US20180259232A1 - Cooling system and cooling method - Google Patents

Cooling system and cooling method Download PDF

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Publication number
US20180259232A1
US20180259232A1 US15/760,345 US201515760345A US2018259232A1 US 20180259232 A1 US20180259232 A1 US 20180259232A1 US 201515760345 A US201515760345 A US 201515760345A US 2018259232 A1 US2018259232 A1 US 2018259232A1
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US
United States
Prior art keywords
refrigerant
cooling
unit
diverted
flowrate
Prior art date
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Abandoned
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US15/760,345
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English (en)
Inventor
Hisato Sakuma
Masato Yano
Minoru Yoshikawa
Masaki Chiba
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NEC Corp
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NEC Corp
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Filing date
Publication date
Application filed by NEC Corp filed Critical NEC Corp
Assigned to NEC CORPORATION reassignment NEC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHIBA, MASAKI, SAKUMA, HISATO, YOSHIKAWA, MINORU
Publication of US20180259232A1 publication Critical patent/US20180259232A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • F25B41/06—
    • 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 which are used to cool an electronic device or the like, and in particular, to a cooling system and a cooling method which use a phase change of a refrigerant.
  • One cooling system being high in cooling capacity is a cooling system using a phase change of a refrigerant.
  • a related refrigeration device described in PTL 1 is a cooling system which combines a vapor compression refrigerator and an adsorption refrigerator.
  • the related refrigeration device includes an adsorption refrigerator including 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 first and second compressors, first and second condensers (radiators), first and second decompressors, an evaporator, and first and second accumulators. Note that the evaporator of the first and second vapor compression refrigerators is integrated.
  • the adsorption refrigerator includes the first and second adsorbers, first and second adsorbent heat exchangers, first and second water heat exchangers, an outdoor heat exchanger, and the like.
  • the related refrigeration device heats an adsorbent in the adsorber in a regeneration state by the first condenser included in the first vapor compression refrigerator, and cools the second condenser of the second vapor compression refrigerator by a cooling action of the adsorber in an adsorption state.
  • the related refrigeration device is configured to then switch, at fixed time intervals, the first adsorber and the second adsorber to the adsorption state, and to the regeneration state in which an adsorbed vapor refrigerant is desorbed and regenerated.
  • Such a configuration enables reduction of compression in the condenser of the second vapor compression refrigerator, and therefore enables reduction of power (compression work) by the compressor of the second vapor compression refrigerator. Consequently, according to the related refrigeration device, it is contemplated that a satisfactory refrigerating capacity can be obtained with a small amount of power in the refrigeration device which combines the first and second vapor compression refrigerators and the adsorption refrigerator.
  • the related refrigeration device described in PTL 1 is configured to cool the condenser included in the second vapor compression refrigerator by the adsorption refrigerator which desorbs the adsorbed refrigerant by use of exhaust heat of the first vapor compression refrigerator.
  • a cooling capacity of the second vapor compression refrigerator is dependent on cooling capacities of the adsorption refrigerator and the first vapor compression refrigerator.
  • a cooling capacity of the refrigeration device is not always constant, and fluctuates depending on a ratio of amounts of refrigerants circulating through the first vapor compression refrigerator and the second vapor compression refrigerator, respectively.
  • a cooling system which combines a plurality of refrigeration cycles has a problem of a fluctuating cooling capacity.
  • An object of the present invention is to provide a cooling system and a cooling method which solve the aforementioned problem of a fluctuating cooling capacity of a cooling system which combines a plurality of refrigeration cycles.
  • a cooling system includes: a first cooling means including a first refrigerant transportation means for circulating a refrigerant that receives heat from an object to be cooled; a second refrigerant transportation means connected to the first refrigerant transportation means, for circulating a diverted refrigerant being a part of the refrigerant; a second cooling means for receiving heat from the refrigerant circulating through the first refrigerant transportation means, and cooling the diverted refrigerant; and a flowrate control means for controlling a flowrate of the diverted refrigerant.
  • a cooling method includes: circulating a refrigerant that receives heat from an object to be cooled; diverting a part of the refrigerant, and circulating the diverted refrigerant; receiving heat from the refrigerant and cooling the diverted refrigerant; and controlling a flowrate of the diverted refrigerant in such a way that a cooling capacity for the object to be cooled is substantially constant.
  • a cooling system and a cooling method of the present invention it is possible to suppress fluctuation of a cooling capacity of the cooling system even when the cooling system is configured to combine a plurality of refrigeration cycles.
  • FIG. 1 is a schematic diagram illustrating a configuration of a cooling system according to a first exemplary embodiment of the present invention.
  • FIG. 2 is a schematic diagram illustrating a configuration of a cooling system according to a second exemplary embodiment of the present invention.
  • FIG. 3 is a schematic diagram illustrating another configuration of the cooling system according to the second exemplary embodiment of the present invention.
  • FIG. 4 is a schematic diagram illustrating yet another configuration of the cooling system according to the second exemplary embodiment of the present invention.
  • FIG. 1 is a schematic diagram illustrating a configuration of a cooling system 100 according to a first exemplary embodiment of the present invention. Dotted arrows in FIG. 1 indicate transfer of heat.
  • the cooling system 100 includes a first cooling means 110 , a second cooling means 120 , a second refrigerant transportation means 121 , and a flowrate control means 130 .
  • the first cooling means 110 includes a first refrigerant transportation means 111 which circulates a refrigerant that has received heat (H 1 ) from an object to be cooled 10 .
  • the second refrigerant transportation means 121 is connected to the first refrigerant transportation means 111 , and circulates a diverted refrigerant being some of the refrigerant.
  • the second cooling means 120 receives heat (H 2 ) from the refrigerant circulating through the first refrigerant transportation means 111 , and cools the diverted refrigerant (H 3 ). Further, the flowrate control means 130 controls a flowrate of the diverted refrigerant.
  • temperature of the diverted refrigerant after being cooled by the second cooling means 120 is dependent not only on a cooling capacity of the second cooling means 120 but also on the flowrate of the diverted refrigerant. It is therefore possible to control the temperature of the diverted refrigerant flowing back to the first refrigerant transportation means 111 through the second refrigerant transportation means 121 , by controlling the flowrate of the diverted refrigerant. This enables a cooling capacity of the cooling system 100 to be maintained even when the cooling capacity of the second cooling means 120 has fluctuated.
  • the cooling system 100 in the present exemplary embodiment it is possible to inhibit fluctuation of the cooling capacity of the cooling system 100 even when the cooling system 100 is configured to combine a plurality of refrigeration cycles including the first cooling means 110 and the second cooling means 120 .
  • the first cooling means 110 can have a configuration using a vapor compression refrigeration cycle.
  • the second cooling means 120 can have a configuration using one of an adsorption refrigeration cycle and an absorption refrigeration cycle.
  • the flowrate control means 130 can be configured to control the flowrate of the diverted refrigerant in such a way that a temperature difference of the diverted refrigerant before and after being cooled by the second cooling means 120 is substantially constant. Specifically, when a temperature difference of the diverted refrigerant is greater than a predetermined value, the flowrate control means 130 increases the flowrate of the diverted refrigerant. On the contrary, when the temperature difference is smaller than the predetermined value, the flowrate control means 130 can be configured to control in such a way as to decrease the flowrate of the diverted refrigerant.
  • the flowrate control means 130 may be configured to control the flowrate of the diverted refrigerant in such a way that a temperature difference of the diverted refrigerant is within a predetermined range, for example, within a range from 0° C. or more to 5° C. or less.
  • the flowrate control means 130 may control in such a way as to increase the flowrate of the diverted refrigerant when the temperature difference of the diverted refrigerant is beyond the predetermined range, and decrease the flowrate of the diverted refrigerant when the temperature difference is within the predetermined range.
  • the flowrate control means 130 can be a flowrate control valve located within a flow path configured by the first refrigerant transportation means 111 .
  • the flowrate control means 130 may be a flowrate control valve located within a flow path configured by the second refrigerant transportation means 121 .
  • a refrigerant that has received heat from an object to be cooled is circulated, some of this refrigerant is diverted, and the diverted refrigerant is circulated. Then, heat is received from the refrigerant, and the diverted refrigerant is cooled.
  • a flowrate of the diverted refrigerant is controlled in such a way that a cooling capacity for the object to be cooled is substantially constant.
  • the aforementioned control of the flowrate of the diverted refrigerant can be configured to control the flowrate of the diverted refrigerant in such a way that a temperature difference of the diverted refrigerant at preliminary and subsequent stages of a process for cooling the diverted refrigerant is substantially constant.
  • the control of the flowrate may be configured to control in such a way as to increase the flowrate of the diverted refrigerant when a temperature difference is greater than a predetermined value, and decrease the flowrate of the diverted refrigerant when the temperature difference is smaller than the predetermined value.
  • the aforementioned process for receiving heat from the refrigerant and cooling the diverted refrigerant can be a process for desorbing an adsorbent by receiving heat from the refrigerant, and cooling the diverted refrigerant by evaporating the desorbed adsorbent.
  • the cooling method according to the present exemplary embodiment is configured to combine a refrigeration cycle for circulating a refrigerant that has received heat from an object to be cooled, and a refrigeration cycle for receiving heat from the refrigerant and cooling a diverted refrigerant.
  • a refrigeration cycle for circulating a refrigerant that has received heat from an object to be cooled and a refrigeration cycle for receiving heat from the refrigerant and cooling a diverted refrigerant.
  • FIG. 2 schematically illustrates a configuration of a cooling system 1000 according to the second exemplary embodiment of the present invention.
  • solid and dotted arrows indicate flow of a refrigerant
  • outline arrows indicate flow of heat, respectively.
  • the cooling system 1000 includes a first cooling device (first cooling means) 1100 , a second cooling device (second cooling means) 1200 , a second refrigerant transportation unit (second refrigerant transportation means) 1210 , and a flowrate control valve (flowrate control means) 1300 .
  • the cooling system 1000 has a configuration which combines a plurality of refrigeration cycles having the first cooling device 1100 and the second cooling device 1200 .
  • the cooling system 1000 is an exhaust heat collecting type cooling system in which the second cooling device 1200 further cools an object to be cooled 10 using, as an energy source, heat that the first cooling device 1100 has collected by cooling the object to be cooled 10 .
  • the object to be cooled 10 is, for example, an electronic device such as a server.
  • the first cooling device 1100 includes an evaporator (evaporation means) 1110 , a compressor (compression means) 1120 , a condenser (condensation means) 1130 , an expansion valve (expansion means) 1140 , and a first refrigerant transportation unit (first refrigerant transportation means) 1150 , thereby configuring a vapor compression refrigeration cycle.
  • evaporator evaporation means
  • compressor compression means
  • condenser condensation means
  • expansion valve expansion means
  • first refrigerant transportation unit first refrigerant transportation means
  • the evaporator 1110 is configured by a radiator or the like, and generates refrigerant vapor resulting from the refrigerant that has received heat and vaporized.
  • the compressor 1120 generates high-pressure refrigerant vapor by adiabatically compressing the refrigerant vapor.
  • the condenser 1130 condenses the high-pressure refrigerant vapor and generates a high-pressure refrigerant liquid. Further, the expansion valve 1140 generates a low-pressure refrigerant liquid by expanding the high-pressure refrigerant liquid.
  • the first refrigerant transportation unit 1150 configures a flow path of the refrigerant flowing back to the evaporator 1110 from the evaporator 1110 via the compressor 1120 , the condenser 1130 , and the expansion valve 1140 .
  • the solid arrows in FIG. 2 indicate flow of the refrigerant.
  • the second cooling device 1200 configures one of an adsorption refrigeration cycle and an absorption refrigeration cycle.
  • an adsorption refrigerator 1201 including an adsorption refrigeration cycle is used as the second cooling device 1200 .
  • the adsorption refrigerator 1201 circulates water or the like as a refrigerant by a pump 1202 , and cools warm water by a cooling tower 1203 or the like.
  • the dotted arrows in FIG. 2 indicate flow of water as the refrigerant of the adsorption refrigerator 1201 .
  • the second refrigerant transportation unit 1210 configures a flow path which circulates the diverted refrigerant being some of the refrigerant, from between the evaporator 1110 and the compressor 1120 to between the evaporator 1110 and the expansion valve 1140 .
  • the condenser 1130 exchanges heat between the high-pressure refrigerant vapor flowing in the first refrigerant transportation unit 1150 and a refrigerant on a heat receiving side of the second cooling device 1200 .
  • a configuration including a heat exchanger (heat exchange means) 1220 which exchanges heat between the diverted refrigerant circulated by the second refrigerant transportation unit 1210 and a refrigerant on a cooling side of the second cooling device 1200 .
  • the flowrate control valve 1300 controls a flowrate of the diverted refrigerant.
  • the flowrate control valve 1300 is located within a flow path configured by the first refrigerant transportation unit 1150 .
  • a flowrate control valve 1301 may be configured to be located within a flow path configured by the second refrigerant transportation unit 1210 , as illustrated in FIG. 3 .
  • heat of the refrigerant transfers to water, warm water at approximately 50 to 100° C. is generated, and temperature of the refrigerant falls.
  • the refrigerant condensed and liquefied by the temperature fall is decreased in pressure by the expansion valve 1140 .
  • the refrigerant then again flows into the evaporator 1110 .
  • the second cooling device 1200 Secondly, an operation of the second cooling device 1200 is described. Heat transfers to the adsorption refrigerator 1201 via the warm water at approximately 50 to 100° C. that has received heat by the heat exchange in the condenser 1130 .
  • the adsorption refrigerator 1201 generates cool water at approximately 5 to 20° C. by using the heat, and cools the diverted refrigerant via the heat exchanger 1220 .
  • the diverted refrigerant cooled by the heat exchanger 1220 is condensed and liquefied, and circulated by the second refrigerant transportation unit 1210 . Because the second refrigerant transportation unit 1210 is connected between the evaporator 1110 and the expansion valve 1140 , the condensed and liquefied diverted refrigerant flows together with the refrigerant liquid decreased in pressure by the expansion valve 1140 , and flows back to the evaporator 1110 .
  • a drive unit (drive means) 1230 such as a pump which circulates the diverted refrigerant may be configured to be provided in a flow path of the diverted refrigerant configured by the second refrigerant transportation unit 1210 .
  • the refrigerant liquid which has flowed back to the evaporator 1110 vaporizes due to exhaust heat from an object to be cooled 10 such as a server.
  • the refrigerant vapor which has vaporized in the evaporator 1110 is diverted to and then flows in the second refrigerant transportation unit 1210 connected between the evaporator 1110 and the compressor 1120 , and the first refrigerant transportation unit 1150 .
  • the diverted refrigerant circulated by the second refrigerant transportation unit 1210 again flows into the heat exchanger 1220 .
  • the flowrate control valve 1300 controls the flowrate of the diverted refrigerant. In other words, the flowrate control valve 1300 adjusts a ratio at which the refrigerant vapor that has been vaporized in the evaporator 1110 is diverted to the first refrigerant transportation unit 1150 and the second refrigerant transportation unit 1210 . This makes it possible to adjust an amount of the refrigerant cooled by the condenser 1130 via the compressor 1120 provided in the first cooling device 1100 , and an amount of the diverted refrigerant cooled by the second cooling device 1200 via the second refrigerant transportation unit 1210 .
  • the cooling system 1000 may also be configured to include a first temperature gauge 1221 which measures temperature of the diverted refrigerant on an entrance side of the heat exchanger 1220 , and a second temperature gauge 1222 which measures temperature of the diverted refrigerant on an exit side.
  • the cooling system 1000 can be configured to then control the flowrate control valve 1300 by use of a before-cooling refrigerant temperature T 1 which is a measurement result by the first temperature gauge 1221 , and an after-cooling refrigerant temperature T 2 which is a measurement result by the second temperature gauge 1222 .
  • the flowrate control valve 1300 or the flowrate control valve 1301 is adjusted in such a way that the temperature difference T 1 ⁇ T 2 is constant at, for example, 5 degrees.
  • opening of the flowrate control valve 1300 provided in the first refrigerant transportation unit 1150 illustrated in FIG. 2 is decreased.
  • opening of the flowrate control valve 1301 provided in the second refrigerant transportation unit 1210 illustrated in FIG. 3 is increased.
  • the opening of the flowrate control valve 1300 provided in the first refrigerant transportation unit 1150 illustrated in FIG. 2 is increased.
  • the opening of the flowrate control valve 1301 provided in the second refrigerant transportation unit 1210 illustrated in FIG. 3 is decreased.
  • the cooling system 1000 in the present exemplary embodiment it is possible to inhibit fluctuation of the cooling capacity of the cooling system 1000 even when the cooling system 1000 is configured to combine a plurality of refrigeration cycles.
  • the cooling system 1000 is configured to combine a plurality of refrigeration cycles including the first cooling device 1100 (vapor compression refrigeration cycle) and the second cooling device 1200 (adsorption refrigeration cycle).
  • the heat exchanger 1220 can be configured to be located higher than the evaporator 1110 .
  • Such a configuration enables the diverted refrigerant to flow in the second refrigerant transportation unit 1210 and flow back to the evaporator 1110 due to a gravitational action.
  • the aforementioned drive unit (drive means) which is a pump or the like becomes unnecessary.

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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)
US15/760,345 2015-09-25 2015-09-21 Cooling system and cooling method Abandoned US20180259232A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2015-188225 2015-09-25
JP2015188225 2015-09-25
PCT/JP2016/004297 WO2017051532A1 (ja) 2015-09-25 2016-09-21 冷却システムおよび冷却方法

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11656008B2 (en) * 2018-01-30 2023-05-23 Exergyn Ltd. Heat pump utilising the shape memory effect

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017164201A1 (ja) * 2016-03-25 2017-09-28 日本電気株式会社 冷却システムおよび冷却システムの制御方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010243086A (ja) * 2009-04-07 2010-10-28 Daikin Ind Ltd 冷凍装置
WO2015125219A1 (ja) * 2014-02-18 2015-08-27 三菱電機株式会社 空気調和装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3719581B2 (ja) * 1998-06-08 2005-11-24 東京瓦斯株式会社 複合空調装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010243086A (ja) * 2009-04-07 2010-10-28 Daikin Ind Ltd 冷凍装置
WO2015125219A1 (ja) * 2014-02-18 2015-08-27 三菱電機株式会社 空気調和装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11656008B2 (en) * 2018-01-30 2023-05-23 Exergyn Ltd. Heat pump utilising the shape memory effect

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