State monitoring device for auxiliary machinery cooling system, and state monitoring method for auxiliary machinery cooling system

Abstract

To provide means that monitors states of heat exchangers and pumps in a nuclear reactor auxiliary machinery cooling system and a turbine auxiliary machinery cooling system.SOLUTION: A heat exchange performance evaluation system 100 of an aspect of the present invention comprises: a thermal load calculation program Pg3 of a RCW connection system for calculating a quantity of heat exchanged by a heat exchanger in the RCW system, on the basis of measurement data from an instrument provided in the RCW system and measurement data from an instrument provided in the other system connected with the RCW system; a heat exchange flow rate and temperature estimation program Pg4 for estimating an amount of water passing through the heat exchanger in the RCW system and an outlet temperature of cooling water from the heat exchanger in the RCW system, on the basis of an inlet temperature and the heat exchange quantity of cooling water input to a pump in the RCW system; and a RCW system mass balance and energy balance correction program Pg5 for correcting the quantity of heat exchanged by the heat exchanger, the flow rate of water passing through the heat exchanger, and the outlet temperature of the heat exchanger, on the basis of consistency between a mass balance and an energy balance of the heat exchange quantity, passing water flow rate, and outlet temperature.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to an apparatus and a method for monitoring the status of an auxiliary cooling system. [Background technology]

[0002] Nuclear power plants are equipped with a reactor building closed cooling water system (hereinafter referred to as RCW (Reactor Building Closed Cooling Water System) system) and a turbine building cooling water system (hereinafter referred to as TCW (Turbine Building Cooling Water System) system). Each system has the role of dissipating heat generated from the reactor equipment or turbine equipment into seawater, which is the final heat sink, and supplying cold water for cooling to each equipment. In particular, the RCW system has the function of not only removing heat during operation, but also removing decay heat generated in the event of an accident. Therefore, it is important to ensure the performance of the RCW system in order to operate a nuclear power plant safely.

[0003] The RCW system and TCW system each consist of closed-loop piping, a pump, a heat exchanger, and a surge tank. The heat exchanger is connected to each heat load and to the seawater cooling system, which is the final heat sink. The seawater cooling system consists of the reactor component cooling seawater system (hereafter referred to as the RSW (Reactor Sea Water System) system) and the turbine component cooling seawater system (hereafter referred to as the TSW (Turbine Sea Water System) system). To ensure the performance of the RCW system and TCW system, it is necessary to maintain the pump and heat exchanger in a state where they can perform as specified.

[0004] Since the exhaust heat from the reactor equipment and turbine equipment is generated even when the plant is shut down, the RCW system and TCW system are system equipment that cannot be shut down even during periodic inspections. Therefore, each pump and heat exchanger of the RCW system and TCW system is configured with redundancy, and during maintenance inspection, some of the multiple systems are isolated and stopped. However, when maintenance inspection is performed in this manner, redundancy decreases during maintenance inspection, making it difficult to perform maintenance inspection over long periods of time. Furthermore, in maintenance inspections that are performed by isolating and stopping some of the multiple systems, the timing of construction work is limited, which has a large impact on the overall process of periodic inspections.

[0005] In domestic nuclear power plants, time-based maintenance, which involves regular maintenance and inspection of equipment, is the norm, but in recent years there has been a move to adopt condition-based maintenance, which involves monitoring the status of target equipment and conducting maintenance and inspection as necessary.As mentioned above, RCW and TCW systems are subject to large loads during maintenance and inspection, so it is desirable to monitor the status of pumps and heat exchangers and conduct maintenance and inspection as necessary.

[0006] From the above, it can be said that monitoring the condition of the pumps and heat exchangers that make up the RCW and TCW systems is important from the perspective of streamlining regular plant inspections.

[0007] Patent Document 1 discloses an abnormality monitoring device for a heat exchanger that can determine the presence or absence of scale adhesion to the drain water level control valve, the presence or absence of leakage from the heat exchange tubes, and the presence or absence of a short path of drain or entrapment of bleed steam in the drain cooling section due to damage to the water chamber partition plate or the heat exchanger drain cooling section enclosure plate by monitoring the inlet feed water flow rate or the drain outlet flow rate to the heat exchanger, or their equivalents. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] Japanese Patent Application Publication No. 5-39902 Summary of the Invention [Problem to be solved by the invention]

[0009] In the technology described in Patent Document 1, the abnormality monitoring device calculates the heat transfer coefficient from the actual measured values ​​of the inlet and outlet temperatures of the heat exchanger, the steam temperature as the heating source, and the outlet temperature of the drain in order to monitor the heat exchange performance, and monitors the condition of the heat exchanger by monitoring the heat transfer coefficient. However, in the RCW system and TCW system, the process quantities required for the abnormality monitoring device described in Patent Document 1 to calculate the heat transfer coefficient are not measured, so in order to implement the system, it is necessary to additionally install a large number of thermometers, pressure gauges, flow meters, etc.

[0010] However, as mentioned above, the RCW system and TCW system are system equipment that need to operate even when the plant is shut down, and large-scale construction work for installing sensors would lead to the shutdown of the entire plant, so installing a large number of sensors is undesirable.Patent Document 1 discloses a means for estimating the temperature in the drain cooling section and in the vicinity of the condenser outlet from other process quantities, but the technology described in Patent Document 1 is intended for a feedwater heater that involves steam condensation, and there is a problem that it cannot be directly applied to the status monitoring of RCW system and TCW system heat exchangers that do not involve phase change.

[0011] The present invention has been made in consideration of the above problems, and an object of the present invention is to provide a means for monitoring the state of each heat exchanger and each pump in a reactor auxiliary cooling system and a turbine auxiliary cooling system. [Means for solving the problem]

[0012] According to one aspect of the present invention, there is provided an auxiliary cooling system status monitoring device for a reactor auxiliary or a turbine auxiliary, the auxiliary cooling system status monitoring device includes: an exchange heat amount calculation unit that calculates an exchange heat amount in a heat exchanger of the auxiliary cooling system based on measurement data by an instrument provided in the auxiliary cooling system and measurement data by an instrument provided in another system on a load side connected to the auxiliary cooling system; a water flow rate and outlet temperature estimation unit that estimates a water flow rate of the heat exchanger of the auxiliary cooling system and an outlet temperature of the cold water from the heat exchanger based on an inlet temperature and an exchange heat amount of cold water input to a pump of the auxiliary cooling system; and a correction unit that corrects the exchange heat amount of the heat exchanger, the water flow rate of the heat exchanger, and the outlet temperature of the heat exchanger based on consistency of the exchange heat amount, the water flow rate, and the outlet temperature with a mass balance and an energy balance. Effect of the Invention

[0013] In accordance with at least one aspect of the present invention, a means is provided for monitoring the condition of each heat exchanger and each pump in a reactor auxiliary cooling system and a turbine auxiliary cooling system. Problems, configurations and effects other than those described above will become apparent from the following description of the embodiments. [Brief description of the drawings]

[0014] [Figure 1] FIG. 1 is a system diagram of an RCW system according to a first embodiment of the present invention. [Diagram 2] FIG. 1 is a diagram showing an example of the configuration of a heat exchange performance evaluation system, which is an RCW system heat exchange performance evaluation system according to a first embodiment of the present invention, and an example of a heat exchange performance evaluation procedure. [Diagram 3] FIG. 2 is a system diagram of an RSW system according to the first embodiment of the present invention. [Figure 4] FIG. 1 is a system diagram of a HECW system according to a first embodiment of the present invention. [Diagram 5] FIG. 1 is a system diagram of an RHR system according to a first embodiment of the present invention. [Figure 6] FIG. 1 is a system diagram of an FPC system according to a first embodiment of the present invention. [Figure 7]FIG. 1 is a system diagram of a CUW system according to a first embodiment of the present invention. [Figure 8] FIG. 2 is a diagram showing the concept of a method for calculating a heat exchange amount and a temperature according to the first embodiment of the present invention. [Figure 9] 4A to 4C are diagrams showing examples of heat transfer water flow rates and outlet temperatures evaluated by the heat exchange amount and temperature estimation program according to the first embodiment of the present invention. [Figure 10] FIG. 2 is a system diagram of a TCW system according to a second embodiment of the present invention. [Figure 11] FIG. 11 is a diagram showing an example of the configuration of a TCW system heat exchanger performance evaluation system according to a second embodiment of the present invention. [Figure 12] FIG. 11 is a system diagram of a TSW system according to a second embodiment of the present invention. [Figure 13] FIG. 1 is a system diagram of an HNCW system according to a second embodiment of the present invention. [Figure 14] 13 is a diagram showing an example of a heat transfer water flow rate and an outlet temperature evaluated by a heat exchange amount and temperature estimation program according to a second embodiment of the present invention. FIG. [Figure 15] 1 is a block diagram showing an example of a hardware configuration of a terminal device according to a first embodiment and a second embodiment of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each embodiment, the same components or components having substantially the same functions are given the same reference numerals, and duplicated explanations will be omitted. Note that each figure is merely a schematic illustration to the extent that the present invention can be fully understood, and the present invention is not limited to the following contents and the contents shown in the drawings, and can be modified or combined as desired within the scope that does not significantly impair the effects of the present invention.

[0016] <First embodiment> [RCW family tree]

[0017] Fig. 1 is a system diagram of an RCW system 1000 in a first embodiment of the present invention. The RCW system 1000 is a system that cools the equipment of each system required for the operation of a nuclear reactor. Among the systems connected to the RCW system 1000, the following six systems, which are the main heat loads of the RCW system 1000, are shown in Fig. 3 and subsequent figures. - Reactor auxiliary cooling sea water system 10 (hereinafter referred to as "RSW (Reactor Sea Water (System)) system", see Figure 3) Heating Ventilation and Conditioning System Emergency Cooling Water (System) 20 (hereinafter referred to as the "HECW (Heating Ventilation and Conditioning System Emergency Cooling Water (System)"; see Figure 4) Residual heat removal system 30 (hereinafter referred to as "RHR (Residual Heat Removal (System)"; see FIG. 5) Fuel Pool Cooling and Filtering (System) 40 (hereinafter referred to as the "FPC (Fuel Pool Cooling and Filtering (System)) system", see Figure 6) Reactor Coolant Clean-up System 50 (hereinafter referred to as "CUW (Reactor Water) Clean-up (System)"; see FIG. 7) -Hot Water Heating System (not shown)

[0018] The RSW system 10 shown in FIG. 3 is a system that releases heat absorbed by each heat exchanger of the RCW system 1000 via the RCW heat exchanger 2 to a water discharge pit 14 (see FIG. 3) into seawater. The HECW system 20 shown in FIG. 4 is a system that supplies cold water for cooling to the cooling coils of each ventilation and air conditioning facility provided in a central control room (not shown) or the like. The RHR system 30 shown in FIG. 5 is a system that supplies cold water to a reactor pressure vessel 31 (see FIG. 5) in the event of an emergency.

[0019] The FPC system 40 shown in Figure 6 is a system that removes decay heat from a spent fuel storage pool 41 (see Figure 6) in which spent fuel is stored, maintains the temperature of the pool water in the spent fuel storage pool 41 below a specified value, and adjusts the water level of the spent fuel storage pool 41.

[0020] The CUW system 50 shown in FIG. 7 is a system that extracts a portion of the coolant (reactor water) inside the reactor pressure vessel 31 (see FIG. 5), removes impurities from the reactor water, and returns the reactor water to the reactor pressure vessel 31. The on-site hot water system is a system that receives exhaust heat from the CUW system 50 and supplies it to each piece of equipment that needs heating within the nuclear power plant.

[0021] The above-mentioned RSW system 10, HECW system 20, RHR system 30, FPC system 40, CUW system 50, and station hot water system are respectively connected to the RCW heat exchanger 2, HECW chiller 3, RHR heat exchanger 4, FPC heat exchanger 5, CUW non-regenerative heat exchanger 6, and station hot water system heat exchanger 7 of the RCW system 1000. In Fig. 1, illustration of other heat loads connected to the RCW system 1000 is omitted. In the following description, the HECW chiller 3, RHR heat exchanger 4, FPC heat exchanger 5, CUW non-regenerative heat exchanger 6, and station hot water system heat exchanger 7 are also collectively referred to as "RCW system heat exchangers."

[0022] The piping of the RCW system 1000 that connects each of the RCW system heat exchangers described above is a closed loop, and fresh cold water is circulated through the piping by an RCW pump 1 connected to the piping. Each heat exchanger of the RCW system 1000 absorbs heat input from each heat load connected to each heat exchanger, using the fresh cold water supplied from the RCW pump 1. The RCW heat exchanger 2 is connected to an RSW system 10 shown in Fig. 3, and the RCW heat exchanger 2 discharges the heat input from each heat load absorbed by each RCW system heat exchanger to seawater, which is the final heat sink, via a water discharge pit 14 (see Fig. 3).

[0023] A surge tank 8 is also connected to the piping of the RCW system 1000. The surge tank 8 is a tank for absorbing expansion and contraction caused by temperature changes of the cold water flowing through the RCW system 1000.

[0024] A flow meter F, a thermometer T, a pressure gauge P, and a level gauge L for monitoring the plant status are connected to the RCW system 1000 and each of the above-mentioned systems on the load side, which serves as the thermal load of the RCW system 1000, and these instruments are connected to a process computer installed in a central control room (not shown).

[0025] The flow meters F installed in the RCW system 1000 include a flow meter F1 installed near the outlet of the RCW heat exchanger 2, a flow meter F2 installed near the inlet of the CUW non-regenerative heat exchanger 6, a flow meter F3 installed near the inlet of the RHR heat exchanger 4, and a flow meter F4 installed near the inlet of the surge tank 8.

[0026] The thermometers T installed in the RCW system 1000 include a thermometer T1 installed near the inlet of the RCW pump 1, a thermometer T2 and a thermometer T3 installed near the outlet of the RCW heat exchanger 2, and a thermometer T4 installed near the outlet of the RHR heat exchanger 4. The pressure gauge P provided in the RCW system 1000 includes a pressure gauge P1 provided near the outlet of the RCW pump 1, and the level gauge L provided in the RCW system 1000 includes a level gauge L1 provided in the surge tank 8.

[0027] In order to monitor the heat exchange performance of the RCW system heat exchangers as the state of each RCW system heat exchanger in the RCW system 1000, it is necessary to know the amount of heat input to the RCW system 1000, but in the RCW system 1000 shown in Fig. 1, it is not possible to obtain the following parameters (1)-(3) because no instruments for detecting these parameters are installed in the RCW system 1000.

[0028] (1) The inlet flow rate and the outlet flow rate of the HECW refrigerator 3, i.e., the water flow rate (2) Water flow rate of FPC heat exchanger 5 (3) Outlet temperatures of the HECW refrigerator 3, FPC heat exchanger 5, CUW non-regenerative heat exchanger 6, and on-site hot water system heat exchanger 7

[0029] In a first embodiment, a means is provided for evaluating the heat exchange performance of the RCW system 1000 using the current instrumentation configuration on the RCW system 1000 and other systems connected to the RCW system 1000. Fig. 2 is a diagram showing an example of the configuration of a heat exchange performance evaluation system 100, which is an RCW system heat exchange performance evaluation system according to the first embodiment of the present invention, and an example of a heat exchange performance evaluation procedure. The heat exchange performance evaluation system 100 has an enthalpy calculation program Pg1, a pump flow rate calculation program Pg2, a heat load calculation program Pg3 of an RCW connection system, a heat exchange amount and temperature estimation program Pg4, and a mass balance and energy balance correction program Pg5 of the RCW system. The heat exchange performance evaluation system 100 shown in Fig. 2 is configured in a terminal device TD (an example of a status monitoring device for an auxiliary cooling system).

[0030] The input data to the heat exchanger performance evaluation system 100 includes process data 101 input from each instrument of the RCW system 1000 to a process computer (not shown), pump performance test data 102, and an instrument specification table 103 related to the instruments of the RCW system. The output from the heat exchanger performance evaluation system 100 is a deterioration state list 104 of the heat exchanger and pump, a drift state list 105 of the instruments, and a recommended inspection timing 106 for deteriorated equipment.

[0031] The enthalpy calculation program Pg1 (an example of an enthalpy calculation section) of the heat exchange performance evaluation system 100 calculates (evaluates) the fluid enthalpy (hereinafter also simply referred to as "enthalpy") of the compressed water flowing through the measurement (location) points of these instruments (pressure gauge, thermometer) based on the pressure value (an example of measurement data) measured by the pressure gauge installed in each system (RCW system 1000 and each system on the load side connected to RCW system 1000) and the measured temperature (an example of measurement data) measured by the thermometer.

[0032] The pump flow rate calculation program Pg2 (an example of a pump flow rate calculation section) evaluates the discharge flow rate (hereinafter also referred to as "thermal transport water flow rate") of each pump installed in each system from the pump head (differential pressure) measured by an instrument (level gauge) installed in each system. The heat load calculation program Pg3 (an example of a heat exchange calculation section) for the RCW-connected system evaluates the heat load (heat exchange amount) in each system using the enthalpy evaluated in the enthalpy calculation program Pg1 and the heat transport water flow rate evaluated in the pump flow calculation program Pg2.

[0033] The heat exchange amount and temperature estimation program Pg4 (an example of a water flow rate and outlet temperature estimation section) estimates (calculates) the water flow rate and outlet temperature in the RCW system 1000 using the enthalpy evaluated by the enthalpy calculation program Pg1, the heat transport water flow rate evaluated by the pump flow rate calculation program Pg2, and the exchanged heat amount output by the heat load calculation program Pg3 of the RCW connected system. The mass balance and energy balance correction program Pg5 (an example of a correction unit) corrects the measured values ​​by each instrument installed in each system and the evaluation values ​​by each program based on the law of conservation of mass and the law of conservation of energy in the RCW system 1000.

[0034] The control unit (not shown) of the terminal device TD first evaluates the enthalpy at each measurement point of each system using an enthalpy calculation program Pg1 (step S1). Next, the control unit evaluates the water flow rate (heat transport water volume) of each pump using a pump flow rate calculation program Pg2 (step S2). Next, the control unit evaluates the heat load in each system using a heat load calculation program Pg3 for the RCW-connected system (step S3). Next, the control unit estimates the water flow rate and outlet temperature in the RCW system using a heat exchange rate and temperature estimation program Pg4 (step S4). Finally, the control unit corrects the measured values ​​in each system and the evaluation values ​​by each program using a mass balance and energy balance correction program Pg5.

[0035] Before proceeding to an explanation of how each evaluation value is calculated by each program Pg, the configuration of each main system connected to the RCW system 1000 will be explained with reference to Figures 3 to 7. Figure 3 is a system diagram of the RSW system 10, Figure 4 is a system diagram of the HECW system 20, Figure 5 is a system diagram of the RHR system 30, Figure 6 is a system diagram of the FPC system 40, and Figure 7 is a system diagram of the CUW system 50.

[0036] The RSW system 10 shown in Fig. 3 has an RSW pump 12, a seawater strainer 13, and an RCW heat exchanger 2. The RSW pump 12 draws up seawater from a seawater intake pit 11 and outputs it. The seawater strainer 13 filters the seawater drawn up by the RSW pump 12 and outputs it to the RCW heat exchanger 2. The RCW heat exchanger 2 discharges heat input from each thermal load absorbed by each RCW system heat exchanger of the RCW system 1000 connected to the RCW heat exchanger 2 to seawater via a water discharge pit 14.

[0037] The instruments provided in the RSW system 10 include a thermometer T1-1 provided near the water intake pit 11, and a pressure gauge P1-1 provided near the outlet of the RSW pump 12. The instruments provided in the RSW system 10 also include a differential pressure gauge dP1-1 that measures the pressure difference (differential pressure) between the pressure value on the upstream (input) side and the pressure value on the downstream (output) side of the seawater strainer 13, and a differential pressure gauge dP1-2 that measures the pressure difference between the upstream and downstream sides of the RCW heat exchanger. The instruments provided in the RSW system 10 also include a thermometer T1-2 provided near the outlet of the RCW heat exchanger 2, and a pressure gauge P1-2 provided near the water discharge pit 14.

[0038] The HECW system 20 shown in Fig. 4 has an intake air treatment device 21, an HECW pump 22, and an HECW chiller 3. The intake air treatment device 21 is a device that removes dust and the like contained in the air and conditions (cools or heats) the air. The HECW pump 22 is a pump that outputs cold water output from the intake air treatment device 21 to the HECW chiller 3. The HECW chiller 3 cools the water supplied from the HECW pump 22 and supplies it to the intake air treatment device 21.

[0039] The instruments installed in the HECW system 20 include a thermometer T2-1 installed in the path from the air supply treatment device 21 to the HECW pump 22, a differential pressure gauge dP2-1 that measures the pressure difference between the upstream and downstream sides of the air supply treatment device 21, and a thermometer T2-2 installed near the outlet of the HECW refrigerator 3.

[0040] The RHR system 30 shown in Fig. 5 includes a reactor pressure vessel 31, a suppression pool 32, an RHR pump 33, and an RHR heat exchanger 4. The reactor pressure vessel 31 is a steel vessel that contains fuel. The suppression pool 32 is a facility that stores a large amount of water and is provided at the bottom of the reactor pressure vessel 31. The suppression pool 32 is a device that suppresses a pressure rise inside the reactor pressure vessel 31 by releasing steam inside the reactor pressure vessel 31 into the suppression pool 32.

[0041] The RHR pump 33 outputs the water pumped out from the suppression pool 32 or the water output from the reactor pressure vessel 31 to the RHR heat exchanger 4. The RHR heat exchanger 4 cools the water pumped out of the suppression pool 32 by the RHR pump 33, and returns the cold water to the suppression pool 32. The RHR heat exchanger 4 also supplies cold water to the reactor pressure vessel 31.

[0042] The instruments provided in the RHR system 30 include a pressure gauge P3-1 and a thermometer T3-1 provided near the outlet of the RHR pump 33, a thermometer T3-2 and a flow meter F3-1 provided near the outlet of the RHR heat exchanger 4, and a pressure gauge P3-2 provided near the outlet of the reactor pressure vessel 31.

[0043] 6 includes a spent fuel storage pool 41, a skimmer surge tank 42, an FPC pump 43, a filtration and demineralization device 44, and an FPC heat exchanger 5. The spent fuel storage pool 41 is a storage pool that accommodates spent fuel, and the skimmer surge tank 42 is a tank into which water that overflows from the spent fuel storage pool 41 flows.

[0044] The FPC pump 43 pumps out the water accumulated in the skimmer surge tank 42 and outputs it to the filtration and desalination device 44. The filtration and desalination device 44 removes impurities from the water pumped out of the skimmer surge tank 42 and also removes salt contained in the water pumped out of the skimmer surge tank 42. The FPC heat exchanger 5 cools the water purified by the filtration and demineralization device 44 and outputs the cold water to the spent fuel storage pool 41.

[0045] The instruments provided in the FPC system 40 include a level gauge L4-1 that measures the water level of the skimmer surge tank 42, a thermometer 4-1 provided near the outlet of the skimmer surge tank 42, a flow meter F4-1 and a pressure gauge P4-1 provided near the outlet of the FPC pump 43, and a flow meter F4-2 provided near the outlet of the filtration and demineralization device 44. The instruments provided in the FPC system 40 also include a thermometer T4-2 provided near the outlet of the FPC heat exchanger 5, and a thermometer T4-3 that measures the temperature of the spent fuel storage pool 41.

[0046] The CUW system 50 shown in FIG. 7 includes a CUW regenerative heat exchanger 51, a CUW non-regenerative heat exchanger 6, a CUW pump 52, and a filtration and demineralization device 53. The CUW regenerative heat exchanger 51 lowers the temperature of the water output to the CUW non-regenerative heat exchanger 6, and raises the temperature of the water purified by the filtration and demineralization device 53, and returns the water to the reactor pressure vessel 31 (see Figure 5). The CUW non-regenerative heat exchanger 6 is a heat exchanger that lowers the temperature of the water to be supplied to the filtration and desalination device 53 .

[0047] The CUW pump 52 is a pump that outputs the cold water supplied from the CUW non-regenerative heat exchanger 6 to the filtration and desalination device 53. The filtration and desalination device 53 removes impurities and salt from the cold water supplied from the CUW non-regenerative heat exchanger 6, and outputs the purified cold water to the CUW regenerative heat exchanger 51.

[0048] [Processing by each program of the heat exchange performance evaluation system] (Enthalpy calculation program) Continuing the explanation by returning to Fig. 2, the enthalpy calculation program Pg1 of the heat exchange performance evaluation system 100 calculates (evaluates) the enthalpy at the measurement locations (measurement points) of the above-mentioned systems (RCW system 1000, RSW system 10, HECW system 20, RHR system 30, FPC system 40, and CUW system 50) based on the pressure values ​​and measured temperatures in these systems.

[0049] In the case of the RCW system 1000 shown in FIG. 1, the enthalpy calculation program Pg1 calculates each enthalpy H at each temperature measurement point of the thermometer T1, the thermometer T2, the thermometer T3, and the thermometer T4 using each of the following formulas (1) to (4). 1 - Enthalpy H 4 Rate the following.

[0050] H 1 =st_HPT(ρg(L 1 -L 0 ),T 1 )...Equation (1) H 2 =st_HPT(P 1 ,T 2 )...Equation (2) H 3 =st_HPT(P 1 ,T 3 )...Equation (3) H 4 =st_HPT(P 1 ,T 4 )...Equation (4)

[0051] In the above formula (1), "ρ" represents the fresh water density, "g" represents the gravitational acceleration, and "L 0 " indicates the height of the measurement point of thermometer T1 (see Figure 1), and "L 1 " indicates the water level of the surge tank 8 measured by the level gauge L1. 1 -L 0 ),T 1) is a steam table function for calculating the enthalpy of compressed water flowing at the location where thermometer T1 (see Figure 1) is installed (near the inlet of RCW heat exchanger 2). Since the air pressure in each system, such as RSW system 10, is kept higher than atmospheric pressure, the water flowing through the piping of RSW system 10 becomes compressed water. 1 " is the temperature (an example of the inlet temperature) measured by a thermometer T1 provided near the inlet of the RCW pump 1.

[0052] In the above formula (2), "st_HPT(P 1 ,T 2 ) is the pressure value P measured by the pressure gauge P1. 1 and the temperature T measured by thermometer T2 2 This is a steam table function that uses the above to calculate the enthalpy of the compressed water flowing at the location where thermometer T2 is installed (near the outlet of RCW heat exchanger 2).

[0053] In the above formula (3), "st_HPT(P 1 ,T 3 ) is the pressure value P measured by the pressure gauge P1. 1 and the temperature T measured by thermometer T3. 3 This is a steam table function that calculates the enthalpy of the compressed water flowing at the location where thermometer T3 is installed (near the outlet of RCW heat exchanger 2) using

[0054] In the above formula (4), "st_HPT(P 1 ,T 4 ) is the pressure value P measured by the pressure gauge P1. 1 and the temperature T measured by thermometer T4. 4 This is a steam table function that uses the above to calculate the enthalpy of the compressed water flowing at the location where the thermometer T4 is installed (near the outlet of the RHR heat exchanger 4).

[0055] In the case of the RSW system 10 shown in FIG. 3, the enthalpy calculation program Pg1 calculates the enthalpy H at each temperature measurement point of the thermometer T1-1 and the thermometer T1-2 using the following formulas (5) and (6). 1-1 and enthalpy H 1-2 Rate the following.

[0056] H 1-1 =st_HPT(P 1-0 ,T 1-1 )...Equation (5) H 1-2 =st_HPT(P 1-1 ,T 1-2 )...Equation (6)

[0057] In the above formula (5), "P 1-0 " indicates atmospheric pressure. "st_HPT(P 1-0 ,T 1-1 ) is the atmospheric pressure and the temperature T measured by the thermometer T1-1 (see Figure 3). 1-1 This is a steam table function that calculates the enthalpy of compressed water flowing at the location where the thermometer T1-1 is installed (water intake pit 11) using the above.

[0058] In the above formula (6), "st_HPT(P 1-1 ,T 1-2 ) is the pressure value P measured by the pressure gauge P1-1 1-1 and the temperature T measured by thermometer T1-2. 1-2 This is a steam table function that calculates the enthalpy of the compressed water flowing at the location where the thermometer T1-2 is installed (near the outlet of the RCW heat exchanger 2) using the above.

[0059] In the case of the HECW system 20 shown in FIG. 4, the enthalpy calculation program Pg1 calculates the enthalpy H at each temperature measurement point of the thermometer T2-1 and the thermometer T2-2 using the following formulas (7) and (8). 2-1 and enthalpy H 2-2 Rate the following.

[0060] H 2-1 =st_HPT(P 2-0 ,T 2-1 )...Equation (7) H 2-2 =st_HPT(P 2-1 ,T 2-2 )...Equation (8)

[0061] In the above formula (7), "P 2-0" is the design system pressure of the HECW system 20. "st_HPT(P 2-0 ,T 2-1 ) is the design system pressure (P 2-0 ) and the temperature T measured by the thermometer T2-1 (see Figure 4). 2-1 This is a steam table function for calculating the enthalpy of the compressed water flowing at the location where the thermometer T2-1 is installed (between the air treatment device 21 and the HECW pump 22) using the above.

[0062] In the above formula (8), "st_HPT(P 2-1 ,T 2-2 ) is the pressure value P measured by the pressure gauge P2-1 2-1 and the temperature T measured by thermometer T2-2. 2-2 This is a steam table function that uses the above to calculate the enthalpy of the compressed water flowing at the location where the thermometer T2-2 is installed (near the outlet of the HECW refrigerator 3).

[0063] In the case of the RHR system 30 shown in FIG. 5, the enthalpy calculation program Pg1 calculates the enthalpy H at each temperature measurement point of the thermometer T3-1 and the thermometer T3-2 using the following formulas (9) and (10). 3-1 and enthalpy H 3-2 Rate the following.

[0064] H 3-1 =st_HPT(P 3-1 ,T 3-1 )...Equation (9) H 3-2 =st_HPT(P 3-1 ,T 3-2 )...Equation (10)

[0065] In the above formula (9), "st_HPT(P 3-1 ,T 3-1 ) is the pressure value P measured by the pressure gauge P3-1. 3-1 and the temperature T measured by the thermometer T3-1. 3-1 This is a steam table function that uses the above to find the enthalpy of the compressed water flowing at the location where the thermometer T3-1 is installed (between the RHR pump 33 and the RHR heat exchanger 4).

[0066] In the above formula (10), "st_HPT(P 3-1 ,T 3-2 ) is the pressure value measured by the pressure gauge P3-1 and the temperature T measured by the thermometer T3-2. 3-2 This is a steam table function that calculates the enthalpy of the compressed water flowing at the location where the thermometer T3-2 is installed (the outlet of the RHR heat exchanger 4) using the above.

[0067] In the case of the FPC system 40 shown in FIG. 6, the enthalpy calculation program Pg1 calculates each enthalpy H at each temperature measurement point of the thermometer T4-1 and the thermometer T4-2 using the following formulas (11) and (12). 4-1 and enthalpy H 4-2 Rate the following.

[0068] H 4-1 =st_HPT(ρg(L 4-1 -L 4-0 ),T 4-1 )...Equation (11) H 4-2 =st_HPT(P 4-1 ,T 4-2 )...Equation (12)

[0069] In equation (11), "st_HPT(ρg(L 4-1 -L 4-0 ),T 4-1 ) is a steam table function for finding the enthalpy of compressed water flowing at the location (near the inlet of the FPC pump 43) where the thermometer T4-1 (see FIG. 6) is installed.

[0070] In the above formula (12), "st_HPT(P 4-1 ,T 4-2 ) is the pressure value P measured by the pressure gauge P4-1. 4-1 and the temperature T measured by thermometer T4-2. 4-2 This is a steam table function that uses the above to calculate the enthalpy of compressed water flowing at the location where the thermometer T4-2 is installed (near the outlet of the FPC heat exchanger 5).

[0071] In the case of the CUW system 50 shown in FIG. 7, the enthalpy calculation program Pg1 calculates each enthalpy H at each temperature measurement point of the thermometer T5-1 and the thermometer T5-2 using the following formulas (13) and (14). 5-1 and enthalpy H 5-2 Rate the following.

[0072] H 5-1 =st_HPT(P 5-1 ,T 5-1 )...Equation (13) H 5-2 =st_HPT(P 5-1 ,T 5-2 )...Equation (14)

[0073] In the above formula (13), "st_HPT(P 5-1 ,T 5-2 ) is the pressure value P measured by the pressure gauge P5-1 5-1 and the temperature T measured by the thermometer T5-1. 5-1 This is a steam table function that uses the above to calculate the enthalpy of the compressed water flowing at the location where the thermometer T5-1 is installed (near the inlet of the CUW non-regenerative heat exchanger 6).

[0074] In the above formula (14), "st_HPT(P 5-1 ,T 5-2 ) is the pressure value P measured by the pressure gauge P5-1 5-1 and the temperature T measured by thermometer T5-2. 5-2 This is a steam table function for calculating the enthalpy of the compressed water flowing at the location where the thermometer T5-2 is installed (near the outlet of the CUW non-regenerative heat exchanger 6) using the above.

[0075] (Pump flow rate calculation program) The pump flow rate calculation program Pg2 of the heat exchange performance evaluation system 100 calculates the pump discharge flow rate in each system (RSW system 10, HECW system 20, RHR system 30, FPC system 40, CUW system 50) from the pump head in each system.

[0076] In the case of the RCW system 1000 shown in FIG. 1, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the RCW pump 1 (see FIG. 1) using the following formula (15): 1 Rate the following.

[0077] F 1 =pump_QH(P 1 -ρg(L 1 -L 0 ))...Equation (15)

[0078] In the above formula (15), "P 1 " indicates the pressure value measured by the pressure gauge P1 installed near the outlet of the RCW pump 1. "P 1 -ρg(L 1 -L 0 )" to "P 1 " and "ρg(L 1 -L 0 When "ΔP" is used to indicate the difference between the pump discharge flow rate and the pump differential pressure (head) ΔP, "pump_QH(ΔP)" indicates the pump QH (Quantity-Height) characteristic curve that determines the pump discharge flow rate from the pump differential pressure (head) ΔP. The pump QH characteristic curve that can be used is one that is obtained based on values ​​obtained from performance test data of the corresponding pump.

[0079] In the case of the RSW system 10 shown in FIG. 3, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the RSW pump 12 (see FIG. 3) using the following equation (16): 1-1 Rate the following.

[0080] F 1-1 =pump_QH(P 1-1 +ρgH)...Equation (16)

[0081] In the above formula (16), "P 1-1 " indicates the pressure value measured by the pressure gauge P1-1 installed near the outlet of the RSW pump 12, and "H" indicates the difference in height between the water level in the water intake pit 11 and the installation level of the RSW pump 12.

[0082] In the case of the HECW system 20 shown in FIG. 4, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the HECW pump 22 (see FIG. 4) using the following equation (17): 2-1 Rate the following.

[0083] F 2-1 =pump_QH(dP 2s-1 -ΔP 2-0 )...Equation (17)

[0084] In the above formula (17), "dP 2-1 " indicates the pressure difference measured by the differential pressure gauge dP2-1. "ΔP 2-0 " indicates the sum of the pressure loss (pressure drop) of the HECW refrigerator 3 and the piping pressure drop, and a planned value can be used.

[0085] In the case of the RHR system 30 shown in FIG. 5, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the HECW pump 22 (see FIG. 5) using the following equation (18): 3-2 Rate the following.

[0086] F 3-2 =pump_QH(P 3-1 -P 3-2 )...Equation (18)

[0087] In the above formula (18), "P 3-1 " indicates the pressure value measured by the pressure gauge P3-1 installed near the outlet of the RHR pump 33, and "P 3-2 " indicates the pressure value measured by the pressure gauge P3-2 installed in the path connecting the reactor pressure vessel 31 and the RHR pump 33.

[0088] In the case of the FPC system 40 shown in FIG. 6, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the FPC pump 43 (see FIG. 6) using the following formula (19): 4-3 Rate the following.

[0089] F 4-3 =pump_QH(P 4-1 -ρg(L 4-1 -L 4-0))...Equation (19)

[0090] In the above formula (19), "P 4-1 " indicates the pressure value measured by the pressure gauge P4-1 installed near the outlet of the FPC pump 43. 4-1 " indicates the water level of the skimmer surge tank 42 measured by the level gauge L4-1, and "L 4-0 " indicates the installation level of the FPC pump 43.

[0091] In the case of the CUW system 50 shown in FIG. 7, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the CUW pump 52 (see FIG. 7) using the following formula (20): 5-2 Rate the following.

[0092] F 5-2 =pump_QH(P 5-2 -P 5-1 )...Equation (20)

[0093] In the above formula (20), "P 5-1 " indicates the pressure value measured by the pressure gauge P5-1 installed near the inlet of the CUW pump 52, and "P 5-2 " indicates the pressure value measured by the pressure gauge P5-2 installed near the outlet of the CUW pump 52.

[0094] (Heat load calculation program) The heat load calculation program Pg3 of the RCW-connected system of the heat exchange performance evaluation system 100 evaluates the heat load (Q: heat exchange amount) in each system using the enthalpy (H) evaluated by the enthalpy calculation program Pg1 and the pump discharge flow rate (F: heat exchange water flow rate) evaluated by the pump flow rate calculation program Pg2.

[0095] In the case of the RSW system 10 shown in FIG. 3, the heat load calculation program Pg3 for the RCW-connected system calculates the heat exchange amount Q of the RCW heat exchanger 2 (see FIG. 3) using the following equation (21): 1 Rate the following.

[0096] Q 1 =F1-1 ×(H 1-2 -H 1-1 )-QRSW-P...Formula (21)

[0097] In the above formula (21), F 1-1 is the discharge flow rate calculated by the above formula (16). H 1-1 is the enthalpy calculated by the above formula (5), and H 1-2 is the enthalpy calculated by the above formula (6). "QRSW-P" is the discharge flow rate of the RSW pump 12. 1-1 The shaft power of the RSW pump 12 corresponding to the discharge flow rate of the RSW pump 12 can be obtained using the pump QH characteristic curve.

[0098] In the case of the HECW system 20 shown in FIG. 4, the heat load calculation program Pg3 for the RCW-connected system calculates the heat exchange amount Q of the HECW refrigerator 3 (see FIG. 4) using the following equation (22): 2 Rate the following.

[0099] Q 2 =F 2-1 ×(H 2-2 -H 2-1 )-QHECW-P...Formula (22)

[0100] In the above formula (22), F 2-1 is the discharge flow rate calculated by the above formula (17). H 2-1 is the enthalpy calculated by the above formula (7), and H 2-2 is the enthalpy calculated by the above formula (8). "QHECW-P" is the discharge flow rate of the HECW pump 22 when "F 2-1 4 shows the shaft power of the HECW pump 22 when

[0101] In the case of the RHR system 30 shown in FIG. 5, the heat load calculation program Pg3 for the RCW-connected system calculates the heat exchange amount Q of the RHR heat exchanger 4 (see FIG. 5) using the following equation (23): 3 Rate the following.

[0102] Q 3 =F 3-1 ×(H 3-2 -H 3-1 )...Equation (23)

[0103] In the above formula (23), F 3-1 is the discharge flow rate of the RHR pump 33 measured by the flow meter F3-1 (see FIG. 5). 3-1 is the enthalpy calculated by the above formula (9), and H 3-2 is the enthalpy calculated by the above formula (10).

[0104] In the case of the FPC system 40 shown in FIG. 6, the heat exchange quantity Q of the FPC heat exchanger 5 (see FIG. 6) is calculated using the following formula (24). 4 Rate the following.

[0105] Q 4 =F 4-1 ×(H 4-2 -H 4-1 )-QFPC-P...Formula (24)

[0106] In the above formula (24), F 4-1 is the discharge flow rate of the FPG pump 43 measured by the flow meter F4-1 (see FIG. 6). 4-1 is the enthalpy calculated by the above formula (11), and H 4-2 is the enthalpy calculated by the above formula (12). "QFPC-P" is the discharge flow rate of the FPC pump 43. 4-1 4 shows the shaft power of the FPC pump 43 when

[0107] In the case of the CUW system 50 shown in FIG. 7, the heat load calculation program Pg3 for the RCW-connected system calculates the heat exchange amount Q of the CUW non-regenerative heat exchanger 6 (see FIG. 7) using the following equation (23): 5 Rate the following.

[0108] Q 5 =F 5-1 ×(H 5-2 -H 5-1 )...Equation (25)

[0109] In the above formula (25), F 5-1 is the discharge flow rate of the filtration and demineralization device 53 measured by the flow meter F5-1 (see FIG. 7). 5-1 is the enthalpy calculated by the above formula (13), and H 5-2 is the enthalpy calculated by the above equation (14).

[0110] (Heat exchange and temperature estimation program) The heat exchange amount and temperature estimation program Pg4 of the heat exchange performance evaluation system 100 calculates the water flow rate (heat exchange amount) and outlet temperature in the RCW system 1000 using the exchanged heat amount (Q) output by the heat load calculation program Pg3 of the RCW connected system, the enthalpy (H) evaluated by the enthalpy calculation program Pg1, and the pump discharge flow rate (F: heat transport water flow rate) evaluated by the pump flow rate calculation program Pg2.

[0111] Here, the concept of the calculation method of the heat exchange amount and temperature according to this embodiment will be described. Fig. 8 is a diagram showing the concept of the calculation method of the heat exchange amount and temperature according to this embodiment. "K" in Fig. 8 indicates the overall heat transfer coefficient (heat flow coefficient) of the RCW heat exchangers (RCW heat exchanger 2, HECW chiller 3, RHR heat exchanger 4, FPC heat exchanger 5, CUW non-regenerative heat exchanger 6, and on-site hot water heat exchanger 7: see Fig. 1). "A" indicates the heat transfer area of ​​the RCW heat exchangers, i.e., the surface area of ​​the heat transfer tubes (not shown) of the heat exchangers.

[0112] The left side of Fig. 8 shows the cooling side (RCW system 1000 side), and the right side shows the load side, i.e., the input side of the heat load. On the cooling side, "T1i" indicates the inlet temperature of the RCW system heat exchanger, "T1o" indicates the outlet temperature of the RCW system heat exchanger, and "F1" indicates the water flow rate (heat transport water flow rate) of the RCW system heat exchanger. On the load side, "T2i" indicates the heat input temperature to the RCW system heat exchanger, "T2o" indicates the outlet temperature of the RCW system heat exchanger, and "F2" indicates the water flow rate (heat transport water flow rate) of the RCW system heat exchanger.

[0113] Around the RCW system heat exchanger (cooling side and load side), the cooling side heat balance equation (Equation (26) below: an example of the "first heat balance equation"), the load side heat balance equation (Equation (27) below: an example of the "second heat balance equation"), and the RCW system heat exchanger performance equation (Equation (28) below) hold true.

[0114] Q=F 1 ×C 1 ×(T 1O -T 1i )...Equation (26) Q=F 2 ×C 2 ×(T 2O -T 2i )...Equation (27) Q = K × A × θ(T 1i ,T 1O ,T 2i ,T 1O )...Equation (28)

[0115] In the above formula (26) and formula (27), "C 1 ", "C 2 " and "represent the low pressure specific heat of the fluid flowing on the cooling side and the constant pressure specific heat of the fluid flowing on the load side, respectively. "θ" in equation (28) is the logarithmic mean temperature difference defined by the following equation (29).

[0116]

number

[0117] Around the RCW system heat exchanger (cooling side and load side), the three simultaneous equations (26), (27), and (28) hold true, so up to three unknowns can be included. In the RCW system 1000 targeted by the first embodiment, as shown in FIG. 8, the unknowns are the water flow rate (discharge) F1 on the cooling side and the outlet temperature T1o. The heat balance equation (27) on the load side has already been used as the above-mentioned equations (21) to (25). Therefore, the equations that can be used to calculate the water flow rate F1 and the outlet temperature T1o are the above-mentioned equations (26) and (28).

[0118] Because of the logarithmic mean temperature difference shown as "θ" in equation (28), equations (26) and (28) cannot be solved by simple algebraic operations. However, by using a convergence calculation method for nonlinear equations such as the Newton-Raphson method, the water flow rate F can be calculated from equations (26) and (28). 1 and outlet temperature T 1O can be uniquely determined.

[0119] The heat exchange amount and temperature estimation program Pg4 estimates the heat exchange amount Q (heat exchange amount Q 1 -Q 5 ) and data obtained from existing sensors in the RCW system 1000 shown in Figure 1 are used to calculate and output the water flow rate (heat transport water flow rate) and outlet temperature of each heat exchanger in the RCW system 1000.

[0120] 9 is a diagram showing an example of the water flow rate and the outlet temperature evaluated by the heat exchange amount and temperature estimation program Pg4. As shown in FIG. 9, the heat exchange water flow rate output from the heat exchange amount and temperature estimation program Pg4 is the heat exchange water flow rate FP 1 -Heat water flow rate FP 5 Heat transport water flow rate FP 1 corresponds to the flow rate of the RCW heat exchanger 2, and the heat transport water flow rate FP 2 corresponds to the water flow rate of HECW refrigerator 3, and the heat transport water flow rate FP 3 corresponds to the flow rate of water through the RHR heat exchanger 4. Heat transport water flow rate FP 4 corresponds to the water flow rate of the FPC heat exchanger 5, and the heat transfer water flow rate FP 5 corresponds to the water flow rate of the CUW non-regenerative heat exchanger 6.

[0121] In addition, the outlet temperature of the RCW system heat exchanger output from the heat exchange amount and temperature estimation program Pg4 is the outlet temperature TP 1 -Outlet temperature TP 5 The outlet temperature TP 1 corresponds to the outlet temperature of RCW heat exchanger 2, and the outlet temperature TP 2 corresponds to the outlet temperature of HECW refrigerator 3, and the outlet temperature TP3 corresponds to the outlet temperature of the RHR heat exchanger 4. The outlet temperature TP 4 corresponds to the outlet temperature of the FPC heat exchanger 5, and the outlet temperature TP 5 corresponds to the outlet temperature of the CUW non-regenerative heat exchanger 6.

[0122] In other words, according to the first embodiment described above, the heat transfer water flow rate and outlet temperature of the RCW system 1000 can be calculated based on the measurement values ​​of each existing sensor (thermometer, pressure gauge, level gauge) of the RCW system 1000 and the load side system.

[0123] (Mass Balance and Energy Balance Correction Program) The measurement data from the instruments contains random errors and bias errors. Furthermore, when the instruments are used for a long period of time, instrument drift due to deterioration over time also becomes a problem. Therefore, it is assumed that the evaluation values ​​obtained by the enthalpy calculation program Pg1, the pump flow rate calculation program Pg2, the heat load calculation program Pg3, and the heat exchange amount and temperature estimation program Pg4 also contain the effects of instrument error and drift. To use these evaluation values ​​in the performance evaluation of heat exchangers and pumps, the effects of instrument error and drift must be removed from the evaluation values.

[0124] The mass balance and energy balance correction program Pg5 minimizes the effects of instrument errors and instrument drift by correcting the measurement values ​​from existing sensors and the evaluation values ​​from the heat exchange performance evaluation system 100 based on consistency with the law of conservation of mass and the law of conservation of energy in the RCW system 1000.

[0125] The inventors have also devised a method for minimizing the effects of instrument error and instrument drift, while also evaluating the deterioration state of the heat exchanger and pump. This method is realized by multiplying the heat transfer coefficient of the heat exchanger and the QH characteristic of the pump shown in equation (15) by a deterioration coefficient D in the mass balance and energy balance correction program Pg5, and taking the deterioration coefficient D into account in the correction equation.

[0126] The correction equation is shown in the following formula (30). The mass balance and energy balance correction program Pg5 performs calculations using the following correction equation (30) for each instrument. In the correction equation (30), "x" represents the measurement value from the existing sensor or each evaluation value evaluated by the above formulas (1) to (25), and "x'" represents the corrected measurement value or evaluation value. "D" represents the deterioration coefficient of the heat exchanger and pump, and "D'" represents the corrected deterioration coefficient.

[0127]

number

[0128] In the above formula (30), "i" indicates the number of the measurement data by the instrument, or the number of the evaluation value by the heat exchange performance evaluation system 100. The measurement data or evaluation value is managed in association with a number, for example, in the RCW system 1000 shown in FIG. 1, the temperature measured by the thermometer T1 is "1", the temperature measured by the thermometer T2 is "2", the enthalpy evaluated by the enthalpy calculation program Pg1 is "3", and so on. In this example, "x1(i=1)" in the above formula (30) indicates the temperature T measured by the thermometer T1. 1 is substituted, and "x2" is the temperature T measured by thermometer T2. 2 is substituted, and "x3" is the evaluation value of enthalpy H 1 is assigned.

[0129] "j" indicates the number of the deterioration coefficient. One deterioration coefficient is assigned to each of the RCW system heat exchangers, each pump included in the RCW system 1000, and each heat exchanger and pump in each system on the load side.

[0130] "im" indicates the total number of measurement data or evaluation values, and "jm" indicates the total number of degradation coefficients. "σx" indicates the sum of the accuracy of the meter or the accuracy of the evaluation values. The value listed in the meter specification table 103 (see Figure 2) can be used for the accuracy of the meter. The accuracy of the evaluation value can be evaluated from the input meter accuracy using the law of error propagation.

[0131] "σD" indicates the total frequency of occurrence of deterioration in the instrument, and the frequency of occurrence of deterioration can be determined from the inspection records to date. Then, by solving the least squares problem of the above equation (30), it is possible to obtain the correction value x' that minimizes the amount of correction and the deterioration coefficient D' after correction. If we assume that the instrument error and the deterioration of the measuring device occur independently and randomly, the solution obtained from equation (30) is a statistically plausible solution.

[0132] In order to avoid obtaining the obvious solutions x'=x and D'=D of equation (30), constraint conditions are taken into consideration in this embodiment. The constraint conditions include the heat balance equation (26) of each heat exchanger on the cooling side, the heat balance equation (27) of each heat exchanger on the load side, the following equations (31) and (32), the constraint equations (33) to (36) based on the law of conservation of mass of the RCW system 1000, and the constraint equations (37) to (45) based on the law of conservation of energy.

[0133] Q = D × K × A × θ(T 1i ,T 1O ,T 2i ,T 1O )...Equation (31)

[0134] In the above formula (31), the performance formula (28) for the RCW system heat exchanger is multiplied by the deterioration coefficient D.

[0135] F 1-1 =D×pump_QH(P 1 -ρg(L 1 -L 0 ))...Equation (32)

[0136] In the above formula (32), the formula (15), which is a formula for calculating the discharge flow rate of the RCW pump 1, is multiplied by a correction coefficient D based on the QH characteristic of the pump.

[0137] The constraint condition equations based on the law of conservation of mass for the RCW system 1000 are the following equations (33) to (36).

[0138] FP 1 =FP2 +FP 3 +FP 4 +FP 5 +F 4 +F'...Formula (33) FP 1 =F 1 ...Equation (34) FP 1 =F 1-1 ...Equation (35) FP 5 =F 2 ...Formula (36)

[0139] In the above equation (33), "F'" indicates the water flow rate of other loads not shown in the RCW system 1000 shown in Figure 1, and the water flow rate of the on-site hot water system heat exchanger 7, and planned values ​​can be used for these.

[0140] The constraint condition equations based on the law of conservation of energy for the RCW system are the following equations (38) to (45).

[0141] C*T 1 *FP 1 =C*TP 2 *FP 2 +C*TP 3 *FP 3 +C*TP 4 *FP 4 +C*TP 5 *FP 5 +Q'...Equation (37) C*TP 1 *FP 1 +Q 1 =C*T 1 *FP 1 +QRCW-P...Formula (38) C*TP 2 *FP 2 -Q 2 =C*TP 1 *FP 2 ...Formula (39) C*TP 3 *FP 3 -Q 3 =C*TP 1 *FP 3 ...Equation (40) C*TP4 *FP 4 -Q 4 =C*TP 1 *FP 4 ...Equation (41) C*TP 5 *FP 5 -Q 5 =C*TP 1 *FP 5 ...Formula (42) C*TP 1 *FP 1 =C*T 2 *FP 1 ...Formula (43) C*TP 1 *FP 1 =C*T 3 *FP 1 ...Formula (44) C*TP 3 *FP 3 =C*T 4 *FP 3 ...Equation (45)

[0142] In the above formulas (37) to (45), "C" indicates the constant pressure specific heat of the fresh water flowing through the RCW system 1000, and "Q'" indicates the heat input from other loads not shown in FIG. 1 and the heat input from the in-house hot water system, for which planned values ​​can be used. "QRCW-P" in the above formula (38) indicates the discharge flow rate of the RCW pump 1 (see FIG. 1) is the discharge flow rate F 1 The shaft power of the RCW pump 1 is shown in the case where

[0143] The mass balance and energy balance correction program Pg5 solves the above correction equation (30) under the constraint condition formulas (26), (27), and (31) to (45), thereby minimizing the influence of the instrument error or the instrument drift on the evaluation value. In addition, the mass balance and energy balance correction program Pg5 can quantitatively evaluate the deterioration state of the RCW pump 1 and each heat exchanger of the RCW system 1000, which affects the heat exchange performance of the RCW system 1000, based on the corrected deterioration coefficient D' in the above correction equation (30). Specifically, the mass balance and energy balance correction program Pg5 can evaluate that no deterioration has occurred in the RCW pump 1 and each heat exchanger when the corrected deterioration coefficient D' is "1", and can evaluate that deterioration has occurred in the RCW pump 1 and each heat exchanger when the corrected deterioration coefficient D' is a value of "1" or less.

[0144] In addition, in order to further improve the accuracy of detecting the deterioration status of the RCW pump 1 and the deterioration status of the RCW system heat exchanger, which affect the heat exchange performance of the RCW system 1000, the mass balance and energy balance correction program Pg5 may add the calculation formulas (21) to (25) for calculating the amount of heat exchanged for each heat load as constraint conditions, in addition to the above formulas (31) to (45).

[0145] The mass balance and energy balance correction program Pg5 compiles the corrected deterioration coefficient D' obtained as a solution to the correction equation (30) for each piece of equipment (pump, heat exchanger) in a list, and outputs this as a heat exchanger and pump deterioration state list 104. In addition, the mass balance and energy balance correction program Pg5 compiles the values ​​obtained by dividing the measured value x and the corrected measured value x' by the uncertainty of each measured value in a list for each instrument, and outputs this as an instrument drift state list 105. The "uncertainty" can be evaluated from the error of each measured value listed in the instrument specification table 103 (see FIG. 2) using the law of error waves.

[0146] Furthermore, since past data is stored in the heat exchanger performance evaluation system 100, the mass balance and energy balance correction program Pg5 generates and outputs the recommended inspection timing 106 for deteriorated equipment based on the time rate of change of the corrected deterioration coefficient D'. The mass balance and energy balance correction program Pg5 generates the recommended inspection timing 106 for deteriorated equipment by predicting the time when the deterioration state of the measuring instrument determined based on the time rate of change of the corrected deterioration coefficient D' will exceed a predetermined threshold value for deterioration of the measuring instrument.

[0147] Based on the heat exchanger and pump deterioration state list 104, the instrument drift state list 105, and the recommended inspection timing 106 for deteriorated equipment, which are output from the heat exchanger performance evaluation system 100, and the overall periodic inspection plan, the manager of the nuclear power plant can determine rational maintenance timing, maintenance method, etc. for RCW system equipment that minimizes the periodic inspection period.

[0148] According to the heat exchange performance evaluation system 100 of the first embodiment described above, the state of the heat exchanger and pump of the RCW system can be monitored using the measured values ​​of the existing sensors. Also, according to this embodiment, the manager of the nuclear power plant can perform rational maintenance of the RCW system equipment to minimize the periodic inspection period based on the results of grasping the state of the heat exchanger and pump of the RCW system.

[0149] <Second embodiment> Next, a second embodiment of the present invention will be described. The heat exchange performance evaluation system according to the second embodiment monitors the states of the pumps and heat exchangers that constitute the TCW system. 10 is a system diagram of a TCW system 2000 according to a second embodiment of the present invention. The TCW system 2000 serves to dissipate heat generated in a turbine system (not shown) of a nuclear power plant to seawater, which is the final heat sink. Since the plant is shut down during regular inspections, the main heat source of the TCW system 2000 during regular inspections is the normal air conditioning equipment chilled water system 80 (hereinafter referred to as the "Heating Ventilating and Air Conditioning System Normal Cooling Water (System) system").

[0150] The HNCW system (see FIG. 13) is connected to the TCW system 2000 via an HNCW refrigerator 64. The piping of the TCW system 2000 is a closed loop, and fresh water is circulated by a TCW pump 61. The TCW heat exchanger 62 is connected to a turbine auxiliary cooling seawater system 70 (hereinafter referred to as the "Turbine Sea Water (System)") shown in FIG. 12, and the heat absorbed by the TCW heat exchanger 62 is discharged to seawater via the TSW system 70.

[0151] Moreover, the TCW system 2000 has a three-way valve 63, an HNCW refrigerator 64, other loads 65, and a surge tank 66. The three-way valve 63 is a valve provided at the intersection of a bypass path (piping) that crosses the TCW heat exchanger 62 and a piping that passes through the TCW heat exchanger 62. The three-way valve 63 adjusts the ratio between the flow rate of water flowing from the TCW heat exchanger 62 and the flow rate of water flowing through the bypass path so that the temperature of the water output from the three-way valve 63, i.e., the water supplied to the HNCW refrigerator 64 and other loads 65, becomes a control temperature.

[0152] The HNCW refrigerator 64 removes the heat absorbed by the TCW heat exchanger 62 . Other loads 65 include, for example, a turbine lubricating oil cooler, a feedwater pump drive turbine oil cooler, a generator hydrogen cooler condensate pump motor cooler, a control oil cooler, a condensate booster pump (CBP) oil cooler, a CBP motor cooler, and the like (all not shown) installed in a turbine building. The surge tank 66 is a tank for absorbing the expansion and contraction of the cold water in the TCW system 2000 due to temperature changes.

[0153] Because the TCW System 2000 is a non-safety system, there are fewer instruments connected to the process computer compared to the RCW System 1000 (see Figure 1), which is a safety system. Therefore, it is difficult to monitor the condition of the heat exchanger and pump using only existing design instruments (sensors). One method that makes condition monitoring possible is to add a permanent design instrument, but when carrying out work to add a permanent design instrument, it is necessary to stop the TCW System 2000. In this case, it becomes necessary to extend the implementation period of regular inspections, and therefore carrying out work to add a permanent design instrument may result in cost losses that far exceed the benefits of condition monitoring.

[0154] One method of adding instruments without shutting down the TCW 2000 is to attach temporary instruments such as thermocouples and strain gauges to the surface of the piping and estimate the fluid temperature and pressure inside the piping based on the measurements from these temporary instruments. However, because temporary instruments generally have large instrument errors, it is expected that the accuracy required for monitoring the condition of heat exchangers and pumps will not be achieved if condition monitoring is performed using only measurements from the temporary instruments.

[0155] This embodiment has been devised in consideration of such problems, and aims to monitor the status of the heat exchanger and pump of the TCW system 2000 based on the measured values ​​from a minimum of temporary design devices and normal design devices. According to this embodiment, large-scale construction work accompanying the addition of normal design devices is not required, and therefore there is no need to stop the TCW system 2000. Therefore, it becomes possible to easily monitor the status of the heat exchanger and pump.

[0156] 10, the TCW system 2000 is provided with a level gauge L6-1, a flow meter F6-1, a pressure gauge P6-1, and a thermometer T6-1 as constant-function instruments constantly monitored by a process computer. The level gauge L6-1 is an instrument that measures the water level in the surge tank 66, and the flow meter F6-1 is an instrument that measures the flow rate of makeup water to the surge tank 66. The pressure gauge P6-1 is an instrument that measures the outlet pressure of the TCW pump 61, and the thermometer T6-1 is an instrument that measures the outlet temperature of the three-way valve 63.

[0157] The temperature of the water flowing through the pipes of the TCW system 2000 is controlled by the three-way valve 63, so the temperature measured by the thermometer T6-1 installed near the outlet of the three-way valve 63 is the mixed temperature of the hot water output from the TCW heat exchanger 62 and the bypass flow output from the bypass passage. Therefore, the thermal conductivity of the TCW heat exchanger 62 cannot be evaluated using the temperature measured by the thermometer T6-1.

[0158] In this embodiment, temporary temperature sensors TK6-1 and TK6-2 (an example of an additional temperature sensor) are installed near the inlet and outlet of the TCW heat exchanger 62, respectively, as the minimum number of temporary sensors required for performance evaluation of the heat exchanger and the pump. Because water is constantly flowing through the TCW system 2000 even during periodic inspection, it is not possible to insert thermocouples inside the piping. Therefore, thermocouples attached to the surface of the piping are used as the temporary temperature sensors TK6-1 and TK6-2. The internal fluid temperature is then estimated from the outer surface temperature of the piping measured by the thermocouples.

[0159] The thermocouple is installed on the pipe by aligning it along the pipe surface and attaching the temperature sensing part with aluminum tape. If there is an air gap between the pipe surface and the temperature sensing part, the air gap will cause temperature measurement errors, so it is desirable to apply thermally conductive grease or the like between the temperature sensing part and the pipe surface. The thermocouple is connected to, for example, a battery-powered data logger (not shown), and trend data of the measured temperature accumulated by the data logger is collected by workers or the like who patrol the site. In addition, it is desirable for each of the above-mentioned temporary devices to be removed after each periodic inspection. In other words, it is desirable for them to be installed only during the periodic inspection.

[0160] 10, the bypass flow rate of the TCW heat exchanger 62, and the outlet temperature and water flow rate of the HNCW refrigerator 64 are not measured. Therefore, the heat exchange performance of the TCW system 2000 cannot be directly evaluated from the measured values ​​by the existing sensors. In this embodiment, the bypass flow rate of the TCW heat exchanger 62, and the outlet temperature and water flow rate of the HNCW refrigerator 64 are evaluated by the TCW system heat exchange performance evaluation system using the measured values ​​by existing or temporary instruments.

[0161] Fig. 11 is a diagram showing an example of the configuration of a TCW system heat exchange performance evaluation system (hereinafter referred to as "heat exchange performance evaluation system") 200 according to a second embodiment. The heat exchange performance evaluation system 200 has an enthalpy calculation program Pg1, a pump flow rate calculation program Pg2, a heat load calculation program Pg3A of a TCW connection system, a heat exchange amount and temperature estimation program Pg4, and a mass balance and energy balance correction program Pg5A of the TCW system. The heat exchange performance evaluation system 200 shown in Fig. 11 is configured in a terminal device TD (an example of a state monitoring device) connected to a process computer (not shown).

[0162] Input data to the heat exchanger performance evaluation system 200 includes process data 201, provisional instrument data 202, pump performance test data 203, and instrument specification table 204. The process data 201, pump performance test data 203, and instrument specification table 204 are similar to the process data 101, pump performance test data 102, and instrument specification table 103 according to the first embodiment, respectively, and therefore description thereof will be omitted. The provisional instrument data 202 is measurement data obtained by provisionally installed temperature sensors and pressure sensors.

[0163] The outputs from the heat exchanger performance evaluation system 200 are a heat exchanger and pump deterioration state list 205, an instrument drift state list 206, and a recommended inspection time for deteriorated equipment 207. The heat exchanger and pump deterioration state list 205, the instrument drift state list 206, and the recommended inspection time for deteriorated equipment 207 are similar to the heat exchanger and pump deterioration state list 104, the instrument drift state list 105, and the recommended inspection time for deteriorated equipment 106 according to the first embodiment, respectively, and therefore descriptions thereof will be omitted.

[0164] The control unit (not shown) of the terminal device TD (see FIG. 11) first evaluates the enthalpy at each measurement point of each system using the enthalpy calculation program Pg1 (an example of an enthalpy calculation unit) (step S11). Next, the control unit evaluates the heat transport water volume using the pump flow calculation program Pg2 (an example of a pump flow calculation unit) (step S12). Next, the control unit evaluates the heat load in each system using the heat load calculation program Pg3A (an example of an exchange heat amount calculation unit) of the TCW connected system (step S13). Next, the control unit estimates the heat exchange volume and outlet temperature in the TCW system 2000 using the heat exchange volume and temperature estimation program Pg4 (an example of a water flow rate and outlet temperature estimation unit) (step S14). Finally, the control unit corrects each measurement value by the normal design device and the temporary design device installed in each system and the evaluation value by each program using the mass balance and energy balance correction program Pg5A (an example of a correction unit) of the TCW system.

[0165] The method of evaluating enthalpy using the enthalpy calculation program Pg1 is the same as the method of evaluating enthalpy using the enthalpy calculation program Pg1 according to the first embodiment, and the method of evaluating the heat transfer water volume (pump discharge flow rate) using the pump flow calculation program Pg2 is the same as the method of evaluating the heat transfer water volume using the pump flow calculation program Pg2 according to the first embodiment.

[0166] In addition, the method of evaluating the heat load by the heat load calculation program Pg3A of the TCW-connected system is the same as the method of evaluating the heat load by the heat load calculation program Pg3 of the RCW system according to the first embodiment, and the method of estimating the heat exchange amount and temperature by the heat exchange amount and temperature estimation program Pg4 is the same as the method of estimating the heat exchange amount and temperature by the heat exchange amount and temperature estimation program Pg4 according to the first embodiment. Furthermore, the correction method by the mass balance and energy balance correction program Pg5A of the TCW system is the same as the correction method by the mass balance and energy balance correction program Pg5 of the RCW system according to the first embodiment.

[0167] Here, the configurations of the TSW system 70 and the HNCW system 80, which are the load-side systems connected to the TCW system 2000, will be described with reference to Figures 12 and 13. Figure 12 is a system diagram of the TSW system 70, and Figure 13 is a system diagram of the HNCW system 80. The system diagrams shown in Figures 12 and 13 are system diagrams during periodic inspection, that is, system diagrams with a temporary device installed.

[0168] The TSW system 70 shown in Fig. 12 has an auxiliary pump 72, a seawater strainer 73, and a TCW heat exchanger 74. The auxiliary pump 72 draws up seawater from a seawater intake pit 71 and outputs it. The seawater strainer 73 filters the seawater drawn up by the auxiliary pump 72 and outputs it to the TCW heat exchanger 74. The TCW heat exchanger 74 absorbs heat input from the TCW system 2000 (see Fig. 10) and discharges the absorbed heat to seawater via a water discharge pit 75.

[0169] The instruments installed in the TSW system 70 include a thermometer T7-1 installed near the water intake pit 11, a temporary pressure sensor PK7-1 (an example of an additional strain sensor) installed near the outlet of the auxiliary pump 72, and a thermometer T7-2 installed near the outlet of the TCW heat exchanger 74.

[0170] Because water is constantly flowing through the TSW system 70 even during routine inspections, it is not possible to insert a pressure sensor inside the piping. Therefore, a strain sensor attached to the surface of the piping is used as the temporary pressure sensor PK7-1. The temperature of the fluid inside the piping is estimated from the amount of strain in the piping measured by the strain sensor. The strain sensor can be attached to the piping surface using adhesive or the like.

[0171] The strain sensor is connected to, for example, a battery-powered data logger (not shown), and trend data of pressure values ​​accumulated by the data logger is collected by workers or the like patrolling the site.

[0172] 13 includes an HNCW chilled water pump 81 and an HNCW chiller 82. The HNCW chilled water pump 81 outputs chilled water returned from a regular air intake treatment device (not shown) to the HNCW chiller 82. The HNCW chiller 82 cools the water supplied from the HNCW chilled water pump 81 and supplies the chilled water to the regular air intake treatment device.

[0173] The instruments installed in the HNCW system 80 include a thermometer T8-1 installed near the inlet of the HNCW chilled water pump 81, a temporary pressure sensor PK8-1 (an example of an additional strain sensor), a temporary pressure sensor PK8-2 (an example of an additional strain sensor) installed near the outlet of the HNCW chilled water pump 81, and a thermometer T8-2 installed on the path through which the chilled water cooled by the HNCW refrigerator 82 passes.

[0174] Because water is constantly flowing through the HNCW system 80 even during regular inspection, it is not possible to insert a pressure sensor inside the piping of the HNCW system 80. Therefore, like the temporary pressure sensor PK7-1 attached to the TSW system 70, the temporary pressure sensors PK8-1 and 8-2 are also installed by adhering strain sensors to the surface of the piping with an adhesive or the like.

[0175] (Enthalpy calculation program) The enthalpy calculation program Pg1 of the heat exchange performance evaluation system 200 calculates (evaluates) the enthalpy at these measurement locations (measurement points) based on the pressure values ​​and measured temperatures in each of the above-mentioned systems (TCW system 2000, TSW system 70, HNCW system 80).

[0176] In the case of the TCW system 2000 shown in FIG. 10, the enthalpy calculation program Pg1 calculates the enthalpy H at each temperature measurement point of the thermometer T6-1, the thermometer TK6-1, and the thermometer TK6-2 using each of the following equations (46) to (48). 6-1 , Enthalpy HK 6-1 , and enthalpy HK 6-2 Rate the following.

[0177] H 6-1 =st_HPT(P 6-1 ,T 6-1 )...Equation (46) HK 6-1 =st_HPT(P 6-1 ,T.K. 6-1 )...Equation (47) HK 6-2 =st_HPT(P 6-1 ,T.K. 6-2 )...Equation (48)

[0178] In the above formula (46) to formula (48), "P 6-1 " indicates the pressure value measured by the pressure gauge P6-1 provided near the outlet of the TCW pump 61 (see FIG. 10), and "T 6-1 " indicates the temperature measured by the thermometer T6-1 installed near the outlet of the three-way valve 63. 6-1" indicates the temperature measured by the temporary temperature sensor TK6-1 installed near the inlet of the TCW heat exchanger 62, and "TK 6-2 " indicates the temperature measured by the temporary temperature sensor TK6-2 installed near the outlet of the TCW heat exchanger 62.

[0179] In the case of the TSW system 70 shown in FIG. 12, the enthalpy calculation program Pg1 calculates the enthalpy H at each temperature measurement point of the thermometer T7-1 and the thermometer T7-2 by using the following formulas (49) and (50), respectively. 7-1 and enthalpy HK 7-2 Rate the following.

[0180] H 7-1 =st_HPT(P 7-0 ,T 7-1 )...Equation (49) H 7-2 =st_HPT(PK 7-1 ,T 7-2 )...Equation (50)

[0181] In the above formula (49), "P 7-0 " indicates atmospheric pressure, "PK 7-1 " indicates the pressure value measured by the temporary sensor PK-1 installed near the outlet of the auxiliary pump 72. 7-1 " indicates the temperature measured by the thermometer T7-1 installed near the water intake pit 71, and "T 7-2 " indicates the temperature measured by the thermometer T7-2 installed on the path connecting the TCW heat exchanger 74 and the water discharge pit 75.

[0182] In the case of the HNCW system 80 shown in FIG. 13, the enthalpy calculation program Pg1 calculates the enthalpy H at each temperature measurement point of the thermometer T8-1 and the thermometer T8-2 by using the following formulas (51) and (52). 8-1 and enthalpy HK 8-2 Rate the following.

[0183] H 8-1 =st_HPT(PK 8-1 ,T 8-1 )...Equation (51) H 8-2 =st_HPT(PK 8-2 ,T 8-2 )...Equation (52)

[0184] In the above formula (51) and formula (52), "PK 8-1 " indicates the pressure value measured by the temporary pressure sensor PK8-1 installed near the inlet of the HNCW cold water pump 81, and "PK 8-2 " indicates the pressure value measured by the temporary pressure sensor PK8-2 installed near the outlet of the HNCW cold water pump 81. 8-1 " indicates the temperature measured by the thermometer T6-1 installed near the inlet of the HNCW cold water pump 81, and "T 8-2 " indicates the temperature measured by the thermometer T8-2 provided on the output side of the HNCW refrigerator 82.

[0185] (Pump flow rate calculation program) The pump flow rate calculation program Pg2 of the heat exchange performance evaluation system 200 calculates the pump discharge flow rate in each system (TCW system 2000, TSW system 70, HNCW system 80) from the pump head in each system.

[0186] In the case of the TCW system 2000 shown in FIG. 10, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the TCW pump 61 (see FIG. 10) using the following equation (53): 6-1 Rate the following.

[0187] F 6-1 =pump_QH(P 6-1 -ρg(L 6-1 -L 6-0 ))...Equation (53)

[0188] In the above formula (53), "L 6-0 " indicates the installation height of the TCW pump 61, and "L 6-1 " indicates the water level of the surge tank 66 measured by a level gauge L6-1 installed near the surge tank 66. 6-1 " indicates the pressure value measured by the pressure gauge P6-1 installed near the outlet of the TCW pump 61.

[0189] In the case of the TSW system 70 shown in FIG. 12, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the auxiliary pump 72 using the following equation (54): 7-1 Rate the following.

[0190] F 7-1 =pump_QH(PK 7-1 +ρgH)...Equation (54)

[0191] In the above formula (54), "H" represents the height difference between the water level of the water intake pit 71 and the installation level of the auxiliary pump 72, and "PK 7-1 " indicates the pressure value measured by the temporary pressure sensor PK7-1 provided near the outlet of the auxiliary pump 72.

[0192] In the case of the HNCW system 80 shown in FIG. 13, the pump flow rate calculation program Pg2 calculates the discharge flow rate F of the HNCW cold water pump 81 using the following equation (55): 8-1 Rate the following.

[0193] F 8-1 =pump_QH(PK 8-1 -PK 8-2 )...Equation (55)

[0194] In the above formula (55), "PK 8-1 " indicates the pressure value measured by the temporary pressure sensor PK8-1 installed near the inlet of the HNCW cold water pump 81, and "PK 8-2 " indicates the pressure value measured by the temporary pressure sensor PK8-2 provided near the outlet of the HNCW chilled water pump 81.

[0195] (Heat load calculation program) The heat load calculation program Pg3A of the TCW connected system of the heat exchange performance evaluation system 200 calculates (evaluates) the heat load (amount of exchanged heat) in each system using the enthalpy calculated by the enthalpy calculation program Pg1 and the discharge flow rate (heat transport water flow rate) output by the pump flow rate calculation program Pg2.

[0196] In the case of the TSW system 70 shown in FIG. 12, the heat load calculation program Pg3A for the TCW-connected system calculates the heat exchange amount Q of the TCW heat exchanger 74 using the following equation (56): 7 Rate the following.

[0197] Q 7 =F 7-1 ×(H 7-2 -H 7-1 )-QTSW-P...Formula (56)

[0198] In the above formula (56), "QTSW-P" is the discharge flow rate of the auxiliary pump 72, which is the "discharge flow rate F 7-1 4 shows the shaft power of the auxiliary pump 72 when

[0199] In the case of the HNCW system 80 shown in FIG. 13, the heat load calculation program Pg3A for the TCW-connected system calculates the heat exchange amount Q of the HNCW refrigerator 82 using the following equation (57): 8 Rate the following.

[0200] Q 8 =F 8-1 ×(H 8-2 -H 8-1 )-QHNCW-P...Formula (57)

[0201] In the above formula (57), "QHNCW-P" is the discharge flow rate of the HNCW cold water pump 81, which is "discharge flow rate F 8-1 The shaft power of the HNCW chilled water pump 81 is shown in the case of "

[0202] (Heat exchange and temperature estimation program) The heat exchange amount and temperature estimation program Pg4 of the heat exchange performance evaluation system 200 calculates the heat exchange amount (flow rate of passing water) and the outlet temperature in the TCW system 2000 using the enthalpy evaluated by the enthalpy calculation program Pg1, the heat transport water flow rate evaluated by the pump flow rate calculation program Pg2, and the amount of exchanged heat output by the heat load calculation program Pg3A of the TCW connected system. The calculation procedure is the same as in the first embodiment.

[0203] 14 is a diagram showing an example of the heat transfer water flow rate and the outlet temperature evaluated by the heat transfer amount and temperature estimation program Pg4. As shown in FIG. 14, the heat transfer water flow rate output from the heat transfer amount and temperature estimation program Pg4 is the heat transfer water flow rate FP 6-1 -Heat water flow rate FP 6-3 Heat transport water flow rate FP 6-1 corresponds to the water flow rate of the TCW heat exchanger 62, and the heat transport water flow rate FP 6-2 corresponds to the water flow rate of the HNCW refrigerator 64, and the heat transport water flow rate FP 6-3 corresponds to the water flow rate of other load 65.

[0204] In addition, the outlet temperature output from the heat exchange amount and temperature estimation program Pg4 is, as shown by the dashed line in FIG. 14, the outlet temperature TP 6-1 and outlet temperature TP 6-2 The outlet temperature TP 6-1 corresponds to the outlet temperature of the TCW heat exchanger 62, and the outlet temperature TP 6-2 corresponds to the outlet temperature of the HNCW chiller 64. The water flow rate FP6-3 of the other loads 65 is evaluated at the design value.

[0205] (Mass Balance and Energy Balance Correction Program) As described in the first embodiment, the data measured by the instrument contains random errors, bias errors, etc., and the instrument drift occurs due to deterioration over time. In addition, since the temporary temperature sensor is attached to the surface of the pipe, when the difference between the outside air temperature and the fluid temperature inside the pipe becomes large and heat is dissipated from the pipe, the deviation between the pipe surface temperature measured by the temporary temperature sensor and the fluid temperature inside the pipe becomes a non-negligible value.

[0206] In addition, since the temporary pressure sensor estimates pressure from the amount of strain in the pipe, if the pipe undergoes thermal expansion due to the influence of the ambient temperature, the thermal expansion will cause measurement errors in the fluid pressure inside the pipe. Therefore, it is difficult to monitor the condition of the heat exchanger and the pump by directly using the measurement value of the temporary sensor.

[0207] The mass balance and energy balance correction program Pg5 corrects the measured values ​​by the existing sensors and the temporary sensors and the evaluation values ​​by each program based on the laws of conservation of mass and energy in the TCW system 2000. The correction equations used for the correction and the deterioration evaluation method for the heat exchanger and the pump are the same as those in the first embodiment described above. The constraint equation based on the law of conservation of mass for TCW 2000 is as follows:

[0208] F 6-1 =FP 6-2 +FP 6-3 ...Formula (58)

[0209] The constraint equation based on the law of conservation of energy for TCW 2000 is as follows:

[0210] C*TK 6-1 *F 6-1 =C*TP 6-2 *FP 6-2 +QTCW-P...Formula (59) C*TK 6-2 *FP 6-1 =C*TP 6-1 *FP 6-1 ...Formula (60) C*(TK 6-1 -T.K. 6-2 )*FP 6-1 =C*(TK 6-1 -T6-1)*F 6-1 ...Formula (61)

[0211] In the above formulas (59)-(61), "C" represents the constant pressure specific heat of fresh water flowing through the TCW system 2000. "QTCW-P" in the above formula (59) represents the discharge flow rate of the TCW pump 61 (see FIG. 10) equal to "discharge flow rate F 6-1 4 shows the shaft power of the TCW pump 61 when

[0212] By solving the correction equation (30) described in the first embodiment under the constraint condition equations (58) to (61), the influence of the instrument error or the instrument drift on the evaluation value is minimized. In addition, the mass balance and energy balance correction program Pg5 can quantitatively evaluate the deterioration states of the TCW pump 61 and each heat exchanger of the TCW system 2000, which affect the heat exchange performance of the TCW system 2000, based on the corrected deterioration coefficient D' in the correction equation (30).

[0213] In order to further improve the accuracy of detecting the deterioration state of the TCW pump 61 and the deterioration state of each heat exchanger, which affect the heat exchange performance of the TCW system 2000, the mass balance and energy balance correction program Pg5 may add, as constraints, the calculation formulas (56)-(57) for calculating the amount of heat exchanged by each heat load, in addition to the above formulas (58)-(61).

[0214] According to the above-mentioned second embodiment, it is possible to monitor the states of the heat exchangers and pumps of the TCW system 2000 while minimizing the effects of instrument errors and instrument drifts by using measured values ​​from existing sensors and a minimum number of temporary sensors. Furthermore, according to this embodiment, the manager of the nuclear power plant, etc., can perform rational maintenance of the TCW system equipment that minimizes the periodic inspection interval based on the results of grasping the states of the heat exchangers and pumps of the TCW system 2000.

[0215] Furthermore, according to the second embodiment described above, based on the heat exchanger and pump deterioration state list 104, the instrument drift state list 105, and the recommended inspection timing 106 for deteriorated equipment, which are output from the heat exchanger performance evaluation system 200, and the overall regular inspection plan, the manager of the nuclear power plant or the like can determine rational maintenance timing, maintenance method, and the like for the TCW system equipment that minimizes the regular inspection period.

[0216] <Computer hardware configuration> Next, the hardware configuration of the terminal device TD for realizing each function of the heat exchange performance evaluation system 100 shown in FIG. 2 and the heat exchange performance evaluation system 200 shown in FIG. 11 will be described with reference to FIG.

[0217] Fig. 15 is a block diagram showing an example of the hardware configuration of the terminal device TD. The calculator 500 shown in Fig. 14 is hardware used as a so-called computer.

[0218] The computer 500 includes a control unit 510, a non-volatile storage 520, a display unit 530, an operation input unit 540, and a communication I / F (Interface) 550, which are all connected to a bus B.

[0219] The control unit 510 includes a CPU (Central Processing Unit) 511, a ROM (Read Only Memory) 512, and a RAM (Random Access Memory) 513. The CPU 511 reads out program code of software (applications) for implementing each function according to this embodiment from the ROM 512, expands it in the RAM 513, and executes it. The computer 500 may include a processing device such as an MPU (Micro-Processing Unit) instead of the CPU 511, or the CPU 511 and an MPU may be used in combination in the computer 500. Variables, parameters, and the like generated during the arithmetic processing are temporarily written in the RAM 513.

[0220] The non-volatile storage 520 may be, for example, a hard disk drive (HDD), a solid state drive (SSD), a flexible disk, an optical disk, a magneto-optical disk, a CD-ROM, a CD-R, a non-volatile memory card, etc. In addition to an operating system (OS) and various parameters, programs for operating the computer 500, etc. are recorded in this non-volatile storage 520. The programs may be stored in the ROM 512.

[0221] The program is stored in the form of a computer-readable program code, and the CPU 511 sequentially executes operations according to the program code. In other words, the ROM 512 or the non-volatile storage 520 is used as an example of a computer-readable non-transitory recording medium that stores a program executed by a computer.

[0222] The functions of each program of the heat exchange performance evaluation system 100 and the heat exchange performance evaluation system 200 are realized by the CPU 511 reading out the corresponding program code from the ROM 512 or the non-volatile storage 520, expanding it in the RAM 513, and executing it.

[0223] The display unit 530 is, for example, a monitor configured with an LCD (Liquid Crystal Display) or the like, and displays the results of processing performed by the computer 500, and the like. The operation input unit 540 is configured with, for example, a keyboard, a mouse, a touch sensor, etc., and generates an operation signal according to an operation by a user and supplies the operation signal to the CPU 511. Display unit 530 and operation input unit 540 may be integrated into one unit as a touch panel.

[0224] The communication I / F 550 may be, for example, a network interface card (NIC), and may transmit and receive various types of data to and from other devices connected via the network N.

[0225] In the above-described embodiments, the heat exchange performance evaluation system 100 and the heat exchange performance evaluation system 200 evaluate the states of all the heat exchangers and pumps constituting the load-side system connected to the system, but the present invention is not limited to this. For example, an operation may be performed in which the equipment or items to be evaluated are changed according to the operating state of the load-side system. For example, immediately after the fuel exchange of the RCW system 1000, the heat exchange rate of the FPC heat exchanger 5 (see FIG. 1) of the RCW system and the pump performance of the RCW pump 1 may be evaluated, and the performance of the other heat exchangers may use the evaluation values ​​evaluated previously. By performing such an operation, it is possible to perform a highly accurate performance evaluation according to the operating state.

[0226] In the above-mentioned first embodiment, an example was given in which the state of the heat exchanger and pump of the RCW system 1000 was monitored using the measured values ​​from the existing sensors, but the present invention is not limited to this. A plurality of external temporary temperature sensors may be installed near the inlet and outlet of the RCW heat exchanger 2 of the RCW system 1000, respectively, to detect minute changes in the amount of heat exchanged by the RCW heat exchanger 2. With this configuration, it becomes possible to detect the leakage of heat to the seawater side, which is the most important monitoring item.

[0227] Furthermore, each of the above-described embodiments provides a detailed and specific description of the configuration of the device and system in order to clearly explain the present invention, and is not necessarily limited to having all of the configurations described.

[0228] In addition, the control lines or information lines indicated by solid arrows in Figures 2 and 11 are those considered necessary for explanation, and do not necessarily show all control lines or information lines in the product. In reality, it can be considered that almost all components are connected to each other.

[0229] In addition, in this specification, the processing steps describing chronological processing include not only processing that is performed chronologically in the order described, but also processing that is not necessarily performed chronologically but is performed in parallel or individually (for example, parallel processing or processing by objects).

[0230] Furthermore, each component of the heat exchange performance evaluation system 100, 200 according to each embodiment of the present invention described above may be implemented in any hardware as long as each hardware can transmit and receive information to and from each other via a network. Also, the processing performed by a certain processing unit may be realized by one piece of hardware, or may be realized by distributed processing by multiple pieces of hardware. [Explanation of symbols]

[0231] 1...RCW pump, 2...RCW heat exchanger, 3...HECW chiller, 4...RHR heat exchanger, 5...FPC heat exchanger, 6...CUW non-regenerative heat exchanger, 7...station hot water system heat exchanger, 10...RSW system, 12...RSW pump, 20...HECW system, 22...HECW pump, 30...RHR system, 33...RHR pump, 40...FPC system, 43...FPC pump, 50...CUW system, 51...CUW regenerative heat exchanger, 52...CUW pump, 61...TCW pump, 62...TCW heat exchanger, 64...HNCW chiller, 70...TSW system, 72...auxiliary pump, 74...TCW heat exchanger, 80...HNCW system, 81...HNCW chilled water pump, 82...HNCW chiller, 100...RCW system heat exchanger performance evaluation system (heat exchanger performance evaluation system), 1 04...Deterioration state list, 105...Drift state list, 106...Recommended inspection period, 200...TCW system heat exchange performance evaluation system (heat exchange performance evaluation system), 205...Deterioration state list, 206...Drift state list, 207...Recommended inspection period, 100...RCW system, 200...TCW system, Pg1...Enthalpy calculation program, Pg2...Pump flow rate calculation program, Pg3, Pg3A...Heat load calculation program, Pg4...Temperature estimation program, Pg5...RCW system mass balance and energy balance correction program, Pg5A...TCW system mass balance and energy balance correction program, PK7-1, PK8-1, PK8-2...Temporary pressure sensor, TK6-1, TK6-2...Temporary temperature sensor

Claims

1. A status monitoring device for an auxiliary cooling system that cools a nuclear reactor auxiliary or an auxiliary cooling system that cools a turbine auxiliary, an exchange heat amount calculation unit that calculates an exchange heat amount in a heat exchanger of the auxiliary cooling system based on measurement data by an instrument provided in the auxiliary cooling system and measurement data by an instrument provided in another system on a load side connected to the auxiliary cooling system; a water flow rate and outlet temperature estimation unit that estimates a water flow rate of a heat exchanger of the auxiliary cooling system and an outlet temperature of the cold water from the heat exchanger based on an inlet temperature of the cold water input to a pump of the auxiliary cooling system and the amount of heat exchanged; and a correction unit that corrects the amount of heat exchanged, the amount of water flow, and the outlet temperature based on consistency between the mass balance and the energy balance of the amount of heat exchanged, the amount of water flow, and the outlet temperature. Auxiliary cooling system status monitoring device.

2. the gauges include a temperature gauge and / or a pressure gauge installed near the heat exchanger or the pump, and a level gauge installed near the pump; an enthalpy calculation unit that calculates a fluid enthalpy of the cold water flowing through an installation location of the thermometer based on the temperature measured by the thermometer and the pressure value measured by the pressure gauge, or based on the measured temperature and the water level of the pump measured by the level gauge; a pump flow rate calculation unit that calculates a discharge flow rate of the pump based on a head of the pump that is determined based on a pressure value measured by the pressure gauge provided near the pump, The heat exchange amount calculation unit calculates the heat exchange amount based on the fluid enthalpy calculated by the enthalpy calculation unit and the discharge flow rate of the pump calculated by the pump flow rate calculation unit. The condition monitoring device for an auxiliary cooling system according to claim 1 .

3. The pump flow rate calculation unit calculates the discharge flow rate of the pump using a characteristic curve that indicates a relationship between the head of the pump and the discharge flow rate of the pump. The condition monitoring device for an auxiliary cooling system according to claim 2.

4. The water flow rate and outlet temperature estimation unit estimates the water flow rate of the heat exchanger of the auxiliary cooling system and the outlet temperature of the cold water from the heat exchanger of the auxiliary cooling system by using simultaneous equations based on a first heat balance equation related to the heat exchange amount on the cooling side of the heat exchanger of the auxiliary cooling system, a second heat balance equation related to the heat exchange amount on the load side connected to the heat exchanger of the auxiliary cooling system, and a performance equation of the heat exchanger of the auxiliary cooling system. The condition monitoring device for an auxiliary cooling system according to claim 3.

5. The mass balance is represented by a constraint equation based on the law of conservation of mass in the auxiliary cooling system, and the energy balance is represented by a constraint equation based on the law of conservation of energy in the auxiliary cooling system. The condition monitoring device for an auxiliary cooling system according to claim 4.

6. The correction unit performs the correction by multiplying the thermal conductivity of the heat exchanger of the auxiliary cooling system and the QH characteristic of the pump of the auxiliary cooling system shown in the characteristic curve by a deterioration coefficient. The condition monitoring device for an auxiliary cooling system according to claim 3.

7. The auxiliary cooling system is an auxiliary cooling system that cools the reactor auxiliary, The load-side other systems connected to the auxiliary cooling system are the reactor auxiliary cooling seawater system, the ventilation and air conditioning auxiliary emergency cooling water system, the residual heat removal system, the fuel pool cooling and purification system, the reactor coolant purification system, and the in-house hot water system. The status monitoring device for an auxiliary cooling system according to any one of claims 1 to 6.

8. the accessory cooling system is an accessory cooling system that cools the turbine accessory, The other systems on the load side connected to the auxiliary cooling system are a turbine auxiliary cooling seawater system and a regular air conditioning equipment chilled water system. The status monitoring device for an auxiliary cooling system according to any one of claims 2 to 6.

9. The auxiliary cooling system further includes additional temperature sensors installed on a surface of an inlet pipe and a surface of an outlet pipe of the heat exchanger, The enthalpy calculation unit calculates the fluid enthalpy based on the surface temperature of the pipe measured by the additional temperature sensor. The condition monitoring device for an accessory cooling system according to claim 8.

10. The auxiliary cooling seawater system further includes a strain sensor installed on a surface of an outlet pipe of a seawater pump of the auxiliary cooling seawater system, The pump flow rate calculation unit calculates a fluid pressure inside the pipe based on the strain of the pipe measured by the strain sensor, and calculates a discharge flow rate of the pump based on the calculated fluid pressure. The condition monitoring device for an accessory cooling system according to claim 8.

11. The cooling system further includes a strain sensor installed on a surface of an inlet pipe and a surface of an outlet pipe of the cooling water pump of the cooling water system of the normal air conditioner, The pump flow rate calculation unit calculates a fluid pressure inside the pipe based on the strain of the pipe measured by the strain sensor, and calculates a discharge flow rate of the pump based on the calculated fluid pressure. The condition monitoring device for an accessory cooling system according to claim 8.

12. A status monitoring method for an auxiliary cooling system for cooling a nuclear reactor auxiliary or an auxiliary cooling system for cooling a turbine auxiliary, comprising: a step of an exchange heat amount calculation unit calculating an exchange heat amount in a heat exchanger of the auxiliary cooling system based on measurement data by an instrument provided in the auxiliary cooling system and measurement data by an instrument provided in another system on a load side connected to the auxiliary cooling system; a water flow rate and outlet temperature estimation unit estimating a water flow rate of a heat exchanger of the auxiliary cooling system and an outlet temperature of the cold water from the heat exchanger based on an inlet temperature of the cold water input to a pump of the auxiliary cooling system and the amount of heat exchanged; and a correction unit correcting the amount of heat exchanged, the amount of water flow, and the outlet temperature based on consistency between the amount of heat exchanged, the amount of water flow, and the outlet temperature and a mass balance and an energy balance. A method for monitoring the condition of an auxiliary cooling system.

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