[go: up one dir, main page]

WO2000033002A1 - Refrigerateur - Google Patents

Refrigerateur Download PDF

Info

Publication number
WO2000033002A1
WO2000033002A1 PCT/JP1999/006666 JP9906666W WO0033002A1 WO 2000033002 A1 WO2000033002 A1 WO 2000033002A1 JP 9906666 W JP9906666 W JP 9906666W WO 0033002 A1 WO0033002 A1 WO 0033002A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
compressor
heat
heat storage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP1999/006666
Other languages
English (en)
Japanese (ja)
Inventor
Hiromune Matsuoka
Osamu Tanaka
Masahiro Honda
Takuya Kotani
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to AU14123/00A priority Critical patent/AU1412300A/en
Publication of WO2000033002A1 publication Critical patent/WO2000033002A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present invention relates to a refrigeration apparatus, and more particularly, to a refrigeration apparatus that condenses at two different temperatures.
  • a heat storage type air conditioner as disclosed in Japanese Patent Application Laid-Open No. 3-28672.
  • This air conditioner has a main passage in which a compressor, an outdoor heat exchanger, an outdoor expansion valve, an indoor expansion valve, and an indoor heat exchanger are connected in order, while the air conditioner is housed in a heat storage tank and forms a heat storage medium and a refrigerant.
  • a heat storage heat exchanger for exchanging heat between them is provided.
  • the air conditioner is configured to perform a normal cooling operation using no heat storage, a heat storage cooling operation using heat storage, and the like.
  • the refrigerant is condensed from the compressor in the outdoor heat exchanger, then depressurized by the indoor expansion valve, evaporated in the indoor heat exchanger, and circulated back to the compressor.
  • the first compressor is connected to the outdoor heat exchanger
  • the second compressor is connected to the heat storage heat exchanger.
  • the refrigerant discharged from the first compressor is condensed in the outdoor heat exchanger to become a liquid refrigerant
  • the refrigerant discharged from the second compressor is condensed in the heat storage heat exchanger to become a liquid refrigerant.
  • the refrigerant is condensed in the outdoor heat exchanger and the heat storage heat exchanger and then joined, so that the degree of supercooling of the refrigerant is reduced.
  • the refrigerant temperature at the outlet of the outdoor heat exchanger is high and the refrigerant temperature at the outlet of the heat storage heat exchanger is low, when both refrigerants are mixed, the degree of supercooling decreases, and the cooling capacity is sufficient. There was a problem that it could not be improved.
  • the present invention has been made in view of the above points, and aims to effectively utilize two heat exchangers having different condensing temperatures, to suppress a decrease in the degree of supercooling of the refrigerant, and to expand the capacity. It is the purpose. Disclosure of the invention
  • the liquid refrigerant from the first heat exchanger (23) and the gas refrigerant from the second compressor (31) are separated from each other, then merged, and supplied to the second heat exchanger (32). That is what we did.
  • the second heat exchanger (32) After the refrigerant discharged from the first compressor (21) condenses in the first heat exchanger (23), it merges with the refrigerant discharged from the second compressor (31), and After condensing at a lower temperature than the first heat exchanger (23) in the heat exchanger (32), the pressure is reduced by the expansion mechanism (E4), 3 It is intended for refrigeration systems that perform at least refrigerant circulation that evaporates in the heat exchanger (42) and returns to the first compressor (21) and the second compressor (31). Further, the second heat exchanger (32) has a plurality of paths.
  • a second solution is the first solution, wherein the first refrigerant passage (20) of the refrigeration circuit (1R) decompresses the refrigerant condensed in the first heat exchanger (23) and diverts the refrigerant. It is equipped with an expansion mechanism (E9).
  • a third solution is the above-mentioned first solution, wherein the first heat exchanger (23) is an air heat exchanger, and the second heat exchanger (32) is a water heat exchanger. I have.
  • the fourth solution is the first solution, wherein the second heat exchanger (32) is housed in the heat storage tank (11) and condenses the refrigerant by the cold heat of the heat storage tank (11). It is composed of
  • the first solution first, when the first compressor (21) and the second compressor (31) are driven, the high-pressure gas refrigerant discharged from the first compressor (21) is subjected to the first heat exchange. Flow into the vessel (23). In the first heat exchanger (23), the gas refrigerant is condensed into a liquid refrigerant.
  • the first heat exchanger (23) is an air heat exchanger, the gas refrigerant exchanges heat with air and condenses. Thereafter, the liquid refrigerant is divided into a plurality of parts.
  • the refrigerant is depressurized by the expansion mechanism (E9) before being divided.
  • the separated liquid refrigerant is also divided into a plurality of high-pressure gas refrigerants discharged from the second compressor (31), so that the liquid refrigerant and the gas refrigerant merge to form a two-phase refrigerant, respectively.
  • This two-phase refrigerant flows through each path of the second heat exchanger (32).
  • the two-phase refrigerant is condensed by exchanging heat with the heat storage medium of the heat storage tank (11) because the second heat exchanger (32) is housed in the heat storage tank (11).
  • the liquid refrigerant becomes the third refrigerant passage (40).
  • the liquid refrigerant condensed in the first heat exchanger (23) and the gas refrigerant discharged from the second compressor (31) are separated from each other and then joined to form a second heat exchanger ( 32), the degree of supercooling of the refrigerant can be sufficiently ensured, so that the capacity of cooling and the like can be surely improved.
  • the refrigerant after each split has a significantly different ratio between the liquid and the gas.
  • the pass-gas refrigerant in which only the liquid refrigerant flows flows A path occurs.
  • the entire ice in the heat storage tank (11) cannot be melted evenly.
  • the ratio of the liquid refrigerant to the gas refrigerant in each path of the second heat exchanger (32) can be made substantially equal, so that the ice is melted evenly and the efficiency of heat storage utilization is improved. Can be done.
  • the degree of supercooling of the refrigerant in each path of the second heat exchanger (32) can be made substantially equal, so that the degree of subcooling of the entire refrigerant can be increased, and the capacity can be further improved. be able to.
  • the pressure of the liquid refrigerant is reduced before the branch, the pressure can be reduced by one expansion mechanism (E9) as compared with the case where the pressure is reduced after the branch. As a result, an increase in the number of parts can be prevented.
  • FIG. 1 is a refrigerant circuit diagram showing an embodiment of the present invention.
  • FIG. 2 is a piping structure diagram showing a junction of a liquid refrigerant and a gas refrigerant.
  • FIG. 6 is a Mollier chart showing a comparative example of the refrigerant characteristics in the high-load operation.
  • FIG. 7 is a refrigerant circuit diagram showing a refrigerant circulation direction in low-load operation during cooling.
  • FIG. 8 is a refrigerant circuit diagram showing a refrigerant circulation direction in normal operation during heating.
  • FIG. 9 is a refrigerant circuit diagram showing a refrigerant circulation direction in a heat storage operation during heating.
  • FIG. 10 is a refrigerant circuit diagram showing a refrigerant circulation direction in a utilization operation during heating.
  • the air conditioner (10) of the present embodiment is a refrigerating device including a heat storage tank (11), and is a multi-type including a plurality of indoor units (12, 12, etc. It is configured.
  • the air conditioner (10) includes a refrigeration circuit (1R) having a first refrigerant passage (20), a second refrigerant passage (30), and a third refrigerant passage (40). Further, the refrigeration circuit (1R) includes a main circuit (1M) including a first refrigerant passage (20) and a third refrigerant passage ( 40 ).
  • the first refrigerant passage (20) is a three-way switching valve (22), an outdoor heat exchanger (23), an outdoor expansion valve (E2), and a first on-off valve (S2) from the discharge side of the first compressor (21). And are connected in series by a refrigerant pipe (24).
  • the outdoor heat exchanger (23) is a first heat exchanger, and is constituted by an air heat exchanger.
  • a plurality of indoor units (12, 12, ...) are connected in parallel to the third refrigerant passage (40).
  • the third refrigerant passage (40) is connected to the plurality of indoor units (12, 12, ).
  • a three-way switching valve (41) is connected in series.
  • the indoor unit (12) is configured such that an indoor expansion valve (E4) as an expansion mechanism and an indoor heat exchanger (42) as a third heat exchanger are connected in series.
  • the indoor expansion valve (E4), the indoor heat exchanger (42), and the three-way switching valve (41) are connected by a refrigerant pipe (43).
  • One end of the third refrigerant passage (40) on the side of the indoor expansion valve (E4) is connected to one end of the first refrigerant passage (20) on the side of the first on-off valve (S2), and is connected to the third refrigerant passage (40).
  • One end of the three-way switching valve (41) is connected to the suction side of the first compressor (21).
  • the first refrigerant passage (20) and the third refrigerant passage (40) constitute a closed circuit main circuit (1M).
  • the heat exchanger for heat storage (32) is a second heat exchanger, which is stored in a heat storage tank (11) in which a heat storage medium such as water is stored, and has a condensation temperature higher than that of the outdoor heat exchanger (23). It consists of a lower water heat exchanger.
  • the heat storage tank (11) stores a heat storage medium such as water or brine.
  • the heat exchanger for heat storage (32) which is not shown, has a plurality of paths through which the refrigerant flows, generates ice on the surface of the heat exchanger and stores cold heat in the heat storage tank (11), while hot water And heat is stored in the heat storage tank (11).
  • a connecting pipe (50) is connected between the discharge side of the first compressor (21) of the first refrigerant passage (20) and the discharge side of the second compressor (31) of the second refrigerant passage (30).
  • the connecting pipe (50) is provided with a third on-off valve (S5).
  • One end of a suction pipe (60) is connected to the three-way switching valve (22) of the first refrigerant passage (20), and the other end of the suction pipe (60) is connected to both compressors in the third refrigerant passage (40). It is connected to the suction side of (21, 31).
  • the three-way switching valve (22) is configured to connect the outdoor heat exchanger (23) to either the discharge side or the suction side of the compressors (21, 31). I have.
  • One end of a high-pressure pipe (70) is connected to the three-way switching valve (41) of the third refrigerant passage (40), and the other end of the high-pressure pipe (70) is connected to a second end of the second refrigerant passage (30). It is connected between the compressor (31) and the second on-off valve (S3).
  • One end Y of a low pressure pipe (80) is connected between the second on-off valve (S3) of the second refrigerant passage (30) and the heat storage heat exchanger (32), and the low pressure pipe (80) is A four-way valve (S8) is provided, and the other end is connected between the three-way switching valve (41) of the third refrigerant passage (40) and the suction sides of both compressors (21, 31).
  • a branch pipe (90) is branched between the outdoor expansion valve (E2) and the first on-off valve (S2) in the first refrigerant passage (20).
  • the branch pipe (90) is provided with a branch expansion valve (E9) as an expansion mechanism, and a connection point Y between the heat storage heat exchanger (32) and the low-pressure pipe (80) in the second refrigerant passage (30). Is connected between.
  • a branch pipe (9a) is provided at the connection end (L portion in FIG. 1) of the second refrigerant passage (30) in the branch pipe (90) of the first refrigerant passage (20). ing.
  • the distribution pipe (9a) is connected to a plurality of refrigerant pipes (9b, 9b,...), And divides the refrigerant from the outdoor heat exchanger (23) into a plurality of parts.
  • a header (3a) is provided at a connection portion (L portion in FIG. 1) of the branch pipe (90) of the first refrigerant passage (20) in the second refrigerant passage (30). ing.
  • the header (3a) is connected to a plurality of refrigerant pipes (3b, 3b,...) And divides the refrigerant from the second compressor (31) into a plurality.
  • the refrigeration circuit (1R) performs at least high-load operation using heat storage during cooling operation, performs low-load operation using heat storage and heat storage operation that stores cold heat during cooling operation, and performs at least heating operation during heating operation.
  • Normal operation without heat storage and utilization operation with heat storage It is configured to perform a heat storage operation for storing heat.
  • the liquid refrigerant is decompressed by the heat storage expansion valve (E3), and then evaporated by the heat storage heat exchanger (32) to cool the heat storage medium and become a gas refrigerant.
  • the gas refrigerant flows through the low-pressure pipe (80) and returns to the first compressor (21) and the second compressor (31). This circulation of the refrigerant is repeated, and ice is generated on the surface of the heat exchanger, and the cold heat is stored in the heat storage tank (11).
  • This high-load operation is the above-described cooling operation using heat storage, and is the most characteristic operation mode of the present invention, as shown in FIG.
  • the two three-way switching valves (22, 41) are switched to the solid lines in FIG. 4, the first on-off valve (S2) is closed, and the second open / close valve (S3) is open. Then, the third on-off valve (S5) switches to the closed state, the fourth on-off valve (S8) switches to the closed state, the outdoor expansion valve (E2) and the heat storage expansion valve (E3) fully open, and the branch expansion valve. (E9) and the indoor expansion valve (E4) are adjusted to the predetermined opening. First, the first compressor (21) and the second compressor (31) are driven.
  • the high-pressure gas refrigerant discharged from the first compressor (21) flows to the outdoor heat exchanger (23) through the three-way switching valve (22).
  • the gas refrigerant exchanges heat with outdoor air to be condensed to become a liquid refrigerant.
  • the liquid refrigerant in the first refrigerant passage (20) passes through the outdoor expansion valve (E2), flows to the branch pipe (90), is decompressed to a predetermined pressure by the branch expansion valve (E9), and flows to the branch pipe (9a). Flows.
  • the high-pressure gas refrigerant discharged from the second compressor (31) flows through the second on-off valve (S3) to the header (3a).
  • the liquid refrigerant flows through each indoor unit (12), is decompressed by the indoor expansion valve (E4), and is evaporated by the indoor heat exchanger (42) to become a gas refrigerant. Thereafter, the gas refrigerant passes through the three-way switching valve (41) and returns to the first compressor (21) and the second compressor (31). This refrigerant circulation is repeated to cool the room.
  • the high-pressure gas refrigerant is discharged from the first compressor (21), and the high-pressure gas refrigerant is condensed by the outdoor heat exchanger (23) to become the liquid refrigerant at the point B.
  • This liquid refrigerant is decompressed to the point C at the branch expansion valve (E9).
  • the high-pressure gas refrigerant is discharged from the second compressor (31), and the high-pressure gas refrigerant (point D) and the liquid refrigerant (point C) in the first refrigerant passage (20) merge to E
  • the point is a two-phase refrigerant.
  • the two-phase refrigerant is condensed in the heat storage heat exchanger (32) to become a liquid refrigerant at point F.
  • This liquid refrigerant is decompressed to the point G by the indoor expansion valve (E4) and evaporated by the indoor heat exchanger (42).
  • the gas refrigerant at point H is returned, and the gas refrigerant returns to the first compressor (21) and the second compressor (31).
  • the liquid refrigerant condensed in the outdoor heat exchanger (23) flows to the connection point X without flowing through the branch pipe (90), and the liquid condensed in the heat storage heat exchanger (32) at the connection point X. Merge with coolant.
  • the high-pressure gas refrigerant is discharged from the first compressor (21) (point A) and condensed in the outdoor heat exchanger (23) (point B). Reduce the pressure by (E2) (point C).
  • the high-pressure gas refrigerant is discharged from the second compressor (31) (point D) and condensed in the heat storage heat exchanger (32) (point I).
  • the two three-way switching valves (22, 41) are switched to the solid line side in FIG. 7, the first on-off valve (S2) is closed, and the second on-off valve (22) is closed. S3) is closed, the third on-off valve (S5) is open, and the fourth on-off valve (S8) is closed, and the outdoor expansion valve (E2), branch expansion valve (E9) and thermal storage expansion
  • the valve (E3) is fully opened, and the indoor expansion valve (E4) is adjusted to a predetermined opening.
  • the heat storage tank (11) stores heat. The cold of the medium is stored.
  • the liquid refrigerant flows through each indoor unit (12), is decompressed by the indoor expansion valve (E4), and is evaporated by the indoor heat exchanger (42) to become a gas refrigerant. Thereafter, the gas refrigerant passes through the three-way switching valve (41) and returns to the first compressor (21) and the second compressor (31). This refrigerant circulation is repeated to cool the room.
  • the two three-way switching valves (22, 41) are switched to the solid line side in FIG. 8, the first on-off valve (S2) is opened, and the second on-off valve (22) is opened. S3) is closed, the third on-off valve (S5) is open, the fourth on-off valve (S8) is closed, the indoor expansion valve (E4) is fully open, and the branch expansion valve (E9) The heat storage expansion valve (E3) is adjusted to a fully closed state, and the outdoor expansion valve (E2) is adjusted to a predetermined opening.
  • the first compressor (21) and the second compressor (31) are driven.
  • the high-pressure gas refrigerant discharged from the first compressor (21) and the second compressor (31) merges and passes from the second refrigerant passage (30) through the high-pressure pipe (70) and the three-way switching valve (41). It flows to the indoor heat exchanger (42).
  • the indoor heat exchanger (42) the gas refrigerant exchanges heat with indoor air and condenses to become a liquid refrigerant.
  • the liquid refrigerant passes through the indoor expansion valve (E4) and flows to the first refrigerant passage (20).
  • the liquid refrigerant passes through the first on-off valve (S2), is decompressed by the outdoor expansion valve (E2), and exchanges heat with outdoor air in the outdoor heat exchanger (23) to evaporate. Become. Thereafter, the gas refrigerant flows from the three-way switching valve (22) through the suction pipe (60), and returns to the first compressor (21) and the second compressor (31). This circulation of the refrigerant is repeated to heat the room. Heat storage operation during heating
  • the two three-way switching valves (22, 41) are switched to the solid line side in FIG. 9, the first on-off valve (S2) is opened, and the second on-off valve (22) is opened.
  • S3) is open
  • the third on-off valve (S5) is open
  • the fourth on-off valve (S8) is closed
  • the heat storage expansion valve (E3) is fully open
  • the branch expansion valve ( E9) and the indoor expansion valve (E4) are adjusted to the fully closed state
  • the outdoor expansion valve (E2) is adjusted to the predetermined opening.
  • the first compressor (21) and the second compressor (31) are driven.
  • the high-pressure gas refrigerant discharged from the first compressor (21) and the second compressor (31) merges and flows to the heat storage heat exchanger (32) through the second refrigerant passage (30).
  • the gas refrigerant exchanges heat with the heat storage medium and condenses to become a liquid refrigerant.
  • the liquid refrigerant passes through the heat storage expansion valve (E3), flows to the connection point X, and flows to the first refrigerant passage (20).
  • the liquid refrigerant passes through the first on-off valve (S2), is decompressed by the outdoor expansion valve (E2), and exchanges heat with outdoor air in the outdoor heat exchanger (23) to evaporate. Become. Thereafter, the gas refrigerant flows from the three-way switching valve (22) through the suction pipe (60), and returns to the first compressor (21) and the second compressor (31). This circulation of the refrigerant is repeated, and the heat such as hot water is stored in the heat storage tank (11).
  • This use operation is a heating operation using the above-described heat storage.
  • the two three-way switching valves (22, 41) are switched to the solid line side in FIG. 10, and the first on-off valve ( S2) is closed, the second on-off valve (S3) is closed, the third on-off valve (S5) is open, the fourth on-off valve (S8) is open, and the indoor expansion valve (E4 ) Is fully opened, the branch expansion valve (E9) and the outdoor expansion valve (E2) are fully closed, and the heat storage expansion valve (E3) is adjusted to a predetermined opening.
  • the first compressor (21) and the second compressor (31) are driven.
  • the high-pressure gas refrigerant discharged from the first compressor (21) and the second compressor (31) merges and passes from the second refrigerant passage (30) through the high-pressure pipe (70) and the three-way switching valve (41). It flows to the indoor heat exchanger (42).
  • the indoor heat exchanger (42) the gas refrigerant condenses by exchanging heat with indoor air, and is cooled by liquid cooling. It becomes a medium.
  • This liquid refrigerant passes through the indoor expansion valve (E4) and flows into the second refrigerant passage (30).
  • the liquid refrigerant is decompressed by the heat storage expansion valve (E3), exchanges heat with the heat storage medium in the heat storage heat exchanger (32), and evaporates to become a gas refrigerant.
  • the gas refrigerant flows through the low-pressure pipe (80) and returns to the first compressor (21) and the second compressor (31). This circulation of the refrigerant is repeated to heat the room.
  • the liquid refrigerant condensed in the outdoor heat exchanger (23) and the gas refrigerant discharged from the second compressor (31) are respectively branched and then merged for each branch.
  • the degree of supercooling of the refrigerant can be sufficiently ensured, so that the cooling capacity can be reliably improved.
  • liquid refrigerant and the gas refrigerant are separated and merged, it is possible to distribute the liquid refrigerant and the gas refrigerant in substantially equal proportions and supply them to each path of the heat storage heat exchanger (32). it can.
  • the ratio of the liquid refrigerant to the gas refrigerant in each path of the heat storage heat exchanger (32) can be made substantially equal, so that the ice is melted evenly and the efficiency of the heat storage utilization is reduced. Can be improved.
  • the degree of supercooling of the refrigerant in each path of the heat storage heat exchanger (32) can be made substantially equal, so that the degree of supercooling of the entire refrigerant can be increased, and the capacity can be further improved. it can.
  • the pressure of the liquid refrigerant is reduced before the branch, the pressure can be reduced by one branch expansion valve (E9) as compared with the case where the pressure is reduced after the branch. As a result, an increase in the number of parts can be prevented.
  • the heat storage tank (11) Since cold energy can be used efficiently, peak power consumption can be reliably shifted.
  • the heating operation is also performed.
  • only the cooling operation may be performed. Only the circulation may be performed.
  • the present invention is not limited to the air conditioner (10), and may be any device that performs a so-called two-temperature condensation operation having different condensation temperatures, and may be various refrigeration devices applied to a freezer or the like.
  • the first heat exchanger (23) is not necessarily limited to an air heat exchanger
  • the second heat exchanger (32) is not limited to a water heat exchanger or a heat storage heat exchanger
  • the third heat exchanger (42) is not limited to indoor heat exchangers.
  • the number of branches in the first refrigerant passage (20) and the number of branch flows in the second refrigerant passage (30) are the same. That is, the refrigerant pipes (9b, 9b,...) Of the branch pipe (9a) in the first refrigerant passage (20) and the refrigerant pipes (3b, 3b,...) Of the header (3a) in the second refrigerant passage (30) are connected. They are the same.
  • the number of passes of the heat storage heat exchanger (32) may be larger than the number of divided refrigerants, or at least good. That is, the number of passes may be larger than the number of the refrigerant pipes (3b, 3b,...) Of the header (3a) in the present embodiment, or at least good. In short, it is only necessary that the refrigerants that have joined together flow through a plurality of paths.
  • the refrigeration apparatus according to the present invention is useful when condensing a refrigerant at two temperatures, and is particularly suitable for a refrigeration apparatus having a heat storage tank.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

Ce refrigérateur comprend un circuit de réfrigération (1R) dans lequel sont reliées entre elles une première voie de réfrigérant (20) comportant un premier compresseur (21) et un échangeur thermique extérieur (23), une deuxième voie de réfrigérant (30) comportant un second compresseur (31) et un échangeur thermique pour l'accumulation de la chaleur (32), et une troisième voie de réfrigérant (40) comportant des valves d'expansion intérieures (E4) et des échangeurs thermiques intérieurs (42). Dans ce circuit, l'échangeur thermique pour l'accumulation de la chaleur (32) présente plusieurs voies, le réfrigérant sortant du premier compresseur (21) est divisé en de multiples voies après sa condensation dans l'échangeur thermique extérieur (23), le réfrigérant sortant du deuxième compresseur (31) est également divisé en plusieurs voies, les deux réfrigérants de chaque voie sont réunis et amenés à passer dans chaque voie de l'échangeur thermique pour l'accumulation de la chaleur (32) et, après la condensation du réfrigérant dans l'échangeur thermique pour l'accumulation de la chaleur (32), la pression du réfrigérant est réduite dans les valves d'expansion intérieures (E4), le réfrigérant est amené à s'évaporer dans les échangeurs thermiques intérieurs (42) et il est renvoyé dans les premier et second compresseurs (21 et 31).
PCT/JP1999/006666 1998-12-01 1999-11-30 Refrigerateur Ceased WO2000033002A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU14123/00A AU1412300A (en) 1998-12-01 1999-11-30 Refrigerator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP10341903A JP3087745B2 (ja) 1998-12-01 1998-12-01 冷凍装置
JP10/341903 1998-12-01

Publications (1)

Publication Number Publication Date
WO2000033002A1 true WO2000033002A1 (fr) 2000-06-08

Family

ID=18349646

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1999/006666 Ceased WO2000033002A1 (fr) 1998-12-01 1999-11-30 Refrigerateur

Country Status (5)

Country Link
JP (1) JP3087745B2 (fr)
KR (1) KR100381634B1 (fr)
CN (2) CN1120968C (fr)
AU (1) AU1412300A (fr)
WO (1) WO2000033002A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1722179A3 (fr) * 2005-05-13 2012-01-25 LG Electronics Inc. Système de refroidissement par régénération et sa méthode de commande
CN103375845A (zh) * 2012-04-28 2013-10-30 青岛海信日立空调系统有限公司 一种空调循环系统
EP2966382A1 (fr) * 2014-07-07 2016-01-13 LG Electronics Inc. Appareil de conditionnement d'air régénératif et procédé de commande de celui-ci
EP3904782A4 (fr) * 2019-05-22 2022-03-02 Hefei Midea Heating & Ventilating Equipment Co., Ltd. Chauffe-eau
EP3995761A1 (fr) * 2020-11-05 2022-05-11 Daikin Industries, Ltd. Circuit de réfrigérant pour un appareil de réfrigération doté d'un stockage thermique et procédé de commande d'un circuit de réfrigérant
WO2022097680A1 (fr) * 2020-11-05 2022-05-12 Daikin Industries, Ltd. Circuit de fluide frigorigène destiné à un appareil de réfrigération à stockage thermique et procédé de commande d'un circuit de fluide frigorigène
WO2022229612A1 (fr) * 2021-04-30 2022-11-03 Dyson Technology Limited Système de réfrigération

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1300526C (zh) * 2005-06-14 2007-02-14 上海理工大学 具有热水功能的四季节能环保冷暖空调机
US9423159B2 (en) * 2009-12-21 2016-08-23 Trane International Inc. Bi-directional cascade heat pump system
CN103403460A (zh) * 2011-02-25 2013-11-20 开利公司 带有蓄冰的空调系统
JP5327308B2 (ja) * 2011-09-30 2013-10-30 ダイキン工業株式会社 給湯空調システム
CN103388920B (zh) * 2013-08-15 2015-07-15 湖北美的电冰箱有限公司 制冷系统和具有它的冰箱
CN104567075B (zh) * 2013-10-28 2017-10-03 珠海格力电器股份有限公司 空调循环装置及其控制方法
JP6020549B2 (ja) * 2014-12-26 2016-11-02 ダイキン工業株式会社 蓄熱式空気調和機
CN105571193B (zh) * 2016-02-27 2017-12-19 李建华 一种热泵应用及贮能系统
CN105783332B (zh) * 2016-05-13 2019-04-16 李建华 实现绿态小区的热泵系统
TWI658238B (zh) * 2016-08-12 2019-05-01 國立勤益科技大學 分體式儲能系統及其方法
CN107883601B (zh) * 2016-09-30 2020-07-07 大金工业株式会社 空调系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0328672A (ja) * 1989-06-23 1991-02-06 Daikin Ind Ltd 蓄熱式空気調和装置
JPH03294754A (ja) * 1990-04-11 1991-12-25 Daikin Ind Ltd 空気調和装置
JPH074721A (ja) * 1993-02-19 1995-01-10 Tokyo Electric Power Co Inc:The 蓄熱式空気調和装置
JPH10227497A (ja) * 1996-12-13 1998-08-25 Daikin Ind Ltd 氷蓄熱装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0328672A (ja) * 1989-06-23 1991-02-06 Daikin Ind Ltd 蓄熱式空気調和装置
JPH03294754A (ja) * 1990-04-11 1991-12-25 Daikin Ind Ltd 空気調和装置
JPH074721A (ja) * 1993-02-19 1995-01-10 Tokyo Electric Power Co Inc:The 蓄熱式空気調和装置
JPH10227497A (ja) * 1996-12-13 1998-08-25 Daikin Ind Ltd 氷蓄熱装置

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1722179A3 (fr) * 2005-05-13 2012-01-25 LG Electronics Inc. Système de refroidissement par régénération et sa méthode de commande
CN103375845A (zh) * 2012-04-28 2013-10-30 青岛海信日立空调系统有限公司 一种空调循环系统
CN103375845B (zh) * 2012-04-28 2015-05-20 青岛海信日立空调系统有限公司 一种空调循环系统
EP2966382A1 (fr) * 2014-07-07 2016-01-13 LG Electronics Inc. Appareil de conditionnement d'air régénératif et procédé de commande de celui-ci
JP2016017738A (ja) * 2014-07-07 2016-02-01 エルジー エレクトロニクス インコーポレイティド 蓄熱式空調装置及びその制御方法
US9970688B2 (en) 2014-07-07 2018-05-15 Lg Electronics Inc. Regenerative air-conditioning apparatus and method of controlling the same
EP3904782A4 (fr) * 2019-05-22 2022-03-02 Hefei Midea Heating & Ventilating Equipment Co., Ltd. Chauffe-eau
EP3995761A1 (fr) * 2020-11-05 2022-05-11 Daikin Industries, Ltd. Circuit de réfrigérant pour un appareil de réfrigération doté d'un stockage thermique et procédé de commande d'un circuit de réfrigérant
WO2022097680A1 (fr) * 2020-11-05 2022-05-12 Daikin Industries, Ltd. Circuit de fluide frigorigène destiné à un appareil de réfrigération à stockage thermique et procédé de commande d'un circuit de fluide frigorigène
WO2022229612A1 (fr) * 2021-04-30 2022-11-03 Dyson Technology Limited Système de réfrigération
GB2606518A (en) * 2021-04-30 2022-11-16 Dyson Technology Ltd A refrigeration system
GB2606518B (en) * 2021-04-30 2024-05-01 Dyson Technology Ltd A refrigeration system

Also Published As

Publication number Publication date
AU1412300A (en) 2000-06-19
JP3087745B2 (ja) 2000-09-11
CN2409462Y (zh) 2000-12-06
KR100381634B1 (ko) 2003-04-21
CN1120968C (zh) 2003-09-10
KR20010074725A (ko) 2001-08-09
CN1294672A (zh) 2001-05-09
JP2000171117A (ja) 2000-06-23

Similar Documents

Publication Publication Date Title
JP5611353B2 (ja) ヒートポンプ
JP3087745B2 (ja) 冷凍装置
US6237356B1 (en) Refrigerating plant
CN100373112C (zh) 冷冻装置
WO2014020651A1 (fr) Dispositif de climatisation
WO1998006983A1 (fr) Conditionneur d'air
AU1685800A (en) Refrigerating plant
WO2013146415A1 (fr) Dispositif de chauffage du type pompe à chaleur
JP2007240025A (ja) 冷凍装置
JP4608303B2 (ja) 蒸気圧縮式ヒートポンプ
JP2006003023A (ja) 冷凍装置
CN1818506A (zh) 冷冻装置
JP2698118B2 (ja) 空気調和装置
JP3071328B2 (ja) 蓄熱式冷房装置
JP2010014343A (ja) 冷凍装置
JP4270803B2 (ja) 冷熱生成システム
JP2646709B2 (ja) 空気調和装置
JP3781340B2 (ja) 蓄熱式冷凍空調装置
JPH10325641A (ja) 冷凍装置
JP3451505B2 (ja) 冷媒回路
JPH04324067A (ja) 空気調和装置
JP2003202135A (ja) 蓄熱式空気調和装置
JPH04257660A (ja) 二段圧縮冷凍サイクル装置
JP2000320908A (ja) 冷凍サイクル回路
JP2524382B2 (ja) 空気調和装置

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 99804304.4

Country of ref document: CN

ENP Entry into the national phase

Ref document number: 2000 14123

Country of ref document: AU

Kind code of ref document: A

AK Designated states

Kind code of ref document: A1

Designated state(s): AE AL AM AT AU AZ BA BB BG BR BY CA CH CN CR CU CZ DE DK DM EE ES FI GB GD GE GH GM HR HU ID IL IN IS KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 1020017000753

Country of ref document: KR

WWP Wipo information: published in national office

Ref document number: 1020017000753

Country of ref document: KR

122 Ep: pct application non-entry in european phase
REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

WWG Wipo information: grant in national office

Ref document number: 1020017000753

Country of ref document: KR