WO2017051532A1 - Système et procédé de refroidissement - Google Patents

Système et procédé de refroidissement Download PDF

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Publication number
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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WO
WIPO (PCT)
Prior art keywords
refrigerant
cooling
flow rate
cooling system
branched
Prior art date
Application number
PCT/JP2016/004297
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English (en)
Japanese (ja)
Inventor
寿人 佐久間
雅人 矢野
吉川　実
正樹 千葉
Original Assignee
日本電気株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to US15/760,345 priority Critical patent/US20180259232A1/en
Application filed by 日本電気株式会社 filed Critical 日本電気株式会社
Priority to JP2017541429A priority patent/JPWO2017051532A1/ja
Publication of WO2017051532A1 publication Critical patent/WO2017051532A1/fr

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Classifications

    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

L'invention concerne un système de refroidissement combinant une pluralité de cycles frigorifiques et présentant une capacité de refroidissement fluctuante. Ainsi, le système de refroidissement comporte : un premier moyen de refroidissement comprenant un premier moyen de transport de fluide réfrigérant destiné à faire circuler un fluide réfrigérant ayant reçu de la chaleur à partir d'un objet à refroidir ; un second moyen de transport de fluide réfrigérant relié au premier moyen de transport de fluide réfrigérant et destiné à faire circuler un fluide réfrigérant dérivé qui représente une partie du fluide réfrigérant ; un second moyen de refroidissement destiné à recevoir de la chaleur à partir du fluide réfrigérant circulant à travers le premier moyen de transport de fluide réfrigérant et destiné à refroidir le fluide réfrigérant dérivé ; et un moyen de régulation de débit destiné à réguler le débit du fluide réfrigérant dérivé.
PCT/JP2016/004297 2015-09-25 2016-09-21 Système et procédé de refroidissement WO2017051532A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US15/760,345 US20180259232A1 (en) 2015-09-25 2015-09-21 Cooling system and cooling method
JP2017541429A JPWO2017051532A1 (ja) 2015-09-25 2016-09-21 冷却システムおよび冷却方法

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JP2015-188225 2015-09-25
JP2015188225 2015-09-25

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017164201A1 (fr) * 2016-03-25 2017-09-28 日本電気株式会社 Système de refroidissement et son procédé de commande

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201801534D0 (en) * 2018-01-30 2018-03-14 Exergyn Ltd A heat pump utilising the shape memory effect

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000241042A (ja) * 1998-06-08 2000-09-08 Tokyo Gas Co Ltd 複合空調装置
JP2010243086A (ja) * 2009-04-07 2010-10-28 Daikin Ind Ltd 冷凍装置
WO2015125219A1 (fr) * 2014-02-18 2015-08-27 三菱電機株式会社 Dispositif de climatisation

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000241042A (ja) * 1998-06-08 2000-09-08 Tokyo Gas Co Ltd 複合空調装置
JP2010243086A (ja) * 2009-04-07 2010-10-28 Daikin Ind Ltd 冷凍装置
WO2015125219A1 (fr) * 2014-02-18 2015-08-27 三菱電機株式会社 Dispositif de climatisation

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017164201A1 (fr) * 2016-03-25 2017-09-28 日本電気株式会社 Système de refroidissement et son procédé de commande

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US20180259232A1 (en) 2018-09-13

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