EP3425320A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
EP3425320A1
EP3425320A1 EP17759461.1A EP17759461A EP3425320A1 EP 3425320 A1 EP3425320 A1 EP 3425320A1 EP 17759461 A EP17759461 A EP 17759461A EP 3425320 A1 EP3425320 A1 EP 3425320A1
Authority
EP
European Patent Office
Prior art keywords
chamber
horizontal
partition plate
region
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP17759461.1A
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German (de)
English (en)
Other versions
EP3425320A4 (fr
Inventor
Hideaki Tatenoi
Takayuki Suzuki
Yoshiyuki Kondo
Yasutaka Aoki
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3425320A1 publication Critical patent/EP3425320A1/fr
Publication of EP3425320A4 publication Critical patent/EP3425320A4/fr
Withdrawn legal-status Critical Current

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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.
  • This application claims priority based on Japanese Patent Application No. 2016-038354 filed on February 29, 2016 ; the contents of which are incorporated herein by reference.
  • a heat exchanger in which a plurality of heat-transfer pipes extending in a horizontal direction are disposed at intervals in a vertical direction and a fin is provided on an outer surface of each heat-transfer pipe, is known as a heat exchanger of an air conditioner. Both ends of the plurality of heat-transfer pipes are connected to a pair of headers extending in the vertical direction, respectively.
  • Such a heat exchanger is configured such that a refrigerant, which is introduced into one header and has flown to the other header via the heat-transfer pipes, turns back at the other header to return to one header again via the heat-transfer pipes, in order to secure a flow path length for the refrigerant.
  • the inside of the header at a turnback side is partitioned into a plurality of regions with a partition plate partitioning the inside of the header in the vertical direction. Accordingly, a refrigerant introduced in one region (first region) of the header via the heat-transfer pipes returns to one header on an entrance side via the plurality of heat-transfer pipes connected to the other region (second region) after being introduced into the other region (second region) of the header via a connection pipe.
  • a partition plate extending in vertical direction is provided in the header, and a refrigerant speed in the header is increased by making a flow path sectional area in the header smaller.
  • the heat exchanger In a case where the heat exchanger is used as an evaporator, not the entire refrigerant, which is introduced into one region (first region) of the header via the heat-transfer pipes, evaporates, and the refrigerant is in a state of a gas-liquid two phase refrigerant, in which a liquid phase refrigerant and a gas phase refrigerant are mixed.
  • a gas-liquid two phase refrigerant is introduced in a lower portion of the other region (second region) of the header via the connection pipe, a liquid phase refrigerant with a high density is unlikely to reach upper heat-transfer pipes.
  • a refrigerant flowing in the upper heat-transfer pipes is a liquid phase refrigerant having a lower flow rate.
  • the heat exchanger does not show a desired performance in some cases.
  • An object of the invention is to provide a heat exchanger which can suppress a performance decrease and an air conditioner in which the heat exchanger is used.
  • a heat exchanger including a plurality of heat-transfer pipes that extend in a horizontal direction to allow a refrigerant to flow therein and are arranged at intervals in a vertical direction, a header part that has a tubular shape extending in the vertical direction and has an internal space connected to one end of each of the plurality of heat-transfer pipes in a communicating state, a flow passage that is connected to an inside of the header part in a communicating state and allows the refrigerant to flow therein, a main vertical partition plate that partitions the inside of the header part into an outflow-side region connected to each of the heat-transfer pipes and an inflow-side region connected to the flow passage, in horizontal sectional view, and an inflow-side vertical partition plate that partitions the inflow-side region into a first chamber and a second chamber, which are adjacent to each other in a circumferential direction of the header part and each of which communicates with the flow passage, in horizontal sectional view.
  • a first horizontal through-hole that allows the first chamber to communicate with the outflow-side region is formed in a portion of the main vertical partition plate facing the first chamber.
  • a second horizontal through-hole that allows the second chamber to communicate with the outflow-side region is formed in a portion of the main vertical partition plate facing the second chamber, the portion having a vertical position different from that of the first horizontal through-hole.
  • a refrigerant is introduced into each of the first chamber and the second chamber in the header part via the flow passage.
  • the refrigerant introduced in the first chamber reaches the outflow-side region in the header part via the first horizontal through-hole.
  • the refrigerant introduced in the second chamber reaches the outflow-side region in the header part via the second horizontal through-hole. That is, refrigerants supplied to the first chamber and the second chamber are forcibly guided by the first horizontal through-hole and the second horizontal through-hole respectively, and are supplied to the outflow-side region.
  • a moving route for a refrigerant can be made longer by the refrigerant moving in the first chamber or the second chamber in the vertical direction toward the first horizontal through-hole or the second horizontal through-hole. Accordingly, the mixing of a refrigerant in a gas-liquid two phase state in the first chamber and the second chamber can be caused.
  • first horizontal through-hole and the second horizontal through-hole are formed at different vertical positions, refrigerants are supplied from vertical positions different from each other to the outflow-side region. Consequently, a refrigerant can be supplied to a vertically wider area in the outflow-side region.
  • the homogenization of a gas-liquid ratio of the refrigerant can be achieved in the outflow-side region as a whole by mixing the refrigerant supplied from each of the first horizontal through-hole and the second horizontal through-hole. For this reason, a liquid phase refrigerant can be effectively introduced also into the heat-transfer pipes which are disposed relatively higher.
  • a plurality of the first horizontal through-holes may be formed at vertical positions different from each other, and a plurality of the second horizontal through-holes may be formed at vertical positions different from each other.
  • a refrigerant can be supplied from a plurality of points having vertical positions different from each other of the first chamber to the outflow-side region.
  • a refrigerant can be supplied from a plurality of points having vertical positions different from each other of the second chamber to the outflow-side region. For this reason, the homogenization of a gas-liquid ratio of a refrigerant in the outflow-side region as a whole can be further achieved.
  • a plurality of the first horizontal through-holes may be formed at horizontal positions different from each other, and a plurality of the second horizontal through-holes may be formed at horizontal positions different from each other.
  • a refrigerant can be supplied from a plurality of points having horizontal positions different from each other of the first chamber to the outflow-side region.
  • a refrigerant can be supplied from a plurality of points having vertical positions different from each other of the second chamber to the outflow-side region. For this reason, the homogenization of a gas-liquid ratio of a refrigerant in the outflow-side region as a whole can be further achieved.
  • the flow rate or pressure loss of an individual flow path in the header part can be adjusted by forming the first horizontal through-hole and the second horizontal through-hole at the same vertical position in the horizontal direction.
  • a first chamber vertical partition plate that partitions the first chamber into a first chamber upstream region connected to the flow passage and a first chamber downstream region facing the main vertical partition plate, in horizontal sectional view and a second chamber vertical partition plate that partitions the second chamber into a second chamber upstream region connected to the flow passage and a second chamber downstream region facing the main vertical partition plate, in horizontal sectional view may be further included.
  • a third horizontal through-hole that allows the first chamber upstream region to communicate with the first chamber downstream region may be formed in a portion of the first chamber vertical partition plate, which has a vertical position different from that of the first horizontal through-hole.
  • a fourth horizontal through-hole that allows the second chamber upstream region to communicate with the second chamber downstream region may be formed in a portion of the second chamber vertical partition plate, which has a vertical position different from that of the second horizontal through-hole.
  • a refrigerant supplied to the first chamber proceeds while moving in the first chamber upstream region and the first chamber downstream region in the vertical direction before reaching the outflow-side region.
  • a refrigerant supplied to the second chamber proceeds while moving in the second chamber upstream region and the second chamber downstream region in the vertical direction before reaching the outflow-side region. Consequently, a moving route to the outflow-side region for a refrigerant introduced in the first chamber and the second chamber can be made longer. For this reason, the homogenization of a gas-liquid two phase type refrigerant on the moving route can be further achieved.
  • a first chamber horizontal partition plate that partitions the first chamber into a first chamber lower region connected to the flow passage and a first chamber upper region disposed above the first chamber lower region and a second chamber horizontal partition plate that partitions the second chamber into a second chamber lower region connected to the flow passage and a second chamber upper region disposed above the second chamber lower region may be further included.
  • a vertical through-hole that allows the upper and lower regions to communicate with each other may be formed in at least one of the first chamber horizontal partition plate and the second chamber horizontal partition plate.
  • a connection portion of the flow passage to the header part may straddle the first chamber and the second chamber by making the circumferential position of the connection portion of the flow passage to the header part be the same point as the inflow-side vertical partition plate.
  • the flow passage may have a first flow passage connected to the first chamber in the header part in a communicating state and a second flow passage connected to the second chamber in the header part in a communicating state.
  • a refrigerant can be forcibly supplied to each of the first chamber and the second chamber.
  • an air conditioner including the heat exchanger of any one of the aspects.
  • the homogenization of a refrigerant supplied from the inside of the header part to the heat-transfer pipes can be achieved, and thus a decrease in a cooling and heating performance can be avoided.
  • a performance decrease caused by the non-homogenization of a refrigerant flowing in the plurality of heat-transfer pipes can be suppressed.
  • 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 a pipe 7 that connects the configuration elements together, and a refrigerant circuit formed of the configuration elements is configured.
  • the compressor 2 compresses a refrigerant and supplies the compressed refrigerant to the refrigerant circuit.
  • the indoor heat exchanger 3 performs heat exchange between the refrigerant and indoor air.
  • the indoor heat exchanger 3 is used as an evaporator to absorb heat from the inside during cooling operation, and is used as a condenser to radiate heat to the inside during heating operation.
  • the outdoor heat exchanger 5 performs heat exchange between the refrigerant and outdoor air.
  • the expansion valve 4 reduces a pressure by expanding the high-pressure refrigerant liquefied by the condenser exchanging heat.
  • the outdoor heat exchanger 5 is used as a condenser to radiate heat to the outside during cooling operation and is used as an evaporator to absorb heat from the outside during heating operation.
  • the four-way valve 6 switches between directions where a refrigerant flows during heating operation and during cooling operation. Consequently, a refrigerant circulates in the compressor 2, the outdoor heat exchanger 5, the expansion valve 4, and the indoor heat exchanger 3 in this order during cooling operation. On the other hand, a refrigerant circulates in the compressor 2, the indoor heat exchanger 3, the expansion valve 4, and the outdoor heat exchanger 5 in this order during heating operation.
  • 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 vertical partition plate 60, and an inflow-side vertical partition plate 70.
  • the heat-transfer pipes 20 are tubular members linearly extending in a horizontal direction, and flow paths through which a refrigerant flows are formed therein.
  • the plurality of heat-transfer pipes 20 are arranged at intervals in a vertical direction, and are disposed so as to be parallel to each other.
  • the heat-transfer pipes 20 each have a flat tubular shape, and the plurality of flow paths arranged in the horizontal direction orthogonal to an extending direction of the heat-transfer pipes 20 are formed inside the heat-transfer pipes 20.
  • the plurality of flow paths are arranged so as to be parallel to each other. Consequently, a sectional shape orthogonal to the extending direction of the heat-transfer pipes 20 is a flat shape of which a longitudinal direction is the horizontal direction orthogonal to the extending direction of the heat-transfer pipes 20.
  • the fins 23 each are disposed between the heat-transfer pipes 20 arranged as described above.
  • the fins 23 extend in a so-called corrugated shape so as to be alternately in contact with the vertically adjacent heat-transfer pipes 20 as facing the extending direction of each of the heat-transfer pipes 20.
  • the shapes of the fins 23 may be any shape insofar as the fins are provided so as to protrude from outer peripheral surfaces of the heat-transfer pipes 20.
  • the pair of headers 30 is provided such that the heat-transfer pipes 20 are sandwiched therebetween.
  • One of the pair of headers 30 is set as an entrance side header 40, which is an entrance of a refrigerant from the outside into the heat exchanger 10, and the other one is set as a turnback side header 50 for a refrigerant to turn back in the heat exchanger 10.
  • the entrance side header 40 is a cylindrical member extending in the vertical direction. An upper end and a lower end of the entrance side header are closed and the inside of the entrance side header is partitioned into two upper and lower regions with a partition plate.
  • the lower region partitioned with an entrance side partition plate 41 is set as a lower entry region 42 and the upper region is set as an upper entry region 43.
  • the lower entry region 42 and the upper entry region 43 are in a state of not communicating with each other in the entrance side header 40.
  • the lower entry region 42 and the upper entry region 43 each are connected to the pipe 7 configuring the refrigerant circuit.
  • the heat-transfer pipes 20 connected to the lower entry region 42 in a communicating state are set as first heat-transfer pipes 21, and the heat-transfer pipes 20 connected to the upper entry region 43 in a communicating state are set as second heat-transfer pipes 22 (heat-transfer pipes 20).
  • the turnback side header 50 includes a header body 51 and a turnback side partition plate 54.
  • the header body 51 is a cylindrical member extending in the vertical direction, and an upper end and a lower end of the header body are closed.
  • the turnback side partition plate 54 is provided in the header body 51, and partitions a space in the header body 51 into two upper and lower regions.
  • a portion of the header body 51 below the turnback side partition plate 54 is set as a first header part 52, and a portion of the header body 51 above the turnback side partition plate 54 is set as a second header part 53 (header part). That is, in the embodiment, the first header part 52 and the second header part 53 each of which has a space therein are formed in the turnback side header 50 by the inside of the header body 51 being partitioned with the turnback side partition plate 54.
  • the turnback side header 50 is configured with the first header part 52 and the second header part 53.
  • the first heat-transfer pipes 21 each are connected to one side (first side) of the first header part 52 in the horizontal direction so as to be in a communicating state with the inside of the first header part 52.
  • the second heat-transfer pipes 22 each are connected one side (first side) of the second header part 53 in the horizontal direction so as to be in a communicating state with the second header part 53.
  • the heat-transfer pipes 20 connected to the first header part 52 are set as the first heat-transfer pipes 21, and the heat-transfer pipes 20 connected to the second header part 53 are set as the second heat-transfer pipes 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 part 52 in a communicating state with the inside of the first header part 52.
  • the other end (second end) of the connection pipe 55 is connected to the second header part 53 in a communicating state with the inside of the second header part 53. More specifically, one end (first end) of the connection pipe 55 is connected to a middle portion of the first header part 52 in the vertical direction.
  • the other end (second end) of the connection pipe 55 is connected to a lower portion of the second header part 53.
  • connection pipe 55 is connected to the other side (second side) of each of the first header part 52 and the second header part 53 in the horizontal direction, which is the opposite side to one side (first side) connected to the first heat-transfer pipes 21 and the second heat-transfer pipes 22 in the horizontal direction.
  • connection pipe 55 The flow path formed inside the connection pipe 55 is a flow passage 56 that allows a refrigerant to flow between the inside of the first header part 52 and the inside of the second header part 53.
  • the main vertical partition plate 60 is a plate-shaped member extending in the vertical direction, and is provided in the second header part 53.
  • the main vertical partition plate 60 partitions a space in the second header part 53 into two regions including a region connected to each of the second heat-transfer pipes 22 and a region connected to the connection pipe 55, in horizontal sectional view.
  • the region which is partitioned with the main vertical partition plate 60 and is connected to the second heat-transfer pipes 22 is set as an outflow-side region 63.
  • the region which is partitioned with the main vertical partition plate 60 and is connected to the connection pipe 55 is set as an inflow-side region 64.
  • the headers 30 have a cylindrical shape extending in the vertical direction, and accordingly an internal space thereof also has a cylindrical shape.
  • the main vertical partition plate 60 is disposed in a diameter direction of the internal space of the second header part 53 having a cylindrical shape, in horizontal sectional view. Accordingly, each of the inflow-side region 64 and the outflow-side region 63 has a semicircular shape, in horizontal sectional view.
  • the inflow-side vertical partition plate 70 is a plate-shaped member extending in the vertical direction, and is provided in the inflow-side region 64 of the second header part 53.
  • the inflow-side vertical partition plate 70 partitions the inflow-side region 64 into two adjacent regions in a circumferential direction of the second header part 53, in horizontal sectional view.
  • a left region is set as a first chamber 71 and a right region is set as a second chamber 72, out of the two regions.
  • the inflow-side vertical partition plate 70 is disposed in a radial direction in horizontal sectional view of the internal space of the second header part 53 having a cylindrical shape.
  • the inflow-side vertical partition plate 70 is disposed such that the inflow-side vertical partition plate extends to be orthogonal to the main vertical partition plate 60, and accordingly the volume of the first chamber 71 and the volume of the second chamber 72 are the same.
  • a first horizontal through-hole 61 that allows the first chamber 71 to communicate with 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 that allows the second chamber 72 to communicate 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-hole 61 and the second horizontal through-hole 62 are disposed at points having vertical positions different from each other.
  • the first horizontal through-hole 61 is formed at a point close to a lowermost portion of the second header part 53, which is a lower portion of the main vertical partition plate 60.
  • the second horizontal through-hole 62 is formed at a point close to an uppermost portion of the second header part 53, which is an upper portion of the main vertical partition plate 60.
  • the vertical positions of the first horizontal through-hole 61 and the second horizontal through-hole 62 are positions different from the vertical position of a connection portion of the connection pipe 55 to the second header part 53. Only one of the first horizontal through-hole 61 and the second horizontal through-hole 62 may have a vertical position different from the connection portion of the connection pipe 55 to the second header part 53.
  • connection portion of the connection pipe 55 to the second header part 53 is the same point as the circumferential position of the inflow-side vertical partition plate 70 on the second header part 53. Consequently, the connection portion of the connection pipe 55 to the second header part 53 is disposed so as to straddle the first chamber 71 and the second chamber 72. Thus, a refrigerant introduced from the connection pipe 55 into the second header part 53 is introduced into both of the first chamber 71 and the second chamber 72.
  • the heat exchanger 10 is used as an evaporator.
  • the heat exchanger 10 is the indoor heat exchanger 3
  • the heat exchanger is used as an evaporator during cooling operation of the air conditioner 1
  • the heat exchanger is used as an evaporator during heating operation of the air conditioner 1.
  • a gas-liquid two phase refrigerant having a high liquid phase content is supplied from the pipe 7 to the lower entry region 42 of the entrance side header 40 illustrated in Fig. 2 .
  • the refrigerant is divided and supplied to the plurality of first heat-transfer pipes 21 in the lower entry region 42, and exchanges heat with the external atmosphere of the first heat-transfer pipes 21 in the process of flowing in the first heat-transfer pipes 21, thereby causing evaporation.
  • the refrigerant supplied from the first heat-transfer pipes 21 into the first header part 52 of the turnback side header 50 becomes a gas-liquid two phase refrigerant, in which the proportion of a liquid phase has dropped, by some of the refrigerant changing from the liquid phase to a gas phase.
  • the refrigerant in a gas-liquid two phase state supplied into the first header part 52 is introduced into the connection pipe 55 connected to the first header part 52, and is introduced into the second header part 53 via the connection pipe 55.
  • the refrigerant is introduced into each of the first chamber 71 and the second chamber 72 since the connection portion of the connection pipe 55 to the second header part 53 straddles the first chamber 71 and the second chamber 72.
  • the refrigerant introduced in the first chamber 71 is introduced into a lower portion of the outflow-side region 63 via the first horizontal through-hole 61 formed in the lower portion of the second header part 53.
  • the refrigerant is introduced into the lower portion of the outflow-side region 63 via the first horizontal through-hole 61 without being stored in the first chamber 71.
  • the refrigerant is introduced into the lower portion of the outflow-side region 63 via the first horizontal through-hole 61 in turn in a state where the refrigerant is stored in the first chamber 71 to some extent.
  • the refrigerant introduced in the second chamber 72 moves upwards in turn in the second chamber 72 as the refrigerant continues to be supplied, and is introduced into an upper portion of the outflow-side region 63 via the second horizontal through-hole 62 formed in the upper portion of the second header part 53. That is, while the connection portion between the connection pipe 55 and the second header part 53 is disposed in the lower portion of the second header part 53, the second horizontal through-hole 62 that allows the second chamber 72 to communicate with the outflow-side region 63 is disposed in the upper portion of the second header part 53. Therefore, the refrigerant introduced in the second chamber 72 is introduced into the upper portion of the outflow-side region 63 after being moved from the lower side to the upper side in the second chamber 72.
  • the respective refrigerants in a gas-liquid two phase state introduced from the first chamber 71 and the second chamber 72 to the outflow-side region 63 is introduced into each of the heat-transfer pipes 20 connected to the second header part 53 after being mixed with each other in the outflow-side region 63.
  • the refrigerant again causes evaporation by exchanging heat with the external atmosphere of the second heat-transfer pipes 22 in the process of flowing in the second heat-transfer pipes 22. Consequently, in the second heat-transfer pipes 22, the remaining liquid phase in the refrigerant changes to the gas phase, and thus the refrigerant in a gas phase state is supplied to the upper entry region 43 of the entrance side header 40. Then, the refrigerant is introduced from the upper entry region 43 to the pipe 7, thereby circulating in the refrigerant circuit.
  • refrigerants supplied to the first chamber 71 and the second chamber 72 are forcibly guided by the first horizontal through-hole 61 and the second horizontal through-hole 62 respectively, and are supplied to the outflow-side region 63.
  • the second horizontal through-hole 62 is at a position vertically spaced apart from a point where a refrigerant is introduced, a moving route to the outflow-side region 63 for a refrigerant introduced in the second chamber 72 is made longer. Accordingly, the mixing of a refrigerant in a gas-liquid two phase state in the second chamber 72 can be caused.
  • first horizontal through-hole 61 and the second horizontal through-hole 62 are formed at different vertical positions, refrigerants are supplied from vertical positions different from each other to the outflow-side region 63.
  • refrigerant is introduced from each of the lowermost portion and the uppermost portion of the outflow-side region 63, a gas-liquid ratio of the refrigerant over the entire area of the outflow-side region 63 in the vertical direction can be homogenized.
  • a heat exchanger 80 according to a second embodiment of the invention will be described with reference to Figs. 5 and 6 .
  • the same configuration elements as the first embodiment will be assigned with the same reference signs as the first embodiment, and the detailed description thereof will be omitted.
  • the heat exchanger 80 of the second embodiment is different from the first embodiment in that a plurality of first horizontal through-holes 61 and a plurality of second horizontal through-holes 62 are formed in the main vertical partition plate 60.
  • first horizontal through-holes 61 are formed.
  • the first one of the first horizontal through-holes 61 is in the lower portion of the main vertical partition plate 60 as in the first embodiment, and is formed in a radially outside portion of the second header part 53.
  • the second one of the first horizontal through-holes 61 is in a vertically middle portion of the main vertical partition plate 60, and is formed in a radially inside portion of the second header part 53.
  • two second horizontal through-holes 62 are formed.
  • the first one of the second horizontal through-holes 62 is in the upper portion of the main vertical partition plate 60 as in the first embodiment, and is formed in a radially outside portion of the second header part 53.
  • the second one of the second horizontal through-holes 62 is in a vertically middle portion of the main vertical partition plate 60, and is formed in a radially inside portion of the second header part 53.
  • the second one of the second horizontal through-holes 62 is formed above the second one of the first horizontal through-holes 61, a relationship of vertical positions thereof may be the opposite.
  • a refrigerant introduced in the first chamber 71 is introduced into the outflow-side region 63 via the first horizontal through-hole 61 in the vertically middle portion in addition to the first horizontal through-hole 61 in the lower portion.
  • a refrigerant introduced in the second chamber 72 is introduced into the outflow-side region 63 via the second horizontal through-hole 62 in the vertically middle portion in addition to the second horizontal through-hole 62 in the upper portion.
  • a refrigerant can be supplied from a plurality of points having vertical positions different from each other of the first chamber 71 to the outflow-side region 63.
  • a refrigerant can be supplied from a plurality of points having vertical positions different from each other of the second chamber 72 to the outflow-side region 63. For this reason, the homogenization of a gas-liquid ratio of a refrigerant in the outflow-side region 63 as a whole can be further achieved.
  • the plurality of first horizontal through-holes 61 having different horizontal positions may be formed at the same vertical position, or the plurality of second horizontal through-holes 62 having different horizontal positions may be formed at the same vertical position. Accordingly, the flow rate or pressure loss of an individual flow path in the header part can be adjusted.
  • the two first horizontal through-holes 61 and the two second horizontal through-holes 62 have horizontal positions different from each other.
  • a refrigerant can be supplied to the outflow-side region 63 from a plurality of points not only having vertical positions different from each other but also having horizontal positions different from each other of the first chamber 71.
  • a refrigerant can be supplied to the outflow-side region 63 from a plurality of points not only having vertical positions different from each other but also having horizontal positions different from each other of the second chamber 72. For this reason, the homogenization of a gas-liquid ratio of a refrigerant in the outflow-side region 63 as a whole can be further achieved.
  • a heat exchanger 90 according to a third embodiment of the invention will be described with reference to Figs. 7 and 8 .
  • the same configuration elements as the first embodiment will be assigned with the same reference signs as the first embodiment, and the detailed description thereof will be omitted.
  • the heat exchanger 90 of the third embodiment is different from the first embodiment in that a first chamber partition plate 91 and a second chamber vertical partition plate 95 are further included.
  • a first chamber vertical partition plate 91 is a plate-shaped member extending in the vertical direction, and is disposed in the first chamber 71.
  • the first chamber vertical partition plate 91 partitions the first chamber 71 into two regions, in horizontal sectional view. Out of the two regions, a region on a side to which the connection pipe 55 is connected is set as a first chamber upstream region 93, and a region facing the main vertical partition plate 60 is set as a first chamber downstream region 94.
  • the first chamber vertical partition plate 91 is disposed so as to extend in parallel with the main vertical partition plate 60.
  • a third horizontal through-hole 92 that allows the first chamber upstream region 93 to communicate with the first chamber downstream region 94 is formed in the first chamber vertical partition plate 91.
  • the third horizontal through-hole 92 is formed to have a position in vertical direction different from that of the first horizontal through-hole 61 formed in the main vertical partition plate 60.
  • the third horizontal through-hole 92 is formed below the first horizontal through-hole 61.
  • 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 in the radially inside of the second header part 53
  • the third horizontal through-hole 92 is formed in the radially outside of the second header part 53.
  • the second chamber vertical partition plate 95 is a plate-shaped member extending in the vertical direction, and is disposed in the second chamber 72.
  • the second chamber vertical partition plate 95 partitions the second chamber 72 into two regions, in horizontal sectional view. Out of the two regions, a region on the side to which the connection pipe 55 is connected is set as a second chamber upstream region 97, and a region facing the main vertical partition plate 60 is set as a 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 as the first chamber vertical partition plate 91.
  • a fourth horizontal through-hole 96 that allows the second chamber upstream region 97 to communicate with the second chamber downstream region 98 is formed in the second chamber vertical partition plate 95.
  • the fourth horizontal through-hole 96 is formed to have a position in vertical direction different from that of the second horizontal through-hole 62 formed in the main vertical partition plate 60. In the embodiment, the fourth horizontal through-hole 96 is formed above the second horizontal through-hole 62.
  • 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 in the radially inside of the second header part 53
  • the fourth horizontal through-hole 96 is formed in the radially outside of the second header part 53.
  • a refrigerant supplied to the first chamber 71 proceeds while moving in the first chamber upstream region 93 and the first chamber downstream region 94 in the vertical direction before reaching the outflow-side region 63.
  • a refrigerant supplied to the second chamber 72 proceeds while moving in the second chamber upstream region 97 and the second chamber downstream region 98 in the vertical direction before reaching the outflow-side region 63. Consequently, a moving route to the outflow-side region 63 for a refrigerant introduced in the first chamber 71 and the second chamber 72 can be made longer. For this reason, the homogenization of a gas-liquid two phase type refrigerant on the moving route can be further achieved.
  • the first chamber vertical partition plate 91 and the second chamber vertical partition plate 95 may be disposed in the first chamber 71 and the second chamber 72 respectively so as to be in the radial direction of the second header part 53, as illustrated in Fig. 9 .
  • the moving route for a refrigerant can be made longer as described above.
  • a heat exchanger 100 according to a fourth embodiment of the invention will be described with reference to Figs. 10 and 11 .
  • the same configuration elements as the first embodiment will be assigned with the same reference signs as the first embodiment, and the detailed description thereof will be omitted.
  • the heat exchanger 100 of the fourth embodiment is different from the first embodiment in that a first chamber horizontal partition plate 101 and a second chamber horizontal partition plate 105 are further included.
  • the first chamber horizontal partition plate 101 is a plate-shaped member extending in the horizontal direction, and is disposed in the first chamber 71.
  • the first chamber horizontal partition plate 101 partitions the inside of the first chamber 71 into two upper and lower regions. Out of the two regions, a lower region connected to the connection pipe 55 is set as a first chamber lower region 103, and an upper region is set as a first chamber upper region 104.
  • a first vertical through-hole 102 that allows the first chamber lower region 103 to communicate with the first chamber upper region 104 is formed in the first chamber horizontal partition plate 101.
  • the second chamber horizontal partition plate 105 is a plate-shaped member extending in the horizontal direction, and is disposed in the second chamber 72.
  • the second chamber horizontal partition plate 105 partitions the inside of the second chamber 72 into two upper and lower regions. Out of the two regions, a lower region connected to the connection pipe 55 is set as a second chamber lower region 107, and an upper region is set as a second chamber upper region 108.
  • a second vertical through-hole 106 that allows the second chamber lower region 107 to communicate with the second chamber upper region 108 is formed in the second chamber horizontal partition plate 105.
  • the first horizontal through-hole 61 formed in the main vertical partition plate 60 allows the first chamber lower region 103 to communicate with the outflow-side region 63.
  • the second horizontal through-hole 62 formed in the main vertical partition plate 60 allows the second chamber upper region 108 to communicate with the outflow-side region 63.
  • the first vertical through-hole 102 is formed in the first chamber horizontal partition plate 101 in the embodiment, the first vertical through-hole may not necessarily be formed. If the first vertical through-hole 102 is formed, there is an advantage in that a refrigerant can be temporarily stored in the first chamber upper region 104, for example, in a case where the flow rate of the refrigerant is relatively high. There is another advantage in that a pressure resistance can be improved by reducing an internal pressure difference between the first chamber upper region 104 and other regions.
  • a 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 part 53 so as to straddle the first chamber 71 and the second chamber 72 in the first to fourth embodiments
  • two connection pipes 55 are connected to the second header part 53 in the embodiment.
  • Each of the connection pipes 55 is also connected to the first header part 52, and the inside of each of the connection pipes is set as a communication passage. Even in this case, a refrigerant can be forcibly introduced into the first chamber 71 and the second chamber 72 as in the first to fourth embodiments.
  • the flow rate of a refrigerant introduced into each of the first chamber 71 and the second chamber 72 can be adjusted as appropriate by changing the flow path sectional areas of the connection pipes 55 as appropriate.
  • the optimization of a heat exchange rate of a refrigerant with a different flow rate can also be achieved by intentionally introducing a refrigerant with a different gas-liquid ratio into each of the connection pipes 55.
EP17759461.1A 2016-02-29 2017-01-23 Échangeur de chaleur et climatiseur Withdrawn EP3425320A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016038354A JP6202451B2 (ja) 2016-02-29 2016-02-29 熱交換器及び空気調和機
PCT/JP2017/002082 WO2017149989A1 (fr) 2016-02-29 2017-01-23 Échangeur de chaleur et climatiseur

Publications (2)

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EP3425320A1 true EP3425320A1 (fr) 2019-01-09
EP3425320A4 EP3425320A4 (fr) 2020-04-01

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EP (1) EP3425320A4 (fr)
JP (1) JP6202451B2 (fr)
WO (1) WO2017149989A1 (fr)

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EP3922941A4 (fr) * 2019-02-04 2022-02-16 Mitsubishi Electric Corporation Échangeur de chaleur et conditionneur d'air équipé de celui-ci
AU2020255434B2 (en) * 2019-03-29 2022-09-15 Fujitsu General Limited Heat exchanger
EP4130612A4 (fr) * 2020-03-27 2023-04-26 Mitsubishi Electric Corporation Échangeur de chaleur, unité d'échangeur de chaleur et dispositif à cycle frigorifique
WO2023222613A1 (fr) * 2022-05-16 2023-11-23 Valeo Klimasysteme Gmbh Échangeur de chaleur pour véhicule automobile
EP4130637A4 (fr) * 2020-03-23 2024-03-27 Fujitsu General Ltd Échangeur de chaleur
EP4130639A4 (fr) * 2020-03-24 2024-03-27 Fujitsu General Ltd Échangeur de chaleur

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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
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AU2020255434B2 (en) * 2019-03-29 2022-09-15 Fujitsu General Limited Heat exchanger
US11846472B2 (en) 2019-03-29 2023-12-19 Fujitsu General Limited Heat exchanger
EP4130637A4 (fr) * 2020-03-23 2024-03-27 Fujitsu General Ltd Échangeur de chaleur
EP4130639A4 (fr) * 2020-03-24 2024-03-27 Fujitsu General Ltd Échangeur de chaleur
EP4130612A4 (fr) * 2020-03-27 2023-04-26 Mitsubishi Electric Corporation Échangeur de chaleur, unité d'échangeur de chaleur et dispositif à cycle frigorifique
WO2023222613A1 (fr) * 2022-05-16 2023-11-23 Valeo Klimasysteme Gmbh Échangeur de chaleur pour véhicule automobile

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EP3425320A4 (fr) 2020-04-01
JP2017155992A (ja) 2017-09-07
JP6202451B2 (ja) 2017-09-27

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