CN115495700A - Method and system for calculating heat loss of discharged working medium of boiler of supercritical thermal power generating unit - Google Patents

Method and system for calculating heat loss of discharged working medium of boiler of supercritical thermal power generating unit Download PDF

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CN115495700A
CN115495700A CN202211177419.5A CN202211177419A CN115495700A CN 115495700 A CN115495700 A CN 115495700A CN 202211177419 A CN202211177419 A CN 202211177419A CN 115495700 A CN115495700 A CN 115495700A
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pressure
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steam
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王彬
孟凡垟
王波
陈广伟
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Huadian Electric Power Research Institute Co Ltd
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
    • G06F17/10—Complex mathematical operations
    • G06F17/11—Complex mathematical operations for solving equations, e.g. nonlinear equations, general mathematical optimization problems
    • 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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B33/00—Steam-generation plants, e.g. comprising steam boilers of different types in mutual association
    • F22B33/18—Combinations of steam boilers with other apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
    • F22D1/50—Feed-water heaters, i.e. economisers or like preheaters incorporating thermal de-aeration of feed-water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays

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Abstract

The invention relates to a method and a system for calculating heat loss of an externally-discharged working medium of a boiler of a supercritical thermal power generating unit, wherein instrument and meter measurement is utilized to obtain superheater attemperation water flow, water supply flow and main steam flow are obtained through calculation, finally, the flow of the externally-discharged working medium of the boiler is obtained through calculation, the pressure of a steam-water separator is measured, an enthalpy map is checked to obtain a saturated water enthalpy value under corresponding pressure, and the heat carried by the externally-discharged working medium can be calculated by knowing the flow and enthalpy value of the externally-discharged working medium.

Description

Method and system for calculating heat loss of discharged working medium of boiler of supercritical thermal power generating unit
Technical Field
The invention relates to the technical field of supercritical thermal power generating units, in particular to a method and a system for calculating heat loss of an externally-discharged working medium of a boiler of a supercritical thermal power generating unit.
Background
The current situation of energy resources in China requires that a thermal power generating unit is transformed to a system regulation power supply for peak regulation and frequency modulation, the emergency peak regulation capacity of the existing thermal power generating unit is fully exerted, and in some regions, policies encourage the thermal power generating unit to have the capacity of continuous and stable operation under the working condition that the peak regulation is below 30%. However, under the working condition that the peak load is deeply regulated to a lower load, the economy of the supercritical thermal power generator set is reduced rapidly, and the energy consumption is increased rapidly. The reason for this is that the supercritical unit is switched from a once-through operation to a wet operation between 30% -25% tha of the unit load during the load shedding process. In the existing production of the supercritical unit, because the initial investment is large, most of the supercritical units are not provided with a boiler water circulating pump, when a boiler operates in a wet state, high-temperature and high-pressure working media separated by a steam-water separator enter a water storage tank and are then discharged outside, and the working media and heat loss is caused; the discharged working media are not measured, the temperature of the working media in the pipeline is high, the conventional ultrasonic flowmeter fails to accurately measure the discharged flow under the high-temperature state, so that the influence of the conventional ultrasonic flowmeter on the economy of the unit cannot be quantitatively analyzed, and the related data are used as supports for energy conservation and emission reduction.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a method and a system for calculating the heat loss of an externally-discharged working medium of a boiler of a supercritical thermal power generating unit.
In order to achieve the purpose, the invention adopts the following technical scheme:
a method for calculating heat loss of a boiler external discharge working medium of a supercritical thermal power generating unit comprises the following steps:
the unit comprises a steam turbine, a boiler and a deaerator, wherein the boiler is provided with an external discharge pipeline, a main steam pipeline is connected between the steam turbine and the boiler, and a water supply pipeline and a superheater temperature reduction water pipeline are connected between the deaerator and the boiler;
determining water inlet flow and water outlet flow by taking the boiler as a whole, wherein the water inlet flow comprises water supply flow F fw Flow rate F of desuperheated water of sum superheater gr The effluent flow rate includes a main steam flow rate F ms And the boiler external discharge flow F wp The inlet and outlet flow rates are balanced, i.e. F fw +F gr ＝F ms +F wp From the feed water flow F fw Superheater desuperheating Water flow F gr And main steam flow F ms Determining the discharge flow F outside the boiler wp ；
Step two, connecting a flow instrument on the superheater attemperation water pipeline to detect the flow F of the superheater attemperation water gr ；
Thirdly, connecting a plurality of high-pressure heaters to the water supply pipeline, taking the flow of the condensed water entering the deaerator as a calculation reference, calculating the steam inlet amount of the deaerator and each high-pressure heater through the heat balance and flow balance calculation of the deaerator and the high-pressure heaters, and calculating the steam inlet amount of the deaerator and each high-pressure heater due to the water supply flow F fw Solving the unknown heat balance and flow balance equations of the simultaneous high-pressure heater and deaerator, and calculating the water supply flow F fw ；
Fourthly, connecting a pressure measuring instrument on the main steam pipeline, detecting the pressure of the regulating stage of the steam turbine, and then calculating the new steam admission flow of the steam turbine, namely the main steam flow F ms ；
Step five, determining the discharge flow F outside the boiler according to the steps wp And determining an enthalpy value corresponding to the discharged working medium, wherein the heat carried by the discharged working medium, namely the discharged flow of the boiler, is multiplied by the corresponding enthalpy value.
Preferably, in the third step, the number of the high-pressure heaters is 3, a water supply pipe between the deaerator and the high-pressure heaters is provided with a water supply pump sealing water inlet, a water supply pump sealing water outlet and a reheater desuperheating water outlet, based on the above,
heat balance calculation equation for high pressure heater No. 1:
F fw (h f0 -h f1 )＝F 1 (h 1 -h d1 )
in the formula: f fw T/h is the water supply flow; h is f0 The water outlet enthalpy of the No. 1 high-pressure heater is kJ/kg; h is f1 The enthalpy of inlet water of the No. 1 high-pressure heater is kJ/kg; f 1 The steam inlet quantity of a No. 1 high-pressure heater is t/h; h is 1 The enthalpy of the inlet steam of the No. 1 high-pressure heater is kJ/kg; h is d1 The enthalpy is the hydrophobic enthalpy of a No. 1 high-pressure heater, kJ/kg;
heat balance calculation equation for high pressure heater No. 2:
F fw (h f1 -h f2 )＝F 2 (h 2 -h d2 )+F 1 (h d1 -h d2 )
in the formula: f 2 The steam inlet quantity of a No. 2 high-pressure heater is t/h; h is 2 Is the steam inlet enthalpy of the No. 2 high-pressure heater, kJ/kg; h is d2 The enthalpy is the hydrophobic enthalpy of a No. 2 high-pressure heater, kJ/kg; h is f2 The water inlet enthalpy of a No. 2 high-pressure heater is kJ/kg;
heat balance calculation equation for high pressure heater No. 3:
F fw (h f2 -h f3 )＝F 3 (h 3 -h d3 )+(F 1 +F 2 )(h d2 -h d3 )
in the formula: f 3 The steam inlet quantity of a No. 3 high-pressure heater is t/h; h is 3 The enthalpy of the inlet steam of the No. 3 high-pressure heater is kJ/kg; h is d3 The hydrophobic enthalpy of a No. 3 high-pressure heater is kJ/kg; h is f3 The water inlet enthalpy of a No. 3 high-pressure heater is kJ/kg;
the heat balance calculation equation of the deaerator is as follows:
F ot4 h ot4 ＝F 4 h 4 +F in h in4 +(F 1 +F 2 +F 3 )h d3 ；
in the formula: f ot4 The water outlet flow of the deaerator is t/h; h is ot4 The enthalpy of the effluent of the deaerator is kJ/kg; f 4 The steam inlet flow of the deaerator is t/h; h is a total of 4 Is the steam inlet enthalpy of the deaerator, kJ/kg; f in Measuring the obtained deaerator inlet condensate flow rate t/h; h is in4 Is the water inlet enthalpy of the deaerator, kJ/kg;
and (3) calculating the flow balance of the deaerator:
F ot4 ＝F 1 +F 2 +F 3 +F 4 +F in ；
feed water flow F fw The calculation equation of (c):
F fw ＝F ot4 +F mfin -F mfot -F gr -F zr ；
in the formula: f mfin Measuring the obtained sealing water inlet flow of the water feeding pump, t/h; f mfot Measuring the obtained flow of the sealing water outlet of the water feeding pump t/h; f gr Measuring the obtained superheater desuperheating water flow, t/h; f zr Measuring the obtained reheater reduced temperature water flow rate, t/h;
the five-element linear equation set is formed by the equation sets, an iteration method is adopted, firstly, an initial value of water supply flow is assumed, a corresponding water supply flow calculation value is obtained through calculation, the deviation of the initial value and the water supply flow calculation value is used for correcting the initial value, the calculation is substituted, the iteration is circulated until the assumed water supply flow and the calculated water supply flow deviation meet the precision requirement, and the accurate water supply flow F can be obtained fw 。
Preferably, in the fourth step, the main steam flow F ms Is calculated by the formula F ms ＝cP 1 + k, wherein: f ms The main steam flow is t/h; p 1 The measured pressure of the regulating stage of the steam turbine is MPa; c is a constant, thermal characteristic data provided by a manufacturer; k is a constant, the thermal property data provided by the manufacturer.
Preferably, in the fifth step, the boiler comprises a steam-water separator, the working medium discharged outside the boiler is saturated water separated by the steam-water separator, and the corresponding enthalpy value can be obtained by checking an enthalpy-entropy diagram according to the pressure of the steam-water separator;
discharge flow F outside boiler wp Is F wp ＝F fw +F gr -F ms ；
Boiler external discharge working medium heat loss Q wp Is Q wp ＝F wp h wp In the formula, h wp For boiler steam-water separator pressureCorresponding to saturated water enthalpy, kJ/kg.
In order to achieve the purpose, the invention also adopts the following technical scheme:
the calculation system for the heat loss of the externally-discharged working medium of the boiler of the supercritical thermal power generating unit comprises a data acquisition module and a calculation module, wherein the data acquisition module is used for acquiring data of the boiler and the deaerator, and the data comprises superheater attemperation water flow F gr The calculation module is used for respectively calculating the steam inlet flow, the steam inlet flow and the water supply flow F of each high-pressure heater based on the data acquired by the data acquisition module fw And main steam flow F ms And calculating the discharge flow F outside the boiler wp And then determining an enthalpy value corresponding to the externally-discharged working medium, and calculating the heat carried by the externally-discharged working medium.
Preferably, the data acquisition module comprises a first orifice plate flowmeter positioned in the superheater attemperation water pipeline, a first pressure measuring instrument positioned on the main steam pipeline and used for detecting the regulating stage pressure of the steam turbine, a first ultrasonic flowmeter arranged at a sealing water inlet of a water supply pump, a second ultrasonic flowmeter arranged at a sealing water outlet of the water supply pump, a second orifice plate flowmeter arranged at a desumperation water outlet of the reheater, a third orifice plate flowmeter used for measuring the flow rate of condensed water at an inlet of the deaerator, a second pressure measuring instrument used for measuring the pressure of the steam-water separator, a third pressure measuring instrument used for measuring the water outlet pressure of the No. 1 high-pressure heater, a fourth pressure measuring instrument used for measuring the water inlet pressure of the No. 1 high-pressure heater, and a fifth pressure measuring instrument used for measuring the steam inlet pressure of the No. 1 high-pressure heater, a sixth pressure measuring instrument for measuring the drainage pressure of the No. 1 high-pressure heater, a seventh pressure measuring instrument for measuring the outlet water pressure of the No. 2 high-pressure heater, an eighth pressure measuring instrument for measuring the inlet water pressure of the No. 2 high-pressure heater, a ninth pressure measuring instrument for measuring the inlet steam pressure of the No. 2 high-pressure heater, a tenth pressure measuring instrument for measuring the drainage pressure of the No. 2 high-pressure heater, an eleventh pressure measuring instrument for measuring the outlet water pressure of the No. 3 high-pressure heater, a twelfth pressure measuring instrument for measuring the inlet water pressure of the No. 3 high-pressure heater, a thirteenth pressure measuring instrument for measuring the inlet steam pressure of the No. 3 high-pressure heater, a fourteenth pressure measuring instrument for measuring the drainage pressure of the No. 3 high-pressure heater, a fifteenth pressure measuring instrument for measuring the outlet water pressure of the deaerator, and a sixteenth pressure measuring instrument for measuring the inlet water pressure of the deaerator, a seventeenth pressure measuring instrument for measuring the steam admission pressure of the deaerator, a first temperature measuring instrument for measuring the water outlet temperature of the high pressure heater No. 1, a second temperature measuring instrument for measuring the water inlet temperature of the high pressure heater No. 1, a third temperature measuring instrument for measuring the steam admission temperature of the high pressure heater No. 1, a fourth temperature measuring instrument for measuring the water discharge temperature of the high pressure heater No. 1, a fifth temperature measuring instrument for measuring the water outlet temperature of the high pressure heater No. 2, a sixth temperature measuring instrument for measuring the water inlet temperature of the high pressure heater No. 2, a seventh temperature measuring instrument for measuring the steam admission temperature of the high pressure heater No. 2, an eighth temperature measuring instrument for measuring the water discharge temperature of the high pressure heater No. 2, a ninth temperature measuring instrument for measuring the water outlet temperature of the high pressure heater No. 3, a tenth temperature measuring instrument for measuring the water inlet temperature of the high pressure heater No. 3, an eleventh temperature measuring instrument for measuring the steam admission temperature of the high pressure heater No. 3, a twelfth deaerator and a fifteenth temperature measuring instrument for measuring the water inlet temperature of the deaerator, a thirteenth temperature measuring instrument for measuring the water outlet temperature of the deaerator.
Compared with the prior art, the invention has the beneficial effects that:
according to the calculation method and the calculation system provided by the technical scheme, quantitative analysis is carried out on the boiler external discharge working medium of the supercritical thermal power generating unit in a wet-state operation state through measurement and calculation, the influence of the boiler external discharge working medium on the economy of the unit is determined, relevant data can be provided as supports to carry out energy conservation and emission reduction, the detection process is rigorous and standard, the obtained conclusion is reliable, and under the condition that the high-parameter and high-capacity supercritical thermal power generating unit frequently participates in peak regulation and frequency modulation, the method and the system are favorable for exploring the optimization space of the thermal power generating unit in peak regulation operation.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
Fig. 1 is a system frame diagram of a boiler, a deaerator and a connected feedwater system in a supercritical thermal power generating unit according to an embodiment of the present invention.
FIG. 2 is a typical main steam flow versus post-conditioning stage pressure characteristic.
Description of the reference numerals:
1. a boiler; 11. an outer discharge pipe; 12. a main steam line; 13. a steam-water separator; 14. a water storage tank; 2. a deaerator; 21. a water supply pipe; 22. a superheater desuperheating water pipeline; 23. a No. 3 high pressure heater; 24. a No. 2 high pressure heater; 25. number 1 high pressure heater; 26. the water inlet of the water feeding pump is sealed; 27. reheater desuperheating water outlet, 28, water pump sealing water outlet.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it is to be understood that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, belong to the protection scope of the present invention.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the prior art, during the load reduction process of the supercritical thermal power generating unit, the boiler is converted from a direct-current working condition to a wet state operation between the unit load of 30% -25% THA working condition. According to the existing supercritical thermal power generating unit, due to large initial investment, most of the existing supercritical thermal power generating units are not provided with a boiler water circulating pump, as shown in the attached drawing 1, when a boiler 1 operates in a wet state, saturated water separated by a steam-water separator 13 enters a water storage tank, 2 paths of outlets are arranged for draining water in the water storage tank 14, one path of water is discharged to a boiler drainage flash tank, and the other path of water is discharged to a condenser hot well. When the quality of the steam water of the boiler is unqualified and the steam water can not be recycled, the drain water is discharged to a drain flash tank of the boiler. When the quality of the steam and water is qualified, the steam and water is discharged to a hot well of the condenser when needing to be recovered. In order to ensure the safety of the unit, the water level of the water storage tank is controlled to be normal by 2 valves connected in parallel with 361. Saturated water separated by the boiler steam-water separator is finally discharged to a boiler drainage flash tank or a condenser hot well through a water storage tank, so that high-temperature and high-pressure working medium heat loss is caused. In the prior art, because a traditional orifice plate type flowmeter and a long-neck nozzle flowmeter are not generally installed in an outward discharge pipeline, and because the temperature of working media in the pipeline is high, the conventional ultrasonic flowmeter fails to accurately measure the outward discharge flow rate under a high-temperature state, the outward discharge working media are not measured, the heat loss caused by the partial outward discharge working media is subjected to no data statistics, and the influence of the partial outward discharge working media on the economy of a unit cannot be determined.
Based on this, as shown in fig. 1, an embodiment of the present invention provides a method for calculating heat loss of a boiler external discharge working medium of a supercritical thermal power generating unit, including the following steps:
the unit comprises a steam turbine (not shown), a boiler 1 and a deaerator 2, wherein the boiler 1 is provided with an outer discharge pipeline 11, a main steam pipeline 12 is connected between the steam turbine and the boiler 1, and a water supply pipeline 21 and a superheater desuperheating water pipeline 22 are connected between the deaerator 2 and the boiler;
determining water inlet flow and water outlet flow of the boiler as a whole, wherein the water inlet flow comprises water supply flow F fw Flow rate F of desuperheated water of sum superheater gr The effluent flow rate includes a main steam flow rate F ms And the boiler external discharge flow F wp The inlet and outlet flow rates being balanced, i.e. F fw +F gr ＝F ms +F wp From the feed water flow F fw Superheater desuperheating Water flow F gr And main steam flow F ms Determining the discharge flow F outside the boiler wp ；
Specifically, as known, the heat carried by the working medium, i.e., the flow rate of the working medium, is multiplied by the corresponding enthalpy value, in this embodiment, the external discharge working medium of the boiler is used as the saturated water separated by the steam-water separator 13, and the corresponding enthalpy value can be obtained by looking up an enthalpy-entropy diagram according to the pressure of the steam-water separator 13. Therefore, the key point of determining the heat carried by the boiler external discharge working medium lies in how to determine the flow rate of the boiler external discharge working medium, i.e. the boiler external discharge flow rate F wp . The boiler is considered as a whole, the feed water flow and the superheater desuperheating water flow are fed in, the main steam flow and the boiler external drainage flow are discharged, namely the boiler external drainage flow F can be obtained by knowing the feed water flow, the superheater desuperheating water flow and the main steam flow wp Therefore, the discharge flow F outside the boiler is obtained in the subsequent step wp 。
Step two, a flow instrument is connected to the superheater attemperation water pipeline 22 to detect the flow of the superheater attemperation waterF gr (ii) a Because the temperature of the superheater desuperheating water is not high, a flow instrument can be directly arranged in the superheater desuperheating water pipeline 22, and the flow instrument is specifically a first orifice flowmeter and is used for detecting the flow F of the superheater desuperheating water gr And then transmits the detected data to the calculation module.
Thirdly, connecting a plurality of high-pressure heaters to the water supply pipeline 21, calculating the steam inlet amount of the deaerator 2 and each high-pressure heater by taking the flow of the condensate entering the deaerator 2 as a calculation reference and calculating the heat balance and the flow balance of the deaerator 2 and the high-pressure heaters, wherein the water supply flow F is fw Solving the unknown heat balance and flow balance equation set of the simultaneous high-pressure heater and the deaerator 2, and calculating the water supply flow F fw 。
Specifically, as shown in fig. 1, the number of the high-pressure heaters in this embodiment is 3, a water supply pipe 21 between the deaerator 2 and the high-pressure heaters is provided with a water supply pump seal water inlet 26, a water supply pump seal water outlet 28, and a reheater desuperheating water outlet 27, and the steam intake amounts of the deaerator 2 and the high-pressure heaters are obtained by taking the flow rate of the condensate entering the deaerator 2 as a calculation reference and by calculating the thermal balance and the flow balance of the deaerator 2 and the high-pressure heater system. Because the water supply flow is unknown, the heat balance and flow balance equation set of the simultaneous heater and the deaerator 2 is solved, specifically, the heat balance calculation equation of the No. 1 high-pressure heater 25:
F fw (h f0 -h f1 )＝F 1 (h 1 -h d1 )
in the formula: f fw T/h is the water supply flow; h is f0 The enthalpy of the effluent of the No. 1 high-pressure heater 25 is kJ/kg; h is f1 The enthalpy of inflow of the No. 1 high-pressure heater 25 is kJ/kg; f 1 The steam inlet quantity of the No. 1 high-pressure heater 25 is t/h; h is 1 Is the steam inlet enthalpy of the No. 1 high-pressure heater 25, kJ/kg; h is d1 The enthalpy of drainage of the No. 1 high-pressure heater 25 is kJ/kg, and the parameters are obtained by measurement; specifically, the water outlet enthalpy, the water inlet enthalpy, the steam inlet enthalpy and the water drainage enthalpy of the No. 1 high-pressure heater 25 can be obtained from the temperature and the pressure of the working medium at each position, and the pressure and the temperature of the working medium at each position are respectively used for measuring the No. 1 high-pressure heatingThe third pressure measuring instrument for measuring the water outlet pressure of the device 25, the first temperature measuring instrument for measuring the water outlet temperature of the No. 1 high-pressure heater 25, the fourth pressure measuring instrument for measuring the water inlet pressure of the No. 1 high-pressure heater 25, the second temperature measuring instrument for measuring the water inlet temperature of the No. 1 high-pressure heater 25, the fifth pressure measuring instrument for measuring the steam inlet pressure of the No. 1 high-pressure heater 25, the third temperature measuring instrument for measuring the steam inlet temperature of the No. 1 high-pressure heater 25, the sixth pressure measuring instrument for measuring the water drainage pressure of the No. 1 high-pressure heater 25, the fourth temperature measuring instrument for measuring the water drainage temperature of the No. 1 high-pressure heater 25 and other measuring instruments are used for measuring, and then the calculation module correspondingly calculates or inquires an enthalpy entropy diagram to obtain the water outlet enthalpy, the water inlet enthalpy, the steam inlet enthalpy and the water drainage enthalpy of the No. 1 high-pressure heater 25.
Heat balance calculation equation for high pressure heater No. 2 24:
F fw (h f1 -h f2 )＝F 2 (h 2 -h d2 )+F 1 (h d1 -h d2 )
in the formula: f 2 The steam inlet quantity of a No. 2 high-pressure heater 24 is t/h; h is 2 Is the steam inlet enthalpy of the No. 2 high-pressure heater 24, kJ/kg; h is d2 Hydrophobic enthalpy, kJ/kg, for No. 2 high pressure heater 24; h is f2 The water inlet enthalpy of the No. 2 high-pressure heater 24 is kJ/kg, and the parameters are obtained by measurement; specifically, the water outlet enthalpy, the water inlet enthalpy, the steam inlet enthalpy and the water drainage enthalpy of the No. 2 high-pressure heater 24 can be obtained from the temperature and the pressure of the working medium at each position, and the pressure and the temperature of the working medium at each position are respectively obtained by a seventh pressure measuring instrument for measuring the water outlet pressure of the No. 2 high-pressure heater 24, a fifth temperature measuring instrument for measuring the water outlet temperature of the No. 2 high-pressure heater 24, an eighth pressure measuring instrument for measuring the water inlet pressure of the No. 2 high-pressure heater 24, a sixth temperature measuring instrument for measuring the water inlet temperature of the No. 2 high-pressure heater 24, a ninth pressure measuring instrument for measuring the steam inlet pressure of the No. 2 high-pressure heater 24, a seventh temperature measuring instrument for measuring the steam inlet temperature of the No. 2 high-pressure heater 24, and a hydrophobic pressure measuring instrument for the No. 2 high-pressure heater 24The tenth pressure measuring instrument is used for measuring the drainage temperature of the No. 2 high-pressure heater 24, and is measured by measuring instruments such as an eighth temperature measuring instrument and the like, and then the computing module correspondingly computes or queries an enthalpy entropy diagram to obtain the water outlet enthalpy, the water inlet enthalpy, the steam inlet enthalpy and the drainage enthalpy of the No. 2 high-pressure heater 24, and the measuring point positions, the measuring methods and the corresponding computing methods of all the measuring instruments are in the prior art.
Heat balance calculation equation for high pressure heater No. 3, 23:
F fw (h f2 -h f3 )＝F 3 (h 3 -h d3 )+(F 1 +F 2 )(h d2 -h d3 )
in the formula: f 3 The steam inlet quantity of a No. 3 high-pressure heater 23 is t/h; h is 3 Is the steam inlet enthalpy of the No. 3 high-pressure heater 23, kJ/kg; h is a total of d3 Hydrophobic enthalpy, kJ/kg, for No. 3 high pressure heater 23; h is a total of f3 The water inlet enthalpy of the No. 3 high-pressure heater 23 is kJ/kg, and the parameters are obtained by measurement; specifically, the water outlet enthalpy, the water inlet enthalpy, the steam inlet enthalpy and the water drainage enthalpy of the No. 3 high-pressure heater 23 can be obtained from the temperature and the pressure of the working medium at each position, the pressure and the temperature of the working medium at each position are respectively measured by an eleventh pressure measuring instrument for measuring the water outlet pressure of the No. 3 high-pressure heater 23, a ninth temperature measuring instrument for measuring the water outlet temperature of the No. 3 high-pressure heater 23, a twelfth pressure measuring instrument for measuring the water inlet pressure of the No. 3 high-pressure heater 23, a thirteenth pressure measuring instrument for measuring the steam inlet pressure of the No. 3 high-pressure heater 23, an eleventh temperature measuring instrument for measuring the steam inlet temperature of the No. 3 high-pressure heater 23, a fourteenth pressure measuring instrument for measuring the water drainage pressure of the No. 3 high-pressure heater 23, a twelfth temperature measuring instrument for measuring the water drainage temperature of the No. 3 high-pressure heater 23, and other measuring instruments, and the like, and a calculation module correspondingly calculates or inquires an entropy diagram to obtain the water outlet enthalpy, the water inlet enthalpy, the steam enthalpy and the water drainage enthalpy of the No. 3 high-pressure heater 23, and the measurement methods and the corresponding calculation method for calculating the position of the existing technical method.
Heat balance calculation equation of deaerator 2:
F ot4 h ot4 ＝F 4 h 4 +F in h in4 +(F 1 +F 2 +F 3 )h d3 ；
in the formula: f ot4 The water outlet flow of the deaerator 2 is t/h; f in For measuring the obtained condensate flow at the inlet of the deaerator 2, the condensate inlet of the deaerator 2 is provided with a third orifice flowmeter for measuring the condensate flow at the inlet of the deaerator 2, from which F is obtained in ，F 4 The steam inlet flow of the deaerator 2 is t/h;
h ot4 is the effluent enthalpy of the deaerator 2, kJ/kg; h is in4 Is the inlet water enthalpy of the deaerator 2, kJ/kg; h is a total of 4 Is the steam inlet enthalpy of the deaerator 2, kJ/kg; all the parameters are obtained by measurement; specifically, the water outlet enthalpy, the water inlet enthalpy and the steam inlet enthalpy of the deaerator 2 can be obtained from the temperature and the pressure of the working medium at each position, the pressure and the temperature of the working medium at each position are respectively measured by a fifteenth pressure measuring instrument for measuring the water outlet pressure of the deaerator 2, a thirteenth temperature measuring instrument for measuring the water outlet temperature of the deaerator 2, a sixteenth pressure measuring instrument for measuring the water inlet pressure of the deaerator 2, a fourteenth temperature measuring instrument for measuring the water inlet temperature of the deaerator 2, a seventeenth pressure measuring instrument for measuring the steam inlet pressure of the deaerator 2, a fifteenth temperature measuring instrument for measuring the steam inlet temperature of the deaerator 2 and other measuring instruments, and then the water outlet enthalpy, the water inlet enthalpy and the steam inlet enthalpy of the deaerator 2 are obtained by correspondingly calculating or inquiring an enthalpy-entropy diagram by a calculating module, and the measuring point positions, the measuring methods and the corresponding calculating methods of the measuring instruments are the prior art.
And (3) calculating the working medium balance of the deaerator 2:
F ot4 ＝F 1 +F 2 +F 3 +F 4 +F in ；
feed water flow F fw The calculation equation of (a):
F fw ＝F ot4 +F mfin -F mfot -F gr -F zr ；
in the formula: f mfin The flow rate of the sealing water inlet of the water feeding pump is measured, t/h,specifically, the measurement is obtained through a first ultrasonic flowmeter arranged at a sealing water inlet 26 of the water feeding pump; f mfot The t/h is the flow of the sealing water outlet of the water feeding pump obtained by measurement, and is measured by a second ultrasonic flowmeter arranged at the sealing water outlet 28 of the water feeding pump; f gr The measured superheater desuperheating water flow rate, t/h, is measured by a first orifice flowmeter located in the superheater desuperheating water pipeline 22; f zr The measured reheater desuperheating water flow rate, t/h, is measured by a second orifice flowmeter disposed at the reheater desuperheating water outlet 27;
the equation set forms a five-element linear equation set, 5 unknowns are provided, namely the steam inlet quantity of a No. 1 high-pressure heater 25, the steam inlet quantity of a No. 2 high-pressure heater 24, the steam inlet quantity of a No. 3 high-pressure heater 23, the steam inlet flow and the water supply flow of a deaerator 2, an iteration method is adopted, firstly, an initial value of the water supply flow is assumed, a corresponding water supply flow calculation value is obtained through calculation, the initial value is corrected through the deviation of the two values, calculation is substituted, and iteration is carried out in a circulating mode until the assumed water supply flow and the calculated water supply flow deviation meet the precision requirement, so that the accurate water supply flow F can be obtained fw . The iterative method adopted by the embodiment is an existing algorithm, and is not described herein.
Step four, connecting a pressure measuring instrument on the main steam pipeline 12, detecting the pressure of the adjusting stage of the steam turbine, and then calculating the new steam admission flow of the steam turbine, namely the main steam flow F ms In particular, the main steam flow F ms Is calculated by the formula F ms ＝cP 1 + k, wherein: f ms The main steam flow is t/h; p is 1 The measured pressure, MPa, of the regulating stage of the steam turbine is measured by a first pressure measuring instrument, which is located on the main steam pipe 12 and is used for detecting the pressure of the regulating stage of the steam turbine; c is a constant, thermal property data provided by a manufacturer; k is a constant, and all the thermal characteristic data provided by manufacturers are known parameters. Fig. 2 shows a typical main steam flow versus post-conditioning pressure characteristic.
Step five, the instrument is obtained through the stepsThe flow F of the water reduced from the superheater is obtained by the measurement of the instrument and meter gr Calculating the water supply flow F wp And main steam flow F ms Thereby determining the discharge flow F outside the boiler wp And determining an enthalpy value corresponding to the discharged working medium, wherein the heat carried by the discharged working medium, namely the discharged flow of the boiler, is multiplied by the corresponding enthalpy value. Specifically, the boiler comprises a steam-water separator 13, the working medium discharged outside the boiler is used as saturated water separated by the steam-water separator 13, the corresponding enthalpy value can be obtained by checking an enthalpy-entropy diagram according to the pressure of the steam-water separator 13, and the pressure of the steam-water separator 13 can be obtained by a pressure measuring device; therefore, the discharge flow F outside the boiler wp Is of the formula F wp ＝F fw +F gr -F ms (ii) a Boiler external discharge working medium heat loss Q wp Is of the formula Q wp ＝F wp h wp In the formula, h wp The saturated water enthalpy corresponding to the pressure of the boiler steam-water separator 13 is kJ/kg, the flow rate and the corresponding enthalpy value of the boiler discharged working medium are determined through the steps, the heat of the boiler discharged working medium can be calculated, the heat loss corresponding to the unit is determined, and the heat loss taken away by the boiler discharged working medium after the peak regulation of the supercritical thermal power generating unit is operated to a dehumidification state is accurately calculated. Under the current situation that a high-parameter high-capacity supercritical unit frequently participates in peak shaving frequency modulation, the optimization space of the thermal power generating unit under peak shaving operation is explored, and data support is provided for follow-up related energy-saving and consumption-reducing work.
The embodiment also provides a calculation system for heat loss of the externally-discharged working medium of the boiler of the supercritical thermal power generating unit, which comprises a data acquisition module and a calculation module, wherein the data acquisition module is used for acquiring data of the boiler and the deaerator 2, and the data comprises superheater desuperheating water flow F gr The steam turbine comprises a regulating stage pressure of the steam turbine, a pressure of a steam-water separator 13, a water outlet pressure temperature, a water inlet pressure temperature, a steam inlet pressure temperature and a drainage pressure temperature of each high-pressure heater, a water outlet pressure temperature, a water inlet pressure temperature, a steam inlet pressure temperature and an inlet condensate flow of a deaerator 2, a flow of a sealing water inlet 26 of a water feed pump, a flow of a sealing water outlet 28 of the water feed pump and a flow of reheater desuperheating water 27, and specifically, the data acquisition module comprises a first pore plate flow positioned in a superheater desuperheating water pipelineThe measuring device comprises a meter, a first pressure measuring instrument, a first ultrasonic flowmeter, a second orifice plate flowmeter, a third orifice plate flowmeter, a second pressure measuring instrument, a third pressure measuring instrument, a fourth pressure measuring instrument, a fifth pressure measuring instrument, a sixth pressure measuring instrument and a seventh pressure measuring instrument, wherein the first pressure measuring instrument is positioned on a main steam pipeline and used for detecting the pressure of a regulating stage of a steam turbine, the first ultrasonic flowmeter is arranged at a sealing water inlet of a feed water pump, the second ultrasonic flowmeter is arranged at a sealing water outlet of the feed water pump, the second orifice plate flowmeter is arranged at a desuperheater temperature-reducing water outlet of a reheater, the third orifice plate flowmeter is used for measuring the flow of condensed water at an inlet of the deaerator, the second pressure measuring instrument is used for measuring the pressure of a steam-water separator, the third pressure measuring instrument is used for measuring the water outlet pressure of a No. 1 high-pressure heater, the fourth pressure measuring instrument is used for measuring the water inlet pressure of a No. 1 high-pressure heater, the fifth pressure measuring instrument is used for measuring the water outlet pressure of a No. 2 high-pressure heater, an eighth pressure measuring instrument for measuring the water inlet pressure of the No. 2 high-pressure heater, a ninth pressure measuring instrument for measuring the steam inlet pressure of the No. 2 high-pressure heater, a tenth pressure measuring instrument for measuring the water drainage pressure of the No. 2 high-pressure heater, an eleventh pressure measuring instrument for measuring the water outlet pressure of the No. 3 high-pressure heater, a twelfth pressure measuring instrument for measuring the water inlet pressure of the No. 3 high-pressure heater, a thirteenth pressure measuring instrument for measuring the steam inlet pressure of the No. 3 high-pressure heater, a fourteenth pressure measuring instrument for measuring the water drainage pressure of the No. 3 high-pressure heater, a fifteenth pressure measuring instrument for measuring the water outlet pressure of the deaerator, a sixteenth pressure measuring instrument for measuring the water inlet pressure of the deaerator, a seventeenth pressure measuring instrument for measuring the steam inlet pressure of the deaerator, and a first temperature measuring instrument for measuring the water outlet temperature of the No. 1 high-pressure heater, a second temperature measuring instrument for measuring the water inlet temperature of the No. 1 high-pressure heater, a third temperature measuring instrument for measuring the steam inlet temperature of the No. 1 high-pressure heater, a fourth temperature measuring instrument for measuring the water outlet temperature of the No. 1 high-pressure heater, a fifth temperature measuring instrument for measuring the water outlet temperature of the No. 2 high-pressure heater, a sixth temperature measuring instrument for measuring the water inlet temperature of the No. 2 high-pressure heater, a seventh temperature measuring instrument for measuring the steam inlet temperature of the No. 2 high-pressure heater, and a fourth temperature measuring instrument for measuring the water outlet temperature of the No. 2 high-pressure heaterThe system comprises eight temperature measuring instruments, a ninth temperature measuring instrument for measuring the water outlet temperature of a No. 3 high-pressure heater, a tenth temperature measuring instrument for measuring the water inlet temperature of the No. 3 high-pressure heater, an eleventh temperature measuring instrument for measuring the steam inlet temperature of the No. 3 high-pressure heater, a twelfth temperature measuring instrument for measuring the water drainage temperature of the No. 3 high-pressure heater, a thirteenth temperature measuring instrument for measuring the water outlet temperature of a deaerator, a fourteenth temperature measuring instrument for measuring the water inlet temperature of the deaerator and a fifteenth temperature measuring instrument for measuring the steam inlet temperature of the deaerator. The measuring instruments are not shown in the drawings, but the measuring positions and measuring methods of the measuring instruments are prior art and are not described herein again.
The data acquisition module is in communication connection with the calculation module for data transmission, and the calculation module is used for respectively calculating the water supply flow F based on the data acquired by the data acquisition module fw And main steam flow F ms And calculating the discharge flow F outside the boiler wp And then calculating the heat carried by the discharged working medium, wherein the calculation module adopts the calculation method of the embodiment.
Specifically, the computing system of the invention comprises a processor and a memory, the memory is used for storing a program code and transmitting the program code to the processor, and the computing module is located on the processor and used for executing the method for computing the heat loss of the boiler external discharge working medium of the supercritical thermal power generating unit according to the instructions in the program code.
The above embodiments are only preferred embodiments of the present invention, and the protection scope of the present invention is not limited thereby, and any insubstantial changes and substitutions made by those skilled in the art based on the present invention are within the protection scope of the present invention.

Claims (6)

1. A method for calculating heat loss of an externally-discharged working medium of a boiler of a supercritical thermal power generating unit is characterized by comprising the following steps of:
the unit comprises a steam turbine, a boiler and a deaerator, wherein the boiler is provided with an external discharge pipeline, a main steam pipeline is connected between the steam turbine and the boiler, and a water supply pipeline and a superheater temperature reduction water pipeline are connected between the deaerator and the boiler;
determining water inlet flow and water outlet flow of the boiler as a whole, wherein the water inlet flow comprises water supply flow F fw Flow F of reduced temperature water for the overtemperor gr The effluent flow rate includes a main steam flow rate F ms And the boiler external discharge flow F wp The inlet and outlet flow rates are balanced, i.e. F fw +F gr ＝F ms +F wp From the feed water flow F fw Superheater desuperheating water flow F gr And main steam flow F ms Determining the discharge flow F outside the boiler wp ；
Step two, connecting a flow instrument on the superheater attemperation water pipeline to detect the flow F of the superheater attemperation water gr ；
Thirdly, connecting a plurality of high-pressure heaters to the water supply pipeline, taking the flow of the condensate entering the deaerator as a calculation reference, calculating the steam inlet quantity of the deaerator and each high-pressure heater through the heat balance and flow balance calculation of the deaerator and the high-pressure heaters, and solving the steam inlet quantity of the deaerator and each high-pressure heater due to the water supply flow F fw Solving the unknown heat balance and flow balance equation set of the simultaneous high-pressure heater and the deaerator, and calculating the water supply flow F fw ；
Fourthly, connecting a pressure measuring instrument on the main steam pipeline, detecting the pressure of the regulating stage of the steam turbine, and then calculating the new steam admission flow of the steam turbine, namely the main steam flow F ms ；
Step five, determining the discharge flow F outside the boiler according to the steps wp And determining an enthalpy value corresponding to the discharged working medium, wherein the heat carried by the discharged working medium, namely the discharged flow of the boiler, is multiplied by the corresponding enthalpy value.
2. The calculation method according to claim 1, wherein in the third step, the number of the high-pressure heaters is 3, a water supply pipe between the deaerator and the high-pressure heaters is provided with a water supply pump seal water inlet, a water supply pump seal water outlet and a reheater desuperheating water outlet, based on which,
heat balance calculation equation for high pressure heater No. 1:
F fw (h f0 -h f1 )＝F 1 (h 1 -h d1 )
in the formula: f fw T/h is the water supply flow; h is f0 Is the water outlet enthalpy of the No. 1 high-pressure heater, kJ/kg; h is a total of f1 The enthalpy of inlet water of the No. 1 high-pressure heater is kJ/kg; f 1 The steam inlet quantity of a No. 1 high-pressure heater is t/h; h is a total of 1 The enthalpy of the inlet steam of the No. 1 high-pressure heater is kJ/kg; h is d1 The enthalpy is the hydrophobic enthalpy of a No. 1 high-pressure heater, kJ/kg;
heat balance calculation equation for high pressure heater No. 2:
F fw (h f1 -h f2 )＝F 2 (h 2 -h d2 )+F 1 (h d1 -h d2 )
in the formula: f 2 The steam inlet quantity of a No. 2 high-pressure heater is t/h; h is 2 The enthalpy of the inlet steam of the No. 2 high-pressure heater is kJ/kg; h is d2 The enthalpy is the hydrophobic enthalpy of a No. 2 high-pressure heater, kJ/kg; h is f2 The enthalpy of inlet water of the No. 2 high-pressure heater is kJ/kg;
heat balance calculation equation for high pressure heater No. 3:
F fw (h f2 -h f3 )＝F 3 (h 3 -h d3 )+(F 1 +F 2 )(h d2 -h d3 )
in the formula: f 3 The steam inlet quantity of a No. 3 high-pressure heater is t/h; h is 3 The enthalpy of the inlet steam of the No. 3 high-pressure heater is kJ/kg; h is a total of d3 The hydrophobic enthalpy of a No. 3 high-pressure heater is kJ/kg; h is a total of f3 The enthalpy of inlet water of a No. 3 high-pressure heater is kJ/kg;
the heat balance calculation equation of the deaerator is as follows:
F ot4 h ot4 ＝F 4 h 4 +F in h in4 +(F 1 +F 2 +F 3 )h d3 ；
in the formula: f ot4 The water outlet flow of the deaerator is t/h; h is ot4 The enthalpy of the effluent of the deaerator is kJ/kg; f 4 The steam inlet flow of the deaerator is t/h; h is a total of 4 Is the steam inlet enthalpy of the deaerator, kJ/kg; f in Measuring the obtained deaerator inlet condensate flow rate t/h; h is in4 The enthalpy of water inlet of the deaerator is kJ/kg;
and (3) calculating the flow balance of the deaerator:
F ot4 ＝F 1 +F 2 +F 3 +F 4 +F in ；
feed water flow F fw The calculation equation of (c):
F fw ＝F ot4 +F mfin -F mfot -F gr -F zr ；
in the formula: f mfin Measuring the obtained sealing water inlet flow of the water feeding pump, t/h; f mfot Measuring the obtained flow of the sealing water outlet of the water feeding pump t/h; f gr Measuring the obtained superheater desuperheating water flow, t/h; f zr Measuring the obtained reheater reduced temperature water flow rate, t/h;
the method comprises assuming an initial value of water supply flow, calculating to obtain a corresponding water supply flow calculation value, correcting the initial value by using the deviation of the initial value and the water supply flow calculation value, substituting the initial value into calculation, and performing iteration circularly until the deviation between the assumed water supply flow and the calculated water supply flow meets the precision requirement, thereby obtaining accurate water supply flow F fw 。
3. The method of claim 1, wherein in step four, the main steam flow F ms Is calculated by the formula F ms ＝cP 1 + k, wherein: f ms The main steam flow is t/h; p 1 The measured pressure of the regulating stage of the steam turbine is MPa; c is a constant, thermal characteristic data provided by a manufacturer; k is a constant, the thermal property data provided by the manufacturer.
4. The calculation method according to claim 1, wherein in the fifth step, the boiler comprises a steam-water separator, the working medium discharged outside the boiler is saturated water separated by the steam-water separator, and the corresponding enthalpy value can be obtained by checking an enthalpy-entropy diagram according to the pressure of the steam-water separator;
boiler outer discharge flow F wp Is F wp ＝F fw +F gr -F ms ；
Boiler external discharge working medium heat loss Q wp Is Q wp ＝F wp h wp In the formula, h wp Is the saturated water enthalpy corresponding to the pressure of the steam-water separator of the boiler, kJ/kg.
5. A calculation system for heat loss of an externally-discharged working medium of a boiler of a supercritical thermal power generating unit is characterized in that the calculation method comprises a data acquisition module and a calculation module, wherein the data acquisition module is used for acquiring data of the boiler and a deaerator, and the data comprises superheater attemperation water flow F gr The steam turbine comprises a steam turbine, a steam-water separator, high-pressure heaters, a deaerator, a water pump, a reheater, a computing module and a steam turbine, wherein the steam turbine is used for regulating stage pressure, the pressure of the steam-water separator, the water outlet pressure temperature, the water inlet pressure temperature, the steam inlet pressure temperature and the water drainage pressure temperature of each high-pressure heater, the deaerator is used for deaerator, the water pump is used for sealing water inlet flow, the water pump is used for sealing water outlet flow and the reheater is used for reducing temperature water flow, the computing module is used for respectively computing the steam inlet flow, the deaerator is used for deaerator, the water supply flow F is used for deaerator, and the computing module is used for computing the steam inlet flow, the steam inlet flow and the water supply flow of each high-pressure heater based on the data collected by the data collecting module fw And main steam flow F ms And calculating the discharge flow F outside the boiler wp And then determining an enthalpy value corresponding to the discharged working medium, and calculating the heat carried by the discharged working medium.
6. The computing system of claim 5, wherein the data collection module comprises a first orifice meter located in the superheater de-superheating water pipeline, a first pressure measurement instrument located in the main steam pipeline and used for detecting the pressure of the turbine regulating stage, a first ultrasonic flow meter arranged at a seal water inlet of a feed pump, a second ultrasonic flow meter arranged at a seal water outlet of the feed pump, a second orifice meter arranged at a reheater de-superheating water outlet, a third orifice meter used for measuring the flow of condensate water at an inlet of a deaerator, a second pressure measurement instrument used for measuring the pressure of a steam-water separator, a third pressure measurement instrument used for measuring the outlet water pressure of a No. 1 high-pressure heater, a fourth pressure measurement instrument used for measuring the inlet water pressure of a No. 1 high-pressure heater, and a fifth pressure measurement instrument used for measuring the inlet steam pressure of a No. 1 high-pressure heater, a sixth pressure measuring instrument for measuring drainage pressure of the No. 1 high-pressure heater, a seventh pressure measuring instrument for measuring outlet water pressure of the No. 2 high-pressure heater, an eighth pressure measuring instrument for measuring inlet water pressure of the No. 2 high-pressure heater, a ninth pressure measuring instrument for measuring inlet steam pressure of the No. 2 high-pressure heater, a tenth pressure measuring instrument for measuring drainage pressure of the No. 2 high-pressure heater, an eleventh pressure measuring instrument for measuring outlet water pressure of the No. 3 high-pressure heater, a twelfth pressure measuring instrument for measuring inlet water pressure of the No. 3 high-pressure heater, a thirteenth pressure measuring instrument for measuring inlet steam pressure of the No. 3 high-pressure heater, a fourteenth pressure measuring instrument for measuring drainage pressure of the No. 3 high-pressure heater, a fifteenth pressure measuring instrument for measuring outlet water pressure of the deaerator, and a sixteenth pressure measuring instrument for measuring inlet water pressure of the deaerator, the device comprises a seventeenth pressure measuring instrument for measuring steam inlet pressure of a deaerator, a first temperature measuring instrument for measuring water outlet temperature of a high-pressure heater No. 1, a second temperature measuring instrument for measuring water inlet temperature of the high-pressure heater No. 1, a third temperature measuring instrument for measuring steam inlet temperature of the high-pressure heater No. 1, a fourth temperature measuring instrument for measuring water drainage temperature of the high-pressure heater No. 1, a fifth temperature measuring instrument for measuring water outlet temperature of the high-pressure heater No. 2, a sixth temperature measuring instrument for measuring water inlet temperature of the high-pressure heater No. 2, a seventh temperature measuring instrument for measuring steam inlet temperature of the high-pressure heater No. 2, an eighth temperature measuring instrument for measuring water drainage temperature of the high-pressure heater No. 2, a ninth temperature measuring instrument for measuring water outlet temperature of the high-pressure heater No. 3, a tenth temperature measuring instrument for measuring water inlet temperature of the high-pressure heater No. 3, an eleventh temperature measuring instrument for measuring steam inlet temperature of the high-pressure heater No. 3, a twelfth temperature measuring instrument for measuring water drainage temperature of the high-pressure heater, a thirteenth temperature measuring instrument for measuring water outlet temperature of the deaerator, and a fourteenth temperature measuring steam inlet temperature of the deaerator.
CN202211177419.5A 2022-09-26 2022-09-26 Method and system for calculating heat loss of discharged working medium of boiler of supercritical thermal power generating unit Pending CN115495700A (en)

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