WO2017018082A1 - 凝縮器および冷却システムと運転方法 - Google Patents
凝縮器および冷却システムと運転方法 Download PDFInfo
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- WO2017018082A1 WO2017018082A1 PCT/JP2016/067503 JP2016067503W WO2017018082A1 WO 2017018082 A1 WO2017018082 A1 WO 2017018082A1 JP 2016067503 W JP2016067503 W JP 2016067503W WO 2017018082 A1 WO2017018082 A1 WO 2017018082A1
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- condenser
- cooling system
- refrigerant
- temperature
- flow rate
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D9/00—Devices not associated with refrigerating machinery and not covered by groups F25D1/00 - F25D7/00; Combinations of devices covered by two or more of the groups F25D1/00 - F25D7/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/04—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid
- F28B9/06—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid with provision for re-cooling the cooling water or other cooling liquid
-
- G—PHYSICS
- G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
- G21C—NUCLEAR REACTORS
- G21C9/00—Emergency protection arrangements structurally associated with the reactor, e.g. safety valves provided with pressure equalisation devices
- G21C9/004—Pressure suppression
-
- G—PHYSICS
- G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
- G21C—NUCLEAR REACTORS
- G21C9/00—Emergency protection arrangements structurally associated with the reactor, e.g. safety valves provided with pressure equalisation devices
- G21C9/004—Pressure suppression
- G21C9/012—Pressure suppression by thermal accumulation or by steam condensation, e.g. ice condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
- F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
- F28D7/085—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1615—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E30/00—Energy generation of nuclear origin
- Y02E30/30—Nuclear fission reactors
Definitions
- the present invention relates to a condenser for allowing a refrigerant to flow in a heat transfer tube and condensing a condensable gas on the outer surface of the heat transfer tube, a cooling system using the same, and an operation method thereof.
- the number and length of heat transfer tubes are determined for the required heat removal.
- the heat transfer coefficient decreases as the concentration of the non-condensable gas increases. Therefore, it is necessary to increase the number and length of heat transfer tubes for a certain amount of heat removal.
- the condenser is designed for a certain non-condensable gas concentration.
- the amount of heat removal can be adjusted by the flow rate of the refrigerant.
- a pipe through which the refrigerant passes is branched in front of the heat exchanger, and the pipe is arranged on one of the branched pipes.
- the distribution amount of the refrigerant to each heat exchanger is adjusted by the flow rate adjusting valve.
- the heat removed by the condenser is carried to an external heat exchanger for releasing to the outside.
- the refrigerant temperature between the condenser outlet and the external heat exchanger inlet rises.
- the cooling system compatible with the high temperature, and the heat transfer area of the external heat exchanger is increased, so that the external heat exchanger is increased in size and costs.
- the cooling system contains a non-condensable gas
- a driving force is generated due to the difference between the gas density inside and outside the condenser, and natural circulation of the mixed gas occurs.
- this driving force is increased, a large amount of mixed gas flows into the condenser, and a heat removal amount can be ensured.
- the present invention has been made in view of the above, a cooling system capable of adjusting the heat removal amount in the condenser and maintaining the temperature of the refrigerant flowing into the heat exchanger below a specified temperature to suppress an increase in cost, and natural circulation
- An object of the present invention is to realize a method of operating a condenser and a cooling system that can increase the inflow rate of the air-fuel mixture.
- the present invention is configured as follows.
- a heat exchanger In the cooling system, a heat exchanger, a condenser that condenses condensable gas including non-condensable gas, an inlet side pipe that connects a refrigerant outlet of the heat exchanger and a refrigerant inlet of the condenser, and the condensation
- An outlet side pipe connecting the refrigerant outlet of the condenser and the refrigerant inlet of the heat exchanger, a bypass pipe branching from the branch part of the inlet side pipe near the refrigerant inlet of the condenser from the inlet side pipe, Refrigerant inlet of the heat exchanger is connected to the outlet side pipe and the bypass pipe, the refrigerant flowing out from the refrigerant outlet of the condenser and the refrigerant supplied from the bypass pipe are mixed, and the refrigerant is supplied to the heat exchanger via the outlet side pipe.
- a flow rate adjusting mechanism that adjusts the amount of refrigerant flowing into the refrigerant inlet
- a condenser that is disposed in a reactor containment vessel in which the nitrogen concentration changes with time in a severe accident and condenses condensable gas containing non-condensable gas, a casing whose upper and lower surfaces are opened, and the casing
- a plurality of heat transfer tubes arranged in the upper space and through which refrigerant flows in and out, and a lower chimney space in which the heat transfer tubes are not disposed is formed in the lower space in the casing.
- thermometer for measuring the refrigerant temperature in the outlet side pipe is arranged, and when the temperature measured by the thermometer is higher than the target temperature, the inlet side flow rate adjusting valve is When the temperature measured by the thermometer is lower than the target temperature, the inlet side flow adjustment valve is opened and the flow adjustment valve of the bypass pipe is throttled. Control.
- the cooling system capable of adjusting the heat removal amount in the condenser and maintaining the temperature of the refrigerant flowing into the heat exchanger below a specified temperature to suppress an increase in cost, and increasing the inflow flow rate of air-fuel mixture by natural circulation Possible condenser and cooling system operating methods can be realized.
- FIG. 1 is a schematic diagram showing a configuration example when the cooling system according to the first embodiment of the present invention is applied to a boiling water nuclear power plant.
- the cooling system releases the condenser 1 installed in the reactor containment vessel 50 and the heat removed by the condenser 1 to the outside.
- an external heat exchanger 8 externally pass the refrigerant flowing out from the refrigerant outlet of the condenser 1 and the inlet side pipe 2 that carries the refrigerant (cooling water) from the refrigerant outlet of the heat exchanger 8 to the refrigerant inlet of the condenser 1. It is connected to the outlet side pipe 3 that carries to the refrigerant inlet of the heat exchanger 8.
- a cooling water pump 7 for circulating the refrigerant through the inlet side pipe 1 and the outlet side pipe 3 is installed in the outlet side pipe 3.
- the inlet side pipe 2 is provided with a bypass pipe 12 that branches off before the condenser 1.
- the bypass pipe 12 is connected to a mixer (mixer) 4 provided in the outlet side pipe 3.
- a flow rate adjusting valve (condenser inlet side flow rate adjusting valve) 5 for adjusting the flow rate of the refrigerant to the condenser 1 is installed.
- the bypass pipe 12 is provided with a flow rate adjustment valve (bypass side flow rate adjustment valve) 6 for adjusting the flow rate of the refrigerant in the bypass pipe 12.
- a cooling water pump 7 is installed between the mixer 4 and the external heat exchanger 8 in the outlet side pipe 3, and between the cooling water pump 7 and the external heat exchanger 8, A thermometer 21 for measuring the refrigerant temperature is installed.
- Seawater is drawn into the external heat exchanger 8 as a refrigerant by the cooling water supply pump 9, the heat carried from the condenser 1 is transmitted to the seawater, and finally the heat removed is released to the sea.
- the reactor containment vessel 50 of the boiling water nuclear power plant is filled with nitrogen during normal operation.
- the steam generated by the decay heat is transferred to the containment vessel 50.
- the pressure in the storage container 50 increases. In order to avoid the pressure rising above the design pressure and damaging the containment vessel 50, a means for condensing the generated steam or venting the steam from the containment vessel 50 is required.
- the condenser 1 in order to prevent the overpressure of the containment vessel 50, it is reasonable to design the condenser 1 under the condition that the heat transfer performance is most deteriorated under the highest possible nitrogen concentration environment.
- the heat transfer tube length of the condenser 1 is determined so that the refrigerant (cooling water) temperature at the outlet of the condenser 1 satisfies the inlet temperature specification of the external heat exchanger 8.
- the nitrogen concentration of the mixed gas in the containment vessel 50 varies depending on the inflow / condensation of steam and the status of nitrogen isolation.
- the nitrogen concentration of the mixed gas in the containment vessel 50 decreases, the heat transfer inhibition effect by the non-condensable gas disappears and the condensation heat transfer coefficient increases.
- the condensation heat transfer rate increases, the amount of heat transferred to the cooling water of the condenser 1 increases, and the cooling water temperature at the outlet of the condenser 1 increases.
- the inlet side pipe 2 of the condenser 1 is branched and a bypass pipe 12 is installed, and is connected to the outlet side pipe 3 by the mixer 4.
- a flow rate adjusting valve 5 is installed in the inlet side pipe 2, and a flow rate adjusting valve 6 is installed in the bypass pipe 12.
- the flow rate is determined by the following equation (1) so that the heat removal amount at the assumed maximum nitrogen concentration becomes the specification temperature of the external heat exchanger 8.
- Q 0 m 0 c p ( T out -T in) ⁇ (1)
- the amount of heat removal decreases and the cooling water outlet temperature rises.
- the amount of cooling water flowing into the condenser 1 is reduced by reducing the opening of the inlet-side flow rate adjustment valve 5 to condense. The amount of heat removal from the vessel 1 can be controlled.
- the cooling water temperature is condensed.
- the temperature reaches 100 ° C. before being discharged from the vessel 1, and after reaching 100 ° C., there is no temperature difference, so heat removal is not performed and the effective heat transfer area is reduced.
- Q is quantity of heat removed (W)
- m is coolant flow rate (kg / s)
- the c p the specific heat (J / kgK)
- the heat removal amount can be controlled by the cooling water flow rate.
- the cooling water temperature at the outlet of the condenser 1 rises to the temperature in the storage container 50.
- the cooling water of the outlet side pipe 3 whose temperature has increased is mixed with the low-temperature cooling water that has passed through the bypass pipe 12 by the mixer 4, and the cooling water is lowered to a temperature that satisfies the specifications of the external heat exchanger 8.
- FIG. 2 is a graph showing the temperature change of the cooling water from the heat transfer tube inlet of the condenser 1 to the outlet of the mixer 4, the vertical axis shows the cooling water temperature, and the horizontal axis shows the position of the cooling water.
- the solid line indicates the change in cooling water temperature when the nitrogen concentration decreases
- the alternate long and short dash line indicates the change in cooling water temperature when the nitrogen concentration is maximum.
- the condenser 1 is designed to be equal to or lower than the limit temperature of the external heat exchanger 8 when the nitrogen concentration becomes maximum.
- the heat transfer rate is improved, so that the temperature rise rate of the cooling water is increased.
- the cooling water temperature reaches 100 ° C., which is the saturation temperature in the containment vessel 50, there is no temperature difference, so heat transfer is not performed, and the cooling water temperature becomes constant at 100 ° C.
- the cooling water that has risen to 100 ° C. is mixed with the low-temperature cooling water supplied from the bypass pipe 12 by the mixer 4 and falls below the limit temperature of the external heat exchanger 8.
- the cooling water whose temperature has been lowered below the specification temperature of the external heat exchanger 8 is cooled by exchanging heat with seawater in the external heat exchanger 8 and supplied to the condenser 1 again. Seawater to which heat is transmitted from the cooling water is returned to the sea, and the heat in the storage container 50 is released to the sea.
- the temperature of the cooling water flowing into the external heat exchanger 8 is measured by the thermometer 21.
- the opening degree of the flow rate adjusting valves 5, 6 is adjusted, the amount of cooling water supplied to the condenser 1, and the cooling supplied to the mixer 4 from the bypass pipe 12.
- the water flow rate is adjusted.
- the opening adjustment of the flow rate adjusting valves 5 and 6 is performed by, for example, monitoring the temperature measured by the thermometer 21 at the control center, and adjusting the opening degree of the flow rate adjusting valves 5 and 6 from the control center to the operator according to the monitored temperature. It is also possible to provide a valve opening degree driving mechanism for the flow rate adjusting valves 5 and 6 and to configure the valve opening degree driving mechanism to operate according to a command from the control center. .
- the amount of cooling water to the condenser 1 is adjusted by the flow rate adjusting valve 5 to condense.
- low-temperature cooling water is supplied from the bypass pipe 12 to the mixer 4, and mixed with the high-temperature cooling water flowing out from the condenser 1 by the mixer 4, so that the cooling water temperature is externally heated. It is comprised so that it may fall below to the specification temperature of the exchanger 8.
- FIG. 3 is a schematic diagram showing a configuration example when the cooling system according to the second embodiment of the present invention is applied to a boiling water nuclear power plant.
- the configuration different from the first embodiment in the second embodiment is that a pressurizer (water tank) 10 that pressurizes the entire cooling system is installed in the inlet side pipe 2, and the other configurations are the same as the first embodiment. It has become.
- the containment vessel 50 is pressurized to atmospheric pressure or higher, and the temperature in the containment vessel 50 is assumed to exceed 100 ° C.
- the cooling water is circulated at atmospheric pressure, the cooling water that has reached 100 ° C. by heating with steam higher than 100 ° C. boils.
- the pressurizer 10 that pressurizes the entire cooling system is installed, and the pressure of the pressurizer 10 (the pressure of the gas in the pressurizer 10) is set higher than the design pressure of the containment vessel 50.
- the pressure of the pressurizer 10 (the pressure of the gas in the pressurizer 10) is set higher than the design pressure of the containment vessel 50.
- FIG. 4 is a graph showing the temperature change of the cooling water from the heat transfer tube inlet of the condenser 1 to the outlet of the mixer 4, the vertical axis shows the cooling water temperature, and the horizontal axis shows the position of the cooling water. Moreover, in FIG. 4, a continuous line shows the temperature change at the time of pressurizing cooling water, and a broken line shows the cooling water temperature change at the time of not pressurizing cooling water.
- the cooling water temperature rises to the temperature in the containment vessel 50 when pressurized by the pressurizer 10, and the cooling water pressure when not pressurized.
- the cooling water temperature rises to the saturation temperature of.
- the mixture is mixed with the low-temperature cooling water flowing from the bypass pipe 12 in the mixer 4 and the cooling water temperature falls below the limit temperature of the external heat exchanger 8, but when not pressurized, the temperature drop is small and the external heat exchanger The limit temperature of 8 may be exceeded.
- FIG. 5 is a graph showing the change in the enthalpy of the cooling water from the heat transfer tube inlet of the condenser 1 to the outlet of the mixer 4, the vertical axis shows the enthalpy of the cooling water, and the horizontal axis shows the position of the cooling water.
- the solid line shows the temperature change when the cooling water is pressurized
- the broken line shows the cooling water temperature change when the cooling water is not pressurized.
- FIG. 6 is a view showing a modification of the second embodiment shown in FIG.
- the example shown in FIG. 3 is an example in the case of applying a water tank as the pressurizer 10, but for adjusting the pressure between the mixer 4 and the cooling water pump 7 in the outlet side pipe 3 as shown in FIG. 6.
- a valve 11 may be installed. By reducing the valve opening of the pressure adjusting valve 11, the pressure loss at the valve 11 increases, and the range from the cooling water pump (circulation pump) 7 to the front of the valve 11 is increased by the pressure loss at the valve 11. be able to. However, a high-lift circulating pump that can compensate for the pressure loss is required.
- valve opening of the valve 11 can be fixed, an orifice may be installed in the outlet side pipe 3 between the mixer 4 and the cooling water pump 7 instead of the valve.
- effect According to the second embodiment, the same effect as that of the first embodiment can be obtained, and the mixer can be obtained by suppressing the boiling of the cooling water by pressurizing the cooling water higher than the pressure in the containment vessel 50. The effect that generation
- FIG. 7 is a schematic diagram showing a configuration example when the cooling system according to the third embodiment of the present invention is applied to a boiling water nuclear power plant.
- the third embodiment is different from the second embodiment in that the third embodiment has a calculation unit 23 to which the temperature detected by the thermometer 21 is input and a valve drive motor 51 that adjusts the valve opening degree of the flow rate adjustment valve 5. And a valve drive motor 60 that adjusts the valve opening degree of the flow rate adjusting valve 6, and the other configuration is the same as that of the second embodiment.
- pressurizer 10 is installed in the example shown in FIG. 7 as in the second embodiment, the pressurizer 10 can be omitted in the third embodiment.
- the change in the nitrogen concentration in the containment vessel 50 is difficult to predict when a non-uniform concentration distribution occurs, and as described above, the adjustment of the cooling water flow rate in the condenser 1 and the bypass pipe 12 flows into the external heat exchanger 8. It is better to monitor the temperature of the cooling water.
- the nitrogen concentration in the storage container 50 decreases and the heat removal amount of the condenser 1 increases, the temperature of the cooling water in the outlet side pipe 3 rises and the indicated value of the thermometer 21 increases.
- the temperature detected by the thermometer 21 is input to the calculation unit 23.
- the calculation unit 23 adjusts the flow rate of the inlet side pipe 2 via the signal cable 22.
- An opening adjustment signal is sent to the first drive motor 51 that adjusts the opening of the valve 5, and an opening adjustment signal is sent to the second drive motor 60 that adjusts the opening of the flow rate adjustment valve 6 of the bypass pipe 12.
- the drive motor 51 throttles the opening of the flow rate adjustment valve 5 according to the opening adjustment signal from the calculation unit 23, and the drive motor 60 opens the flow rate adjustment valve 6 of the bypass pipe 12 according to the opening adjustment signal from the calculation unit 23. Increase the degree.
- the cooling water temperature can be controlled below the specification temperature of the external heat exchanger 8.
- the temperature indication value of the thermometer 21 decreases (when it is lower than the specified temperature (target temperature)).
- the calculation unit 23 sends an opening degree adjustment signal to the drive motors 51 and 60, and the flow rate adjustment valve 5 of the inlet side pipe 2 is adjusted so that the temperature of the cooling water flowing into the external heat exchanger 8 does not exceed the specified temperature.
- the opening degree is increased, and the opening degree of the flow rate adjustment valve 6 of the bypass pipe 12 is reduced.
- thermometer 21 that measures the temperature of the cooling water in the outlet side pipe 3 between the mixer 4 and the external heat exchanger 8, the calculation unit 23, and the measurement of the thermometer 21.
- the inside of the containment vessel 50 is controlled by a control system including a signal cable 22 for transmitting a signal for adjusting the opening degree of the flow rate adjusting valves 5 and 6 according to values and drive motors 51 and 60 for driving the flow rate adjusting valves 5 and 6. Even if the nitrogen concentration of the refrigerant changes, the temperature of the cooling water flowing into the external heat exchanger 8 can be automatically controlled to be equal to or lower than the specification temperature of the external heat exchanger 8 to ensure the necessary heat removal amount in the condenser 1. it can.
- FIG. 8 is a schematic diagram showing the configuration of the condenser 1 applied to the cooling system according to the fourth embodiment of the present invention.
- the condenser 1 includes a plurality of heat transfer tubes (tubes through which refrigerant flows in and out) 32 arranged in the horizontal direction and the vertical direction, and a casing 31 that surrounds the heat transfer tubes 32 and is open at the top and bottom.
- a space (lower chimney) 43 in which the heat transfer tube 32 is not disposed is provided in a lower portion of 31.
- the upper and lower sides of the casing 31 are opened to form an upper surface opening 41 and a lower surface opening 42, and a lower chimney space 43 without a heat transfer pipe 32 through which cooling water flows is formed in the lower part of the casing 31.
- nitrogen and steam nitrogen has a higher density, and the higher the nitrogen concentration, the higher the density of the mixed gas.
- the lower surface opening 42 is provided and the lower surface of the casing 31 is opened so that the mixed gas in the casing 31 having a high density is smoothly discharged to the outside of the casing 31.
- the surrounding mixed gas flows into the condenser 1 from the upper surface opening 41.
- the upper surface of the casing is opened, the surrounding mixed gas smoothly flows into the condenser 1. Since the driving force generated by the density difference is small, the use of the casing 31 with the upper and lower surfaces open allows the pressure loss associated with the inflow / discharge of the mixed gas to be minimized and more mixed gas flows into the condenser 1. Can be made.
- the height of the lower chimney space 43 should be increased as much as possible with respect to the allowable dimensions of the installation location.
- the driving force increases, more mixed gas flows into the condenser 1. Since only the vapor of the mixed gas that has flowed in is condensed, the nitrogen concentration increases toward the bottom of the condenser. That is, the lower the heat transfer tube in the condenser, the lower the heat transfer amount due to the heat transfer inhibition effect of nitrogen.
- the amount of steam passing through the heat transfer tube per unit time increases, but the amount of condensation does not increase greatly, and therefore, an increase in the downward nitrogen concentration is suppressed. . For this reason, since steam can be condensed in a state where the nitrogen concentration is low in the lower heat transfer tube, the heat removal effect can be improved.
- the upper and lower surfaces of the casing 31 are openings, so that the mixed gas generated due to the density difference can flow smoothly and the lower chimney space 43 is installed.
- the driving force for natural circulation can be increased, and a larger amount of mixed gas can flow into the condenser 1.
- the heat removal effect of the condenser 1 can be improved.
- condenser 1 of the fourth embodiment of the present invention can also be applied to the cooling system according to the present invention.
- the flow rate adjusting valve 5 is arranged in the inlet side pipe 2 of the condenser 1 and the flow rate adjusting valve 6 is arranged in the bypass pipe 12.
- a configuration in which only one of the flow rate adjusting valve 5 and the flow rate adjusting valve 6 is used as the flow rate adjusting valve may be another embodiment of the present invention.
- the present invention can be applied not only to cooling in a reactor pressure vessel but also to an in-vessel cooling system in other manufacturing plants.
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Abstract
Description
(構成)
図1は、本発明の第1実施例に係る冷却システムを沸騰水型原子力プラントに適用した場合の一構成例を表す概要図である。
沸騰水型原子力プラントの原子炉格納容器50は、通常運転時には窒素が充填されている。炉心から発生する崩壊熱を除去する機能が喪失するような事故が発生した場合には、崩壊熱で発生した蒸気が格納容器50に移行する。格納容器50からの除熱量よりも崩壊熱量が大きい場合は、格納容器50の圧力は上昇していく。設計圧力を超えて圧力が上昇し格納容器50が破損するのを回避するため、発生した蒸気を凝縮させるか、格納容器50から蒸気をベントする手段が必要となる。
Q0=m0cp(Tout-Tin) ・・・(1)
Q=mcp(100-Tin) ・・・(2)
本第1実施例によれば、格納容器50内の窒素濃度が低下して凝縮器1での除熱量が増加する場合に、流量調整バルブ5により凝縮器1への冷却水量を調整して凝縮器1での除熱量を制御するとともに、バイパス配管12から低温の冷却水をミキサ4に供給して、凝縮器1から流出した高温の冷却水とミキサ4で混合させて冷却水温度を外部熱交換器8の仕様温度以下に低下させるように構成される。
(構成)
図3は、本発明の第2実施例に係る冷却システムを沸騰水型原子力プラントに適用した場合の一構成例を表す概要図である。
過酷事故時には、格納容器50は大気圧以上に加圧され、格納容器50内の温度は100℃超となると想定される。冷却水を大気圧で循環させた場合、100℃超の蒸気による加熱で100℃に到達した冷却水は沸騰する。
本第2実施例によれば、第1実施例と同様な効果を得ることができる他、冷却水を格納容器50内の圧力よりも高く加圧して冷却水の沸騰を抑制することにより、ミキサ4でのウォーターハンマー発生を防止することができるという効果が得られる。
(構成)
図7は、本発明の第3実施例に係る冷却システムを沸騰水型原子力プラントに適用した場合の一構成例を表す概要図である。
格納容器50内の窒素濃度の変化は、不均一な濃度分布が発生すると予測が難しく、上述したように、凝縮器1とバイパス配管12の冷却水流量の調整は外部熱交換器8へ流入する冷却水の温度を監視しながら行うのが良い。格納容器50内の窒素濃度が低下して、凝縮器1の除熱量が増加すると、出口側配管3内の冷却水温度が上昇し、温度計21の指示値が高くなる。
本発明の第3実施例によれば、ミキサ4から外部熱交換器8までの間の出口側配管3に冷却水の温度を測定する温度計21と、演算部23と、温度計21の計測値により流量調整バルブ5、6の開度を調整する信号を伝達する信号ケーブル22と、流量調整バルブ5、6を駆動する駆動モータ51、60とで構成された制御系により、格納容器50内の窒素濃度が変化しても、外部熱交換器8に流入する冷却水温度を外部熱交換器8の仕様温度以下に自動的に制御し、凝縮器1において必要な除熱量を確保することができる。
(構成)
図8は、本発明の第4実施例に係る冷却システムに適用する凝縮器1の構成を示す概略図である。
過酷事故時に格納容器50内に蒸気が流入すると、湿度が上昇しファン等の電動機器が使えなくなる可能性がある。また、蒸気を凝縮させて過圧を防止するため格納容器50内にスプレイを散布する場合もあり、電動機器の動作を期待しない凝縮器設計が望ましい。この場合、格納容器50内に設置される凝縮器1への混合ガスの流入は、自然循環力を利用することになる。
F=△ρ・g・h ・・・(3)
本発明の第4実施例によれば、ケーシング31の上面および下面を開口部とすることにより、密度差によって発生する混合ガスの鉛直方向の流れを円滑にでき、下部チムニ空間43を設置することにより、自然循環の駆動力を増加させ、より多くの混合ガスを凝縮器1内に流入させることができる。これにより、凝縮器1の除熱効果を向上することができる。
Claims (10)
- 熱交換器と、
非凝縮性ガスを含む凝縮性ガスを凝縮させる凝縮器と、
上記熱交換器の冷媒出口と上記凝縮器の冷媒入口とを接続する入口側配管と、
上記凝縮器の冷媒出口と上記熱交換器の冷媒入口とを接続する出口側配管と、
上記入口側配管から上記凝縮器の上記冷媒入口付近の上記入口側配管の分岐部から分岐するバイパス配管と、
上記出口側配管と上記バイパス配管とに接続され、上記凝縮器の冷媒出口から流出した冷媒と上記バイパス配管から供給された冷媒とを混合し、上記出口側配管を介して上記熱交換器の冷媒入口に供給するミキサと、
上記入口側配管から上記凝縮器の冷媒入口に流入する冷媒の流入量と上記バイパス配管への冷媒の流入量とを調整する流量調整機構と、
を備えることを特徴とする冷却システム。 - 請求項1に記載の冷却システムにおいて、
上記凝縮器は、原子力プラントの原子炉格納容器内に配置されることを特徴とする冷却システム。 - 請求項1に記載の冷却システムにおいて、
上記流量調整機構は、上記凝縮器の冷媒入口と上記分岐部との間に配置される凝縮器入口側流量調整バルブと、上記バイパス配管に配置されるバイパス側流量調整バルブとを有することを特徴とする冷却システム。 - 請求項1に記載の冷却システムにおいて、
上記入口側配管及び出口側配管内の冷媒圧力を加圧する加圧器を、さらに備えることを特徴とする冷却システム。 - 請求項4に記載の冷却システムにおいて、
上記加圧器は、水タンクであることを特徴とする冷却システム。 - 請求項4に記載の冷却システムにおいて、
上記加圧器は、上出口側配管に配置される圧力調整用バルブであることを特徴とする冷却システム。 - 請求項3に記載の冷却システムにおいて、
上記出口側配管内の冷媒温度を計測する温度計と、この温度計が計測した冷媒温度に基づいて、上記凝縮器入口側流量調整バルブの弁開度及び上記バイパス側流量調整バルブの弁開度を演算する演算部と、この演算部からの開度調整信号に従って上記凝縮器入口側流量調整バルブの弁開度を調整する第1駆動モータと、上記演算部からの開度調整信号に従って上記バイパス側流量調整バルブの弁開度を調整する第2駆動モータとをさらに備えることを特徴とする冷却システム。 - 非凝縮性ガスを含む凝縮性ガスを凝縮させる凝縮器において、
上面および下面が開放されたケーシングと、
上記ケーシング内の上部空間に配置され、冷媒が流入流出する複数の伝熱管と、を備え、
上記ケーシング内の下部空間に上記伝熱管が配置されていない下部チムニ空間が形成されていることを特徴とする凝縮器。 - 請求項1に記載の冷却システムにおいて、
上記凝縮器は、上面および下面が開放されたケーシングと、上記ケーシング内の上部空間に配置され、冷媒が流入流出する複数の伝熱管とを備え、上記ケーシング内の下部空間に上記伝熱管が配置されていない下部チムニ空間が形成され、窒素濃度が変化する原子炉格納容器内に配置されることを特徴とする冷却システム。 - 冷却システムの運転方法において、
請求項3に記載の冷却システムの上記出口側配管内に冷媒温度を計測する温度計を配置し、この温度計の計測した温度が目標温度よりも高い場合には、上記入口側流量調整バルブを絞り、上記バイパス配管の流量調整バルブを開き、上記温度計の計測した温度が目標温度よりも低い場合には、上記入口側流量調整バルブを開き、上記バイパス配管の上記流量調整バルブを絞るように制御することを特徴とする冷却システムの運転方法。
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CN107449289A (zh) * | 2017-07-27 | 2017-12-08 | 江苏长海化工有限公司 | 一种冷凝器进水温度的自动控制系统及方法 |
CN112466485A (zh) * | 2020-11-26 | 2021-03-09 | 中国船舶工业集团公司第七0八研究所 | 一种非能动余热排出系统缓冲水箱 |
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