WO2023199466A1 - Échangeur de chaleur et dispositif de climatisation l'incluant - Google Patents

Échangeur de chaleur et dispositif de climatisation l'incluant Download PDF

Info

Publication number
WO2023199466A1
WO2023199466A1 PCT/JP2022/017797 JP2022017797W WO2023199466A1 WO 2023199466 A1 WO2023199466 A1 WO 2023199466A1 JP 2022017797 W JP2022017797 W JP 2022017797W WO 2023199466 A1 WO2023199466 A1 WO 2023199466A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
header
refrigerant
space
gas separation
Prior art date
Application number
PCT/JP2022/017797
Other languages
English (en)
Japanese (ja)
Inventor
理人 足立
洋次 尾中
七海 岸田
哲二 七種
祐基 中尾
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/017797 priority Critical patent/WO2023199466A1/fr
Publication of WO2023199466A1 publication Critical patent/WO2023199466A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • the present disclosure relates to a heat exchanger including a plurality of heat transfer tubes and an air conditioner including the same.
  • refrigerant distribution is performed in which refrigerant in a gas-liquid two-phase state is passed through a header section that is a refrigerant distributor.
  • the distribution characteristics of the flow rate of liquid refrigerant to each heat exchanger tube differ depending on the structure of the header section, and affect heat exchange performance. For example, if the header section extends horizontally and a plurality of heat transfer tubes extend vertically, when the refrigerant flows inside the header section, the dryness, which is the mass ratio of gas refrigerant to liquid phase refrigerant, and the flow inside the header.
  • the distribution characteristics of the refrigerant vary greatly depending on the flow rate of the refrigerant.
  • a heat exchanger is known in which a gas-liquid separator is installed on the upstream side of the header in the refrigerant flow direction in order to reduce the dryness of the refrigerant at the refrigerant inlet of the header (for example, see Patent Document 1) .
  • the present disclosure has been made to solve the above-mentioned problems, and provides a heat exchanger that improves refrigerant distribution characteristics to a plurality of heat transfer tubes without the need for a new refrigerant auxiliary device, and an air conditioner equipped with the same. It provides a harmonization device.
  • a heat exchanger is a heat exchanger that exchanges heat between air and a refrigerant, and includes a plurality of heat exchangers each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction.
  • the first header has a partition wall that separates the inside of the first header into a plurality of spaces including a mainstream space and a gas separation space, and the main flow space and the gas separation space are separated from each other.
  • a plurality of first openings are provided in the partition wall to communicate with each other, the gas separation space is arranged above the mainstream space, and the gas separation space and the refrigerant pipe are connected by the gas separation pipe.
  • An air conditioner according to the present disclosure includes the heat exchanger described above, a blower that supplies the air to the heat exchanger, and a casing that houses the heat exchanger and the blower.
  • the first header is provided with a gas separation space that separates a gas refrigerant from a gas-liquid two-phase refrigerant.
  • the gas refrigerant is separated from the mainstream space into the gas separation space, and the proportion of the gas refrigerant in the mainstream space is reduced. Therefore, in the mainstream space, the ratio of liquid refrigerant to the gas-liquid two-phase refrigerant becomes high, and the refrigerant distribution from the mainstream space to the plurality of heat transfer tubes can be made more uniform. As a result, the refrigerant distribution characteristics can be improved without providing a new refrigerant auxiliary device.
  • FIG. 2 is a refrigerant circuit diagram of the air conditioner according to the first embodiment.
  • FIG. 2 is a refrigerant circuit diagram showing the flow of refrigerant when the air conditioner according to the first embodiment performs cooling operation.
  • FIG. 2 is a plan view showing an example of a configuration of a heat source side heat exchanger housed in a heat source side unit of the air conditioner according to the first embodiment.
  • 7 is a plan view showing another configuration example of the heat source side heat exchanger housed in the heat source side unit of the air conditioner according to Embodiment 1.
  • FIG. 7 is a plan view showing another configuration example of the heat source side heat exchanger housed in the heat source side unit of the air conditioner according to Embodiment 1.
  • FIG. 3 is a plan view showing a configuration example of a heat source side heat exchanger housed in another heat source side unit of the air conditioner according to the first embodiment.
  • FIG. 3 is a plan view showing another configuration example of a heat source side heat exchanger housed in another heat source side unit of the air conditioner according to the first embodiment.
  • FIG. 3 is a plan view showing another configuration example of a heat source side heat exchanger housed in another heat source side unit of the air conditioner according to the first embodiment.
  • FIG. 2 is a side view for explaining the configuration of the heat source side heat exchanger according to Embodiment 1.
  • FIG. FIG. 10 is a side view showing a configuration example when the heat source side heat exchanger shown in FIG. 9 is provided with radiation fins.
  • FIG. 9 is a schematic cross-sectional view showing the structure taken along line AA in FIG. 9.
  • FIG. 12 is a schematic diagram showing an example of the internal configuration of the first header shown in FIG. 11.
  • FIG. 7 is a schematic diagram illustrating an example of the internal configuration of a first header of Modification 1.
  • FIG. 12 is a schematic diagram showing an example of the internal configuration of a first header of Modification 2.
  • FIG. 12 is a schematic diagram showing an example of the internal configuration of a first header in Modification 3.
  • FIG. 12 is a schematic diagram showing an example of the internal configuration of a first header of Modification 4.
  • FIG. FIG. 7 is a schematic cross-sectional view showing an example of the internal configuration of a first header of a heat source side heat exchanger according to a second embodiment.
  • FIG. 7 is a side view for explaining the configuration of a heat source side heat exchanger according to Embodiment 3;
  • FIG. 7 is a side view for explaining the configuration of a heat source side heat exchanger according to Embodiment 4.
  • FIG. 7 is a side view for explaining the configuration of a heat source side heat exchanger according to Embodiment 5.
  • FIG. 7 is a side view for explaining the configuration of a heat source side heat exchanger according to a sixth embodiment.
  • FIG. 22 is a side view of the heat source side heat exchanger shown in FIG. 21 when viewed from another direction.
  • FIG. 7 is a refrigerant circuit diagram of an air conditioner having a heat source side heat exchanger according to a seventh embodiment.
  • FIG. 7 is a side view for explaining the configuration of a heat source side heat exchanger according to Embodiment 7.
  • arrows of three orthogonal axes (X-axis, Y-axis, and Z-axis) that define directions are shown in the drawings.
  • the X-axis arrow indicates the width direction
  • the Y-axis arrow indicates the depth direction.
  • the opposite direction of the Z-axis arrow indicates the vertical direction (direction of gravity).
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner according to Embodiment 1.
  • the air conditioner 10 includes a heat source side heat exchanger 1, a load side heat exchanger 2, a compressor 3, a throttle device 4, and a four-way valve 5.
  • the compressor 3, the heat source side heat exchanger 1, the expansion device 4, and the load side heat exchanger 2 are connected by a refrigerant pipe 6, and a refrigerant circuit 20 in which refrigerant circulates is configured.
  • a gas separation pipe 9 is connected to the heat source side heat exchanger 1 .
  • the throttle device 4 is, for example, an expansion valve.
  • the air conditioner 10 also includes a heat source side blower 7 and a load side blower 8.
  • the heat source side blower 7 sucks outside air and supplies the sucked outside air to the heat source side heat exchanger 1.
  • the load-side blower 8 sucks air from inside the target space and supplies the sucked air to the load-side heat exchanger 2.
  • the liquid refrigerant flowing out of the load-side heat exchanger 2 is expanded and depressurized by the expansion device 4, and becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant flows into the heat source side heat exchanger 1 .
  • the gas-liquid two-phase refrigerant that has flowed into the heat source side heat exchanger 1 absorbs heat and evaporates by exchanging heat with the outside air supplied by the heat source side blower 7, and becomes a low-temperature, low-pressure gas refrigerant.
  • the low temperature and low pressure gas refrigerant flows out from the heat source side heat exchanger 1.
  • the low-temperature, low-pressure gas refrigerant is sucked into the compressor 3 again, and when compressed by the compressor 3, it becomes a high-temperature, high-pressure gas refrigerant and is discharged from the compressor 3. In this way, the refrigerant is repeatedly circulated.
  • FIG. 2 is a refrigerant circuit diagram showing the flow of refrigerant when the air conditioner according to the first embodiment performs cooling operation.
  • the arrows shown in FIG. 2 indicate the direction of flow of the refrigerant.
  • the liquid refrigerant flowing out from the heat source side heat exchanger 1 is expanded and depressurized by the expansion device 4, and becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant flows into the load-side heat exchanger 2 .
  • the gas-liquid two-phase refrigerant that has flowed into the load-side heat exchanger 2 exchanges heat with the indoor air supplied by the load-side blower 8, absorbs heat, and evaporates, becoming a low-temperature, low-pressure gas refrigerant.
  • the low-temperature, low-pressure gas refrigerant flows out from the load-side heat exchanger 2.
  • the low-temperature, low-pressure gas refrigerant is sucked into the compressor 3 again, and when compressed by the compressor 3, it becomes a high-temperature, high-pressure gas refrigerant and is discharged from the compressor 3. In this way, the refrigerant is repeatedly circulated.
  • the low-temperature, low-pressure gas refrigerant When the low-temperature, low-pressure gas refrigerant is sucked by the compressor 3 and compressed by the compressor 3, it becomes a high-temperature, high-pressure gas refrigerant.
  • the high temperature and high pressure gas refrigerant When the high temperature and high pressure gas refrigerant is discharged from the compressor 3, it flows through the four-way valve 5 and then flows into the heat source side heat exchanger 1.
  • the high-temperature, high-pressure gas refrigerant that has flowed into the heat source side heat exchanger 1 radiates heat and condenses by exchanging heat with the outside air supplied by the heat source side blower 7 and the frost attached to the outer surface of the heat source side heat exchanger 1.
  • the refrigerant becomes a high-temperature, high-pressure liquid refrigerant and flows out of the heat source side heat exchanger 1.
  • the liquid refrigerant flowing out from the heat source side heat exchanger 1 is expanded and depressurized by the expansion device 4, and becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant flows into the load-side heat exchanger 2 .
  • the gas-liquid two-phase refrigerant that has flowed into the load-side heat exchanger 2 exchanges heat with the indoor air supplied by the load-side blower 8, absorbs heat, and evaporates, becoming a low-temperature, low-pressure gas refrigerant.
  • the low-temperature, low-pressure gas refrigerant flows out from the load-side heat exchanger 2.
  • the low-temperature, low-pressure gas refrigerant is sucked into the compressor 3 again, and when compressed by the compressor 3, it becomes a high-temperature, high-pressure gas refrigerant and is discharged from the compressor 3. In this way, the refrigerant is repeatedly circulated.
  • the respective numbers of the heat source side heat exchangers 1 and the load side heat exchangers 2 are not limited to the numbers shown in FIGS. 1 and 2.
  • the number of heat source side heat exchangers 1 and load side heat exchangers 2 is determined depending on the environment in which the air conditioner 10 is installed or the size of the target space to be air conditioned by the air conditioner 10. It's okay.
  • FIG. 3 is a plan view showing a configuration example of a heat source side heat exchanger housed in a heat source side unit of the air conditioner according to the first embodiment.
  • FIG. 3 is a top plan view of the casing 25 of the heat source unit that houses the heat source heat exchanger 1 and the heat source blower 7.
  • the casing 25 is a top flow type casing that sucks air from the four sides of the casing 25 and blows it out in the opposite direction in the vertical direction when the propeller of the heat source side blower 7 rotates.
  • the planar shape of the housing 25 is rectangular.
  • arrow Dar indicates the direction in which air flows
  • Drf indicates the direction in which refrigerant flows.
  • the heat source side heat exchanger 1 shown in FIG. 3 includes a first heat exchanger 35a and a second heat exchanger 35b. As shown in FIG. 3, the heat source side blower 7 is arranged at the center of the casing 25, and the first heat exchanger 35a and the second heat exchanger 35b are arranged along the sides of the casing 25. Each of the first heat exchanger 35a and the second heat exchanger 35b has a bent region 110 bent in an L-shape along a corner where two side surfaces of the housing 25 touch. have
  • FIG. 4 is a plan view showing another configuration example of the heat source side heat exchanger housed in the heat source side unit of the air conditioner according to the first embodiment.
  • arrow Dar indicates the direction in which air flows
  • arrow Drf indicates the direction in which refrigerant flows.
  • the heat source side heat exchanger 1 shown in FIG. 4 includes a first heat exchanger 36a and a second heat exchanger 36b. Each of the first heat exchanger 36a and the second heat exchanger 36b has multiple rows of heat exchangers arranged in the direction of air flow.
  • the first heat exchanger 36a connects the first row heat exchanger 131a, the second row heat exchanger 132a, and the first row heat exchanger 131a and the second row heat exchanger 132a. It has a connecting pipe 27a.
  • the first row of heat exchangers 131a is arranged on the windward side, and the second row of heat exchangers 132a is arranged on the leeward side.
  • Each of the first row of heat exchangers 131a and the second row of heat exchangers 132a has a bent region 110 bent into an L-shape along the corner of the housing 25.
  • the second heat exchanger 36b connects the first row heat exchanger 131b, the second row heat exchanger 132b, and the first row heat exchanger 131b and the second row heat exchanger 132b. It has a connecting pipe 27b.
  • the first row of heat exchangers 131b is arranged on the windward side, and the second row of heat exchangers 132b is arranged on the leeward side.
  • Each of the first row of heat exchangers 131b and the second row of heat exchangers 132b has a bent region 110 bent into an L-shape along the corner of the housing 25.
  • FIG. 5 is a plan view showing another configuration example of the heat source side heat exchanger housed in the heat source side unit of the air conditioner according to the first embodiment.
  • arrow Dar indicates the direction in which air flows
  • arrow Drf indicates the direction in which refrigerant flows.
  • the heat source side heat exchanger 1 shown in FIG. 5 includes a first heat exchanger 37a and a second heat exchanger 37b.
  • Each of the first heat exchanger 37a and the second heat exchanger 37b has a plurality of rows of heat exchangers arranged in the direction in which air flows.
  • the first heat exchanger 37a has a first row of heat exchangers 131a and a second row of heat exchangers 132a, but does not have the connection pipe 27a shown in FIG. 4.
  • the first row of heat exchangers 131a is arranged on the windward side
  • the second row of heat exchangers 132a is arranged on the leeward side.
  • Each of the first row of heat exchangers 131a and the second row of heat exchangers 132a has a bent region 110 bent into an L-shape along the corner of the housing 25.
  • the second heat exchanger 36b has the first row of heat exchangers 131b and the second row of heat exchangers 132b, but does not have the connection pipe 27b shown in FIG. 4.
  • the first row of heat exchangers 131b is arranged on the windward side
  • the second row of heat exchangers 132b is arranged on the leeward side.
  • Each of the first row of heat exchangers 131b and the second row of heat exchangers 132b has a bent region 110 bent into an L-shape along the corner of the housing 25.
  • FIGS. 4 and 5 show a case where a plurality of heat exchangers are arranged in the air flow direction in the casing 25 of the heat source side unit.
  • FIG. 6 is a plan view showing a configuration example of a heat source side heat exchanger housed in another heat source side unit of the air conditioner according to the first embodiment.
  • FIG. 6 is a plan view of the casing 26 of the heat source unit that houses the compressor 3, the heat source heat exchanger 1, and the heat source blower 7, viewed from above.
  • the housing 26 is a side flow type housing that sucks air from two of the four sides of the housing 25 and blows the sucked air out from one side when the propeller of the heat source side blower 7 rotates. be.
  • the planar shape of the housing 26 is rectangular.
  • arrow Dar indicates the direction in which air flows
  • Drf indicates the direction in which refrigerant flows.
  • the heat source side blower 7 is arranged along one side of the four sides of the casing 26, and the heat source side heat exchanger 1 is arranged along two sides of the casing 26. ing.
  • the heat source side heat exchanger 1 has a bent region 110 bent into an L-shape along the corner of the housing 26 .
  • FIG. 7 is a plan view showing another configuration example of the heat source side heat exchanger housed in another heat source side unit of the air conditioner according to the first embodiment.
  • arrow Dar indicates the direction in which air flows
  • arrow Drf indicates the direction in which refrigerant flows.
  • the heat source side heat exchanger 1 shown in FIG. It has a connecting pipe 28 that connects to the container 37b.
  • the first heat exchanger 37a is arranged on the windward side
  • the second heat exchanger 37b is arranged on the leeward side.
  • Each of the first heat exchanger 37a and the second heat exchanger 37b has a bent region 110 bent into an L-shape along the corner of the housing 26.
  • FIG. 8 is a plan view showing another configuration example of the heat source side heat exchanger housed in another heat source side unit of the air conditioner according to the first embodiment.
  • arrow Dar indicates the direction in which air flows
  • arrow Drf indicates the direction in which refrigerant flows.
  • the heat source side heat exchanger 1 shown in FIG. 8 has a first heat exchanger 37a and a second heat exchanger 37b arranged in the direction in which air flows, but the connection piping 28 shown in FIG. does not have.
  • the first heat exchanger 37a is arranged on the windward side
  • the second heat exchanger 37b is arranged on the leeward side.
  • Each of the first heat exchanger 37a and the second heat exchanger 37b has a bent region 110 bent into an L-shape along the corner of the housing 26.
  • FIGS. 7 and 8 show a case where a plurality of heat exchangers are arranged in the air flow direction in the casing 26 of the heat source side unit.
  • FIGS. 3 to 8 a configuration example of the heat source side heat exchanger 1 having the bent regions 110 bent in an L-shape with the horizontal direction as a reference has been described, but the number of bent regions 110 formed is
  • the present invention is not limited to the cases shown in FIGS. 3 to 8.
  • the bending regions 110 may be provided at two or more locations in the heat source side heat exchanger 1.
  • the bending region 110 may not be provided in the heat source side heat exchanger 1.
  • FIG. 3 shows a configuration in which two heat exchangers each having one bending region 110 are arranged in the housing 25, the number of bending regions 110 and the way in which the bending regions 110 are arranged are different. The number of heat exchangers and the arrangement of the heat exchangers may be changed.
  • FIG. 9 is a side view for explaining the configuration of the heat source side heat exchanger according to the first embodiment.
  • arrow Drf indicates the direction in which the refrigerant flows.
  • the heat source side heat exchanger 1 includes a plurality of heat exchanger tubes 11, a first header 12, and a second header, each of which extends in the vertical direction and is arranged at intervals in a horizontal direction perpendicular to the vertical direction. 13.
  • the first header 12 is connected to the end of each heat exchanger tube 11 of the plurality of heat exchanger tubes 11 in the opposite direction of the vertical direction (Z-axis arrow direction).
  • the second header 13 is connected to the end of each heat exchanger tube 11 of the plurality of heat exchanger tubes 11 in the vertical direction (opposite direction of the Z-axis arrow).
  • the first header 12 serves to distribute the refrigerant flowing from the expansion device 4 to the plurality of heat exchanger tubes 11 .
  • the second header 13 serves to join the refrigerant flowing through the plurality of heat transfer tubes 11 .
  • the heat exchanger tube 11 is a flat tube, but it may be a circular tube.
  • FIG. 10 is a side view showing a configuration example in which the heat source side heat exchanger shown in FIG. 9 is provided with radiation fins.
  • the heat source side heat exchanger shown in FIG. 9 is provided with radiation fins.
  • corrugated corrugated fins 19 are provided between adjacent heat exchanger tubes 11 at intervals.
  • the radiation fins are not limited to the corrugated fins 19, but may be plate fins.
  • the heat source side heat exchanger 1 does not need to be provided with radiation fins.
  • the first header 12 functions as a distribution header
  • the second header 13 functions as a confluence header
  • the distribution header and confluence header form one set.
  • the combination and positional relationship of each header is not limited to this configuration example.
  • the second header 13 may function as a distribution header.
  • each of the first header 12 and the second header 13 may be a combination of a distribution header and a confluence header.
  • the flow of refrigerant in the heat source side heat exchanger 1 will be explained with reference to FIGS. 1 and 9.
  • the heat source side heat exchanger 1 operates as an evaporator
  • the gas-liquid two-phase refrigerant that has flowed into the first header 12 from the inlet 22 first flows into the mainstream space 15 .
  • a portion of the gas refrigerant flows into the gas separation space 16 through the first opening 31 .
  • the gas refrigerant that has flowed into the gas separation space 16 flows through the gas separation pipe 9 to the refrigerant pipe 6 connected to the outlet 23 of the second header 13 .
  • the refrigerant that has not flowed into the gas separation space 16 is distributed to the plurality of heat transfer tubes 11 . Since a part of the gas refrigerant flows into the gas separation space 16, the refrigerant distributed to the plurality of heat transfer tubes 11 has a high proportion of liquid phase.
  • the gas-liquid two-phase refrigerant distributed to the plurality of heat transfer tubes 11 evaporates by exchanging heat with air, flows through each heat transfer tube 11 while being gasified, and flows into the second header 13 .
  • the gas refrigerant that has merged at the second header 13 flows out from the second header 13 to the refrigerant pipe 6 via the outlet 23.
  • FIG. 11 is a schematic cross-sectional view showing the structure taken along line AA in FIG. 9.
  • the heat exchanger tubes 11 are shown which are arranged in the X-axis direction shown in FIG. 9 from the line AA.
  • Arrow Drf shown in FIG. 11 indicates the direction in which the refrigerant flows.
  • the first header 12 has a structure in which an internal space is partitioned into a mainstream space 15 and a gas separation space 16 by a partition wall 17 made of a plate-like member.
  • the gas separation space 16 is arranged above the mainstream space 15 in the Z-axis direction.
  • a plurality of first openings 31 are provided in the partition wall 17 at intervals in the X-axis direction, which communicate the mainstream space 15 and the gas separation space 16.
  • the plurality of first openings 31 are formed at a position higher than the liquid level of the refrigerant in a liquid phase flowing through the mainstream space 15. This is to prevent the liquid refrigerant from flowing into the gas separation space 16 from the gas-liquid two-phase refrigerant flowing through the mainstream space 15, and to facilitate separation of the gas refrigerant from the gas-liquid two-phase refrigerant into the gas separation space 16.
  • the gas-liquid two-phase refrigerant that has flowed into the first header 12 is affected by gravity, and the liquid refrigerant mainly flows in the lower part of the mainstream space 15, and the gas refrigerant mainly flows in the lower part of the mainstream space 15. It flows above the space 15. Therefore, the gas refrigerant passes through the first opening 31 from the mainstream space 15 and is separated into the gas separation space 16, and the gas ratio in the mainstream space 15 decreases.
  • the configuration example shown in FIG. 11 shows a case where the cross-sectional area of the mainstream space 15 is larger than the cross-sectional area of the gas separation space 16, but the size relationship of these cross-sectional areas is different in the case of the configuration shown in FIG. Not exclusively.
  • the cross-sectional area of the gas separation space 16 may be larger than the cross-sectional area of the mainstream space 15, or the cross-sectional area of the gas separation space 16 and the cross-sectional area of the mainstream space 15 may be equal.
  • FIG. 12 is a schematic diagram showing an example of the internal configuration of the first header shown in FIG. 11.
  • FIG. 12 shows the shape and position of the first opening 31 and the positional relationship between the first opening 31 and the heat exchanger tube 11.
  • FIG. 12 is a top view of the first header 12.
  • the first openings 31 and the heat exchanger tubes 11 are arranged alternately.
  • the relationship between the position of the first opening 31 and the position of the heat exchanger tube 11 is not limited to the configuration shown in FIG. 12. Below, a modification of the positional relationship between the first opening 31 and the heat exchanger tube 11 will be described.
  • FIG. 13 is a schematic diagram showing an example of the internal configuration of the first header of Modification 1. As shown in FIG. 13, the first openings 31 may be arranged to overlap with the positions of the heat exchanger tubes 11.
  • FIG. 14 is a schematic diagram showing an example of the internal configuration of the first header of Modification 2.
  • the number of first openings 31 may be smaller than the number of heat exchanger tubes 11. Further, the configuration is not limited to the configuration shown in FIG. 14, and the number of first openings 31 may be greater than the number of heat exchanger tubes 11.
  • FIG. 15 is a schematic diagram showing an example of the internal configuration of the first header of Modification 3. As shown in FIG. 15, the positions of the plurality of first openings 31 may be biased toward one side of the first header 12. In the case of the configuration example shown in FIG. 15, the plurality of first openings 31 are located in the opposite direction of the X-axis arrow from the half position of the first header 12 on the X-axis.
  • FIG. 16 is a schematic diagram showing an example of the internal configuration of the first header of Modification 4. As shown in FIG. 16, the first openings 31 may have a flat shape that is longer in the X-axis direction than the interval between the heat exchanger tubes 11.
  • FIGS. 12 to 16 illustrate cases in which the shape of the first opening 31 is circular and flat, the shape of the first opening 31 is not limited to the shapes shown in FIGS. 12 to 16. .
  • the shape of the first opening 31 may be rectangular or polygonal, or may be a closed curved shape.
  • each of the first heat exchanger 35a and the second heat exchanger 35b shown in FIG. 3 has the same configuration as the heat source side heat exchanger 1 shown in FIG. 9.
  • each of the first row heat exchanger 131a and the second row heat exchanger 132a shown in FIG. 4 has the same configuration as the heat source side heat exchanger 1 shown in FIG. 9.
  • the first header 12 of the first row of heat exchangers 131a and the first header 12 of the second row of heat exchangers 132a are connected via the connection pipe 27.
  • This connection pipe 27 is referred to as a first connection pipe.
  • a plurality of second headers are connected via connection piping.
  • the second header 13 of the first row of heat exchangers 131a and the second header 13 of the second row of heat exchangers 132a are connected via a connecting pipe 27.
  • This connection pipe 27 is referred to as a second connection pipe.
  • Each of the two first headers 12 connected via the first connection pipe has a mainstream space 15 and a gas separation space 16.
  • the heat source side heat exchanger 1 shown in FIG. 4 may be bent. Even with such a configuration, a plurality of heat exchangers are arranged at intervals in the direction in which the air flows. In this case, the first header 12 of the windward heat exchanger and the first header 12 of the leeward heat exchanger share the gas separation space 16.
  • each of the first row heat exchanger 131a and the second row heat exchanger 132a shown in FIG. 5 has the same configuration as the heat source side heat exchanger 1 shown in FIG. 9.
  • the heat source side heat exchanger 1 shown in FIG. 9 is applied to the configurations shown in FIGS. 6 to 8, it is the same as when applied to the configurations shown in FIGS. 3 to 5. A detailed explanation thereof will be omitted.
  • the heat source side heat exchanger 1 of the first embodiment includes a plurality of heat exchanger tubes 11 each extending in the vertical direction and arranged at intervals in a horizontal direction orthogonal to the vertical direction, and a plurality of heat exchanger tubes 11. and a first header 12 connected to each heat exchanger tube 11 at an end in the opposite vertical direction; and a second header 13 connected to the plurality of heat exchanger tubes 11 at an end in the vertical direction of each heat exchanger tube 11. and a gas separation pipe 9.
  • the gas separation pipe 9 is configured to connect the first header 12 and the refrigerant pipe 6 from which the refrigerant flows out from the second header 13 when the heat source side heat exchanger 1 operates as an evaporator.
  • the first header 12 has a partition wall 17 that separates the inside of the first header 12 into a plurality of spaces including a mainstream space 15 and a gas separation space 16 .
  • a plurality of first openings 31 are provided in the partition wall 17 to communicate the mainstream space 15 and the gas separation space 16 .
  • the gas separation space 16 is arranged above the mainstream space 15.
  • the gas separation space 16 and the refrigerant pipe 6 from which the refrigerant flows out from the second header 13 are connected by a gas separation pipe 9.
  • the first header 12 of the heat source side heat exchanger 1 is provided with the gas separation space 16 that separates the gas refrigerant from the gas-liquid two-phase refrigerant.
  • the gas refrigerant is separated from the mainstream space 15 into the gas separation space 16, and the proportion of the gas refrigerant in the mainstream space 15 decreases. Therefore, in the mainstream space 15, the ratio of liquid refrigerant to the gas-liquid two-phase refrigerant becomes high, and the refrigerant distribution from the mainstream space 15 to the plurality of heat transfer tubes 11 can be made more uniform.
  • the refrigerant distribution characteristics are improved and the heat exchange performance of the heat exchanger can be improved without providing a new refrigerant auxiliary device.
  • the refrigerant distribution characteristics are improved. can be achieved.
  • the flow rate of the gas refrigerant flowing through the plurality of heat exchanger tubes 11 and the second header 13 can be reduced. Therefore, the refrigerant pressure loss occurring inside the plurality of heat exchanger tubes 11 and the second header 13 can be reduced, and the heat exchanger performance can be improved.
  • the air conditioner 10 when the air conditioner 10 is operated under operating conditions in which the proportion of gas refrigerant is high, it is possible to suppress deterioration in refrigerant distribution to the plurality of heat transfer tubes 11 and to reduce pressure loss of the refrigerant.
  • Embodiment 2 the internal configuration of the first header 12 is different from the configuration described in the first embodiment.
  • the same components as those described in the first embodiment or those corresponding to the components described in the first embodiment are denoted by the same reference numerals, and detailed explanation thereof will be omitted.
  • FIG. 17 is a schematic cross-sectional view showing an example of the internal configuration of the first header of the heat source side heat exchanger according to the second embodiment. 17 shows the structure of the section taken along line AA shown in FIG. 9, but for convenience of explanation, the heat exchanger tubes 11 arranged in the X-axis direction shown in FIG. 9 are shown in the figure rather than the section taken along line AA. ing. Arrow Drf shown in FIG. 17 indicates the direction in which the refrigerant flows.
  • the first header 12 has a structure in which the space inside the first header 12 is separated by a partition wall 17 into a gas separation space 16, a mainstream space 15, and an ejection space 18.
  • a plurality of first openings 31 and a plurality of second openings 32 are formed in the partition wall 17 .
  • the plurality of first openings 31 communicate the mainstream space 15 and the gas separation space 16.
  • the plurality of second openings 32 communicate the mainstream space 15 and the ejection space 18 .
  • each of the plurality of second openings 32 is not located in the direction of the Z-axis arrow of the heat exchanger tube 11.
  • each of the plurality of second openings 32 is provided at a position that does not overlap with a plane obtained by projecting the flow path cross section of the heat exchanger tube 11 in the opposite direction (Z-axis arrow direction) in the vertical direction. This is to prevent the refrigerant ejected from the mainstream space 15 into the ejection space 18 through the second opening 32 from directly flowing into the heat exchanger tubes 11 .
  • each of the plurality of second openings 32 is desirably located at a boundary between the liquid levels of the refrigerant in a liquid phase flowing through the mainstream space 15 . This is to suppress an increase in the proportion of gas refrigerant flowing into the ejection space 18.
  • FIG. 17 shows a configuration in which two mainstream spaces 15 are provided in the first header 12, the number of mainstream spaces 15 is not limited to two.
  • the number of mainstream spaces 15 may be one, or three or more.
  • FIG. 17 shows a case in which each of the two second openings 32 is formed so as to face inward, it may be formed so as to face in the direction of the Y-axis arrow or in the opposite direction of the Y-axis arrow. Good too.
  • the flow rate of refrigerant jetted from the mainstream space 15 to the jetting space 18 can be made uniform. Therefore, the amount of refrigerant distributed to the plurality of heat transfer tubes 11 can be made more uniform. Thereby, the heat exchanger performance can be further improved. Moreover, the amount of gas refrigerant flowing through the plurality of heat exchanger tubes 11 and the second header 13 can be reduced. Therefore, the refrigerant pressure loss occurring within the plurality of heat exchanger tubes 11 and the second header 13 can be reduced, and the heat exchanger performance can be improved.
  • each of the first header 12 and the second header 13 has the functions of a distribution header and a merging header.
  • the same components as those described in Embodiment 1 or components corresponding to the configurations described in Embodiment 1 are given the same reference numerals, and detailed explanation thereof will be omitted.
  • FIG. 18 is a side view for explaining the configuration of the heat source side heat exchanger according to the third embodiment.
  • Arrow Drf shown in FIG. 18 indicates the direction in which the refrigerant flows.
  • the heat source side heat exchanger 1a includes a first header 12a, a second header 13a, and a plurality of heat transfer tubes 11.
  • the first header 12a has an upper merging header 41a and an upper distribution header 42a.
  • the upper merging header 41a merges the refrigerant flowing through some of the heat exchanger tubes 11.
  • the upper distribution header 42a distributes the refrigerant that has joined the upper merging header 41a to the remaining heat exchanger tubes 11 excluding some of the heat exchanger tubes 11 among the plurality of heat exchanger tubes 11.
  • the second header 13a has a lower distribution header 44a and a lower merging header 43a.
  • the lower distribution header 44a distributes the refrigerant flowing from the inlet 22 to some of the heat exchanger tubes 11 when the heat source side heat exchanger 1a operates as an evaporator.
  • the lower merging header 43a merges the refrigerant flowing through the remaining heat transfer tubes 11 from the upper distribution header 42a.
  • a partition portion 24 is provided between the lower distribution header 44a and the lower merging header 43a.
  • the upper merging header 41a and the upper distribution header 42a share the gas separation space 16.
  • the flow of refrigerant in the heat source side heat exchanger 1a of the third embodiment will be explained.
  • the refrigerant flows into the lower distribution header 44a of the second header 13a, flows through some of the heat transfer tubes 11 while being evaporated and gasified, and flows into the upper merging header 41a.
  • the gas-liquid two-phase refrigerant that has flowed into the upper merging header 41a flows into the adjacent upper distribution header 42a. Since the upper merging header 41a and the upper distribution header 42a have a common gas separation space 16, the gas refrigerant is separated from the gas-liquid two-phase refrigerant in the shared gas separation space 16.
  • the gas refrigerant is separated from the mainstream space 15 into the gas separation space 16, and the gas refrigerant is separated from the mainstream space 15 into the gas separation space 16.
  • the proportion of gas refrigerant in 15 decreases. Therefore, in the mainstream space 15, the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant becomes high, and refrigerant distribution from the mainstream space 15 to the plurality of heat exchanger tubes 11 can be made more uniform. Thereby, heat exchanger performance can be improved.
  • the flow rate of the gas refrigerant flowing through the remaining heat exchanger tubes 11 and the lower merging header 43a can be reduced. Therefore, the refrigerant pressure loss occurring in the remaining heat exchanger tubes 11 and the lower merging header 43a can be reduced, and the heat exchanger performance can be improved.
  • the gas refrigerant is separated inside the upper merging header 41a and the flow rate of the gas refrigerant decreases at the stage when the refrigerant flows into the upper distribution header 42a adjacent to the upper merging header 41a, the refrigerant pressure loss can be further reduced. is obtained.
  • each of the first header 12 and the second header 13 has the functions of a distribution header and a merging header, but the configuration is different from that of the third embodiment.
  • the same reference numerals are given to the same configurations as those explained in Embodiments 1 to 3, or the configurations corresponding to the configurations explained in Embodiments 1 to 3, and detailed explanation thereof will be given. omitted.
  • FIG. 19 is a side view for explaining the configuration of the heat source side heat exchanger according to the fourth embodiment.
  • Arrow Drf shown in FIG. 19 indicates the direction in which the refrigerant flows.
  • the heat source side heat exchanger 1b includes a first header 12b, a second header 13b, and a plurality of heat transfer tubes 11.
  • the first header 12b has an upper merging header 41b and an upper distribution header 42b.
  • the upper merging header 41b merges the refrigerant flowing through some of the heat exchanger tubes 11.
  • the upper distribution header 42b distributes the refrigerant that has joined the upper merging header 41b to the remaining heat exchanger tubes 11 excluding some of the heat exchanger tubes 11 among the plurality of heat exchanger tubes 11.
  • the second header 13b has a lower distribution header 44b and a lower merging header 43b.
  • the lower distribution header 44b distributes the refrigerant flowing from the inlet 22 to some of the heat exchanger tubes 11 when the heat source side heat exchanger 1b operates as an evaporator.
  • the lower merging header 43b merges the refrigerant flowing through the remaining heat transfer tubes 11 from the upper distribution header 42b.
  • the upper merging header 41b has a gas separation space 16 and a mainstream space 15, whereas the upper distribution header 42b has only a mainstream space 15.
  • the flow passage cross-sectional area of the mainstream space 15 of the upper distribution header 42b is smaller than the flow passage cross-section area of the mainstream space 15 of the upper merging header 41b.
  • the refrigerant flow velocity which has become smaller due to separation of the gas refrigerant at the upper merging header 41b, is increased at the upper distribution header 42b adjacent to the upper merging header 41b. I can do it. Thereby, in the upper distribution header 42b, deterioration of refrigerant distribution characteristics caused by a decrease in flow velocity can be suppressed. Moreover, the mass of the parts constituting the first header 12b can be reduced, and the cost performance of the heat source side heat exchanger 1b can be improved.
  • each of the first header 12 and the second header 13 has the functions of a distribution header and a merging header, but the configuration is different from that of the third and fourth embodiments.
  • the same reference numerals are given to the same configurations as those explained in Embodiments 1 to 4, or the configurations corresponding to the configurations explained in Embodiments 1 to 4, and detailed explanation thereof will be given. omitted.
  • FIG. 20 is a side view for explaining the configuration of the heat source side heat exchanger according to the fifth embodiment.
  • Arrow Drf shown in FIG. 20 indicates the direction in which the refrigerant flows.
  • the heat source side heat exchanger 1c includes a first header 12c, a second header 13c, and a plurality of heat transfer tubes 11.
  • the first header 12c has an upper merging header 41c and an upper distribution header 42c.
  • the upper merging header 41c merges the refrigerant flowing through some of the heat exchanger tubes 11.
  • the upper distribution header 42c distributes the refrigerant that has joined the upper merging header 41c to the remaining heat exchanger tubes 11 excluding some of the heat exchanger tubes 11 among the plurality of heat exchanger tubes 11.
  • the upper merging header 41c and the upper distribution header 42c share the mainstream space 15.
  • a partition portion 24 is provided between the refrigerant inlet and the upper merging header 41c.
  • the second header 13c has a lower distribution header 44c and a lower merging header 43c.
  • the lower distribution header 44c distributes the inflowing refrigerant to some of the heat exchanger tubes 11 when the heat source side heat exchanger 1c operates as an evaporator.
  • the lower merging header 43c merges the refrigerant flowing through the remaining heat transfer tubes 11 from the upper distribution header 42c.
  • a partition portion 24 is provided between the lower distribution header 44c and the lower merging header 43c.
  • the heat source side heat exchanger 1c has one or more bending regions 110 shown in FIGS. 3 to 8.
  • a heat exchange portion composed of an upper distribution header 42c, a lower merging header 43c, and two or more heat exchanger tubes 11 connected to the upper distribution header 42c and the lower merging header 43c is located in the bending region 110. do.
  • the upper merging header 41c located upstream of the bending region 110 in the flow direction of the refrigerant has a gas separation space 16 and a mainstream space 15.
  • the flow of refrigerant in the heat source side heat exchanger 1c of the fifth embodiment will be explained.
  • the refrigerant that has flowed into the upper merging header 41c from the lower distribution header 44c is partially separated into the gas separation space 16 at the upper merging header 41c located upstream of the bending region 110.
  • the refrigerant having a high proportion of liquid refrigerant flows into the upper distribution header 42c where the bending region 110 is located, and then divides the flow through the two or more heat transfer tubes 11.
  • Embodiment 6 The heat exchanger of Embodiment 6 has a plurality of heat exchangers arranged at intervals in the direction in which air flows.
  • the same configurations as those explained in the first to fifth embodiments or the configurations corresponding to the configurations explained in the first to fifth embodiments are denoted by the same reference numerals, and detailed description thereof will be given. omitted.
  • FIG. 21 is a side view for explaining the configuration of the heat source side heat exchanger according to the sixth embodiment.
  • FIG. 22 is a side view of the heat source side heat exchanger shown in FIG. 21 when viewed from another direction.
  • Arrow Drf shown in FIGS. 21 and 22 indicates the direction in which the refrigerant flows.
  • Arrow Dar shown in FIG. 22 indicates the direction in which air flows.
  • the heat source side heat exchanger 1d includes a first header 12-1, a plurality of heat exchanger tubes 11, and a second header 13-1, a first header 12-2, and a plurality of heat exchanger tubes. 11 and a heat exchanger composed of a second header 13-2. As shown in FIG. 22, these heat exchangers are arranged at intervals in the direction in which the air flows.
  • the heat source side heat exchanger 1d has a connection header 14 that is integrally configured to which the first headers 12-1 and 12-2 are connected.
  • the second header 13-1 functions as a distribution header that distributes the refrigerant to the plurality of heat transfer tubes 11.
  • the second header 13-2 functions as a merging header for merging the refrigerant flowing through the plurality of heat transfer tubes 11 from the connection header 14.
  • the connection header 14 has a main flow space 15 and a gas separation space 16 .
  • the refrigerant with a high proportion of gas refrigerant can be transferred to the connection header 14, and the proportion of gas refrigerant can be lowered. Therefore, the refrigerant distribution to the plurality of heat transfer tubes 11 located downstream of the connection header 14 can be made uniform, and the heat exchanger performance can be improved. Further, the flow rate of the gas refrigerant flowing through the second header 13-2 and the plurality of heat transfer tubes 11 connected to the second header 13-2 can be reduced. Therefore, the refrigerant pressure loss occurring inside the second header 13-2 and the plurality of heat transfer tubes 11 connected to the second header 13-2 can be reduced, and the heat exchanger performance can be improved.
  • Embodiment 7 the flow rate of the gas refrigerant flowing out from the gas separation space 16 of the first header 12 can be adjusted.
  • Embodiment 7 the same configurations as those explained in Embodiments 1 to 6 or structures corresponding to the configurations explained in Embodiments 1 to 6 are denoted by the same reference numerals, and detailed description thereof will be given. omitted.
  • FIG. 23 is a refrigerant circuit diagram of an air conditioner having a heat source side heat exchanger according to Embodiment 7.
  • FIG. 24 is a side view for explaining the configuration of the heat source side heat exchanger according to the seventh embodiment. Arrow Drf shown in FIG. 24 indicates the direction in which the refrigerant flows.
  • the heat source side heat exchanger 1e of the seventh embodiment has a gas separation throttle device 21 provided in the gas separation pipe 9.
  • the gas separation throttle device 21 is, for example, a thermostatic expansion valve.
  • the gas separation throttle device 21 adjusts the flow rate of the refrigerant in the gas phase.
  • the gas separation throttle device 21 adjusts the flow rate of the separated gas refrigerant depending on the opening degree. For example, when the heat source side heat exchanger 1e operates as a condenser, the gas separation throttle device 21 is in a closed state, but when the heat source side heat exchanger 1e operates as an evaporator, the gas separation throttle device 21 is closed. It becomes open. In addition, when the air conditioner 10a performs heating operation, when the proportion of gas refrigerant increases, the opening degree of the gas separation throttle device 21 becomes larger to adjust the amount of gas refrigerant to be separated. can.
  • the flow rate of the gas to be separated is adjusted in accordance with the dryness of the refrigerant flowing into the heat source side heat exchanger 1e. I can do it. Therefore, refrigerant distribution can be made uniform over a wider range of operating conditions, and heat exchanger performance is further improved.
  • Embodiments 1 to 7 described above are examples for explaining the heat exchanger and air conditioner of the present disclosure
  • Embodiments 1 to 7 of Embodiments 1 to 7 are examples for explaining the heat exchanger and air conditioner of the present disclosure.
  • the above embodiments may be combined.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur qui amène la chaleur à être échangée entre l'air et un fluide frigorigène et inclut une pluralité de tuyaux de transfert de chaleur ayant chacun une direction d'extension dans une direction verticale et agencés espacés dans une direction horizontale perpendiculaire à la direction verticale, un premier collecteur relié à la pluralité de tuyaux de transfert de chaleur au niveau de parties d'extrémité de ceux-ci dans la direction opposée à la direction verticale, un second collecteur relié à la pluralité de tuyaux de transfert de chaleur au niveau de parties d'extrémité de ceux-ci dans la direction verticale et un tuyau de séparation de gaz reliant le premier collecteur et un tuyau de fluide frigorigène hors duquel le fluide frigorigène s'écoule à partir du second collecteur si l'échangeur de chaleur fonctionne en tant qu'évaporateur, le premier collecteur comprenant une paroi de séparation séparant un intérieur du premier collecteur en une pluralité d'espaces incluant un espace d'écoulement principal et un espace de séparation de gaz ; une pluralité de premières ouvertures fournissant une communication entre l'espace d'écoulement principal et l'espace de séparation de gaz étant disposées dans la paroi de séparation ; l'espace de séparation de gaz étant disposé au-dessus de l'espace d'écoulement principal ; et l'espace de séparation de gaz et le tuyau de fluide frigorigène hors duquel le fluide frigorigène s'écoule à partir du second collecteur étant reliés au moyen du tuyau de séparation de gaz.
PCT/JP2022/017797 2022-04-14 2022-04-14 Échangeur de chaleur et dispositif de climatisation l'incluant WO2023199466A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/017797 WO2023199466A1 (fr) 2022-04-14 2022-04-14 Échangeur de chaleur et dispositif de climatisation l'incluant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/017797 WO2023199466A1 (fr) 2022-04-14 2022-04-14 Échangeur de chaleur et dispositif de climatisation l'incluant

Publications (1)

Publication Number Publication Date
WO2023199466A1 true WO2023199466A1 (fr) 2023-10-19

Family

ID=88329383

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2022/017797 WO2023199466A1 (fr) 2022-04-14 2022-04-14 Échangeur de chaleur et dispositif de climatisation l'incluant

Country Status (1)

Country Link
WO (1) WO2023199466A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02183779A (ja) * 1989-01-10 1990-07-18 Nippondenso Co Ltd 蒸発器
JPH08320192A (ja) * 1994-07-22 1996-12-03 Mitsubishi Electric Corp 熱交換器及びその製造方法、冷凍システム、空調装置、熱交換器の製造装置及びその治具
JP2003028540A (ja) * 2001-07-12 2003-01-29 Japan Climate Systems Corp 熱交換器
US20040050537A1 (en) * 2002-09-14 2004-03-18 Samsung Electronics Co., Ltd. Heat exchanger
JP2005156144A (ja) * 2003-10-29 2005-06-16 Showa Denko Kk 熱交換器
JP2009198016A (ja) * 2008-02-19 2009-09-03 Sharp Corp 熱交換器
JP2010139196A (ja) * 2008-12-15 2010-06-24 Sharp Corp 熱交換器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02183779A (ja) * 1989-01-10 1990-07-18 Nippondenso Co Ltd 蒸発器
JPH08320192A (ja) * 1994-07-22 1996-12-03 Mitsubishi Electric Corp 熱交換器及びその製造方法、冷凍システム、空調装置、熱交換器の製造装置及びその治具
JP2003028540A (ja) * 2001-07-12 2003-01-29 Japan Climate Systems Corp 熱交換器
US20040050537A1 (en) * 2002-09-14 2004-03-18 Samsung Electronics Co., Ltd. Heat exchanger
JP2005156144A (ja) * 2003-10-29 2005-06-16 Showa Denko Kk 熱交換器
JP2009198016A (ja) * 2008-02-19 2009-09-03 Sharp Corp 熱交換器
JP2010139196A (ja) * 2008-12-15 2010-06-24 Sharp Corp 熱交換器

Similar Documents

Publication Publication Date Title
US9651317B2 (en) Heat exchanger and air conditioner
EP2851641B1 (fr) Échangeur de chaleur, unité intérieure, et dispositif de cycle de réfrigération
US10309701B2 (en) Heat exchanger and air conditioner
US10041710B2 (en) Heat exchanger and air conditioner
JP2021017991A (ja) 熱交換器、空気調和装置、室内機および室外機
WO2017208493A1 (fr) Climatiseur
JP6742112B2 (ja) 熱交換器及び空気調和機
CN111512099B (zh) 热交换器及制冷循环装置
WO2023199466A1 (fr) Échangeur de chaleur et dispositif de climatisation l'incluant
JP3632248B2 (ja) 冷媒蒸発器
WO2021192903A1 (fr) Échangeur de chaleur
JP6590957B2 (ja) 冷凍装置
JP7327213B2 (ja) 熱交換器
JP6853867B2 (ja) 熱交換器及び空気調和機
JP7327214B2 (ja) 熱交換器
JP7137092B2 (ja) 熱交換器
EP3971507B1 (fr) Échangeur de chaleur, et dispositif de cycle frigorifique
JP6767606B1 (ja) 分配装置、分配装置を備えた熱交換器およびその熱交換器を備えた空気調和機
WO2021245877A1 (fr) Échangeur de chaleur et dispositif à cycle de réfrigération
KR102088826B1 (ko) 열교환기
WO2021234955A1 (fr) Échangeur de chaleur et climatiseur
JP7459402B1 (ja) 熱交換器及び空気調和装置
JP7310655B2 (ja) 熱交換器
JP7146139B1 (ja) 熱交換器及び空気調和装置
JP7150157B2 (ja) 熱交換器および冷凍サイクル装置

Legal Events

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

Ref document number: 22937445

Country of ref document: EP

Kind code of ref document: A1