WO2017149989A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2017149989A1
WO2017149989A1 PCT/JP2017/002082 JP2017002082W WO2017149989A1 WO 2017149989 A1 WO2017149989 A1 WO 2017149989A1 JP 2017002082 W JP2017002082 W JP 2017002082W WO 2017149989 A1 WO2017149989 A1 WO 2017149989A1
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WO
WIPO (PCT)
Prior art keywords
chamber
horizontal
partition plate
region
refrigerant
Prior art date
Application number
PCT/JP2017/002082
Other languages
English (en)
Japanese (ja)
Inventor
秀哲 立野井
鈴木　孝幸
近藤　喜之
青木　泰高
Original Assignee
三菱重工業株式会社
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 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to EP17759461.1A priority Critical patent/EP3425320A4/fr
Publication of WO2017149989A1 publication Critical patent/WO2017149989A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators

Definitions

  • the present invention relates to a heat exchanger and an air conditioner.
  • Priority is claimed on Japanese Patent Application No. 2016-038354, filed Feb. 29, 2016, the content of which is incorporated herein by reference.
  • a plurality of heat transfer tubes extending in the horizontal direction are arranged at intervals in the vertical direction, and fins are provided on the outer surface of each heat transfer tube. Both ends of the plurality of heat transfer tubes are respectively connected to a pair of vertically extending headers.
  • a heat exchanger is introduced again into one of the headers, and the refrigerant that has flowed through the heat transfer pipe and the other through the heat transfer tube is again transmitted in the other header. It is configured to return to one of the headers through the heat pipe.
  • Patent Document 1 describes that a dividing plate extending in the vertical direction is provided in the header, and the flow velocity in the header is increased by reducing the flow passage cross-sectional area in the header.
  • the refrigerant introduced into one region (first region) in the header via the heat transfer tube is not limited to the fact that all of the refrigerant is vaporized, and the liquid phase refrigerant It is in the state of a gas-liquid two-phase refrigerant mixed with a gas phase refrigerant.
  • a gas-liquid two-phase refrigerant is introduced to the lower part of the other region (second region) in the header via the connection pipe, the liquid refrigerant having a high density hardly reaches the upper heat transfer pipe . Therefore, as the refrigerant flows in the upper heat transfer pipe, the flow rate of the liquid-phase refrigerant decreases.
  • the present invention provides a heat exchanger capable of suppressing performance degradation, and an air conditioner using the heat exchanger.
  • the heat exchanger extends horizontally and allows the refrigerant to flow therein, and a plurality of heat transfer tubes arranged at intervals in the vertical direction, and a tubular extending in the vertical direction
  • a main vertical partition plate that divides the outlet side area to which the heat transfer pipes are connected and an inflow side area to which the flow passage is connected;
  • a portion facing the first chamber of the main vertical partition plate further including an inflow side vertical partition plate which is adjacent to each other in the circumferential direction and which is divided into a first chamber and a second chamber respectively communicating with the flow passage;
  • a first horizontal penetration connecting the first chamber and the outflow side region A hole is formed, and the second chamber and the outflow side region are communicated with each other at a portion facing the second chamber of the main longitudinal partition plate
  • the refrigerant is introduced into each of the first chamber and the second chamber in the header portion via the flow passage.
  • the refrigerant introduced into the first chamber reaches the outflow side area in the header through the first horizontal through hole.
  • the refrigerant introduced into the second chamber reaches the outflow side region in the header portion via the second horizontal through hole. That is, the refrigerant supplied to the first chamber and the second chamber is forcibly guided to the first horizontal through hole or the second horizontal through hole, and is supplied to the outflow side region.
  • the moving path of the refrigerant can be made longer by moving the refrigerant vertically in the first chamber or the second chamber toward the first horizontal through hole or the second horizontal through hole.
  • the refrigerant is supplied to the outflow side region from different vertical positions. Thereby, the refrigerant can be supplied to a wider vertical range in the outflow side region. Further, the refrigerant supplied from the first horizontal through hole and the second horizontal through hole are mixed with each other, so that the gas-liquid ratio of the refrigerant can be made uniform in the entire outflow side region. Therefore, it is possible to effectively introduce the liquid phase refrigerant also into the heat transfer tube disposed relatively upward.
  • a plurality of the first horizontal through holes are formed at mutually different vertical positions, and the second horizontal through holes are different from each other in the vertical direction.
  • a plurality of positions may be formed.
  • the refrigerant can be supplied from a plurality of different positions in the vertical direction from the first chamber to the outflow side area. Furthermore, the refrigerant can be supplied from a plurality of different positions in the vertical direction from the second chamber to the outflow side region. Therefore, equalization of the gas-liquid ratio of the refrigerant can be further achieved in the entire outflow side region.
  • a plurality of the first horizontal through holes are formed at different horizontal positions, and the second horizontal through holes have different horizontal directions.
  • a plurality of positions may be formed.
  • the refrigerant can be supplied from a plurality of different horizontal positions from the first chamber to the outflow side area. Furthermore, the refrigerant can be supplied from a plurality of different horizontal positions from the second chamber to the outflow side region. Therefore, it is possible to further equalize the gas-liquid ratio of the refrigerant as the entire outflow side region. Further, by forming the first horizontal through hole and the second horizontal through hole at the same vertical position in the horizontal direction, it is possible to adjust the flow rate and pressure loss of the individual flow paths in the header portion.
  • the first chamber faces the first chamber upstream region to which the flow passage is connected and the main vertical partition plate in a horizontal cross-sectional view.
  • a first chamber longitudinal partition plate partitioned into a first chamber downstream region, a second chamber upstream region connected with the flow passage, and the main longitudinal partition plate in a horizontal sectional view of the second chamber
  • a second chamber longitudinal partition plate partitioned into a second chamber downstream region, and the first chamber longitudinal partition plate is disposed at a portion different from the first horizontal through hole in the vertical direction and the first chamber upstream region;
  • a third horizontal through hole communicating with the first chamber downstream region is formed, and the second chamber upstream region and the second chamber vertical partition plate are different in position in the vertical direction from the second horizontal through hole.
  • a fourth horizontal through hole may be formed to communicate with the second chamber downstream region.
  • the refrigerant supplied to the first chamber travels while moving up and down in the first chamber upstream region and the first chamber downstream region before reaching the outflow side region.
  • the refrigerant supplied to the second chamber travels while moving up and down in the second chamber upstream region and the second chamber downstream region before reaching the outflow side region.
  • the heat exchanger includes the first chamber, a first chamber lower region connected to the flow passage, and a second chamber disposed above the first chamber lower region.
  • a first chamber horizontal partition plate which is divided into one chamber upper region, a second chamber lower region to which the flow passage is connected, and a second chamber disposed above the second chamber lower region
  • the refrigerant advancing upward collides with the first chamber lateral partition plate or the second chamber lateral partition plate The gas-liquid two-phase flow refrigerant can be homogenized.
  • the refrigerant introduced into the outflow side region after passing through the first chamber upper region and the second chamber upper region of the first chamber and the second chamber is directed upward through the upper and lower through holes, As the flow velocity increases, the refrigerant can be more easily spread to the upper side. As a result, the liquid phase of the refrigerant can be more effectively supplied to the heat transfer tube disposed above.
  • the circumferential direction position of the connection portion to the header portion is the same as the inflow side vertical partition plate in the flow passage.
  • the connection portion of the flow passage to the header portion may straddle the first chamber and the second chamber.
  • the flow passage communicates with a first-class passage connected in communication with the first chamber in the header portion and with the second chamber in the header portion It may have a second flow passage connected in a state.
  • the refrigerant can be forcibly supplied to each of the first chamber and the second chamber.
  • an air conditioner comprises any of the above heat exchangers.
  • the heat exchanger and the air conditioner of the present invention it is possible to suppress the performance deterioration due to the nonuniformization of the refrigerant flowing through the plurality of heat transfer pipes.
  • the air conditioner 1 provided with the heat exchanger 10 according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 4.
  • the air conditioner 1 includes a compressor 2, an indoor heat exchanger 3 (heat exchanger 10), an expansion valve 4, an outdoor heat exchanger 5 (heat exchanger 10), a four-way valve 6, and And a pipe 7 for connecting them, and constitute a refrigerant circuit composed of these.
  • the compressor 2 compresses the refrigerant and supplies the compressed refrigerant to the refrigerant circuit.
  • the indoor heat exchanger 3 exchanges heat between the refrigerant and the indoor air.
  • the indoor heat exchanger 3 is used as an evaporator at the time of cooling operation, absorbs heat from the room, and is used as a condenser at the time of heating operation, and releases heat to the room.
  • the outdoor heat exchanger 5 performs heat exchange between the refrigerant and the air outside the room.
  • the expansion valve 4 reduces the pressure by expanding a high pressure refrigerant liquefied by heat exchange in the condenser.
  • the outdoor heat exchanger 5 is used as a condenser and dissipates heat to the outside during cooling operation, and is used as an evaporator and absorbs heat from outside during heating operation.
  • the four-way valve 6 switches the flow direction of the refrigerant between the heating operation and the cooling operation.
  • the refrigerant circulates in the order of the compressor 2, the outdoor heat exchanger 5, the expansion valve 4, and the indoor heat exchanger 3.
  • the refrigerant circulates in the order of the compressor 2, the indoor heat exchanger 3, the expansion valve 4, and the outdoor heat exchanger 5.
  • the heat exchanger 10 used as the indoor heat exchanger 3 and the outdoor heat exchanger 5 will be described with reference to FIGS. 2 to 4.
  • the heat exchanger 10 includes a plurality of heat transfer pipes 20, a plurality of fins 23, a pair of headers 30, a connection pipe 55, a main longitudinal partition plate 60, and an inflow side longitudinal partition plate 70. .
  • the heat transfer tube 20 is a tubular member extending linearly in the horizontal direction, and a flow passage in which the refrigerant flows is formed inside.
  • a plurality of such heat transfer tubes 20 are arranged at intervals in the vertical direction, and are arranged in parallel to each other.
  • each heat transfer tube 20 has a flat tubular shape, and inside the heat transfer tube 20, a plurality of flow paths arranged in parallel in the horizontal direction orthogonal to the extending direction of the heat transfer tube 20 are formed. ing.
  • the plurality of flow paths are arranged in parallel to one another.
  • the outer shape of the cross section orthogonal to the extending direction of the heat transfer tube 20 is flat with the horizontal direction orthogonal to the extending direction of the heat transfer tube 20 as the longitudinal direction.
  • the fins 23 are respectively disposed between the heat transfer tubes 20 arranged as described above.
  • the heat transfer tubes 20 extend in a so-called corrugated shape so as to alternately contact the heat transfer tubes 20 vertically adjacent to each other in the extending direction of the heat transfer tubes 20.
  • the shape of the fins 23 is not limited to this, and may be any shape as long as it is provided so as to project from the outer peripheral surface of the heat transfer tube 20.
  • the pair of headers 30 is provided at both ends of the plurality of heat transfer tubes 20 so as to sandwich the heat transfer tubes 20.
  • One of the pair of headers 30 is an inlet / outlet header 40 serving as an inlet / outlet of the refrigerant into the heat exchanger 10 from the outside, and the other is a return side header 50 for the refrigerant to be folded back in the heat exchanger 10. It is assumed.
  • the inlet / outlet side header 40 is a cylindrical member extending in the vertical direction, and the upper end and the lower end are closed and the inside is divided into two upper and lower areas by a partition plate.
  • a lower region divided by the in / out side partition plate 41 is a lower in / out region 42, and an upper region is a upper in / out region 43.
  • the lower access area 42 and the upper access area 43 are out of communication with each other in the access header 40.
  • the piping 7 which comprises a refrigerant circuit is each connected to these lower in-and-out area
  • the heat transfer pipe 20 connected in communication with the lower entrance / exit area 42 is taken as a first heat transfer pipe 21 and is connected in communication with the upper entrance / exit area 43.
  • the heat transfer pipe 20 is a second heat transfer pipe 22 (heat transfer pipe 20).
  • the return side header 50 includes the header main body 51 and the return side partition plate 54.
  • the header body 51 is a cylindrical member extending in the vertical direction, and the upper end and the lower end are closed.
  • the return side partition plate 54 is provided in the header main body 51, and divides the space in the header main body 51 into upper and lower two regions.
  • the lower portion of the return side partition plate 54 of the header main body 51 is the first header portion 52
  • the upper portion of the return side partition plate 54 of the header main body 51 is the second header portion 53 (header portion) There is. That is, in the present embodiment, by dividing the inside of the header main body 51 by the folding side partition plate 54, the first header portion 52 and the second header portion 53 having a space inside are formed in the folding side header 50, respectively. ing. In other words, the first header portion 52 and the second header portion 53 constitute the return side header 50.
  • the first heat transfer pipe 21 is connected to the first header portion 52 from one side (first side) in the horizontal direction so as to be in communication with the inside of the first header portion 52, respectively.
  • the second heat transfer tubes 22 are connected to the second header portion 53 from one side (first side) in the horizontal direction so as to be in communication with the inside of the second header portion 53, respectively.
  • the heat transfer pipe 20 connected to the first header portion 52 is the first heat transfer pipe 21
  • the heat transfer pipe 20 connected to the second header portion 53 is the second heat transfer pipe 22.
  • connection pipe 55 is a tubular member in which a flow path is formed.
  • One end (first end) of the connection pipe 55 is connected to the first header portion 52 in communication with the inside of the first header portion 52.
  • the other end (second end) of the connection pipe 55 is connected to the second header portion 53 in communication with the inside of the second header portion 53. More specifically, one end (first end) of the connection pipe 55 is connected to the central portion in the vertical direction of the first header portion 52.
  • the other end (second end) of the connection pipe 55 is connected to the lower portion of the second header portion 53.
  • Connection pipe 55 is opposite to first header portion 52 and second header portion 53 in the horizontal direction one side (first side) to which first heat transfer pipe 21 and second heat transfer pipe 22 are connected. Are connected from the other side (second side) in the horizontal direction.
  • a flow passage formed inside the connection pipe 55 is a flow passage 56 which enables the flow of the refrigerant between the inside of the first header portion 52 and the inside of the second header portion 53.
  • the main vertical partition plate 60 is a plate-like member extending in the vertical direction, and is provided in the second header portion 53.
  • the main vertical partition plate 60 divides the space in the second header portion 53 into two regions of a region to which the second heat transfer pipes 22 are connected and a region to which the connection tubes 55 are connected in a horizontal cross-sectional view. ing.
  • An area to which the second heat transfer pipe 22 divided by the main vertical partition plate 60 is connected is an outflow side area 63.
  • An area to which the connection pipe 55 divided by the main vertical partition plate 60 is connected is an inflow side area 64.
  • the header 30 has a cylindrical shape extending in the vertical direction, and along with this, the internal space also has a cylindrical shape.
  • the main vertical partition plate 60 is arrange
  • region 63 each have comprised the semicircle shape in horizontal cross section view.
  • the inflow side vertical partition plate 70 is a plate-like member extending in the vertical direction, and is provided in the inflow side area 64 in the second header portion 53.
  • the inflow side vertical partition plate 70 divides the inflow side area 64 into two areas adjacent to each other in the circumferential direction of the second header portion 53 in a horizontal cross-sectional view. Of these two areas, the area on the left side viewed from the other side (second side) in the horizontal direction, which is the connection direction of the connection pipe 55, is the first chamber 71, and the area on the right side is the second chamber 72. ing.
  • the inflow side vertical partition plate 70 is disposed along the radial direction in the horizontal cross sectional view of the internal space of the cylindrical second header portion 53. Further, the inflow side vertical partition plate 70 is disposed to extend orthogonal to the main vertical partition plate 60, whereby the volumes of the first chamber 71 and the second chamber 72 are made the same.
  • a first horizontal through hole 61 for communicating the first chamber 71 and the outflow side region 63 is formed in a portion of the main vertical partition plate 60 facing the first chamber 71.
  • a second horizontal through hole 62 communicating the second chamber 72 with the outflow side region 63 is formed in a portion of the main vertical partition plate 60 facing the second chamber 72.
  • the first horizontal through holes 61 and the second horizontal through holes 62 are arranged at different positions in the vertical direction.
  • the first horizontal through hole 61 is formed in the lower portion of the main vertical partition plate 60 and near the lowermost portion of the second header portion 53.
  • the second horizontal through holes 62 are formed in the upper part of the main vertical partition plate 60 and at a position close to the uppermost part of the second header portion 53.
  • the vertical direction positions of the first horizontal through hole 61 and the second horizontal through hole 62 are different from the vertical direction position of the connection portion of the connection pipe 55 to the second header portion 53. Note that only one of the first horizontal through hole 61 and the second horizontal through hole 62 may be different in the position in the vertical direction from the connection point of the connection pipe 55 to the second header portion 53.
  • connection point between the connection pipe 55 and the second header portion 53 is the same as the circumferential position of the second header portion 53 of the inflow side vertical partition plate 70.
  • connection portion of the connection pipe 55 to the second header portion 53 is disposed across the first chamber 71 and the second chamber 72. Therefore, the refrigerant introduced from the connection pipe 55 to the second header portion 53 is introduced to both the first chamber 71 and the second chamber 72.
  • the heat exchanger 10 is the indoor heat exchanger 3, it is used as an evaporator during the cooling operation of the air conditioner 1, and in the case of the outdoor heat exchanger 5, it evaporates during the heating operation of the air conditioner 1. It will be used as a container.
  • a gas-liquid two-phase refrigerant having a large amount of liquid phase is supplied from the pipe 7 to the lower entrance / exit area 42 of the entrance / exit side header 40 shown in FIG.
  • the refrigerant is distributed and supplied into the plurality of first heat transfer pipes 21 in the lower entrance / exit area 42, and heat is exchanged with the external atmosphere of the first heat transfer pipes 21 in the process of flowing through the first heat transfer pipes 21. Evaporation is prompted.
  • the refrigerant supplied from the first heat transfer pipe 21 into the first header portion 52 of the return side header 50 is a gas-liquid two-phase gas in which the liquid phase ratio is reduced by the partial change from the liquid phase to the gas phase. It becomes a refrigerant.
  • the refrigerant in the gas-liquid two-phase state supplied into the first header portion 52 is introduced into the connection pipe 55 connected to the first header portion 52, and the second header via the connection pipe 55. Introduced in section 53.
  • the connection portion of the connection pipe 55 to the second header portion 53 spans the first chamber 71 and the second chamber 72, the inside of the first chamber 71 and the second chamber 72 is A refrigerant is introduced into each of the
  • the refrigerant introduced into the first chamber 71 is introduced into the lower part of the outflow side area 63 via the first horizontal through hole 61 formed in the lower part of the second header portion 53. At this time, when the flow rate of the refrigerant is small, the refrigerant is not stored in the first chamber 71 and introduced into the lower part of the outflow side region 63 via the first horizontal through hole 61. On the other hand, when the flow rate of the refrigerant is large, the refrigerant is sequentially introduced to the lower part of the outflow side area 63 through the first horizontal through hole 61 in a state where the refrigerant is stored to some extent in the first chamber 71.
  • the refrigerant introduced into the second chamber 72 sequentially moves upward in the second chamber 72 as the refrigerant continues to be supplied, and the second horizontal through hole 62 formed in the upper portion of the second header portion 53 It is introduced into the upper part of the outflow side area 63 via That is, while the connection portion between the connection pipe 55 and the second header portion 53 is disposed at the lower portion of the second header portion 53, the second horizontal portion in which the second chamber 72 and the outflow side region 63 are communicated. Since the through hole 62 is disposed at the upper part of the second header part 53, the refrigerant introduced into the second chamber 72 moves from the lower part to the upper part of the second chamber 72 and then introduced to the upper part of the outflow side area 63. Be done.
  • the refrigerants in the gas-liquid two-phase state introduced from the first chamber 71 and the second chamber 72 in the outflow side area 63 are mixed with each other in the outflow side area 63, and then the second header portion 53 is It is introduced into each connected heat transfer tube 20. Thereafter, the refrigerant exchanges heat with the outside atmosphere of the second heat transfer pipe 22 in the process of flowing through the second heat transfer pipe 22 to promote evaporation again. As a result, the liquid phase remaining in the refrigerant in the second heat transfer pipe 22 changes to the gas phase, and the refrigerant in the gas phase is supplied to the upper entrance / exit area 43 of the entrance / exit side header 40. Then, the refrigerant is introduced into the pipe 7 from the upper entrance / exit area 43 and circulates in the refrigerant circuit.
  • the refrigerant supplied to the first chamber 71 and the second chamber 72 is forcibly forced to be the first horizontal through hole 61 or the second horizontal through hole 62. , And supplied to the outflow side area 63.
  • the second horizontal through hole 62 is at a position separated upward from the introduction point of the refrigerant, the movement path until the refrigerant introduced into the second chamber 72 is introduced into the outflow side region 63 Become longer. This can promote mixing of the gas-liquid two-phase refrigerant in the second chamber 72.
  • the refrigerant is supplied to the outflow side region 63 from different vertical positions.
  • the refrigerant is introduced from the lowermost part and the uppermost part of the outflow side area 63, the gas-liquid ratio of the refrigerant in the whole area in the vertical direction of the outflow side area 63 can be averaged. Therefore, the liquid-phase refrigerant can be effectively introduced also into the second heat transfer pipe 22 disposed relatively upward. As a result, in the air conditioner using the heat exchanger 10 of the present embodiment, the cooling performance and the heating performance are not impaired.
  • the heat exchanger 80 of the second embodiment is a first embodiment in that a plurality of first horizontal through holes 61 and second horizontal through holes 62 are formed in the main vertical partition plate 60. It is different from the form.
  • first horizontal through holes 61 are formed, and the first horizontal through hole 61 is a lower portion of the main longitudinal partition plate 60 as in the first embodiment, and the second header portion It is formed on the 53 radial outer part.
  • the second first horizontal through hole 61 is formed at the central portion in the vertical direction of the main vertical partition plate 60 and at the radially inner side of the second header portion 53.
  • two second horizontal through holes 62 are formed, and the first second horizontal through hole 62 is an upper portion of the main vertical partition plate 60 as in the first embodiment, and the second It is formed on the radially outer portion of the header portion 53.
  • a second second horizontal through hole 62 is formed at a central portion in the vertical direction of the main vertical partition plate 60 and in a radially inner portion of the second header portion 53.
  • the second second horizontal through hole 62 is formed above the second first horizontal through hole 61, the positional relationship in the vertical direction may be reversed.
  • the refrigerant introduced into the first chamber 71 is added to the lower first horizontal through hole 61 and the outflow side area 63 through the first horizontal through hole 61 at the center in the vertical direction. be introduced. Further, the refrigerant introduced into the second chamber 72 is introduced into the outflow side area 63 through the second horizontal through hole 62 in the middle in the vertical direction in addition to the upper second horizontal through hole 62. As a result, the refrigerant can be supplied from the first chamber 71 to the outflow side area 63 from a plurality of different positions in the vertical direction. Furthermore, the refrigerant can be supplied from the second chamber 72 to the outflow side area 63 from a plurality of different positions in the vertical direction.
  • the gas-liquid ratio of the refrigerant can be made more uniform throughout the outflow side region 63.
  • a plurality of first horizontal through holes 61 having different horizontal positions may be formed at the same vertical position, and a plurality of second horizontal through holes 62 having different horizontal positions may be at the same vertical position. You may form. By this, it is possible to adjust the flow rate and pressure loss of the individual flow paths in the header portion.
  • the horizontal positions of the two first horizontal through holes 61 and the second horizontal through holes 62 are different from each other. Therefore, the refrigerant can be supplied from the first chamber 71 to the outflow side area 63 from not only the position in the vertical direction but also from a plurality of different positions in the horizontal direction. Furthermore, the refrigerant can be supplied from the second chamber 72 to the outflow side area 63 from not only the vertical position but also from a plurality of different horizontal positions. Therefore, the gas-liquid ratio of the refrigerant can be further equalized in the entire outflow side region 63.
  • a heat exchanger 90 according to a third embodiment of the present invention will be described with reference to FIGS. 7 and 8.
  • the same components as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and the detailed description thereof is omitted.
  • the heat exchanger 90 of the third embodiment is different from the first embodiment in that the first chamber partition plate 91 and the second chamber vertical partition plate 95 are provided.
  • the first chamber vertical partition plate 91 is a plate-like member extending in the vertical direction, and is disposed in the first chamber 71.
  • the first chamber longitudinal partition plate 91 divides the inside of the first chamber 71 into two regions in a horizontal cross sectional view. Of the two regions, the region on the side where the connection pipe 55 is connected is the first chamber upstream region 93, and the region facing the main vertical partition plate 60 is the first chamber downstream region 94.
  • the first chamber longitudinal partition plate 91 is arranged to extend in parallel with the main longitudinal partition plate 60. Further, in the first chamber longitudinal partition plate 91, a third horizontal through hole 92 is formed, which allows the first chamber upstream region 93 and the first chamber downstream region 94 to communicate with each other.
  • the third horizontal through holes 92 are formed so that the positions of the first horizontal through holes 61 formed in the main vertical partition plate 60 in the vertical direction are different from each other.
  • the third horizontal through hole 92 is disposed below the first horizontal through hole 61. Further, the horizontal positions of the first horizontal through hole 61 and the third horizontal through hole 92 are different from each other.
  • the first horizontal through hole 61 is formed radially inward of the second header portion 53
  • the third horizontal through hole 92 is formed radially outward of the second header portion 53.
  • the second chamber vertical partition plate 95 is a plate-like member extending in the vertical direction, and is disposed in the second chamber 72.
  • the second chamber longitudinal partition plate 95 divides the inside of the second chamber 72 into two regions in a horizontal cross sectional view. Of the two regions, the region on the side where the connection pipe 55 is connected is the second chamber upstream region 97, and the region facing the main vertical partition plate 60 is the second chamber downstream region 98.
  • the second chamber vertical partition plate 95 is disposed so as to extend in parallel with the main vertical partition plate 60. Further, in the second chamber longitudinal partition plate 95, a fourth horizontal through hole 96 for communicating the second chamber upstream region 97 and the second chamber downstream region 98 with each other is formed.
  • the fourth horizontal through holes 96 are formed such that the positions of the second horizontal through holes 62 formed in the main vertical partition plate 60 in the vertical direction are different from each other.
  • the fourth horizontal through hole 96 is disposed above the second horizontal through hole 62. Further, the horizontal positions of the second horizontal through hole 62 and the fourth horizontal through hole 96 are different from each other.
  • the second horizontal through hole 62 is formed radially inward of the second header portion 53
  • the fourth horizontal through hole 96 is formed radially outward of the second header portion 53.
  • the refrigerant supplied to the first chamber 71 vertically moves the first chamber upstream region 93 and the first chamber downstream region 94 before reaching the outflow side region 63. It moves while moving.
  • the refrigerant supplied to the second chamber 72 travels while moving up and down in the second chamber upstream region 97 and the second chamber downstream region 98 before reaching the outflow side region 63.
  • the movement path of the refrigerant introduced into the first chamber 71 and the second chamber 72 until reaching the outflow side region 63 can be lengthened. Therefore, the gas-liquid two-phase flow refrigerant can be further homogenized in the movement path.
  • the first chamber longitudinal partition plate 91 and the second chamber longitudinal partition plate 95 in the first chamber 71 or in the second chamber 72, respectively. may be disposed along the radial direction of the second header portion 53. This also makes it possible to lengthen the movement path of the refrigerant as described above.
  • the heat exchanger 100 of 4th embodiment is a point which is equipped with the 1st chamber horizontal partition plate 101 and the 2nd chamber horizontal partition plate 105, and differs from 1st embodiment.
  • the first chamber horizontal partition plate 101 is a plate-like member extending in the horizontal direction, and is disposed in the first chamber 71.
  • the first chamber horizontal partition plate 101 divides the inside of the first chamber 71 into two upper and lower regions. Of the two regions, the lower region to which the connection pipe 55 is connected is the first chamber lower region 103, and the upper region is the first chamber upper region 104.
  • first upper and lower through holes 102 are formed to allow the first chamber lower region 103 and the first chamber upper region 104 to communicate with each other.
  • the second chamber lateral partition plate 105 is a horizontally extending plate-like member, and is disposed in the second chamber 72.
  • the second chamber lateral partition plate 105 divides the inside of the second chamber 72 into two upper and lower regions. Of the two regions, the lower region to which the connection pipe 55 is connected is the second chamber lower region 107, and the upper region is the second chamber upper region 108.
  • a second upper and lower through hole 106 is formed in the second chamber lateral partition plate 105 to allow the second chamber lower area 107 and the second chamber upper area 108 to communicate with each other.
  • the first horizontal through holes 61 formed in the main vertical partition plate 60 communicate the first chamber lower area 103 and the outflow side area 63 with each other. Further, the second horizontal through holes 62 formed in the main vertical partition plate 60 communicate the second chamber upper area 108 with the outflow side area 63.
  • the refrigerant traveling upward is the first chamber horizontal partition plate 101 or It collides with the second chamber horizontal partition plate 105. Since the refrigerant
  • coolant can be achieved further.
  • the refrigerant in the second chamber 72 introduced into the outflow side region 63 after passing through the second chamber upper region 108 in particular is increased in flow velocity when going upward through the second upper and lower through holes 106. It becomes easy to distribute the refrigerant to the upper side. As a result, the liquid phase of the refrigerant can be more effectively supplied to the second heat transfer pipe 22 disposed above.
  • the 1st up-and-down through-hole 102 is formed in the 1st chamber horizontal partition plate 101, it does not necessarily need to be formed. If the first upper and lower through holes 102 are formed, for example, if the flow rate of the refrigerant is relatively large, there is an advantage that the refrigerant can be temporarily stored in the first chamber upper region 104. There is also an advantage that pressure resistance can be improved by reducing the internal pressure difference between the first chamber upper area 104 and the other area.
  • the refrigerant introduced from the connection pipe 55 into the first chamber lower region 103 is directed to the outflow side region 63 through the first horizontal through hole 61, so the first chamber upper portion The liquid phase refrigerant does not reach the region 104.
  • the first vertical chamber partition plate 91 and the second chamber vertical partition plate 95 described in the third embodiment may be provided.
  • connection pipe 55 is connected to the second header portion 53 so as to straddle the first chamber 71 and the second chamber 72.
  • two connection pipes 55 are connected. Are connected to the second header portion 53.
  • Each of the connection pipes 55 is also connected to the first header portion 52, and the inside thereof is a communication passage. Even in this case, the refrigerant can be forcibly introduced into the first chamber 71 and the second chamber 72 as in the first to fourth embodiments.
  • transduced into the 1st chamber 71 and the 2nd chamber 72 can be suitably adjusted by changing the flow-path cross-sectional area of the connection pipe
  • the refrigerants having different flow rates can be intentionally introduced to the connection pipes 55 so as to optimize the heat exchange rate.
  • the heat exchanger and the air conditioner it is possible to suppress the performance deterioration due to the non-uniformization of the refrigerant flowing through the plurality of heat transfer pipes.

Landscapes

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

Abstract

La présente invention concerne un échangeur de chaleur (10) qui comprend : des tuyaux de transfert de chaleur (20); une partie de collecteur à laquelle l'extrémité des tuyaux de transfert de chaleur (20) est raccordée de façon à être en communication avec un espace interne; un passage d'écoulement (56) qui est raccordé à l'intérieur de la partie de collecteur de façon à être en communication avec celle-ci et qui comporte un écoulement de réfrigérant à travers celui-ci; une partie de séparation verticale principale (60) qui divise une section transversale horizontale de l'intérieur de la partie de collecteur dans une région côté écoulement de sortie (63) qui est raccordée aux tuyaux de transfert de chaleur (20) et une région côté écoulement d'entrée (64) qui est raccordée au passage d'écoulement (56); et une plaque de séparation verticale côté écoulement d'entrée (70) qui divise une section transversale horizontale de la région côté écoulement d'entrée (64) en une première chambre (71) et une deuxième chambre (72) qui sont mutuellement adjacentes dans la direction circonférentielle de la partie de collecteur et qui sont en communication avec le passage d'écoulement (56). Une section de la plaque de séparation verticale principale (60) faisant face à la première chambre (71) comporte, formé dans celle-ci, un premier trou traversant horizontal (61) qui permet à la première chambre (71) de communiquer avec la région côté écoulement de sortie (63). Une section de la plaque de séparation verticale principale (60) faisant face à la deuxième chambre (72) et à une position différente dans la direction verticale du premier trou traversant horizontal (61) comporte, formé dans celle-ci, un deuxième trou traversant horizontal (62) qui permet à la deuxième chambre (72) de communiquer avec la région côté écoulement de sortie (63).
PCT/JP2017/002082 2016-02-29 2017-01-23 Échangeur de chaleur et climatiseur WO2017149989A1 (fr)

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JP2016-038354 2016-02-29
JP2016038354A JP6202451B2 (ja) 2016-02-29 2016-02-29 熱交換器及び空気調和機

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JP2019052784A (ja) * 2017-09-13 2019-04-04 三菱電機株式会社 熱交換器及び空気調和機
WO2020217271A1 (fr) * 2019-04-22 2020-10-29 三菱電機株式会社 Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique
EP3951286A4 (fr) * 2019-03-29 2022-12-28 Fujitsu General Limited Échangeur thermique

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FR3075347B1 (fr) * 2017-12-19 2020-05-15 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant destine a etre loge dans une boite collectrice d'un echangeur de chaleur
WO2019207799A1 (fr) * 2018-04-27 2019-10-31 日立ジョンソンコントロールズ空調株式会社 Climatiseur et échangeur thermique
CN108801008B (zh) * 2018-09-13 2023-09-26 西安热工研究院有限公司 一种横向连通结构印刷电路板式换热器芯体
US20220316804A1 (en) * 2019-02-04 2022-10-06 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus including the same
US11402161B2 (en) * 2019-04-22 2022-08-02 Hitachi-Johnson Controls Air Conditioning, Inc. Distributor, heat exchanger, indoor unit, outdoor unit, and air-conditioning device
JP7310655B2 (ja) * 2020-03-03 2023-07-19 株式会社富士通ゼネラル 熱交換器
JP6927352B1 (ja) * 2020-03-23 2021-08-25 株式会社富士通ゼネラル 熱交換器
JP6930622B1 (ja) * 2020-03-24 2021-09-01 株式会社富士通ゼネラル 熱交換器
WO2021192192A1 (fr) * 2020-03-27 2021-09-30 三菱電機株式会社 Échangeur de chaleur, unité d'échangeur de chaleur et dispositif à cycle frigorifique
IT202000024268A1 (it) * 2020-10-14 2022-04-14 Hudson Italiana Fbm Sistema testata-fascio tubiero per la distribuzione ottimizzata del fluido in un dispositivo aerorefrigerante
DE102022112229A1 (de) * 2022-05-16 2023-11-16 Valeo Klimasysteme Gmbh Wärmetauscher für ein Kraftfahrzeug

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Publication number Priority date Publication date Assignee Title
JP2019052784A (ja) * 2017-09-13 2019-04-04 三菱電機株式会社 熱交換器及び空気調和機
EP3951286A4 (fr) * 2019-03-29 2022-12-28 Fujitsu General Limited Échangeur thermique
US11846472B2 (en) 2019-03-29 2023-12-19 Fujitsu General Limited Heat exchanger
WO2020217271A1 (fr) * 2019-04-22 2020-10-29 三菱電機株式会社 Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique
JPWO2020217271A1 (ja) * 2019-04-22 2021-10-21 三菱電機株式会社 冷媒分配器、熱交換器及び冷凍サイクル装置
JP7086279B2 (ja) 2019-04-22 2022-06-17 三菱電機株式会社 冷媒分配器、熱交換器及び冷凍サイクル装置

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