WO2017169925A1 - Système et procédé de refroidissement - Google Patents

Système et procédé de refroidissement Download PDF

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Publication number
WO2017169925A1
WO2017169925A1 PCT/JP2017/011001 JP2017011001W WO2017169925A1 WO 2017169925 A1 WO2017169925 A1 WO 2017169925A1 JP 2017011001 W JP2017011001 W JP 2017011001W WO 2017169925 A1 WO2017169925 A1 WO 2017169925A1
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Prior art keywords
heat
cooling
pressure refrigerant
vapor
refrigerant liquid
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PCT/JP2017/011001
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English (en)
Japanese (ja)
Inventor
正樹 千葉
吉川　実
寿人 佐久間
雅人 矢野
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日本電気株式会社
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Priority to JP2018509063A priority Critical patent/JPWO2017169925A1/ja
Publication of WO2017169925A1 publication Critical patent/WO2017169925A1/fr

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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
    • F25B1/00—Compression machines, plants or systems with non-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
    • 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

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.
  • a phase change cooling method using a refrigerant vaporization and condensation cycle is used to cool a heat source. Then, after the refrigerant vapor generated at this time is compressed by a compressor and converted into a high-temperature refrigerant vapor, a cooling / exhaust heat recovery system has been developed in which heat is exchanged with water to generate and reuse hot water.
  • a related cooling / waste heat recovery system described in Patent Document 1 includes a vapor compression refrigerator that cools a heat-generating device, and an adsorption refrigerator that is thermally coupled to the condenser of the vapor compression refrigerator.
  • the related cooling and exhaust heat recovery system is a thermal connection of a desorbing adsorbent and a condenser that make up an adsorption refrigeration machine, and the exhaust refrigeration machine uses the exhaust heat from the electronic equipment. It is configured to form a desorption process.
  • the adsorption refrigerator includes an adsorbent for adsorption, an adsorbent for desorption, an evaporator, a condenser, and the like, and can produce cold water.
  • warm water is supplied to the desorbing adsorbent, and cooling water is supplied to the adsorbing adsorbent.
  • the heat removal from the electronic device can be used to form a desorption process and to generate cold water, thereby obtaining an energy saving effect. It is supposed to be.
  • JP 2012-37203 A Japanese Patent Laid-Open No. 10-19418
  • An object of the present invention is a cooling system that solves the above-described problem that a cooling system that performs cooling and exhaust heat recovery by combining a plurality of refrigeration cycles varies in efficiency of the cooling system due to changes in the external environment. It is to provide a system and a cooling method.
  • the cooling system of the present invention includes a first cooling means by a vapor compression refrigeration cycle that compresses refrigerant vapor received and vaporized from a cooling target and condenses it by releasing heat to form a high-pressure refrigerant liquid, and adsorbate by heat. And a second cooling means by an adsorption refrigeration cycle for desorbing the refrigerant, and an overheating heat exchanging means for exchanging heat between the refrigerant vapor and the high-pressure refrigerant liquid.
  • the cooling method of the present invention comprises a vapor compression refrigeration cycle that compresses refrigerant vapor received and vaporized from the object to be cooled, condenses it by releasing heat and uses it as a high-pressure refrigerant liquid, and adsorbs adsorbate by desorbing heat.
  • a refrigerating cycle is configured to exchange heat between refrigerant vapor and high-pressure refrigerant liquid.
  • the cooling system and the cooling method of the present invention it is possible to suppress fluctuations in the efficiency of the cooling system due to changes in the external environment even when the cooling and exhaust heat recovery are configured by combining a plurality of refrigeration cycles. Can do.
  • FIG. 9 is a diagram for explaining the operation of the cooling system according to the second embodiment of the present invention, and shows a Ph diagram in the case where a configuration including a heat exchanger for overheating is provided. It is the schematic which shows the structure of the cooling system which concerns on the 3rd Embodiment of this invention.
  • 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, and a heat exchange unit 130 for overheating.
  • the first cooling means 110 constitutes a vapor compression refrigeration cycle that compresses the refrigerant vapor R1 vaporized by receiving heat (H1) from the object to be cooled 10 and condenses it by releasing heat (H2) to form a high-pressure refrigerant liquid R2. To do.
  • the second cooling means 120 constitutes an adsorption refrigeration cycle in which the adsorbate is desorbed by this amount of heat (H2).
  • the overheating heat exchanging means 130 causes the refrigerant vapor R1 and the high-pressure refrigerant liquid R2 to exchange heat (H3).
  • the second cooling means 120 by the adsorption refrigeration cycle reduces the amount of heat (H2) recovered when the temperature or humidity of the outside air rises. Therefore, the temperature of the high-pressure refrigerant liquid R2 in the first cooling means 110 increases.
  • the heat exchanger 130 for superheating can move the amount of heat corresponding to the temperature rise to the low-pressure refrigerant vapor R1.
  • the amount of heat (H2) recovered by the second cooling means 120 can be increased, so that the performance of the second cooling means 120 by the adsorption refrigeration cycle can be improved.
  • fluctuations in the efficiency of the cooling system 100 due to changes in the external environment can be suppressed.
  • the first cooling unit 110 may include a heat receiving unit, a compression unit, a heat dissipation unit, and an expansion unit.
  • the heat receiving means vaporizes the refrigerant liquid by heat reception (H1) to generate the refrigerant vapor R1.
  • the compression means compresses the refrigerant vapor R1 to generate high-pressure refrigerant vapor.
  • the heat dissipating means condenses the high-pressure refrigerant vapor by releasing heat (H2) to generate a high-pressure refrigerant liquid R2.
  • the expansion means generates a refrigerant liquid that expands the high-pressure refrigerant liquid R2 to a low pressure.
  • a low-boiling-point material can be used for the refrigerant of the first cooling means 110.
  • an organic refrigerant such as hydrofluorocarbon or hydrofluoroether can be used.
  • the second cooling means 120 can be configured to include a desorption means, a condensation means, an evaporation means, and an adsorption means.
  • the desorption means receives heat (heat amount H2) from the high-pressure refrigerant vapor and desorbs the adsorbate.
  • the condensing means condenses the desorbed adsorbate.
  • the evaporation means generates cold heat by evaporating the condensed adsorbate.
  • the adsorbing means adsorbs the evaporated adsorbate.
  • water vapor, ammonia, methanol, ethanol or the like can be used as the adsorbate of the second cooling means 120 described above.
  • the heat exchanger 130 for superheating includes a first channel structure in which the refrigerant vapor R1 flows, a second channel structure in which the high-pressure refrigerant liquid R2 flows, and heat exchange between the refrigerant vapor R1 and the high-pressure refrigerant liquid R2. It can be set as the structure provided with the heat exchange means which mediates. Specifically, for example, an outer layer pipe through which the refrigerant vapor R1 flows and an inner layer pipe through which the high-pressure refrigerant liquid R2 flows are provided, and a double pipe that shares the outer peripheral surface of the inner layer tube and the inner peripheral surface of the outer layer tube is provided. It can be configured.
  • a vapor compression refrigeration cycle in which the refrigerant vapor received and vaporized from the object to be cooled is compressed and condensed by releasing the amount of heat to form a high-pressure refrigerant liquid is configured.
  • an adsorption refrigeration cycle in which the adsorbate is desorbed by the amount of heat is configured. Then, heat exchange is performed between the refrigerant vapor and the high-pressure refrigerant liquid.
  • the above-described vapor compression refrigeration cycle can be configured to vaporize the refrigerant liquid by receiving heat to generate refrigerant vapor and compress the refrigerant vapor to generate high-pressure refrigerant vapor. Furthermore, the high pressure refrigerant vapor can be condensed by releasing heat to generate a high pressure refrigerant liquid, and the high pressure refrigerant liquid can be expanded to generate a low pressure refrigerant liquid.
  • the adsorption refrigeration cycle described above receives heat from the high-pressure refrigerant vapor to desorb the adsorbate, condenses the desorbed adsorbate, and evaporates the condensed adsorbate to generate cold heat. It can be set as the structure including adsorb
  • the cooling system 100 and the cooling method of the present embodiment even when the cooling and exhaust heat recovery are performed by combining a plurality of refrigeration cycles, the cooling system due to a change in the external environment The fluctuation of the efficiency can be suppressed.
  • FIG. 2 schematically shows the configuration of a cooling system 1000 according to the second embodiment of the present invention.
  • the solid arrows indicate the refrigerant flow
  • the white arrows indicate the heat flow.
  • the cooling system 1000 includes a heat recovery apparatus 1100, an adsorption refrigeration apparatus (second cooling means) 1200, and a heat circulation unit (heat circulation means) 1300.
  • the cooling system 1000 has a configuration in which, for example, a heat source 21 such as a server mounted on a server rack 20 disposed in a data center (DC) is a cooling target, and the recovered heat is reused by the adsorption refrigeration apparatus 1200. That is, the cooling system 1000 according to the present embodiment is an exhaust heat recovery type cooling system.
  • the heat recovery apparatus 1100 includes a heat receiving section (heat receiving means) 1110, a compressor (compression means) 1120, a heat exchanger (heat radiating means) 1130, an expansion valve (expansion means) 1140, and an overheating heat exchanger (overheating heat exchange). Means) 1150.
  • the heat receiving part 1110, the compressor 1120, the heat exchanger 1130, and the expansion valve 1140 constitute a first cooling means.
  • the heat receiving unit 1110 receives heat from the heat source 21 and absorbs heat by vaporizing the refrigerant stored inside.
  • the refrigerant vapor evaporated in the heat receiving unit 1110 moves in the low-pressure vapor transport pipe 1161.
  • the compressor 1120 compresses the refrigerant vapor.
  • the heat exchanger 1130 condenses the high-pressure refrigerant vapor that has been compressed and heated, and generates hot water using the energy of the high-pressure refrigerant vapor.
  • the high-pressure refrigerant liquid condensed in the heat exchanger 1130 is transported to the expansion valve 1140 through the high-pressure liquid transport pipe 1162.
  • the expansion valve 1140 converts the high-pressure refrigerant liquid into a low pressure.
  • the superheat heat exchanger 1150 thermally connects the low-pressure steam transport pipe 1161 and the high-pressure liquid transport pipe 1162.
  • the superheat heat exchanger 1150 can be a double pipe heat exchanger including an outer pipe pipe as the low-pressure steam transport pipe 1161 and an inner pipe pipe as the high-pressure liquid transport pipe 1162 (for example, Patent Document 2). reference). In this case, it is possible to adopt a configuration in which the refrigerant vapor flows in the outer pipe and the high-pressure refrigerant liquid flows in the inner pipe.
  • the superheat heat exchanger 1150 supplies the heat of the condensed high-pressure refrigerant liquid to the low-pressure refrigerant vapor, thereby overheating the low-pressure refrigerant vapor and reducing the temperature of the high-pressure refrigerant liquid. That is, it is possible to increase the heat supply amount and supply temperature in the heat exchanger 1130 and to lower the temperature of the high-pressure refrigerant liquid sent to the expansion valve 1140. Thereby, the performance of the heat receiving part 1110 can be improved. Moreover, liquid compression in the compressor 1120 can be prevented by the heat exchanger for overheating 1150.
  • the adsorption refrigeration apparatus 1200 includes an evaporator (evaporating means) 1210, an adsorbing part (adsorbing means) 1220, a desorbing part (desorbing means) 1230, and a condenser (condensing means) 1240.
  • the evaporator 1210 generates water vapor as an adsorbate.
  • the adsorption unit 1220 adsorbs water vapor to the adsorbent 1221.
  • the desorption unit 1230 desorbs the water vapor adsorbed on the adsorbent 1231.
  • the condenser 1240 condenses the water vapor desorbed from the adsorbent 1231.
  • Cooling water 1250 is supplied to the adsorbent 1221 and the condenser 1240 of the adsorption unit 1220.
  • Hot water via the heat exchanger 1130 is supplied to the adsorbent 1231 of the desorption unit 1230.
  • the adsorbent 1221 and the adsorbent 1231 are in an adsorbing state, the other is in a desorbing state.
  • the generation of water vapor can be promoted by disposing the evaporator 1210 and the adsorbent 1221 of the adsorbing unit 1220 in the same space. At this time, the cold water flow 1260 thermally connected to the evaporator 1210 is cooled by the cooling action by the heat of vaporization accompanying the generation of water vapor to generate cold water.
  • the heat circulation unit 1300 transports the amount of heat released when the high-pressure refrigerant vapor condenses from the heat recovery apparatus 1100 constituting the first cooling means to the heat receiving side of the adsorption refrigeration apparatus (second cooling means) 1200. Circulate the heat exchange fluid (hot water).
  • the heat circulation unit 1300 may include a hot water supply pipe 1310 and a hot water return pipe 1320.
  • the pump P can be used as a drive source for circulating the heat exchange fluid (warm water).
  • the hot water supply pipe 1310 supplies the hot water generated by the heat exchanger 1130 to the adsorbent 1231 of the desorption unit 1230 included in the adsorption refrigeration apparatus 1200.
  • the hot water return pipe 1320 transports the hot water that has been deprived of heat by desorption to the heat exchanger 1130 again.
  • the heat receiving unit 1110 provided in the heat recovery apparatus 1100 is attached in thermal connection with the heat source 21.
  • the refrigerant is vaporized by receiving heat from the heat source 21, and refrigerant vapor is generated.
  • the refrigerant vapor passes through the low-pressure vapor transport pipe 1161 and the superheat heat exchanger 1150 and flows into the compressor 1120.
  • the refrigerant vapor flowing into the compressor 1120 is compressed into high-pressure and high-temperature high-pressure refrigerant vapor and flows into the heat exchanger 1130.
  • the high-pressure refrigerant vapor that has flowed in is condensed by being deprived of heat by the hot water circulating between the heat exchanger 1130 and the adsorption refrigeration apparatus 1200 via the heat circulation unit 1300.
  • the condensed high-pressure refrigerant liquid passes through the high-pressure liquid transport pipe 1162 and the superheat heat exchanger 1150 and then becomes a low-pressure refrigerant liquid through the expansion valve 1140 and is returned to the heat receiving unit 1110.
  • the hot water that has received the heat energy in the heat exchanger 1130 becomes higher in temperature, and is supplied to the adsorbent 1231 of the desorption unit 1230 included in the adsorption refrigeration apparatus 1200 through the hot water supply pipe 1310.
  • the hot water supplied with heat to the adsorbent 1231 of the desorption unit 1230 is supplied again to the heat exchanger 1130 via the hot water return pipe 1320.
  • Cooling water 1250 is supplied to the adsorbent 1221 and the condenser 1240 of the adsorption unit 1220.
  • the cooling water 1250 is supplied to the adsorption refrigeration apparatus 1200 while keeping the temperature constant by a cooling tower or the like installed outside.
  • a cooling tower or the like installed outside.
  • the amount of water vapor desorbed also decreases, so that the temperature drop of the hot water in the desorption part 1230 is also suppressed, and the hot water returns to the heat exchanger 1130 in a high temperature state.
  • the temperature of the high-pressure refrigerant liquid flowing out from the heat exchanger 1130 also increases or the condensation becomes insufficient.
  • Fig. 3 shows the temperature dependence of the efficiency of the adsorption refrigeration system.
  • the vertical axis represents the efficiency of the adsorption refrigeration apparatus
  • the horizontal axis represents the temperature of hot water supplied to the adsorption refrigeration apparatus.
  • it shows about the case where the temperature of the cooling water of an adsorption type refrigerating machine differs.
  • FIG. 4B A Ph diagram of the vapor compression refrigerator at this time is shown in FIG. 4B.
  • the refrigerant of the vapor compression refrigerator becomes insufficiently cooled and the reusable heat quantity H22 is reduced, so that the heat quantity H13 recovered from the heat source is also reduced.
  • the ratio of the amount of heat H13 recovered from the heat source to the amount of work H12 performed by the compressor decreases.
  • the cooling system 1000 of the present embodiment is configured to supply the heat of the high-pressure refrigerant liquid after condensation to the low-pressure refrigerant vapor in the superheat heat exchanger 1150.
  • the low-pressure refrigerant vapor can be overheated and the temperature of the high-pressure refrigerant liquid can be reduced.
  • the Ph diagram at this time is shown in FIG. 4C.
  • the amount of heat recovered from the heat source (H11 + H31) and the amount of heat that can be reused (H21 + H32) are increased (dH) by the amounts of heat H31 and H32 that move due to overheating.
  • the temperature of the hot water supplied to the adsorption refrigeration apparatus 1200 through the hot water supply pipe 1310 increases. Thereby, since the adsorption refrigeration apparatus 1200 operates in the state C shown in FIG. 3, the efficiency of the adsorption refrigeration apparatus 1200 also increases.
  • the cooling system 1000 of this embodiment is configured to include both the superheat heat exchanger 1150 and the adsorption refrigeration apparatus 1200, it is possible to suppress fluctuations in the efficiency of the cooling system due to changes in the external environment. it can. That is, even when the temperature of the high-pressure refrigerant liquid discharged from the heat exchanger 1130 rises due to an increase in the temperature and humidity of the outside air, the amount of heat corresponding to the temperature rise is transferred to the low-pressure refrigerant vapor. Can do. Then, high-temperature high-pressure refrigerant vapor is generated by the compressor 1120, and the hot water flowing out to the hot water supply pipe 1310 can be further heated. As described above, according to the cooling system 1000 of the present embodiment, it is possible to improve the performance of the heat recovery apparatus 1100 by the vapor compression refrigeration cycle and to suppress the performance degradation of the adsorption refrigeration apparatus 1200. it can.
  • FIG. 5 schematically shows the configuration of a cooling system 2000 according to the third embodiment of the present invention.
  • the solid arrows indicate the refrigerant flow
  • the white arrows indicate the heat flow.
  • the cooling system 2000 includes a heat recovery apparatus 1100, an adsorption refrigeration apparatus (second cooling means) 1200, and a heat circulation unit (heat circulation means) 1300.
  • the cooling system 2000 is configured such that, for example, a heat source 21 such as a server mounted in a server rack 20 disposed in a data center (DC) is a cooling target, and the recovered heat is reused by the adsorption refrigeration apparatus 1200. That is, the cooling system 2000 according to the present embodiment is an exhaust heat recovery type cooling system.
  • the heat recovery apparatus 1100 includes a heat receiving section (heat receiving means) 1110, a compressor (compression means) 1120, a heat exchanger (heat radiating means) 1130, an expansion valve (expansion means) 1140, and an overheating heat exchanger (overheating heat exchange). Means) 1150.
  • the adsorption refrigeration apparatus 1200 includes an evaporator (evaporating means) 1210, an adsorbing part (adsorbing means) 1220, a desorbing part (desorbing means) 1230, and a condenser (condensing means) 1240.
  • the heat circulation part 1300 can be configured to include a hot water supply pipe 1310 and a hot water return pipe 1320.
  • the heat receiving unit 1110 provided in the heat recovery apparatus 1100 is attached in thermal connection with the heat source 21.
  • the refrigerant is vaporized by receiving heat from the heat source 21, and refrigerant vapor is generated.
  • the refrigerant vapor passes through the low-pressure vapor transport pipe 1161 and the superheat heat exchanger 1150 and flows into the compressor 1120.
  • the refrigerant vapor flowing into the compressor 1120 is compressed into high-pressure and high-temperature high-pressure refrigerant vapor and flows into the heat exchanger 1130.
  • the high-pressure refrigerant vapor that has flowed in is condensed by being deprived of heat by the hot water circulating between the heat exchanger 1130 and the adsorption refrigeration apparatus 1200 via the heat circulation unit 1300.
  • the condensed high-pressure refrigerant liquid passes through the high-pressure liquid transport pipe 1162 and the superheat heat exchanger 1150 and then becomes a low-pressure refrigerant liquid through the expansion valve 1140 and is returned to the heat receiving unit 1110.
  • the hot water that has received the heat energy in the heat exchanger 1130 becomes higher in temperature, and is supplied to the adsorbent 1231 of the desorption unit 1230 included in the adsorption refrigeration apparatus 1200 through the hot water supply pipe 1310.
  • the adsorption refrigeration apparatus 1200 uses the warm water and the cooling water 1250 to adsorb and desorb water vapor on the adsorbents 1221 and 1231.
  • the evaporator 1210 cools the chilled water passage 1260 thermally connected to the evaporator 1210 by a cooling action by the heat of vaporization of the generated water vapor to generate cold water.
  • the configuration and operation of the cooling system 2000 so far are the same as the configuration and operation of the cooling system 1000 according to the first embodiment.
  • the cooling system 2000 includes a sensor (temperature detection means) 2100 that monitors the temperature of hot water (heat exchange fluid) that has received heat from the heat exchanger 1130 and outputs a detected temperature based on the temperature of the hot water.
  • a sensor temperature detection means 2100 that monitors the temperature of hot water (heat exchange fluid) that has received heat from the heat exchanger 1130 and outputs a detected temperature based on the temperature of the hot water.
  • the configuration was as follows.
  • the control unit (not shown) included in the cooling system 2000 according to the present embodiment falls within a predetermined range. It can be set as the structure which controls one side.
  • the compressor 1120 or the expansion valve 1140 is controlled. Specifically, for example, the rotation speed of the compressor 1120 or the opening degree of the expansion valve 1140 is controlled. Thereby, the temperature rise of a high pressure refrigerant
  • the cooling method of this embodiment in addition to the cooling method according to the first embodiment, circulating hot water (heat exchange fluid) that transports heat from the vapor compression refrigeration cycle to the heat receiving side of the adsorption refrigeration cycle. It was set as the structure containing. And monitoring the temperature of the hot water which received the calorie
  • the vapor compression refrigeration cycle described above can be configured to include compressing the refrigerant vapor to generate a high-pressure refrigerant vapor and generating a low-pressure refrigerant liquid by expanding the high-pressure refrigerant liquid. At this time, at least one of the compression amount of the refrigerant vapor and the expansion amount of the high-pressure refrigerant liquid can be controlled so that the detected temperature falls within a predetermined range.
  • the cooling system 2000 and the cooling method of the present embodiment even when the cooling and exhaust heat recovery are performed by combining a plurality of refrigeration cycles, the cooling system due to a change in the external environment The fluctuation of the efficiency can be suppressed.
  • the coefficient of performance (COP) is one of the indexes representing the energy consumption efficiency of the cooling system, and is represented by the ratio of the amount of heat cooled by the cooling system to the power necessary to operate the cooling system. .
  • the power efficiency of the entire building can be optimized by determining the specified value of the temperature of the hot water in consideration of the efficiency of the cooling system 2000 and the power consumption and efficiency of other air conditioning equipment.
  • a cooling system comprising: a second cooling means based on an adsorption refrigeration cycle; and an overheating heat exchange means for exchanging heat between the refrigerant vapor and the high-pressure refrigerant liquid.
  • the first cooling means includes a heat receiving means for generating a refrigerant vapor by receiving a refrigerant liquid by receiving heat, and a high pressure refrigerant vapor by compressing the refrigerant vapor.
  • Compression means for generating, heat radiating means for condensing the high-pressure refrigerant vapor by releasing the amount of heat to generate the high-pressure refrigerant liquid, and expansion means for generating the refrigerant liquid having a low pressure by expanding the high-pressure refrigerant liquid;
  • the second cooling means receives heat from the high-pressure refrigerant vapor and desorbs the adsorbate, condensing means for condensing the adsorbed adsorbate, and evaporating the condensed adsorbate.
  • a cooling system comprising: an evaporating unit that generates cold heat by the evaporating unit; and an adsorbing unit that adsorbs the evaporated adsorbate.
  • the heat exchange means for overheating includes a first flow path structure in which the refrigerant vapor flows and a second flow path structure in which the high-pressure refrigerant liquid flows. And a heat exchange means for mediating heat exchange between the refrigerant vapor and the high-pressure refrigerant liquid.
  • the heat exchange means for superheating includes an outer layer pipe through which the refrigerant vapor flows and an inner layer pipe through which the high-pressure refrigerant liquid flows.
  • a cooling system comprising a double pipe sharing an outer peripheral surface and an inner peripheral surface of the outer layer pipe.
  • the cooling system comprising a temperature detection means for monitoring a temperature of the heat exchange fluid that has received the heat quantity and outputting a detection temperature based on the temperature of the heat exchange fluid.
  • steam received and vaporized from the cooling object is compressed, it comprises the vapor
  • the vapor compression refrigeration cycle vaporizes a refrigerant liquid by receiving heat to generate the refrigerant vapor, compresses the refrigerant vapor to generate high-pressure refrigerant vapor,
  • the adsorption refrigeration cycle includes: condensing the high-pressure refrigerant vapor by releasing the heat to generate the high-pressure refrigerant liquid, and expanding the high-pressure refrigerant liquid to generate the refrigerant liquid at a low pressure.
  • the cooling method comprising monitoring the temperature of the heat exchange fluid that has received the heat quantity, and acquiring a detected temperature based on the temperature of the heat exchange fluid.
  • the vapor compression refrigeration cycle compresses the refrigerant vapor to generate a high-pressure refrigerant vapor, and generates a refrigerant liquid having a low pressure by expanding the high-pressure refrigerant liquid.
  • Cooling system 110 1st cooling means 120 2nd cooling means 130 Heat exchange means for overheating 1100 Heat recovery device 1110 Heat receiving part 1120 Compressor 1130 Heat exchanger 1140 Expansion valve 1150 Heat exchanger for overheating 1161 Low pressure Steam transport pipe 1162 High-pressure liquid transport pipe 1200 Adsorption refrigeration apparatus 1210 Evaporator 1220 Adsorption part 1230 Desorption part 1221, 1231 Adsorbent 1240 Condenser 1250 Cooling water 1300 Thermal circulation unit 1310 Hot water supply pipe 1320 Hot water return pipe 2100 Sensor 10 Cooling target 20 Server rack 21 Heat source

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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)

Abstract

La présente invention a trait à un système et à un procédé de refroidissement. Dans un procédé de refroidissement combinant une pluralité de cycles frigorifiques destinés à effectuer un refroidissement et à récupérer la chaleur perdue, l'efficacité du système de refroidissement dans un système de refroidissement flucture suite aux changements dans l'environnement externe. Par conséquent, le système de refroidissement selon la présente invention comprend : un premier moyen de refroidissement utilisant un cycle frigorifique du type à compression de vapeur dans lequel une vapeur de fluide frigorigène obtenue suite à l'évaporation du fluide frigorigène après réception de la chaleur en provenance d'un objet à refroidir, est comprimée, et est condensée suite au dégagement d'une quantité de chaleur, en vue d'obtenir un fluide frigorigène liquide à haute pression ; un second moyen de refroidissement utilisant un cycle frigorifique du type à adsorption dans lequel un adsorbat est désorbé en une quantité de chaleur ; et un moyen d'échange de chaleur de surchauffe amenant la chaleur à être échangée entre la vapeur de fluide frigorigène et le fluide frigorigène liquide à haute pression.
PCT/JP2017/011001 2016-03-29 2017-03-17 Système et procédé de refroidissement WO2017169925A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108168145A (zh) * 2017-12-29 2018-06-15 广东申菱环境系统股份有限公司 一种吸附和蒸气压缩结合的制冷系统及其控制方法
CN108469198A (zh) * 2018-03-21 2018-08-31 深圳市英维克科技股份有限公司 一种节能型焓差实验室

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