WO2023275936A1 - 冷媒分配器、熱交換器及び冷凍サイクル装置 - Google Patents

冷媒分配器、熱交換器及び冷凍サイクル装置 Download PDF

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Publication number
WO2023275936A1
WO2023275936A1 PCT/JP2021/024368 JP2021024368W WO2023275936A1 WO 2023275936 A1 WO2023275936 A1 WO 2023275936A1 JP 2021024368 W JP2021024368 W JP 2021024368W WO 2023275936 A1 WO2023275936 A1 WO 2023275936A1
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WIPO (PCT)
Prior art keywords
plate
refrigerant
shaped member
protrusions
branch
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/JP2021/024368
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English (en)
French (fr)
Japanese (ja)
Inventor
篤史 ▲高▼橋
剛志 前田
悟 梁池
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP21948248.6A priority Critical patent/EP4365511A1/en
Priority to CN202180099717.4A priority patent/CN117545971A/zh
Priority to PCT/JP2021/024368 priority patent/WO2023275936A1/ja
Priority to US18/557,806 priority patent/US20240328729A1/en
Priority to JP2023531153A priority patent/JP7486671B2/ja
Publication of WO2023275936A1 publication Critical patent/WO2023275936A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F28D1/053—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 straight
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates

Definitions

  • the present disclosure relates to a refrigerant distributor that distributes refrigerant to a plurality of heat transfer tubes, a heat exchanger that includes the refrigerant distributor, and a refrigeration cycle device that includes the heat exchanger.
  • a heat exchanger is provided with a multi-branch refrigerant distributor that distributes and supplies the refrigerant flowing from one inlet channel to multiple paths in order to increase the number of paths.
  • the heat exchanger is required to have a compact refrigerant distributor capable of suppressing drift of the refrigerant to each path in order to maintain the heat exchange performance.
  • a plate-shaped member having a through-groove for branching the refrigerant into two and a plate-shaped member having a through-hole for circulating the refrigerant in the through-groove are used. Laminated construction is disclosed.
  • the plate-shaped member having the through-groove formed thereon is sandwiched between other plate-shaped members in order to establish the through-groove formed in the plate-shaped member as a flow path. Further, in the refrigerant distributor of Patent Document 1, there are two plate-like members formed with only openings into which the flat tubes are inserted in order to secure the insertion space for the flat tubes. As described above, the refrigerant distributor of Patent Document 1 has a large number of plate-like members that do not have a function of distributing the refrigerant, and is large.
  • the present disclosure has been made to solve the above problems, and provides a downsized refrigerant distributor, a heat exchanger, and a refrigeration cycle apparatus including the heat exchanger.
  • a refrigerant distributor is a refrigerant distributor in which a refrigerant pipe and a plurality of heat transfer pipes are connected, and the refrigerant flowing from the refrigerant pipe is distributed to the plurality of heat transfer pipes by circulating it through a channel formed inside.
  • the first plate-shaped member is formed to penetrate in the first direction, and has an inflow path through which the refrigerant flows from the refrigerant pipe, and the refrigerant flowing from the second plate-shaped member side is folded back toward the second plate-shaped member side.
  • the second plate member has a plurality of through passages penetrating in the first direction; and the third plate member and the second plate member. a plurality of protrusions protruding in opposite directions, each of the plurality of through passages communicating with one of the inflow passages or the plurality of turn-around passages; A space communicating with the road is formed.
  • part of the flow path is formed in the projecting portion of the third plate-shaped member to which the flat tube is connected. Therefore, the refrigerant distributor of the present disclosure is miniaturized by reducing the number of plate members required to form part of the flow path.
  • FIG. 1 is a circuit diagram showing refrigeration cycle apparatus 1 according to Embodiment 1.
  • FIG. Fig. 2 is a perspective view showing an indoor heat exchanger 7 according to Embodiment 1; 4 is a schematic diagram showing a refrigerant distributor 7b according to Embodiment 1.
  • FIG. 2 is a perspective view showing first plate member 10 according to Embodiment 1.
  • FIG. 4 is a rear view showing the third plate member 30 according to Embodiment 1.
  • FIG. 4 is a perspective view showing a third plate member 30 according to Embodiment 1.
  • FIG. FIG. 4 is a cross-sectional view showing a third plate member 30 according to Embodiment 1; 4 is a diagram for explaining a channel according to Embodiment 1;
  • FIG. 4 is a diagram for explaining a channel according to Embodiment 1;
  • FIG. FIG. 10 is a cross-sectional view showing a third plate member 30A according to Modification 1 of Embodiment 1;
  • FIG. 11 is a cross-sectional view showing a third plate member 30B according to Modification 2 of Embodiment 1;
  • FIG. 7 is a schematic diagram showing a refrigerant distributor 7Ab according to Embodiment 2;
  • FIG. 11 is a perspective view showing a third plate member 30 according to Embodiment 2;
  • FIG. 11 is a cross-sectional view showing a third plate member 30 according to Embodiment 2;
  • FIG. 10 is a diagram for explaining a channel according to Embodiment 2;
  • FIG. 11 is a schematic diagram showing a refrigerant distributor 7Bb according to Embodiment 3;
  • FIG. 11 is a perspective view showing a third plate member 30 according to Embodiment 3;
  • FIG. 11 is a cross-sectional view showing a third plate member 30 according to Embodiment 3;
  • FIG. 11 is a diagram for explaining a flow path according to Embodiment 3;
  • FIG. 11 is a schematic diagram showing a refrigerant distributor 7Cb according to Embodiment 4;
  • FIG. 11 is a perspective view showing a third plate member 30 according to Embodiment 4;
  • FIG. 11 is a cross-sectional view showing a third plate member 30 according to Embodiment 4;
  • FIG. 11 is a diagram for explaining a flow path according to Embodiment 4;
  • FIG. 11 is a diagram for explaining a flow path according to Embodiment 4;
  • Embodiment 1 A refrigeration cycle apparatus 1 including a refrigerant distributor according to Embodiment 1 will be described below with reference to the drawings and the like.
  • the same reference numerals denote the same or equivalent parts, and are common throughout the embodiments described below.
  • the size relationship of each component may differ from the actual size.
  • detailed structures are simplified or omitted as appropriate.
  • the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to the forms described in the specification.
  • FIG. 1 is a circuit diagram showing a refrigeration cycle device 1 according to Embodiment 1.
  • the refrigeration cycle device 1 has an outdoor unit 2 , an indoor unit 3 and refrigerant pipes 4 .
  • the outdoor unit 2 has a compressor 5, a channel switching valve 6, an expansion valve 8, an outdoor heat exchanger 9, and an outdoor fan 9a.
  • the indoor unit 3 has an indoor heat exchanger 7 and an indoor fan 7a.
  • the refrigerant pipe 4 is a pipe that connects the compressor 5, the flow path switching valve 6, the indoor heat exchanger 7, the expansion valve 8, and the outdoor heat exchanger 9, and through which the refrigerant flows.
  • the refrigerant pipe 4 and each device connected to the refrigerant pipe 4 constitute a refrigerant circuit.
  • the compressor 5 sucks in low-temperature and low-pressure refrigerant, compresses the sucked-in refrigerant, converts it into high-temperature and high-pressure refrigerant, and discharges it.
  • the channel switching valve 6 switches the flow direction of the refrigerant in the refrigerant circuit, and is, for example, a four-way valve.
  • the expansion valve 8 reduces the pressure of the refrigerant to expand it, and is, for example, an electronic expansion valve.
  • the outdoor heat exchanger 9 exchanges heat between refrigerant and outdoor air, and is, for example, a fin-and-tube heat exchanger.
  • the outdoor heat exchanger 9 acts as a condenser during cooling operation, and acts as an evaporator during heating operation.
  • the outdoor blower 9 a is a device that sends outdoor air to the outdoor heat exchanger 9 .
  • the indoor heat exchanger 7 exchanges heat between the indoor air and the refrigerant.
  • the indoor heat exchanger 7 acts as an evaporator during cooling operation, and acts as a condenser during heating operation.
  • the indoor air blower 7a is a device for sending indoor air to the indoor heat exchanger 7, and is, for example, a cross-flow fan.
  • the indoor heat exchanger 7 has a refrigerant distributor 7b.
  • the refrigerant distributor 7b is provided on the inflow side through which the liquid-rich refrigerant flows when the indoor heat exchanger 7 functions as an evaporator.
  • the outdoor heat exchanger 9 has a refrigerant distributor 9b.
  • the refrigerant distributor 9b is provided on the inflow side when the outdoor heat exchanger 9 acts as an evaporator. The description of the refrigerant distributor 7b and the refrigerant distributor 9b will be given later.
  • the refrigeration cycle device 1 performs cooling operation by switching the flow path switching valve 6 so that the discharge side of the compressor 5 and the outdoor heat exchanger 9 are connected.
  • the refrigerant sucked into the compressor 5 is compressed by the compressor 5 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 5 passes through the flow path switching valve 6 and flows into the outdoor heat exchanger 9 acting as a condenser.
  • the refrigerant that has flowed into the outdoor heat exchanger 9 exchanges heat with the outdoor air sent by the outdoor fan 9a, condenses, and liquefies.
  • the liquid refrigerant flows into the expansion valve 8 and is decompressed and expanded to become a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows into the indoor heat exchanger 7 acting as an evaporator.
  • the refrigerant that has flowed into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the indoor fan 7a, evaporates, and gasifies. At that time, the room air is cooled to cool the room. Thereafter, the vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow path switching valve 6 and is sucked into the compressor 5 .
  • the refrigeration cycle device 1 performs heating operation by switching the flow path switching valve 6 so that the discharge side of the compressor 5 and the indoor heat exchanger 7 are connected.
  • the refrigerant sucked into the compressor 5 is compressed by the compressor 5 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 5 passes through the flow path switching valve 6 and flows into the indoor heat exchanger 7 acting as a condenser.
  • the refrigerant that has flowed into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the indoor fan 7a, condenses, and liquefies.
  • the room air is warmed, and the room is heated.
  • the liquid refrigerant flows into the expansion valve 8 and is decompressed and expanded to become a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 9 acting as an evaporator.
  • the refrigerant that has flowed into the outdoor heat exchanger 9 exchanges heat with the outdoor air sent by the outdoor fan 9a, evaporates, and gasifies. Thereafter, the vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow path switching valve 6 and is sucked into the compressor 5 .
  • FIG. 2 is a perspective view showing the indoor heat exchanger 7 according to Embodiment 1.
  • FIG. 2 the refrigerant distributor 7b side of the indoor heat exchanger 7 is shown enlarged.
  • the indoor heat exchanger 7 includes a refrigerant distributor 7b, multiple heat transfer tubes 50, and a gas header (not shown). As shown in FIG. 2, the refrigerant pipe 4 of the refrigeration cycle device 1 and a plurality of heat transfer tubes 50 are connected to the refrigerant distributor 7b.
  • the refrigerant distributor 7 b circulates the refrigerant that has flowed from the refrigerant pipe 4 through channels formed therein, and distributes the refrigerant to the plurality of heat transfer tubes 50 .
  • the heat transfer tube 50 is, for example, a flat tube or circular tube in which a plurality of flow paths are formed.
  • the heat transfer tubes 50 are made of copper or aluminum, for example.
  • the end of the heat transfer tube 50 on the side of the refrigerant distributor 7b is inserted into the refrigerant distributor 7b.
  • FIG. 2 shows the case where the number of heat transfer tubes 50 is eight, the number is not limited to this.
  • the flow of refrigerant in the indoor heat exchanger 7 according to Embodiment 1 will be described.
  • the indoor heat exchanger 7 functions as an evaporator
  • the refrigerant flowing through the refrigerant pipes 4 flows into the refrigerant distributor 7 b and is distributed, and then flows out to the plurality of heat transfer tubes 50 .
  • the refrigerant exchanges heat with the air or the like supplied by the indoor fan 7a in the plurality of heat transfer tubes 50 .
  • the refrigerant flowing through the plurality of heat transfer tubes 50 flows into the gas header, merges, and flows out to the refrigerant pipe 4 .
  • the indoor heat exchanger 7 functions as a condenser
  • the refrigerant flows in a direction opposite to this flow.
  • FIG. 3 is a schematic diagram showing the refrigerant distributor 7b according to the first embodiment.
  • FIG. 3 shows a state in which the refrigerant distributors 7b are deployed and arranged.
  • the refrigerant distributor 7b is formed by stacking, for example, a rectangular first plate member 10, a second plate member 20, a third plate member 30, and a fourth plate member 40. It is The first plate-like member 10, the second plate-like member 20, the fourth plate-like member 40, and the third plate-like member 30 are arranged in this order in the X-axis direction of FIG. In the following description, the X-axis direction will be referred to as the stacking direction. Note that the stacking direction corresponds to the first direction.
  • the width direction of the refrigerant distributor 7b corresponding to the Y-axis direction in FIG. 3 is simply referred to as the width direction.
  • the arrangement direction of the plurality of heat transfer tubes 50 corresponding to the Z-axis direction in FIG. 3 is simply referred to as the arrangement direction.
  • the first plate-like member 10, the second plate-like member 20, the fourth plate-like member 40, and the third plate-like member 30 are integrally joined by, for example, brazing.
  • the first plate-like member 10, the second plate-like member 20, the fourth plate-like member 40, and the third plate-like member 30 are processed by, for example, press working or cutting.
  • FIG. 4 is a perspective view showing the first plate member 10 according to Embodiment 1.
  • FIG. The viewpoint in FIG. 4 is located on the opposite side of FIG. 3 in the stacking direction.
  • the first plate member 10 has two step-spanning protrusions 12a and four step-spanning protrusions 12b.
  • the step-spanning projecting portion 12a and the step-spanning projecting portion 12b protrude in the direction opposite to the second plate member 20 in the stacking direction.
  • the step-spanning projecting portion 12a is formed so as to straddle two heat transfer tubes 50 inserted into the refrigerant distributor 7b when viewed from the stacking direction.
  • the step-spanning projecting portion 12b is formed so as to straddle one heat transfer tube 50 inserted into the refrigerant distributor 7b when viewed from the stacking direction.
  • a turn-back flow path 13a is formed inside each of the step-spanning protrusions 12a.
  • the return flow path 13 a is a flow path that causes the coolant that has flowed from a through path 21 b of the second plate-shaped member 20 to be described later to flow back to the through path 21 c of the second plate-shaped member 20 .
  • a turn-back flow path 13b is formed inside each of the step-spanning protrusions 12b.
  • the return flow path 13b is a flow path in which the coolant that has flowed from a through-path 21d of the second plate-shaped member 20 described later is turned back to the through-path 21e of the second plate-shaped member 20 to flow.
  • An inflow passage 11 is formed in the first plate member 10 .
  • the inflow path 11 is formed through the first plate member 10 in the stacking direction.
  • a refrigerant pipe 4 is connected to the first plate member 10 , and an internal space of the refrigerant pipe 4 communicates with an inflow passage 11 .
  • the inflow channel 11, the turn-back flow channel 13a, and the turn-back flow channel 13b constitute the flow channel of the refrigerant distributor 7b.
  • the second plate-shaped member 20 has a through-passage 21a, two through-passages 21b, two through-passages 21c, four through-passages 21d, and four through-passages 21e formed through in the stacking direction.
  • the through passage 21a has a substantially circular shape when viewed from the stacking direction, and is formed substantially in the center of the second plate-shaped member 20 .
  • the through passage 21a communicates with the inflow passage 11 of the first plate member 10 and a first communication passage 41a of the fourth plate member 40, which will be described later.
  • Each through path 21b has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the through path 21a in the width direction.
  • Each through-passage 21b communicates with the turn-back flow path 13a of the first plate-shaped member 10 and the first communication passage 41b of the fourth plate-shaped member 40, which will be described later.
  • Each through-path 21c has a substantially circular shape when viewed in the stacking direction, and is formed at an equal interval from the through-path 21a and substantially at the center in the width direction.
  • Each through path 21c communicates with the turn-back flow path 13a of the first plate member 10 and the first communication path 41c of the fourth plate member 40, which will be described later.
  • Each through path 21d has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the through path 21c in the width direction.
  • Each of the through passages 21d communicates with the turn-back passage 13b of the first plate-shaped member 10 and the first communication passage 41d of the fourth plate-shaped member 40, which will be described later.
  • Each through-passage 21e has a substantially circular shape when viewed from the stacking direction, and the through-passages 21a and two through-passages 21c are alternately formed in the arrangement direction.
  • Each through path 21e is formed at regular intervals in the arrangement direction.
  • Each of the through passages 21e communicates with the turn-back passage 13b and the second communication passage 42 of the fourth plate member 40, which will be described later.
  • the through passages 21a, the two through passages 21b, the two through passages 21c, the four through passages 21d, and the four through passages 21e form flow paths of the refrigerant distributor 7b.
  • FIG. 5 is a rear view showing the third plate member 30 according to Embodiment 1.
  • FIG. FIG. 6 is a perspective view showing the third plate member 30 according to Embodiment 1.
  • FIG. 5 and 6 are located on the opposite side of FIG. 3 in the stacking direction.
  • the third plate member 30 has fifteen protrusions 31 that protrude in the opposite direction to the second plate member 20.
  • Each protruding portion 31 protrudes substantially perpendicularly from the surface of the third plate-like member 30 opposite to the second plate-like member 20 .
  • Insertion openings 32 into which the heat transfer tubes 50 are inserted are formed at respective ends of the eight protrusions 31 among them. Further, as shown in FIG.
  • a branch path 34a is formed inside the other projecting portion 31. As shown in FIG. A branch path 34b is formed inside the other two protrusions 31 . Branch paths 34c are formed inside the remaining four protrusions 31 .
  • the protruding portions 31 formed with the insertion openings 32 are alternately provided with the protruding portions 31 formed with any of the branched passages 34a, 34b, or 34c.
  • the protruding portion 31 having the branched path 34a is provided substantially in the center of the third plate member 30 in the arrangement direction.
  • the branch passage 34a communicates the first communication passage 41a and the first communication passage 41b of the fourth plate member 40 with each other.
  • Each projecting portion 31 having the branched path 34b is provided at equal intervals from the projecting portion 31 having the branched path 34a in the arrangement direction.
  • the branch passage 34b communicates the first communication passage 41c and the first communication passage 41d of the fourth plate member 40 with each other.
  • Each protruding portion 31 having a branched path 34c is alternately provided with two protruding portions 31 having a branched path 34a and a branched path 34b in the arrangement direction.
  • the protrusions 31 having the branch paths 34c formed thereon are formed at regular intervals in the arrangement direction.
  • Each branch path 34c communicates a first communication path 41e and a second communication path 42 of the fourth plate member 40, which will be described later.
  • FIG. 7 is a cross-sectional view showing the third plate member 30 according to Embodiment 1.
  • FIG. FIG. 7 is a cross section taken along the arrangement direction of the center of the refrigerant distributor 7b in the width direction, that is, from the AA cross section of FIG.
  • the projecting portion 31 is shown enlarged.
  • an insertion space 33 is formed inside each projection 31 having an insertion opening 32 formed therein.
  • the insertion space 33 also includes a space corresponding to the plate thickness of the third plate member 30 .
  • the insertion space 33 extends from the surface of the third plate-like member 30 on the side of the second plate-like member 20 to the downstream end surface inside the projecting portion 31 in the stacking direction.
  • a tip portion of the corresponding heat transfer tube 50 is positioned in the insertion space 33 .
  • the branch path 34a, the branch path 34b, and the branch path 34c also include a space corresponding to the plate thickness of the third plate member 30.
  • the branch path 34a, the branch path 34b, and the branch path 34c extend from the surface of the third plate-like member 30 on the side of the second plate-like member 20 to the downstream end surface inside the projecting portion 31 in the stacking direction. It is reaching The insertion space 33, the branch passages 34a, the branch passages 34b, and the branch passages 34c form flow paths of the refrigerant distributor 7b.
  • the fourth plate member 40 includes a first communication path 41a, two first communication paths 41b, two first communication paths 41c, four first communication paths 41c, and four first communication paths 41a, 41b, 41b, and 41c. It has one communication path 41 d , four first communication paths 41 e and eight second communication paths 42 .
  • the first communication path 41 a has a substantially circular shape when viewed in the stacking direction, and is formed substantially in the center of the second plate member 20 .
  • the first communication path 41 a communicates with the through path 21 a of the second plate member 20 and the branch path 34 a of the third plate member 30 . That is, the through passage 21a of the second plate member 20 and the branch passage 34a of the third plate member 30 communicate with each other through the first communication passage 41a.
  • Each first communication path 41b has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the first communication path 41a in the width direction.
  • Each first communication path 41 b communicates with the through path 21 b of the second plate member 20 and the branch path 34 a of the third plate member 30 . That is, the through passage 21b of the second plate member 20 and the branch passage 34a of the third plate member 30 communicate with each other through the first communication passage 41b.
  • Each of the first communication paths 41c has a substantially circular shape when viewed in the stacking direction, and is formed at equal intervals from the first communication path 41a and substantially at the center in the width direction.
  • Each first communication path 41 c communicates with the through path 21 c of the second plate member 20 and the branch path 34 b of the third plate member 30 . That is, the through passage 21c of the second plate member 20 and the branch passage 34b of the third plate member 30 communicate with each other through the first communication passage 41c.
  • Each first communication path 41d has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the first communication path 41c in the width direction.
  • Each first communication path 41 d communicates with the through path 21 d of the second plate member 20 and the branch path 34 b of the third plate member 30 . That is, the through passage 21d of the second plate member 20 and the branch passage 34b of the third plate member 30 communicate with each other through the first communication passage 41d.
  • Each first communication path 41e has a substantially circular shape when viewed from the stacking direction, and is formed alternately with the first communication path 41a and two first communication paths 41c in the arrangement direction. The respective first communication paths 41e are formed at regular intervals in the arrangement direction.
  • Each first communication path 41 e communicates with the through path 21 e of the second plate member 20 and the branch path 34 c of the third plate member 30 . That is, the through passage 21e of the second plate member 20 and the branch passage 34c of the third plate member 30 communicate with each other through the first communication passage 41e.
  • Each second communication path 42 is substantially L-shaped when viewed from the stacking direction, and is formed so as to surround the first communication path 41e.
  • Each second communication path 42 communicates with the branch path 34 c of the third plate member 30 and the insertion space 33 .
  • the branch path 34 c of the third plate-shaped member 30 and the insertion space 33 of the third plate-shaped member 30 communicate with each other via the second communication path 42 . Therefore, the through passage 21e of the second plate member 20 and the insertion space 33 of the third plate member 30 are defined by the first communication passage 41e, the branch passage 34c of the third plate member 30, and the second communication passage 42.
  • the first communication passages 41a, the two first communication passages 41b, the two first communication passages 41c, the four first communication passages 41d, the four first communication passages 41e, and the eight second communication passages 42 distribute the refrigerant. It constitutes the flow path of the vessel 7b.
  • FIG. 8 is a diagram for explaining a channel according to Embodiment 1.
  • FIG. FIG. 9 is a diagram for explaining a channel according to Embodiment 1.
  • FIG. The flow path shown in FIG. 9 is a continuation of the flow path shown in FIG.
  • the flow path according to Embodiment 1 will be described with reference to FIGS. 8 and 9.
  • FIG. Note that all the branches of the flow path are not explained here, and one of the plurality of branches of the flow path is representative until the refrigerant flowing from the refrigerant pipe 4 flows out to one of the heat transfer tubes 50. and explain. First, as shown in FIG.
  • the refrigerant that has flowed in from the refrigerant pipe 4 flows through the inflow passage 11 of the first plate-shaped member 10, the through passage 21a of the second plate-shaped member 20, and the first through-hole of the fourth plate-shaped member 40. It goes straight through the communication path 41a and reaches the branch path 34a of the third plate-like member 30 .
  • the coolant that has reached the branch passage 34a of the third plate member 30 is split and folded back toward the fourth plate member 40 side.
  • One of the branched refrigerants passes through the first communication path 41b of the fourth plate-shaped member 40 and the through-path 21b of the second plate-shaped member 20, and reaches the turn-back flow path 13a of the first plate-shaped member 10. , is folded back toward the second plate member 20 .
  • the folded refrigerant passes through the through passage 21c of the second plate-shaped member 20 and the first communication passage 41c of the fourth plate-shaped member 40 to the third plate-shaped member 30. reaches the fork 34b.
  • the coolant that has reached the branch path 34b of the third plate-like member 30 is split and folded back toward the fourth plate-like member 40 side.
  • One of the branched refrigerants passes through the first communication path 41d of the fourth plate-shaped member 40 and the through-path 21d of the second plate-shaped member 20, and reaches the turn-back flow path 13b of the first plate-shaped member 10. , is folded back toward the second plate member 20 .
  • the folded-back refrigerant passes through the through passage 21 e of the second plate-shaped member 20 and the first communication passage 41 e of the fourth plate-shaped member 40 to reach the branch passage 34 c of the third plate-shaped member 30 .
  • the coolant that has reached the branch path 34c of the third plate-like member 30 is split and folded back toward the fourth plate-like member 40 side.
  • One of the branched refrigerants passes through the second communication passage 42 of the fourth plate-shaped member 40 and is turned back toward the third plate-shaped member 30 .
  • the folded refrigerant reaches the insertion space 33 of the third plate member 30 and flows out to one of the heat transfer tubes 50 .
  • Embodiment 1 the insertion space 33, the branch passages 34a, the branch passages 34b, and the branch passages 34c, that is, part of the flow passages, are formed in the projecting portion 31 of the third plate member 30 to which the heat transfer tubes 50 are connected. It is Therefore, the refrigerant distributor 7b of Embodiment 1 is miniaturized by eliminating the plate-like member required to form part of the flow path.
  • the insertion space 33 is required to have a predetermined width so that the refrigerant does not stagnate in order to allow the refrigerant to smoothly flow out to the heat transfer tubes 50 .
  • the insertion space 33 is formed in a plate-like member, it is necessary to increase the thickness or width of the entire plate-like member in order to satisfy the required width.
  • the insertion space 33 is formed in the projecting portion 31 of the third plate member. Therefore, when securing the width of the insertion space 33, there is no need to enlarge the portion that does not contribute to the formation of the insertion space 33. FIG. Therefore, the refrigerant distributor 7b of Embodiment 1 can be made smaller.
  • the branch passages 34a, 34b, and 34c are also required to have a predetermined width that prevents the refrigerant from stagnation in order to smoothly divide the refrigerant.
  • the branch path 34a, the branch path 34b, and the branch path 34c are formed in the projecting portion 31 of the third plate member. Therefore, when securing the width of the branch passages 34a, 34b, and 34c, it is not necessary to enlarge the portions that do not contribute to the formation of the insertion space 33. FIG. Therefore, the refrigerant distributor 7b of Embodiment 1 can be made smaller.
  • the refrigerant distributor 7b by reducing the size of the refrigerant distributor 7b, the mounting area of the heat transfer tubes 50 can be secured in the indoor heat exchanger 7, and the heat exchange performance can be improved. Moreover, the refrigerant distributor 7b and the indoor heat exchanger 7 can be made lighter.
  • the refrigerant distributor 7b can simplify the manufacturing process and reduce the manufacturing cost by reducing the number of plate-shaped members required to form part of the flow path.
  • the turn-back flow paths 13a and turn-back flow paths 13b that is, part of the flow paths are formed in the step-spanning projecting portions 12a and 12b of the first plate member 10, respectively. Therefore, the refrigerant distributor 7b of Embodiment 1 is miniaturized by eliminating the plate-like member required to form part of the flow path.
  • the refrigerant that has reciprocated between the first plate-like member 10 and the third plate-like member 30 is 3 It can be circulated to the plate member 30 side.
  • the same plate-shaped member can be circulated a plurality of times, so the required number of plate-shaped members is reduced.
  • FIG. 10 is a cross-sectional view showing a third plate member 30A according to Modification 1 of Embodiment 1.
  • FIG. FIG. 10 is an enlarged view of three projecting portions 31 located on the + side end in the arrangement direction of the third plate member 30A from a cross section corresponding to the AA cross section of FIG. 5 in the third plate member 30A. is shown.
  • the inside of each projecting portion 31 is formed in an arc shape on the downstream side.
  • the projecting portion 31 is formed so that the dimension in the arrangement direction becomes smaller toward the tip portion. It should be noted that the projecting portion 31 may project substantially perpendicularly from the surface of the third plate-like member 30A opposite to the second plate-like member 20, as in the first embodiment.
  • FIG. 11 is a cross-sectional view showing a third plate member 30B according to Modification 2 of Embodiment 1. As shown in FIG. FIG. 11 is an enlarged view of three projecting portions 31 located on the + side end in the arrangement direction of the third plate member 30B from a cross section corresponding to the AA cross section of FIG. 5 in the third plate member 30B.
  • the third plate-like member 30B has a tapered portion facing the projecting portion 31 on the surface on the second plate-like member 20 side. Moreover, the projecting portion 31 is formed so that the dimension in the arrangement direction becomes smaller toward the tip portion.
  • the tapered shape of the third plate-shaped member 30B suppresses rapid expansion of the flow path just before it flows into the heat transfer tube 50 . Therefore, the pressure loss is reduced, and the heat exchange performance of the indoor heat exchanger 7 can be improved.
  • FIG. 12 is a schematic diagram showing a refrigerant distributor 7Ab according to the second embodiment.
  • Embodiment 2 differs from Embodiment 1 in that the fourth plate member 40 is omitted and the insertion space 33 of the third plate member 30 and the branch path 34c are formed to communicate with each other.
  • the first plate-like member 10 and the second plate-like member 20 have the same shape as the first plate-like member 10 and the second plate-like member 20 of the first embodiment.
  • the same reference numerals are given to the parts that are common to the first embodiment, and detailed description thereof will be omitted.
  • Each through passage 21 a communicates with the inflow passage 11 of the first plate member 10 and the branch passage 34 a of the third plate member 30 .
  • Each through passage 21 b communicates with the return passage 13 a of the first plate member 10 and the branch passage 34 a of the third plate member 30 .
  • Each through passage 21 c communicates with the return passage 13 a of the first plate member 10 and the branch passage 34 b of the third plate member 30 .
  • Each through passage 21 d communicates with the return passage 13 b of the first plate member 10 and the branch passage 34 b of the third plate member 30 .
  • Each through passage 21 e communicates with the turn-back passage 13 b of the first plate member 10 and the branch passage 34 c of the third plate member 30 .
  • FIG. 13 is a perspective view showing the third plate member 30 according to Embodiment 2.
  • FIG. The viewpoint in FIG. 13 is located on the opposite side of FIG. 12 in the stacking direction.
  • the two projecting portions 31 having the insertion space 33 and the projecting portion 31 having the branch path 34c are integrally formed.
  • the two insertion spaces 33 and the branch path 34c are in communication.
  • FIG. 14 is a cross-sectional view showing the third plate member 30 according to Embodiment 2.
  • FIG. 14 is a cross section obtained by cutting the center of the refrigerant distributor 7Ab in the width direction in the arrangement direction, that is, a cross section corresponding to the AA cross section in FIG.
  • the three projections 31 located at the side ends are shown enlarged.
  • the insertion space 33 and the branch path 34c extend from the surface of the third plate member 30 on the side of the second plate member 20 to the inside of the projecting portion 31 in the stacking direction, as in the first embodiment. It extends to the downstream end face of the .
  • the insertion space 33, the branch passage 34a, the branch passage 34b, and the branch passage 34c constitute the flow path of the refrigerant distributor 7Ab.
  • FIG. 15 is a diagram for explaining a flow path according to Embodiment 2.
  • FIG. A flow path according to Embodiment 2 will be described with reference to FIG. 15 .
  • the refrigerant flowing from the refrigerant pipe 4 passes through the inflow passage 11 of the first plate-shaped member 10 and the through passage 21a of the second plate-shaped member 20, and passes through the third plate-shaped member 30. reaches the fork 34a.
  • the coolant that has reached the branch path 34a of the third plate-like member 30 is split and folded back toward the second plate-like member 20 side.
  • One of the branched refrigerants passes through the through passage 21b of the second plate-shaped member 20, reaches the turn-back flow path 13a of the first plate-shaped member 10, and is turned back toward the second plate-shaped member 20 side.
  • the folded refrigerant passes through the through passage 21c of the second plate-shaped member 20 and reaches the branch passage 34b of the third plate-shaped member 30.
  • the coolant that has reached the branch path 34b of the third plate-like member 30 is split and folded back toward the second plate-like member 20 side.
  • One of the branched refrigerants passes through the through passage 21d of the second plate-shaped member 20, reaches the turn-back flow path 13b of the first plate-shaped member 10, and is turned back toward the second plate-shaped member 20 side.
  • the folded refrigerant passes through the through passage 21e of the second plate-shaped member 20 and reaches the branch passage 34c of the third plate-shaped member 30 .
  • the coolant that has reached the branch path 34 c of the third plate-like member 30 is branched to the insertion space 33 of the third plate-like member 30 .
  • One of the split refrigerant flows out to one of the heat transfer tubes 50 .
  • the insertion space 33, the branch passages 34a, the branch passages 34b, and the branch passages 34c, that is, part of the passages are formed in the projecting portion 31 of the third plate member 30 to which the heat transfer tubes 50 are connected. It is Therefore, the refrigerant distributor 7Ab of Embodiment 2 is reduced in size by eliminating the plate-like member required to form part of the flow path.
  • the two projecting portions 31 having the insertion space 33 and the projecting portion 31 having the branch path 34c are integrally formed.
  • the function of branching the refrigerant is concentrated in the third plate member 30 . Therefore, the refrigerant distributor 7Ab can be made smaller by omitting another plate-like member for dividing the refrigerant.
  • FIG. 16 is a schematic diagram showing a refrigerant distributor 7Bb according to the third embodiment.
  • the protrusions 31 having the branch paths 34a, 34b, or 34c are omitted, and the insertion spaces 33 are formed inside all the protrusions 31.
  • the first plate-like member 10 and the second plate-like member 20 have the same shape as the first plate-like member 10 and the second plate-like member 20 of the first embodiment.
  • the same reference numerals are given to the parts that are common to the first embodiment, and detailed description thereof will be omitted.
  • Each through passage 21a communicates with the inflow passage 11 of the first plate-shaped member 10 and a first sub-branch passage 43a of the fourth plate-shaped member 40, which will be described later.
  • Each through passage 21 b communicates with the turn-back flow path 13 a of the first plate-shaped member 10 and the first sub-branch passage 43 a of the fourth plate-shaped member 40 .
  • Each through passage 21c communicates with the turn-back flow path 13a of the first plate member 10 and the first sub-branch passage 43b of the fourth plate member 40, which will be described later.
  • Each through passage 21 d communicates with the turn-back passage 13 b of the first plate member 10 and the first sub-branch passage 43 b of the fourth plate member 40 .
  • Each through passage 21e communicates with the turn-back flow path 13b of the first plate-like member 10 and the second sub-branch passage 44 of the fourth plate-like member 40, which will be described later.
  • FIG. 17 is a perspective view showing the third plate member 30 according to Embodiment 3.
  • FIG. The viewpoint in FIG. 17 is located on the opposite side in the stacking direction from that in FIG.
  • the third plate-like member 30 has eight protrusions 31 that protrude in the opposite direction to the second plate-like member 20 . Insertion openings 32 into which the heat transfer tubes 50 are inserted are formed at the ends of the eight protrusions 31 .
  • FIG. 18 is a cross-sectional view showing the third plate member 30 according to Embodiment 3.
  • FIG. 18 is a cross section obtained by cutting the center of the refrigerant distributor 7Bb in the width direction in the arrangement direction, that is, a cross section corresponding to the AA cross section in FIG.
  • the two projections 31 located at the side ends are shown enlarged.
  • an insertion space 33 is formed inside each protrusion 31 having an insertion opening 32 formed therein.
  • the insertion space 33 also includes a space corresponding to the plate thickness of the third plate member 30 .
  • the insertion space 33 extends from the surface of the third plate-like member 30 on the side of the second plate-like member 20 to the downstream end surface inside the projecting portion 31 in the stacking direction.
  • a tip portion of the corresponding heat transfer tube 50 is positioned in the insertion space 33 .
  • the inside of the projecting portion 31 is formed in an arc shape on the downstream side.
  • the projecting portion 31 is formed so that the dimension in the arrangement direction becomes smaller toward the end portion.
  • the insertion space 33 constitutes the flow path of the refrigerant distributor 7Bb.
  • the fourth plate member 40 includes a first sub-branch path 43a, two second sub-branch paths 44, and four second sub-branch paths 44, which are formed to penetrate in the stacking direction.
  • the first sub-branch path 43 a has a linear shape when viewed from the stacking direction, and is formed substantially in the center of the second plate member 20 .
  • the first secondary branch passage 43 a communicates with the through passage 21 a of the second plate member 20 and the two through passages 21 b of the second plate member 20 .
  • Each of the first sub-branch paths 43b has a linear shape when viewed from the stacking direction, and is formed at positions equidistant from the first sub-branch paths 43a.
  • Each first sub-branch passage 43 b communicates with the through passage 21 c of the second plate member 20 and the two through passages 21 d of the second plate member 20 .
  • Each of the second sub-branch paths 44 has a substantially S-shape when viewed from the - side to the + side in the stacking direction. formed alternately.
  • the respective second sub-branch paths 44 are formed at regular intervals in the arrangement direction.
  • Each of the second sub-branch paths 44 communicates with the through path 21 e of the second plate-shaped member 20 and the two insertion spaces 33 of the third plate-shaped member 30 .
  • the first sub-branch passage 43a, the two second sub-branch passages 44, and the four second sub-branch passages 44 constitute the flow path of the refrigerant distributor 7Bb.
  • FIG. 19 is a diagram for explaining a channel according to Embodiment 3.
  • the refrigerant flowing from the refrigerant pipe 4 passes through the inflow passage 11 of the first plate-shaped member 10 and the through passage 21a of the second plate-shaped member 20 to the fourth plate-shaped member 40. reaches the first sub-branch 43a.
  • the refrigerant reaching the first sub-branch passage 43a of the fourth plate-shaped member 40 is branched and folded back toward the second plate-shaped member 20 side.
  • One of the branched refrigerants passes through the through passage 21b of the second plate-shaped member 20, reaches the turn-back flow path 13a of the first plate-shaped member 10, and is turned back toward the second plate-shaped member 20 side.
  • the folded refrigerant passes through the through passage 21 c of the second plate-shaped member 20 and reaches the first sub-branch passage 43 b of the fourth plate-shaped member 40 .
  • the refrigerant reaching the first sub-branch passage 43b of the fourth plate-shaped member 40 is split and folded back toward the second plate-shaped member 20 side.
  • One of the branched refrigerants passes through the through passage 21d of the second plate-shaped member 20, reaches the turn-back flow path 13b of the first plate-shaped member 10, and is turned back toward the second plate-shaped member 20 side.
  • the folded refrigerant passes through the through passage 21e of the second plate-shaped member 20 and reaches the second sub-branch passage 44 of the fourth plate-shaped member 40 .
  • the coolant that has reached the second sub-branch passage 44 of the fourth plate-like member 40 is divided into two insertion spaces 33 of the third plate-like member 30 .
  • One of the split refrigerant flows out to one of the heat transfer tubes 50 .
  • the insertion space 33 that is, part of the flow path is formed in the projecting portion 31 of the third plate member 30 to which the heat transfer tube 50 is connected. Therefore, in the third embodiment as well, the refrigerant distributor 7Bb is reduced in size by eliminating the plate-like member required to form part of the flow path.
  • FIG. 20 is a schematic diagram showing a refrigerant distributor 7Cb according to the fourth embodiment.
  • the protruding portion 31 having the insertion space 33 formed therein is omitted, and all the protruding portions 31 have a branch passage 34a, a branch passage 34b, or a branch passage 34c. is formed, which is different from the first embodiment.
  • the first plate-like member 10, the second plate-like member 20 and the fourth plate-like member 40 are the same as the first plate-like member 10, the second plate-like member 20 and the fourth plate-like member 40 of the first embodiment. Shape.
  • the same reference numerals are given to the parts that are common to the first embodiment, and detailed description thereof will be omitted.
  • FIG. 21 is a perspective view showing the third plate member 30 according to Embodiment 4.
  • FIG. The viewpoint in FIG. 21 is located on the opposite side in the stacking direction from that in FIG.
  • the third plate member 30 has seven projecting portions 31 projecting in the direction opposite to the direction of the second plate member 20 .
  • a branch path 34a is formed inside one protrusion 31 among them.
  • a branch path 34b is formed inside the other two protrusions 31 .
  • Branch paths 34c are formed inside the remaining four protrusions 31 .
  • Eight insertion openings 32 are formed alternately with the protruding portions 31 in which any of the branched passages 34a, 34b, and 34c are formed.
  • the formation positions of the protruding portions 31 in which the branch passages 34a, 34b, or 34c are formed are the same as in the first embodiment. Further, the flow path from the inflow path 11 of the first plate-like member 10 to the second communication path 42 of the fourth plate-like member 40 is also the same as in the first embodiment. Also in Embodiment 4, the branch passage 34a, the branch passage 34b, and the branch passage 34c constitute the flow path of the refrigerant distributor 7Cb.
  • the insertion opening 32 is formed in the planar portion of the third plate-shaped member 30 . Therefore, the second communication path 42 of the fourth plate member 40 communicates with the branch path 34 c of the third plate member 30 and the insertion opening 32 of the third plate member 30 .
  • FIG. 22 is a cross-sectional view showing the third plate member 30 according to Embodiment 4.
  • FIG. 22 is a cross section obtained by cutting the center of the refrigerant distributor 7Cb in the width direction in the arrangement direction, that is, a cross section corresponding to the AA cross section in FIG.
  • the three projections 31 located at the side ends are shown enlarged.
  • the inside of the projecting portion 31 is formed in an arc shape on the downstream side.
  • the projecting portion 31 is formed so that the dimension in the arrangement direction becomes smaller toward the end portion.
  • the fourth plate member 40 is omitted in FIG. 22, the tip of the heat transfer tube 50 inserted into the refrigerant distributor 7Cb passes through the insertion opening 32 and is positioned in the second communication path 42. .
  • FIG. 23 is a diagram for explaining a channel according to Embodiment 4.
  • FIG. FIG. 24 is a diagram for explaining a channel according to Embodiment 1.
  • FIG. The flow path shown in FIG. 24 is a continuation of the flow path shown in FIG. A channel according to Embodiment 4 will be described with reference to FIGS. 23 and 24.
  • FIG. 24 the flow path from the inflow path 11 of the first plate-like member 10 to the second communication path 42 of the fourth plate-like member 40 is the same as in Embodiment 1, and therefore will be omitted.
  • the refrigerant that has passed through the second communication passage 42 of the fourth plate member 40 flows out to one of the heat transfer tubes 50 inserted into the insertion opening 32 .
  • the branch passages 34a, 34b, and 34c that is, part of the flow passages, are formed in the projecting portion 31 of the third plate member 30 to which the heat transfer tubes 50 are connected. Therefore, in the fourth embodiment as well, the refrigerant distributor 7Cb is reduced in size by eliminating the plate-like member necessary for forming part of the flow path.
  • the indoor heat exchanger 7 or the outdoor heat exchanger 9 may have multiple fins joined to the heat transfer tubes 50 .
  • the fins are made of aluminum, for example.
  • the number of branches is not limited to this, and the number of branches can be changed by changing the number of branched paths. .
  • the turn-back flow path 13a is provided inside the step-spanning protrusion 12a, and the turn-back flow path 13b is provided inside the step-straddling protrusion 12b.
  • the turn-back channel 13a and the turn-back channel 13b may be formed as grooves penetrating the first plate-shaped member 10 and blocked by another plate-shaped member to form a channel.
  • the turn-back flow path 13 a and turn-up flow path 13 b may be formed as grooves having a depth less than the plate thickness of the first plate member 10 . Even in these cases, the size of the refrigerant distributor 7b can be reduced if a part of the flow path is formed in the projecting portion 31 of the third plate member 30 .
  • the modification 1 of the first embodiment may be combined to form the inside of the protruding portion 31 so that the downstream side has an arc shape.
  • the surface on the side of the second plate-like member 20 may be tapered.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2021/024368 2021-06-28 2021-06-28 冷媒分配器、熱交換器及び冷凍サイクル装置 Ceased WO2023275936A1 (ja)

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EP21948248.6A EP4365511A1 (en) 2021-06-28 2021-06-28 Refrigerant distributor, heat exchanger, and refrigeration cycle device
CN202180099717.4A CN117545971A (zh) 2021-06-28 2021-06-28 制冷剂分配器、热交换器和制冷循环装置
PCT/JP2021/024368 WO2023275936A1 (ja) 2021-06-28 2021-06-28 冷媒分配器、熱交換器及び冷凍サイクル装置
US18/557,806 US20240328729A1 (en) 2021-06-28 2021-06-28 Refrigerant distributor, heat exchanger, and refrigeration cycle apparatus
JP2023531153A JP7486671B2 (ja) 2021-06-28 2021-06-28 冷媒分配器、熱交換器及び冷凍サイクル装置

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WO2025238677A1 (ja) * 2024-05-13 2025-11-20 日本キヤリア株式会社 熱交換器

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