WO2023013347A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

Info

Publication number
WO2023013347A1
WO2023013347A1 PCT/JP2022/026751 JP2022026751W WO2023013347A1 WO 2023013347 A1 WO2023013347 A1 WO 2023013347A1 JP 2022026751 W JP2022026751 W JP 2022026751W WO 2023013347 A1 WO2023013347 A1 WO 2023013347A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
refrigeration cycle
section
heat
Prior art date
Application number
PCT/JP2022/026751
Other languages
English (en)
Japanese (ja)
Inventor
義和 川邉
誠之 飯高
晃 鶸田
富之 野間
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to EP22852773.5A priority Critical patent/EP4382831A4/fr
Priority to CN202280053780.9A priority patent/CN117795268A/zh
Publication of WO2023013347A1 publication Critical patent/WO2023013347A1/fr

Links

Images

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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02743—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using three four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present disclosure relates to a refrigeration cycle device using a refrigeration cycle and a heat pump cycle.
  • the air flow is controlled in both the outdoor and indoor heat exchangers for both cooling and heating.
  • the flow direction of the coolant is configured to flow in a direction opposite to the direction.
  • FIG. 3 shows the configuration of a heat pump device using a plurality of four-way valves disclosed in Patent Document 1, and shows the state during heating operation.
  • the refrigerant flows in the direction 30 indicating the flow direction of the refrigerant during the heating operation.
  • Refrigerant exiting the compressor 21 passes through a four-way valve 27, a utilization-side four-way valve 28, a utilization-side heat exchanger 22, a utilization-side four-way valve 28, an expansion device 26, a heat source-side four-way valve 29, a heat source-side heat exchanger 23, and a heat source. It returns to the compressor 21 via the side four-way valve 29 and the four-way valve 27 .
  • Air which is an external fluid
  • Air which is an external fluid
  • Air is sent to the user-side heat exchanger 22 by a user-side fan 24 .
  • Air which is an external fluid, is sent to the heat source side heat exchanger 23 by a heat source side fan 25 .
  • the flow direction of the refrigerant is countercurrent to the flow direction 32 of the external fluid.
  • the four-way valve 27, the four-way valve 28 on the usage side, and the four-way valve 29 on the heat source side are switched.
  • the refrigerant exiting the compressor 21 flows in the direction 31 indicating the flow direction of the refrigerant during the cooling operation.
  • the flow direction of the refrigerant becomes a counterflow in which the flow direction is opposite to the flow direction 32 of the external fluid.
  • a check valve bridge refrigerant circuit is used to control whether the user-side heat exchanger is used during heating or cooling.
  • the direction of air flow and the direction of coolant flow are arranged to face each other.
  • the direction of flow of air and the direction of flow of refrigerant are opposed to each other when the heat exchanger functions as an evaporator and when it functions as a condenser, and the refrigerant flow path is cut off.
  • a refrigeration cycle device that realizes excellent performance of a heat exchanger by enabling adjustment of the area and improves operating efficiency.
  • a refrigeration cycle device includes a heat exchanger having a plurality of heat transfer fins and a plurality of heat transfer tubes, and a refrigerant flow adjustment section that adjusts the direction of refrigerant flow.
  • the heat exchanger is partitioned into a plurality of first heat exchanger compartments, and the refrigerant flow conditioner is connected with the first heat exchanger compartments.
  • the first heat exchanger section is regulated by a refrigerant flow conditioner such that refrigerant flows from the leeward side to the windward side whether the heat exchanger functions as an evaporator or as a condenser.
  • a refrigeration cycle device includes a heat exchanger having a plurality of heat transfer fins and a plurality of heat transfer tubes, and a refrigerant flow adjustment section that adjusts the direction of refrigerant flow.
  • the heat exchanger is partitioned into a first heat exchanger section and a second heat exchanger section, and the refrigerant flow conditioner is connected to the first heat exchanger section.
  • the first heat exchanger section is regulated by a refrigerant flow conditioner so that refrigerant flows from the leeward side to the windward side when the heat exchanger functions both as an evaporator and as a condenser.
  • the second heat exchanger section is undirected for refrigerant flow.
  • the refrigeration cycle device according to the present disclosure can achieve excellent heat exchange performance.
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present disclosure.
  • FIG. 2 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present disclosure.
  • FIG. 3 is a configuration diagram of a conventional heat pump device.
  • a heat exchanger that exchanges heat between refrigerant and air is one of the components that has a significant impact on the operating efficiency of air conditioners.
  • One of the representative forms of heat exchangers is a fin-tube heat exchanger in which a refrigerant flows through tubes having fins for promoting heat exchange.
  • a plate fin tube is used in which a plurality of plate fins are stacked and a plurality of tubes arranged in rows penetrate the stacked plate fins. In many cases, the rows of tubes are also multiple.
  • the refrigerant changes from a superheated gas state to a gas-liquid two-phase state, and finally to a supercooled liquid state.
  • the temperature of the refrigerant increases from the windward side to the leeward side. For this reason, it is desirable that the refrigerant flow countercurrently from the leeward side to the windward side.
  • the performance can be improved by flowing the refrigerant from the leeward side to the windward side rather than the configuration in which the refrigerant flows from the windward side to the leeward side.
  • air conditioners such as room air conditioners have often used single-component refrigerants or pseudo-azeotropic refrigerant mixtures.
  • the heat exchanger functions as a condenser, the refrigerant flows countercurrently from the leeward side to the windward side.
  • the heat exchange efficiency is improved by configuring the cooling medium temperature to decrease.
  • the refrigerant absorbs heat and evaporates at an almost constant temperature for single-component refrigerants and quasi-azeotropic refrigerant mixtures.
  • the density of the refrigerant changes greatly as the gas-liquid phase changes, and the flow velocity of the refrigerant flowing through the tube changes.
  • Higher coolant flow velocities increase the heat transfer and pressure drop characteristics on the inner surface of the tube. Therefore, there is a desirable flow rate depending on the wetness of the refrigerant.
  • Optimization of the flow velocity of the coolant is performed by adjusting the cross-sectional area of the coolant channel by changing the number of passes, which is the number of tubes arranged in parallel, and the diameter of the tubes. It is desirable that the cross-sectional area of the coolant channel be decreased as the wettability of the coolant increases.
  • the inventors found the following problems.
  • the smaller the cross-sectional area of the refrigerant outlet channel the better, but in the evaporator, the larger the cross-sectional area of the refrigerant outlet channel. That is, there is a problem that the cross-sectional area of the refrigerant flow path cannot be adjusted in a heat exchanger in which the refrigerant flows in opposite directions both in the case of condensation and in the case of evaporation.
  • the inventors have come to constitute the subject matter of this disclosure in order to solve this problem.
  • FIG. 1 shows a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1.
  • the refrigerating cycle device 100 may include, for example, air conditioners such as room air conditioners and commercial air conditioners, as well as vending machines and showcases.
  • the heat exchangers 40 are arranged in two rows, a windward row 12 and a leeward row 13, with respect to the air flow direction 8.
  • the heat transfer fins 2 have a surface perpendicular to the heat transfer tube 1, and are stacked in large numbers in the depth direction of FIG.
  • the heat exchanger 40 of Embodiment 1 is divided into two.
  • the two compartments are the first heat exchanger compartment 3a and the first heat exchanger compartment 3b.
  • the first heat exchanger section 3a and the first heat exchanger section 3b have different numbers of paths of heat transfer tubes connected in parallel.
  • the first heat exchanger section 3a has four passes and the first heat exchanger section 3b has two passes. It should be noted that the number of paths means the number of flow paths of refrigerant flowing in parallel in the heat exchanger 40 .
  • a check valve bridge refrigerant circuit 5a which is a refrigerant flow adjusting section, is connected to the first heat exchanger section 3a. This ensures that refrigerant flows from the leeward row 13 to the upwind row 12 in the first heat exchanger section 3a, whether the heat exchanger 40 is used as a condenser or as an evaporator.
  • a check valve bridge refrigerant circuit 5b which is a refrigerant flow adjusting section, is connected to the first heat exchanger section 3b. This ensures that refrigerant flows from the leeward row 13 to the upwind row 12 in the first heat exchanger section 3b both when the heat exchanger 40 is used as a condenser and as an evaporator. .
  • the check valve bridge refrigerant circuit 5a which is a refrigerant flow adjusting section, is configured by connecting four check valves 11 in a ring.
  • the check valve bridge refrigerant circuit 5a is connected to the first refrigerant connection 6, the leeward row 13 of the first heat exchanger section 3a, the upwind row 12 of the first heat exchanger section 3a, and the check valve bridge refrigerant circuit 5b. It is connected.
  • the check valve bridge refrigerant circuit 5b which is a refrigerant flow adjusting section, is constructed by connecting four check valves 11 in a ring.
  • the check valve bridge refrigerant circuit 5b is connected to the second refrigerant connection 7, the leeward row 13 of the first heat exchanger section 3b, the upwind row 12 of the first heat exchanger section 3b, and the check valve bridge refrigerant circuit 5a. It is connected.
  • the refrigerant flow adjustment unit 5a and the refrigerant flow adjustment unit 5b may be configured by an on-off valve and a switching valve.
  • the first refrigerant connection port 6 is a connection port that serves as a refrigerant inlet when the heat exchanger 40 is used as a condenser, and serves as a refrigerant outlet when the heat exchanger 40 is used as an evaporator.
  • the second refrigerant connection port 7 is a connection port that serves as a refrigerant outlet when the heat exchanger 40 is used as a condenser, and serves as a refrigerant inlet when the heat exchanger 40 is used as an evaporator. .
  • the type of refrigerant used in the heat exchanger of the refrigeration cycle apparatus of the present disclosure is not limited, and a single-component refrigerant, a pseudo-azeotropic refrigerant mixture, or a non-azeotropic refrigerant mixture may be used.
  • the refrigerant flows in the refrigerant flow direction 9 during condensation. That is, the gas refrigerant flows in from the first refrigerant connection port 6, passes through the check valve bridge refrigerant circuit 5a and the first heat exchanger section 3a, which are the refrigerant flow adjusting section, and returns to the check valve bridge refrigerant circuit 5a. It flows to the check valve bridge refrigerant circuit 5b, which is the flow adjusting section.
  • the number of paths of the heat transfer tubes connected in parallel is four, and the refrigerant flows from the leeward row 13 to the upwind row 12.
  • the refrigerant then flows from the check valve bridge refrigerant circuit 5 b through the first heat exchanger section 3 b back into the check valve bridge refrigerant circuit 5 b and to the second refrigerant connection 7 .
  • the number of paths of the heat transfer tubes connected in parallel is two, and the refrigerant flows from the leeward line 13 to the windward line 12 .
  • the refrigerant flows in the refrigerant flow direction 10 during evaporation. That is, a gas-liquid two-phase refrigerant flows in from the second refrigerant connection port 7, passes through the check valve bridge refrigerant circuit 5b and the first heat exchanger section 3b, which are refrigerant flow adjustment units, and flows through the check valve bridge refrigerant circuit 5b. , and flows to the check valve bridge refrigerant circuit 5a, which is the refrigerant flow adjusting section.
  • the number of paths of the heat transfer tubes connected in parallel is two, and the refrigerant flows from the leeward line 13 to the windward line 12 .
  • the refrigerant then flows from the check valve bridge refrigerant circuit 5 a through the first heat exchanger section 3 a back into the check valve bridge refrigerant circuit 5 a and to the first refrigerant connection 6 .
  • the number of paths of the heat transfer tubes connected in parallel is four, and the refrigerant flows from the leeward row 13 to the upwind row 12.
  • the first heat exchanger sections 3a, 3b are provided in opposite directions for refrigerant to flow from the leeward row 13 to the leeward row 12. flow. Thereby, good heat exchange characteristics can be obtained.
  • the number of paths is four in the first heat exchanger section 3a where the ratio of gas refrigerant is high, and the number of paths is two in the first heat exchanger section 3b where the ratio of liquid refrigerant is high. In this manner, the number of passes, that is, the cross-sectional area of the refrigerant flow path is set according to the state of the refrigerant, and good heat exchange characteristics can be obtained.
  • the refrigeration cycle device includes the heat exchanger 40 configured with a plurality of heat transfer fins 2 and a plurality of heat transfer tubes 1, and a refrigerant flow adjuster for adjusting the direction of refrigerant flow.
  • a part 5 is provided.
  • the heat exchanger 40 is partitioned into a plurality of first heat exchanger sections 3 (first heat exchanger section 3a, first heat exchanger section 3b).
  • a refrigerant flow conditioner 5 is connected to the first heat exchanger section 3 .
  • the first heat exchanger section 3 is adjusted by the refrigerant flow adjusting section 5 so that the refrigerant flows from the leeward side to the windward side in both cases when the heat exchanger 40 functions as an evaporator and as a condenser. be.
  • the heat exchanger 40 is divided into a plurality of first heat exchanger sections 3, the cross-sectional area of the refrigerant flow path can be flexibly set according to the wetness of the refrigerant. Therefore, it is possible to provide a refrigeration cycle apparatus capable of achieving excellent heat exchange performance.
  • the heat exchanger may be provided with a plurality of first heat exchanger sections 3 with different number of paths. That is, the number of paths connected in parallel may be different among the plurality of first heat exchanger sections 3 .
  • the cross-sectional area of the refrigerant flow path can be set according to the wetness of the refrigerant.
  • a check valve bridge refrigerant circuit may be used as the refrigerant flow adjusting section 5 .
  • a non-azeotropic mixed refrigerant may be used as the refrigerant.
  • the configuration of the present disclosure can provide a refrigeration cycle device with excellent heat exchange performance.
  • Embodiment 2 A refrigeration cycle apparatus according to Embodiment 2 will be described below with reference to FIG. Note that in the second embodiment, differences from the first embodiment will be mainly described. In the second embodiment, the same reference numerals are given to the same or equivalent configurations as in the first embodiment. Also, in the second embodiment, explanations that overlap with the first embodiment may be omitted.
  • FIG. 2 shows a configuration diagram of a refrigeration cycle device 100 according to Embodiment 2.
  • FIG. 2 shows a configuration diagram of a refrigeration cycle device 100 according to Embodiment 2.
  • the heat exchanger 50 of Embodiment 2 is partitioned into two.
  • the two compartments are the first heat exchanger compartment 3 and the second heat exchanger compartment 4 .
  • the first heat exchanger section 3 has four paths of heat transfer tubes connected in parallel.
  • the second heat exchanger section 4 has two passes in the downwind row 13 .
  • the two paths join between the leeward row 13 and the upwind row 12 to form one path.
  • the second heat exchanger section 4 therefore has one pass in the upwind row 12 .
  • a plurality of first heat exchanger sections 3 may exist, and the number of paths of heat transfer tubes connected in parallel may be different in the plurality of first heat exchanger sections 3 .
  • the second heat exchanger section 4 is connected to the check valve bridge refrigerant circuit 5, which is a refrigerant flow adjusting section, but the direction of refrigerant flow is not adjusted. Therefore, as shown by the refrigerant flow direction 9 during condensation, the refrigerant flows from the leeward line 13 to the windward line 12 during condensation, and as shown by the refrigerant flow direction 10 during evaporation, the refrigerant flows in the windward line. 12 to the leeward row 13.
  • the check valve bridge refrigerant circuit 5 which is a refrigerant flow adjusting section, is configured by connecting four check valves 11 in a ring.
  • the check valve bridge refrigerant circuit 5 includes a first refrigerant connection 6 , a leeward row 13 of the first heat exchanger section 3 , an upwind row 12 of the first heat exchanger section 3 and a windward line of the second heat exchanger section 4 . It is connected with the lower row 13 .
  • the refrigerant flows in the refrigerant flow direction 9 during condensation. That is, the gas refrigerant flows in from the first refrigerant connection port 6, passes through the check valve bridge refrigerant circuit 5 and the first heat exchanger section 3, which are the refrigerant flow adjusting section, and returns to the check valve bridge refrigerant circuit 5.
  • Second heat exchanger section 4 flows to second refrigerant connection 7 .
  • the number of paths of heat transfer tubes connected in parallel is four, and the refrigerant flows from the leeward row 13 to the upwind row 12 .
  • the number of paths of heat transfer tubes connected in parallel is two.
  • the refrigerant flows through two passes in the downwind row 13 . After passing through the leeward row 13 , the two paths merge into one path, and the refrigerant flows through one path of the upwind row 12 and flows to the second refrigerant connection port 7 .
  • the refrigerant flows in the refrigerant flow direction 10 during evaporation. That is, the gas-liquid two-phase refrigerant flows from the second refrigerant connection port 7, passes through the second heat exchanger section 4, the check valve bridge refrigerant circuit 5 which is the refrigerant flow adjustment section, and the first heat exchanger section 3. , returns to the check valve bridge refrigerant circuit 5 and flows to the first refrigerant connection port 6 . In the second heat exchanger section 4 the refrigerant flows by one pass in the upwind train 12 .
  • the refrigerant flows through the two paths of the leeward row 13 to the first refrigerant connection port 6 .
  • the number of paths of heat transfer tubes connected in parallel is four, and the refrigerant flows from the leeward row 13 to the upwind row 12 .
  • the first heat exchanger section 3 has an opposing section in which refrigerant flows from the leeward row 13 to the upwind row 12 both when the heat exchanger 50 functions as an evaporator and as a condenser. flow. Thereby, good heat exchange characteristics can be obtained.
  • the number of paths is set such that the first heat exchanger section 3, in which the ratio of gas refrigerant is high, has four paths, and the second heat exchanger section 4, in which the ratio of liquid refrigerant is high, has two paths and one path. It is In this manner, the number of paths, that is, the cross-sectional area of the refrigerant flow path is set according to the state of the refrigerant, and good heat exchange characteristics can be obtained.
  • the second heat exchanger section 4 during condensation, the flow direction of the air and the flow direction of the refrigerant are opposite to each other, while during evaporation, the flow direction of the air and the flow direction of the refrigerant are parallel. There is a parallel flow.
  • the heat exchanger 50 functions as an evaporator
  • the second heat exchanger section 4 corresponds to the portion where the refrigerant starts to evaporate, and the refrigerant in the second heat exchanger section 4 is gas-liquid two-phase.
  • the first heat exchanger section 3 corresponds to the end of refrigerant evaporation.
  • the second heat exchanger section 4 has a limited influence on the deterioration of the evaporation performance of the heat exchanger 50 as a whole.
  • the number of paths is doubled in the portion flowing from the windward row 12 to the leeward row 13, that is, the cross-sectional area of the refrigerant passage is doubled. decreases significantly.
  • the temperature of the refrigerant in the upwind row 12 is higher than the temperature of the refrigerant in the leeward row 13 with this pressure drop. That is, in the second heat exchanger section 4, the temperature distribution of the refrigerant is opposed to the air flow direction, and good heat exchange performance is obtained.
  • the refrigeration cycle device includes the heat exchanger 50 configured by the plurality of heat transfer fins 2 and the plurality of heat transfer tubes 1, and the refrigerant flow adjuster for adjusting the direction of refrigerant flow.
  • a part 5 is provided.
  • the heat exchanger 50 is partitioned into one or more first heat exchanger compartments 3 and second heat exchanger compartments 4 .
  • a refrigerant flow conditioner 5 is connected to the first heat exchanger section 3 .
  • the first heat exchanger section 3 is adjusted by the refrigerant flow adjusting section 5 so that the refrigerant flows from the leeward side to the windward side in both cases when the heat exchanger 50 functions as an evaporator and as a condenser. be.
  • the second heat exchanger section 4 is not directed through the refrigerant.
  • the heat exchanger functions as an evaporator or a condenser
  • the direction of air flow and the direction of refrigerant flow can be countercurrent.
  • the cross-sectional area of the coolant flow path can be set according to the wetness of the coolant.
  • the number of refrigerant flow adjusting units can be reduced. Therefore, it is possible to provide an inexpensive refrigeration cycle apparatus while achieving excellent heat exchange performance.
  • the second heat exchanger section 4 may be configured such that the refrigerant flows from the leeward side to the windward side when the heat exchanger functions as a condenser.
  • the heat exchanger functions as a condenser
  • the second heat exchanger section 4 the refrigerant flows countercurrently to the airflow direction, and good heat exchange performance can be obtained.
  • the heat exchanger functions as an evaporator
  • the second heat exchanger section 4 the refrigerant flows parallel to the air flow direction.
  • the decrease in heat exchange performance due to the refrigerant flow direction being parallel to the air flow direction is not as large as in the case of the condenser.
  • the number of paths of the heat transfer tubes 1 connected in parallel in the second heat exchanger section 4 is such that the number of paths on the leeward side is greater than the number of paths on the windward side.
  • the temperature of the refrigerant flowing through the heat transfer tubes 1 of the upwind row 12 can be brought closer to the temperature of the air than the refrigerant flowing through the heat transfer tubes 1 of the leeward row 13 without using the refrigerant flow adjusting unit 5 . Therefore, heat exchange efficiency can be improved. Therefore, it is possible to provide an inexpensive heat exchanger that achieves excellent heat exchange performance.
  • the number of paths of the heat transfer tubes 1 connected in parallel in the second heat exchanger section 4 is equal to the number of paths of the heat transfer tubes 1 connected in parallel in the first heat exchanger section 3.
  • the number of passes may be less than the number of passes of the heat tube 1.
  • the refrigeration cycle device provides good heat exchange performance, and its technology is not limited to air conditioners, but also vending machines and showcases that perform both cooling and heating. It can also be widely applied to

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

L'invention concerne un dispositif à cycle de réfrigération (100) comprenant : un échangeur de chaleur (50) qui comprend une pluralité d'ailettes (2) de transfert de chaleur et une pluralité de tubes (1) de transfert de chaleur ; et une unité de réglage d'écoulement de fluide frigorigène (5) qui règle la direction d'écoulement d'un fluide frigorigène. L'échangeur de chaleur (50) est divisé en une première section (3) d'échangeur de chaleur et une seconde section (4) d'échangeur de chaleur. L'unité de réglage de débit de fluide frigorigène (5) règle l'écoulement de fluide frigorigène de telle sorte qu'une direction d'écoulement d'air (8) et des directions d'écoulement de fluide frigorigène (9, 10) soient opposées dans la première section d'échangeur de chaleur (3), dans les deux cas où l'échangeur de chaleur (50) fonctionne en tant qu'évaporateur et en tant que condenseur.
PCT/JP2022/026751 2021-08-02 2022-07-05 Dispositif à cycle de réfrigération WO2023013347A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP22852773.5A EP4382831A4 (fr) 2021-08-02 2022-07-05 Dispositif à cycle de réfrigération
CN202280053780.9A CN117795268A (zh) 2021-08-02 2022-07-05 制冷循环装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021-126370 2021-08-02
JP2021126370A JP2023021486A (ja) 2021-08-02 2021-08-02 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
WO2023013347A1 true WO2023013347A1 (fr) 2023-02-09

Family

ID=85155865

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2022/026751 WO2023013347A1 (fr) 2021-08-02 2022-07-05 Dispositif à cycle de réfrigération

Country Status (4)

Country Link
EP (1) EP4382831A4 (fr)
JP (1) JP2023021486A (fr)
CN (1) CN117795268A (fr)
WO (1) WO2023013347A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59115945A (ja) 1982-12-24 1984-07-04 松下電器産業株式会社 熱ポンプ装置
JPH07280375A (ja) * 1994-04-06 1995-10-27 Hitachi Ltd 空気調和装置
WO2013190830A1 (fr) * 2012-06-18 2013-12-27 パナソニック株式会社 Échangeur de chaleur et conditionneur d'air
WO2014178164A1 (fr) * 2013-04-30 2014-11-06 ダイキン工業株式会社 Unité intérieure pour dispositif de climatisation

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59115945A (ja) 1982-12-24 1984-07-04 松下電器産業株式会社 熱ポンプ装置
JPH07280375A (ja) * 1994-04-06 1995-10-27 Hitachi Ltd 空気調和装置
WO2013190830A1 (fr) * 2012-06-18 2013-12-27 パナソニック株式会社 Échangeur de chaleur et conditionneur d'air
WO2014178164A1 (fr) * 2013-04-30 2014-11-06 ダイキン工業株式会社 Unité intérieure pour dispositif de climatisation

Also Published As

Publication number Publication date
CN117795268A (zh) 2024-03-29
EP4382831A1 (fr) 2024-06-12
EP4382831A4 (fr) 2024-11-13
JP2023021486A (ja) 2023-02-14

Similar Documents

Publication Publication Date Title
JP4922669B2 (ja) 空気調和機及び空気調和機の熱交換器
US20190024951A1 (en) Refrigeration cycle apparatus
JP6884784B2 (ja) 冷凍サイクル装置
CN108775725B (zh) 三管制多联机的室内机及三管制多联机
CN109477669A (zh) 热交换器以及具备该热交换器的制冷循环装置
US5660056A (en) Air conditioner
JP6727297B2 (ja) 室外ユニットおよびそれを備えた冷凍サイクル装置
WO2018138770A1 (fr) Unité côté source de chaleur et dispositif à cycle de réfrigération
JP6888131B2 (ja) 冷凍サイクル装置
WO2003062710A1 (fr) Climatiseur du type a pompe a chaleur
JPH07280375A (ja) 空気調和装置
WO2022264348A1 (fr) Échangeur de chaleur et dispositif à cycle de réfrigération
WO2023013347A1 (fr) Dispositif à cycle de réfrigération
JP2007163013A (ja) 冷凍サイクル装置
JP5677237B2 (ja) 空気調和機
JP2017101854A (ja) 空気調和装置
JP4710869B2 (ja) 空気調和装置
WO2021131038A1 (fr) Échangeur de chaleur et dispositif à cycle frigorifique
JPH1151412A (ja) 空気調和機用室内ユニットとその室内熱交換器
JP2022115320A (ja) 空気調和機及び熱交換器
JPH10196984A (ja) 空気調和機
KR20050043089A (ko) 히트 펌프
JP7357137B1 (ja) 空気調和機
WO2023188009A1 (fr) Dispositif à cycle de réfrigération
JPH08145490A (ja) ヒートポンプエアコン用熱交換器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22852773

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 202280053780.9

Country of ref document: CN

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2022852773

Country of ref document: EP

Effective date: 20240304