CN113701519B - Method for optimizing circulating water system under condenser separately arranged on main turbine and small turbine - Google Patents
Method for optimizing circulating water system under condenser separately arranged on main turbine and small turbine Download PDFInfo
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- CN113701519B CN113701519B CN202110936943.5A CN202110936943A CN113701519B CN 113701519 B CN113701519 B CN 113701519B CN 202110936943 A CN202110936943 A CN 202110936943A CN 113701519 B CN113701519 B CN 113701519B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B11/00—Controlling arrangements with features specially adapted for condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/04—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid
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Abstract
The invention discloses a method for optimizing a circulating water system under a condenser of a main turbine and a small turbine, which comprises the steps of adopting independent optimization of cold end equipment of the main turbine part, checking calculation of the small turbine part to determine individual parameters, setting a virtual condenser and comprehensive cooling multiplying power, matching a main turbine cooling tower with a shared cooling tower, optimizing other parameters of the small turbine condenser according to a hydraulic balance principle, and the like, and carrying out different combinations and hydraulic, thermodynamic and economic calculation and comparative analysis on the variable parameters of the cold end equipment of the main turbine and the small turbine, including the condenser area, the cooling tower area, the circulating water cooling multiplying power, the water supply and drainage pipe diameter, and the like, so as to obtain a most economical cold end configuration combination scheme which is matched with engineering conditions.
Description
Technical Field
The invention relates to a circulating water system optimization method under a condenser separately arranged on a main turbine and a small turbine, and belongs to the field of circulating water system design of thermal power plants.
Background
In the design process of a thermal power plant, the optimization of a cold end (a circulating water system) is an extremely important link: the cold end equipment mainly comprises a condenser area, a cooling tower area, a circulating water cooling multiplying power, a water supply and drainage pipe diameter and other variable parameters, and the most economical cold end configuration combination scheme which is matched with the engineering condition is obtained through hydraulic, thermal and economic calculation, comparison and analysis.
The optimization calculation of the circulating water system needs to compare various variable parameters through hydraulic, thermal and economic calculation in a multi-scheme manner, and the calculation process is complicated and is mainly completed through a calculation program of design software of the thermal power plant ("circulating water system optimization calculation program"). The optimization calculation program of the circulating water system adopted in the domestic power design industry is optimization software identified by the industry, and each unit is provided with 1 condenser as an optimization object: namely, a turbine (hereinafter referred to as a main turbine) and a turbine for driving a boiler feed pump (hereinafter referred to as a small turbine) share 1 condenser.
However, the prior art is not suitable for optimizing the circulating water system of the condenser separately arranged on the main turbine and the small turbine, the circulating water system of the condenser separately arranged on the main turbine and the small turbine in China is optimized, belongs to the technical blank, and in the practical operation of the main turbine and the small turbine, the design parameters caused by the specific thermodynamic data of the small turbine cannot be obtained in the initial setting stage, so that the design is inaccurate, and the circulating water system of the condenser separately arranged on the main turbine and the small turbine is optimized directly along the cold end configuration of the main turbine or is simply estimated by technicians, so that a cold end configuration combination scheme which is not matched with engineering conditions is obtained, serious construction waste and resource loss are caused, and a certain potential safety hazard is buried.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a method for optimizing a circulating water system under a condenser of which a main turbine and a small turbine are separately arranged, which can be used for optimizing the circulating water system under the condenser of which the main turbine and the small turbine are separately arranged.
In order to achieve the above purpose, the invention is realized by adopting the following technical scheme:
a method for optimizing a circulating water system under a condenser of a main turbine and a small turbine comprises the following steps:
acquiring engineering information, main turbine parameters and small turbine parameters;
according to the engineering information and the main turbine parameters, optimizing and calculating the cold end parameters of the main turbine with the minimum annual cost as a target to obtain a recommended main turbine cold end parameter combination scheme;
determining the condenser area and the cooling rate of the small turbine through checking calculation according to the recommended main turbine cold end parameter combination scheme and the small turbine parameters;
according to the recommended main turbine cold end parameter combination scheme, the condenser area and the cooling rate of the small turbine, the comprehensive cooling rate of the condenser for the main turbine and the small turbine is calculated;
according to the comprehensive cooling rate, a preferred cold end parameter combination of the condenser for the main turbine and the small turbine is obtained through a condenser optimization algorithm, and the configuration of the cooling tower for the main turbine and the small turbine is determined according to the preferred cold end parameter combination of the condenser for the main turbine and the small turbine;
according to the configuration of the cooling tower used by the main turbine and the small turbine, other parameters of the small turbine condenser are obtained through a small turbine condenser optimization algorithm, and the other parameters of the small turbine condenser comprise the back pressure type, the flow type, the cooling tube bundle type, the length and the design flow rate of the small turbine condenser.
Further, the engineering information includes: engineering profile, meteorological conditions, economic indicators; the main steam engine parameters comprise type, rated power, exhaust pressure, thermal data of different working conditions of the main steam engine and the relation between micro-power increase and back pressure of the main steam engine.
Further, according to the engineering information and the main turbine parameters, optimizing and calculating the cold end parameters of the main turbine with the aim of minimum annual cost, and the method for obtaining the recommended main turbine cold end parameter combination scheme comprises the following steps:
the method comprises the steps of performing sensitivity analysis on main steam turbine parameters, and independently optimizing a main steam turbine part by utilizing a steam turbine parameter optimization algorithm of thermal power plant design software to obtain a main steam turbine water supply system optimal calculation result;
the method comprises the steps of obtaining a recommended main steam turbine cold end parameter combination scheme by carrying out annual total cost sequencing on a main steam turbine water supply system optimization calculation result, wherein the recommended main steam turbine cold end parameter combination scheme comprises cold end parameters matched with a main steam turbine part; the cold end parameters matched with the main turbine part comprise: the area of the cooling tower matched with the main turbine part, the area of the condenser, the cooling rate and the water temperature of the cooling tower in each season.
Further, according to the recommended main turbine cold end parameter combination scheme and the small turbine parameters, the method for determining the condenser area and the cooling rate of the small turbine through checking calculation comprises the following steps:
taking the water temperature of the cooling tower in each season matched with the main steam turbine part as the input of a small steam turbine checking algorithm of design software of the thermal power plant to obtain parameters of a small steam turbine condenser;
taking the small turbine condenser parameters and the small turbine parameters as inputs of a condenser checking algorithm of design software of the thermal power plant to obtain the condenser area and cooling rate of the small turbine; the parameters of the small turbine comprise design back pressure of the small turbine, equipment arrangement and thermal data of different working conditions of the small turbine.
Further, the method for calculating the comprehensive cooling rate of the condenser for the main turbine and the small turbine according to the recommended main turbine cold end parameter combination scheme, the condenser area of the small turbine and the cooling rate comprises the following steps:
and taking the recommended main steam turbine cold end parameter combination scheme, the condenser area, the cooling rate and the design back pressure of the small steam turbine as inputs of a comprehensive cooling rate optimization algorithm of design software of the thermal power plant, and obtaining the comprehensive cooling rate of the condenser for the main steam turbine and the small steam turbine and the sum of the condensing capacities of the main steam turbine and the small steam turbine.
Further, according to the comprehensive cooling rate, the method for obtaining the preferable cold end parameter combination of the condenser for the main steam turbine and the small steam turbine through the condenser optimization algorithm comprises the following steps:
taking the sum of the comprehensive cooling rate and the condensing capacity of the main steam turbine and the small steam turbine as the input of a combined condenser optimization algorithm of design software of the thermal power plant to obtain a preferable cold end parameter combination of the combined condenser of the main steam turbine and the small steam turbine; the cold end parameter combination of the condenser for the main steam turbine and the small steam turbine comprises the cooling tower area, the water temperature of the outlet tower, the specification of the circulating water pipe ditch and the pipe diameter of the circulating water pipe of the condenser for the main steam turbine and the small steam turbine.
Further, the method for determining the configuration of the cooling tower for the main turbine and the small turbine according to the preferred combination of the cold end parameters of the condenser for the main turbine and the small turbine comprises the following steps: and searching a cold end configuration with basically equivalent water temperature and high fire proximity in the cold end parameter combination of the condenser for the main steam turbine and the small steam turbine according to the water temperature of the cooling tower in each season matched with the main steam turbine part, and determining the cold end configuration as the cooling tower configuration for the main steam turbine and the small steam turbine.
Compared with the prior art, the invention has the beneficial effects that:
1. the method comprises the steps of adopting the cold end equipment of the main turbine part to be optimized independently, adopting the small turbine part to be checked and calculated to determine individual parameters, setting comprehensive cooling multiplying power, matching a main turbine cooling tower with a shared cooling tower and the like, carrying out different combinations and hydraulic, thermal and economic calculation and comparative analysis on variable parameters such as condenser area, cooling tower area, circulating water cooling multiplying power, water supply and drainage pipe diameter and the like on the main turbine and the small turbine cold end equipment to obtain a most economical cold end configuration combination scheme which is consistent with engineering conditions, thereby optimizing the configuration of a circulating water system under the condenser of the main turbine and the small turbine, solving the problem of inaccurate design in the practical working main turbine and the small turbine shared design, making up the blank of the method for optimizing the design of the circulating water system for the main turbine and the small turbine in the prior art, and reducing the construction waste and resource loss of a thermal power station;
2. according to the invention, through solving a plurality of main steam turbine cold end parameter combination schemes, and through hydraulic, thermal and economic calculation and comparison analysis, a most economical cold end configuration combination scheme matched with engineering conditions is obtained, so that annual cost related to investment and operation cost of cold end equipment is minimized, and meanwhile, the maximum output of a steam turbine unit can be ensured, namely, under the condition of highest cooling water temperature, the back pressure of a steam turbine is ensured not to exceed the highest allowable value in full-load operation, and the safety of construction of a thermal power station is improved.
Drawings
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a main turbine backpressure-power curve for embodiment two.
Detailed Description
The invention is further described below with reference to the accompanying drawings. The following examples are only for more clearly illustrating the technical aspects of the present invention, and are not intended to limit the scope of the present invention.
Embodiment one:
the embodiment provides a method for optimizing a circulating water system under a condenser separately arranged on a main turbine and a small turbine, as shown in fig. 1, the method comprises the following steps:
acquiring engineering information, main turbine parameters and small turbine parameters;
according to the engineering information and the main turbine parameters, optimizing and calculating the cold end parameters of the main turbine with the minimum annual cost as a target to obtain a recommended main turbine cold end parameter combination scheme;
determining the condenser area and the cooling rate of the small turbine through checking calculation according to the recommended main turbine cold end parameter combination scheme and the small turbine parameters;
calculating the comprehensive cooling rate of the condenser for the main turbine and the small turbine according to the recommended main turbine cold end parameter combination scheme, the condenser area of the small turbine, the cooling rate and the design back pressure;
obtaining a preferred cold end parameter combination of the condenser for the main turbine and the small turbine through optimization calculation according to the comprehensive cooling multiplying power, and determining the configuration of a cooling tower for the main turbine and the small turbine according to the preferred cold end parameter combination of the condenser for the main turbine and the small turbine;
and obtaining other parameters of the condenser of the small turbine through optimization calculation according to the configuration of the cooling tower used by the main turbine and the small turbine.
Embodiment two:
the embodiment provides a circulating water system optimization method under a condenser of a main turbine and a small turbine. The calculation program (circulating water system optimization calculation program) of the design software of the thermal power plant on the market at least comprises a combined condenser optimization algorithm, a small turbine condenser optimization algorithm, a turbine parameter optimization algorithm, a small turbine checking algorithm and a comprehensive cooling rate optimization algorithm.
The general circulating water system optimization method comprises the following principles: the water supply system is used for supplying water to the condenser in the thermal power plant so as to achieve the purpose of condensing steam. From the turbine point of view, the water supply system corresponds to a cooling system. From the thermodynamic point of view, the condensing device and the water supply system function as a cold source. The condenser is used as a core, a low-pressure cylinder of the steam turbine is connected in the condenser, and a water supply system is connected outside the condenser, so that a 'cold end' of a thermodynamic system of the power station is formed.
The back pressure Pk of the condenser can be determined from its saturated steam temperature tc, which is calculated as follows:
tc＝t w1 +δt+Δt
wherein the circulated cooling water Wen Sheng t is related to enthalpy difference Δh of exhaust and condensed water, circulation cooling rate m, Δt=Δh/(4.1868 ·m), and heat transfer end difference δt=Δt/[ exp (KA/1163W) -1 ].
As can be seen from the above formula, the back pressure of the condenser and the inflow temperature t of the cooling water w1 It is also related to the circulating water W, i.e. the cooling rate m, and also to the condenser area A, the condenser tube material and the low pressure cylinder type. The above parameters together determine the cold end parameters of the turbine.
The method is a main way for improving the heat efficiency of the unit by improving the primary steam parameters and reducing the cold end steam parameters (exhaust temperature and exhaust pressure) of the steam turbine. When the primary parameters of the steam turbine are fixed, the cold end parameters of the steam turbine are reduced, so that the ideal steam enthalpy drop of the steam turbine can be increased, the cold source loss is reduced, and the heat efficiency of circulation is improved.
To obtain low-parameter steam parameters, the back pressure P of the condenser is reduced k Can be achieved by reducing the cooling tower outlet water temperature (cooling water inlet water temperature (t w1 ) Reducing temperature difference (circulation) between condenser and condenserWater temperature rise Δt) and condenser heat transfer end difference δt:
(1) By increasing the cooling tower area, the cooling tower outlet water temperature tw1 can be reduced. However, the area of the cooling tower is increased, and the water supply geometric height of the cooling tower is correspondingly increased, so that the power consumption of the circulating water pump is increased; at the same time, the area of the cooling tower is increased, which results in an increase in the cost of the cooling tower.
(2) Increasing the cooling rate m, i.e. increasing the amount of circulating water, reduces the temperature difference Δt, which however leads to an increase in the power consumption of the circulating water pump motor, the equipment costs, the circulating water pipe ditches and the building costs.
(3) The end difference can be reduced by increasing the heat exchange area of the condenser, but the manufacturing cost of the condenser is increased.
It can be seen from this that the design of the cold end parameters of the turbine is related to the design and selection of the condenser and the water supply system. The design and selection of any of the device and system parameters in the "cold end" cannot be done in isolation, apart from the design and selection of other factors. Reasonable parameters are the proper combination of parameters among the factors. The proper combination of the parameters is obtained only through the optimization design of a cold end (circulating water system).
The optimization calculation method adopts the annual cost minimum method recommended by the 'water engineering design Specification of thermal power plant'. The method combines two factors of investment and production cost, and calculates by combining time factors, namely, the capital investment of each scheme considers the complex factor, converts the investment into the equal repayment cost in the service life and the annual end, and combines the annual operation cost to form the annual cost of the scheme. The lowest annual cost of each solution is an economically desirable solution.
The objective function established at the minimum annual cost is as follows:
NF＝P·AFCR+AP-AT
wherein: NF is annual cost (ten thousand yuan), P is total investment present value (ten thousand yuan), AFCR is annual fixed cost rate (%), AP is annual circulating water pump electricity charge (ten thousand yuan), AT is annual slightly increased power income electricity charge (ten thousand yuan); the P.AFCR is the cost of equity reimbursement converted from the capital investment of a power plant water supply system to the end of the year in the economic service life, and can also be called annual fixed allocation cost, and the AP-AT is annual operation cost.
Sensitivity analysis is mainly to calculate some important but uncertain factors in a set variation range so as to study and analyze the degree of influence of the factors on a scheme. The economic indicators of sensitivity in the cold end optimization design mainly comprise the reduction coefficient of the electric charge price of the micro-increment force, the power generation cost (the price of fire coal) and the annual fixed allocation rate (the investment profit margin).
The embodiment provides a circulating water system optimization method under a condenser of a main turbine and a small turbine, which mainly comprises the steps of carrying out different combinations on a plurality of variable parameters of condenser area, cooling tower area, circulating water cooling multiplying power, water supply and drainage pipe diameter and the like on cold end equipment, and obtaining the most economical cold end configuration combination scheme which is matched with engineering conditions through hydraulic, thermal and economic calculation and comparative analysis. Under the combined scheme, the annual cost related to the investment and the operation cost of the cold end equipment can be minimized, and the maximum output of the turbine unit can be ensured, namely, the back pressure of the turbine is ensured not to exceed the maximum allowable value in the full-load operation under the condition of the highest cooling water temperature.
The following further describes the present embodiment with reference to engineering examples, and the specific steps are as follows:
step 1: acquiring engineering information, wherein the engineering information comprises: engineering profile, meteorological conditions, economic indexes, main turbine parameters and thermodynamic data of different working conditions of the small turbine.
Engineering profile: A2X 1000MW ultra-supercritical unit is newly built in a certain power plant, a main turbine and a small turbine in a main plant are respectively provided with condensers, wherein the small turbines are configured in a 2X 50% mode, each small turbine is independently provided with a condenser, and the maximum continuous power is not less than 20.1MW. The main building external circulation cooling water supply system consists of a natural ventilation cooling tower, a circulating water pump house, an inlet water return pipe trench and the like, and each machine unit is provided with an oversized natural ventilation cooling tower, and 1 circulating water inlet pipe and 1 circulating water return pipe are respectively arranged.
Meteorological conditions: the annual observation data of the gas station in the administrative district where the plant address is located are shown in Table 1.
Table 1 weather parameter list for each season
The wet bulb temperature of 10% in summer is 27.5 ℃, and the corresponding meteorological parameters are as follows: dry bulb temperature 30.8 ℃, relative humidity 79%, atmospheric pressure 1006.2hPa.
Economic index:
1. station service electricity fee: 0.26 yuan/degree (based on the coal price 780 yuan/ton)
2. Micro-increment of power price unit price: 0.221 yuan/degree (0.85 according to reduction coefficient)
3. Price per unit area of condenser: 600 yuan/m 2
4. The cost of the cooling tower is shown in Table 2.
Table 2 cost table for cooling tower
5. Economic service life of power plant: for 20 years
6. Fund recovery rate: 10.2% (calculated as 8% of investment recovery)
7. Annual maintenance cost rate: 2%
8. Annual fixed split rate: 12.20%
9. Number of hours of annual usage: 5500 hours
Main turbine parameters:
(1) Pattern: ultra-supercritical, secondary intermediate reheating double back pressure and condensing type;
(2) Rated power: 1000MW;
(3) Exhaust pressure: 4.8kPa;
(4) The thermodynamic data of different working conditions of the main turbine are shown in tables 2-3;
(5) The graph of the relation between the micro-power and the back pressure of the main turbine is shown in figure 2.
Table 3 thermal data list for different working conditions of main turbine
The main steam turbine condenser and the small steam turbine condenser are different in form, the main steam turbine condenser is generally double-back pressure and single-flow, the small steam turbine condenser is single-back pressure and double-flow, the tube bundles are different in specification and length, and 2 kinds of condensers cannot be regarded as 1 kind of condenser. Thermodynamic data of different working conditions of the small turbine:
the small steam turbines are configured according to 2X 50 percent, each small steam turbine is provided with a condenser independently, and the thermodynamic data of the small steam turbines under different working conditions are shown in Table 4.
Table 4 list of thermodynamic data for different working conditions of small turbine
Step 2: the main steam turbine part is independently optimized by performing sensitivity analysis on main steam turbine parameters and utilizing a circulating water system optimization calculation program to obtain a main steam turbine water supply system optimization calculation result; and the main steam turbine circulating water system design scheme comprises optimal cold end parameters such as cooling tower area, condenser area, cooling rate, cooling tower outlet water temperature of a cooling tower in each season and the like matched with the main steam turbine.
The results of the optimization calculation are shown in Table 5.
TABLE 5 ranking of preferred calculation results for main turbine water supply system
Through sensitivity analysis, the recommended main turbine cold end parameter combination scheme is as follows:
the cooling rate is 54 times, each unit is provided with 1 natural ventilation cooling tower with the water spraying area of 11500 square meters, and each unit is provided with 1 condenser with the water spraying area of 61000 square meters. The condenser is double back pressure and single flow, the cooling tube bundle adopts 304 stainless steel tubes D22×0.5, the length of the tube bundle is 13.4m, the design flow speed is 1.9m/s, and the head loss of the condenser is 7.5m. Under recommended conditions, the water temperature of the cooling tower at each season is shown in Table 3-2.
Table 5 main machine configured cooling tower outlet water temp. meter
| Area of cooling tower water spray | 11500m 2 |
| Summer 10% condition tower outlet water temperature (DEG C) | 31.50 |
| Water temperature (DEG C) of tower outlet in summer | 28.86 |
| Water temperature (DEG C) of tower outlet in spring and autumn | 20.62 |
| Winter outlet water temperature (DEG C) | 12.30 |
| Annual average tower outlet water temperature (DEG C) | 20.59 |
Step 3: the annual average out-of-tower water temperature of Table 5 was used to cool summerThe method comprises the steps of determining parameters of a condenser of a small turbine through checking calculation under the condition of the water temperature of a tower outlet at the condition of 10% in season, and determining the area of the condenser and the cooling water quantity of the small turbine through checking calculation by combining the design back pressure and equipment arrangement of the small turbine: the design cooling rate is 65 times, the design back pressure is 5.5kPa, and the area of the small turbine condenser is 2500m 2 。
Step 4: setting 1 virtual condenser (condenser for combining a main turbine and a small turbine), calculating the comprehensive cooling rate (virtual condenser cooling rate) to be 55 according to the recommended main turbine cold end parameter combination scheme and the small turbine condenser parameters, and calculating the result as shown in Table 6.
Table 6 cooling rate calculation table
| Project | Condensing capacity (t/h) | Enthalpy difference (kJ/kg) | Cooling rate | Cooling water quantity (m) 3 /h) |
| Main steam engine | 1412.75 | 2279.86 | 54 | 76288 |
| Small turbine (2 tables together) | 149.15 | 2370.20 | 65 | 9695 |
| Merging | 1561.90 | 2288.49 | 55 | 85983 |
Step 5: setting 1 virtual condenser by using a 'circulating water system optimization calculation program', wherein the condensing capacity discharged into the condenser is the sum of the condensing capacities of the main steam turbine and the small steam turbine, and the cooling rate adopts the comprehensive cooling rate, so that the optimal calculation result of the full water supply system is calculated and obtained, wherein the optimal calculation result comprises the optimal combination of cold end parameters of the condenser for the main steam turbine and the small steam turbine; the preferred combination of cold end parameters of the condenser for the main steam turbine and the small steam turbine comprises the area of a cooling tower, the water temperature of the outlet tower and the specification of a circulating water pipe ditch.
Table 7 shows the calculation results of the total water supply system optimization calculated by the "circulating water system optimization calculation program". The step simultaneously determines the optimal pipe diameter of the circulating water system: at this time, it can be seen that the optimal circulating water pipe diameter is DN3800 under the comprehensive cooling rate of 55 times.
TABLE 7 full Water supply System preference calculation results
Step 6: comparing recommended main steam turbine cold end parameter combination scheme (table 5), searching cooling tower configuration with basically equal or basically approximate water temperature in the optimal calculation result (table 7) of the full water supply system, namely, a scheme with the serial number 3, and determining the water spraying area 13000m of the cooling tower for the main steam turbine and the small steam turbine 2 。
Step 7: and optimizing other parameters of the small turbine condenser according to the hydraulic balance principle. Deducing parameters of the small turbine condenser under respective cooling water quantity according to the principle that the resistance of the pipe section of the main turbine condenser is equal to that of the small turbine condenser: the condenser is single back pressure and double flow, the cooling tube bundle adopts 304 stainless steel tubes D20×0.5, the tube bundle length is 7.7m, and the design flow speed is about 2m/s. According to the invention, the condensers are respectively arranged on the main steam turbine and the small steam turbine, the respective water inlet and outlet pipelines are arranged, and the resistance of each section is optimized according to the respective water quantity requirement so as to distribute the water quantity, so that the functional defect of uneven water distribution of the existing thermal power plant design software is overcome.
Step 8: summarizing: determining the configuration of the circulating water system according to the related conclusion of the steps: (1) the design cooling rate of the main turbine is 54 times, the design cooling rate of the small turbine is 65 times, and the comprehensive cooling rate is 55 times; (2) each unit is provided with 1 water spraying area of 13000m 2 Is a natural draft cooling tower; (3) the diameter of the circulating water supply and drainage pipe is DN3800; (4) each unit main steam engine is provided with 1 61000m 2 Condenser, each small turbine is configured with 1 2500m 2 A condenser. The main steam turbine condenser is double back pressure and single flow, the cooling tube bundle adopts 304 stainless steel tubes D22×0.5, the length of the tube bundle is 13.4m, and the design flow speed is about 1.9m/s; the small turbine condenser is of single back pressure and double flow, the cooling tube bundle adopts 304 stainless steel tubes D20×0.5, the tube bundle length is 7.7m, and the design flow speed is about 2m/s.
The optimization calculation process of the circulating water system of the thermal power plant at the current stage is complicated and is mainly completed through a calculation program. The 'circulating water system optimization calculation program' commonly adopted in the domestic power design industry cannot be directly used for optimizing and calculating the water supply system of the condenser respectively arranged on the large steam turbine and the small steam turbine. The invention adopts the steps of independent optimization of the cold end equipment of the main turbine part, checking calculation of the small turbine part to determine individual parameters, setting a virtual condenser and comprehensive cooling multiplying power, matching a main turbine cooling tower with a shared cooling tower, optimizing other parameters of the small turbine condenser according to a hydraulic balance principle, and the like, and carries out different combination and hydraulic, thermal and economic calculation and comparative analysis on the variable parameters of the main turbine and the small turbine cold end equipment, such as condenser area, cooling tower area, circulating water cooling multiplying power, water supply and drainage pipe diameter, and the like, so as to obtain the most economical cold end (circulating water system) configuration which is matched with engineering conditions.
The foregoing is merely a preferred embodiment of the present invention, and it should be noted that modifications and variations could be made by those skilled in the art without departing from the technical principles of the present invention, and such modifications and variations should also be regarded as being within the scope of the invention.
Claims (5)
1. The method for optimizing the circulating water system under the condenser of the main turbine and the small turbine is characterized by comprising the following steps of:
acquiring engineering information, main turbine parameters and small turbine parameters;
according to the engineering information and the main turbine parameters, optimizing and calculating the cold end parameters of the main turbine with the minimum annual cost as a target to obtain a recommended main turbine cold end parameter combination scheme;
determining the condenser area and the cooling rate of the small turbine through checking calculation according to the recommended main turbine cold end parameter combination scheme and the small turbine parameters;
according to the recommended main turbine cold end parameter combination scheme, the condenser area and the cooling rate of the small turbine, the comprehensive cooling rate of the virtual shared condenser of the main turbine and the small turbine is calculated;
obtaining a cold end parameter combination of a virtual shared condenser of the preferred main steam turbine and the small steam turbine through a shared condenser optimization algorithm according to the comprehensive cooling rate, and determining a cooling tower configuration for the main steam turbine and the small steam turbine according to the cold end parameter combination of the virtual shared condenser of the preferred main steam turbine and the small steam turbine;
according to the configuration of a cooling tower used by a main turbine and a small turbine, other parameters of the small turbine condenser are obtained through a small turbine condenser optimization algorithm, wherein the other parameters of the small turbine condenser comprise the back pressure type, the flow type, the cooling tube bundle type, the length and the design flow rate of the small turbine condenser;
according to the recommended main turbine cold end parameter combination scheme and the small turbine parameters, the method for determining the condenser area and the cooling rate of the small turbine through checking calculation comprises the following steps:
taking the water temperature of the cooling tower in each season matched with the main steam turbine part as the input of a small steam turbine checking algorithm of design software of the thermal power plant to obtain parameters of a small steam turbine condenser;
taking the small turbine condenser parameters and the small turbine parameters as inputs of a condenser checking algorithm of design software of the thermal power plant to obtain the condenser area and cooling rate of the small turbine;
the method for calculating the comprehensive cooling rate of the virtual shared condenser of the main turbine and the small turbine according to the recommended main turbine cold end parameter combination scheme, the condenser area of the small turbine and the cooling rate comprises the following steps:
taking the recommended main steam turbine cold end parameter combination scheme, the condenser area, the cooling rate and the design backpressure of the small steam turbine as inputs of a comprehensive cooling rate optimization algorithm of design software of the thermal power plant, and obtaining the comprehensive cooling rate of the virtual shared condenser of the main steam turbine and the small steam turbine and the sum of the condensing capacities of the main steam turbine and the small steam turbine;
according to the comprehensive cooling rate, the method for obtaining the cold end parameter combination of the virtual shared condenser of the preferred main turbine and the small turbine through the shared condenser optimization algorithm comprises the following steps:
taking the sum of the comprehensive cooling rate and the condensing capacity of the main steam turbine and the small steam turbine as the input of a shared condenser optimization algorithm of design software of the thermal power plant to obtain a preferable cold end parameter combination of a virtual shared condenser of the main steam turbine and the small steam turbine;
the method for determining the configuration of the cooling tower for the main turbine and the small turbine according to the preferred combination of the cold end parameters of the virtual combined condenser of the main turbine and the small turbine comprises the following steps: and searching the cold end configuration of which the water temperature is basically equivalent or close to that of the virtual combined condenser of the main steam turbine and the small steam turbine in the cold end parameter combination of the preferred virtual combined condenser according to the water temperature of the cooling tower in each season matched with the main steam turbine part, and determining the cold end configuration as the cooling tower configuration for the main steam turbine and the small steam turbine.
2. The method for optimizing a circulating water system of claim 1, wherein the engineering information includes: engineering profile, meteorological conditions, economic indicators; the main steam engine parameters comprise type, rated power, exhaust pressure, thermal data of different working conditions of the main steam engine and the relation between micro-power increase and back pressure of the main steam engine.
3. The optimization method of a circulating water system according to claim 1, wherein the method for optimizing and calculating the cold end parameters of the main turbine with the aim of minimizing annual cost according to the engineering information and the main turbine parameters to obtain the recommended main turbine cold end parameter combination scheme comprises the following steps:
the method comprises the steps of performing sensitivity analysis on main steam turbine parameters, and independently optimizing a main steam turbine part by utilizing a steam turbine parameter optimization algorithm of thermal power plant design software to obtain a main steam turbine water supply system optimal calculation result;
the method comprises the steps of obtaining a recommended main steam turbine cold end parameter combination scheme by carrying out annual total cost sequencing on a main steam turbine water supply system optimization calculation result, wherein the recommended main steam turbine cold end parameter combination scheme comprises cold end parameters matched with a main steam turbine part; the cold end parameters matched with the main turbine part comprise: the area of the cooling tower matched with the main turbine part, the area of the condenser, the cooling rate and the water temperature of the cooling tower in each season.
4. The method for optimizing a circulating water system according to claim 3, wherein the parameters of the small turbine include design back pressure of the small turbine, equipment arrangement and thermodynamic data of different working conditions of the small turbine.
5. The optimization method of a circulating water system according to claim 3, wherein the method for obtaining the preferred combination of cold end parameters of virtual shared condensers of the main turbine and the small turbine through the shared condenser optimization algorithm according to the comprehensive cooling rate comprises the following steps:
the cold end parameter combination of the virtual shared condenser of the main turbine and the small turbine comprises the cooling tower area, the water temperature of the outlet tower, the specification of the circulating water pipe ditch and the pipe diameter of the circulating water pipe of the virtual shared condenser of the main turbine and the small turbine.
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Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3935902A (en) * | 1971-10-25 | 1976-02-03 | Tyeploelektroprojekt | Condensation apparatus for steam turbine power plants |
| JPS63247592A (en) * | 1987-04-03 | 1988-10-14 | Hitachi Ltd | Condenser cooling water flow rate control system |
| CN102279565A (en) * | 2011-05-09 | 2011-12-14 | 浙江省电力试验研究院 | Optimized guidance system of cold end equipment of thermal generator set |
| CN102358633A (en) * | 2011-06-21 | 2012-02-22 | 中国神华能源股份有限公司 | Seawater desalination system used in water-electricity cogeneration and method for desalinating seawater |
| CN102705021A (en) * | 2012-05-25 | 2012-10-03 | 国电龙源电力技术工程有限责任公司 | Cold end optimizing and residual heat utilizing system for steam turbine |
| CN104317282A (en) * | 2014-11-21 | 2015-01-28 | 张伟 | Industrial cold end circulating water optimization and energy saving control system |
| CN104564190A (en) * | 2013-10-29 | 2015-04-29 | 烟台龙源电力技术股份有限公司 | Steam condenser |
| CN104749999A (en) * | 2015-03-20 | 2015-07-01 | 国电科学技术研究院 | Accurate guidance system for optimizing operation of turbo generator group cold end system of assembly wet-type cooling tower |
| CN105271549A (en) * | 2015-10-23 | 2016-01-27 | 内蒙古兰太实业股份有限公司 | System and method for comprehensive utilization of circuiting water resource of thermal power plant |
| CN105869063A (en) * | 2016-03-16 | 2016-08-17 | 国网江西省电力科学研究院 | Economical monitoring device and method for adjustment of operation modes of circulating water system of power station |
| CN209588749U (en) * | 2018-07-18 | 2019-11-05 | 中国能源建设集团江苏省电力设计院有限公司 | A kind of circulating water device matched with high position receipts water tower |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3154062B1 (en) * | 2012-03-26 | 2019-07-31 | Mitsubishi Heavy Industries, Ltd. | Plant operation assistance device and plant operation assistance method of a nuclear power plant |
-
2021
- 2021-08-16 CN CN202110936943.5A patent/CN113701519B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3935902A (en) * | 1971-10-25 | 1976-02-03 | Tyeploelektroprojekt | Condensation apparatus for steam turbine power plants |
| JPS63247592A (en) * | 1987-04-03 | 1988-10-14 | Hitachi Ltd | Condenser cooling water flow rate control system |
| CN102279565A (en) * | 2011-05-09 | 2011-12-14 | 浙江省电力试验研究院 | Optimized guidance system of cold end equipment of thermal generator set |
| CN102358633A (en) * | 2011-06-21 | 2012-02-22 | 中国神华能源股份有限公司 | Seawater desalination system used in water-electricity cogeneration and method for desalinating seawater |
| CN102705021A (en) * | 2012-05-25 | 2012-10-03 | 国电龙源电力技术工程有限责任公司 | Cold end optimizing and residual heat utilizing system for steam turbine |
| CN104564190A (en) * | 2013-10-29 | 2015-04-29 | 烟台龙源电力技术股份有限公司 | Steam condenser |
| CN104317282A (en) * | 2014-11-21 | 2015-01-28 | 张伟 | Industrial cold end circulating water optimization and energy saving control system |
| CN104749999A (en) * | 2015-03-20 | 2015-07-01 | 国电科学技术研究院 | Accurate guidance system for optimizing operation of turbo generator group cold end system of assembly wet-type cooling tower |
| CN105271549A (en) * | 2015-10-23 | 2016-01-27 | 内蒙古兰太实业股份有限公司 | System and method for comprehensive utilization of circuiting water resource of thermal power plant |
| CN105869063A (en) * | 2016-03-16 | 2016-08-17 | 国网江西省电力科学研究院 | Economical monitoring device and method for adjustment of operation modes of circulating water system of power station |
| CN209588749U (en) * | 2018-07-18 | 2019-11-05 | 中国能源建设集团江苏省电力设计院有限公司 | A kind of circulating water device matched with high position receipts water tower |
Non-Patent Citations (3)
| Title |
|---|
| 曾上将.华北电力大学专业硕士学位论文"火力发电机组冷端优化".2011,全文. * |
| 空冷机组汽动给水泵运行方式的探讨;司派友;伍小林;;华北电力技术(04);12-13 * |
| 给水泵焓升对机组经济性影响算法研究;李兵;王培红;;华东电力(09);177-179 * |
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