WO2017051532A1 - Cooling system and cooling method - Google Patents
Cooling system and cooling method Download PDFInfo
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- WO2017051532A1 WO2017051532A1 PCT/JP2016/004297 JP2016004297W WO2017051532A1 WO 2017051532 A1 WO2017051532 A1 WO 2017051532A1 JP 2016004297 W JP2016004297 W JP 2016004297W WO 2017051532 A1 WO2017051532 A1 WO 2017051532A1
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- refrigerant
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/02—Compression-sorption machines, plants, or systems
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
- F25B15/16—Sorption machines, plants or systems, operating continuously, e.g. absorption type using desorption cycle
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/006—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the sorption type system
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
-
- 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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2507—Flow-diverting valves
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
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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
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
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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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/62—Absorption based systems
Definitions
- the present invention relates to a cooling system and a cooling method used for cooling electronic devices and the like, and more particularly to a cooling system and a cooling method using a phase change of a refrigerant.
- Patent Document 1 An example of a cooling system using refrigerant phase change is described in Patent Document 1.
- the related refrigeration apparatus described in Patent Document 1 is a cooling system that combines a vapor compression refrigerator and an adsorption refrigerator.
- the related refrigeration apparatus has an adsorption refrigerator having a first adsorber and a second adsorber, a first vapor compression refrigerator, and a second vapor compression refrigerator.
- the first and second vapor compression refrigerators include a first and second compressor, first and second condensers (heat radiators), first and second decompressors, an evaporator, and first and second accumulators. Is provided. Note that the evaporators of the first and second vapor compression refrigerators are integrated.
- the adsorption refrigerator includes a first and second adsorber, a first and second adsorbent heat exchanger, a first and second water heat exchanger, an outdoor heat exchanger, and the like.
- the adsorbent in the adsorber in the regenerated state is heated by the first condenser provided in the first vapor compression refrigerator, and the second vapor compression is performed by the cooling action of the adsorber in the adsorbed state.
- the second condenser of the type refrigerator is cooled.
- the first adsorber and the second adsorber are switched between an adsorption state and a regeneration state in which the adsorbed vapor refrigerant is desorbed and regenerated at regular intervals.
- the pressure in the condenser of the second vapor compression refrigeration machine can be reduced, so that the power (compression work) of the compressor of the second vapor compression refrigeration machine can be reduced. it can. Therefore, according to the related refrigeration apparatus, a sufficient refrigeration capacity can be obtained with a small amount of power in the refrigeration apparatus in which the first and second vapor compression refrigerators and the adsorption refrigerator are combined.
- JP-A-11-190566 paragraphs [0005] to [0019], FIG. 1) JP 2014-009624 A Japanese Patent Laid-Open No. 5-272833
- the related refrigeration apparatus described in Patent Document 1 uses a second vapor compression refrigeration by an adsorption refrigerator that desorbs the adsorbed refrigerant using the exhaust heat of the first vapor compression refrigerator. It is set as the structure which cools the condenser with which a machine is equipped. Therefore, the cooling capacity of the second vapor compression refrigerator depends on the cooling capacity of the adsorption refrigerator and the first vapor compression refrigerator. As a result, the cooling capacity of the refrigeration apparatus is not always constant, and the cooling capacity varies depending on the ratio of the amount of refrigerant circulating through each of the first vapor compression refrigerator and the second vapor compression refrigerator.
- An object of the present invention is to provide a cooling system and a cooling method that solve the above-mentioned problem that the cooling capacity of a cooling system varies in a cooling system that combines a plurality of refrigeration cycles.
- the cooling system of the present invention includes a first cooling means having a first refrigerant transporting means for circulating a refrigerant received from a cooling target, and a branched refrigerant that is connected to the first refrigerant transporting means and is a part of the refrigerant.
- a second refrigerant transporting means that circulates, a second cooling means that receives heat from the refrigerant circulating through the first refrigerant transporting means and cools the branch refrigerant, and a flow rate control means that controls the flow rate of the branch refrigerant.
- the cooling method of the present invention circulates the refrigerant received from the object to be cooled, branches a part of the refrigerant, circulates the branched branch refrigerant, receives heat from the refrigerant, cools the branch refrigerant, Control is performed so that the cooling capacity for the object to be cooled is substantially constant.
- FIG. 1 is a schematic diagram showing a configuration of a cooling system 100 according to the first embodiment of the present invention. Broken line arrows in the figure indicate heat transfer.
- the cooling system 100 includes a first cooling unit 110, a second cooling unit 120, a second refrigerant transporting unit 121, and a flow rate control unit 130.
- 1st cooling means 110 is provided with the 1st refrigerant transportation means 111 through which the refrigerant which received heat (H1) from cooling object 10 circulates.
- the second refrigerant transport means 121 is connected to the first refrigerant transport means 111, and a branched refrigerant that is a part of the refrigerant circulates.
- the second cooling means 120 receives heat (H2) from the refrigerant circulating in the first refrigerant transport means 111 and cools (H3) the branched refrigerant. Then, the flow rate control means 130 controls the flow rate of the branched refrigerant.
- the temperature of the branched refrigerant after being cooled by the second cooling means 120 depends not only on the cooling capacity of the second cooling means 120 but also on the flow rate of the branched refrigerant. Therefore, by controlling the flow rate of the branch refrigerant, the temperature of the branch refrigerant that flows back to the first refrigerant transport means 111 through the second refrigerant transport means 121 can be controlled. Thereby, even if the cooling capacity of the second cooling means 120 varies, it is possible to maintain the cooling capacity of the cooling system 100.
- the cooling system 100 of the present embodiment even when the cooling system 100 has a configuration in which a plurality of refrigeration cycles including the first cooling unit 110 and the second cooling unit 120 are combined, Variations in cooling capacity can be suppressed.
- the first cooling means 110 can be configured to use a vapor compression refrigeration cycle.
- the second cooling means 120 can be configured to use either an adsorption refrigeration cycle or an absorption refrigeration cycle.
- the flow rate control means 130 can be configured to control the flow rate of the branched refrigerant so that the temperature difference of the branched refrigerant before and after being cooled by the second cooling means 120 becomes substantially constant. Specifically, when the temperature difference of the branch refrigerant is larger than a predetermined value, the flow rate control means 130 increases the flow rate of the branch refrigerant. Conversely, when the temperature difference is smaller than a predetermined value, the flow rate control means 130 can be configured to control to decrease the flow rate of the branched refrigerant.
- coolant so that the temperature difference of a branch refrigerant
- coolant may become a predetermined range, for example, the range of 0 degreeC or more and 5 degrees C or less.
- the flow rate of the branch refrigerant may be increased, and when the temperature difference is within the predetermined range, the flow rate of the branch refrigerant may be decreased.
- the flow rate control means 130 can be a flow rate control valve located in the flow path constituted by the first refrigerant transport means 111.
- the flow rate control means 130 may be a flow rate control valve located in a flow path constituted by the second refrigerant transport means 121.
- the refrigerant that has received heat from the cooling target is circulated, a part of this refrigerant is branched, and the branched branched refrigerant is circulated. And while receiving heat from this refrigerant
- the flow rate of the branching refrigerant is controlled so that the cooling capacity for the cooling target is substantially constant.
- the control of the flow rate of the branching refrigerant described above can be configured to control the flow rate of the branching refrigerant so that the temperature difference between the branching refrigerant before and after the step of cooling the branching refrigerant becomes substantially constant. At this time, when the temperature difference is larger than a predetermined value, the flow rate of the branched refrigerant may be increased, and when the temperature difference is smaller than the predetermined value, the flow rate of the branched refrigerant may be decreased.
- the step of receiving heat from the refrigerant and cooling the branched refrigerant may be a step of cooling the branched refrigerant by receiving heat from the refrigerant, desorbing the adsorbent, and evaporating the adsorbed adsorbent.
- the cooling method according to the present embodiment has a configuration in which the refrigeration cycle in which the refrigerant received from the cooling target circulates and the refrigeration cycle that receives the heat from the refrigerant and cools the branched refrigerant are combined. And as above-mentioned, according to the cooling method of this embodiment, even if it is a case where it is the case where it is the case where it is the structure which combined such a some refrigeration cycle, the fluctuation
- FIG. 2 schematically shows the configuration of a cooling system 1000 according to the second embodiment of the present invention.
- solid and broken arrows indicate the refrigerant flow
- white arrows indicate the heat flow.
- the cooling system 1000 includes a first cooling device (first cooling means) 1100, a second cooling device (second cooling means) 1200, a second refrigerant transport unit (second refrigerant transport means). ) 1210 and a flow rate control valve (flow rate control means) 1300.
- the cooling system 1000 has a configuration in which a plurality of refrigeration cycles including the first cooling device 1100 and the second cooling device 1200 are combined. That is, the cooling system 1000 is an exhaust heat recovery type in which the second cooling device 1200 further cools the cooling target 10 using the heat recovered by the first cooling device 1100 cooling the cooling target 10 as an energy source. Cooling system.
- the cooling target 10 is an electronic device such as a server.
- the first cooling device 1100 includes an evaporator (evaporating means) 1110, a compressor (compressing means) 1120, a condenser (condensing means) 1130, an expansion valve (expanding means) 1140, and a first refrigerant transport section (first (Refrigerant transport means) 1150, and constitutes a vapor compression refrigeration cycle.
- evaporator evaporating means
- compressor compressor
- condenser condensing means
- expansion valve expansion valve
- first refrigerant transport section first (Refrigerant transport means) 1150
- the evaporator 1110 is composed of a radiator or the like, and generates refrigerant vapor that is vaporized by receiving heat from the refrigerant.
- the compressor 1120 adiabatically compresses the refrigerant vapor to generate high-pressure refrigerant vapor.
- the condenser 1130 condenses the high-pressure refrigerant vapor to generate a high-pressure refrigerant liquid.
- the expansion valve 1140 expands the high-pressure refrigerant liquid to generate a low-pressure refrigerant liquid.
- the first refrigerant transport unit 1150 constitutes a refrigerant flow path that returns from the evaporator 1110 to the evaporator 1110 via the compressor 1120, the condenser 1130, and the expansion valve 1140.
- a solid line arrow in FIG. 2 indicates the flow of the refrigerant.
- the second cooling device 1200 constitutes either an adsorption refrigeration cycle or an absorption refrigeration cycle.
- an adsorption refrigerator 1201 having an adsorption refrigeration cycle is used as the second cooling device 1200.
- the adsorption refrigerator 1201 circulates water or the like as a refrigerant with a pump 1202 and cools hot water with a cooling tower 1203 or the like.
- a broken-line arrow in FIG. 2 indicates a flow of water as a refrigerant of the adsorption refrigerator 1201.
- the second refrigerant transport unit 1210 constitutes a flow path in which a branched refrigerant that is a part of the refrigerant circulates between the evaporator 1110 and the compressor 1120 and between the evaporator 1110 and the expansion valve 1140.
- the condenser 1130 exchanges heat between the high-pressure refrigerant vapor flowing through the first refrigerant transport unit 1150 and the refrigerant on the heat receiving side of the second cooling device 1200.
- a heat exchanger (heat exchanging means) 1220 for exchanging heat between the branched refrigerant circulated by the second refrigerant transport section 1210 and the refrigerant on the cooling side of the second cooling device 1200 can be provided.
- the flow control valve 1300 controls the flow rate of the branched refrigerant.
- FIG. 2 shows a case where the flow control valve 1300 is located in a flow path constituted by the first refrigerant transport portion 1150. Not only this but as shown in FIG. 3, it is good also as a structure where the flow control valve 1301 is located in the flow path comprised by the 2nd refrigerant
- the refrigerant liquid flowing into the evaporator 1110 made of a radiator or the like is vaporized by the exhaust heat of about 40 to 50 ° C. sent from the cooling target 10 such as a server and becomes refrigerant vapor.
- the cooling target 10 such as a server
- the refrigerant vapor is adiabatically compressed by the compressor 1120, the pressure rises and the temperature of the refrigerant vapor rises to about 50 to 100 ° C.
- heat is exchanged between the refrigerant and water by the condenser 1130.
- the heat of the refrigerant moves to the water, hot water of about 50 to 100 ° C. is generated, and the temperature of the refrigerant decreases.
- the refrigerant condensed and liquefied as the temperature decreases is reduced in pressure by the expansion valve 1140. Thereafter, it flows again into the evaporator 1110.
- Heat is transferred to the adsorption refrigeration machine 1201 through hot water of about 50 to 100 ° C. received by heat exchange in the condenser 1130.
- the adsorption refrigeration machine 1201 generates cold water of about 5 to 20 ° C. using the warm heat, and cools the branched refrigerant via the heat exchanger 1220.
- the branched refrigerant cooled by the heat exchanger 1220 is condensed and liquefied and circulated by the second refrigerant transport unit 1210. Since the second refrigerant transport unit 1210 is connected between the evaporator 1110 and the expansion valve 1140, the condensed and liquefied branch refrigerant merges with the refrigerant liquid whose pressure has been reduced by the expansion valve 1140, and returns to the evaporator 1110. .
- drive parts (drive means) 1230 such as a pump which circulates a branch refrigerant, in the flow path of the branch refrigerant which the 2nd refrigerant transport part 1210 comprises.
- the refrigerant liquid returned to the evaporator 1110 is vaporized by exhaust heat from the cooling target 10 such as a server.
- the refrigerant vapor evaporated in the evaporator 1110 branches and flows into the second refrigerant transport part 1210 and the first refrigerant transport part 1150 connected between the evaporator 1110 and the compressor 1120.
- the branched refrigerant circulated by the second refrigerant transport unit 1210 flows into the heat exchanger 1220 again.
- the flow control valve 1300 controls the flow rate of the branched refrigerant. That is, the flow control valve 1300 adjusts the ratio at which the refrigerant vapor vaporized in the evaporator 1110 branches to the first refrigerant transport part 1150 and the second refrigerant transport part 1210. As a result, the amount of refrigerant cooled by the condenser 1130 via the compressor 1120 included in the first cooling device 1100 and the branch cooled by the second cooling device 1200 via the second refrigerant transport unit 1210. The amount of refrigerant can be adjusted.
- thermometer 1221 that measures the temperature of the branched refrigerant on the inlet side of the heat exchanger 1220 and the second thermometer 1222 that measures the temperature of the branched refrigerant on the outlet side may be provided.
- the flow control valve 1300 is controlled using the pre-cooling refrigerant temperature T1 that is the measurement result of the first thermometer 1221 and the post-cooling refrigerant temperature T2 that is the measurement result of the second thermometer 1222. be able to.
- the flow rate control valve 1300 or the flow rate control valve 1301 is adjusted so that the temperature difference T1-T2 becomes constant at 5 degrees, for example.
- the opening degree of the flow control valve 1300 provided in the first refrigerant transport portion 1150 shown in FIG. make it smaller.
- the opening degree of the flow control valve 1301 provided in the second refrigerant transport unit 1210 shown in FIG. 3 is increased.
- the opening degree of the flow control valve 1300 provided in the first refrigerant transport portion 1150 shown in FIG. 2 is increased.
- the opening degree of the flow control valve 1301 provided in the second refrigerant transport unit 1210 shown in FIG. 3 is reduced.
- the flow control valve 1300 By controlling the flow control valve 1300 in this way, the temperature of the branched refrigerant that flows back to the first refrigerant transport part 1150 through the second refrigerant transport part 1210 can be controlled. Thereby, even if the cooling capacity of the second cooling device 1200 varies, the cooling capacity of the cooling system 1000 can be maintained.
- the cooling system 1000 of the present embodiment fluctuations in the cooling capacity of the cooling system 1000 can be suppressed even when the cooling system 1000 is configured by combining a plurality of refrigeration cycles. That is, even if it is a case where it is the case where it is the case where it is the case where it is the case where it is the structure which combined the some refrigeration cycle which consists of the 1st cooling device 1100 (vapor compression refrigeration cycle) and the 2nd cooling device 1200 (adsorption refrigeration cycle), the cooling capacity of the cooling system 1000 Fluctuations can be suppressed.
- the heat exchanger 1220 may be positioned above the evaporator 1110.
- the branched refrigerant can flow through the second refrigerant transport portion 1210 and return to the evaporator 1110 by the action of gravity. This eliminates the need for a drive unit (drive means) such as the pump described above.
- Cooling system 110 1st cooling means 111 1st refrigerant
- Flow control means 1000 Cooling system 1100 1st cooling device 1110 Evaporator 1120 Compressor 1130 Condensation Vessel 1140 expansion valve 1150 first refrigerant transport unit 1200 second cooling device 1201 adsorption refrigerator 1202 pump 1203 cooling tower 1210 second refrigerant transport unit 1220 heat exchanger 1221 first thermometer 1222 second thermometer 1230 Drive unit 1300, 1301 Flow control valve 10 Cooling target
Abstract
Description
図1は、本発明の第1の実施形態に係る冷却システム100の構成を示す概略図である。同図中の破線矢印は、熱の移動を示す。 [First Embodiment]
FIG. 1 is a schematic diagram showing a configuration of a
次に、本発明の第2の実施形態について説明する。図2に、本発明の第2の実施形態に係る冷却システム1000の構成を模式的に示す。同図中、実線および破線の矢印は冷媒の流れを、白抜き矢印は熱の流れをそれぞれ示す。 [Second Embodiment]
Next, a second embodiment of the present invention will be described. FIG. 2 schematically shows the configuration of a
110 第1の冷却手段
111 第1の冷媒輸送手段
120 第2の冷却手段
121 第2の冷媒輸送手段
130 流量制御手段
1000 冷却システム
1100 第1の冷却装置
1110 蒸発器
1120 圧縮機
1130 凝縮器
1140 膨張弁
1150 第1の冷媒輸送部
1200 第2の冷却装置
1201 吸着式冷凍機
1202 ポンプ
1203 冷却塔
1210 第2の冷媒輸送部
1220 熱交換器
1221 第1の温度計
1222 第2の温度計
1230 駆動部
1300、1301 流量制御バルブ
10 冷却対象 DESCRIPTION OF
Claims (14)
- 冷却対象から受熱した冷媒が循環する第1の冷媒輸送手段を備えた第1の冷却手段と、
前記第1の冷媒輸送手段と接続し、前記冷媒の一部である分岐冷媒が循環する第2の冷媒輸送手段と、
前記第1の冷媒輸送手段を循環する前記冷媒から受熱し、前記分岐冷媒を冷却する第2の冷却手段と、
前記分岐冷媒の流量を制御する流量制御手段と、を有する
冷却システム。 A first cooling means comprising a first refrigerant transport means for circulating the refrigerant received from the object to be cooled;
A second refrigerant transporting means connected to the first refrigerant transporting means, in which a branched refrigerant that is part of the refrigerant circulates;
Second cooling means for receiving heat from the refrigerant circulating in the first refrigerant transport means and cooling the branched refrigerant;
And a flow rate control means for controlling the flow rate of the branched refrigerant. - 請求項1に記載した冷却システムにおいて、
前記流量制御手段は、前記第1の冷媒輸送手段によって構成される流路内に位置する流量制御バルブである
冷却システム。 The cooling system according to claim 1,
The flow rate control means is a flow rate control valve located in a flow path constituted by the first refrigerant transport means. Cooling system. - 請求項1または2に記載した冷却システムにおいて、
前記流量制御手段は、前記第2の冷媒輸送手段によって構成される流路内に位置する流量制御バルブである
冷却システム。 The cooling system according to claim 1 or 2,
The flow rate control means is a flow rate control valve located in a flow path constituted by the second refrigerant transport means. Cooling system. - 請求項1から3のいずれか一項に記載した冷却システムにおいて、
前記流量制御手段は、前記第2の冷却手段によって冷却される前後における前記分岐冷媒の温度差が、所定の範囲内となるように前記分岐冷媒の流量を制御する
冷却システム。 The cooling system according to any one of claims 1 to 3,
The cooling system that controls the flow rate of the branch refrigerant so that a temperature difference of the branch refrigerant before and after being cooled by the second cooling unit is within a predetermined range. - 請求項4に記載した冷却システムにおいて、
前記流量制御手段は、
前記温度差が前記所定の範囲を超えている場合、前記分岐冷媒の流量を増大させ、
前記温度差が前記所定の範囲内にある場合、前記分岐冷媒の流量を減少させる
冷却システム。 The cooling system according to claim 4, wherein
The flow rate control means is
If the temperature difference exceeds the predetermined range, increase the flow rate of the branch refrigerant,
A cooling system that reduces the flow rate of the branched refrigerant when the temperature difference is within the predetermined range. - 請求項1から5のいずれか一項に記載した冷却システムにおいて、
前記第1の冷却手段は、蒸気圧縮冷凍サイクルを構成し、
前記冷媒が受熱して気化した冷媒蒸気を生成する蒸発手段と、
前記冷媒蒸気を圧縮して高圧冷媒蒸気を生成する圧縮手段と、
前記高圧冷媒蒸気を凝縮させ高圧冷媒液を生成する凝縮手段と、
前記高圧冷媒液を膨張させて低圧の冷媒液を生成する膨張手段、とを備え、
前記第1の冷媒輸送手段は、前記蒸発手段から、前記圧縮手段、前記凝縮手段、および前記膨張手段を経由して前記蒸発手段に還流する前記冷媒の流路を構成し、
前記第2の冷媒輸送手段は、前記蒸発手段と前記圧縮手段の間から、前記蒸発手段と前記膨張手段の間に前記分岐冷媒が循環する流路を構成する
冷却システム。 The cooling system according to any one of claims 1 to 5,
The first cooling means constitutes a vapor compression refrigeration cycle,
Evaporating means for generating a refrigerant vapor vaporized by receiving heat from the refrigerant;
Compression means for compressing the refrigerant vapor to generate high-pressure refrigerant vapor;
Condensing means for condensing the high-pressure refrigerant vapor to produce a high-pressure refrigerant liquid;
Expansion means for expanding the high-pressure refrigerant liquid to generate a low-pressure refrigerant liquid,
The first refrigerant transport means constitutes a flow path for the refrigerant that flows back from the evaporation means to the evaporation means via the compression means, the condensation means, and the expansion means,
The cooling system, wherein the second refrigerant transport means constitutes a flow path through which the branched refrigerant circulates between the evaporation means and the expansion means between the evaporation means and the compression means. - 請求項6に記載した冷却システムにおいて、
前記分岐冷媒と前記第2の冷却手段の冷却側の冷媒を熱交換させる熱交換手段を備え、
前記凝縮手段は、前記高圧冷媒蒸気と前記第2の冷却手段の受熱側の冷媒を熱交換させる
冷却システム。 The cooling system according to claim 6, wherein
Heat exchange means for exchanging heat between the branched refrigerant and the refrigerant on the cooling side of the second cooling means;
The condensing unit is a cooling system for exchanging heat between the high-pressure refrigerant vapor and a refrigerant on a heat receiving side of the second cooling unit. - 請求項7に記載した冷却システムにおいて、
前記熱交換手段は、前記蒸発手段よりも上方に位置している
冷却システム。 The cooling system according to claim 7, wherein
The heat exchange means is located above the evaporation means. - 請求項1から8のいずれか一項に記載した冷却システムにおいて、
前記第2の冷却手段は、吸着冷凍サイクルおよび吸収冷凍サイクルのいずれかを構成する
冷却システム。 The cooling system according to any one of claims 1 to 8,
The second cooling means constitutes one of an adsorption refrigeration cycle and an absorption refrigeration cycle. - 請求項1から9のいずれか一項に記載した冷却システムにおいて、
前記第2の冷媒輸送手段が構成する前記分岐冷媒の流路内に、前記分岐冷媒を循環させる駆動手段を備える
冷却システム。 The cooling system according to any one of claims 1 to 9,
A cooling system comprising driving means for circulating the branched refrigerant in the flow path of the branched refrigerant constituted by the second refrigerant transporting means. - 冷却対象から受熱した冷媒を循環させ、
前記冷媒の一部を分岐し、分岐した分岐冷媒を循環させ、
前記冷媒から受熱するとともに前記分岐冷媒を冷却し、
前記分岐冷媒の流量を、前記冷却対象に対する冷却能力が略一定となるように制御する
冷却方法。 Circulate the refrigerant that has received heat from the cooling target,
Branching a part of the refrigerant, circulating the branched refrigerant,
Receiving heat from the refrigerant and cooling the branched refrigerant;
A cooling method for controlling the flow rate of the branched refrigerant so that a cooling capacity for the cooling target is substantially constant. - 請求項11に記載した冷却方法において、
前記分岐冷媒を冷却する工程の前段と後段における前記分岐冷媒の温度差が、略一定となるように前記分岐冷媒の流量を制御する
冷却方法。 The cooling method according to claim 11,
A cooling method in which the flow rate of the branch refrigerant is controlled so that a temperature difference between the branch refrigerant in the former stage and the latter stage of the step of cooling the branch refrigerant becomes substantially constant. - 請求項12に記載した冷却方法において、
前記温度差が所定値よりも大きい場合、前記分岐冷媒の流量を増大させ、
前記温度差が所定値よりも小さい場合、前記分岐冷媒の流量を減少させる
冷却方法。 The cooling method according to claim 12, wherein
If the temperature difference is greater than a predetermined value, increase the flow rate of the branch refrigerant,
A cooling method that reduces the flow rate of the branched refrigerant when the temperature difference is smaller than a predetermined value. - 請求項11から13のいずれか一項に記載した冷却方法において、
前記冷媒から受熱して吸着材を脱着させ、脱着した前記吸着材を蒸発させることにより前記分岐冷媒を冷却する
冷却方法。 The cooling method according to any one of claims 11 to 13,
A cooling method in which the branched refrigerant is cooled by receiving heat from the refrigerant, desorbing the adsorbent, and evaporating the desorbed adsorbent.
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Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000241042A (en) * | 1998-06-08 | 2000-09-08 | Tokyo Gas Co Ltd | Combined air conditioner |
JP2010243086A (en) * | 2009-04-07 | 2010-10-28 | Daikin Ind Ltd | Refrigerating device |
WO2015125219A1 (en) * | 2014-02-18 | 2015-08-27 | 三菱電機株式会社 | Air conditioning device |
-
2015
- 2015-09-21 US US15/760,345 patent/US20180259232A1/en not_active Abandoned
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2016
- 2016-09-21 WO PCT/JP2016/004297 patent/WO2017051532A1/en active Application Filing
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000241042A (en) * | 1998-06-08 | 2000-09-08 | Tokyo Gas Co Ltd | Combined air conditioner |
JP2010243086A (en) * | 2009-04-07 | 2010-10-28 | Daikin Ind Ltd | Refrigerating device |
WO2015125219A1 (en) * | 2014-02-18 | 2015-08-27 | 三菱電機株式会社 | Air conditioning device |
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WO2017164201A1 (en) * | 2016-03-25 | 2017-09-28 | 日本電気株式会社 | Cooling system, and method for controlling cooling system |
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