WO2021234959A1 - 冷媒分配器、熱交換器及び空気調和装置 - Google Patents

冷媒分配器、熱交換器及び空気調和装置 Download PDF

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Publication number
WO2021234959A1
WO2021234959A1 PCT/JP2020/020352 JP2020020352W WO2021234959A1 WO 2021234959 A1 WO2021234959 A1 WO 2021234959A1 JP 2020020352 W JP2020020352 W JP 2020020352W WO 2021234959 A1 WO2021234959 A1 WO 2021234959A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
inner pipe
heat exchanger
pipe
flow hole
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/JP2020/020352
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English (en)
French (fr)
Japanese (ja)
Inventor
洋次 尾中
崇 松本
理人 足立
哲二 七種
祐基 中尾
裕之 森本
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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 PCT/JP2020/020352 priority Critical patent/WO2021234959A1/ja
Priority to JP2022524504A priority patent/JP7353480B2/ja
Priority to US17/918,237 priority patent/US12270581B2/en
Priority to CN202180035734.1A priority patent/CN115667832A/zh
Priority to PCT/JP2021/018888 priority patent/WO2021235463A1/ja
Priority to EP21808264.2A priority patent/EP4155655B1/en
Publication of WO2021234959A1 publication Critical patent/WO2021234959A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • 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
    • F28D1/05375—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
    • F28F9/0273—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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • 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
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0297—Side headers, e.g. for radiators having conduits laterally connected to common header

Definitions

  • the present disclosure relates to a double-structured refrigerant distributor, heat exchanger, and air conditioner including an inner pipe and an outer pipe.
  • a refrigerant distributor that distributes a refrigerant using a double-structured pipe having an inner pipe and an outer pipe is known.
  • a refrigerant flow hole also called an orifice hole is provided at the lowermost portion of the inner pipe.
  • the refrigerant flowing out of the refrigerant flow hole is ejected into the space between the inner pipe and the outer pipe, flows into the heat transfer pipe from the outer pipe, and exchanges heat with air there (see, for example, Patent Document 1).
  • the refrigerant distributor it is difficult for the flow state of the refrigerant to transition to the annular flow for various reasons, and the refrigerant distributor is in the vertical direction even though it is in the annular basin in the general flow mode diagram.
  • the liquid phase distribution in the cross section is biased.
  • the inflow pipe of the refrigerant is short, or when the heat exchanger and the heat exchanger are connected by a connecting pipe having a bent portion to form one heat exchanger.
  • the conventional refrigerant distributor has a problem that the refrigerant cannot be sufficiently distributed due to the bias of the liquid phase distribution.
  • the present disclosure has been made in view of the above circumstances, and provides a refrigerant distributor, a heat exchanger, and an air conditioner capable of suppressing the bias of the liquid phase distribution of the refrigerant distributor and appropriately distributing the refrigerant.
  • the purpose is to provide.
  • the refrigerant distributor of the present disclosure includes an outer pipe in which a plurality of heat transfer pipes are connected at predetermined intervals, and an inner pipe housed in the outer pipe and having a refrigerant flow hole, and the refrigerant flow hole is the inner pipe.
  • the angle ⁇ seen from the center of the inner pipe from the lower end of the inner pipe on the vertical line passing through the center of the pipe to the position where the refrigerant flow hole exists is provided in the range of 10 ° ⁇ ⁇ ⁇ 80 °, and the refrigerant is provided.
  • the refrigerant distributor of the present disclosure has only one refrigerant flow hole in the vertical cross section of the inner pipe at the position where the refrigerant flow hole is provided.
  • the refrigerant flow hole is provided in a range where the angle ⁇ from the lower end of the inner pipe on the vertical line passing through the center of the inner pipe to the position where the refrigerant flow hole exists is in the range of 10 ° ⁇ ⁇ ⁇ 80 °. Therefore, the refrigerant flow holes are provided only in the vicinity of the liquid level of the refrigerant. Thereby, the refrigerant distributor can uniformly distribute the refrigerant in the space formed between the inner pipe and the outer pipe, and can appropriately distribute the refrigerant.
  • FIG. It is a refrigerant circuit diagram of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a side schematic of the outdoor heat exchanger of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a top view of the outdoor heat exchanger of the air conditioner according to the first embodiment. It is a figure which shows the state of the refrigerant in the inner pipe of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a vertical sectional view of the refrigerant distributor of line AA of FIG. 3 of the air conditioner which concerns on Embodiment 1.
  • FIG. It is sectional drawing in the vertical direction which shows the relationship between the liquid level of the refrigerant of the inner pipe and the refrigerant outflow hole for demonstrating the effect of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure which shows the influence range to the refrigerant of the refrigerant outflow hole for explaining the effect of the air conditioner which concerns on Embodiment 1, and the flow state of a refrigerant. It is a figure which shows the refrigerant distribution amount characteristic when the refrigerant outflow hole for demonstrating the effect of the air conditioner which concerns on Embodiment 1 is provided in the lower part of the inner pipe.
  • FIG. 1 It is sectional drawing in the vertical direction which shows the relationship between the liquid level of the refrigerant of the inner pipe, and the refrigerant outflow hole for demonstrating the effect of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure which shows the influence range to the refrigerant of the refrigerant outflow hole for explaining the effect of the air conditioner which concerns on Embodiment 1, and the flow state of a refrigerant. It is a figure which shows the refrigerant distribution amount characteristic at the time of providing the refrigerant outflow hole in the upper part of the inner pipe for explaining the effect of the air conditioner which concerns on Embodiment 1.
  • FIG. 15 is a vertical cross-sectional view taken along the line AA shown in FIG.
  • FIG. 15 is a vertical sectional view taken along line BB shown in FIG. 15 of the refrigerant distributor of the air conditioner according to the second embodiment. It is a side schematic of the 2nd outdoor heat exchanger of the air conditioner which concerns on Embodiment 3.
  • FIG. 15 is a vertical sectional view taken along line BB shown in FIG. 15 of the refrigerant distributor of the air conditioner according to the second embodiment. It is a side schematic of the 2nd outdoor heat exchanger of the air conditioner which concerns on Embodiment 3.
  • Embodiment 1 an air conditioner having a refrigerant distributor according to the embodiment will be described with reference to the drawings.
  • the same components will be described with the same reference numerals, and duplicate explanations will be given only when necessary.
  • the present disclosure may include any combination of configurable configurations among the configurations described in each of the following embodiments.
  • FIG. 1 is a refrigerant circuit diagram of the air conditioner 100 according to the first embodiment.
  • the air conditioner 100 includes an outdoor unit 10 and a plurality of indoor units 11, 12, and 13.
  • the indoor units 11, 12 and 13 are connected in parallel with each other.
  • the refrigerant circulates inside the outdoor unit 10 and the plurality of indoor units 11, 12, and 13.
  • the air conditioner 100 is a multi-type air conditioner.
  • the first embodiment does not limit the number of indoor units 11, 12, and 13 connected to the outdoor unit 10.
  • the air conditioner 100 has a refrigerant circuit in which a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 5, an indoor heat exchanger 6, and an accumulator 8 are connected by a refrigerant pipe. .. In each of the outdoor heat exchanger 3 and the indoor heat exchanger 6, heat is exchanged between the refrigerant flowing inside and the air by the wind generated by the fan 4 and the fan 7.
  • the refrigerant of the high-temperature and high-pressure gas compressed by the compressor 1 is transferred from the refrigerant pipe 26 connecting the four-way valve 2 and the outdoor heat exchanger 3 to the outdoor heat exchanger 3 via the four-way valve 2. Inflow.
  • the refrigerant flowing into the outdoor heat exchanger 3 exchanges heat with the wind generated by the fan 4, and then flows out from the refrigerant pipe 27 connecting the outdoor heat exchanger 3 and the expansion valve 5.
  • the refrigerant flows in the direction opposite to the refrigerant flow direction in the case of the above-mentioned condenser.
  • FIG. 2 is a schematic side view of the outdoor heat exchanger 3 of the air conditioner 100 according to the first embodiment.
  • FIG. 3 is a top-level drawing of the outdoor heat exchanger 3 of the air conditioner 100 according to the first embodiment.
  • the black arrow in the figure indicates the flow of the refrigerant when it functions as an evaporator.
  • the outdoor heat exchanger 3 mounted on the outdoor unit 10 of the air conditioner 100 exchanges heat between the outside air sucked from the suction port by the fan 4 and the refrigerant.
  • the outdoor heat exchanger 3 is arranged below the fan 4.
  • the outdoor heat exchanger 3 has a refrigerant distributor 30, a plurality of heat transfer tubes 31, and a plurality of fins 32.
  • the refrigerant distributor 30 is arranged in the horizontal direction.
  • the plurality of heat transfer tubes 31 are provided at intervals, and one end of each is inserted into the refrigerant distributor 30.
  • the fin 32 is attached to the heat transfer tube 31 and is provided between the heat transfer tubes 31. The fin 32 transfers heat to the heat transfer tube 31.
  • the refrigerant distributor 30 has a double pipe structure including an inner pipe 33 and an outer pipe 34.
  • a plurality of heat transfer tubes 31 are connected to the outer tube 34 in the extending direction of the outer tube 34.
  • the refrigerant flowing between the inner pipe 33 and the outer pipe 34 is distributed to the plurality of heat transfer pipes 31.
  • the inner pipe 33 is held horizontally in the pipe extension direction.
  • a refrigerant including a liquid refrigerant flows into one end of the inner pipe 33.
  • a cap 36 is provided at the most downstream end of the inner pipe 33 of the flow of the refrigerant when the outdoor heat exchanger 3 functions as an evaporator.
  • the refrigerant pipe 27 of the refrigerating cycle circuit is connected to the uppermost flow end of the inner pipe 33 of the refrigerant flow of the inner pipe 33.
  • a refrigerant outflow hole 35 which is also called an orifice hole, is formed between the heat transfer pipes 31 at intervals in the pipe extending direction of the inner pipe 33. .. Since the refrigerant outflow hole 35 is provided between the heat transfer tubes 31, the refrigerant distribution of the refrigerant distributor 30 is compared with the case where the refrigerant outflow hole 35 is provided in the inner pipe 33 directly below the heat transfer tube 31. Performance can be improved.
  • the refrigerant outflow hole 35 may be formed in the inner pipe 33 directly below the heat transfer pipe 31.
  • the inner pipe 33 is provided with a refrigerant inflow portion 41.
  • the refrigerant inflow portion 41 has a length L as a run-up distance.
  • L when the inner diameter of the inner pipe 33 is D, L ⁇ 5D.
  • FIG. 4 is a diagram showing a state of the refrigerant in the inner pipe 33 of the air conditioner 100 according to the first embodiment.
  • the inner pipe 33 there are two types of refrigerant, a gas phase and a liquid phase.
  • the refrigerant outflow hole 35 is provided in the vicinity of the angle ⁇ 'of the liquid level AL of the liquid phase refrigerant.
  • FIG. 5 is a vertical sectional view of the refrigerant distributor 30 of the AA line of FIG. 3 of the air conditioner 100 according to the first embodiment.
  • FIG. 5 is a diagram showing a state in which the refrigerant is flowing in the inner pipe 33 in a semi-circular flow state.
  • FIG. 5 shows an example in which the refrigerant outflow hole 35 is provided at the angle ⁇ 'of the liquid level AL of the liquid phase refrigerant.
  • the angle ⁇ at which the refrigerant outflow hole 35 is provided is the angle ⁇ from the lower end of the vertical inner pipe 33 passing through the center of the inner pipe 33 as seen from the center of the inner pipe 33 to the position where the refrigerant outflow hole 35 exists. 10 ° ⁇ ⁇ ⁇ 80 ° It may be provided in the range of.
  • Equation (1) is a prediction equation that reflects the experimental results of the inventors based on the estimation equation of the Nusselt liquid film.
  • x is the distance projected from the refrigerant outflow hole 35 onto the horizontal line orthogonal to the pipe extension direction passing through the center of the inner pipe 33.
  • Ja is the number of Jacobs
  • Ga is the number of Galileo
  • Pr L is the number of liquid Prandtl numbers
  • ⁇ L is the hydraulic viscosity coefficient
  • L is the approach distance of the inner pipe
  • D is the inner diameter of the inner pipe
  • Ga gD 3 / ⁇ L 2
  • Ja CpL / ⁇ iv
  • CpL is constant pressure specific heat
  • ⁇ iv latent heat
  • L ⁇ 5D Each state quantity and physical property value shall be estimated by the pressure flowing into the refrigerant distributor 30.
  • FIG. 6 is a vertical sectional view showing the relationship between the liquid level AL of the refrigerant of the inner pipe 33 and the refrigerant outflow hole 35 for explaining the effect of the air conditioner 100 according to the first embodiment.
  • FIG. 6 shows a case where the liquid phase of the refrigerant flowing through the inner pipe 33 is a semi-circular flow. Further, the case where the refrigerant outflow hole 35 is provided at the lowermost portion of the inner pipe 33 is shown.
  • FIG. 7 is a diagram showing the range of influence of the refrigerant outflow hole 35 on the refrigerant and the flow state of the refrigerant for explaining the effect of the air conditioner 100 according to the first embodiment.
  • FIG. 8 is a diagram showing the refrigerant distribution amount characteristics when the refrigerant outflow hole 35 for explaining the effect of the air conditioner 100 according to the first embodiment is provided in the lower part of the inner pipe 33.
  • FIGS. 7 and 8 show a case where the refrigerant outflow hole 35 is provided at the lowermost portion of the inner pipe 33, as shown in FIG.
  • the position of the refrigerant outflow hole 35 near the refrigerant inflow portion 41 is designated as A
  • the position far from the refrigerant inflow portion 41 is designated as G in alphabetical order.
  • the broken line represents the range of influence of each refrigerant outflow hole 35, and at a certain time, the refrigerant in the broken line passes through the refrigerant outflow hole 35 and is distributed.
  • the liquid refrigerant distribution amount of the refrigerant outflow holes A to D on the upstream side is the liquid refrigerant distribution of the refrigerant outflow holes E to G on the downstream side. It is large compared to the amount.
  • FIG. 9 is a vertical sectional view showing the relationship between the liquid level AL of the refrigerant of the inner pipe 33 and the refrigerant outflow hole 35 for explaining the effect of the air conditioner 100 according to the first embodiment.
  • FIG. 9 shows a case where the liquid phase of the refrigerant flowing
  • FIG. 10 is a diagram showing the range of influence of the refrigerant outflow hole 35 on the refrigerant and the flow state of the refrigerant for explaining the effect of the air conditioner 100 according to the first embodiment.
  • the liquid refrigerant distribution amount of the refrigerant outflow holes A to C on the upstream side is the liquid refrigerant distribution of the refrigerant outflow holes D to G on the downstream side. Less than the amount.
  • FIG. 12 is a vertical sectional view showing the relationship between the liquid level AL of the refrigerant of the inner pipe 33 of the inner pipe 33 of the air conditioner 100 according to the first embodiment and the refrigerant outflow hole 35.
  • FIG. 12 shows a case where the liquid phase of the refrigerant flowing through the inner pipe 33 is a semi-circular flow.
  • the refrigerant outflow hole 35 is provided near the liquid level AL of the inner pipe 33. Only one refrigerant outflow hole 35 is provided in the vertical cross section of the inner pipe 33.
  • FIG. 13 is a diagram showing the range of influence of the refrigerant outflow hole 35 of the air conditioner 100 according to the first embodiment on the refrigerant and the flow state.
  • FIG. 14 is a diagram showing the refrigerant distribution amount characteristics when the refrigerant outflow hole 35 of the air conditioner 100 according to the first embodiment is provided on the liquid level AL of the inner pipe 33. 13 and 14 show a case where the refrigerant outflow hole 35 is provided at the position of the liquid level AL of the inner pipe 33, as shown in FIG. Even when the flow mode of the refrigerant is a semi-circular flow, as shown in FIG. 14, the liquid refrigerant distribution amounts of the refrigerant outflow holes A to G are relatively uniform as compared with FIGS. 8 and 11. ..
  • the refrigerant outflow hole 35 is provided in the vicinity of the liquid level AL even when a sufficient approach distance cannot be secured (L ⁇ 5D).
  • the gas and liquid can be relatively uniformly distributed to the space formed between the outer pipe 34 and the inner pipe 33. Therefore, the refrigerant distributor 30 can appropriately distribute the refrigerant.
  • Embodiment 2 In the first embodiment, the case of one outdoor heat exchanger 3 has been described. In the second embodiment, a case where the first outdoor heat exchanger 3a and the second outdoor heat exchanger 3b are connected by the bending inner pipe 33r will be described.
  • FIG. 15 is a top-level drawing of the outdoor heat exchanger 3 of the air conditioner 100 according to the second embodiment.
  • the outdoor heat exchanger 3 has a first outdoor heat exchanger 3a and a second outdoor heat exchanger 3b.
  • the first refrigerant distributor 30a of the first outdoor heat exchanger 3a and the second refrigerant distributor 30b of the second outdoor heat exchanger 3b are connected by a bent inner pipe 33r having a bent portion having a curvature.
  • the bent inner pipe 33r connects the inner pipe 33 of the first outdoor heat exchanger 3a and the inner pipe 33 of the second outdoor heat exchanger 3b.
  • FIG. 16 is a vertical sectional view taken along line AA shown in FIG. 15 of the first refrigerant distributor 30a of the air conditioner 100 according to the second embodiment.
  • the flow mode of the refrigerant flowing through the inner pipe 33 of the first refrigerant distributor 30a of the first outdoor heat exchanger 3a is a semi-circular flow.
  • FIG. 17 is a vertical sectional view taken along line BB shown in FIG. 15 of the first refrigerant distributor 30a of the air conditioner 100 according to the second embodiment.
  • the flow mode of the refrigerant flowing through the inner pipe 33 of the second refrigerant distributor 30b of the second outdoor heat exchanger 3b is a separate flow.
  • the angle ⁇ 2 of the refrigerant outflow hole 35 of the second refrigerant distributor 30b includes one having a larger angle ⁇ 1 of the refrigerant outflow hole 35 of the first refrigerant distributor 30a in the range of ⁇ 180 ° to 180 ° ( ⁇ 2>. ⁇ 1).
  • the flow mode of the refrigerant flowing through the inner pipe 33 of the first refrigerant distributor 30a before passing through the bent inner pipe 33r is a semi-circular flow.
  • the flow mode of the refrigerant flowing through the inner pipe 33 of the second refrigerant distributor 30b after passing through the bent inner pipe 33r is a separated flow. Therefore, as shown in FIG. 17, the liquid level AL of the refrigerant rises, and the refrigerant distribution performance deteriorates.
  • the angle ⁇ 2 of the refrigerant outflow hole 35 of the second refrigerant distributor 30b is larger than the angle ⁇ 1 of the refrigerant outflow hole 35 of the first refrigerant distributor 30a. Thereby, the refrigerant distribution performance of the first refrigerant distributor 30a and the second refrigerant distributor 30b can be improved.
  • the bent inner pipe 33r may be an L-shaped pipe joint (elbow). Further, it may be formed by bending the outer pipe 34 of the first refrigerant distributor 30a.
  • Embodiment 3 As the outdoor heat exchanger 3 of the third embodiment, the configuration including the first outdoor heat exchanger 3a and the second outdoor heat exchanger 3b is adopted as in the second embodiment shown in FIG. In the third embodiment, in such a configuration, the diameter of the inner pipe 33 of the second outdoor heat exchanger 3b is reduced toward the end portion.
  • FIG. 18 is a schematic side view of the second outdoor heat exchanger 3b of the air conditioner 100 according to the third embodiment.
  • the second outdoor heat exchanger 3b has an inner pipe 33a and an inner pipe 33b.
  • the inner pipe 33 of the first outdoor heat exchanger 3a is connected to the inner pipe 33a (see FIG. 15) of the second outdoor heat exchanger 3b via the bent inner pipe 33r (see FIG. 15). It is connected.
  • the inner diameter of the inner pipe 33a of the second outdoor heat exchanger 3b is the same as the inner diameter of the inner pipe 33 of the first outdoor heat exchanger 3a.
  • the inner pipe 33a is connected to the inner pipe 33b.
  • the inner diameter of the inner pipe 33b is smaller than the inner diameter of the inner pipe 33a.
  • a cap 36 is provided at the end of the inner pipe 33b. That is, the inner diameter of the end portion of the inner pipe 33b of the second outdoor heat exchanger 3b on the side where the cap 36 is provided is the side to which the bent inner pipe 33r of the inner pipe 33a of the second heat exchanger is connected. It is smaller than the inner diameter of the starting end.
  • the refrigerant flow rate at the terminal portion of the second refrigerant distributor 30b of the second outdoor heat exchanger 3b is reduced, and the flow mode changes from the semi-circular flow to the separated flow. Can be suppressed. Therefore, the flow rate robustness of the refrigerant distribution characteristic can be improved.
  • the inner pipe 33 of the second outdoor heat exchanger 3b ends from the start end.
  • the pipe may be such that the inner diameter gradually decreases toward the portion.
  • 1 Compressor 2 4-way valve, 3 Outdoor heat exchanger, 3a 1st outdoor heat exchanger, 3b 2nd outdoor heat exchanger, 4 fan, 5 expansion valve, 6 indoor heat exchanger, 7 fan, 8 accumulator, 10 Outdoor unit, 11, 12, 13 indoor unit, 26, 27 refrigerant pipe, 30 refrigerant distributor, 30a first refrigerant distributor, 30b second refrigerant distributor, 31 heat transfer tube, 32 fins, 33, 33a, 33b inner tube , 33r bending inner pipe, 34 outer pipe, 35 refrigerant outflow hole, 36 cap, 41 inflow part, 100 air exchanger, AL liquid level.

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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)
  • Other Air-Conditioning Systems (AREA)
PCT/JP2020/020352 2020-05-22 2020-05-22 冷媒分配器、熱交換器及び空気調和装置 Ceased WO2021234959A1 (ja)

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PCT/JP2020/020352 WO2021234959A1 (ja) 2020-05-22 2020-05-22 冷媒分配器、熱交換器及び空気調和装置
JP2022524504A JP7353480B2 (ja) 2020-05-22 2021-05-19 冷媒分配器、熱交換器及び空気調和装置
US17/918,237 US12270581B2 (en) 2020-05-22 2021-05-19 Refrigerant distributor, heat exchanger, and air-conditioning apparatus
CN202180035734.1A CN115667832A (zh) 2020-05-22 2021-05-19 制冷剂分配器、热交换器以及空调装置
PCT/JP2021/018888 WO2021235463A1 (ja) 2020-05-22 2021-05-19 冷媒分配器、熱交換器及び空気調和装置
EP21808264.2A EP4155655B1 (en) 2020-05-22 2021-05-19 Refrigerant distributor, heat exchanger, and air conditioner

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2025158522A1 (ja) * 2024-01-23 2025-07-31 三菱電機株式会社 熱交換器、室外機および冷凍サイクル装置
WO2025158523A1 (ja) * 2024-01-23 2025-07-31 三菱電機株式会社 熱交換器、室外機および冷凍サイクル装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7693095B2 (ja) * 2022-03-18 2025-06-16 三菱電機株式会社 空気調和装置の室外機および空気調和装置
WO2024042575A1 (ja) * 2022-08-22 2024-02-29 三菱電機株式会社 熱交換器および冷凍サイクル装置
WO2024257145A1 (ja) * 2023-06-12 2024-12-19 三菱電機株式会社 熱交換器及び空気調和装置
JP7612110B1 (ja) * 2023-09-27 2025-01-10 三菱電機株式会社 熱交換器、室外機および空気調和装置
WO2025159144A1 (ja) * 2024-01-23 2025-07-31 三菱電機株式会社 分配器、熱交換器、分配器の製造方法および、熱交換器の製造方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0886591A (ja) * 1994-07-22 1996-04-02 Nippondenso Co Ltd 熱交換器、および冷媒蒸発器
JP2005180910A (ja) * 2003-12-22 2005-07-07 Hussmann Corp マイクロ分配器を設ける平管蒸発器
US20100089559A1 (en) * 2006-10-13 2010-04-15 Carrier Corporation Method and apparatus for improving distribution of fluid in a heat exchanger
US20110000255A1 (en) * 2008-05-16 2011-01-06 Taras Michael F Microchannel heat exchanger with enhanced refrigerant distribution
US20110203308A1 (en) * 2008-01-17 2011-08-25 Robert Hong-Leung Chiang Heat exchanger including multiple tube distributor
JP2017032244A (ja) * 2015-08-05 2017-02-09 東芝キヤリア株式会社 冷凍サイクル装置
WO2019239446A1 (ja) * 2018-06-11 2019-12-19 三菱電機株式会社 空気調和装置の室外機及び空気調和装置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101782297B (zh) * 2009-01-19 2012-08-22 三花控股集团有限公司 一种热交换器
DE102009057232A1 (de) * 2009-12-05 2011-06-09 GM Global Technology Operations LLC, ( n. d. Ges. d. Staates Delaware ), Detroit Rohrförmiger Wärmetauscher für Kraftfahrzeug-Klimaanlage
CN101839590B (zh) * 2010-02-22 2012-03-21 三花丹佛斯（杭州）微通道换热器有限公司 一种微通道换热器
JP2012002475A (ja) * 2010-06-21 2012-01-05 Mitsubishi Electric Corp 冷媒分配器及びこの冷媒分配器を用いたヒートポンプ装置
JP2012021734A (ja) * 2010-07-16 2012-02-02 Showa Denko Kk 二重管式熱交換器
KR101217454B1 (ko) * 2012-05-29 2013-01-02 안정국 축냉시스템의 냉매분배기
CN103604254B (zh) * 2013-11-12 2016-07-06 清华大学 一种内置气液两相流分流结构
CN107208948B (zh) * 2015-04-24 2019-12-24 株式会社电装 制冷剂蒸发器
KR102132742B1 (ko) * 2018-07-25 2020-07-10 엘지전자 주식회사 열교환기

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0886591A (ja) * 1994-07-22 1996-04-02 Nippondenso Co Ltd 熱交換器、および冷媒蒸発器
JP2005180910A (ja) * 2003-12-22 2005-07-07 Hussmann Corp マイクロ分配器を設ける平管蒸発器
US20100089559A1 (en) * 2006-10-13 2010-04-15 Carrier Corporation Method and apparatus for improving distribution of fluid in a heat exchanger
US20110203308A1 (en) * 2008-01-17 2011-08-25 Robert Hong-Leung Chiang Heat exchanger including multiple tube distributor
US20110000255A1 (en) * 2008-05-16 2011-01-06 Taras Michael F Microchannel heat exchanger with enhanced refrigerant distribution
JP2017032244A (ja) * 2015-08-05 2017-02-09 東芝キヤリア株式会社 冷凍サイクル装置
WO2019239446A1 (ja) * 2018-06-11 2019-12-19 三菱電機株式会社 空気調和装置の室外機及び空気調和装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2025158522A1 (ja) * 2024-01-23 2025-07-31 三菱電機株式会社 熱交換器、室外機および冷凍サイクル装置
WO2025158523A1 (ja) * 2024-01-23 2025-07-31 三菱電機株式会社 熱交換器、室外機および冷凍サイクル装置

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US20230146747A1 (en) 2023-05-11
EP4155655A4 (en) 2023-11-15
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EP4155655A1 (en) 2023-03-29

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