EP3064880A1 - Collecteur stratifié, échangeur de chaleur, et appareil de climatisation - Google Patents

Collecteur stratifié, échangeur de chaleur, et appareil de climatisation Download PDF

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Publication number
EP3064880A1
EP3064880A1 EP13896215.4A EP13896215A EP3064880A1 EP 3064880 A1 EP3064880 A1 EP 3064880A1 EP 13896215 A EP13896215 A EP 13896215A EP 3064880 A1 EP3064880 A1 EP 3064880A1
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EP
European Patent Office
Prior art keywords
plate
tubes
stacking
bodies
opening ports
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.)
Granted
Application number
EP13896215.4A
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German (de)
English (en)
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EP3064880A4 (fr
EP3064880B1 (fr
Inventor
Takumi NISHIYAMA
Takashi Okazaki
Akira Ishibashi
Shinya Higashiiue
Shigeyoshi MATSUI
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3064880A1 publication Critical patent/EP3064880A1/fr
Publication of EP3064880A4 publication Critical patent/EP3064880A4/fr
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Publication of EP3064880B1 publication Critical patent/EP3064880B1/fr
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Classifications

    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to a stacking-type header, a heat exchanger, and an air-conditioning apparatus.
  • a conventionally-known heat exchanger has a return header including a tube joining member configured to join a flat tube and a member, a tube fixing member configured to position an end of the flat tube, a spacer section configured to move refrigerant in a row-wise direction, and a back board (e.g., see Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2013-29243 (paragraph [0033], Fig. 6 )
  • liquid refrigerant flowing out through the end of the flat tube to the spacer section comes to flow in a more laminar flow state, as the spacer section increases in space. This creates imbalances in the inflow of refrigerant from the spacer section into each separate flow passage hole of the flat tube, thus making it difficult to evenly distribute the refrigerant.
  • the present invention has been made to solve problems such as those described above. It is an object of the present invention to provide a stacking-type header connected to a plurality of tubes, configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, and configured to be able to reduce imbalances in the inflow of the fluid into the tube. Further, it is another object of the present invention to provide a heat exchanger including such a stacking-type header. Further, it is still another object of the present invention to provide an air-conditioning apparatus including such a heat exchanger.
  • a stacking-type header is a stacking-type header connected to a plurality of tubes and configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, including: a first plate-like body having first opening ports, each of the plurality of tubes being connected to the first opening ports of the first plate-like body, and a plurality of second plate-like bodies having second opening ports, the plurality of second plate-like bodies being stacked on the first plate-like body so that the second opening ports communicate with the first opening ports to form flow passages, in which each of the flow passages has a flow passage area that continuously or gradually changes in a stacking direction of the plurality of second plate-like bodies.
  • a stacking-type header is connected to a plurality of tubes, configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, and configured to be able to reduce imbalances in the inflow of the fluid into the tube.
  • a stacking-type header according to the present invention is applied to a heat exchanger. Note, however, that a stacking-type header according to the present invention may be applied to another device.
  • Fig. 1 is a side view schematically showing a configuration of a heat exchanger 1 according to Embodiment 1 of the present invention.
  • Fig. 2 is a top view schematically showing the configuration of the heat exchanger 1 according to Embodiment 1 of the present invention.
  • the heat exchanger 1 includes a stacking-type header 10, a plurality of flat tubes 20, and a plurality of fins 3.
  • the stacking-type header 10 to which an end of each flat tube 20 is connected, allows inflow of fluid (e.g., refrigerant) from one of the flat tubes 20 and inflow of the fluid into another one of the flat tubes 20.
  • fluid e.g., refrigerant
  • the stacking-type header 10 will be described in detail later.
  • the fins 3 are for example in the form of plates.
  • the fins 3 are stacked at predetermined intervals.
  • the fins 3 allow passage of a heat medium (e.g., air) therebetween.
  • the fins 3 are for example made of a metal material such as aluminum or copper.
  • the flat tubes 20 are flat in cross-section.
  • the flat tubes 20 are for example made of a metal material such as aluminum or copper.
  • the flat tubes 20 have flat shapes whose longer axes are oriented in a direction of passage of air.
  • the flat tubes 20 are placed at intervals along the short axes of the flat shapes.
  • the flat tubes 20 include plural columns of flat tubes 20 arranged in a column-wise direction crossing a direction of flow of air. Further, the flat tubes 20 include plural rows of flat tubes 20 arranged in a row-wise direction along the direction of flow of air.
  • Embodiment 1 describes a case where the flat tubes 20 include two rows of flat tubes 20.
  • the two rows of flat tubes 20 include a flat tube 20a through which the refrigerant flows into the stacking-type header 10 and a flat tube 20b through which the refrigerant flows out of the stacking-type header 10. It should be noted that the absence of the suffixes means that the content of descriptions is common to all of the flat tubes 20.
  • Fig. 3 is a schematic view showing a cross-section of each flat tube 20 of the heat exchanger 1 according to Embodiment 1 of the present invention.
  • the flat tube 20 has at least one divider provided therein to form a plurality of flow passages.
  • the tube height H21 is the short axis length of the flat tube 20
  • the tube width L22 is the long axis length of the flat tube 20
  • the tube thickness t23 is the length between the outer circumference of the flat tube 20 and the inner circumference of each flow passage.
  • the flat tubes 20 correspond to the "tubes" of the present invention.
  • Embodiment 1 describes a case where the flat tubes 20 are used, the present invention is not limited thereto and can use tubes of any shape such as circular tubes or rectangular or square tubes.
  • Fig. 4 is a schematic exploded perspective view showing the stacking-type header 10 of the heat exchanger 1 according to Embodiment 1 of the present invention.
  • Fig. 4 is also an enlarged view of part A of Fig. 1 .
  • the stacking-type header 10 includes a plurality of bare materials 11 and a plurality of clad materials 12.
  • the clad materials 12 are plate-like members coated with a brazing material.
  • the bare materials 11 are plate-like members coated with no brazing material.
  • the stacking-type header 10 is constituted by the bare materials 11 and the clad members 12 being alternately stacked.
  • the bare materials 11 and the clad materials 12 include a bare material 11 and a clad material 12 each having first opening ports 30 formed therethrough, bear materials 11 and clad materials 12 each having second opening ports 40 formed therethrough to communicate with the first opening ports 30, a bare material 11 and a clad material 12 each having third opening ports 50 formed therethrough to each communicate with a plurality of the second opening ports 40, and a bare material 11 having no opening port formed therethrough. All of these bear materials 11 and clad materials 12 are stacked to form flow passages through which the fluid flows.
  • any numbers of bear materials 11 and clad materials 12 may be stacked to form the stacking-type header 10.
  • the bear materials 11 and the clad materials 12 are assigned the suffixes a to f as they are stacked from the side of insertion of the flat tubes 20.
  • the first opening ports 30, the second opening ports 40, and the third opening ports 50 are assigned the same suffixes as the corresponding bare materials 11 or clad materials 12. It should be noted that the absence of the suffixes means that the content of descriptions is common to all suffixes.
  • Fig. 5 is a schematic perspective view showing a stacked state of the stacking-type header 10 of the heat exchanger 1 according to Embodiment 1 of the present invention.
  • Fig. 5 illustrates layers of the bare materials 11 and the clad materials 12 with varying column-wise lengths.
  • Fig. 6 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 1 of the present invention. Fig. 6 is also an enlarged view of cross-section B-B of Fig. 1 .
  • a configuration of the stacking-type header 10 according to Embodiment 1 is described below with reference to Figs. 5 and 6 .
  • the layers of the bare materials 11 and the clad materials 12 of the stacking-type header 10 constitute the first opening ports 30, to which the flat tubes 20 are connected, contracted flow passages 41 formed by the second opening ports 40, and a row-connecting flow passage 51 formed by the third opening ports 50.
  • the contracted flow passages 41 are assigned the same suffixes as the corresponding flat tubes 20. It should be noted that the absence of the suffixes means that the content of descriptions is common to all suffixes.
  • the bare material 11 a and the clad material 12a have first opening ports 30a formed therethrough.
  • Each of the first opening ports 30a has a flat shape corresponding to the shape of the corresponding one of the flat tubes 20.
  • Each of the first opening ports 30a has its long axis oriented in the row-wise direction.
  • the first opening ports 30a are larger than outer circumferences of the flat tubes 20. That is, the hole height H31, which is the short axis length of each first opening port 30, is equal to or greater than the tube height H21 of the corresponding one of the flat tubes 20, and the hole width L32, which is the long axis length of each first opening port 30, is equal to or greater than the tube width L22 of the corresponding one of the flat tubes 20.
  • each flat tube 20 is inserted into the corresponding one of the first opening ports 30a.
  • the bare materials 11 b to 11 d and the clad materials 12b to 12d have second opening ports 40b to 40d formed therethrough, respectively.
  • Each of the second opening ports 40b to 40d has a flat shape corresponding to the shape of the corresponding one of the flat tubes 20.
  • Each of the second opening ports 40b to 40d has its long axis oriented in the row-wise direction.
  • the bare materials 11 b to 11 d and the clad materials 12b to 12d are stacked so that the second opening ports 40b to 40d communicate with the first opening ports 30a to form the contracted flow passages 41.
  • the second opening ports 40b of the bare material 11 b which is adjacent to the clad material 12a, are smaller than the outer circumferences of the flat tubes 20. That is, the hole height H41, which is the short axis length of each second opening port 40b of the bare material 11 b, is less than the tube height H21 of the corresponding one of the flat tubes 20, and the hole width L42, which is the long axis length of each second opening port 40b, is less than the tube width L22 of the corresponding one of the flat tubes 20.
  • each of the flat tubes 20 inserted in the first opening ports 30a makes partial contact with a side surface of the bare material 11 b.
  • a structure in which the position of insertion of each flat tube 20 is defined by the bare material 11 b receiving an end of the flat tube 20.
  • each of the second opening ports 40b be in size equal to or larger than inner circumference of the corresponding one of the flat tubes 20. That is, the following relationships hold: Tube height H21 > Hole height H41 ⁇ (Tube height H21 - 2 x Tube thickness t23) and Tube width L22 > Hole width L42 ⁇ (Tube width L22 - 2 x Tube thickness t23). This prevents the flow passages in each flat tube 20 from being closed by the bare material 11 b, thus allowing a reduction in flow passage resistance.
  • the brazing material of the clad material 12a is heated in a state where each of the flat tubes 20 is inserted in the corresponding ones of the first opening ports 30 and an end face of the flat tube 20 is in partial contact with the bare material 11 b, and the brazing material thus molten connects a side surface of the flat tube 20 and inner circumferential surfaces of the corresponding first opening ports 30a.
  • the end face of the flat tube 20 is connected in partial contact with the bare material 11 b coated with no brazing material.
  • the second opening ports 40c of the bare material 11c and the second opening ports 40c of the clad material 12c are smaller than the second opening ports 40b of the bare material 11 b and the second opening ports 40b of the clad material 12b. Furthermore, the second opening ports 40d of the bare material 11 d and the second opening ports 40d of the clad material 12d are smaller than the second opening ports 40c of the bare material 11 c and the second opening ports 40c of the clad material 12c.
  • each of the contracted flow passages 41 is structured to have a flow passage area (opening port cross-sectional area) that gradually increases in a stacking direction of the bare materials 11 and the clad materials 12.
  • the bare material 11 d and the clad material 12d which are located farthest away from the bare material 11a of the pluralities of bare materials 11 and clad materials 12 having the second opening ports 40, have their second opening ports 40d formed to be smallest in size. That is, the flow passage area (opening cross-sectional area) of each contracted flow passage 41 is smallest in a position farthest away from the bare material 11a.
  • the bare material 11 d or the clad material 12d may have its second opening ports 40d formed to be smallest.
  • Embodiment 1 has described a case where the contracted flow passages 41 are formed by the second opening ports 40b to 40d of the bare materials 11 b to 11 d and the second opening ports 40b to 40d of the clad materials 12b to 12d, the number of layers that are stacked can be arbitrarily set. It is desirable that each of the contracted flow passages 41 be formed so that the length thereof in the stacking direction is greater than the total thickness of two bare materials 11.
  • each flat tube 20 is inserted into at least one clad material 12a.
  • the bare material 11e and the clad material 12e have third opening ports 50e formed therethrough.
  • Each of the third opening ports 50e is formed by a single opening of a size encompassing the two second opening ports 40d formed in the bare material 11 d and the two second opening ports 40d formed in the clad material 12d.
  • the bare material 11f has no opening provided in a part thereof that faces the third opening ports 50e.
  • the bare material 11 e, the clad material 12e, and the bare material 11f are stacked to form the row-connecting flow passage 51, through which the plurality of contracted flow passages 41 communicate with each other.
  • the row-connecting flow passage 51 allows communication between a contracted flow passage 41 a corresponding to the flat tube 20a and a contracted flow passage 41 b corresponding to the flat tube 20b.
  • Embodiment 1 has described a case where the bare material 11e, the clad material 12e, and the bare material 11f are stacked to form the row-connecting flow passage 51, the present invention is not limited thereto.
  • a single plate-like member having a groove-like flow passage formed therein may be stacked on the clad material 12d.
  • a connecting tube such as a U-bend tube may be provided to allow communication between the contracted flow passage 41 a corresponding to the flat tube 20a and the contracted flow passage 41 b corresponding to the flat tube 20b.
  • the numbers of bare materials 11e and clad materials 12e that are stacked to form the row-connecting flow passage 51 are not limited to one but may be arbitrarily changed.
  • two bare materials 11e having third opening ports 50 formed therethrough and two clad materials 12e each having third opening ports 50 formed therethrough may be alternately stacked to form the row-connecting flow passage 51.
  • the bare material 11a and the clad material 12a correspond to the "first plate-like bodies" of the present invention.
  • the bare materials 11 b to 11 d and the clad materials 12b to 12d correspond to the "second plate-like bodies" of the present invention.
  • the bare materials 11e and 11f and the clad materials 12e and 12f correspond to the "third plate-like bodies" of the present invention.
  • Fig. 7 is a schematic cross-sectional view illustrating flows of refrigerant in the stacking-type header 10 according to Embodiment 1 of the present invention.
  • arrows shown in Fig. 7 indicate the directions of flows of refrigerant.
  • the inflow of refrigerant through an end of the flat tube 20a into the stacking-type header 10 is contracted by the contracted flow passage 41 a and flows through the row-connecting flow passage 51.
  • the flow passage area (opening cross-sectional area) of the flow passage of the refrigerant from the end of the flat tube 20a toward the row-connecting flow passage 51 gradually decreases. This suppresses imbalances in the outflow of two-phase gas-liquid refrigerant from the flat tube 20.
  • the contraction of the flow by the contracted flow passage 41 allows the refrigerant to flow in a more atomized state.
  • the refrigerant flowing through the row-connecting flow passage 51 flows into the contracted flow passage 41 b corresponding to the flat tube 20b.
  • the refrigerant flowing into the contracted flow passage 41 b flows into the flat tube 20b.
  • the flow passage area (opening cross-sectional area) of the flow passage of the refrigerant from the contracted flow passage 41 b toward the flat tube 20b gradually increases. This allows the refrigerant to be evenly distributed to each flow passage of the flat tube 20b.
  • the direction of passage of the refrigerant is not limited to that described above, but the refrigerant may flow in the opposite direction.
  • a heat medium e.g., air
  • the direction of flow of a heat medium may be parallel to or opposite to the direction of flow of the row-connecting flow passage 51.
  • the bare materials 11 and clad materials 12 having the second opening ports 40 are stacked to form the contracted flow passages 41, whose flow passage areas gradually change in the stacking direction.
  • each of the second opening ports 40 becomes larger with decreasing distance from the flat tubes 20.
  • the bare material 11 and the clad material 12 that are located farthest away from the flat tubes 20 of the bare materials 11 and clad materials 12 having the second opening ports 40 formed therethrough have their second opening ports 40 formed to be smallest in size.
  • first opening ports 30a of the bare material 11 a and clad material 12a, into which an end of each flat tube 20 is inserted are larger than the outer circumferences of the flat tubes 20. That is, the hole height H31 of each first opening port 30a is equal to or greater than the tube height H21, and the hole width L32 of each first opening port 30a is equal to or greater than the tube width L22.
  • each of the flat tubes 20 is joined to the stacking-type header 10 during brazing.
  • each flat tube 20 can be arbitrarily defined by arbitrarily setting the numbers of bare materials 11 a and clad materials 12a that are stacked.
  • the second opening ports 40b of the bare material 11 b which is adjacent to the clad material 12a, are smaller than the outer circumferences of the flat tubes 20. That is, the hole height H41 of each second opening port 40b is less than the tube height H21, and the hole width L42 of each second opening port 40b is less than the tube width L22.
  • each of the flat tubes 20 inserted in the first opening ports 30 can be brought into partial contact with the side surface of the bare material 11 b to define the position of insertion of the flat tube 20. That is, an end of each flat tube 20 can be prevented from sticking out of the bare material 11 b.
  • each flat tube 20 makes partial contact with the bare material 11 b coated with no brazing material, the inflow of a brazing material into the flat tube 20 can be prevented.
  • a heat exchanger can be manufactured without excessive lengthening of the edge for insertion, and the proportion of a heat exchange section in a heat exchanger of the same size can be increased.
  • each flat tube 20 can reduce the size of the heat exchanger 1 in achieving equal heat-exchange capabilities.
  • each flat tube 20 can increase the joint area between the flat tube 20 and the stacking-type header 10 and therefore improve the joint strength.
  • the second opening ports 40b are in size equal to or larger than the inner circumference of the flat tubes 20. That is, the following relationships hold: Tube height H21 > Hole height H41 of second opening port 40b ⁇ (Tube height H21 - 2 x Tube thickness t23) and Tube width L22 > Hole width L42 of second opening port 40b ⁇ (Tube width L22 - 2 x Tube thickness t23).
  • each contracted flow passage in a staircase pattern can make manufacturing easier than chamfering or curved surface shape processing can. Further, the ease of manufacture can reduce manufacturing costs.
  • the staircase pattern of simple shapes can make the making of molds easy also in the case of manufacture in molds by cutting, casting, or the like. Further, the ease of making can reduce manufacturing costs.
  • a stacking-type header 10 according to Embodiment 2 is described below with a focus on the differences from Embodiment 1.
  • Fig. 9 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 2 of the present invention.
  • each of the contracted flow passages 41 is structured to have a flow passage area (opening cross-sectional area) that continuously changes in the stacking direction of the bare materials 11 and the clad materials 12.
  • a wall surface shape 13 of a cross-section of each contracted flow passage 41 in the stacking direction of the bare materials 11 b to 11d and the clad materials 12b to 12d is formed in a linear shape (chamfered shape).
  • the flow passage area of each contracted flow passage 41 continuously changes in such a manner as to increase toward the corresponding one of the flat tubes 20.
  • each contracted flow passage 41 needs only be a shape that continuously changes, and is not limited to the linear shape.
  • the bare materials 11 b to 11 d and the clad materials 12b to 12d may be only partially formed into shapes that continuously change.
  • a wall surface shape 14 of a cross-section in the stacking direction of the bare materials 11c and 11 d and the clad materials 12c and 12d of the bare materials 11 b to 11 d and the clad materials 12b to 12d may be formed in a curved shape (rounded shape).
  • a wall surface shape 15 of all of the bare materials 11 b to 11 d and clad materials 12b to 12d may be formed in a curved shape (rounded shape).
  • the bare materials 11 and clad materials 12 having the second opening ports 40 are stacked to form the contracted flow passages 41, whose flow passage areas continuously change in the stacking direction.
  • the reduction in the flow separation and vortex development can lead to a reduction in loss of pressure in the flow passage.
  • the reduction in the flow separation and vortex development can lead to reduce a sound that is generated when the refrigerant flows.
  • the reduction in the flow separation and vortex development allows the refrigerant to be evenly distributed to each flow passage provided in the flat tube 20.
  • each contracted flow passage 41 can suppress the retention of liquid refrigerant or oil.
  • a stacking-type header 10 according to Embodiment 3 is described below with a focus on the differences from Embodiment 1.
  • Fig. 12 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 3 of the present invention. Fig. 12 is also an enlarged view of main components of the stacking-type header 10.
  • the stacking-type header 10 includes clearances 60 in which the molten brazing material accumulates.
  • Each of the clearances 60 is provided between a side surface of the corresponding one of the flat tubes 20 and inner circumferential surfaces of the corresponding ones of the first opening ports 30a of the bare material 11 a and clad material 12a.
  • each clearance 60 is too large, the molten brazing material does not sufficiently spread onto the flat tube 20 and the inner circumference surfaces of the corresponding first opening ports 30. This makes it difficult to join the flat tube 20 to the stacking-type header 10. For this reason, for example, it is desirable that sizes of the height and width of each clearance 60 be equal to or less than 0.10 mm.
  • Fig. 13 is a schematic cross-sectional view illustrating the action of the stacking-type header 10 according to Embodiment 3 of the present invention during brazing.
  • the brazing material of the clad material 12a is heated and molten in a state where each of the flat tubes 20 is inserted in the corresponding ones of the first opening ports 30 and an end face of the flat pie 20 is in partial contact with the bare material 11 b.
  • Gravitation or surface tension causes the molten brazing material 61 to penetrate between a side surface of the flat tube 20 and inner circumferential surfaces of the corresponding first opening ports 30a.
  • the molten brazing material 61 flows onto the side surface of the flat tube 20 (in the directions of arrows shown in Fig. 13 ) along the clearance 60, which is an open end. This causes the side surface of the flat tube 20 to be joined to the bare material 11 a and the clad material 12a.
  • the stacking-type header 10 according to Embodiment 3 includes clearances 60 in which the molten brazing material accumulates.
  • Each of the clearances 60 is provided between a side surface of the corresponding one of the flat tubes 20 and inner circumferential surfaces of the corresponding ones of the first opening ports 30 of the bare material 11 a and clad material 12a.
  • the provision of the clearances 60 makes it possible to absorb displacements that are caused by dimension errors in the simultaneous insertion of the plurality of flat tubes 20 into the stacking-type header 10. This makes it possible to easily insert the flat tubes 20 into the stacking-type header 10.
  • the ease of insertion of the flat tubes 20 into the stacking-type header 10 can reduce manufacturing costs.
  • each clearance 60 by causing each clearance 60 to have a length of 0.10 mm or less, the number of imperfect joints between the bare material 11 a and the side surface of each flat tube 20 can be reduced.
  • the improved joint strength can lead to improved reliability.
  • the provision of the clearances 60 allows a fillet to be formed at a contact boundary surface between the bare material 11 b and the vicinity of an end of each flat tube 20.
  • a stacking-type header 10 according to Embodiment 4 is described below with a focus on the differences from Embodiment 1.
  • Fig. 14 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 4 of the present invention.
  • Fig. 15 is an enlarged view of part C of Fig. 14 .
  • the bare material 11 b, with which an end face of each flat tube 20 makes partial contact is smaller in thickness in a portion with which the end face of the flat tube 20 makes partial contact than in a portion with which the end face of the flat tube 20 makes no contact.
  • the bare material 11 b varies in size of the opening ports between an insertion side into which the end of the flat tube 20 is inserted and a side (back surface side) with which the end of the flat tube 20 makes contact.
  • the portion with which the end face of the flat tube 20 makes partial contact is hereinafter referred to as "projection-shaped portion 110".
  • each second opening port 40b of the bare material 11 b into which the end of the flat tube 20 is inserted is sized such that the following relationships hold: Hole height H31 of first opening port 30a ⁇ Hole height H41 of second opening port 40b ⁇ Tube height H21, and Hole width L32 of first opening port 30a ⁇ Hole width L42 of second opening port 40b ⁇ Tube width L22.
  • the back surface side with which the end of the flat tube 20 makes contact is sized such that the following relationships hold: Tube height H21 ⁇ Hole height H41 of second opening port 40b ⁇ (Tube height H21 - 2 x Tube thickness t23), and Tube width L22 ⁇ Hole width L42 of second opening port 40b ⁇ (Tube width L22 - 2 x Tube thickness t23).
  • Fig. 16 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 4 of the present invention, with a flat tube 20 inserted therein.
  • Fig. 17 is an enlarged view of part D of Fig. 16 .
  • Fig. 18 is a schematic cross-sectional view illustrating the action of the stacking-type header 10 according to Embodiment 4 of the present invention during brazing.
  • Fig. 19 is an enlarged view of part E of Fig. 18 .
  • the end of the flat tube 20 communicates with the insertion side of the bare material 11 b in which the flat tube 20 is inserted, and the end face of the flat tube 20 makes surface contact with the projection-shaped portion 110 on the back surface side.
  • molten brazing material 61 As shown in Figs. 18 and 19 , during brazing, gravitation or surface tension causes the molten brazing material 61 to penetrate between a side surface of the flat tube 20 and inner circumferential surfaces of the corresponding first opening ports 30a and into the insertion side of the bare material 11 b in which the flat tube 20 is inserted. At this point in time, the molten brazing material 61 flows onto the side surface of the flat tube 20 (in the directions of arrows shown in Figs. 18 and 19 ), which has an open end. This causes the side surface of the flat tube 20 to be joined to the bare material 11 a and the clad material 12a and to the insertion side of the bare material 11 b in which the flat tube 20 is inserted.
  • the bare material 11 a is smaller in thickness in a portion with which the end face of the flat tube 20 makes partial contact than in a portion with which the end face of the flat tube 20 makes no contact. That is, the bare material 11 b has a projection-shaped portion 110 provided on the back surface side thereof.
  • the flat tube 20 does not have its end on the contact boundary surface between the bare material 11 b and the clad material 12a, the entrance of the brazing material 61 into the flat tube 20 can be prevented.
  • fixation of the end of the flat tube 20 in the bare material 11 b allows a larger edge for insertion.
  • the larger edge for insertion allows a larger joint area during brazing.
  • the larger joint area can lead to improved joint strength.
  • the improved contact strength can lead to improved reliability.
  • such a structure in which the end of the flat tube 20 is at a longer distance from the clad material 12a can prevent the brazing material 61 from flowing into the flat tube 20 even if the brazing material 61 flows toward the flat tube 20.
  • Embodiment 5 describes a configuration of an air-conditioning apparatus to which a stacking-type header 10 and a heat exchanger including the stacking-type header 10 are applied.
  • Figs. 20 and 21 are diagrams schematically illustrating a configuration of an air-conditioning apparatus 91 according to Embodiment 5 of the present invention.
  • Fig. 20 shows a case where the air-conditioning apparatus 91 is in a heating operation.
  • Fig. 21 shows a case where the air-conditioning apparatus 91 is in a cooling operation.
  • the air-conditioning apparatus 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger 94, an expansion device 95, an indoor heat exchanger 96, an outdoor fan 97, an indoor fan 98, and a controller 99.
  • the compressor 92, the four-way valve 93, the outdoor heat exchanger 94, the expansion device 95, and the indoor heat exchanger 96 are connected through refrigerant tubes to form a refrigerant circuit.
  • the four-way valve 93 may be replaced by another flow passage switching device.
  • the outdoor heat exchanger 94 is a heat exchanger 1.
  • the heat exchanger 1 allows passage of air generated by driving the outdoor fan 97.
  • the outdoor fan 97 may be provided on the windward side of the heat exchanger 1. Alternatively, the outdoor fan 97 may be provided on the leeward side of the heat exchanger 1.
  • the controller 99 Connected to the controller 99 are for example the compressor 92, the four-way valve 93, the expansion device 95, the outdoor fan 97, the indoor fan 98, and various types of sensor.
  • the controller 99 switches flow passages of the four-way valve 93, thereby switching between the heating operation and the cooling operation.
  • High pressure and temperature gaseous refrigerant that is discharged from the compressor 92 flows through the four-way valve 93 into the indoor heat exchanger 96, condenses by exchanging heat with air that is supplied by the indoor fan 98, and thereby heats the interior of a room.
  • the condensed refrigerant flows out of the indoor heat exchanger 96 in the form of high-pressure subcooled liquid (or low-quality two-phase gas-liquid refrigerant) and turns into low-pressure two-phase gas-liquid refrigerant through the expansion device 95.
  • the low-pressure two-phase gas-liquid refrigerant flows into the outdoor heat exchanger 94, exchanges heat with air that is supplied by the outdoor fan 97, and evaporates.
  • the evaporated refrigerant turns into low-pressure superheated gas, flows out of the outdoor heat exchanger 94, and is sucked into the compressor 92 through the four-way valve 93. That is, the outdoor heat exchanger 94 acts as an evaporator during heating operation. Further, in the outdoor heat exchanger 94, the refrigerant passes through the row of flat tubes 20a located on the windward side and flows through the stacking-type header 10 into the row of flat tubes 20b located on the leeward side.
  • High pressure and temperature gaseous refrigerant that is discharged from the compressor 92 flows through the four-way valve 93 into the outdoor heat exchanger 94 and condenses by exchanging heat with air that is supplied by the outdoor fan 97.
  • the condensed refrigerant flows out of the outdoor heat exchanger 94 in the form of high-pressure subcooled liquid (or low-quality two-phase gas-liquid refrigerant) and turns into low-pressure two-phase gas-liquid refrigerant through the expansion device 95.
  • the low-pressure two-phase gas-liquid refrigerant flows into the indoor heat exchanger 96, evaporates by exchanging heat with air that is supplied by the indoor fan 98, and thereby cools the interior of the room.
  • the evaporated refrigerant turns into low-pressure superheated gas, flows out of the indoor heat exchanger 96, and is sucked into the compressor 92 through the four-way valve 93. That is, the outdoor heat exchanger 94 acts as a condenser during the cooling operation. Further, in the outdoor heat exchanger 94, the refrigerant passes through the row of flat tubes 20b located on the leeward side and flows through the stacking-type header 10 into the row of flat tubes 20b located on the windward side.
  • Embodiment 3 The stacking-type header 10 according to Embodiment 3 is described below with a focus on the differences from Embodiment 1.
  • Fig. 22 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 5 of the present invention. Fig. 22 is also an enlarged view of main components of the stacking-type header 10.
  • a central axis of each of the first opening port 30a of the bare material 11 a and clad material 12a and a central axis of the corresponding one of the second opening ports 40d, which serves as an outlet of the corresponding one of the contracted flow passages 41, of the bare material 11 d and clad material 12d are eccentric to each other.
  • each second opening port 40d of the contracted flow passage 41 corresponding to one of the two flat tubes 20a and 20b is more eccentric toward the other flat tube 20 than the central axis of each first opening port 30a of the contracted flow passage 41.
  • the central axes are eccentric so that the distance between the central axis of each of the second opening ports 40d corresponding to the flat tube 20a and the central axis of the flat tube 20a is shorter than the distance between the central axis of the flat tube 20b and the central axis of each of the second opening ports 40d corresponding to the flat tube 20a.
  • the central axes are eccentric so that the distance between the central axis of each of the second opening ports 40d corresponding to the flat tube 20b and the central axis of the flat tube 20b is shorter than the distance between the central axis of the flat tube 20a and the central axis of each of the second opening ports 40d corresponding to the flat tube 20b.
  • Figs. 23 and 24 are a diagram and a graph, respectively, illustrating a liquid distribution of refrigerant that flows into a flat tube 20b in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as an evaporator.
  • the flow of refrigerant is parallel to the flow of air that is generated by driving the outdoor fan 97. That is, the refrigerant flows from the flat tube 20a to the contracted flow passage 41 a, and flows from the row-connecting flow passage 51 into the contracted flow passage 41 b in a two-phase gas-liquid state.
  • the two-phase gas-liquid refrigerant passing through the row-connecting flow passage 51 is subject to influence of inertial force, with the result that a high-density refrigerant flows through an outer portion of the row-connecting flow passage 51 and a low-density refrigerant flows through an inner portion of the row-connecting flow passage 51.
  • the heat exchanger 1 acts as an evaporator
  • Figs. 25 and 26 are a diagram and a graph, respectively, illustrating a liquid distribution of refrigerant that flows into a flat tube 20a in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as a condenser.
  • the flow of refrigerant is opposite to the flow of air that is generated by driving the outdoor fan 97. That is, the refrigerant flows from the flat tube 20b to the contracted flow passage 41 b, and flows from the row-connecting flow passage 51 into the contracted flow passage 41 a in a two-phase gas-liquid state.
  • the two-phase gas-liquid refrigerant passing through the row-connecting flow passage 51 is subject to influence of inertial force, with the result that a high-density refrigerant flows through an outer portion of the row-connecting flow passage 51 and a low-density refrigerant flows through an inner portion of the row-connecting flow passage 51.
  • the heat exchanger 1 acts as a condenser
  • Embodiments 1 to 5 Although the foregoing has described Embodiments 1 to 5, the present invention is not limited to any of the descriptions of Embodiments 1 to 5. For example, it is possible to combine all or part of Embodiments 1 to 5.

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  • 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)
EP13896215.4A 2013-10-30 2013-10-30 Collecteur stratifié, échangeur de chaleur, et appareil de climatisation Active EP3064880B1 (fr)

Applications Claiming Priority (1)

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PCT/JP2013/079346 WO2015063875A1 (fr) 2013-10-30 2013-10-30 Collecteur stratifié, échangeur de chaleur, et appareil de climatisation

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EP3064880A1 true EP3064880A1 (fr) 2016-09-07
EP3064880A4 EP3064880A4 (fr) 2017-10-18
EP3064880B1 EP3064880B1 (fr) 2021-03-24

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US10794636B2 (en) 2016-09-29 2020-10-06 Daikin Industries, Ltd. Heat exchanger and air conditioner
EP4012296A4 (fr) * 2019-08-07 2022-09-21 Daikin Industries, Ltd. Échangeur de chaleur et dispositif de pompe à chaleur

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EP3112791B1 (fr) * 2014-01-27 2018-12-19 Mitsubishi Electric Corporation Collecteur stratifié, échangeur thermique et dispositif de climatisation
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JP6717256B2 (ja) * 2017-05-10 2020-07-01 株式会社デンソー 冷媒蒸発器およびその製造方法
JP7253894B2 (ja) * 2018-10-30 2023-04-07 三星電子株式会社 洗濯機
JP7038892B2 (ja) * 2019-02-26 2022-03-18 三菱電機株式会社 積層型ヘッダ、熱交換器、及び熱交換器の製造方法
JP7275699B2 (ja) * 2019-03-19 2023-05-18 株式会社富士通ゼネラル 積層体及び積層体の製造方法
EP4354069A1 (fr) * 2021-06-07 2024-04-17 Mitsubishi Electric Corporation Échangeur de chaleur et unité extérieure
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WO2024157369A1 (fr) * 2023-01-25 2024-08-02 三菱電機株式会社 Distributeur de fluide frigorigène et échangeur de chaleur

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US11555655B2 (en) 2019-08-07 2023-01-17 Daikin Industries, Ltd. Heat exchanger and heat pump device

Also Published As

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JPWO2015063875A1 (ja) 2017-03-09
EP3064880A4 (fr) 2017-10-18
JP6116702B2 (ja) 2017-04-19
WO2015063875A1 (fr) 2015-05-07
EP3064880B1 (fr) 2021-03-24

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