EP2998680B1 - Colonne stratifiée, échangeur de chaleur, et climatiseur - Google Patents

Colonne stratifiée, échangeur de chaleur, et climatiseur Download PDF

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Publication number
EP2998680B1
EP2998680B1 EP13884722.3A EP13884722A EP2998680B1 EP 2998680 B1 EP2998680 B1 EP 2998680B1 EP 13884722 A EP13884722 A EP 13884722A EP 2998680 B1 EP2998680 B1 EP 2998680B1
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EP
European Patent Office
Prior art keywords
refrigerant
plate
passage
passages
heat exchanger
Prior art date
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Application number
EP13884722.3A
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German (de)
English (en)
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EP2998680A1 (fr
EP2998680A4 (fr
Inventor
Takashi Okazaki
Akira Ishibashi
Takuya Matsuda
Shinya Higashiiue
Daisuke Ito
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2998680A1 publication Critical patent/EP2998680A1/fr
Publication of EP2998680A4 publication Critical patent/EP2998680A4/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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present invention relates to a stacking-type header, a heat exchanger, and an air-conditioning apparatus.
  • WO 03/054467 A1 discloses a stacking type header having the features in the preamble of claim 1.
  • a conventional stacking-type header including a first plate-shaped unit having a plurality of outlet flow passages and a plurality of inlet flow passages, and a second plate-shaped unit stacked on the first plate-shaped unit and having an inlet flow passage communicating with the plural outlet flow passages provided in the first plate-shaped unit and an outlet flow passage communicating with the plural inlet flow passages provided in the first plate-shaped unit (see, for example, Patent Literature 1).
  • JP 6-11291 A discloses a laminated plate header for a cooling system and manufacture thereof.
  • a plurality of plates, etc. are stacked together to form a laminate adapted to fluidly connect between a header inlet and a core unit of a heat exchanger.
  • a distribution plate where a passageway is formed with first and second channels comprises a first expansion chamber for fluid communication between the first and second channels for the fluid to spread.
  • the plate, etc. is interleaved in such manner as to selectively provide a plate passageway for distribution a refrigerant to the core unit from the inlet through the passageway.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2000-161818 (paragraph [0032]-paragraph [0036], Figs. 7 and 8 )
  • a stacking-type header for example, when gaseous refrigerant flows into the plural inlet flow passages in the first plate-shaped unit, the pressure loss of the refrigerant caused between the plural inlet flow passages in the first plate-shaped unit and the outlet flow passage in the second plate-shaped unit increases.
  • the refrigerant with the increased pressure loss flows from the outlet flow passage in the second plate-shaped unit into a compressor, the suction pressure of the compressor decreases, and the workload of the compressor increases. That is, the conventional stacking-type header has the problem in that the pressure loss of the refrigerant is high.
  • the present invention has been made in the context of the above-described problem, and an object of the invention is to obtain a stacking-type header in which the pressure loss of refrigerant is reduced. Another object of the invention is to obtain a heat exchanger including the stacking-type header. A further object of the invention is to obtain an air-conditioning apparatus including the heat exchanger.
  • a stacking-type header includes a first plate-shaped unit (11) having a plurality of first outlet flow passages (11A) and a plurality of first inlet flow passages (11B); and a second plate-shaped unit stacked on the first plate-shaped unit (11) and having a second inlet flow passage (12A), a second outlet flow passage (12D) and at least a part of a distribution flow passage (12B) configured to distribute refrigerant, which passes through the second inlet flow passage (12A) to flow into the second plate-shaped unit, to the plurality of first outlet flow passages (11A), the second plate-shaped unit having at least a part of a joining flow passage (12C), the joining flow passage (12C) causing refrigerant entering from each of the first inlet flow passages (11B) to join and enter the second outlet flow passage (12D), characterized in that any one of the plurality of first inlet flow passages (11B) communicates with any one of the first outlet flow passages (11A) via a heat transfer tube
  • the passage area of any one of the first inlet flow passages of the plurality of first inlet flow passages is larger than the passage area of any one of the first outlet flow passage of the plurality of first outlet flow passages communicating with the one first inlet flow passage.
  • the stacking-type header of the present invention may distribute refrigerant that flows into other devices.
  • the following structures, actions, and so on are just exemplary, and structures, actions, and so on are not limited thereto.
  • the same or similar components are denoted by the same reference numerals, or are not denoted by any reference numeral. Illustrations of detailed structures are appropriately simplified or omitted. Overlapping or similar descriptions are appropriately simplified or omitted.
  • the term "passage area” means the cross-sectional area of the passage, and when a plurality of passages are provided, the term “passage area” means the sum of cross-sectional areas of the plural passages.
  • Fig. 1 illustrates the structure of the heat exchanger according to Embodiment 1.
  • a heat exchanger 1 includes a stacking-type header 2, a plurality of first heat transfer tubes 3, a holding member 4, and a plurality of fins 5.
  • the stacking-type header 2 includes a refrigerant inflow part 2A, a plurality of refrigerant outflow parts 2B, a plurality of refrigerant inflow parts 2C, and a refrigerant outflow part 2D.
  • Refrigerant pipes are connected to the refrigerant inflow part 2A of the stacking-type header 2 and the refrigerant outflow part 2D of the stacking-type header 2.
  • the first heat transfer tubes 3 are flat tubes subjected to hairpin bending.
  • the plural first heat transfer tubes 3 are connected between the plural refrigerant outflow parts 2B of the stacking-type header 2 and the plural refrigerant inflow parts 2C of the stacking-type header 2.
  • the first heat transfer tubes 3 are flat tubes each having a plurality of passages.
  • the first heat transfer tubes 3 are formed of aluminum.
  • the plural first heat transfer tubes 3 are each connected at two ends to the plural refrigerant outflow parts 2B and the plural refrigerant inflow parts 2C of the stacking-type header 2 while being held by the holding member 4 shaped like a plate.
  • the holding member 4 is formed of aluminum.
  • a plurality of fins 5 are joined to the first heat transfer tubes 3.
  • the fins 5 are formed of aluminum.
  • the first heat transfer tubes 3 and the fins 5 are preferably joined by brazing. While the number of first heat transfer tubes 3 is eight in Fig. 1 , the present invention is not limited to such a case.
  • Refrigerant flowing through the refrigerant pipe flows into the stacking-type header 2 via the refrigerant inflow part 2A, is distributed, and flows out to the plural first heat transfer tubes 3 via the plural refrigerant outflow parts 2B.
  • the refrigerant exchanges heat with, for example, air supplied by a fan.
  • the refrigerant flows into the stacking-type header 2 via the plural refrigerant inflow parts 2C, joins together, and flows out to the refrigerant pipe via the refrigerant outflow part 2D.
  • the refrigerant can flow back.
  • Fig. 2 is an exploded perspective view of the stacking-type header in the heat exchanger of Embodiment 1.
  • Fig. 3 is a developed view of the stacking-type header in the heat exchanger of Embodiment 1. In Fig. 3 , illustration of double-sided clad materials 24 is omitted.
  • the stacking-type header 2 includes a first plate-shaped unit 11 and a second plate-shaped unit 12.
  • the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked.
  • the first plate-shaped unit 11 is stacked on the outflow side of the refrigerant.
  • the first plate-shaped unit 11 includes a first plate-shaped member 21.
  • the first plate-shaped unit 11 has a plurality of first outlet flow passages 11A and a plurality of first inlet flow passages 11B.
  • the plural first outlet flow passages 11A correspond to the plural refrigerant outflow parts 2B in Fig. 1 .
  • the plural first inlet flow passages 11B correspond to the plural refrigerant inflow parts 2C in Fig. 1 .
  • the first plate-shaped member 21 has a plurality of passages 21A and a plurality of passages 21B.
  • the plural passages 21A and the plural passages 21B are through holes shaped so that their inner peripheral surfaces follow outer peripheral surfaces of the first heat transfer tubes 3.
  • the passage area (that is, the cross-sectional area) of one passage 21B of the plural passages 21B is larger than the passage area (that is, the cross-sectional area) of one passage 21A of the plural passages 21A communicating with the one passage 21B.
  • the plural passages 21A function as the plural first outlet flow passages 11A
  • the plural passages 21B function as the plural first inlet flow passages 11B.
  • the first plate-shaped member 21 has a thickness of about 1 to 10 mm, and is formed of aluminum.
  • the second plate-shaped unit 12 is stacked on the inflow side of the refrigerant.
  • the second plate-shaped unit 12 includes a second plate-shaped member 22 and a plurality of third plate-shaped members 23_1 to 23_3.
  • the second plate-shaped unit 12 has a second inlet flow passage 12A, a distribution flow passage 12B, a joining flow passage 12C, and a second outlet flow passage 12D.
  • the distribution flow passage 12B includes a plurality of branch passages 12b.
  • the joining flow passage 12C includes a mixing passage 12c.
  • the second inlet flow passage 12A corresponds to the refrigerant inflow part 2A in Fig. 1 .
  • the second outlet flow passage 12D corresponds to the refrigerant outflow part 2D in Fig. 1 .
  • a part of the distribution flow passage 12B or a part of the joining flow passage 12C may be provided in the first plate-shaped unit 11. In such a case, it is only necessary that a passage that allows the inflow refrigerant to return and flow out should be provided in the first plate-shaped member 21, the second plate-shaped member 22, the plural third plate-shaped members 23_1 to 23_3, and so on.
  • the width of the stacking-type header 2 can be made substantially equal to the width of the first heat transfer tubes 3, and this makes the heat exchanger 1 compact.
  • the second plate-shaped member 22 has a passage 22A and a passage 22B.
  • the passage 22A and the passage 22B are circular through holes.
  • the passage area (that is, the cross-sectional area) of the passage 22B is larger than the passage area (that is, the cross-sectional area) of the passage 22A.
  • the passage 22A functions as the second inlet flow passage 12A
  • the passage 22B functions as the second outlet flow passage 12D.
  • the second plate-shaped member 22 has a thickness of about 1 to 10 mm, and is formed of aluminum.
  • mouthpieces or the like are provided on a surface of the second plate-shaped member 22 on which other members are not stacked, and the refrigerant pipes are connected to the second inlet flow passage 12A and the second outlet flow passage 12D via the mouthpieces or the like.
  • Inner peripheral surfaces of the second inlet flow passage 12A and the second outlet flow passage 12D may be shaped to be fitted on outer peripheral surfaces of the refrigerant pipes, and the refrigerant pipes may be directly connected to the second inlet flow passage 12A and the second outlet flow passage 12D without using mouthpieces or the like. In such a case, for example, the component cost is reduced.
  • the plural third plate-shaped members 23_1 to 23_3 have a plurality of passages 23A_1 to 23A_3.
  • the plural passages 23A_1 to 23A_3 are through grooves each having two end portions 23a and 23b.
  • each of the plural passages 23A_1 to 23A_3 functions as a branch passage 12b.
  • the plural third plate-shaped members 23_1 to 23_3 have a thickness of about 1 to 10 mm, and are formed of aluminum.
  • the plural third plate-shaped members 23A_1 to 23A_3 are formed by press working, working is simplified and the production cost is reduced.
  • the plural third plate-shaped members 23_1 to 23_3 further have a plurality of passages 23B_1 to 23B_3.
  • the plural passages 23B_1 to 23B_3 are rectangular through holes that penetrate almost the entire areas of the third plate-shaped members 23_1 to 23_3 in the height direction.
  • the passage area (that is, the cross-sectional area) of the passages 23B_1 to 23B_3 is larger than the passage area (that is, the sum of cross-sectional areas) of the plural passages 21A.
  • each of the plural passages 23B_1 to 23B_3 functions as a part of the mixing passage 12c.
  • the plural passages 23B_1 to 23B_3 do not always need to be rectangular.
  • the plural third plate-shaped members 23_1 to 23_3 are sometimes generically referred to as third plate-shaped members 23.
  • the plural passages 23A_1 to 23A_3 are sometimes generically referred to as passages 23A.
  • the plural passages 23B_1 to 23B_3 are sometimes generically referred to as passages 23B.
  • the holding member 4, the first plate-shaped member 21, the second plate-shaped member 22, and the third plate-shaped members 23 are sometimes generically referred to as plate-shaped members.
  • the passage 23A provided in each third plate-shaped member 23 is shaped to connect two end portions 23a and 23b via a straight portion 23c perpendicular to the gravitational direction. Areas of the passage 23A other than an area 23d (hereinafter, referred to as an opening 23d) in a part between two ends of the straight portion 23c are closed by a member adjacently stacked on the inflow side of the refrigerant, and areas other than the end portions 23a and 23b are closed by a member adjacently stacked on the outflow side of the refrigerant, so that branch passage 12b is formed.
  • the end portion 23a and the end portion 23b are located at different heights. Particularly when one of the end portion 23a and the end portion 23b is located on the upper side of the straight portion 23c and the other is located on the lower side of the straight portion 23c, deviation of the distances from the opening 23d to the end portion 23a and the end portion 23b along the passage 23A can be reduced without complicating the shape. Since a straight line that connects the end portion 23a and the end portion 23b is parallel to the longitudinal direction of the third plate-shaped member 23, the dimension of the third plate-shaped member 23 in the shorter side direction can be reduced, and this reduces the component cost, weight, and so on. Further, since the straight line that connects the end portion 23a and the end portion 23b is parallel to the arrangement direction of the first heat transfer tubes 3, space saving of the heat exchanger 1 is achieved.
  • Each branch passage 12b branches the inflow refrigerant in two and sends out the refrigerant. For this reason, when eight first heat transfer tubes 3 are connected, at least three third plate-shaped members 23 are needed. When sixteen first heat transfer tubes 3 are connected, at least four third plate-shaped members 23 are needed.
  • the number of first heat transfer tubes 3 to be connected is not limited to the power of two. In such a case, the branch passage 12b is preferably combined with a passage that does not branch. The number of first heat transfer tubes 3 to be connected may be two.
  • the stacking-type header 2 is not limited to the one in which the plural first outlet flow passages 11A and the plural first inlet flow passages 11 B are arranged along the gravitational direction.
  • the stacking-type header 2 may be used when the heat exchanger 1 is disposed in an inclined manner like heat exchangers in a wall-hung indoor unit of a room air-conditioning apparatus, an outdoor unit of an air-conditioning apparatus, an outdoor unit of a chiller, and so on.
  • the straight portion 23c is preferably a through groove having a shape such as not to be perpendicular to the longitudinal direction of the third plate-shaped member 23.
  • the passage 23A may have other shapes.
  • the passage 23A may have no straight portion 23c.
  • a horizontal portion substantially perpendicular to the gravitational direction between the end portion 23a and the end portion 23b of the passage 23A serves as an opening 23d.
  • the passage 23A may be a through groove shaped so that an area that connects both ends of the straight portion 23c and an area that connects the end portion 23a and the end portion 23b are branched.
  • the branch passage 12b branches the inflow refrigerant in two and does not branch the branched refrigerant into a plurality of parts, uniformity of distribution of the refrigerant can be enhanced.
  • the areas that connect both ends of the straight portion 23c to the end portion 23a and the end portion 23b may be straight or curved.
  • the plate-shaped members are stacked by brazing.
  • a brazing material for joint may be supplied by using double-sided clad materials having the brazing material rolled on both surfaces for all plate-shaped members or for alternate plate-shaped members.
  • the brazing material for joint may be supplied by using single-sided clad materials having the brazing material rolled on one surface for all the plate-shaped members.
  • the brazing material may be supplied by stacking brazing-material sheets between the plate-shaped members.
  • the brazing material may be supplied by applying brazing material paste between the plate-shaped members.
  • the brazing material may be supplied by stacking double-sided clad materials having the brazing material rolled on both surfaces between the plate-shaped members.
  • the plate-shaped members When the plate-shaped members are stacked by brazing, they are stacked with no gap therebetween. This suppresses leakage of the refrigerant, and ensures pressure resistance. When the plate-shaped members are brazed while being pressurized, the occurrence of brazing failure is suppressed further. When a portion where the refrigerant is apt to leak is subjected to processing for promoting formation of a fillet, for example, a rib is formed, the occurrence of brazing failure is suppressed further.
  • first heat transfer tubes 3 and the fins 5 are formed of the same material (for example, formed of aluminum), they can be collectively brazed, and this enhances productivity.
  • the first heat transfer tubes 3 and the fins 5 may be brazed after the stacking-type header 2 is brazed.
  • first plate-shaped unit 11 may be first brazed to the holding member 4, and the second plate-shaped unit 12 may then be brazed.
  • the brazing material is preferably supplied by stacking plate-shaped members having the brazing material rolled on both surfaces, that is, double-sided clad materials between the plate-shaped members.
  • double-sided clad materials 24_1 to 24_5 are stacked between the plate-shaped members.
  • the plural double-sided clad materials 24_1 to 24_5 are sometime generically referred to as double-sided clad materials 24.
  • the double-sided clad materials 24 have passages 24A and passages 24B penetrating therethrough.
  • the passages 24A and the passages 24B are formed by press working, working is simplified, and, for example, the production cost is reduced.
  • all of the members to be brazed, including the double-sided clad materials 24, are formed of the same material (for example, formed of aluminum), they can be collectively brazed, and this enhances productivity.
  • the passages 24A provided in the double-sided clad materials 24 stacked on the second plate-shaped member 22 and the third plate-shaped members 23 are circular through holes.
  • the passages 24B provided in the double-sided clad materials 24 stacked on the third plate-shaped members 23_1 and 23_2 are rectangular through holes that penetrate almost the entire area of the double-sided clad materials 24 in the height direction.
  • the passages 24B do not always need to be rectangular.
  • the passage area (that is, the cross-sectional area) of the passages 24B is larger than the passage area (that is the sum of cross-sectional areas) of the plural passages 21A.
  • the plural passages 24B provided in the double-sided clad material 24_4 stacked between the third plate-shaped ember 23_3 and the first plate-shaped member 21 are rectangular through holes.
  • the plural passages 24B do not always need to be rectangular.
  • the passage area (that is, the cross-sectional area) of one passage 24B of the plural passages 24B is larger than the passage area (that is, the cross-sectional area) of one passage 21A of the plural passages 21A communicating with the one passage 24B.
  • the plural passages 24A and the plural passages 24B provided in the double-sided clad material 24_5 stacked between the first plate-shaped member 21 and the holding member 4 are through holes shaped so that their inner peripheral surfaces extend along the outer peripheral surfaces of the first heat transfer tubes 3.
  • the passage area (that is, the cross-sectional area) of one passage 24B of the plural passages 24B is larger than the passage area (that is, the cross-sectional area) of one passage 21A of the plural passages 21A communicating with the one passage 24B.
  • the passages 24A function as refrigerant separation passages for the first outlet flow passages 11A, the distribution flow passage 12B, and the second inlet flow passage 12A
  • the passages 24B function as refrigerant separation passages for the first inlet flow passages 11B, the joining flow passage 12C, and the second outlet flow passage 12D. Since the refrigerant separation passages are formed by the double-sided clad materials 24, separation of the refrigerant is performed reliably. Further, since separation of the refrigerant is reliably performed, the flexibility in designing the passages is improved.
  • the double-sided clad materials 24 may be stacked between some of the plate-shaped members, and the brazing material may be supplied between the other plate-shaped members by other methods.
  • the double-sided clad material 24_5 is stacked on the holding member 4, and the inner peripheral surfaces of the passages 24A and 24B of the double-sided clad material 24_5 are fitted on the outer peripheral surfaces of the end portions.
  • the first heat transfer tubes 3 are connected to the first outlet flow passages 11A and the first inlet flow passages 11B.
  • the first outlet flow passages 11A and the first inlet flow passages 11B, and the first heat transfer tubes 3 may be positioned, for example, by fitting projections provided on the holding member 4 in recessed portions provided in the first plate-shaped unit 11.
  • the end portions of the first heat transfer tubes 3 do not have to protrude from the surface of the holding member 4.
  • the first heat transfer tubes 3 may be directly connected to the first outlet flow passages 11A and the first inlet flow passages 11B without providing the holding member 4. In such a case, for example, the component cost is reduced.
  • refrigerant that has passed through the passage 22A of the second plate-shaped member 22 flows into the opening 23d of the passage 23A provided in the third plate-shaped member 23_1.
  • the refrigerant that has flowed in the opening 23d strikes the surface of the adjacently stacked member, and is branched in two toward both ends of the straight portion 23c.
  • the branched refrigerant reaches the end portions 23a and 23b of the passage 23A, and flows into the openings 23d of the passages 23A provided in the third plate-shaped member 23_2.
  • the refrigerant that has flowed in the opening 23d of each passage 23A provided in the third plate-shaped member 23_2 strikes the surface of the adjacently stacked member, and is branched in two toward both ends of the straight portion 23c.
  • the branched refrigerant reaches the end portions 23a and 23b of the passage 23A, and flows into the openings 23d of the passages 23A provided in the third plate-shaped member 23_3.
  • the refrigerant that has flowed in the opening 23d of each passage 23A provided in the third plate-shaped member 23_3 strikes the surface of the adjacently stacked member, and is branched in two toward both ends of the straight portion 23c.
  • the branched refrigerant reaches the end portions 23a and 23b of the passage 23A, passes through the passages 21A of the first plate-shaped member 21, and flows into the first heat transfer tubes 3.
  • the refrigerant which has flowed out from the passages 21A of the first plate-shaped member 21 and has passed through the first heat transfer tubes 3, flows into the passages 21B of the first plate-shaped member 21.
  • the refrigerant that has flowed in the passages 21B of the first plate-shaped member 21 flows into the passages 23B provided in the third plate-shaped members 23 so as to be mixed.
  • the mixed refrigerant passes through the passage 22B of the second plate-shaped member 22, and flows out to the refrigerant pipe.
  • the present invention is not limited to such a case.
  • the heat exchanger of Embodiment 1 may be used in other refrigeration cycle apparatuses including a refrigerant circuit.
  • cooling operation and heating operation are switched in the air-conditioning apparatus, the present invention is not limited to such a case, and only cooling operation or heating operation may be performed.
  • Fig. 4 illustrates the configuration of an air-conditioning apparatus to which the heat exchanger of Embodiment 1 is applied.
  • the flow of refrigerant in cooling operation is shown by solid arrows
  • the flow of the refrigerant in heating operation is shown by dotted arrows.
  • an air-conditioning apparatus 51 includes a compressor 52, a four-way valve 53, a heat-source-side heat exchanger 54, an expansion device 55, a load-side heat exchanger 56, a heat-source-side fan 57, a load-side fan 58, and a controller 59.
  • the compressor 52, the four-way valve 53, the heat-source -heat exchanger 54, the expansion device 55, and the load-side heat exchanger 56 are connected by refrigerant pipes to form a refrigerant circuit.
  • the controller 59 for example, the compressor 52, the four-way valve 53, the expansion device 55, the heat-source-side fan 57, the load-side fan 58, and various sensors are connected.
  • the controller 59 switches the passage of the four-way valve 53 to switch between cooling operation and heating operation.
  • the heat-source-side heat exchanger 54 functions as a condenser in the cooling operation and functions as an evaporator in the heating operation.
  • the load-side heat exchanger 56 functions as an evaporator in the cooling operation and functions as a condenser in the heating operation.
  • the high-pressure liquid refrigerant that has flowed out from the heat-source-side heat exchanger 54 flows into the expansion device 55, and is turned into a low-pressure two-phase gas-liquid refrigerant.
  • the low-pressure two-phase gas-liquid refrigerant flowing out from the expansion device 55 flows into the load-side heat exchanger 56, is evaporated into a low-pressure gaseous refrigerant by heat exchange with indoor air supplied by the load-side fan 58, and flows out from the load-side heat exchanger 56.
  • the low-pressure gaseous refrigerant flowing out from the load-side heat exchanger 56 is sucked by the compressor 52 via the four-way valve 53.
  • the low-pressure two-phase gas-liquid refrigerant flowing out from the expansion device 55 flows into the heat-source-side heat exchanger 54, is evaporated into a low-pressure gaseous refrigerant by heat exchange with outdoor air supplied by the heat-source-side fan 57, and flows out from the heat-source-side heat exchanger 54.
  • the low-pressure gaseous refrigerant flowing out from the heat-source-side heat exchanger 54 is sucked by the compressor 52 via the four-way valve 53.
  • the heat exchanger 1 is used in at least one of the heat-source-side heat exchanger 54 and the load-side heat exchanger 56.
  • the heat exchanger 1 is connected so that the refrigerant flows from the distribution flow passage 12B of the stacking-type header 2 into the first heat transfer tubes 3 and the refrigerant flows from the first heat transfer tubes 3 into the joining flow passage 12C of the stacking-type header 2 when the heat exchanger 1 operates as an evaporator.
  • a two-phase gas-liquid refrigerant flows from the refrigerant pipe into the distribution flow passage 12B of the stacking-type header 2, and a gaseous refrigerant flows from the first heat transfer tubes 3 into the joining flow passage 12C of the stacking-type header 2.
  • a gaseous refrigerant flows from the refrigerant pipe into the joining flow passage 12C of the stacking-type header 2
  • a liquid refrigerant flows from the first heat transfer tubes 3 into the distribution flow passage 12B of the stacking-type header 2.
  • the passage area of one first inlet flow passage 11B of the plural first inlet flow passages 11B is larger than the passage area of one first outlet flow passage 11A of the plural first outlet flow passages 11A that communicates with the first inlet flow passage 11B. For this reason, even during use in a situation where the gaseous refrigerant flows into the plural first inlet flow passages 11B in the first plate-shaped unit 11, it is possible to suppress the increase in pressure loss of the refrigerant caused between the plural first inlet flow passages 11B of the first plate-shaped unit 11 and the second outlet flow passage 12D of the second plate-shaped unit 12.
  • the passage area of the joining flow passage 12c is larger than the passage area of the plural first outlet flow passages 11A. For this reason, even during use in a situation where the gaseous refrigerant flows into the plural first inlet flow passages 11B of the first plate-shaped unit 11, it is possible to suppress the increase in pressure loss of the refrigerant caused between the plural first inlet flow passages 11B of the first plate-shaped unit 11 and the second outlet flow passage 12D of the second plate-shaped unit 12.
  • the passage area of the second outlet flow passage 12D is larger than the passage area of the second inlet flow passage 12A. For this reason, even during use in a situation where the gaseous refrigerant flows into the plural first inlet flow passages 11B of the first plate-shaped unit 11, it is possible to suppress the increase in pressure loss of the refrigerant caused in the second outlet flow passage 12D of the second plate-shaped unit 12.
  • the conventional stacking-type header when the heat transfer tubes are changed from circular tubes to flat tubes, for example, in order to reduce the refrigerant amount and to achieve space saving of the heat exchanger, the conventional stacking-type header must be increased in size in the circumferential direction perpendicular to the inflow direction of the refrigerant.
  • the stacking-type header 2 does not have to be increased in size in the circumferential direction perpendicular to the inflow direction of the refrigerant, and this leads to space saving of the heat exchanger 1. That is, when the heat transfer tubes are changed from circular tubes to flat tubes in the conventional stacking-type header, the passage cross-sectional area in the heat transfer tubes decreases, and the pressure loss occurring in the heat transfer tubes increases.
  • the stacking-type header 2 is increased in size in the circumferential direction perpendicular to the inflow direction of the refrigerant.
  • the stacking-type header 2 even when the necessary of increasing the number of paths occurs, it is only necessary to increase the number of third plate-shaped members 23.
  • the increase in size of the stacking-type header 2 in the circumferential direction perpendicular to the inflow direction of the refrigerant is suppressed.
  • the stacking-type header 2 is not limited to the one in which the first heat transfer tubes 3 are flat tubes.
  • Fig. 5 is an exploded perspective view of a stacking-type header in Modification-1 of the heat exchanger according to Embodiment 1.
  • peripheral edges of passages 23B may be enlarged to be closer to peripheral edges of passages 23A.
  • the pressure loss is reduced.
  • the passages 23B penetrate areas that do not overlap with any of the passages 23A.
  • Passages 24B of double-sided clad materials 24 stacked between a second plate-shaped member 22 and a third plate-shaped member 23_3 also have the same shape.
  • Fig. 6 is an exploded perspective view of a stacking-type header in Modification-2 of the heat exchanger according to Embodiment 1.
  • the number of third plate-shaped members 23 may be reduced by forming a plurality of passages 22A in a second plate-shaped member 22, that is, by forming a plurality of second inlet flow passages 12A in a second plate-shaped unit 12.
  • This structure reduces, for example, the component cost and weight.
  • the passage area (that is, the cross-sectional area) of a passage 22B is larger than the passage area (that is, the sum of cross-sectional areas) of the plural passages 22A.
  • Fig. 7 is an exploded perspective view of a stacking-type header in Modification-3 of the heat exchanger according to Embodiment 1.
  • a second plate-shaped member 22 and third plate-shaped members 23 may have a plurality of passages 22B and a plurality of passages 23B. That is, a joining flow passage 12C may have a plurality of mixing passages 12c.
  • a plurality of passages 24B of double-sided clad materials 24 stacked between the second plate-shaped member 22 and a third plate-shaped member 23_3 have the same shape as that of the plural passages 23B.
  • the passage area (the sum of cross-sectional areas) of the plural passages 22B is larger than the passage area (that is, the cross-sectional area) of a passage 22A.
  • the passage area (that is, the sum of cross-sectional areas) of the plural passages 23B is larger than the passage area (that is, the sum of cross-sectional areas) of a plurality of passages 21A.
  • the passage area (that is, the sum of cross-sectional areas) of the plural passages 24B is larger than the passage area (that is, the sum of cross-sectional areas) of the plural passages 21A.
  • Fig. 8 includes a perspective view of the principal part and a cross-sectional view of the principal part in an exploded state of a stacking-type header in Modification-4 of the heat exchanger according to Embodiment 1.
  • Fig. 8(a) is a perspective view of the principal part of the stacking-type header in the exploded state
  • Fig. 8(b) is a cross-sectional view of a third plate-shaped member 23, taken along line A-A of Fig. 8(a) .
  • any of passages 23A provided in third plate-shaped members 23 is a bottomed groove.
  • a circular through hole 23e is provided in each of an end portion 23a and an end portion 23b of a bottom surface of the groove of the passage 23A.
  • double-sided clad materials 24 do not have to be stacked between the plate-shaped members so that passages 24A functioning as refrigerant separation passages are provided between branch passages 12b. This enhances production efficiency.
  • the refrigerant outflow side of the passage 23A is the bottom surface in Fig. 8
  • the refrigerant inflow side of the passage 23A may be the bottom surface. In such a case, it is only necessary that a through hole should be provided in an area corresponding to an opening 23d.
  • Fig. 9 is an exploded perspective view of a stacking-type header in Modification-5 of the heat exchanger according to Embodiment 1.
  • a passage 22A serving as a second inlet flow passage 12A may be provided in a stacked member other than a second plate-shaped member 22, that is, for example, in another plate-shaped member or a double-sided clad material 24.
  • the passage 22A is formed by a through hole that extends through the plate-shaped member from a side surface to a surface on the side of the second plate-shaped member 22.
  • Fig. 10 is an exploded perspective view of a stacking-type header in Modification-6 of the heat exchanger according to Embodiment 1.
  • a passage 22B serving as a second outlet flow passage 12D may be provided in, for example, a plate-shaped member other than a second plate-shaped member 22 of a second plate-shaped unit 12 or a double-sided clad material 24.
  • a cutout should be provided to communicate between a part of a passage 23B or a passage 24B and a side surface of a third plate-shaped member 23 or a double-sided clad material 24.
  • the passage 22B serving as the second outlet flow passage 12D may be provided in a first plate-shaped member 21 by bending back a mixing passage 12c.
  • Fig. 11 illustrates the structure of the heat exchanger according to Embodiment 2.
  • a heat exchanger 1 includes a stacking-type header 2, a plurality of first heat transfer tubes 3, a plurality of second heat transfer tubes 6, a holding member 4, and a plurality of fins 5.
  • the stacking-type header 2 includes a plurality of refrigerant return parts 2E.
  • the second heat transfer tubes 6 are flat tubes subjected to hairpin bending, similarly to the first heat transfer tubes 3.
  • the plural first heat transfer tubes 3 are connected between a plurality of refrigerant outflow parts 2B and the plural refrigerant return parts 2E in the stacking-type header 2, and the plural second heat transfer tubes 6 are connected between the plural refrigerant return parts 2E and a plurality of refrigerant inflow parts 2C in the stacking-type header 2.
  • Refrigerant flowing through a refrigerant pipe flows into the stacking-type header 2 via a refrigerant inflow part 2A, is distributed, and flows out to the plural first heat transfer tubes 3 via the plural refrigerant outflow parts 2B.
  • the refrigerant exchanges heat with, for example, air supplied by a fan.
  • the refrigerant that has passed through the plural first heat transfer tubes 3 flows into the plural refrigerant return parts 2E of the stacking-type header 2, is returned, and flows out to the plural second heat transfer tubes 6.
  • the refrigerant exchanges heat with, for example, air supplied by a fan.
  • the refrigerant that has passed through the plural second heat transfer tubes 6 flows into the stacking-type header 2 via the plural refrigerant inflow parts 2C, joins, and flows out to a refrigerant pipe via a refrigerant outflow part 2D.
  • the refrigerant can flow back.
  • Fig. 12 is an exploded perspective view of the stacking-type header in the heat exchanger according to Embodiment 2.
  • Fig. 13 is a developed view of the stacking-type header in the heat exchanger according to Embodiment 2. In Fig. 13 , illustration of double-sided clad materials 24 is omitted.
  • the stacking-type header 2 includes a first plate-shaped unit 11 and a second plate-shaped unit 12.
  • the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked.
  • the first plate-shaped unit 11 has a plurality of first outlet flow passages 11A, a plurality of first inlet flow passages 11B, and a plurality of return passages 11C.
  • the plural return passages 11C correspond to the plural refrigerant return parts 2E in Fig. 11 .
  • a first plate-shaped member 21 has a plurality of passages 21C.
  • the plural passages 21C are through holes shaped so that inner peripheral surfaces thereof surround outer peripheral surfaces of refrigerant outflow-side end portions of the first heat transfer tubes 3 and outer peripheral surfaces of refrigerant inflow-side end portions of the second heat transfer tubes 6.
  • the plural passages 21C function as the plural return passages 11C.
  • brazing material is preferably supplied by stacking double-sided clad materials 24 having the brazing material rolled on both surfaces between the plate-shaped members.
  • Passages 24C provided in a double-sided clad material 24_5 stacked between the holding member 4 and the first plate-shaped member 21 are through holes shaped so that inner peripheral surfaces thereof surround the outer peripheral surfaces of the refrigerant outflow-side end portions of the first heat transfer tubes 3 and the outer peripheral surfaces of the refrigerant inflow-side end portions of the second heat transfer tubes 6.
  • the passages 24C function as refrigerant separation passages of the return passages 11C.
  • the refrigerant that has flowed out from the passages 21A of the first plate-shaped member 21 and has passed through the first heat transfer tubes 3 flows into the passages 21C of the first plate-shaped member 21, is returned, and flows into the second heat transfer tubes 6.
  • the refrigerant that has passed through the second heat transfer tubes 6 flows into the passages 21B of the first plate-shaped member 21.
  • the refrigerant that has flowed in the passages 21B of the first plate-shaped member 21 flows into passages 23B provided in third plate-shaped members 23 so as to be mixed.
  • the mixed refrigerant passes through the passage 22B of the second plate-shaped member 22, and flows out to the refrigerant pipe.
  • Fig. 14 illustrates the configuration of an air-conditioning apparatus to which the heat exchanger of Embodiment 2 is applied.
  • the heat exchanger 1 is used in at least one of a heat-source-side heat exchanger 54 and a load-side heat exchanger 56.
  • the heat exchanger 1 is connected so that refrigerant flows from a distribution flow passage 12B of the stacking-type header 2 into the first heat transfer tubes 3 and the refrigerant flows from the second heat transfer tubes 6 into a joining flow passage 12C of the stacking-type header 2 when the heat exchanger 1 operates as an evaporator.
  • a two-phase gas-liquid refrigerant flows from the refrigerant pipe into the distribution flow passage 12B of the stacking-type header 2 and a gaseous refrigerant flows from the second heat transfer tubes 6 into the joining flow passage 12C of the stacking-type header 2.
  • a gaseous refrigerant flows from the refrigerant pipe into the joining flow passage 12C of the stacking-type header 2 and a liquid refrigerant flows from the first heat transfer tubes 3 into the distribution flow passage 12B of the stacking-type header 2.
  • the heat exchanger 1 is disposed so that the first heat transfer tubes 3 are located on the upstream side (windward side) of the second heat transfer tubes 6 in an airflow produced by a heat-source-side fan 57 or a load-side fan 58. That is, the flow of the refrigerant from the second heat transfer tubes 6 to the first heat transfer tubes 3 is opposed to the airflow.
  • the temperature of the refrigerant in the first heat transfer tubes 3 is lower than the temperature of the refrigerant in the second heat transfer tubes 6.
  • the temperature of the airflow produced by the heat-source-side fan 57 or the load-side fan 58 is lower on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1.
  • the refrigerant can be subcooled (subjected to so-called SC) by the low-temperature airflow flowing on the upstream side of the heat exchanger 1, and this enhances condenser performance.
  • the heat-source-side fan 57 and the load-side fan 58 may be provided on the windward side or the leeward side.
  • the plural return passages 11C are provided in the first plate-shaped unit 11, and the plural second heat transfer tubes 6 are connected in addition to the plural first heat transfer tubes 3.
  • the heat exchange amount can be increased by increasing the area of the heat exchanger 1 when viewed from the front side, a housing that contains the heat exchanger 1 is increased in size in this case.
  • the heat exchange amount can be increased by reducing the interval of the fins 5 to increase the number of fins 5, it is difficult to set the interval of the fins 5 less than about 1 mm from the viewpoints of drainage performance, frosting performance, and dust resistance, and the increase in heat exchange amount sometimes becomes insufficient.
  • the heat exchange amount can be increased without changing, for example, the area of the heat exchanger 1 when viewed from the front side and the interval of the fins 5.
  • the heat exchange amount increases by a factor of about 1.5 or more.
  • the number of rows of the heat transfer tubes may be three or more. Further, for example, the area of the heat exchanger 1 when viewed from the front side, and the interval of the fins 5 may be changed.
  • the header (stacking-type header 2) is provided on only one side of the heat exchanger 1.
  • the header (stacking-type header 2) is provided on only one side of the heat exchanger 1, as in the stacking-type header 2, even if the end portions are not aligned among the rows of heat transfer tubes, it is only necessary that the end portions should be aligned on only one side. This improves the flexibility in design and production efficiency.
  • the heat exchanger 1 can be bent after the members of the heat exchanger 1 are joined, and this further enhances the production efficiency.
  • the first heat transfer tubes 3 are located on the windward side of the second heat transfer tubes 6.
  • a header is provided on each side of the heat exchanger, it is difficult to enhance the condenser performance by making differences in refrigerant temperature among the rows of heat transfer tubes.
  • the first heat transfer tubes 3 and the second heat transfer tubes 6 are flat tubes, the flexibility in bending is low, unlike circular tubes. Hence, it is difficult to make the differences in temperature of the refrigerant among the rows of heat transfer tubes by deforming the passages of the refrigerant.
  • Embodiment 1 and Embodiment 2 have been described above, the present invention is not limited to the descriptions of Embodiments.

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

Claims (9)

  1. Collecteur à empilement comprenant :
    une première unité en forme de plaque (11) ayant une pluralité de premiers passages d'écoulement d'évacuation (11A) et une pluralité de premiers passages d'écoulement d'admission (11B) ; et
    une seconde unité en forme de plaque empilée sur la première unité en forme de plaque (11) et ayant un second passage d'écoulement d'admission (12A), un second passage d'écoulement d'évacuation (12D) et au moins une partie d'un passage d'écoulement de distribution (12B) configurée pour distribuer un réfrigérant, qui passe par le second passage d'écoulement d'admission (12A) afin de s'écouler vers la seconde unité en forme de plaque, à la pluralité de premiers passages d'écoulement d'évacuation (11A), la seconde unité en forme de plaque ayant au moins une partie d'un passage d'écoulement de jonction (12C), le passage d'écoulement de jonction (12C) permettant au réfrigérant qui pénètre depuis chacun des premiers passages d'écoulement d'admission (11B) de rejoindre et de pénétrer dans le second passage d'écoulement d'évacuation (12D),
    dans lequel n'importe lequel de la pluralité de premiers passages d'écoulement d'admission (11B) communique avec n'importe lequel des premiers passages d'écoulement d'évacuation (11A) via un tube d'échange thermique, caractérisé en ce que
    une zone de passage de n'importe lequel de la pluralité de premiers passages d'écoulement d'admission (11B) qui communique avec le tube d'échange thermique est plus grande qu'une zone de passage de n'importe lequel de la pluralité de premiers passages d'écoulement d'évacuation (11A) qui communique avec le tube d'échange thermique.
  2. Collecteur à empilement selon la revendication 1, dans lequel une zone de passage d'un passage d'écoulement du passage d'écoulement de jonction (12C) par laquelle le réfrigérant passe après la jonction est plus grande qu'une zone de passage de la pluralité de premiers passages d'écoulement d'évacuation (11A).
  3. Collecteur à empilement selon la revendication 1 ou 2, dans lequel une zone de passage du second passage d'écoulement d'évacuation (12D) est plus grande qu'une zone de passage du second passage d'écoulement d'admission (12A).
  4. Collecteur à empilement selon l'une quelconque des revendications 1 à 3, dans lequel la première unité en forme de plaque (11) possède une pluralité de passages d'écoulement à rebours (11C) formée à l'intérieur, la pluralité de passages d'écoulement à rebours (11C) étant configurée pour faire revenir en arrière le réfrigérant qui circule dans la première unité en forme de plaque (11) afin que le réfrigérant sorte de la première unité en forme de plaque (11).
  5. Échangeur thermique comprenant :
    le collecteur à empilement selon l'une quelconque des revendications 1 à 3 ; et
    une pluralité de premiers tubes d'échange thermique (3) qui sont chacun reliés à la pluralité de premiers passages d'écoulement d'évacuation (11A) et à la pluralité de premiers passages d'écoulement d'admission (11B).
  6. Échangeur thermique comprenant :
    le collecteur à empilement selon la revendication 4 ;
    une pluralité de premiers tube d'échange thermique (3) qui sont chacun reliés à la pluralité de premiers passages d'écoulement d'évacuation (11A) et à un côté admission de la pluralité de passages d'écoulement à rebours (11C) ; et
    une pluralité de seconds tubes d'échange thermique (6) qui sont chacun reliés à un coté évacuation de l'un des passages d'écoulement à rebours correspondants (11C) et à l'un des premiers passages d'écoulement d'admission correspondants (12B).
  7. Échangeur thermique selon la revendication 5 ou 6, dans lequel les tubes d'échange thermique comprennent chacun un tube plat.
  8. Appareil de climatisation comprenant l'échangeur thermique selon l'une quelconque des revendications 5 à 7,
    dans lequel le passage d'écoulement de distribution (12B) est configuré pour permettre au réfrigérant de sortir du passage d'écoulement de distribution (12B), vers la pluralité de premiers passages d'écoulement d'évacuation (11A) lorsque l'échangeur thermique agit comme un évaporateur.
  9. Appareil de climatisation comprenant l'échangeur thermique selon la revendication 6,
    dans lequel le passage d'écoulement de distribution (12B) est configuré pour permettre au réfrigérant de sortir du passage d'écoulement de distribution (12B), vers la pluralité de premiers passages d'écoulement d'évacuation (11A) lorsque l'échangeur thermique agit comme un évaporateur, et
    dans lequel la pluralité de premiers tubes d'échange thermique (3) est positionnée sur un côté ventilé par rapport à la pluralité de seconds tubes d'échange thermique (6) lorsque l'échangeur thermique agit comme un condenseur.
EP13884722.3A 2013-05-15 2013-05-15 Colonne stratifiée, échangeur de chaleur, et climatiseur Active EP2998680B1 (fr)

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EP3348945B1 (fr) * 2015-09-07 2021-03-17 Mitsubishi Electric Corporation Distributeur, collecteur stratifié, échangeur de chaleur et climatiseur
WO2018189892A1 (fr) * 2017-04-14 2018-10-18 三菱電機株式会社 Distributeur, échangeur de chaleur et dispositif à cycle de réfrigération
WO2020262699A1 (fr) * 2019-06-28 2020-12-30 ダイキン工業株式会社 Échangeur de chaleur et appareil de pompe à chaleur
JP6822525B2 (ja) * 2019-06-28 2021-01-27 ダイキン工業株式会社 熱交換器およびヒートポンプ装置
WO2021025156A1 (fr) * 2019-08-07 2021-02-11 ダイキン工業株式会社 Échangeur de chaleur et dispositif de pompe à chaleur
JP7313557B2 (ja) * 2020-06-05 2023-07-24 三菱電機株式会社 冷媒分配器、熱交換器および空気調和装置
WO2023148841A1 (fr) * 2022-02-02 2023-08-10 三菱電機株式会社 Échangeur de chaleur et dispositif de climatisation

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CN203940770U (zh) 2014-11-12
EP2998680A1 (fr) 2016-03-23
JPWO2014184918A1 (ja) 2017-02-23
JP6005268B2 (ja) 2016-10-12
EP2998680A4 (fr) 2017-02-01
WO2014184918A1 (fr) 2014-11-20

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