WO2019167312A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2019167312A1
WO2019167312A1 PCT/JP2018/032413 JP2018032413W WO2019167312A1 WO 2019167312 A1 WO2019167312 A1 WO 2019167312A1 JP 2018032413 W JP2018032413 W JP 2018032413W WO 2019167312 A1 WO2019167312 A1 WO 2019167312A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchange
header pipe
exchange unit
header
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/032413
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English (en)
Japanese (ja)
Inventor
円 上野
野衣 浅地
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.)
Sharp Corp
Original Assignee
Sharp Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sharp Corp filed Critical Sharp Corp
Priority to JP2020502791A priority Critical patent/JPWO2019167312A1/ja
Publication of WO2019167312A1 publication Critical patent/WO2019167312A1/fr
Anticipated expiration legal-status Critical
Priority to JP2022146227A priority patent/JP7376654B2/ja
Ceased 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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

Definitions

  • the present invention relates to a heat exchanger.
  • the heat exchanger described in Patent Document 1 includes a plurality of flat tubes, a cylindrical hollow upper header, and a cylindrical hollow lower header.
  • the plurality of flat tubes are arranged such that the longitudinal direction is inclined with respect to the vertical direction.
  • An upper header and a lower header are connected to both ends of each flat tube.
  • Each of the upper header and the lower header is arranged such that the longitudinal direction is the horizontal direction.
  • Two inlet pipes are provided in the upper header.
  • One outlet pipe is provided in the lower header.
  • This invention is made
  • the objective is to provide the heat exchanger which can simplify piping of a refrigerant
  • the heat exchanger includes a first heat exchange unit that performs heat exchange.
  • the first heat exchange unit includes a plurality of first flat tubes, a plurality of second flat tubes, a first header tube, a second header tube, and a third header tube.
  • Each of the plurality of first flat tubes extends along the first direction, and the plurality of first flat tubes are arranged along a second direction orthogonal to the first direction.
  • Each of the plurality of second flat tubes extends along the first direction, and the plurality of second flat tubes are arranged along the second direction.
  • the first header pipe is connected to one end of the plurality of first flat pipes in the first direction and extends along the second direction.
  • the second header pipe is connected to the other end in the first direction of the plurality of first flat tubes and one end of the plurality of second flat tubes in the first direction, and extends along the second direction.
  • the third header pipe is connected to the other end of the plurality of second flat pipes in the first direction and extends along the second direction.
  • the second header pipe includes at least one refrigerant inflow portion into which a refrigerant flows from the outside of the first heat exchange unit, and at least one refrigerant outflow portion from which the refrigerant flows out of the first heat exchange unit.
  • FIG. 1 It is a perspective view which shows the air conditioner which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the air conditioner which concerns on Embodiment 1 typically. It is a figure which shows the 1st heat exchange unit of the air conditioner which concerns on Embodiment 1. FIG. It is a figure which shows the 2nd heat exchange unit of the air conditioner which concerns on Embodiment 1. FIG. It is a figure which shows typically piping in the heat exchanger of the air conditioner which concerns on Embodiment 1. FIG. It is a figure which shows typically the internal structure of the 1st heat exchange unit of the air conditioner which concerns on Embodiment 1. FIG. It is a top view which shows the heat exchanger and fan unit of the air conditioner which concern on Embodiment 1. FIG.
  • FIG. It is a top view which shows the heat exchanger and fan unit of the air conditioner which concern on Embodiment 2 of this invention. It is sectional drawing which shows the inside of the 2nd header pipe
  • FIG. It is a figure which shows typically the internal structure of the 1st heat exchange unit of the air conditioner concerning Embodiment 3 of this invention. It is a figure which shows typically the 1st heat exchange unit of the air conditioner which concerns on Embodiment 4 of this invention. It is a figure which shows typically the internal structure of the 1st heat exchange unit of the air conditioner concerning Embodiment 5 of this invention.
  • the X axis and the Y axis are substantially parallel to the horizontal direction
  • the Z axis is substantially parallel to the vertical direction
  • the X axis, the Y axis, and the Z axis are orthogonal to each other.
  • the positive direction of the Z axis indicates the upward direction
  • the negative direction of the Z axis indicates the downward direction.
  • FIG. 1 is a perspective view showing an air conditioner 100.
  • the air conditioner 100 performs air conditioning.
  • the air conditioner 100 is an indoor unit. Therefore, the air conditioner 100 is installed indoors.
  • the air conditioner 100 is connected to the outdoor unit by piping. And a refrigerant
  • coolant circulates between the air conditioner 100 and an outdoor unit through piping.
  • the outdoor unit is installed outside the room.
  • the outdoor unit includes a fan, a compressor, a heat exchanger, and various components such as a four-way valve.
  • the air conditioner 100 includes a housing 1 and a panel 3.
  • the panel 3 is supported by the housing 1 so that the posture of the panel 3 can be changed with respect to the housing 1.
  • the panel 3 is substantially plate-shaped and is curved in a convex shape toward the housing 1.
  • FIG. 2 is a cross-sectional view schematically showing the air conditioner 100.
  • the housing 1 of the air conditioner 100 has an inlet 10 and an outlet 13.
  • the suction port 10 is located at the lower part of the housing 1 and opens toward the lower side of the housing 1.
  • the air outlet 13 opens toward the panel 3.
  • the air conditioner 100 further includes a fan unit 5 and a heat exchanger 7.
  • the heat exchanger 7 is located downstream of the fan unit 5 in the air flow.
  • the fan unit 5 and the heat exchanger 7 are accommodated in the housing 1.
  • the fan unit 5 sucks the air W1 through the suction port 10 and sends the sucked air W1 to the outside through the air outlet 13.
  • the fan unit 5 sends out the sucked air W ⁇ b> 1 toward the heat exchanger 7.
  • the air W ⁇ b> 2 that has passed through the heat exchanger 7 passes through the air outlet 13 and is sent out toward the panel 3.
  • the heat exchanger 7 performs heat exchange. Specifically, the heat exchanger 7 includes a first heat exchange unit 9 and a second heat exchange unit 11. Each of the first heat exchange unit 9 and the second heat exchange unit 11 performs heat exchange. The first heat exchange unit 9 is located downstream of the second heat exchange unit 11 in the air flow.
  • FIG. 3 is a diagram showing the first heat exchange unit 9.
  • the first heat exchange unit 9 is viewed from the back.
  • the rear view indicates that the object is viewed from the direction VD1 in FIG.
  • the first heat exchange unit 9 is a parallel flow heat exchanger. Specifically, the first heat exchange unit 9 includes a first header tube 21, a second header tube 22, a third header tube 23, a plurality of first flat tubes 31, and a plurality of second flat tubes 32. Including.
  • Each of the plurality of first flat tubes 31 extends along the first direction D1 and is aligned along the second direction D2.
  • the second direction D2 is orthogonal to the first direction D1.
  • the refrigerant flows through the plurality of first flat tubes 31.
  • each of the plurality of first flat tubes 31 has a plurality of refrigerant flow paths (not shown) arranged substantially parallel to each other.
  • Each of the plurality of second flat tubes 32 extends along the first direction D1 and is aligned along the second direction D2.
  • the refrigerant flows through the plurality of second flat tubes 32.
  • each of the plurality of second flat tubes 32 has a plurality of refrigerant flow paths (not shown) arranged substantially parallel to each other.
  • the first header pipe 21, the second header pipe 22, and the third header pipe 23 are disposed substantially parallel to each other.
  • the first header pipe 21 is substantially cylindrical.
  • the first header pipe 21 is connected to one end 31a of the plurality of first flat tubes 31 in the first direction D1.
  • the first header pipe 21 extends along the second direction D2.
  • a refrigerant flows through the first header pipe 21.
  • the first header pipe 21 does not have a refrigerant inflow portion where the refrigerant flows in from the outside of the first heat exchange unit 9 and a refrigerant outflow portion where the refrigerant flows out of the first heat exchange unit 9.
  • the second header tube 22 is substantially cylindrical.
  • the second header pipe 22 is connected to the other ends 31b of the plurality of first flat tubes 31 in the first direction D1 and one ends 32a of the plurality of second flat tubes 32 in the first direction D1.
  • the second header tube 22 extends along the second direction D2. The refrigerant flows through the second header pipe 22.
  • the second header pipe 22 includes at least one refrigerant inflow portion 25 and at least one refrigerant outflow portion 27.
  • the second header pipe 22 includes a plurality of refrigerant inflow portions 25 (specifically, two refrigerant inflow portions 25).
  • the refrigerant inflow portion 25 is substantially cylindrical.
  • the refrigerant flows into the refrigerant inflow portion 25 from the outside of the first heat exchange unit 9.
  • the second header pipe 22 includes a plurality of refrigerant outflow portions 27 (specifically, two refrigerant outflow portions 27).
  • the refrigerant outflow portion 27 is substantially cylindrical.
  • the refrigerant flows out of the first heat exchange unit 9 from the refrigerant outflow portion 27.
  • the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 are the same. Further, the refrigerant inflow portion 25 and the refrigerant outflow portion 27 are alternately arranged.
  • the third header tube 23 is substantially cylindrical.
  • the third header tube 23 is connected to the other end 32b of the plurality of second flat tubes 32 in the first direction D1.
  • the third header tube 23 extends along the second direction D2.
  • the refrigerant flows through the third header pipe 23.
  • the third header pipe 23 does not have a refrigerant inflow portion into which refrigerant flows from the outside of the first heat exchange unit 9 and a refrigerant outflow portion from which refrigerant flows out of the first heat exchange unit 9.
  • the first header tube 21, the plurality of first flat tubes 31, and the second header tube 22 constitute one heat exchange unit 31 ⁇ / b> X.
  • the third header tube 23, the plurality of second flat tubes 32, and the second header tube 22 constitute one heat exchanging portion 32X. Therefore, compared with the case where a heat exchange unit has one heat exchange part, the 1st heat exchange unit 9 can increase the amount of heat exchange. That is, the heat exchanger 7 can increase the heat exchange amount.
  • the heat exchange amount is the total amount of heat exchanged per unit time.
  • the refrigerant inflow portion 25 and the refrigerant outflow portion 27 are formed by the heat exchange portion 31X and the heat exchange portion 32X. 27 is shared. Therefore, the refrigerant piping in the heat exchanger 7 can be simplified as compared with the case where two parallel flow heat exchangers are provided.
  • the heat exchanger 7 can simplify the piping of the refrigerant while increasing the amount of heat exchange.
  • both the refrigerant inflow portion 25 and the refrigerant outflow portion 27 are arranged in the second header pipe 22. Therefore, the temperature distribution of the first heat exchange unit 9 can be made uniform more easily than when the refrigerant inflow portion and the refrigerant outflow portion are arranged in the first header pipe 21 (that is, the end portion of the heat exchanger). Specifically, the refrigerant changes from a gas to a two-phase state and further from a two-phase state to a liquid during heating operation. In this case, the temperature of the gaseous refrigerant is high, and the temperature of the liquid refrigerant is relatively low.
  • the refrigerant inflow portion when the refrigerant inflow portion is disposed at the end of the heat exchanger, the temperature of the flat tube near the refrigerant inflow portion is high, and the temperature of the flat tube is relatively low in the central portion of the heat exchanger.
  • the refrigerant when there is a refrigerant inflow portion at the end of the heat exchanger, the refrigerant exchanges heat with the high temperature only at the end of the heat exchanger, so the temperature distribution of the heat exchanger can be non-uniform.
  • Embodiment 1 since the refrigerant
  • the amount of heat exchange can be increased by disposing the refrigerant inflow portion 25 in the second header pipe 22 located in the central portion of the first heat exchange unit 9.
  • the refrigerant flows into the first header pipe 21 and the third header pipe 23 from the central portion (that is, the second header pipe 22) of the first heat exchange unit 9, thereby A pressure loss can be made low compared with the case where a refrigerant
  • the pressure loss can be reduced to the same extent as when the number of flat tubes through which the refrigerant flows at a time is doubled.
  • pressure loss refers to a phenomenon in which the refrigerant pressure decreases due to flow path resistance when the refrigerant flows. The greater the flow rate or the narrower the flow path, the greater the pressure loss.
  • the heat exchanger 7 (the 1st heat exchange unit 9 and the 2nd heat exchange unit 11) is arrange
  • the temperature distribution of the heat exchanger 7 is close to the temperature distribution of the outlet 13.
  • the temperature distribution of the first heat exchange unit 9 is made uniform by disposing the refrigerant inflow portion 25 in the second header pipe 22 located at the center of the first heat exchange unit 9. As a result, air having a uniform temperature distribution is sent out from the air outlet 13 to improve the comfort of the user.
  • the first direction D1 in which the first flat tube 31 and the second flat tube 32 extend is substantially parallel to the horizontal direction. That is, the first flat tube 31 and the second flat tube 32 extend along the horizontal direction. Accordingly, the first heat exchange unit 9 functions as a side flow type parallel flow type heat exchanger.
  • FIG. 2 is orthogonal to the central axis AX1 of the first header pipe 21, the central axis AX2 of the second header pipe 22, and the central axis AX3 of the third header pipe 23. Further, the direction VD2 in FIG. 2 is parallel to the central axis AX1, the central axis AX2, and the central axis AX3.
  • the first heat exchange unit 9 may further include a plurality of first corrugated fins 41 and a plurality of second corrugated fins 42.
  • Each of the plurality of first corrugated fins 41 is disposed between the first flat tubes 31 adjacent to each other in the second direction D2.
  • Each of the plurality of first corrugated fins 41 has a shape bent into a waveform.
  • Each of the plurality of second corrugated fins 42 is disposed between the second flat tubes 32 adjacent to each other in the second direction D2.
  • Each of the plurality of second corrugated fins 42 has a shape bent into a waveform.
  • FIG. 4 is a diagram showing the second heat exchange unit 11.
  • the second heat exchange unit 11 exchanges thermal energy between air and the refrigerant.
  • the second heat exchange unit 11 is viewed from the back.
  • the second heat exchange unit 11 includes a first heat exchange unit 11A that performs heat exchange and a second heat exchange unit 11B that performs heat exchange.
  • Each of the first heat exchange unit 11A and the second heat exchange unit 11B is a fin-and-tube heat exchanger.
  • the first heat exchange unit 11A includes a plurality of substantially flat first fins 51 and a substantially cylindrical first pipe 61.
  • Each of the plurality of first fins 51 extends along the third direction D3 and is aligned along the fourth direction D4.
  • the fourth direction D4 is orthogonal to the third direction D3.
  • the third direction D3 and the first direction D1 are substantially orthogonal to each other.
  • the third direction D3 and the second direction D2 are substantially parallel to each other.
  • the fourth direction D4 and the first direction D1 are substantially parallel to each other. Accordingly, the fourth direction D4 is substantially parallel to the horizontal direction.
  • the first pipe 61 snakes through the plurality of first fins 51 in the fourth direction D4.
  • a refrigerant flows through the first pipe 61.
  • tube 61 contains 1st refrigerant
  • the refrigerant flows into the first refrigerant inflow part A1 from the outside of the first heat exchange part 11A. From the first refrigerant outflow part B1, the refrigerant flows out of the first heat exchange part 11A.
  • the second heat exchange unit 11B includes a plurality of substantially flat second fins 52 and a substantially cylindrical second pipe 62. Each of the plurality of second fins 52 extends along the third direction D3 and is aligned along the fourth direction D4.
  • the second pipe 62 snakes through the plurality of second fins 52 in the fourth direction D4.
  • the refrigerant flows through the second pipe 62.
  • the second pipe 62 includes a second refrigerant inflow portion A2 and a second refrigerant outflow portion B2.
  • the refrigerant flows into the second refrigerant inflow portion A2 from the outside of the second heat exchange portion 11B. From the second refrigerant outflow part B2, the refrigerant flows out to the outside of the second heat exchange part 11B.
  • FIG. 5 is a diagram schematically showing piping in the heat exchanger 7.
  • the first header tube 21, the third header tube 23, the first flat tube 31, and the second flat tube 32 are omitted for simplification of the drawing.
  • the heat exchanger 7 further includes a merging portion 71, a diverting portion 72, a tube 73, a tube 74, a tube 75, a tube 76, and a tube 77.
  • the pipe 77 is connected to the diversion unit 72.
  • the diverter 72 diverts the flow path of the pipe 77 and connects the pipe 77 to the pipe 78 and the pipe 79.
  • the pipe 78 is connected to one of the two refrigerant inflow parts 25 of the second header pipe 22, and the pipe 79 is connected to the other refrigerant inflow part 25.
  • One of the two refrigerant outflow portions 27 is connected to the pipe 76, and the other refrigerant outflow section 27 is connected to the pipe 75.
  • the pipe 75 and the pipe 76 are connected to the junction 71.
  • the junction 71 joins the flow paths of the pipe 75 and the pipe 76 to connect the pipe 75 and the pipe 76 to the pipe 74.
  • the pipe 74 is connected to the second refrigerant inflow part A2 of the second heat exchange part 11B.
  • the second refrigerant outflow part B ⁇ b> 2 is connected to one end of the pipe 73.
  • the other end of the pipe 73 is connected to the first refrigerant inflow portion A1 of the first heat exchange portion 11A.
  • the second refrigerant outflow portion B2 and the first refrigerant inflow portion A1 are connected.
  • the refrigerant flow during the heating operation will be described with reference to FIG. As shown in FIG. 5, during the heating operation, the refrigerant AR1 flows from the first heat exchange unit 9 to the second heat exchange unit 11.
  • the refrigerant AR1 from the outside of the heat exchanger 7 flows from the pipe 77 into the flow dividing section 72. Then, the refrigerant AR1 is diverted by the diverter 72 and flows into the refrigerant inflow part 25 of the first heat exchange unit 9. Then, the refrigerant AR1 flows out from the refrigerant outflow portion 27 via the heat exchanging portion 31X and the heat exchanging portion 32X. Furthermore, the refrigerant AR1 is merged by the merge section 71 and flows into the second refrigerant inflow section A2 of the second heat exchange section 11B.
  • the refrigerant AR1 flows out from the second refrigerant outflow portion B2 via the second pipe 62, and flows into the first refrigerant inflow portion A1 of the first heat exchange portion 11A. Further, the refrigerant AR1 flows out from the first refrigerant outflow portion B1 via the first pipe 61.
  • the flow of the refrigerant during the cooling operation will be described. As shown in FIG. 5, during the cooling operation, the refrigerant AR2 flows from the second heat exchange unit 11 to the first heat exchange unit 9.
  • the refrigerant AR2 from the outside of the heat exchanger 7 flows into the first refrigerant outflow part B1 of the first heat exchange part 11A. Accordingly, the first refrigerant outflow portion B1 functions as an “inflow portion”. Then, the refrigerant AR2 flows out from the first refrigerant inflow portion A1 via the first pipe 61. Accordingly, the first refrigerant inflow portion A1 functions as an “outflow portion”. Furthermore, the refrigerant AR2 flows into the second refrigerant outflow part B2 of the second heat exchange part 11B via the pipe 73. Accordingly, the second refrigerant outflow portion B2 functions as an “inflow portion”. Further, the refrigerant AR2 flows out from the second refrigerant inflow portion A2 via the second pipe 62. Accordingly, the second refrigerant inflow portion A2 functions as an “outflow portion”.
  • the refrigerant AR2 is diverted by the merging portion 71 and flows into the refrigerant outflow portion 27 of the first heat exchange unit 9. Therefore, the merging portion 71 functions as a “distribution portion” and the refrigerant outflow portion 27 functions as an “inflow portion”. Furthermore, the refrigerant AR2 flows out of the refrigerant inflow part 25 via the heat exchange part 31X and the heat exchange part 32X. Accordingly, the refrigerant inflow portion 25 functions as an “outflow portion”. Further, the refrigerant AR ⁇ b> 2 is merged by the diverter 72 and flows out from the pipe 77. Therefore, the diversion part 72 functions as a “merging part”.
  • FIG. 6 is a diagram schematically showing the internal structure of the first heat exchange unit 9.
  • the flow of the refrigerant in the first heat exchange unit 9 during the heating operation is indicated by “arrows”.
  • the plurality of first flat tubes 31 are represented as “block BL11 and block BL21”.
  • the plurality of second flat tubes 32 are represented as “block BL12 and block BL22”.
  • the first header pipe 21 of the first heat exchange unit 9 includes at least one partition plate 211.
  • the partition plate 211 partitions the internal space of the first header pipe 21 and divides the internal space of the first header pipe 21 into two in the second direction D2.
  • the second header pipe 22 includes a plurality of partition plates 220.
  • the second header pipe 22 includes three partition plates 220.
  • the three partition plates 220 partition the internal space of the second header pipe 22 and divide the internal space of the second header pipe 22 into four in the second direction D2.
  • the third header pipe 23 includes at least one partition plate 231.
  • the partition plate 231 partitions the internal space of the third header pipe 23 and divides the internal space of the third header pipe 23 in the second direction D2.
  • the refrigerant flowing from the refrigerant inflow portion 25 of the second header pipe 22 flows through the block BL11 of the heat exchange section 31X, turns at the first header pipe 21, and flows into the block BL21. Then, the refrigerant flows through the block BL21 and flows out from the refrigerant outflow portion 27.
  • the refrigerant flowing in from the refrigerant inflow portion 25 flows through the block BL12 of the heat exchange portion 32X, turns at the third header pipe 23, and flows into the block BL22. Then, the refrigerant flows through the block BL22 and flows out from the refrigerant outflow portion 27.
  • the refrigerant flows in the opposite direction to that in the heating operation.
  • FIG. 7 is a top view showing the heat exchanger 7 and the fan unit 5.
  • the heat exchanger 7 and the fan unit 5 are viewed from above.
  • the top view indicates that the object is viewed from the direction VD2 in FIG.
  • the first header pipe 21, the second header pipe 22, and the third header pipe 23 are arranged on a straight line.
  • One end 31 c of the first flat tube 31 in the first direction D ⁇ b> 1 protrudes into the internal space of the first header tube 21.
  • the other end 31 d of the first flat tube 31 in the first direction D ⁇ b> 1 protrudes into the internal space of the second header tube 22.
  • the one end portion 32 c of the second flat tube 32 in the first direction D ⁇ b> 1 protrudes into the internal space of the second header tube 22.
  • the other end 32 d of the second flat tube 32 in the first direction D ⁇ b> 1 protrudes into the internal space of the third header tube 23.
  • the base end portion 25 a of the refrigerant inflow portion 25 and the base end portion 27 a of the refrigerant outflow portion 27 protrude into the internal space of the second header pipe 22.
  • the number of heat exchange parts (first heat exchange part 11A and second heat exchange part 11B) of the second heat exchange unit 11 is the same as the number of heat exchange parts (heat exchange part 31X and heat exchange part 32X) of the first heat exchange unit 9. Is the same as
  • the first heat exchange unit 11A faces the heat exchange unit 31X of the first heat exchange unit 9. Accordingly, the first heat exchanging portion 11 ⁇ / b> A faces the plurality of first flat tubes 31 connected to the first header tube 21 and the second header tube 22.
  • the second heat exchange unit 11B faces the heat exchange unit 32X of the first heat exchange unit 9. Accordingly, the second heat exchanging portion 11 ⁇ / b> B faces a plurality of second flat tubes 32 connected to the second header tube 22 and the third header tube 23.
  • the first refrigerant inflow portion A1 and the first refrigerant outflow portion B1 are directed in the direction from the first header pipe 21 toward the second header pipe 22. That is, the first refrigerant inflow portion A1 and the first refrigerant outflow portion B1 are disposed on the second header tube 22 side with respect to the first header tube 21.
  • the second refrigerant inflow portion A2 and the second refrigerant outflow portion B2 face the direction from the third header pipe 23 toward the second header pipe 22. That is, the second refrigerant inflow portion A ⁇ b> 2 and the second refrigerant outflow portion B ⁇ b> 2 are arranged on the second header tube 22 side with respect to the third header tube 23.
  • first refrigerant inflow portion A1 and the first refrigerant outflow portion B1 and the second refrigerant inflow portion A2 and the second refrigerant outflow portion B2 face each other.
  • first refrigerant inflow portion A1 and the first refrigerant outflow portion B1, and the second refrigerant inflow portion A2 and the second refrigerant outflow portion B2 are located in the vicinity of the refrigerant inflow portion 25 and the refrigerant outflow portion 27.
  • Embodiment 1 compared with the case where 1st refrigerant
  • the inner diameter of the refrigerant inflow portion 25 that functions as the “outflow portion” of the refrigerant in the first heat exchange unit 9 during the cooling operation is equal to the inner diameter of the first pipe 61 of the first heat exchange portion 11A and the second It is larger than each of the inner diameters of the second tubes 62 of the heat exchange unit 11B. Therefore, the pressure loss of the refrigerant during the cooling operation can be reduced.
  • the refrigerant in the “outflow part” of the refrigerant during the cooling operation, the refrigerant is a gas, and thus the flow rate of the refrigerant is large. The greater the flow rate or the narrower the flow path, the greater the pressure loss. As a result, the pressure loss of the refrigerant increases at the “outflow portion” during the cooling operation. Therefore, in the first embodiment, the refrigerant pressure loss is reduced by increasing the inner diameter of the refrigerant inflow portion 25 that functions as an “outflow portion” of the refrigerant during the cooling operation. Note that the inner diameter of the refrigerant inflow portion 25 is not particularly limited as long as the refrigerant flows through the refrigerant inflow portion 25.
  • the inner diameter of the second header pipe 22 is larger than each of the inner diameter of the first header pipe 21 and the inner diameter of the third header pipe 23. Therefore, according to the first embodiment, it is possible to increase the inner diameter of the refrigerant inflow portion 25 that functions as the “outflow portion” of the refrigerant during the cooling operation. As a result, the pressure loss of the refrigerant during the cooling operation can be reduced.
  • the second header tube 22 a sufficient area can be easily secured for connecting both the first flat tube 31 and the second flat tube 32.
  • the inner diameter of the second header tube 22 is not particularly limited as long as both the first flat tube 31 and the second flat tube 32 can be connected to the second header tube 22.
  • the fan unit 5 includes a fan 5A and a fan 5B.
  • Each of the fan 5A and the fan 5B is, for example, a cross flow fan.
  • the number of fans (fan 5A and fan 5B) of the fan unit 5 is the same as the number of heat exchange parts (first heat exchange part 11A and second heat exchange part 11B) of the second heat exchange unit 11.
  • the fan 5A faces the first heat exchange part 11A.
  • the fan 5A sucks in the air W1 and sends out the sucked air W1 toward the first heat exchange unit 11A.
  • the air W2 is sent out toward the air outlet 13 through the first heat exchange unit 11A and the heat exchange unit 31X.
  • the fan 5B is opposed to the second heat exchange unit 11B.
  • the fan 5B sucks in the air W1, and sends out the sucked air W1 toward the second heat exchange unit 11B.
  • the air W2 is sent out toward the outlet 13 through the second heat exchange unit 11B and the heat exchange unit 32X.
  • Embodiment 2 With reference to FIG.8 and FIG.9, the heat exchanger 7 which concerns on Embodiment 2 of this invention is demonstrated.
  • the second embodiment is that the second header pipe 22 of the heat exchanger 7 according to the second embodiment is disposed on the second heat exchange unit 11 side with respect to the first header pipe 21 and the third header pipe 23 in a top view. 2 is mainly different from the first embodiment.
  • the points of the second embodiment different from the first embodiment will be mainly described.
  • FIG. 8 is a top view showing the heat exchanger 7 and the fan unit 5 according to the second embodiment.
  • the heat exchanger 7 and the fan unit 5 are viewed from above.
  • the central axis AX2 of the second header pipe 22 of the first heat exchange unit 9A is the central axis AX1 of the first header pipe 21 and the central axis AX3 of the third header pipe 23.
  • tube 23 are arrange
  • the second header pipe 22 even if the outer diameter of the second header pipe 22 is larger than each of the outer diameter of the first header pipe 21 and the outer diameter of the third header pipe 23, the second header pipe 22 It can suppress that 22 protrudes in the downstream of the flow of air with respect to the 1st header pipe
  • the line LN is a line segment connecting the most downstream end of the first header pipe 21 and the most downstream end of the third header pipe 23.
  • the central axis AX2 of the second header pipe 22 is exchanged with the first heat exchange part 11A and the second heat exchange with respect to the central axis AX1 of the first header pipe 21 and the central axis AX3 of the third header pipe 23.
  • the first header pipe 21, the second header pipe 22, and the third header pipe 23 are arranged so as to be located on the space SP side between the section 11B.
  • FIG. 9 is a cross-sectional view showing the inside of the second header tube 22.
  • the inclination of the first flat tube 31 and the second flat tube 32 is shown larger than the first flat tube 31 and the second flat tube 32 of FIG.
  • the first flat tube 31 includes a refrigerant channel 311, a refrigerant channel 312, a refrigerant channel 313, a refrigerant channel 314, and a refrigerant channel 315.
  • the second flat tube 32 includes a refrigerant channel 321, a refrigerant channel 322, a refrigerant channel 323, a refrigerant channel 324, and a refrigerant channel 325.
  • the central axis AX2 of the second header pipe 22 is located on the second heat exchange unit 11 side with respect to the central axis AX1 and the central axis AX3. Accordingly, each of the end surface 316 of the first flat tube 31 and the end surface 326 of the second flat tube 32 is inclined with respect to the inflow direction of the refrigerant CM so as to spread toward the refrigerant inflow portion 25.
  • the refrigerant flow path 321 is compared with the case where each of the end surface 316 of the first flat tube 31 and the end surface 326 of the second flat tube 32 is substantially parallel to the inflow direction of the refrigerant CM.
  • the refrigerant CM can effectively flow into the refrigerant channel 325 and the refrigerant channel 321 to the refrigerant channel 325.
  • Embodiment 3 With reference to FIG. 10, the heat exchanger 7 which concerns on Embodiment 3 of this invention is demonstrated.
  • the third embodiment is mainly different from the first embodiment in that the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 of the second header pipe 22 of the heat exchanger 7 according to the third embodiment are different.
  • the points of the third embodiment different from the first embodiment will be mainly described.
  • FIG. 10 is a diagram schematically showing the internal structure of the first heat exchange unit 9B of the heat exchanger 7 according to the third embodiment.
  • the flow of the refrigerant in the first heat exchange unit 9B during the heating operation is indicated by “arrows”.
  • the plurality of first flat tubes 31 are represented as “block BL11a, block BL21a, block BL11b, and block BL21b”.
  • the plurality of second flat tubes 32 are represented as “block BL12a, block BL22a, block BL12b, and block BL22b”.
  • the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 of the second header pipe 22 are different. Therefore, compared with the case where the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 are the same, the number of tubes connected to the refrigerant inflow portion 25 or the number of tubes connected to the refrigerant outflow portion 27 is reduced. Can be reduced. As a result, the piping can be further simplified.
  • the number of refrigerant outflow portions 27 is smaller than the number of refrigerant inflow portions 25.
  • the second header pipe 22 has two refrigerant inflow portions 25 and one refrigerant outflow portion 27. Therefore, the number of pipes connected to the refrigerant outflow portion 27 can be reduced.
  • any one of the pipe 75 and the pipe 76 may be provided, and the joining portion 71 may not be provided.
  • the number of the refrigerant inflow portions 25 is smaller than the number of the refrigerant outflow portions 27, the number of pipes connected to the refrigerant inflow portion 25 can be reduced.
  • the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 of the second header pipe 22 are different, the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 are the same.
  • the distance in the second direction D2 between the refrigerant inflow portion 25 and the refrigerant outflow portion 27 is increased. As a result, heat exchange loss can be suppressed and heat exchange by the first heat exchange unit 9 can be executed effectively.
  • the refrigerant is in an overheated state at the refrigerant inflow portion 25 of the second header pipe 22 during the heating operation.
  • the refrigerant is in a gas-liquid two-phase state at the refrigerant outflow portion 27 of the second header pipe 22. Therefore, by increasing the distance in the second direction D2 between the refrigerant inflow portion 25 and the refrigerant outflow portion 27, heat exchange between the refrigerant in the refrigerant inflow portion 25 and the refrigerant in the refrigerant outflow portion 27 can be suppressed.
  • the heat exchange between the refrigerant in the refrigerant inflow portion 25 and the refrigerant in the refrigerant outflow portion 27 is not heat exchange to be performed by the first heat exchange unit 9 but a heat exchange loss for the first heat exchange unit 9.
  • the heat exchange by the 1st heat exchange unit 9 can be performed effectively by suppressing the loss of heat exchange.
  • the second header tube 22 includes a plurality of partition plates 220.
  • the second header pipe 22 includes two partition plates 220. The two partition plates 220 partition the internal space of the second header tube 22 and divide the internal space of the second header tube 22 into three in the second direction D2.
  • the refrigerant that has flowed from one of the two refrigerant inflow portions 25 flows through the block BL11a of the heat exchange portion 31X, turns at the first header pipe 21, and flows into the block BL21a. Then, the refrigerant flows through the block BL21a and flows out from one refrigerant outflow portion 27.
  • the refrigerant flowing in from the other refrigerant inflow portion 25 flows through the block BL11b of the heat exchanging portion 31X, turns at the first header pipe 21, and flows into the block BL21b. Then, the refrigerant flows through the block BL21b and flows out from one refrigerant outflow portion 27. Therefore, the refrigerant flowing from the two refrigerant inflow portions 25 and flowing through the heat exchanging portion 31 ⁇ / b> X shares one refrigerant outflow portion 27.
  • the refrigerant flowing from one of the two refrigerant inflow portions 25 flows through the block BL12a of the heat exchanging portion 32X, turns at the third header pipe 23, and flows into the block BL22a. Then, the refrigerant flows through the block BL22a and flows out from one refrigerant outflow portion 27.
  • the refrigerant flowing in from the other refrigerant inflow portion 25 flows through the block BL12b of the heat exchanging portion 32X, turns at the third header pipe 23, and flows into the block BL22b. Then, the refrigerant flows through the block BL22b and flows out from one refrigerant outflow portion 27. Therefore, the refrigerant flowing from the two refrigerant inflow portions 25 and flowing through the heat exchanging portion 32 ⁇ / b> X shares one refrigerant outflow portion 27.
  • the refrigerant flowing in from the two refrigerant inflow portions 25 is one refrigerant outflow portion 27 located between the two refrigerant inflow portions 25. Is shared.
  • the refrigerant flows in the opposite direction to that in the heating operation.
  • the fourth embodiment is the third embodiment in that the first heat exchange unit 9C of the heat exchanger 7 according to the fourth embodiment has a first plate member 81 and a second plate member 82 extending along the first direction D1. And mainly different.
  • the points of the fourth embodiment different from the third embodiment will be mainly described.
  • FIG. 11 is a diagram schematically illustrating the first heat exchange unit 9C of the heat exchanger 7 according to the fourth embodiment.
  • the first heat exchange unit 9C is viewed from the back. Further, the first corrugated fins 41 and the second corrugated fins 42 are omitted for simplification of the drawing.
  • the first heat exchange unit 9C of the heat exchanger 7 further includes a first plate member 81 and a second plate member 82.
  • the first plate-like member 81 extends along the first direction D1 from the second header pipe 22 to the first header pipe 21.
  • the first plate member 81 is disposed instead of the first flat tube 31 proximate to the refrigerant outflow portion 27, the first plate member 81 is disposed. Therefore, the first plate member 81 is disposed between the two first flat tubes 31.
  • the first plate member 81 does not have a refrigerant flow path.
  • the second plate-like member 82 extends from the second header pipe 22 to the third header pipe 23 along the first direction D1.
  • the second plate member 82 is disposed instead of the second flat tube 32 adjacent to the refrigerant outflow portion 27, the second plate member 82 is disposed. Accordingly, the second plate member 82 is disposed between the two second flat tubes 32. The second plate-like member 82 does not have a refrigerant flow path.
  • the distance d1 between the two first flat tubes 31 sandwiching the first plate-like member 81 is larger than the pitch p1 of the other first flat tubes 31. can do.
  • the distance d2 between the two second flat tubes 32 sandwiching the second plate-like member 82 can be made larger than the pitch p2 of the other second flat tubes 32. it can.
  • the base end portion 27 a (FIG. 7) of the refrigerant outflow portion 27 includes the end portion 31 d (FIG. 7) of the first flat tube 31 and the end portion 32 c ( It is possible to easily suppress contact with FIG. As a result, the outer diameter and inner diameter of the refrigerant outflow portion 27 can be easily increased.
  • the fourth embodiment by providing the first plate-like member 81, the side closer to the refrigerant outflow portion 27 that functions as the “inflow portion” among the plurality of first flat tubes 31 during the cooling operation. It can suppress that the flow volume of the refrigerant
  • the second flat tube 32 on the side close to the refrigerant outflow portion 27 that functions as an “inflow portion” among the plurality of second flat tubes 32 during the cooling operation, It is possible to prevent the flow rate of the refrigerant flowing into the second flat tube 32 from becoming uneven with the second flat tube 32 on the far side.
  • first flat tube 31Q when the first flat tube 31 (hereinafter, referred to as “first flat tube 31Q”) is disposed at the position of the first plate-like member 81, the first flat tube 31Q serves as a refrigerant outflow portion. 27. Therefore, during the cooling operation, a larger amount of refrigerant may flow into the first flat tube 31Q from the refrigerant outflow portion 27 functioning as the “inflow portion” than the refrigerant flowing into the other first flat tube 31. There is.
  • the first plate member 81, the second plate member 82, and the refrigerant outflow portion 27 of the second header pipe 22 are arranged as follows. That is, the refrigerant outflow portion 27 is close to the end portion 81 a of the first plate-like member 81 and the end portion 82 a of the second plate-like member 82.
  • the end portion 81 a of the first plate-like member 81 is an end portion on the second header tube 22 side among both end portions of the first plate-like member 81 in the first direction D1.
  • the end portion 82 a of the second plate-like member 82 is an end portion on the second header tube 22 side among both end portions of the second plate-like member 82 in the first direction D1.
  • the refrigerant outflow portion 27, the first plate-like member 81, and the second plate-like member 82 are arranged on a straight line in the rear view. That is, the position of the refrigerant outflow portion 27 in the second direction D2 is substantially equal to the position of the first plate member 81 in the second direction D2, and is substantially equal to the position of the second plate member 82 in the second direction D2. .
  • the coolant outlet 27, the end 81 a of the first plate member 81, and the end 82 a of the second plate member 82 are arranged on the same circumference in the second header tube 22.
  • the position and the number of the first plate-like member 81 are not particularly limited.
  • the 2nd plate-shaped member 82 is arrange
  • first plate-like members 81 and two second plate-like members 82 are arranged at positions different from the positions shown in FIG. 11, and each of the refrigerant inflow portions 25 of the second header pipe 22
  • the end portion 81a of the first plate member 81 and the end portion 82a of the second plate member 82 may be close to each other.
  • the outer diameter and inner diameter of the refrigerant inflow portion 25 can be easily increased.
  • the first flat tube 31 on the side closer to the refrigerant inflow portion 25 and the first flat tube 31 on the far side flow into the first flat tube 31. It can suppress that the flow volume of a refrigerant
  • the second flat tube 32 on the side close to the refrigerant inflow portion 25 and the second flat tube 32 on the far side flow into the second flat tube 32. It can suppress that the flow volume of the refrigerant
  • At least one of the refrigerant inflow portion 25 and the refrigerant outflow portion 27 of the second header pipe 22 is close to the end portion 81 a of the first plate member 81 and the end portion 82 a of the second plate member 82. Just do it.
  • the strength of the first heat exchange unit 9C can be improved.
  • Embodiment 5 With reference to FIG. 12, the heat exchanger 7 which concerns on Embodiment 5 of this invention is demonstrated.
  • the fifth embodiment is mainly different from the third embodiment in that the partition plate 220 of the first heat exchange unit 9D of the heat exchanger 7 according to the fifth embodiment is inclined.
  • the points of the fifth embodiment different from the third embodiment will be mainly described.
  • FIG. 12 is a diagram schematically showing the internal structure of the first heat exchange unit 9D of the heat exchanger 7 according to the fifth embodiment.
  • the flow of the refrigerant in the first heat exchange unit 9D during the heating operation is indicated by “arrows”.
  • the second header pipe 22 includes at least two partition plates 220 that partition the internal space of the second header pipe 22.
  • the at least two partition plates 220 are inclined so as to be separated from each other from the third header pipe 23 side toward the first header pipe 21 side.
  • the number N of the first flat tubes 31 included in the blocks BL21a and BL21b of the heat exchange unit 31X is different from the number M of the second flat tubes 32 included in the blocks BL22a and BL22b of the heat exchange unit 32X.
  • the number N of the first flat tubes 31 through which the refrigerant flows from the first header tube 21 toward the refrigerant outflow portion 27 is the number M of the second flat tubes 32 through which the refrigerant flows from the third header tube 23 toward the refrigerant outflow portion 27.
  • the flow resistance is large because air with a strong airflow passes, and in the region Q2 of the heat exchanging portion 32X, the airflow with weak airflow passes and the flow resistance is small.
  • the number N of flat tubes 31 is made larger than the number M of second flat tubes 32. As a result, the heat exchange efficiency in the first heat exchange unit 9D can be improved.
  • At least two partition plates 220 are inclined away from each other from the first header pipe 21 side toward the third header pipe 23 side.
  • the number N is larger than the number M of the second flat tubes 32.
  • the at least two partition plates 220 may be inclined so as to be separated from each other from the first header pipe 21 side toward the third header pipe 23 side.
  • the number M of the second flat tubes 32 is larger than the number N of the first flat tubes 31.
  • the heat exchanger 7 has the second heat exchange unit 11. However, the heat exchanger 7 performs the first heat exchange. As long as any of the units 9 to 9D is included, the heat exchanger 7 may not include the second heat exchange unit 11. In this case, the heat exchanger 7 may have, for example, one first heat exchange unit 9 or a plurality of first heat exchange units 9.
  • first heat exchange units 9 to 9D may be located upstream of the second heat exchange unit 11 in the air flow.
  • the refrigerant flows from the first heat exchange units 9 to 9D to the second heat exchange unit 11, During operation, the refrigerant flowed from the second heat exchange unit 11 to the first heat exchange units 9 to 9D. However, during the heating operation, the refrigerant flows from the second heat exchange unit 11 to the first heat exchange units 9 to 9D, and during the cooling operation, the refrigerant flows from the first heat exchange units 9 to 9D to the second heat exchange unit. 11 may flow.
  • the refrigerant inflow portion 25, the first refrigerant inflow portion A1, and the second refrigerant inflow portion A2 are “inflow portions” during the heating operation, but may be “inflow portions” during the cooling operation.
  • the refrigerant outflow portion 27, the first refrigerant outflow portion B1, and the second refrigerant outflow portion B2 are “outflow portions” during the heating operation, but may be “outflow portions” during the cooling operation. .
  • the partition plate 220 may be inclined as in the fifth embodiment described with reference to FIG.
  • the number of the refrigerant inflow portions 25 and the number of the refrigerant outflow portions 27 are different from each other as in the third to fifth embodiments. It may be allowed.
  • the refrigerant flows through the first heat exchange unit 11A after flowing through the second heat exchange unit 11B during the heating operation, and the refrigerant exchanges the first heat exchange during the cooling operation.
  • the refrigerant flows through the 2nd heat exchange part 11B after flowing through part 11A, how to flow a refrigerant is not specifically limited.
  • the refrigerant can flow in parallel to the first heat exchange unit 11A and the second heat exchange unit 11B.
  • it compares with one 2nd heat exchange unit (henceforth "2nd heat exchange unit EX") of the magnitude
  • the temperature drift between the heat exchanger 11B) can be suppressed.
  • the temperature drift is a phenomenon in which the refrigerant flows in one region and the other region while the temperature of the refrigerant is biased between the one region and the other region in the fourth direction D4 of the second heat exchange unit.
  • the refrigerant flows into the first refrigerant inflow portion A1 of the first heat exchange unit 11A, and the refrigerant flows into the second refrigerant inflow portion A2 of the second heat exchange unit 11B.
  • the refrigerant flows through the first heat exchange unit 11A and the second heat exchange unit 11B in parallel. That is, the refrigerant flows from the first refrigerant inflow portion A1 along the fourth direction D4 toward the one end in the fourth direction D4 of the second heat exchange unit 11, and from the first refrigerant outflow portion B1 while meandering. leak.
  • the refrigerant flows from the second refrigerant inflow portion A2 along the fourth direction D4 toward the other end in the fourth direction D4 of the second heat exchange unit 11, and from the second refrigerant outflow portion B2 while meandering. leak.
  • the refrigerant flows into the first refrigerant outflow part B1 of the first heat exchange unit 11A, and the refrigerant flows into the second refrigerant outflow part B2 of the second heat exchange unit 11B.
  • the refrigerant flows in parallel through the first heat exchange unit 11A and the second heat exchange unit 11B. That is, the refrigerant flows from the first refrigerant outflow portion B1 along the fourth direction D4 toward one end in the fourth direction D4 of the second heat exchange unit 11, and from the first refrigerant inflow portion A1 while meandering. leak.
  • the refrigerant flows from the second refrigerant outflow portion B2 along the fourth direction D4 toward the other end in the fourth direction D4 of the second heat exchange unit 11, and from the second refrigerant inflow portion A2 while meandering. leak.
  • the present invention provides a heat exchanger and has industrial applicability.

Landscapes

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

Abstract

L'invention concerne un échangeur de chaleur (7) qui comprend une première unité d'échange de chaleur (9) comprenant une pluralité de premiers tubes plats (31), une pluralité de seconds tubes plats (32), un premier tube collecteur (21), un deuxième tube collecteur (22) et un troisième tube collecteur (23). Le premier tube collecteur (21) est relié à une extrémité (31a), dans une première direction (D1), de chaque premier tube plat (31). Le deuxième tube collecteur (22) est relié à l'autre extrémité (31b), dans la première direction (D1), de chaque premier tube plat (31), et à une extrémité (32a), dans la première direction (D1), de chaque second tube plat (32). Le troisième tube collecteur (23) est relié à l'autre extrémité (32b), dans la première direction (D1), de chaque second tube plat (32). Le deuxième tube collecteur (22) comprend au moins une partie d'entrée (25) de fluide frigorigène dans laquelle coule un fluide frigorigène à partir de l'extérieur de la première unité d'échange de chaleur (11), et au moins une partie de sortie (25) de fluide frigorigène à partir de laquelle le fluide frigorigène coule vers l'extérieur de la première unité d'échange de chaleur (11).
PCT/JP2018/032413 2018-02-28 2018-08-31 Échangeur de chaleur Ceased WO2019167312A1 (fr)

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JP2020502791A JPWO2019167312A1 (ja) 2018-02-28 2018-08-31 熱交換器
JP2022146227A JP7376654B2 (ja) 2018-02-28 2022-09-14 熱交換器及び空気調和機

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JP2018-034796 2018-02-28
JP2018034796 2018-02-28

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WO2019167312A1 true WO2019167312A1 (fr) 2019-09-06

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JP7197255B2 (ja) * 2016-02-29 2022-12-27 三菱ケミカル株式会社 透明両面粘着シート及び粘着シート積層体

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JPH0213952U (fr) * 1988-07-11 1990-01-29
JPH0236769U (fr) * 1988-08-22 1990-03-09
JPH0674684A (ja) * 1992-08-31 1994-03-18 Showa Alum Corp 熱交換器
JPH09113154A (ja) * 1995-10-11 1997-05-02 Nippon Light Metal Co Ltd 熱交換器
JP2006214704A (ja) * 2005-02-07 2006-08-17 T Rad Co Ltd クロスフロー型ラジエータ
JP2010025456A (ja) * 2008-07-22 2010-02-04 Sharp Corp 熱交換器ユニット及びこれを使用する空気調和機の室内機
JP2013047585A (ja) * 2011-08-29 2013-03-07 Sanden Corp 熱交換器
JP2015230129A (ja) * 2014-06-05 2015-12-21 パナソニックＩｐマネジメント株式会社 熱交換器

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Publication number Priority date Publication date Assignee Title
JP2008249252A (ja) * 2007-03-30 2008-10-16 Denso Corp 熱交換装置
JP2009145009A (ja) * 2007-12-17 2009-07-02 Hitachi Appliances Inc 空気調和機
JP5079857B2 (ja) * 2010-09-16 2012-11-21 シャープ株式会社 空気調和機の室内機
DE112014007130T5 (de) * 2014-11-04 2017-07-20 Mitsubishi Electric Corporation Inneneinheit für eine Klimaanlage

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0213952U (fr) * 1988-07-11 1990-01-29
JPH0236769U (fr) * 1988-08-22 1990-03-09
JPH0674684A (ja) * 1992-08-31 1994-03-18 Showa Alum Corp 熱交換器
JPH09113154A (ja) * 1995-10-11 1997-05-02 Nippon Light Metal Co Ltd 熱交換器
JP2006214704A (ja) * 2005-02-07 2006-08-17 T Rad Co Ltd クロスフロー型ラジエータ
JP2010025456A (ja) * 2008-07-22 2010-02-04 Sharp Corp 熱交換器ユニット及びこれを使用する空気調和機の室内機
JP2013047585A (ja) * 2011-08-29 2013-03-07 Sanden Corp 熱交換器
JP2015230129A (ja) * 2014-06-05 2015-12-21 パナソニックＩｐマネジメント株式会社 熱交換器

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