WO2017164201A1 - Système de refroidissement et son procédé de commande - Google Patents

Système de refroidissement et son procédé de commande Download PDF

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Publication number
WO2017164201A1
WO2017164201A1 PCT/JP2017/011321 JP2017011321W WO2017164201A1 WO 2017164201 A1 WO2017164201 A1 WO 2017164201A1 JP 2017011321 W JP2017011321 W JP 2017011321W WO 2017164201 A1 WO2017164201 A1 WO 2017164201A1
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Prior art keywords
cooling
refrigerant
heat
amount
cooling system
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PCT/JP2017/011321
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English (en)
Japanese (ja)
Inventor
寿人 佐久間
吉川　実
雅人 矢野
正樹 千葉
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日本電気株式会社
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Priority to JP2018507352A priority Critical patent/JPWO2017164201A1/ja
Publication of WO2017164201A1 publication Critical patent/WO2017164201A1/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 used for cooling an electronic device or the like and a method for controlling the cooling system, and more particularly, to a cooling system using a phase change of a refrigerant and a method for controlling the cooling system.
  • 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)
  • 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. That is, a primary cooling device such as a compression refrigeration cycle takes heat from the object to be cooled to generate warm heat, and a secondary cooling device such as an adsorption refrigeration cycle converts this warm heat to cold.
  • a related cooling device including such a primary cooling device and a secondary cooling device can efficiently cool one cooling target by combining the cold heat generated by the primary cooling device and the secondary cooling device, respectively. It is.
  • the cooling device is operated at the rated power with the highest efficiency in order to obtain the required amount of cooling heat with the minimum power.
  • the amount of cooling necessary for cooling the cooling target is equal to or less than the rated cooling capacity of the primary cooling device, that is, equal to or less than the amount of cooling generated by the primary cooling device during rated operation, surplus cooling is generated.
  • the primary cooling device is operating at a rated cooling capacity of 20 kW.
  • the amount of cold generated by the secondary cooling device generally varies depending on the amount of cold generated by the primary cooling device.
  • the secondary cooling device generates 50% of the cold generated by the primary cooling device. That is, the secondary cooling device is operated at a rated cooling capacity of 10 kW.
  • the amount of cooling (necessary cooling) necessary for cooling the object to be cooled is equal to or less than the rated cooling capacity of the primary cooling device, for example, 15 kW. In this case, if the primary cooling device and the secondary cooling device are operated at the rated cooling capacity of 20 kW and 10 kW, respectively, excessive cooling (excess cooling) is generated.
  • the primary cooling device and the secondary cooling are performed so that the sum of the cooling heat generated by the primary cooling device and the secondary cooling device matches the cooling heat necessary for cooling the object to be cooled.
  • the device is operated, no excessive cooling is generated.
  • the cooling efficiency is significantly reduced.
  • An object of the present invention is a cooling system that solves the above-described problem that it is difficult to efficiently cool a cooling system that combines a plurality of refrigeration cycles according to the amount of heat to be cooled, and It is to provide a control method of a cooling system.
  • the cooling system of the present invention is connected to a first cooling means having a first refrigerant transporting means through which a first refrigerant received from a cooling target circulates, and to the first refrigerant transporting means.
  • the second refrigerant transporting means through which the branching refrigerant that is a part circulates, and the second refrigerant that receives heat from the first refrigerant circulating through the first refrigerant transporting means via the second refrigerant and cools the branching refrigerant. It has a cooling means and a heat storage means for storing heat transported by the second refrigerant.
  • the cooling system control method of the present invention is connected to a first cooling means having a first refrigerant transporting means through which a first refrigerant received from a cooling target circulates, and to the first refrigerant transporting means. Heat is received from the first refrigerant circulating through the first refrigerant transporting means through the second refrigerant transporting means through which the branching refrigerant that is a part of the refrigerant circulates, and cools the branching refrigerant Controlling the flow rate of the second refrigerant passing through the heat storage tank with respect to the cooling system having the second cooling means and the heat storage tank storing the second refrigerant that transports the cold generated by the second cooling means. To do.
  • cooling can be efficiently performed according to the heat generation amount of the cooling target even in the case of a configuration in which a plurality of refrigeration cycles are combined.
  • 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 means 110, a second cooling means 120, a second refrigerant transport means 121, and a heat storage means 130.
  • 1st cooling means 110 is provided with the 1st refrigerant transportation means 111 through which the 1st 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 first refrigerant circulates.
  • the second cooling means 120 receives heat (H2) from the first refrigerant circulating through the first refrigerant transport means 111 via the second refrigerant, and cools (H3) the branched refrigerant.
  • the heat storage means 130 stores heat transported by the second refrigerant.
  • the cooling system 100 includes the heat storage means 130. Therefore, even if excessive heat is generated according to the cooling capacity of the first cooling unit 110 and the second cooling unit 120 and the amount of heat received from the cooling target 10, the heat storage unit 130 stores this heat. be able to. As a result, after the heat storage means 130 performs the necessary heat storage, the operation of the first cooling means 110 and the second cooling means 120 is stopped, and cooling is performed by the heat stored in the heat storage means 130, for example, cold heat. It becomes possible to do.
  • the heat storage means 130 may include a heat storage tank that stores the second refrigerant, and the heat storage tank may be positioned in a flow path through which the second refrigerant circulates.
  • the second refrigerant can be configured to transport the cold generated by the second cooling means 120.
  • the second refrigerant may be configured to transport the heat received from the first refrigerant circulating in the first refrigerant transport means 111.
  • 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.
  • a low boiling point material can be used as the first refrigerant.
  • an organic refrigerant such as hydrofluorocarbon or hydrofluoroether can be used.
  • water can be used as the second refrigerant.
  • the control method of the cooling system according to the present embodiment is a control method for a cooling system having a first cooling means, a second refrigerant transporting means, a second cooling means, and a heat storage tank.
  • the first cooling means includes first refrigerant transporting means for circulating the first refrigerant received from the object to be cooled.
  • the second refrigerant transporting means is connected to the first refrigerant transporting means, and a branched refrigerant that is a part of the first refrigerant circulates.
  • the second cooling means receives heat from the first refrigerant circulating through the first refrigerant transport means via the second refrigerant, and cools the branched refrigerant.
  • a heat storage tank stores the 2nd refrigerant
  • coolant which goes through said heat storage tank with respect to the cooling system comprised in this way is controlled.
  • the excess cooling heat produced according to the cooling capacity of the first cooling means and the second cooling means and the amount of heat received from the cooling target can be stored.
  • the operations of the first cooling means and the second cooling means are stopped, and cooling can be performed by the cold heat of the second refrigerant stored in the heat storage tank.
  • the first cooling means may be controlled. And it can be set as the structure which controls the flow volume of the 2nd refrigerant
  • the reference cooling capacity described above is typically a rated cooling capacity.
  • the control method as described with reference to FIG. 4B that is, the first cooling means and the second cooling means generate the first cooling means as compared with the case where control is performed so as to match the amount of heat received.
  • the cooling means operates in a state closer to the reference cooling capacity (rated cooling capacity). Therefore, it becomes possible to cool efficiently.
  • the cooling system 100 and the cooling system control method of the present embodiment even when the configuration is a combination of a plurality of refrigeration cycles such as the first cooling means and the second cooling means.
  • the cooling can be efficiently performed according to the heat generation amount of the cooling target.
  • 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 heat storage device (heat storage 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 configured by a radiator or the like, and generates a refrigerant vapor that is vaporized by receiving heat from the first 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 flow path of the first refrigerant that flows back from the evaporator 1110 to the evaporator 1110 via the compressor 1120, the condenser 1130, and the expansion valve 1140.
  • a low boiling point material such as an organic refrigerant such as hydrofluorocarbon or hydrofluoroether can be used.
  • a solid line arrow in FIG. 2 indicates the flow of the first refrigerant.
  • the second cooling device 1200 constitutes either an adsorption refrigeration cycle or an absorption refrigeration cycle.
  • the adsorption refrigeration machine 1201 circulates water or the like as a second 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 the flow of water as the second refrigerant of the adsorption refrigeration machine 1201.
  • the second refrigerant transport unit 1210 constitutes a flow path through which the branched refrigerant that is a part of the first 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 portion 1150 and the second refrigerant on the heat receiving side of the second cooling device 1200.
  • the heat exchanger (heat exchanging means) 1220 for exchanging heat between the branched refrigerant circulated by the second refrigerant transport unit 1210 and the second refrigerant on the cooling side of the second cooling device 1200 may be provided. it can.
  • the heat storage device 1300 stores heat transported by the second refrigerant.
  • the heat storage device 1300 can include a heat storage tank that stores the second refrigerant, and can be configured to be located in a flow path through which the second refrigerant circulates.
  • the heat storage device 1300 can be configured to be positioned in the flow path of the second refrigerant on the cooling side of the second cooling device 1200. That is, FIG. 2 shows a case where the heat storage device 1300 is installed in the water circulation path between the adsorption refrigerator 1201 and the heat exchanger 1220. In this case, the water as the second refrigerant transports the cold generated by the second cooling device 1200.
  • cooling system 1000 Next, the operation of the cooling system 1000 according to the present embodiment will be described. Below, the case where the cooling system 1000 is used for cooling a server etc. is demonstrated as an example. Therefore, the temperatures described below are typical numerical examples in this case.
  • the refrigerant liquid (first refrigerant) that has flowed into the evaporator 1110 composed 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 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 (second refrigerant) 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 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 cooling system 1000 can include a flow rate control unit (flow rate control unit) that controls the flow rate of the second refrigerant that passes through the heat storage tank provided in the heat storage device 1300.
  • the flow rate control unit (not shown) can typically be configured using a flow rate control valve.
  • the cooling system 1000 can be configured to include a first cooling device 1100, a second cooling device 1200, and a control unit (control means) that controls the flow rate control unit.
  • the control unit (not shown) operates the cooling system 1000 as follows based on at least one of the flow rate and temperature of the first refrigerant, the flow rate and temperature of the second refrigerant, and the power consumption of the cooling target. It can be set as the structure which controls a flow control part so that it may do.
  • the amount of heat received from the object 10 to be cooled is larger than the amount of heat generated when the first cooling device 1100 operates at the reference cooling capacity.
  • the amount of heat received at this time is assumed to be smaller than the total amount of cold heat, which is the total amount of cold heat generated when the first cooling device 1100 and the second refrigerant transport unit 1210 operate at the reference cooling capacity.
  • the reference cooling capacity is typically the rated cooling capacity, and the following description will be made assuming that the reference cooling capacity is the rated cooling capacity.
  • the rated cooling capacity of the first cooling device 1100 is 20 kW
  • the rated cooling capacity of the second cooling device 1200 is set by the heat generated at that time.
  • the rated cooling capacity of the second cooling device 1200 is 10 kW.
  • the cooling target 10 is generating 25 kW of heat that is larger than the first cooling device 1100 rated cooling capacity (20 kW).
  • the first cooling device 1100 and the second cooling device 1200 are controlled so that the first cooling device 1100 and the second cooling device 1200 each operate at the rated cooling capacity. Then, the amount of surplus cooling heat (5 kW) that is the difference between the total cooling amount (30 kW) that is the sum of the cooling amounts generated by the first cooling device 1100 and the second cooling device 1200 and the amount of heat received from the cooling target 10 (25 kW). ).
  • the 1st cooling device 1100 and the 2nd cooling device 1200 operate
  • the generated 30 kW of cold energy 25 kW can be used for cooling the cooling object 10 (necessary cold energy), and the remaining 5 kW of cold energy can be stored.
  • the flow rate control unit is controlled so that water (second refrigerant) having a capacity for transporting the excess amount of cold heat (5 kW) is stored in the heat storage tank.
  • the amount of heat received from the object 10 to be cooled is equal to or less than the amount of heat generated when the first cooling device 1100 operates at the rated cooling capacity. Specifically, for example, as illustrated in FIG. 3B, it is assumed that the cooling target 10 generates heat of 15 kW, which is smaller than the rated cooling capacity (20 kW) of the first cooling device 1100.
  • the first cooling device 1100 and the second cooling device 1200 are controlled so that the first cooling device 1100 and the second cooling device 1200 each operate at the rated cooling capacity. Then, the cold heat (10 kW) generated by the second cooling device 1200 is stored. Specifically, the flow control unit is controlled so that water (second refrigerant) transporting cold heat (10 kW) generated by the second cooling device 1200 is stored in the heat storage tank.
  • the heat storage tank can increase the heat storage amount in proportion to the volume, it is possible to store in the heat storage tank water having a capacity for transporting all of the cold heat generated by the second cooling device 1200. .
  • water as the second refrigerant is inexpensive, the cost of the cooling system 1000 is greatly reduced as compared with the case where the first cooling device 1100 stores a low-boiling organic refrigerant used as the first refrigerant. be able to.
  • the first cooling device 1100 is controlled such that the amount of heat generated by the first cooling device 1100 is equal to the amount of heat received from the object 10 to be cooled.
  • the first cooling device 1100 is controlled so as to generate only the cold energy (15 kW) necessary for cooling.
  • the heat storage device 1300 stores the cold generated by the second cooling device 1200 at this time.
  • the flow control unit is controlled so that water (second refrigerant) transporting cold heat (7.5 kW) generated by the second cooling device 1200 is stored in the heat storage tank.
  • the cooling system 1000 By controlling the cooling system 1000 to perform such an operation, it is possible to prevent surplus in the cold generated by the first cooling device 1100. Further, when compared with the case where the first cooling device 1100 is operated so that the total amount of cold heat generated by the first cooling device 1100 and the second cooling device 1200 matches the required cold heat (see FIG. 4B). The first cooling device 1100 operates closer to the rated cooling capacity (20 kW). Therefore, the cooling system 1000 can operate with high efficiency.
  • the operations of the first cooling device 1100 and the second cooling device 1200 are stopped, and the heat stored in the heat storage device 1300 is stored. It becomes possible to perform cooling.
  • the cooling system 1000 is configured to control the flow rate of water (second refrigerant) that passes through the heat storage tank provided in the heat storage device 1300.
  • the present invention is not limited to this, and the amount of cold heat stored may be increased by lowering the water temperature stored in the heat storage tank. This is because the second cooling device 1200 constituting the adsorption refrigeration cycle can adjust the temperature of the generated cold water (second refrigerant).
  • cooling system 1000 and the cooling system control method of the present embodiment even when the configuration is a combination of a plurality of refrigeration cycles, cooling is efficiently performed according to the heat generation amount of the cooling target. can do.
  • the cooling system described in Additional remark 1 WHEREIN The cooling system described in Additional remark 1 WHEREIN: The said thermal storage means is equipped with the thermal storage tank which stores the said 2nd refrigerant
  • the cooling system according to supplementary note 3, comprising a flow rate control means for controlling a flow rate of the second refrigerant passing through the heat storage tank.
  • the cooling system includes a control unit that controls the first cooling unit, the second cooling unit, and the flow rate control unit, wherein the control unit includes the cooling unit
  • the amount of heat received from the target is larger than the amount of heat generated when the first cooling means operates at the reference cooling capacity, and the first cooling means and the second cooling means operate at the reference cooling capacity, respectively.
  • the first cooling means and the second cooling means so that each of the first cooling means and the second cooling means operates at a reference cooling capacity when the total cooling quantity is smaller than the total cooling quantity that is generated.
  • a cooling system for controlling the flow rate control means so as to store the second refrigerant having a capacity for transporting an excess amount of cold heat, which is a difference between the total amount of cold energy and the amount of received heat, in the heat storage tank. .
  • the cooling system includes a control unit that controls the first cooling unit, the second cooling unit, and the flow rate control unit, and the control unit is configured to control the cooling target.
  • the amount of heat received is equal to or less than the amount of heat generated when the first cooling means operates at a reference cooling capacity
  • the amount of heat generated by the first cooling means is equal to the amount of heat received.
  • a cooling system that controls the flow rate control means so as to store the second refrigerant, which controls the first cooling means and transports the cold generated by the second cooling means, in the heat storage tank.
  • the control means includes a flow rate and a temperature of the first refrigerant, a flow rate and a temperature of the second refrigerant, and the cooling target.
  • the first cooling means constitutes a vapor compression refrigeration cycle, and the refrigerant vapor received and vaporized by the first refrigerant is received.
  • Expansion means for generating a refrigerant liquid, wherein the first refrigerant transporting means returns from the evaporation means to the evaporation means via the compression means, the condensation means, and the expansion means.
  • 1 refrigerant flow path, and the second refrigerant transporting means forms a flow path through which the branched refrigerant circulates between the evaporation means and the expansion means from between the evaporation means and the compression means. Cooling system.
  • the cooling system according to supplementary note 9, further comprising heat exchange means for exchanging heat between the branched refrigerant and the second refrigerant on the cooling side of the second cooling means, wherein the condensing means includes the high-pressure refrigerant.
  • a cooling system for exchanging heat between the steam and the second refrigerant on the heat receiving side of the second cooling means.
  • the second cooling means is a cooling system that constitutes either an adsorption refrigeration cycle or an absorption refrigeration cycle.
  • the amount of heat received from the object to be cooled is greater than the amount of heat generated when the first cooling means operates at a reference cooling capacity, and the first If the cooling means and the second cooling means are smaller than the total amount of cold heat generated when the cooling means and the second cooling means operate at the reference cooling capacity, respectively, the first cooling means and the second cooling means are respectively The second refrigerant having a capacity for controlling the first cooling means and the second cooling means so as to operate at a reference cooling capacity and transporting an excess amount of cold heat that is a difference between the total amount of cold heat and the amount of received heat.
  • a control method of a cooling system for controlling a flow rate of the second refrigerant passing through the heat storage tank so as to be stored in the heat storage tank.
  • Cooling system 110 1st cooling means 111 1st refrigerant
  • Cooling system 1100 1st cooling device 1110 Evaporator 1120 Compressor 1130 Condenser DESCRIPTION OF SYMBOLS 1140
  • Expansion valve 1150 1st refrigerant

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Abstract

L'invention porte sur un système de refroidissement dans lequel une pluralité de cycles frigorifiques sont combinés, et dans lequel il est souvent difficile d'effectuer un refroidissement efficace en fonction de la quantité de chaleur émise par un objet à refroidir. La solution selon la présente invention concerne un système de refroidissement comportant : un premier moyen de refroidissement muni d'un premier moyen de transport de fluide frigorigène destiné à faire circuler un premier fluide frigorigène ayant reçu de la chaleur en provenance de l'objet à refroidir ; un second moyen de transport de fluide frigorigène relié au premier moyen de transport de fluide frigorigène, le second moyen de transport de fluide frigorigène étant destiné à faire circuler un fluide frigorigène de dérivation qui est une partie du premier fluide frigorigène ; un second moyen de refroidissement recevant de la chaleur par l'intermédiaire d'un second fluide frigorigène à partir du premier fluide frigorigène circulant dans le premier moyen de transport de fluide frigorigène, et destiné à refroidir le fluide frigorigène de dérivation ; et un moyen de stockage de la chaleur destiné à stocker la chaleur transportée par le second fluide frigorigène.
PCT/JP2017/011321 2016-03-25 2017-03-22 Système de refroidissement et son procédé de commande WO2017164201A1 (fr)

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JPH08145437A (ja) * 1994-11-17 1996-06-07 Hitachi Ltd 蓄熱式冷暖房装置およびその制御方法
JP2007170792A (ja) * 2005-12-26 2007-07-05 Takenaka Komuten Co Ltd 空調装置
JP2013181666A (ja) * 2012-02-29 2013-09-12 Fujitsu General Ltd 空気調和システム
WO2017051532A1 (fr) * 2015-09-25 2017-03-30 日本電気株式会社 Système et procédé de refroidissement

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Publication number Priority date Publication date Assignee Title
JPH03144263A (ja) * 1989-10-28 1991-06-19 Hitachi Ltd 蓄熱型圧縮式冷凍サイクル
JPH0769093B2 (ja) * 1990-04-10 1995-07-26 東京瓦斯株式会社 冷水発生用コージェネレーション装置及びこれを利用した地下鉄冷房装置
JPH08145437A (ja) * 1994-11-17 1996-06-07 Hitachi Ltd 蓄熱式冷暖房装置およびその制御方法
JP2007170792A (ja) * 2005-12-26 2007-07-05 Takenaka Komuten Co Ltd 空調装置
JP2013181666A (ja) * 2012-02-29 2013-09-12 Fujitsu General Ltd 空気調和システム
WO2017051532A1 (fr) * 2015-09-25 2017-03-30 日本電気株式会社 Système et procédé de refroidissement

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