WO2019167909A1 - Unité d'échangeur de chaleur et climatiseur l'utilisant - Google Patents

Unité d'échangeur de chaleur et climatiseur l'utilisant Download PDF

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Publication number
WO2019167909A1
WO2019167909A1 PCT/JP2019/007174 JP2019007174W WO2019167909A1 WO 2019167909 A1 WO2019167909 A1 WO 2019167909A1 JP 2019007174 W JP2019007174 W JP 2019007174W WO 2019167909 A1 WO2019167909 A1 WO 2019167909A1
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WIPO (PCT)
Prior art keywords
heat exchanger
pipe
refrigerant
heat exchangers
unit
Prior art date
Application number
PCT/JP2019/007174
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English (en)
Japanese (ja)
Inventor
拓也 奥村
一彦 丸本
憲昭 山本
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to EP19760689.0A priority Critical patent/EP3760949B1/fr
Priority to CN201980016272.1A priority patent/CN111801538A/zh
Publication of WO2019167909A1 publication Critical patent/WO2019167909A1/fr

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    • 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
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • 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
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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
    • F25B41/48—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow path resistance control on the downstream side of the diverging point, e.g. by an orifice
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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
    • 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 heat exchanger unit configured by connecting a plurality of heat exchangers in parallel, and an air conditioner using the heat exchanger unit.
  • the present invention relates to a heat exchanger unit suitable for the case where the heat exchanger is a plate fin stacked heat exchanger, and an air conditioner using the heat exchanger unit.
  • an air conditioner performs cooling or heating by circulating a refrigerant compressed by a compressor through a heat exchanger such as a condenser and an evaporator to exchange heat with air.
  • a heat exchanger such as a condenser and an evaporator to exchange heat with air.
  • the heat exchanger may be a unit obtained by combining a plurality of heat exchangers. In such a case, it is preferable that the refrigerant flows through each heat exchanger substantially evenly so that the heat exchange efficiency of each heat exchanger becomes substantially the same.
  • the refrigerant is divided through the distributor, and the refrigerant is supplied to each heat exchanger almost uniformly (see, for example, Patent Document 1).
  • FIG. 13 shows a schematic configuration of a conventional heat exchanger unit described in Patent Document 1.
  • Three heat exchangers 101 are connected in parallel, and a distributor 102 is provided at the refrigerant branch. Further, a flow rate adjusting unit 103 is provided between the distributor 102 and the inlet pipe portion of the heat exchanger 101 on the downstream side. Then, the refrigerant is diverted by the distributor 102. Then, the flow rate adjustment unit 103 adjusts the flow rate of the refrigerant, that is, the pressure loss (hereinafter referred to as pressure loss), and the refrigerant is supplied to each heat exchanger 101.
  • pressure loss the pressure loss
  • the refrigerant diverted by the distributor 102 is adjusted in flow rate by the flow rate adjusting unit 103 and flows into each heat exchanger 101.
  • the pressure loss of the outlet pipes is different, the dryness of the inlets changes between the plurality of heat exchangers 101, and a difference in the divided flow rate may occur, so that it may not be possible to evenly distribute to the plurality of heat exchangers. That is, if the flow rate adjustment by the flow rate adjusting unit 103 at the inlet portion of the heat exchanger, in other words, the pressure loss adjustment is performed, the equalization of the divided flow proceeds as compared with the case where the pressure loss adjustment is not performed, but the equalization degree of the divided flow is still not sufficient. There is room for improvement.
  • the present disclosure provides a heat exchanger unit that improves the degree of equalization when the refrigerant is divided into a plurality of heat exchangers and exhibits good heat exchange performance, and a high-performance air conditioner using the heat exchanger unit To do.
  • the heat exchanger unit of the present disclosure is a heat exchanger unit including a plurality of heat exchangers, and each of the plurality of heat exchangers includes a first pipe into which a refrigerant flows and a first pipe A plurality of refrigerants that communicate the first header channel that communicates with the outflow side of the piping, the second header channel that is disposed downstream of the first header channel, and the first header channel and the second header channel. A flow path and a second pipe communicating with the outflow side of the second header flow path.
  • At least one of a branching unit that splits the refrigerant to the first pipe in each of the plurality of heat exchangers, a merging unit that joins the refrigerant from the second pipe in each of the plurality of heat exchangers, and a plurality of heat exchangers A first flow rate adjusting unit provided in the first pipe, and a second flow rate adjusting unit provided in the second pipe in at least one of the plurality of heat exchangers.
  • the flow rate adjustment unit is adjusted so that the pressure loss on the inlet side and the pressure loss on the outlet side of each heat exchanger are equal, the dryness of the refrigerant and the circulation amount are made equal to each heat exchanger. Can be distributed. Therefore, it is possible to increase the degree of equalization of the refrigerant diversion between the heat exchangers. In other words, the uniform flow of the refrigerant to each heat exchanger is made more reliable, the heat exchange efficiency among a plurality of heat exchangers is equalized, and the heat exchange performance as a whole heat exchanger unit is improved. Can do.
  • FIG. 1 is a diagram illustrating a schematic configuration of a heat exchanger unit according to Embodiment 1 of the present disclosure.
  • FIG. 2 is an exploded perspective view of the heat exchanger of the heat exchanger unit in FIG. 1 as viewed from below.
  • FIG. 3 is a plan view of plate fins constituting the heat exchanger of the heat exchanger unit in FIG. 1.
  • 4 is an exploded perspective view showing a part of the plate fin in FIG. 3 in an enlarged manner.
  • FIG. 5 is a perspective view showing a cross section of a refrigerant flow path portion in the heat exchanger of the heat exchanger unit in FIG. 1.
  • 6 is a perspective view showing a cross section of the header flow path portion of the heat exchanger in FIG.
  • FIG. 1 is a diagram illustrating a schematic configuration of a heat exchanger unit according to Embodiment 1 of the present disclosure.
  • FIG. 2 is an exploded perspective view of the heat exchanger of the heat exchanger unit in FIG. 1 as viewed from below.
  • FIG. 7 is a diagram illustrating a schematic configuration of a heat exchanger unit according to the second embodiment of the present disclosure.
  • FIG. 8 is a diagram showing a schematic configuration of a portion indicated by a in FIG.
  • FIG. 9 is a refrigeration cycle diagram of the air conditioner according to Embodiment 3 of the present disclosure.
  • FIG. 10 is a diagram showing a cross-sectional configuration when the air conditioner according to Embodiment 3 is viewed from the right side.
  • FIG. 11 is a figure which shows the cross-sectional structure when the air conditioner in Embodiment 3 is seen from the top.
  • FIG. 12 is a diagram illustrating an arrangement configuration of the heat exchanger of the air conditioner according to the third embodiment.
  • FIG. 13 is a diagram showing a schematic configuration of a conventional heat exchanger unit.
  • the plate fin laminated heat exchanger can easily reduce the diameter of the heat transfer channel between the header of the inlet portion and the header of the outlet portion, and can increase the number of heat transfer channels (number of passes). Therefore, when it is used as an indoor heat exchanger for an air conditioner, a great effect can be obtained.
  • the present inventors connected a plurality of these plate fin stacked heat exchangers in parallel, and provided a flow rate adjusting unit on the inlet side of each heat exchanger to equalize the pressure loss of the inlet piping between the plurality of heat exchangers. Even if it adjusts so that it may become, if the pressure loss differs among several heat exchangers, for example, the length of outlet piping differs, the equal distribution of the refrigerant to each heat exchanger cannot be realized.
  • the present inventors came to consider as the cause as follows. That is, in a multi-pass type small heat exchanger such as a plate fin laminated heat exchanger, even if the flow rate is adjusted at the inlet of the heat exchanger, the internal pressure loss of the heat exchanger itself is extremely small.
  • Patent Document 1 when a heat exchanger unit in which a plurality of heat exchangers are combined is used in an outdoor unit, the plurality of heat exchangers are respectively connected to separate outlets. Therefore, even if the heat exchange efficiency is somewhat different between the plurality of heat exchangers, there is no problem.
  • a heat exchanger unit in which multiple heat exchangers are combined in parallel is used to face one outlet for an indoor unit, the difference in heat exchange efficiency between the heat exchangers Directly linked to the air temperature difference. Therefore, the user is uncomfortable. Therefore, it is necessary to further increase the degree of equalization of the diversion flow to each heat exchanger.
  • a heat exchanger unit is a heat exchanger unit including a plurality of heat exchangers, and each of the plurality of heat exchangers includes a first pipe into which a refrigerant flows and a first pipe.
  • a first header channel communicating with the outflow side of the first header channel, a second header channel disposed downstream of the first header channel, and a plurality of refrigerant flows communicating the first header channel and the second header channel And a second pipe communicating with the outflow side of the second header channel.
  • At least one of a branching unit that splits the refrigerant to the first pipe in each of the plurality of heat exchangers, a merging unit that joins the refrigerant from the second pipe in each of the plurality of heat exchangers, and a plurality of heat exchangers A first flow rate adjusting unit provided in the first pipe, and a second flow rate adjusting unit provided in the second pipe in at least one of the plurality of heat exchangers.
  • the flow rate adjustment unit is adjusted so that the pressure loss on the inlet side and the pressure loss on the outlet side of each heat exchanger are equal, the dryness of the refrigerant and the circulation amount are made equal to each heat exchanger. Can be distributed. Therefore, it is possible to increase the degree of equalization of the refrigerant diversion between the heat exchangers. That is, it is possible to improve the heat exchange performance of the heat exchanger unit as a whole by making the uniform flow of the refrigerant to each heat exchanger more reliable and equalizing the heat exchange efficiency.
  • each of the plurality of heat exchangers is a plate fin stacked heat exchanger having a plurality of plate fins, and each of the plurality of plate fins includes two sheets.
  • the plurality of refrigerant flow paths are formed by concave grooves formed in at least one of the two plate-shaped members, and the first header flow path and the second header flow path are formed.
  • the heat exchanger unit according to another aspect of the present disclosure may have a configuration in which a distributor is provided in a refrigerant distribution part.
  • a branch pipe is provided in the refrigerant branching portion, and a throttle pipe having a pipe diameter smaller than the pipe diameter at the inlet of the branch pipe is provided upstream of the branch pipe. It may be a configured.
  • the refrigerant is accelerated by the throttle tube so that the flow rate of the refrigerant immediately after the throttle tube becomes an annular flow. Therefore, when such a refrigerant flows in from the inlet of the branch pipe, the refrigerant can be divided and supplied to each heat exchanger with a substantially similar gas-liquid balance. Therefore, the heat exchange efficiency of each heat exchanger can be made substantially uniform, and the heat exchange efficiency as a whole heat exchanger unit can be made good.
  • An air conditioner according to an aspect of the present disclosure is an air conditioner including an indoor unit and an outdoor unit, and at least one of the indoor unit and the outdoor unit includes the heat exchanger unit. is there.
  • the indoor unit includes a housing, a heat exchanger unit disposed in the housing, an air passage configured in the housing, and an outlet of the air passage.
  • the plurality of heat exchangers of the heat exchanger unit may be arranged in parallel along the first direction across the air passage in the air passage.
  • the temperature of the air blown out from the outlet of the indoor unit can be made substantially uniform. Therefore, it is possible to obtain a high-efficiency and high-quality air conditioner that improves heat exchange performance using a fin-stacked heat exchanger with high heat exchange efficiency and has little air temperature unevenness from the air outlet. .
  • the diversion unit and the merging unit are disposed outside one end in the first direction of the plurality of heat exchangers arranged side by side, and each of the plurality of heat exchangers includes:
  • the one pipe and the second pipe may be configured to be disposed within a projection range of the header area onto a plane perpendicular to the direction of the wind flowing through the air path or a plane perpendicular to the first direction.
  • the first pipe connected to the upstream header flow path and the downstream header flow path of the heat exchanger located away from the merge portion and the first pipe Two pipes will cross the air path.
  • the first pipe and the second pipe crossing the air path are located in the header region where at least one of the upstream header flow path and the downstream header flow path of the heat exchanger is provided and not used for heat exchange. .
  • the fall of the heat exchange efficiency by 1st piping and 2nd piping crossing an air path can be suppressed. Therefore, a high-performance air conditioner with high energy saving performance can be obtained by utilizing the high heat exchange efficiency of the heat exchanger.
  • FIG. 1 is a diagram illustrating a schematic configuration of a heat exchanger unit according to Embodiment 1 of the present disclosure.
  • the heat exchanger unit 100 of the present embodiment includes a plurality of heat exchangers 1 (in the present embodiment, two heat exchangers 1a and 1b).
  • the heat exchangers 1a and 1b are juxtaposed in the left-right direction (first direction) in FIG.
  • each of the heat exchangers 1a and 1b includes a first header channel 28, a second header channel 29 disposed downstream of the first header channel, and a first header channel and a second header channel. It has a plurality of refrigerant channels 31 that communicate with the header channel (see FIG. 3).
  • the heat exchangers 1a and 1b have inflow pipes 6a and 6b communicating with the first header channel 28 (see FIG. 3) via the inlet pipes 2a and 2b, respectively. Further, the heat exchangers 1a and 1b have outflow pipes 7a and 7b communicating with the second header flow path 29 (see FIG. 3) via the outlet pipes 3a and 3b, respectively.
  • the inlet pipe 2a and the inflow pipe 6a, and the inlet pipe 2b and the inflow pipe 6b constitute first pipes in the heat exchangers 1a and 1b, respectively.
  • the outlet pipe 3a and the outflow pipe 7a, and the outlet pipe 3b and the outflow pipe 7b constitute a second pipe in the heat exchangers 1a and 1b, respectively.
  • the heat exchanger unit 100 includes a flow divider (a diverter) 4 that diverts the refrigerant to the first pipes 6a and 6b in the heat exchangers 1a and 1b, and a second pipe 7a and the heat exchangers 1a and 1b, respectively. And a merging device (merging portion) 5 for merging the refrigerant from 7b.
  • the heat exchanger unit 100 is configured such that the refrigerant flowing into the heat exchanger unit 100 from the main pipe 70 flows in parallel to the heat exchangers 1a and 1b.
  • the refrigerant circuits of the heat exchangers 1a and 1b are connected in parallel to each other.
  • the refrigerant is branched by the flow divider 4 and flows into the first pipes 6a and 6b, and the refrigerant flowing through the second pipes 7a and 7b is merged. 5 joins.
  • the refrigerant is supplied from the main pipe 70 to the heat exchanger unit 100, flows out of the heat exchanger unit 100, and returns to the main pipe 70.
  • the heat exchangers 1a and 1b are configured to be bilaterally symmetric with respect to the boundary portion, that is, have a mirror image relationship.
  • a flow rate adjusting unit 81 is provided in the first pipe in at least one of the plurality of heat exchangers 1a and 1b. Moreover, the flow volume adjustment part 82 is provided in the 2nd piping in at least any one of several heat exchanger 1a, 1b. That is, the heat exchanger unit 100 is provided with at least one flow rate adjusting unit on each of the upstream side and the downstream side of the heat exchanger 1.
  • both the inflow pipe 6 and the outflow pipe 7 of the heat exchanger with the smaller pressure loss from the flow divider 4 to the merger 5 including the heat exchanger A flow rate adjustment unit 81 and a flow rate adjustment unit 82 are provided.
  • the pressure loss of the right heat exchanger 1b is smaller than the pressure loss of the left heat exchanger 1a. Therefore, in the right heat exchanger 1b, the inflow pipe 6b is provided with the flow rate adjusting unit 81, and the outflow pipe 7b is provided with the flow rate adjusting unit 82.
  • the flow rate adjusting unit 81 is constituted by, for example, a thin pipe having a pipe diameter smaller than the pipe diameter of the inflow pipe 6.
  • the flow rate adjusting unit 82 is configured by, for example, a thin pipe having a pipe diameter smaller than the pipe diameter of the outflow pipe 7.
  • the flow rate adjusting unit 81 is configured such that the pipe pressure losses of the inlet pipes 2a and 2b from the two left and right heat exchangers 1a and 1b to the flow divider 4 are substantially equal.
  • the flow rate adjusting unit 82 is configured such that the pipe pressure losses of the outlet pipes 3a and 3b from the two left and right heat exchangers 1a and 1b to the merger 5 are substantially equal.
  • the flow rate adjustment unit 81 has a pipe diameter larger than the pipe diameter of the inflow pipe 6 so that the pipe pressures of the inlet pipes 2a and 2b from the heat exchangers 1a and 1b to the merger 5 are substantially equal. You may comprise a diameter pipe. Further, the flow rate adjusting unit 82 has a pipe diameter larger than the pipe diameter of the outflow pipe 7 so that the pipe pressure loss of the outlet pipes 3a and 3b from the heat exchangers 1a and 1b to the merger 5 is substantially equal. It may be composed of a large diameter tube. That is, for the first pipe and the second pipe, it is possible to configure the flow rate adjustment unit 81 and the flow rate adjustment unit 82 by making the pipe diameters in some parts different from the pipe diameters in other parts.
  • the flow rate adjustment unit 81 and the flow rate adjustment unit 82 have a pressure loss from the flow divider 4 to the merger 5 including the heat exchangers 1a and 1b among the plurality of heat exchangers 1a and 1b. The case where it was provided only in the smaller heat exchanger was shown. However, the flow rate adjusting unit 81 and the flow rate adjusting unit 82 may be provided in each of the inflow pipes 6a and 6b and the outflow pipes 7a and 7b of the heat exchangers 1a and 1b. That is, the pressure loss may be adjusted for each of the plurality of heat exchangers 1a and 1b.
  • FIG. 2 is an exploded perspective view of the heat exchanger of the heat exchanger unit in FIG. 1 as viewed from below.
  • the heat exchanger 1 (1a, 1b) of the heat exchanger unit 100 is a plate fin stacked heat exchanger.
  • the heat exchanger 1 includes a plate fin laminated body 22 formed by laminating a plurality of plate fins 21, an inlet pipe 2 serving as a refrigerant inlet, and an outlet pipe serving as a refrigerant outlet. 3.
  • the inlet piping 2 and the outlet piping 3 the direction where a refrigerant
  • the case where the heat exchangers 1a and 1b are used as an evaporator will be described as an example. Accordingly, the description will be made by specifying the inlet pipes 2a and 2b as the first pipe and the outlet pipes 3a and 3b as the second pipe.
  • the plate fin 21 has a rectangular plate shape. End plates 23 and 24 are provided on both sides (left side and right side in FIG. 2) of the plate fin stacked body 22 in the stacking direction.
  • the end plates 23 and 24 are constituted by flat plates.
  • the shape of the end plates 23 and 24 in plan view is substantially the same as the shape of the plate fins 21 in plan view shown in FIG.
  • the end plates 23 and 24 are formed of a rigid plate material.
  • the end plates 23 and 24 are formed, for example, by processing a metal material such as aluminum, an aluminum alloy, and stainless steel by grinding.
  • end plates 23 and 24 and the plurality of plate fins 21 are joined and integrated with each other by brazing in a state where these are laminated.
  • each of the end plates 23 and 24 on both sides of the plate fin laminate 22 is connected to the plate fin laminate 22 by connecting means 25 such as bolts and nuts or caulking pin shafts, and It has been fixed.
  • the connecting means 25 connects the end plates 23, 24 to the plate fin laminate 22 at both ends in the longitudinal direction in plan view of the end plates 23, 24. That is, the end plates 23 and 24 on both sides of the plate fin laminate 22 are mechanically connected to and fixed to the plate fin laminate 22 with the plate fin laminate 22 sandwiched therebetween.
  • FIG. 3 is a plan view of plate fins constituting the heat exchanger of the heat exchanger unit in FIG.
  • FIG. 4 is an exploded perspective view showing a part of the plate fin in FIG. 3 in an enlarged manner.
  • the plate fin 21 has a refrigerant flow path 31.
  • the refrigerant flow path 31 includes a plurality of refrigerant flow paths (first refrigerant flow path 31a and second refrigerant flow path 31b) that are arranged in parallel with each other and in which a refrigerant that is a first fluid flows. That is, the refrigerant flow path 31 is composed of a group of first refrigerant flow paths 31a and second refrigerant flow paths 31b.
  • the refrigerant channel 31 is arranged in a substantially U shape. Specifically, in FIG.
  • the refrigerant flows from the left side to the right side inside the first refrigerant channel 31 a and is folded at the right end, and flows inside the second refrigerant channel 31 b from the right side to the left side.
  • the inlet pipe 2 and the outlet pipe 3 connected to this are collectively arranged on one end side in the longitudinal direction of the end plate 23a on one side (right side in FIG. 2) of the plate fin laminate 22.
  • the plate fin 21 has a plurality of heat transfer channels (hereinafter referred to as refrigerant channels 31) arranged in parallel.
  • the refrigerant flow path 31 is connected to an upstream header flow path (first header flow path) 28 and a downstream header flow path (second header flow path) 29.
  • the upstream header flow path 28 and the downstream header flow path 29 connected to the plurality of refrigerant flow paths 31 are collectively arranged on one end side in the longitudinal direction of the plate fin 21.
  • the upstream header channel 28 and the downstream header channel 29 may be separately disposed on both end sides in the longitudinal direction of the plate fin 21.
  • an area where the header flow path is arranged is a header area H, and an area where the refrigerant flow path 31 is arranged is a flow area P.
  • the upstream header channel 28 serves as a refrigerant inlet when the heat exchanger 1 is used as an evaporator, and serves as a refrigerant outlet when the heat exchanger 1 is used as a condenser.
  • the downstream header channel 29 is reversed. That is, the downstream header channel 29 serves as a refrigerant outlet when the heat exchanger 1 is used as an evaporator, and serves as a refrigerant inlet when the heat exchanger 1 is used as a condenser.
  • the plate fin 21 is configured such that a pair of first plate-like member 26a and second plate-like member 26b face each other and are joined to each other by brazing.
  • the plurality of refrigerant flow paths 31 are formed in a substantially U shape as described above.
  • FIG. 5 is a perspective view showing a cross section of the refrigerant flow path portion in the heat exchanger of the heat exchanger unit in FIG.
  • FIG. 6 is a perspective view showing a cross section of the header flow path portion of the heat exchanger in FIG.
  • a large number of plate fins 21 are laminated to constitute a plate fin laminated body 22 that forms the main body of the heat exchanger 1.
  • the plate fin 21 is appropriately provided with a plurality of protrusions 27 (see FIG. 3) between both ends in the longitudinal direction in plan view of the plate fin 21 and between the refrigerant flow paths 31.
  • a gap d (see FIGS. 5 and 6) is formed between the plate fins 21 by the plurality of protrusions 27, and air as the second fluid flows through the gap d.
  • coolant flow path 31 is formed of the concave groove
  • coolant flow path 31 may be comprised by the concave groove provided in at least any one of the 1st plate-shaped member 26a and the 2nd plate-shaped member 26b.
  • the refrigerant flow path 31 includes an upstream header flow path side refrigerant flow path (first refrigerant flow path) 31a connected to the upstream header flow path 28 and a downstream header flow path side refrigerant flow path (second flow path) connected to the downstream header flow path 29. (Refrigerant flow path) 31b.
  • first header flow path 28 and the first refrigerant flow path 31a are communicated with each other via the passage portion 34a, and the second header flow path 29 and the second refrigerant flow path 31b are The communication is made via the passage part 34b.
  • a slit groove 35 (see FIG. 3) is disposed between the first refrigerant channel 31a and the second refrigerant channel 31b. As shown in FIG. 3, the slit groove 35 is a folded portion of the refrigerant flow path 31 from the end (left side in FIG. 3) of the plate fin 21 on the side where the upstream header flow path 28 and the downstream header flow path 29 are disposed. It is formed over the vicinity. The slit groove 35 can prevent direct heat transfer between the first refrigerant flow path 31a and the second refrigerant flow path 31b.
  • the number of the second refrigerant flow paths 31b is larger than the number of the first refrigerant flow paths 31a.
  • the non-hole part 36 is arrange
  • the refrigerant that is the first fluid flows into the heat exchangers 1a and 1b from the inlet pipes 2a and 2b provided on the inlet side (upstream side) of the heat exchangers 1a and 1b.
  • the refrigerant flows into the first refrigerant flow path 31 a provided in each of the plurality of plate fins 21 constituting the plate fin stacked body 22 via the upstream header flow path 28.
  • the refrigerant flows in the plurality of first refrigerant flow paths 31a in parallel in the longitudinal direction, makes a U-turn, and then flows in the plurality of second refrigerant flow paths 31b in parallel in the longitudinal direction. Thereafter, the refrigerant flows out through the outlet pipes 3a and 3b provided on the outlet side (downstream side) of the heat exchangers 1a and 1b via the downstream header channel 29.
  • the air (second fluid) that exchanges heat with the refrigerant (first fluid) passes through a gap d (see FIGS. 5 and 6) formed between the plate fins 21 constituting the plate fin laminate 22. . Thereby, heat exchange is performed between the refrigerant that is the first fluid and the air that is the second fluid.
  • the heat exchangers 1a and 1b perform heat exchange between the refrigerant and the air. Further, the refrigerant is divided by the flow divider 4 on the inlet side (upstream side) of the heat exchanger 1 and is supplied into the heat exchangers 1a and 1b from the two inlet pipes 2a and 2b, respectively. And the refrigerant
  • the refrigerant is distributed to each heat exchanger.
  • the flow rate of the refrigerant flowing into each heat exchanger is uniform.
  • the flow rate adjusting unit is provided only on the inlet piping side, that is, on the upstream side of the heat exchanger, and the pressure is adjusted.
  • coolant which flows in into inlet piping is a difference in the piping pressure of an outlet piping side (downstream side), respectively. Affected by. Therefore, the dryness of the refrigerant flowing into each heat exchanger is different for each heat exchanger. Therefore, it cannot be divided so that the flow rate of the refrigerant flowing into each heat exchanger becomes equal. That is, the equalization degree at the time of branching of the inflowing refrigerant becomes low, and the flow is not evenly split to each heat exchanger.
  • the flow rate adjusting unit 82 is provided not only on the upstream side of the heat exchangers 1a and 1b but also on the outlet pipes 3a and 3b (downstream side). That is, the pressure is adjusted on both the inlet side and the outlet side of the heat exchangers 1a and 1b.
  • the pressure loss on the inlet side of the heat exchangers 1a and 1b can be made equal, and the pressure loss on the outlet side of the heat exchangers 1a and 1b can be made equivalent. Therefore, the state of each refrigerant at the inlets of the heat exchangers 1a and 1b, that is, the dryness of the refrigerant can be made equal.
  • coolant can be equally shunted with respect to several heat exchanger 1a, 1b. That is, it is possible to greatly improve the equalization rate of the refrigerant diversion and to divert the refrigerant so that it can flow evenly into the heat exchangers 1a and 1b.
  • the plate fin laminated heat exchanger exemplified in the present embodiment has a large number of first refrigerant channels 31a and second refrigerant channels 31b that connect the upstream header channel 28 and the downstream header channel 29 (the number of passes is). Many). Therefore, the pressure loss in the entire refrigerant flow path 31, that is, the internal pressure loss as a heat exchanger is as low as about one-tenth of the internal pressure loss of the fin tube heat exchanger. Accordingly, even when the pressure on the inlet pipes 2a and 2b (upstream side) is adjusted, the dryness of the refrigerant flowing in from the inlet pipes 2a and 2b is determined on the outlet pipes 3a and 3b side (downstream side). Under the influence of the difference in piping pressure, the heat exchangers 1a and 1b are different. Therefore, the refrigerant cannot be evenly divided into the plurality of heat exchangers 1a and 1b.
  • the flow rate adjusting unit 82 is also provided on the outlet pipes 3a, 3b side (downstream side).
  • the pressure can be adjusted on both the inlet side and the outlet side of the refrigerant, the pressure loss on the inlet side of the heat exchangers 1a and 1b can be made equal, and the pressure loss on the outlet side can be made equivalent.
  • coolant which flows into heat exchanger 1a, 1b can be made equivalent, a refrigerant
  • each heat exchanger 1a , 1b the degree of equalization of the flow of the refrigerant flowing in can be increased, and the heat exchange performance of the entire heat exchanger unit can be improved.
  • the plate fin laminated heat exchanger is used as the heat exchangers 1a and 1b, thereby reducing the diameter of the refrigerant flow path 31 between the upstream header flow path 28 and the downstream header flow path 29.
  • the heat exchange efficiency in the heat exchangers 1a and 1b can be improved.
  • the heat exchanger unit 100 of this Embodiment can distribute a refrigerant
  • the heat exchange unit 100 provided with the heat exchanger 1a and the heat exchanger 1b, Comprising: It connects with the main piping 70 which supplies a refrigerant
  • the second pipe 7b, the second pipe 7a, the second pipe 7b, and the main pipe 70 connected to the main pipe 70, and the merger 5 that supplies the refrigerant supplied from the second pipe 7a and the second pipe 2b to the main pipe 70.
  • the first pipe 6a supplies the refrigerant divided by the flow divider 4 to the heat exchanger 1a
  • the first pipe 6b supplies the refrigerant divided by the flow divider 4 to the heat exchanger 1b.
  • the heat exchanger 1a has a first header channel 28a and a second header channel 29a
  • the heat exchanger 1b has a first header channel 28a and a second header channel 29b.
  • the first pipe 6a is connected to the first header flow path 28a
  • the first pipe 6b is connected to the first header flow path 28b
  • the second pipe 7a is connected to the second header flow path 29a
  • the second The pipe 7b is connected to the second header channel 29b.
  • the first flow rate adjusting unit 81 is disposed on at least one of the first pipe 6a and the first pipe 6b
  • the second flow rate adjusting unit 82 is disposed on at least one of the second pipe 7a and the second pipe 7b.
  • Each of the first flow rate adjustment unit 81 and the second flow rate adjustment unit 82 adjusts the flow rate of the refrigerant flowing through the pipe.
  • the first flow rate adjustment unit 81 and the second flow rate adjustment unit 82 are adjusted so that the pressure loss on the inlet side and the pressure loss on the outlet side of each heat exchanger 1a, 1b are equal, the dryness of the refrigerant And it can distribute with respect to each heat exchanger 1a, 1b by equalizing the amount of circulation. Accordingly, it is possible to increase the degree of equalization of the refrigerant branch flow between the heat exchangers 1a and 1b. Therefore, it is possible to equalize the heat exchange efficiency by ensuring an even flow of the refrigerant to each of the heat exchangers 1a and 1b, thereby improving the heat exchange performance of the heat exchanger unit 100 as a whole.
  • FIG. 7 is a diagram illustrating a schematic configuration of a heat exchanger unit according to the second embodiment of the present disclosure.
  • FIG. 8 is a diagram showing a schematic configuration of a portion indicated by a in FIG.
  • the heat exchanger unit 110 is provided with a branch pipe 9 in the upstream portion of the inlet pipes 2a and 2b of the heat exchangers 1a and 1b. It is the structure which branches the refrigerant
  • a throttle pipe 10 is provided on the inlet side (upstream side) of the branch pipe 9.
  • a branch pipe 9 is provided at a branching portion for branching the refrigerant to the first pipes 6 a and 6 b in each of the plurality of heat exchangers 1 a and 1 b.
  • a Y branch pipe branched into two is used as the branch pipe 9.
  • a throttle tube 10 having a diameter smaller than the diameter of the inlet tube 9 a at the inlet of the branch tube 9 is provided on the inlet side (upstream side) of the branch tube 9.
  • the refrigerant flowing from the inlet pipe 9a of the branch pipe 9 is throttled by the throttle pipe 10 located on the upstream side thereof, the flow velocity is increased, and an annular flow is formed. Therefore, the refrigerant can be evenly divided in the branch pipe 9 (Y branch pipe). Therefore, it is possible to supply the refrigerant having substantially the same gas-liquid balance to the heat exchangers 1a and 1b. Therefore, the heat exchange efficiency of the heat exchangers 1a and 1b can be made substantially uniform, and the heat exchange efficiency of the heat exchanger unit 110 as a whole can be made good.
  • the branch pipe 9 as a Y branch pipe
  • the refrigerant is less susceptible to the influence of gravity during the diversion. Therefore, the refrigerant can be supplied to the heat exchangers 1a and 1b without destroying the gas-liquid separation ratio of the refrigerant that has been throttled by the throttle pipe 10 and divided by the branch pipe 9.
  • the heat exchange efficiency of each heat exchanger 1a, 1b can be improved more reliably, and the heat exchange efficiency as the heat exchanger unit 110 whole can be made favorable.
  • a distributor may be provided on the upstream side of the first pipes 6a and 6b instead of the combination of the branch pipe (Y branch pipe) 9 and the throttle pipe 10 described above.
  • the distributor By providing the distributor, the refrigerant can be distributed almost uniformly to each of the plurality of heat exchangers 1a and 1b connected in parallel. Therefore, the heat exchange efficiency of the heat exchanger unit 110 as a whole can be improved.
  • FIG. 9 is a refrigeration cycle diagram of the air conditioner according to the third embodiment.
  • the air conditioner 200 of the present embodiment is configured using any one of the heat exchanger units shown in the first and second embodiments.
  • the air conditioner 200 includes an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51.
  • the outdoor unit 51 includes a compressor 53 that compresses refrigerant, a four-way valve 54 that switches a refrigerant circuit by cooling operation and heating operation, an outdoor heat exchanger 55 that performs heat exchange between the refrigerant and the outside air, and refrigerant.
  • a decompressor 56 for reducing the pressure and an outdoor blower 59 are provided.
  • the indoor unit 52 is provided with an indoor heat exchanger 57 that performs heat exchange between the refrigerant and the indoor air, and an indoor blower 58.
  • the compressor 53, the four-way valve 54, the indoor heat exchanger 57, the decompressor 56, and the outdoor heat exchanger 55 are connected to form a refrigerant circuit through which the refrigerant flows, thereby forming a heat pump refrigeration cycle. .
  • FIG. 10 is a diagram illustrating a cross-sectional configuration when the indoor unit of the air conditioner according to Embodiment 3 is viewed from the right side.
  • FIG. 11 is a figure which shows the cross-sectional structure when the indoor unit in Embodiment 3 is seen from the upper side.
  • the indoor heat exchanger 57 includes a housing 64, a heat exchanger unit 60 disposed in the housing 64, and a heat exchange air passage (air channel) configured in the housing 64. 62).
  • the heat exchanger unit 60 any one of the heat exchanger units 100 and 110 shown in the first and second embodiments is used.
  • An outlet 61 is disposed at the outlet of the air passage 62.
  • a suction port 63 is disposed at the entrance of the air passage.
  • the indoor heat exchanger 57 constituting the heat exchanger unit 60 is arranged in the air passage 62. Further, as shown in FIG. 11, the indoor heat exchanger 57 is configured such that the heat exchangers 1 a and 1 b are arranged in parallel along the first direction crossing the air passage 62. In the present embodiment, the indoor heat exchanger 57 is arranged in the full width of the air passage 62. Specifically, the heat exchangers 1 a and 1 b are arranged side by side in the left-right direction in FIG. 11 so as to face one air outlet 61 in a plan view of the indoor unit 52.
  • tetrafluoropropene or trifluoropropene and difluoromethane, pentafluoroethane, or tetrafluoroethane may be used alone or as a mixture of two or three components.
  • the four-way valve 54 is switched so that the discharge side of the compressor 53 and the outdoor heat exchanger 55 communicate with each other.
  • the refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant and is sent to the outdoor heat exchanger 55 through the four-way valve 54.
  • the refrigerant exchanges heat with the outside air to dissipate heat and condense into a high-pressure liquid refrigerant and is sent to the decompressor 56.
  • the refrigerant is decompressed by the decompressor 56 to become a low-temperature and low-pressure two-phase refrigerant and sent to the indoor unit 52.
  • the refrigerant flows into the indoor heat exchanger 57.
  • the refrigerant exchanges heat with room air, thereby absorbing heat and evaporating to become a low-temperature gas refrigerant. At this time, the indoor air is cooled by exchanging heat with the refrigerant to cool the room.
  • the refrigerant flowing out of the indoor heat exchanger 57 returns to the outdoor unit 51 and returns to the compressor 53 via the four-way valve 54.
  • the four-way valve 54 is switched so that the discharge side of the compressor 53 and the indoor unit 52 communicate with each other.
  • the refrigerant compressed by the compressor 53 is sent to the indoor unit 52 through the four-way valve 54 as a high-temperature and high-pressure refrigerant.
  • the high-temperature and high-pressure refrigerant enters the indoor heat exchanger 57 and dissipates heat and cools by exchanging heat with indoor air.
  • the refrigerant condenses and becomes a high-pressure liquid refrigerant.
  • the room air is heated by exchanging heat with the refrigerant to heat the room.
  • the refrigerant is sent to the decompressor 56, decompressed by the decompressor 56, becomes a low-temperature and low-pressure two-phase refrigerant, and is sent to the outdoor heat exchanger 55.
  • the refrigerant exchanges heat with the outside air to evaporate and returns to the compressor 53 via the four-way valve 54.
  • the air conditioner 200 of the present embodiment is equalized in the heat exchanger unit 60 constituting the indoor unit without variation in the heat exchange efficiency of the heat exchangers 1a and 1b. Therefore, the temperature of the cold air or hot air blown out from the air outlet 61 can be made substantially uniform in the width direction of the air outlet. For this reason, even if a fin laminated heat exchanger is used as the heat exchangers 1a and 1b, the temperature unevenness of the blown air is reduced, and the air conditioner 200 with high reliability and high quality is provided. Can be obtained.
  • heat exchangers 1a and 1b by using a fin-stacked heat exchanger as the heat exchangers 1a and 1b, it is possible to reduce the diameter of the refrigerant flow path 31 and increase the number of passes of the refrigerant flow path 31. Thereby, the heat exchange efficiency of heat exchanger 1a, 1b can be improved, and the high performance air conditioner 200 with high energy-saving property can be obtained.
  • any one of the heat exchanger units 100 and 110 shown in the first and second embodiments is used for the indoor unit 52 is shown.
  • the outdoor unit 51 and the indoor unit 52 are used.
  • the structure used for at least one of these may be sufficient.
  • heat exchange efficiency can be improved and the energy-saving property of the air conditioner 200 can be improved.
  • FIG. 12 is a diagram illustrating an arrangement configuration of the heat exchanger of the air conditioner according to the third embodiment.
  • a plurality of heat exchangers 1a and 1b are disposed in an inclined state in the housing 64 of the indoor unit 52 as shown in FIG. explain.
  • one of the heat exchangers 1 has an inlet pipe 2 (first pipe 6) connected to the upstream header flow path 28 and an outlet pipe 3 (first pipe connected to the downstream header flow path 29).
  • the two pipes 7) are arranged as shown in FIG.
  • the first pipe 6 and the second pipe 7 of one heat exchanger 1 of the heat exchanger 1 (1a, 1b) are arranged by the upstream header channel 28 and the downstream header channel 29 of the heat exchanger 1.
  • the header area H is arranged in a projection range W projected on a plane perpendicular to a direction substantially parallel to the air flow B (see FIGS. 10 and 12).
  • the first pipe 6 and the second pipe 7 of one heat exchanger 1 of the heat exchanger 1 (1a, 1b) are arranged with the upstream header channel 28 and the downstream header channel 29 of the heat exchanger 1.
  • the header area H may be disposed within a projection range W projected onto a plane that is vertical and parallel to the first direction.
  • the flow dividing section that diverts the refrigerant to the first pipe 6a and the first pipe 6b on either the left or right side
  • a merging portion (merger 5) for merging refrigerant from the second pipe 7a and the second pipe 7b is provided (the diverter 4 or the branch pipe 9)
  • the diverting portion and the merging portion are
  • the first pipe 6 and the second pipe 7 of the heat exchanger 1 that are located away from the provided side extend along a direction (first direction) in which the heat exchangers 1a and 1b are arranged in parallel. Will be established. Therefore, the first pipe 6 and the second pipe 7 are disposed within the projection range W described above in the header region H in which at least one of the upstream header flow path 28 and the downstream header flow path 29 is provided.
  • the flow dividing portion (the flow divider 4 or the branch pipe) for dividing the refrigerant into the first pipe 6a and the first pipe 6b 9), and the first pipe 6 of the heat exchanger 1 that is located away from the side on which the merge section (the merger 5) that merges the refrigerant from the second pipe 7a and the second pipe 7b is provided, and
  • the second pipe 7 crosses the air path 62.
  • the first pipe 6 and the second pipe 7 are provided with the upstream header flow path 28 and the downstream header flow path 29 of the heat exchangers 1a and 1b and are not used for heat exchange. It is located in the wake range of the region H (behind the header region H). Accordingly, it is possible to minimize a decrease in heat exchange efficiency caused by the first pipe 6 and the second pipe 7 crossing the air passage 62 (ventilation obstruction).
  • the 1st piping 6 and the 2nd piping 7 which cross the air path 62 should just be piping within the said projection range W of the header area
  • the arrangement positions of the first pipe 6 and the second pipe 7 are set within the projection plane range W of the header region H in which both the upstream header channel 28 and the downstream header channel 29 are provided. did. However, when the upstream header flow path 28 and the downstream header flow path 29 are provided separately at both ends of the plate fin 21, the upstream header flow path 28 and the downstream header flow path 29 may be within the projection plane range W of the header area H where either one is provided. That's fine.
  • the present disclosure provides a heat exchanger unit that equalizes the heat exchange efficiency of each of a plurality of heat exchangers connected in parallel and exhibits good heat exchange performance, and a high-performance air conditioner that uses the same and has high energy efficiency.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

Une unité d'échangeur de chaleur (100) comprend une pluralité d'échangeurs de chaleur (1), chacun de la pluralité d'échangeurs de chaleur (1) ayant une première tuyauterie (6) dans lesquelles s'écoule un fluide frigorigène, un premier chemin d'écoulement de collecteur communiquant avec le côté de sortie de la première tuyauterie (6), un second chemin d'écoulement de collecteur agencé en aval du premier chemin d'écoulement de collecteur, une pluralité de chemins d'écoulement de fluide frigorigène permettant au premier chemin d'écoulement de collecteur et au second chemin d'écoulement de collecteur de communiquer l'un avec l'autre, et une seconde tuyauterie (7) communiquant avec le côté de sortie du second chemin d'écoulement de collecteur. De plus, l'unité d'échangeur de chaleur (100) comprend une première unité de réglage de débit (81) disposée sur la première tuyauterie (6) d'au moins l'un de la pluralité d'échangeurs de chaleur (1), et une seconde unité de réglage de débit (82) disposée sur la seconde tuyauterie (7) d'au moins l'un de la pluralité d'échangeurs de chaleur (1).
PCT/JP2019/007174 2018-03-02 2019-02-26 Unité d'échangeur de chaleur et climatiseur l'utilisant WO2019167909A1 (fr)

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WO2021191952A1 (fr) * 2020-03-23 2021-09-30 三菱電機株式会社 Unité intérieure et climatiseur
KR102620053B1 (ko) * 2021-06-24 2024-01-02 한국원자력연구원 열교환기 및 이를 구비하는 원전
JP7392757B2 (ja) * 2022-03-30 2023-12-06 株式会社富士通ゼネラル 空気調和機の室内機

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CN111801538A (zh) 2020-10-20
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JP2019152367A (ja) 2019-09-12
EP3760949A1 (fr) 2021-01-06

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