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WO2023062800A1 - Distributeur, échangeur de chaleur et dispositif de thermopompe - Google Patents

Distributeur, échangeur de chaleur et dispositif de thermopompe Download PDF

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Publication number
WO2023062800A1
WO2023062800A1 PCT/JP2021/038152 JP2021038152W WO2023062800A1 WO 2023062800 A1 WO2023062800 A1 WO 2023062800A1 JP 2021038152 W JP2021038152 W JP 2021038152W WO 2023062800 A1 WO2023062800 A1 WO 2023062800A1
Authority
WO
WIPO (PCT)
Prior art keywords
distributor
refrigerant
orifice
orifice holes
tubular
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/JP2021/038152
Other languages
English (en)
Japanese (ja)
Inventor
七海 岸田
洋次 尾中
理人 足立
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 US18/696,373 priority Critical patent/US20240384946A1/en
Priority to PCT/JP2021/038152 priority patent/WO2023062800A1/fr
Priority to GB2405105.4A priority patent/GB2625961A/en
Priority to JP2022526087A priority patent/JP7142806B1/ja
Priority to DE112021008363.5T priority patent/DE112021008363T5/de
Priority to CN202180103181.9A priority patent/CN118176402A/zh
Publication of WO2023062800A1 publication Critical patent/WO2023062800A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F28F9/027—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 distribution pipes
    • F28F9/0273—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 distribution pipes with multiple holes
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05325—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • F28F9/027—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 distribution pipes
    • F28F9/0275—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 distribution pipes with multiple branch pipes
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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 distributor that distributes refrigerant to a plurality of heat transfer tubes, a heat exchanger and a heat pump device that include this distributor.
  • Some distributors have a double-tube configuration of an outer tube and an inner tube (see Patent Document 1, for example).
  • the inner tube is provided with coolant outlet holes, also called orifice holes.
  • the refrigerant that has flowed into the flow path inside the inner pipe in the distributor is ejected into the space between the inner pipe and the outer pipe through the plurality of refrigerant outflow holes, and flows into the plurality of heat transfer tubes from this space.
  • the present disclosure has been made to solve the above problems, and aims to provide a distributor, a heat exchanger, and a heat pump device that suppress an increase in pressure loss while maintaining uniform distribution through orifice holes. aim.
  • a distributor according to the present disclosure includes a laterally extending cylindrical outer wall portion, and a channel extending in the lateral direction and provided in the outer wall portion or a hollow portion inside the outer wall portion and having a circular cross section inside. and a plurality of tubular portions formed with a plurality of tubular portions, the plurality of tubular portions being provided in parallel with each other, and a plurality of tubular portions spaced apart in the lateral direction on the upper or lower portion of the outer wall portion.
  • a connecting port is formed, and a plurality of orifice holes are formed in the tubular portion at intervals in the lateral direction.
  • the heat exchanger includes a plurality of heat transfer tubes arranged in the horizontal direction and extending in the vertical direction, two headers provided at both ends of the plurality of heat transfer tubes for distributing and joining the refrigerant, wherein at least one of the two headers includes the distributor, and a portion of the plurality of heat transfer tubes are connected to the plurality of connection ports of the distributor.
  • the heat pump device includes a refrigerant circuit including the above heat exchanger and a compressor that compresses the refrigerant.
  • a distributor, a heat exchanger, and a heat pump device include a plurality of tubular portions in which flow paths having a circular cross section are formed. Since it is provided in the hollow portion, the refrigerant flows into the distributor through a plurality of flow paths. Therefore, compared with the conventional configuration in which the refrigerant is distributed to a plurality of heat transfer tubes via only one inner tube, the cross-sectional area of the flow path per tubular portion can be reduced. As a result, it is possible to provide a distributor, a heat exchanger, and a heat pump device that suppress an increase in pressure loss in the flow path while maintaining uniform distribution through the orifice holes.
  • FIG. 1 is a cross-sectional view showing an example of a heat exchanger provided with a distributor according to Embodiment 1;
  • FIG. FIG. 2 is a refrigerant circuit diagram of a heat pump device equipped with the heat exchanger of FIG. 1;
  • FIG. 9 is a schematic diagram showing positions of orifice holes in a cylindrical portion of a distributor according to Embodiment 2;
  • FIG. 6 is a graph showing the influence of the dryness of the refrigerant on the liquid level angle of the refrigerant in FIG. 5 ;
  • FIG. 11 is a schematic diagram showing a first modification of the cylindrical portion of the distributor according to Embodiment 2;
  • FIG. 11 is a cross-sectional view showing an example of a distributor according to Embodiment 3;
  • FIG. 11 is a schematic diagram showing a second modification of the distributor according to Embodiment 3;
  • FIG. 11 is a cross-sectional view showing an example of a distributor according to Embodiment 4;
  • FIG. 12 is a cross-sectional view showing an example of a distributor according to Embodiment 5;
  • FIG. 12 is a sectional view showing the BB section of the distributor of FIG. 11;
  • FIG. 12 is a sectional view showing the CC section of the distributor of FIG. 11;
  • FIG. 14 is a cross-sectional view showing an example of a distributor according to Embodiment 6;
  • FIG. 1 is a cross-sectional view showing an example of a heat exchanger 100 including a distributor 20 according to Embodiment 1.
  • FIG. FIG. 2 is a sectional view showing the AA section of the distributor 20 of FIG.
  • FIG. 3 is a cross-sectional view showing an example of the end partition 23 of FIG. The configuration of the heat exchanger 100 will be described with reference to FIGS. 1 to 3.
  • FIG. 1 is a cross-sectional view showing an example of a heat exchanger 100 including a distributor 20 according to Embodiment 1.
  • FIG. FIG. 2 is a sectional view showing the AA section of the distributor 20 of FIG.
  • FIG. 3 is a cross-sectional view showing an example of the end partition 23 of FIG.
  • the configuration of the heat exchanger 100 will be described with reference to FIGS. 1 to 3.
  • the heat exchanger 100 includes a plurality of heat transfer tubes 1, first headers 2a and second headers 2b arranged at both ends of the plurality of heat transfer tubes 1, and refrigerant in the heat exchanger 100. It is provided with two pipes 3a and 3b serving as entrances and exits. Moreover, although not shown, the heat exchanger 100 includes a plurality of fins. In the following description, when the first header 2a and the second header 2b are not particularly distinguished, they may simply be referred to as headers.
  • the header has a cylindrical header outer wall. In FIG. 1, white arrows and solid arrows shown in the header indicate the direction in which the refrigerant flows.
  • the three mutually orthogonal directions are defined as a first direction D1, a second direction D2 and a third direction D3 (see FIG. 2)
  • the first direction D1 is defined as the longitudinal direction of the header, that is, the axial direction.
  • the plurality of heat transfer tubes 1 are arranged at regular intervals in the first direction D1, and each of the plurality of heat transfer tubes 1 extends in the second direction D2.
  • directional terms e.g., “up”, “down”, “right”, “left”, “front”, “back”, etc.
  • these terms are not intended to limit this disclosure.
  • these directional terms mean directions when the heat exchanger 100 is viewed from the front side (front side) as shown in FIG.
  • the first direction D1 which is the longitudinal direction of the header, is defined as the horizontal direction of the heat exchanger 100, and is the longitudinal direction of the plurality of heat transfer tubes 1.
  • the second direction D2 is defined as the vertical direction of the heat exchanger 100 .
  • the heat transfer tube 1 is composed of, for example, a flat tube.
  • the upper end 1e of the plurality of heat transfer tubes 1 is inserted into the header outer wall of the first header 2a, and the lower end 1e of the plurality of heat transfer tubes 1 is inserted into the header outer wall of the second header 2b. .
  • a plurality of connection openings 21o into which the upper ends 1e of the heat transfer tubes 1 are inserted are formed at intervals in the lateral direction in the lower portion of the header outer wall of the first header 2a.
  • a plurality of connection ports 21o into which the lower ends 1e of the heat transfer tubes 1 are inserted are formed at intervals in the lateral direction on the upper portion of the outer wall of the header of the second header 2b.
  • a space through which a coolant flows is formed inside each of the first header 2a and the second header 2b. The space inside the first header 2 a and the space inside the second header 2 b communicate with each other via a plurality of heat transfer tubes 1 .
  • the first header 2a and the second header 2b respectively distribute the refrigerant to the plurality of heat transfer tubes 1 and allow the refrigerant from the plurality of heat transfer tubes 1 to join. Further, in the example shown in FIG. 1, the pipe 3a is provided at the left end of the second header 2b, and the pipe 3b is provided at the right end of the second header 2b.
  • Each of the plurality of fins (not shown) is composed of, for example, corrugated fins formed into a wave shape.
  • Each fin is arranged between adjacent heat transfer tubes 1 and joined to the surfaces of the heat transfer tubes 1 on both sides. The fins transfer heat to the heat transfer tubes 1 and improve the heat exchange efficiency between the air and the refrigerant.
  • the plurality of heat transfer tubes 1, the plurality of fins (not shown), the first header 2a, and the second header 2b can all be made of aluminum. In this case they are joined, for example by brazing.
  • At least one of the first header 2a and the second header 2b is provided with a distributor 20. Further, when the distributor 20 is provided in a part of the longitudinal direction of one of the first header 2a and the second header 2b, the inner space of the header without the distributor 20 is arranged in the longitudinal direction.
  • a partition plate 4 is provided for partitioning into a plurality of parts. In the example shown in FIG. 1, the right half of the first header 2a in the longitudinal direction (first direction D1) is the distributor 20, and the second header 2b without the distributor 20 is the partition plate 4.
  • the internal space of the second header 2b is divided by a partition plate 4 into a left space and a right space.
  • the configuration of the distributor 20 will be described based on FIGS. 1 to 3.
  • FIG. The distributor 20 includes a cylindrical outer wall portion 21 having a hollow portion 21a, and a cylindrical portion 22 provided in the hollow portion 21a so as to extend in the lateral direction (first direction D1) and having a flow path 22p formed therein. and have.
  • the outer wall portion 21 of the distributor 20 is composed of the right half of the header outer wall of the first header 2a.
  • a plurality of orifice holes 22o are formed in the cylindrical portion 22 at regular intervals in the axial direction of the channel, that is, in the first direction D1.
  • 18 heat transfer tubes 1 are connected to the outer wall portion 21 of the distributor 20, and seven orifice holes 22o are formed in the cylindrical portion 22 in the horizontal direction.
  • a plurality of cylindrical portions 22 extending in the horizontal direction in FIG. 1 are provided as shown in FIG. 2, and the plurality of cylindrical portions 22 are provided in parallel with each other in the hollow portion 21a.
  • the orifice hole 22o has, for example, a circular shape.
  • the shape of the orifice hole 22o may be a slit-like shape.
  • the channel 22p has a circular cross section in a cross section perpendicular to the axial direction of the cylindrical portion 22.
  • the tubular portion 22 has a cylindrical shape.
  • the upper side of the line passing through the center C1 of the cylindrical portion 22 and parallel to the third direction D3 (the front-rear direction of the heat exchanger 100) is the upper side cylindrical portion, and The lower side may be referred to as a lower tubular portion.
  • the orifice hole 22o may be provided anywhere in the cross section perpendicular to the axial direction of the cylindrical portion 22.
  • the orifice hole 22o is provided near the connection port 21o of the outer wall portion 21 into which the heat transfer tube 1 is inserted, of the upper cylindrical portion that is the upper half and the lower cylindrical portion that is the lower half, The distance between the end portion 1e of the heat transfer tube 1 and the orifice hole 22o is reduced.
  • a connection port 21o is formed in the lower portion of the outer wall portion 21 of the distributor 20, and each tubular portion 22 is provided with an orifice hole 22o in the lower tubular portion.
  • the distributor 20 has an end partition 23 provided at one end of the outer wall portion 21 in the first direction D1 so as to block a space on the inner peripheral side of the outer wall portion 21 and on the outer peripheral side of the plurality of flow paths 22p. It has In the example shown in FIG. 1, the end partition 23 is provided at the left end of the distributor 20 in the lateral direction (first direction D1). As shown in FIG. 3, the end partition 23 is, for example, a plate-like member arranged along a plane perpendicular to the first direction D1, and has a substantially circular opening 23a connected to the flow path 22p. It can be configured as The end partition 23 is formed with the same number of openings 23a as the flow paths 22p.
  • each tubular portion 22 is connected to the inner surface of the right end portion of the first header 2a. is blocked.
  • the left end surface of each cylindrical portion 22 is connected to the edge of the opening 23a on the right surface of the end partition 23, and the end partition 23 allows the hollow portion 21a outside the plurality of cylindrical portions 22 to be separated. is blocked at the left end.
  • the opening 23 a of the end partition 23 communicates the left space inside the first header 2 a with the plurality of flow paths 22 p in the distributor 20 .
  • the orifice hole 22o described above communicates the flow path 22p with the space outside the cylindrical portion 22 in the hollow portion 21a.
  • the plurality of heat transfer tubes 1 connected to the outer wall portion 21 of the distributor 20 are connected to the right side of the partition plate 4 in the second header 2b, and are connected to the space outside the cylindrical portion 22 in the hollow portion 21a of the distributor 20. , and the right space inside the second header 2b.
  • the partition plate 4 allows the refrigerant that has flowed from the distributor 20 of the first header 2a to the right space of the second header 2b through the plurality of heat transfer tubes 1 to flow into the left space of the second header 2b, that is, the first header 2a. It is configured so that it does not mix with the refrigerant before it flows.
  • the refrigerant flows from the pipe 3a into the left space of the second header 2b, is distributed to the plurality of heat transfer tubes 1 connected to this left space, and heat-exchanges with the air while rising inside these heat transfer tubes 1, It flows into the left space of the first header 2a.
  • the refrigerant that has flowed into the left space of the first header 2 a flows into the plurality of flow paths 22 p of the distributor 20 via the openings 23 a of the end partition 23 .
  • the coolant that has flowed into the flow path 22p through the opening 23a passes through a plurality of orifice holes 22o provided at intervals in the tubular portion 22 while flowing rightward through the flow path 22p.
  • the refrigerant flowing into these heat transfer tubes 1 from the distributor 20 exchanges heat with the air while descending inside the heat transfer tubes 1, flows into the right space of the second header 2b, and then passes through the pipe 3b to the heat exchanger. outflow from 100.
  • the flow of the refrigerant is not limited to one direction, and may flow in the opposite direction. That is, in the heat exchanger 100, the refrigerant that has flowed through the pipe 3b can flow out through the pipe 3a after performing heat exchange in the plurality of heat transfer pipes 1.
  • the distributor 20 is provided on the right half of the first header 2a in the first direction D1. be able to.
  • the distributor 20 may be the entire area of the first header 2a in the first direction D1.
  • the distributor 20 is provided only in the upper first header 2a of the first header 2a and the second header 2b. It may be provided in both the header 2a and the second header 2b.
  • the position where the partition plate 4 is provided in the other header can be determined according to the position and range in which the distributor 20 is provided in the one header.
  • the positions where the pipes 3a and 3b are provided in the heat exchanger 100 are not limited to the positions shown in FIG.
  • the number of orifice holes 22o in each tubular portion 22 and the intervals between the orifice holes 22o are not limited to the above case.
  • FIG. 4 is a refrigerant circuit diagram of the heat pump device 10 provided with the heat exchanger 100 of FIG.
  • white arrows indicate the direction in which the refrigerant flows.
  • the heat pump device 10 has a refrigerant circuit 10a that transfers heat using the latent heat of evaporation and condensation of refrigerant.
  • Examples of the heat pump device 10 include an air conditioner in which an evaporator is installed outdoors and a condenser is installed in a room to heat the room, and a hot water supply system in which water is heated by the condenser to produce hot water. . In the following, as shown in FIG.
  • the heat exchanger 100 described above is provided in the refrigerant circuit 10a so as to function as an evaporator during the heating operation of the heat pump device 10.
  • the refrigerant circuit 10a is formed by connecting a compressor 11, a heat exchanger 13, a pressure reducer 14, and a heat exchanger 100 by refrigerant pipes.
  • the compressor 11 sucks in a low-pressure gas refrigerant, compresses it, converts it into a high-pressure gas refrigerant, discharges it, and circulates it in the refrigerant circuit 10a.
  • the heat exchanger 13 and the heat exchanger 100 exchange heat between refrigerant and air.
  • the decompressor 14 is composed of, for example, an expansion valve, and expands and decompresses the refrigerant.
  • the compressor 11 can be configured, for example, by an inverter compressor or the like whose capacity, which is the output amount per unit time, is controlled by changing the operating frequency.
  • the frequency of the compressor 11 can be adjusted to change the amount of refrigerant circulating in the refrigerant circuit 10a, and the amount of heat transferred in the refrigeration cycle can be changed according to the load or the like.
  • the pressure of the refrigerant circulating in the refrigerant circuit 10a can be changed.
  • the refrigerant circuit 10a further has a channel switching device 12.
  • the channel switching device 12 switches the channel of the refrigerant discharged from the compressor 11, and is configured by, for example, a four-way valve.
  • the configuration of the refrigerant circuit 10a is not limited to the configuration described above.
  • the channel switching device 12 can be omitted.
  • the passage switching device 12 switches between cooling and heating.
  • heating operation the refrigerant discharged from the compressor 11 flows through the heat exchanger 13 , the pressure reducer 14 , and the heat exchanger 100 in order and returns to the compressor 11 .
  • cooling operation the refrigerant discharged from the compressor 11 flows through the heat exchanger 100 , the pressure reducer 14 and the heat exchanger 13 in order, and returns to the compressor 11 .
  • the condenser radiates the heat of the high-pressure gas refrigerant to the outside air and condenses it into liquid refrigerant.
  • the evaporator causes the liquid refrigerant contained in the low-pressure refrigerant to absorb heat from the outside air and evaporate it into gas refrigerant.
  • the distributor 20 of the first embodiment includes the cylindrical outer wall portion 21 extending in the lateral direction (first direction D1) and having the hollow portion 21a, and the laterally extending hollow portion 21a provided in the outer wall portion 21. , and a plurality of cylindrical portions 22 in which channels 22p having a circular cross section are formed.
  • a plurality of tubular portions 22 are provided in parallel with each other.
  • a plurality of connection ports 21o are formed at intervals in the lateral direction in the upper or lower portion of the outer wall portion 21, and a plurality of orifice holes 22o are formed in the tubular portion 22 at intervals in the lateral direction. .
  • the distributor 20 includes a plurality of cylindrical portions 22 in which flow paths 22p having a circular cross section are formed.
  • the refrigerant flows into the distributor 20 through a plurality of flow paths 22p.
  • Refrigerant that has flowed into the flow paths 22p of the plurality of tubular portions 22 is distributed to the plurality of heat transfer tubes 1 via the plurality of orifice holes 22o. Therefore, compared to a conventional configuration in which the refrigerant is distributed to a plurality of heat transfer tubes 1 via only one inner tube, the present disclosure can reduce the size of the flow path 22p per tubular portion 22 .
  • the plurality of tubular parts 22 are arranged in the hollow part 21 a of the distributor 20 .
  • each of the plurality of tubular portions 22 has a cylindrical shape. Thereby, the channel 22p having a circular cross section can be easily formed.
  • the distributor 20 is provided at one end of the outer wall portion 21 in the lateral direction (first direction D1) so as to close the space on the inner peripheral side of the outer wall portion 21 and on the outer peripheral side of the plurality of flow paths 22p.
  • An end partition 23 is provided. Thereby, the refrigerant can be divided and made to flow into only the plurality of flow paths 22p.
  • the heat exchanger 100 includes a plurality of heat transfer tubes 1 arranged in a horizontal direction (first direction D1) and extending in a vertical direction (second direction D2), and both ends of the plurality of heat transfer tubes 1 and two headers (a first header 2a and a second header 2b) for distributing and joining the refrigerant.
  • At least one of the two headers (for example, the first header 2a) includes a distributor 20 and a portion of the plurality of heat transfer tubes 1 (in the example shown in FIG. 1, 18 heat transfer tubes on the right side). 1) are connected to a plurality of connection ports 21 o of the distributor 20 .
  • the header of the heat exchanger 100 includes the distributor 20, the heat exchanger 100 with high heat exchange efficiency can be realized. Moreover, since the header can be made small by providing the distributor 20 that achieves both the avoidance of an increase in pressure loss and the miniaturization of the distributor 20, the size of the heat exchanger 100 can be reduced.
  • the heat pump device 10 according to Embodiment 1 also includes a refrigerant circuit 10a including a heat exchanger 100 and a compressor 11 that compresses refrigerant.
  • a refrigerant circuit 10a including a heat exchanger 100 and a compressor 11 that compresses refrigerant.
  • FIG. 5 is a schematic diagram showing the positions of the orifice holes 22o in the tubular portion 22 of the distributor 20 according to the second embodiment.
  • FIG. 5 shows a cross section of the cylindrical portion 22 perpendicular to the first direction D1.
  • FIG. 5 also shows the liquid level Ra of the coolant R flowing through the flow path 22p and the liquid level angle ⁇ [°] in the cross section of the tubular portion 22 .
  • the liquid level angle ⁇ refers to a reference line L0 extending vertically downward from the center C1 of the flow channel 22p in the cross section of the cylindrical portion 22 shown in FIG. 22 and the line L1 that connects the position of the liquid surface Ra on the inner surface of .
  • the second embodiment differs from the first embodiment in that the position of the orifice hole 22o is restricted, and the rest of the configuration is the same as the first embodiment.
  • the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • Each of the plurality of orifice holes 22o is provided at an oblique or lateral position, excluding directly below and directly above the center C1 of the channel 22p, in the cross section of the tubular portion 22 shown in FIG. That is, the orifice holes 22o are not provided directly below and above the center C1 of the flow path 22p.
  • the orifice hole 22o is provided in the tubular portion 22 vertically below the center C1 of the flow path 22p, i.e. directly below, when the gas-liquid two-phase refrigerant flows into the flow path 22p, the longitudinal direction of the distributor 20 (first The liquid refrigerant preferentially flows out on the upstream side in one direction D1). Therefore, the amount of liquid refrigerant tends to be insufficient on the downstream side of the distributor 20 in the longitudinal direction, and the distribution is not uniform.
  • the orifice hole 22o by providing the orifice hole 22o at a position shifted to the left or right from the vertical line passing through the center C1 of the flow path 22p in the cylindrical portion 22, the orifice hole 22o is located near the liquid surface Ra of the coolant R. Therefore, both the liquid refrigerant and the gas refrigerant easily flow out from the orifice hole 22o, and the distribution uniformity is improved.
  • FIG. 6 is a graph showing the influence of the dryness x of the refrigerant on the liquid level angle ⁇ of the refrigerant in FIG.
  • the horizontal axis of the graph in FIG. 6 represents the dryness x of the refrigerant flowing into the heat exchanger 100, and the vertical axis of the graph in FIG. show.
  • the dryness of the refrigerant flowing into the evaporator is generally used at about 0.2 to 0.8 as shown in FIG.
  • the liquid level angle ⁇ is smaller than 90°, and is about 50° to 70°. Therefore, in order to cause both the liquid refrigerant and the gas refrigerant to flow out from the orifice hole 22o, the orifice hole 22o should be provided at the same position as the liquid surface Ra in the cross section of the cylindrical portion 22 shown in FIG. Specifically, in FIG. 5, the angle formed by the reference line L0 and the line connecting the center C1 of the flow path 22p and the center of the orifice hole 22o is within the angle range of 50° to 70°.
  • An orifice hole 22o is provided. Considering that the liquid surface Ra in the flow path 22p is not always constant, the above angular range is slightly widened, and the angular position of the orifice hole 22o is set within the angular range of 40° to 80° shown in FIG. You may adjust it with .
  • the angle is taken on the front side in the depth direction (third direction D3) of heat exchanger 100, but the angle is taken on the back side in the depth direction (third direction D3) of heat exchanger 100. be able to. That is, here, the angular position where the orifice hole 22o is provided is defined as a positive angle, and the orifice hole 22o may be provided on the near side or on the far side within the angular range from the reference line L0. Also good.
  • the orifice holes 22o of the adjacent tubular portions 22 are provided so as to face each other as shown in FIG. With such a configuration, even if the refrigerant sprayed from the orifice holes 22o of the two cylindrical portions 22 collides with each other and the distribution of the refrigerant to the plurality of flow paths 22p is uneven, it is distributed to the plurality of heat transfer tubes 1. before it can reduce the effects of that bias.
  • the expression that the orifice holes 22o of the adjacent cylindrical portions 22 face each other means that the directions in which the refrigerant blows out from the orifice holes 22o of the adjacent cylindrical portions 22 (indicated by dashed arrows in FIG. 2) are parallel to each other. It suffices if it is configured so as to be closer than .
  • two tubular portions 22 are provided on the front side and the back side in the hollow portion 21a in the outer wall portion 21 of the distributor 20, and the tubular portion 22 on the front side has a flow path.
  • An orifice hole 22o is provided below the center C1 of the passage 22p and on the far side (for example, at the 4 o'clock position), and the tubular portion 22 on the far side is provided below and on the near side of the center C1 of the passage 22p.
  • An orifice hole 22o is provided at (for example, the 8 o'clock position).
  • the positions of the orifice holes 22o in the two cylindrical portions 22 are symmetrical in the arrangement direction (third direction D3) of the cylindrical portions 22. good. For example, even if the orifice hole 22o is provided at the 4 o'clock position in the tubular part 22 on the near side and the orifice hole 22o is provided at the 7 o'clock position in the tubular part 22 on the far side, each tubular part 22 Refrigerants collide with each other more easily than when the orifice hole 22o is provided at the bottom.
  • FIG. 7 is a schematic diagram showing a first modification of the cylindrical portion 22 of the distributor 20 according to Embodiment 2.
  • FIG. Orifice holes 22o of adjacent cylindrical portions 22 may be arranged to face outward, that is, not to face each other, as shown in FIG.
  • the expression that the orifice holes 22o of the adjacent cylindrical portions 22 face outward means that the direction in which the refrigerant blows out from the orifice holes 22o of the adjacent cylindrical portions 22 (indicated by the dashed arrows in FIG. 7) is , so long as they are separated from each other rather than parallel to each other.
  • the tubular portion 22 on the front side is provided with an orifice hole 22o below and on the front side of the center C1 of the flow path 22p, and the tubular portion 22 on the back side is provided with the orifice hole 22o.
  • An orifice hole 22o is provided below and behind the center C1 of the flow path 22p.
  • the distributor 20 according to the second embodiment also includes a plurality of tubular portions 22 provided in the hollow portion 21a. The same effect as in the case of 1 is exhibited.
  • each of the plurality of orifice holes 22o is positioned directly below and directly below the center C1 of the flow path 22p in a cross section perpendicular to the lateral direction (first direction D1) of the tubular portion 22. It is formed at positions other than the top.
  • the orifice hole 22o becomes closer to the liquid surface Ra of the refrigerant R even in a state where the liquid refrigerant tends to accumulate in the lower portion of the flow path 22p due to the influence of gravity. It is possible to prevent uneven distribution of the liquid refrigerant and achieve better distribution of the gas-liquid two-phase refrigerant.
  • each of the plurality of orifice holes 22o connects the center C1 of the flow path 22p and the portion immediately below the center C1 of the flow path 22p in a cross section perpendicular to the lateral direction (first direction D1) of the cylindrical portion 22.
  • the angle between the reference line L0 and the line connecting the part where the orifice hole 22o is formed and the center C1 of the flow path 22p is set within the angle range of 40° or more and 80° or less.
  • the orifice hole 22o is provided at a position closer to the liquid level Ra of the refrigerant R in the distributor 20 that is used with a general refrigerant dryness x, so that both the liquid refrigerant and the gas refrigerant flow through the orifice hole 22o. Easy to flow and more even distribution can be achieved.
  • FIG. 8 is a cross-sectional view showing an example of distributor 20 according to the third embodiment.
  • the third embodiment is different from the first embodiment in that a plurality of cylindrical portions 22 are provided on the outer wall portion 21, and the rest of the configuration is the same as the first embodiment.
  • the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • first direction D1 of the distributor 20 shown in FIG. It is provided on the outer wall portion 21 .
  • the two tubular portions 22 are connected by a portion 21b located between the two tubular portions 22 in the outer wall portion 21, and the lower portion of each tubular portion 22 is connected to the outer wall portion 21. It protrudes from the portion 21 into the hollow portion 21a.
  • the orifice hole 22o is formed in a portion of the tubular portion 22 located in the hollow portion 21a, and allows the passage 22p inside the tubular portion 22 and the hollow portion 21a outside the tubular portion 22 to communicate with each other.
  • the distributor 20 in which the flow path 22p having a substantially circular cross section is provided in the outer wall portion 21 of the distributor 20 can be integrally manufactured by extrusion molding or the like.
  • the distributor 20 may be composed of a plurality of parts.
  • the tubular portion 22 having the flow path 22p with a substantially circular cross section may be configured by vertically combining plate-like members having substantially arc-shaped unevenness.
  • each of the first header 2a and the second header 2b is configured to extend linearly in the first direction D1, but two linear portions extending in the first direction D1 and two A U-shaped configuration having a bent portion connecting the straight portions may be employed.
  • the distributor 20 of the present disclosure since the flow path 22p has a plurality of flow paths 22p, the amount of refrigerant flowing through each flow path 22p is smaller than in the conventional case. The effect of centrifugal force is reduced and good distribution of the refrigerant can be achieved.
  • FIG. 9 is a schematic diagram showing a second modification of the distributor 20 according to the third embodiment.
  • the outer wall portion 21 of the distributor 20 has the bent portion 20b that is U-shaped in plan view as described above.
  • FIG. 9 shows a cross section of the distributor 20 passing through the vertex of the bent portion 20b and perpendicular to the third direction D3.
  • Each of the plurality of orifice holes 22o is provided closer to the inner peripheral side of the bent portion 20b than the position directly below the center C1 of the flow path 22p in the cylindrical portion 22.
  • two cylindrical portions 22 are provided on the upper portion of the outer wall portion 21, and both the inner cylindrical portion 22 and the outer cylindrical portion 22 are located at the center of the flow path 22p.
  • a plurality of orifice holes 22o are provided below C1 and on the inner peripheral side.
  • each cylindrical portion 22 has an orifice hole 22o below and nearer than the center C1 of the flow path 22p.
  • each cylindrical portion 22 is provided with an orifice hole 22o below and behind the center C1 of the flow path 22p.
  • the distributor 20 according to the third embodiment also includes a plurality of cylindrical portions 22, similarly to the distributor 20 according to the first embodiment. play.
  • each of the plurality of cylindrical portions 22 has a hollow portion 21a at least part of the flow path 22p in a cross section perpendicular to the lateral direction (first direction D1) of the outer wall portion 21. It is provided on the outer wall portion 21 so as to be positioned at .
  • the plurality of cylindrical portions 22 are not independent of each other, but are connected by the outer wall portion 21 . Therefore, for example, even when the header including the distributor 20 is bent, it is easier to uniformly apply a force to each of the cylindrical portions 22 than when the plurality of cylindrical portions 22 exist independently. Therefore, the mutual positional relationship of the components of the distributor 20 is ensured. As a result, after processing the header including the distributor 20, problems such as the orifice holes 22o provided in the cylindrical portions 22 being crushed or the cylindrical portions 22 interfering with each other can be avoided, and processing can be performed while ensuring the function. easy.
  • the outer wall portion 21 has a bent portion 20b, and each of the plurality of orifice holes 22o is provided closer to the inner peripheral side of the bent portion 20b than the position directly below the center C1 of the flow path 22p. It is As a result, the orifice hole 22o in the cylindrical portion 22 is provided at a position opposite to the direction of the centrifugal force (the first direction D1 in the cross section of the cylindrical portion 22 shown in FIG. 9). Good distribution can be provided even when the liquid surface Ra of the liquid is inclined.
  • FIG. 10 is a cross-sectional view showing an example of distributor 20 according to the fourth embodiment.
  • the fourth embodiment is different from the first embodiment in that a plurality of cylindrical portions 22 are provided in an intermediate partition 24 arranged in a hollow portion 21a. It is the same as the case.
  • the same parts as those in Embodiment 1 are denoted by the same reference numerals, and differences from Embodiment 1 will be mainly described.
  • the distributor 20 of the fourth embodiment is particularly effective when the distributor 20 is provided in the second header 2b arranged on the lower side of the first header 2a and the second header 2b shown in FIG. be.
  • the distributor 20 is provided in the second header 2b shown in FIG. 1, and the configuration of the distributor 20 will be described based on FIG.
  • a plurality of connection ports 21o into which the end portions 1e of the plurality of heat transfer tubes 1 are inserted are formed in the upper portion of the outer wall portion 21 of the distributor 20.
  • the distributor 20 has an intermediate partition 24 extending in the lateral direction (first direction D1).
  • the intermediate partition 24 is arranged in the hollow portion 21a and divides the hollow portion 21a into upper and lower halves. As shown in FIG. 10 , the front and rear ends of the intermediate partition 24 are connected to the inner surface of the outer wall 21 .
  • the cross-sectional area of the upper space 21a1 in which the ends 1e of the plurality of heat transfer tubes 1 are arranged is It is larger than the cross-sectional area of the lower space 21a2.
  • a plurality of tubular parts 22 are provided in the intermediate partition 24 .
  • the outer wall portion 21 is provided with a plurality of cylindrical portions 22, and the outer wall portion 21 prevents the orifice hole 22o and the like from being crushed. Even when a plurality of cylindrical portions 22 are provided in the intermediate partition 24 connected to the outer wall portion 21 as in the fourth embodiment, the same effect as in the case of the third embodiment can be obtained.
  • a slit 24a is formed in the intermediate partition 24 to allow communication between the lower space 21a2 and the upper space 21a1.
  • a plurality of slits 24a are provided in the longitudinal direction of distributor 20 (first direction D1). Although only one slit 24a is provided in the depth direction (third direction D3) in the example shown in FIG. 10, a plurality of slits 24a may be provided in the depth direction.
  • a plurality of orifice holes 22o in each of the plurality of cylindrical portions 22 are formed so as to communicate between the lower space 21a2 and the upper space 21a1, the space farther from the plurality of connection ports 21o, and the flow path 22p. . As shown in FIG.
  • the plurality of orifice holes 22o in each of the plurality of tubular portions 22 are arranged below the tubular portion 22 protruding into the lower space 21a2. It is provided in the side tubular portion.
  • the refrigerant that has flowed into each of the plurality of flow paths 22p in the distributor 20 is ejected into the lower space 21a2 of the hollow portion 21a through the plurality of orifice holes 22o.
  • the refrigerant ejected from the plurality of flow paths 22p into the lower space 21a2 flows through the slits 24a of the intermediate partition 24 into the upper space 21a1 in which the ends 1e of the plurality of heat transfer tubes 1 are arranged. It flows into the hot tube 1 .
  • the distributor 20 according to the fourth embodiment also includes a plurality of cylindrical portions 22, similarly to the distributor 20 according to the first embodiment, so that the same effects as in the case of the first embodiment can be obtained. play.
  • the distributor 20 of Embodiment 4 includes an intermediate partition 24 extending in the horizontal direction (first direction D1) that vertically bisects the hollow portion 21a.
  • a plurality of cylindrical portions 22 are provided in an intermediate partition 24 arranged in the hollow portion 21a.
  • the intermediate partition 24 is formed with a slit 24a that communicates between the lower space 21a2 and the upper space 21a1 of the hollow portion 21a.
  • a plurality of orifice holes 22o in each of the plurality of cylindrical portions 22 are formed so as to communicate between the lower space 21a2 and the upper space 21a1, the space farther from the plurality of connection ports 21o, and the flow path 22p. .
  • the plurality of cylindrical portions 22 are connected by the intermediate partitions 24, so that even when processing headers, the functions of the distributor 20 can be maintained.
  • a space (lower space 21a2 in the example shown in FIG. 10) partitioned from the plurality of heat transfer tubes 1 by the intermediate partition 24 can be formed, and even when the distributor 20 is provided below the heat transfer tubes 1 , the direction of the coolant can be changed smoothly through the partitioned space. Then, the refrigerant can be sprayed upward through the slits 24 a of the intermediate partition 24 to facilitate the flow into the heat transfer tubes 1 .
  • FIG. 11 is a cross-sectional view showing an example of distributor 20 according to Embodiment 5.
  • FIG. 12 is a sectional view showing the BB section of the distributor 20 of FIG. In FIG. 12, the white arrow indicates the direction in which the coolant flows.
  • FIG. 12 also shows the pitch P1 between the heat transfer tubes 1 inserted into the distributor 20.
  • FIG. 13 is a sectional view showing the CC section of the distributor 20 of FIG. 11. As shown in FIG.
  • the fifth embodiment is different from the first embodiment in that the positions of the orifice holes 22o in the first direction D1 are different among the plurality of tubular portions 22, and the other configurations are the same as those of the first embodiment. is similar to In the fifth embodiment, the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • the lead lines of the orifice holes 22o formed in the cylindrical portion 22 on the front side are indicated by solid lines, and the lead lines of the orifice holes 22o formed on the cylindrical portion 22 on the back side are indicated by broken lines.
  • the pitch P2 of the orifice holes 22o in the tubular portion 22 is the same for the plurality of tubular portions 22. As shown in FIG. In the case where the distributor 20 has two tubular portions 22 as shown in FIG. 11, for example, the pitch P2 of the orifice holes 22o in the tubular portion 22 as shown in FIG. It can be doubled.
  • the orifice holes 22o in the tubular portion 22 on the near side are provided at positions different from those in which the orifice holes 22o are provided in the tubular portion 22 on the far side. Therefore, as shown in FIGS. 12 and 13, among the plurality of heat transfer tubes 1 connected to the distributor 20, the odd-numbered heat transfer tubes 1 from the left have the orifices provided in the cylindrical portion 22 on the front side. Coolant is ejected from the holes 22o. In addition, refrigerant is jetted from the orifice holes 22o provided in the cylindrical portion 22 on the far side to the even-numbered heat transfer tubes 1 from the left.
  • the pitch P1 of the heat transfer tubes 1 is a narrow pitch of less than 10 [mm]
  • the pitch of the orifice holes 22o becomes narrower. Therefore, it becomes difficult to form the orifice hole 22o in the tubular portion 22 in terms of manufacturing, and the tubular portion 22 is weakened in terms of pressure resistance.
  • the orifice holes 22o of the adjacent cylindrical portions 22 are provided at different positions so as to alternate in the lateral direction (first direction D1).
  • the pitch P2 of the orifice holes 22o provided in each tubular portion 22 is increased, making it easier to provide one orifice hole 22o per heat transfer tube, ensuring good distribution. Furthermore, by increasing the pitch P2 of the orifice holes 22o, manufacturing difficulties can be avoided and the pressure resistance is improved.
  • FIG. 14 is a cross-sectional view showing an example of distributor 20 according to the sixth embodiment.
  • the number of orifice holes 22o provided in each cylindrical portion 22 in the cross section perpendicular to the lateral direction (first direction D1) of distributor 20 is different from that in Embodiment 1, and other is the same as that of the first embodiment.
  • the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • a plurality of orifice holes 22o are provided on the same plane (cross section shown in FIG. 14).
  • two tubular portions 22 are provided on the near side and the far side in the hollow portion 21a in the outer wall portion 21 of the distributor 20, and the tubular portion 22 on the near side is provided with the flow path.
  • Orifice holes 22o are provided below the center C1 of the channel 22p and on the front side and below the center C1 of the channel 22p.
  • An orifice hole 22o is provided on each of the lower and inner sides.
  • a plurality of orifice holes 22o are provided in the cross section of the tubular portion 22, even if the distribution of the liquid refrigerant in the tubular portion 22 is uneven, the plurality of orifice holes 22o allow the refrigerant to be transmitted. The distribution when entering the heat tube 1 is evened out and a better distribution can be provided.
  • a plurality of orifice holes 22o in the cross section of the tubular portion 22 it is possible to distribute the liquid or gas in a biased manner not only for uniform distribution.
  • the portion where a plurality of orifice holes 22o are provided on the same plane does not have to be the entire distributor 20 .
  • the shape of the orifice holes 22o in Embodiment 6 may be a slit-like shape, and the number of orifice holes 22o may be equal to or less than the number of heat transfer tubes 1, that is, the number of connection openings 21o provided in the outer wall portion 21. good.
  • the orifice holes 22o do not need to have the same shape and size throughout the tubular portion 22, and the orifice holes 22o may have a larger area only in a portion of the tubular portion 22.
  • FIG. the size of the orifice hole 22o provided in one portion of the tubular portion 22 and the size of the orifice hole 22o provided in another portion of the tubular portion 22 may be different.
  • the shape or size of the orifice holes 22o are changed, or the number of orifices 22o is the same or less than the number of the heat transfer tubes 1, etc., so that the refrigerant with a biased liquid or gas ratio is intentionally distributed to any portion. be able to.
  • a plurality of orifice holes 22o are provided on the same plane perpendicular to the channel 22p in one cylindrical portion 22.
  • the plurality of orifice holes 22o make the distribution of the refrigerant uniform when it flows into the heat transfer tube 1, resulting in better heat transfer.
  • a distribution can be provided.
  • the shape of the orifice holes 22o may be a slit-like shape, and the number of orifice holes 22o is equal to or less than the number of heat transfer tubes 1, that is, the number of connection ports 21o provided in the outer wall portion 21. It's okay.
  • the orifice holes 22o do not have to have the same shape or size over the entire tubular portion 22, and the orifice holes 22o may have a larger area only in a part of the tubular portion 22.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

Le distributeur, l'échangeur de chaleur et le dispositif de thermopompe de l'invention comprennent : une partie de paroi externe cylindrique se déployant latéralement ; et plusieurs parties cylindriques se déployant latéralement, qui sont disposées dans la partie de paroi externe ou dans une partie creuse à l'intérieur de la partie de paroi externe, et qui présentent un intérieur dans lequel est formé un trajet d'écoulement ayant une section transversale circulaire. Les parties cylindriques sont disposées parallèlement les unes aux autres. Plusieurs orifices de raccordement sont formés à intervalles espacés latéralement au sommet ou au fond de la partie de paroi externe, et plusieurs trous d'orifice sont formés à intervalles espacés latéralement dans les parties cylindriques.
PCT/JP2021/038152 2021-10-15 2021-10-15 Distributeur, échangeur de chaleur et dispositif de thermopompe Ceased WO2023062800A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US18/696,373 US20240384946A1 (en) 2021-10-15 2021-10-15 Distributor, heat exchanger, and heat pump apparatus
PCT/JP2021/038152 WO2023062800A1 (fr) 2021-10-15 2021-10-15 Distributeur, échangeur de chaleur et dispositif de thermopompe
GB2405105.4A GB2625961A (en) 2021-10-15 2021-10-15 Distributor, heat exchanger, and heat pump device
JP2022526087A JP7142806B1 (ja) 2021-10-15 2021-10-15 分配器、熱交換器およびヒートポンプ装置
DE112021008363.5T DE112021008363T5 (de) 2021-10-15 2021-10-15 Verteiler, Wärmetauscher, und Wärmepumpengerät
CN202180103181.9A CN118176402A (zh) 2021-10-15 2021-10-15 分配器、热交换器以及热泵装置

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Application Number Priority Date Filing Date Title
PCT/JP2021/038152 WO2023062800A1 (fr) 2021-10-15 2021-10-15 Distributeur, échangeur de chaleur et dispositif de thermopompe

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WO2023062800A1 true WO2023062800A1 (fr) 2023-04-20

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US (1) US20240384946A1 (fr)
JP (1) JP7142806B1 (fr)
CN (1) CN118176402A (fr)
DE (1) DE112021008363T5 (fr)
GB (1) GB2625961A (fr)
WO (1) WO2023062800A1 (fr)

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JPH09166368A (ja) * 1995-12-14 1997-06-24 Sanden Corp 熱交換器
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JP2004177041A (ja) * 2002-11-28 2004-06-24 Matsushita Electric Ind Co Ltd 熱交換器
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JP7142806B1 (ja) 2022-09-27
CN118176402A (zh) 2024-06-11
DE112021008363T5 (de) 2024-08-01
US20240384946A1 (en) 2024-11-21
JPWO2023062800A1 (fr) 2023-04-20
GB2625961A (en) 2024-07-03

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