the mass flow of the feed water in the low-pressure regenerative heater is kg/s; c. C7,coldIs the specific heat capacity of the feed water in the low-pressure regenerative heater, kJ/(kg.K); t is7,cold,inIs the inlet water temperature of the feed water in the low-pressure regenerative heater, K; t is7,cold,outIs the outlet water temperature of the feed water in the low-pressure regenerative heater, K;
and 4, step 4: carrying out multi-parameter optimization, wherein the variable of the multi-parameter optimization is the steam quantity entering each steam chamber of the multi-pressure condenser
Figure FDA0002968441250000061
Area A of each steam chamber of the condenser3-1,A3-2,…,A3-nAnd the flow rate of the circulating water
Figure FDA0002968441250000062
The objective function of multi-parameter optimization is that the total entropy production of the cold end system is minimized, the multi-parameter optimization mode adopts a genetic algorithm, alternative feasible solutions in a variable range are traversed, then the total entropy production of the cold end system is obtained, the total entropy production values of the cold end system of all the solutions are compared, and the minimum total entropy production value is foundThe entropy value of the power station is corresponding to a feasible solution, and the solution is the optimal efficiency of the cold end system of the thermal power plant.
6. The method of claim 5, wherein the method comprises the following steps: the population scale of the genetic algorithm is 150-250, the number of the individuals of the previous generation in each generation is 2-5, the cross probability is 0.6-0.8, and the iteration generation number is 150-300.
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