WO2013005729A1 - Échangeur de chaleur et climatiseur le comportant - Google Patents

Échangeur de chaleur et climatiseur le comportant Download PDF

Info

Publication number
WO2013005729A1
WO2013005729A1 PCT/JP2012/066944 JP2012066944W WO2013005729A1 WO 2013005729 A1 WO2013005729 A1 WO 2013005729A1 JP 2012066944 W JP2012066944 W JP 2012066944W WO 2013005729 A1 WO2013005729 A1 WO 2013005729A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
pipe
section
outlet pipe
Prior art date
Application number
PCT/JP2012/066944
Other languages
English (en)
Japanese (ja)
Inventor
円 上野
雄一 六角
理 浜口
Original Assignee
シャープ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by シャープ株式会社 filed Critical シャープ株式会社
Priority to CN201280031611.1A priority Critical patent/CN103620336B/zh
Publication of WO2013005729A1 publication Critical patent/WO2013005729A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • 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
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions

Definitions

  • the present invention relates to a side flow type parallel flow heat exchanger and an air conditioner equipped with the same.
  • a parallel flow type heat exchange in which a plurality of flat tubes are arranged between two header pipes so that a refrigerant passage inside the flat tubes communicates with the header pipe, and fins such as corrugated fins are arranged between the flat tubes.
  • the equipment is widely used in car air conditioners and building air conditioners.
  • a parallel flow heat exchanger described in Patent Document 1 includes a cylindrical hollow header, a refrigerant inlet pipe connected to the refrigerant inflow chamber of the header, and a plurality of tubes connected to the refrigerant inflow chamber.
  • the refrigerant inflow chamber is divided into a plurality of inflow partition chambers, the refrigerant inlet pipe is branched into a corresponding number of branch pipes, and the branch pipes are connected to the inflow partition chambers so that the refrigerant is evenly divided into the tubes.
  • the parallel flow heat exchanger described in Patent Document 2 has a configuration in which a vertical tube is combined with a horizontal header.
  • a refrigerant dispersion pipe that communicates with the refrigerant inlet pipe is disposed along the length direction thereof.
  • a plurality of refrigerant dispersion holes are provided in the peripheral wall of the refrigerant dispersion tube so that the liquid refrigerant flowing into the lower header through the refrigerant inlet pipe is evenly distributed to the tubes.
  • the heat exchanger described in Patent Document 3 is not a parallel flow type but a fin-and-tube type, and even in this heat exchanger, an equal distribution of refrigerant is pursued.
  • a crushing portion is provided in an inlet pipe connected to a plurality of heat exchange paths, and a flow path resistance capable of diverting an appropriate amount of refrigerant is provided.
  • JP-A-6-74609 Japanese Patent Laid-Open No. 6-159983 JP-A-9-145198
  • a parallel flow heat exchanger includes two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes.
  • the refrigerant flow path of the parallel flow heat exchanger is as follows. The refrigerant flows into a predetermined section inside one of the header pipes through an inlet pipe, flows into the other of the header pipes through the plurality of flat tubes connected to the section, It is divided up and down by the partition plate in the other header pipe, and finally flows out from the upper outlet pipe and the lower outlet pipe, than the refrigerant flow path from the inlet pipe to the lower outlet pipe, The refrigerant tends to enter the refrigerant flow path from the inlet pipe to the upper outlet pipe.
  • the plurality of flat tubes connected to the section through which the refrigerant flows from the inlet pipe has a comparatively large number on the upper side and a comparatively small number on the lower side. It is preferable that the partition plate is divided up and down.
  • the inlet pipe is connected to an upper position of the section into which the refrigerant flows from the inlet pipe.
  • the flat tubes are distributed more in the refrigerant flow path from the inlet pipe to the upper outlet pipe than in the refrigerant flow path from the inlet pipe to the lower outlet pipe. It is preferable that
  • a plurality of the inlet pipes are connected to one of the header pipes, and the upper outlet pipe and the lower outlet pipe are provided for each of the plurality of inlet pipes. Preferably it is.
  • one of a plurality of branch pipes separated from one refrigerant pipe is connected to each of the plurality of inlet pipes, and the refrigerant pipe is connected to the plurality of branch pipes. It is preferable that the flattening is performed immediately upstream of the location where the pipe branches.
  • the refrigerant pipe is flattened in a side-by-side direction of the plurality of branch pipes arranged side by side.
  • the air conditioner according to the present invention is one in which the parallel flow heat exchanger having the above configuration is mounted on an indoor unit or an outdoor unit.
  • the refrigerant in the gas-liquid mixed state flowing into the parallel flow heat exchanger from the inlet pipe tends to move downward as a natural tendency.
  • the refrigerant is divided into two parts up and down, and finally from both the upper outlet pipe and the lower outlet pipe
  • a partition plate is provided to allow the refrigerant to flow out, and the refrigerant is more likely to enter the refrigerant flow path from the inlet pipe to the upper outlet pipe than the refrigerant flow path from the inlet pipe to the lower outlet pipe.
  • the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.
  • FIG. 2 is a vertical cross-sectional view of a heat exchanger cut along a line II-II in FIG. 1. It is a front view of the heat exchanger which concerns on 2nd Embodiment of this invention. It is a front view of the heat exchanger which concerns on 3rd Embodiment of this invention. It is a front view of the heat exchanger which concerns on 4th Embodiment of this invention. It is a front view of the heat exchanger which concerns on 5th Embodiment of this invention. It is an expanded sectional view of a part of FIG.
  • the upper side of the paper is the upper side of the heat exchanger
  • the lower side of the paper is the lower side of the heat exchanger
  • the parallel flow type heat exchanger 1A is a side flow type, and includes two vertical header pipes 2 and 3 and a plurality of horizontal flat tubes 4 arranged therebetween.
  • the header pipes 2 and 3 are arranged in parallel in the horizontal direction at intervals, and the flat tubes 4 are arranged at a predetermined pitch in the vertical direction. Since the parallel flow type heat exchanger 1 is installed at various angles according to design requirements at the stage of actually mounting on equipment, “vertical direction” and “horizontal direction” in this specification should not be strictly interpreted. Absent. It should be understood as a mere measure of direction.
  • the flat tube 4 is an elongated molded product obtained by extruding a metal, and as shown in FIG. 2, a refrigerant passage 5 through which a refrigerant flows is formed. Since the flat tube 4 is disposed so that the extrusion direction, which is the longitudinal direction, is horizontal, the refrigerant flow direction of the refrigerant passage 5 is also horizontal. A plurality of refrigerant passages 5 having the same cross-sectional shape and cross-sectional area are arranged in the left-right direction in FIG. 2, and therefore the vertical cross section of the flat tube 4 has a harmonica shape. Each refrigerant passage 5 communicates with the inside of the header pipes 2 and 3.
  • Corrugated fins 6 are arranged between the adjacent flat tubes 4. Of the corrugated fins 6 arranged in the vertical direction, side plates 7 are arranged outside the uppermost and lowermost ones.
  • the header pipes 2 and 3, the flat tubes 4, the corrugated fins 6, and the side plates 7 are all made of a metal having good heat conductivity such as aluminum.
  • the flat tubes 4 are the flat tubes 4 with respect to the header pipes 2 and 3.
  • the side plate 7 is fixed to the corrugated fin 6 by brazing or welding, respectively.
  • the inside of the header pipe 2 is partitioned into four sections S1, S2, S3, and S4 by three partition plates P1, P2, and P3.
  • the section S1 is responsible for four of the total 24 flat tubes 4, the section S2 is responsible for eight, the section S3 is responsible for seven, and the section S4 is responsible for five.
  • the inside of the header pipe 3 is partitioned into three sections S5, S6, and S7 by two partition plates P4 and P5.
  • the section S5 is responsible for eight of the total 24 flat tubes 4, the section S6 is responsible for six, and the section S7 is responsible for ten.
  • the total number of the flat tubes 4 described above, the number of partition plates inside each header pipe and the number of partitions partitioned thereby, and the number of flat tubes 4 that each partition is responsible for are only examples, and limit the invention. is not. The same applies to the second and subsequent embodiments.
  • the entrance pipe 8 is connected to the section S6.
  • the upper outlet pipe 9 is connected to the section S1, and the lower outlet pipe 10 is connected to the section S4.
  • the inlet pipe 8 is disposed at the center in the vertical direction of the section S6.
  • the six flat tubes 4 whose one ends are connected to the partition S6 are divided into the upper four and the lower two by the partition plate P2.
  • the upper four flat tubes 4 connect the section S6 and the section S2 to form the refrigerant flow path A1.
  • the lower two flat tubes 4 connect the sections S6 and S3 to form the refrigerant flow path A2.
  • Refrigerant flow paths A1 and A2 are symbolized by block arrows, respectively.
  • the four flat tubes 4 connecting the section S2 and the section S5 form a refrigerant flow path B.
  • the four flat tubes 4 connecting the section S5 and the section S1 form a refrigerant flow path C.
  • the five flat tubes 4 connecting the section S3 and the section S7 form a refrigerant flow path D.
  • the five flat tubes 4 connecting the section S7 and the section S4 form a refrigerant flow path E.
  • the function of the parallel flow type heat exchanger 1A is as follows.
  • the refrigerant is supplied to the compartment S6 through the inlet pipe 8
  • the refrigerant goes to the compartments S2 and S3 through the refrigerant flow paths A1 and A2.
  • the refrigerant that has entered the compartment S2 is turned back through the refrigerant flow path B toward the compartment S5.
  • the refrigerant that has entered the compartment S5 turns back there, and passes through the refrigerant flow path C toward the compartment S1.
  • the refrigerant that has entered the compartment S1 flows out from the upper outlet pipe 9.
  • the refrigerant that has entered the section S3 is turned back through the refrigerant flow path D and heads for the section S7.
  • the refrigerant that has entered the compartment S7 is turned back through the refrigerant flow path E to the compartment S4.
  • the refrigerant that has entered the compartment S4 flows out from the lower outlet pipe 10.
  • the six flat tubes 4 connected to the section S6 are divided up and down by a partition plate P2.
  • the partition plate P2 is compared with four on the upper side and two on the lower side and on the upper side.
  • the refrigerant flow from the inlet pipe 8 to the upper outlet pipe 9 rather than the refrigerant flow path from the inlet pipe 8 to the lower outlet pipe 10 is divided so that a large number is formed and the lower one forms a comparatively small number. It is easy for refrigerant to enter the road. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, particularly when used as an evaporator, gas-liquid separation is performed inside the header pipe 3 where the inlet pipe 8 is located, and the liquid refrigerant is lower. In spite of being easy to flow into the other refrigerant flow path, the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.
  • the partition plate is slidable so that the height can be changed, it becomes easier to prevent drift according to the amount of refrigerant circulating and the dryness of the refrigerant.
  • FIG. 3 shows the structure of a side flow parallel flow heat exchanger according to the second embodiment of the present invention.
  • Components that are functionally common to the components of the first embodiment are denoted by the same reference numerals as those used in the first embodiment, and description thereof is omitted.
  • the third and subsequent embodiments are processed in the same manner.
  • the partition plate P2 divides the six flat tubes 4 connected to the section S6 into the same number of top and bottom, three on the top and three on the bottom. Yes.
  • the three flat tubes 4 connecting the sections S6 and S2 form the refrigerant flow path A1
  • the three flat tubes 4 connecting the sections S6 and S3 form the refrigerant flow path A2.
  • the position of the inlet pipe 8 is different from that of the parallel flow type heat exchanger 1A of the first embodiment. That is, the inlet pipe 8 is not positioned at the center in the up-down direction of the section S6 but at a position above the section S6.
  • the refrigerant flow path A1 Most of the refrigerant that has flowed into the section S6 from the inlet pipe 8 is directed to the refrigerant flow path A1 due to its own movement inertia. For this reason, although the refrigerant flow path A1 and the refrigerant flow path A2 are formed of the same number of flat tubes 4, the refrigerant flow path A1 tends to enter. As a result, the refrigerant is more likely to enter the refrigerant flow path from the inlet pipe 8 to the upper outlet pipe 9 than the refrigerant flow path from the inlet pipe 8 to the lower outlet pipe 10.
  • the refrigerant tends to flow toward the lower refrigerant flow path originally, particularly when used as an evaporator, gas-liquid separation is performed inside the header pipe 3 where the inlet pipe 8 is located, and the liquid refrigerant is lower.
  • the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.
  • FIG. 4 shows the structure of a side flow type parallel flow heat exchanger according to the third embodiment of the present invention.
  • the partition plate P2 has four upper flat tubes 4 connected to the section S6 as in the parallel flow type heat exchanger 1A of the first embodiment. It is placed in a position that is divided into two. Similarly to the parallel flow heat exchanger 1B of the second embodiment, the inlet pipe 8 is disposed at a position above the section S6.
  • the refrigerant flow path A1 has more flat tubes 4 than the refrigerant flow path A2, and the upper inlet pipe 8 is connected to the upper position of the section S6, so that the refrigerant flowing into the section S6 flows into the refrigerant flow. Easy to enter road A1. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path, the amount of the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.
  • the refrigerant flow path B is constituted by four flat tubes 4, and the refrigerant flow path C is constituted by five flat tubes 4.
  • the refrigerant flow path D is composed of five flat tubes 4, and the refrigerant flow path E is composed of four flat tubes 4. Therefore, the number of the flat tubes 4 included in the refrigerant passages (A1, B, C) from the inlet pipe 8 to the upper outlet pipe 9 and the refrigerant passages (A2, D, E from the inlet pipe 8 to the lower outlet pipe 10). ) Includes 13 flat tubes 4 and 11 flat tubes. Thereby, the heat radiation area of the refrigerant passage from the inlet pipe 8 to the upper outlet pipe 9 is increased, and the heat exchange amount is increased.
  • FIG. 5 shows the structure of a side flow parallel flow heat exchanger according to a fourth embodiment of the present invention.
  • the parallel flow type heat exchanger 1D of the fourth embodiment is different from the parallel flow type heat exchangers 1A, 1B, 1C from the first embodiment to the third embodiment in that the partition plates in the header pipes 2, 3 The number and the number of compartments provided thereby, and the position of the upper outlet pipe 9 and the lower outlet pipe 10. That is, it is as follows.
  • the inside of the header pipe 2 is partitioned into two sections S1 and S2 by a single partition plate P1.
  • the section S1 is responsible for 13 of the total 24 flat tubes 4, and the section S2 is responsible for 11.
  • the inside of the header pipe 3 is partitioned into three sections S3, S4, and S5 by two partition plates P2 and P3.
  • the section S3 is responsible for nine of the 24 flat tubes 4, the section S4 is responsible for six, and the section S5 is responsible for nine.
  • the entrance pipe 8 is connected to the section S4.
  • the upper outlet pipe 9 is connected to the section S3, and the lower outlet pipe 10 is connected to the section S5.
  • the inlet pipe 8 is not located at the center in the up-down direction of the section S4 but at a position above the section S4.
  • the six flat tubes 4 whose one ends are connected to the partition S4 are divided into the upper four and the lower two by the partition plate P1.
  • the upper four flat tubes 4 connect the section S4 and the section S1 to form the refrigerant flow path A1.
  • the two lower flat tubes 4 connect the section S4 and the section S2 to form the refrigerant flow path A2.
  • the function of the parallel flow type heat exchanger 1D is as follows.
  • the refrigerant goes to the sections S1 and S2 through the refrigerant flow paths A1 and A2.
  • the refrigerant that has entered the section S1 is turned back through the refrigerant flow path B toward the section S3.
  • the refrigerant that has entered the compartment S3 flows out from the upper outlet pipe 9.
  • the refrigerant that has entered the section S2 is turned back through the refrigerant flow path C and then travels to the section S5.
  • the refrigerant that has entered the compartment S5 flows out from the lower outlet pipe 10.
  • the refrigerant flow path A1 has more flat tubes 4 than the refrigerant flow path A2, and the upper inlet pipe 8 is connected to the upper position of the section S4, so that the refrigerant flowing into the section S4 flows into the refrigerant flow. Easy to enter road A1. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, especially when used as an evaporator, the liquid refrigerant tends to flow downward, but the refrigerant flows into the upper and lower refrigerant flow paths. In a well-balanced manner, improving the heat exchange efficiency.
  • the refrigerant flow path B and the refrigerant flow path C are each composed of nine flat tubes 4.
  • the number of flat tubes 4 included in the refrigerant passage (A1, B) from the inlet pipe 8 to the upper outlet pipe 9 and the refrigerant passage (A2, C) from the inlet pipe 8 to the lower outlet pipe 10 are included.
  • the number of the flat tubes 4 is 13 for the former and 11 for the latter.
  • the upper outlet pipe 9 and the lower outlet pipe are connected to a header pipe different from the header pipe to which the inlet pipe 8 is connected.
  • the upper outlet pipe 9 and the lower outlet pipe 10 are also connected to the same header pipe to which the inlet pipe 8 is connected. For this reason, design and enforcement of refrigerant piping are easy.
  • FIG. 6 shows the structure of a side flow parallel flow heat exchanger according to a fifth embodiment of the present invention.
  • the parallel flow heat exchanger 1E according to the fifth embodiment is characterized by a configuration in which the parallel flow heat exchanger 1D according to the fourth embodiment is stacked in two upper and lower stages.
  • the header pipes 2 and 3 of the parallel flow type heat exchanger 1E are longer than the header pipes 2 and 3 of the first to fourth embodiments.
  • the total number of the flat tubes 4 is 34, which is larger than the first to fourth embodiments.
  • the internal space of the header pipe 2 is divided vertically by the intermediate partition plate MP1, and the internal space of the header pipe 3 is divided vertically by the intermediate partition plate MP2.
  • the intermediate partition plates MP1 and MP2 are at the same height, and the parallel flow heat exchanger 1E is divided vertically by the intermediate partition plates MP1 and MP2.
  • an arrangement of inlet pipe, upper outlet pipe and lower outlet pipe is arranged.
  • the section above the intermediate partition plate MP1 is partitioned into two sections S1H and S2H by one partition plate P1H.
  • the section S1H is responsible for nine of the 34 flat tubes 4, and the section S2H is responsible for eight.
  • the section below the intermediate partition plate MP1 is partitioned into two partitions S1L and S2L by one partition plate P1L.
  • the section S1L is responsible for nine of the 34 flat tubes 4, and the section S2L is responsible for eight.
  • the section above the intermediate partition plate MP2 is partitioned into three partitions S3H, S4H, and S5H by two partition plates P2H and P3H.
  • the section S3H is responsible for five of the total 34 flat tubes 4, the section S4H is responsible for six, and the section S5H is responsible for six.
  • the section below the intermediate partition plate MP2 is partitioned into three sections S3L, S4L, and S5L by two partition plates P2L and P3L.
  • the section S3L is responsible for five of the total 34 flat tubes 4, the section S4L is responsible for six, and the section S5L is responsible for six.
  • An inlet pipe 8H is connected to the section S4H.
  • An upper outlet pipe 9H is connected to the section S3H, and a lower outlet pipe 10H is connected to the section S5H.
  • the inlet pipe 8H is not positioned at the center in the vertical direction of the section S4H, but is disposed at a position above the section S4H.
  • the entrance pipe 8L is connected to the section S4L.
  • the upper outlet pipe 9L is connected to the section S3L, and the lower outlet pipe 10L is connected to the section S5L.
  • the inlet pipe 8L is not positioned at the center in the up-down direction of the section S4L, but is disposed at a position above the section S4L.
  • the six flat tubes 4 whose one ends are connected to the partition S4H are divided into the upper four and the lower two by the partition plate P1H.
  • the upper four flat tubes 4 connect the section S4H and the section S1H to form a refrigerant flow path A1H.
  • the two lower flat tubes 4 connect the section S4H and the section S2H to form a refrigerant flow path A2H.
  • the five flat tubes 4 connecting the section S1H and the section S3H form a refrigerant flow path BH.
  • the six flat tubes 4 connecting the section S2H and the section S5H form a refrigerant channel CH.
  • the six flat tubes 4 whose one ends are connected to the partition S4L are divided into the upper four and the lower two by the partition plate P1L.
  • the upper four flat tubes 4 connect the section S4L and the section S1L to form a refrigerant flow path A1L.
  • the lower two flat tubes 4 connect the section S4L and the section S2L to form a refrigerant flow path A2L.
  • the five flat tubes 4 connecting the section S1L and the section S3L form a refrigerant flow path BL.
  • the six flat tubes 4 connecting the section S2L and the section S5L form a refrigerant flow path CL.
  • the functions of the parallel flow type heat exchanger 1E are as follows.
  • the refrigerant goes to the sections S1H and S2H through the refrigerant flow paths A1H and A2H.
  • the refrigerant that has entered the section S1H is turned back there and travels to the section S3H through the refrigerant flow path BH.
  • the refrigerant that has entered the section S3H flows out from the upper outlet pipe 9H.
  • the refrigerant that has entered the section S2H is turned back there and travels to the section S5H through the refrigerant channel CH.
  • the refrigerant that has entered the compartment S5H flows out from the lower outlet pipe 10H.
  • the refrigerant flow path A1H has more flat tubes 4 than the refrigerant flow path A2H, and the upper inlet pipe 8H is connected to the upper position of the section S4H, so that the refrigerant flowing into the section S4H flows into the refrigerant flow. Easy to enter road A1H. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, especially when used as an evaporator, the liquid refrigerant tends to flow downward, but the refrigerant flows into the upper and lower refrigerant flow paths. In a well-balanced manner, improving the heat exchange efficiency.
  • the number of tubes 4 is 9 for the former and 8 for the latter.
  • the refrigerant When the refrigerant is supplied to the section S4L through the inlet pipe 8L, the refrigerant goes to the sections S1L and S2L through the refrigerant flow paths A1L and A2L.
  • the refrigerant that has entered the section S1L is turned back there, and passes through the refrigerant flow path BL toward the section S3L.
  • the refrigerant that has entered the compartment S3L flows out of the upper outlet pipe 9L.
  • the refrigerant that has entered the section S2L turns back there, and travels to the section S5L through the refrigerant flow path CL.
  • the refrigerant that has entered the compartment S5L flows out of the lower outlet pipe 10L.
  • the refrigerant flow path A1L has more flat tubes 4 than the refrigerant flow path A2L, and the upper inlet pipe 8L is connected to the upper position of the section S4L, so that the refrigerant flowing into the section S4L flows into the refrigerant flow. Easy to enter road A1L. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, especially when used as an evaporator, the liquid refrigerant tends to flow downward, but the refrigerant flows into the upper and lower refrigerant flow paths. In a well-balanced manner, improving the heat exchange efficiency.
  • the number of tubes 4 is 9 for the former and 8 for the latter.
  • the inlet pipes 8H and 8L are connected to each of a plurality of branch pipes separated from the single refrigerant pipe 11.
  • the side connected to the inlet pipe 8H is a branch pipe 12H
  • the side connected to the inlet pipe 8L is a branch pipe 12L.
  • the shunt used in the fifth embodiment is of a type having two shunt pipes. If the number of inlet pipes exceeds 2, the shunt has a number of shunt pipes corresponding to that number. Can be used. Or what is necessary is just to respond
  • the refrigerant pipe 11 is branched by the flow divider 13 into the flow dividing pipe 12H and the flow dividing pipe 12L.
  • the diversion pipes 12H and 12L are connected to the diversion device 13 in a side-by-side state, and are parallel to each other at the connection location.
  • the refrigerant pipe 11 is formed in such a manner that one line parallel to these center lines is drawn at the center between the center lines of the branch pipes 12H and 12L that are parallel to each other, and the center line is aligned with the line. Be placed.
  • the refrigerant pipe 11 is flattened at a branching point, that is, immediately upstream of the flow divider 13, and the part is a flat part 11a.
  • the refrigerant pipe 11 is flattened in the side-by-side direction of the two branch pipes 12H and 12L arranged side by side.
  • the flow rate of the refrigerant that has passed through the refrigerant pipe 11 increases at the flat portion 11a, and strikes the tip of the diversion wall 13a inside the diversion device 13 with force. .
  • the flow velocity in this way the refrigerant can be easily divided equally. Further, the flow is stabilized by dividing the refrigerant against the flow dividing wall 13a inside the flow divider 13.
  • the flattening in the side-by-side direction of the diverter pipes 12H and 12L causes the refrigerant to hit the diverting wall 13a without spreading, making it easier to divert more evenly.
  • Parallel flow type heat exchangers 1A, 1B, 1C, 1D, and 1E can be mounted on a separate air conditioner.
  • a separate type air conditioner is composed of an outdoor unit and an indoor unit.
  • the outdoor unit includes a compressor, a four-way valve, an expansion valve, an outdoor heat exchanger, an outdoor fan, and the like.
  • the indoor unit is an indoor heat exchanger, a room Includes an internal blower.
  • the outdoor heat exchanger functions as an evaporator during heating operation and functions as a condenser during cooling operation.
  • the indoor heat exchanger functions as a condenser during heating operation and functions as an evaporator during cooling operation.
  • FIG. 8 shows a basic configuration of a separate air conditioner that uses a heat pump cycle as a refrigeration cycle.
  • the heat pump cycle 101 includes a compressor 102, a four-way valve 103, an outdoor heat exchanger 104, a decompression / expansion device 105, and an indoor heat exchanger 106 connected in a loop.
  • the compressor 102, the four-way valve 103, the heat exchanger 104, and the decompression / expansion device 105 are accommodated in the casing of the outdoor unit, and the heat exchanger 106 is accommodated in the casing of the indoor unit.
  • An outdoor fan 107 is combined with the heat exchanger 104, and an indoor fan 108 is combined with the heat exchanger 106.
  • the blower 107 includes a propeller fan, and the blower 108 includes a cross flow fan.
  • the side flow parallel flow heat exchangers 1A, 1B, 1C, 1D, and 1E according to the present invention can be used as components of the heat exchanger 106 of the indoor unit.
  • the heat exchanger 106 is a combination of three heat exchangers 106A, 106B, 106C like a roof that covers the blower 108, and any one of the heat exchangers 106A, 106B, 106C is a parallel flow heat exchanger. 1A, 1B, 1C, 1D, 1E.
  • Fig. 8 shows the state during heating operation.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the indoor heat exchanger 106 where it dissipates heat and condenses.
  • the refrigerant exiting the heat exchanger 106 enters the outdoor heat exchanger 104 from the decompression / expansion device 105 and expands there, takes heat from the outdoor air, and returns to the compressor 102.
  • the airflow generated by the indoor fan 108 promotes heat dissipation from the heat exchanger 106, and the airflow generated by the outdoor fan 107 accelerates heat absorption of the heat exchanger 104.
  • FIG. 9 shows a state during cooling operation or defrosting operation.
  • the four-way valve 103 is switched so that the refrigerant flow is reversed from that during the heating operation. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the outdoor heat exchanger 104, where it dissipates heat and condenses.
  • the refrigerant exiting the heat exchanger 104 enters the heat exchanger 106 on the indoor side from the decompression / expansion device 105 and expands there, takes heat from the indoor air, and returns to the compressor 102.
  • the airflow generated by the outdoor fan 107 promotes heat dissipation from the heat exchanger 104, and the airflow generated by the indoor fan 108 promotes heat absorption of the heat exchanger 106.
  • Parallel flow type heat exchangers 1A, 1B, 1C, 1D, and 1E can also be used as heat exchangers 104 for outdoor units.
  • the present invention is widely applicable to side flow type parallel flow heat exchangers.

Landscapes

  • 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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

L'invention porte sur un échangeur de chaleur du type à écoulement parallèle (1A), lequel échangeur comprend des tuyaux collecteurs verticaux (2 et 3), et une pluralité de tubes plats horizontaux (4) qui relient les tuyaux collecteurs entre eux. Un réfrigérant s'écoule dans un compartiment (S6) dans le tuyau collecteur (3) à travers un tuyau d'entrée (8), et s'écoule dans le tuyau collecteur (2) à travers la pluralité de tubes plats reliés au compartiment (S6). La pluralité de tubes plats reliés au compartiment (S6) sont divisés verticalement par une plaque de séparation (P2) dans le tuyau collecteur (2), et le réfrigérant s'écoule finalement vers l'extérieur à partir d'un tuyau de sortie supérieur (9) et d'un tuyau de sortie inférieur (10). La position de la plaque de séparation est établie de sorte que le réfrigérant entre plus facilement dans un côté d'une trajectoire d'écoulement de réfrigérant allant à partir du tuyau d'entrée jusqu'au tuyau de sortie supérieur que d'une trajectoire d'écoulement de réfrigérant allant à partir du tuyau d'entrée jusqu'au tuyau de sortie.
PCT/JP2012/066944 2011-07-05 2012-07-03 Échangeur de chaleur et climatiseur le comportant WO2013005729A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201280031611.1A CN103620336B (zh) 2011-07-05 2012-07-03 热交换器和具有该热交换器的空气调节机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-149366 2011-07-05
JP2011149366A JP5073849B1 (ja) 2011-07-05 2011-07-05 熱交換器及びそれを搭載した空気調和機

Publications (1)

Publication Number Publication Date
WO2013005729A1 true WO2013005729A1 (fr) 2013-01-10

Family

ID=47277867

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/066944 WO2013005729A1 (fr) 2011-07-05 2012-07-03 Échangeur de chaleur et climatiseur le comportant

Country Status (3)

Country Link
JP (1) JP5073849B1 (fr)
CN (1) CN103620336B (fr)
WO (1) WO2013005729A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015039894A1 (fr) * 2013-09-17 2015-03-26 Volkswagen Aktiengesellschaft Échangeur thermique
JP2017519961A (ja) * 2014-05-28 2017-07-20 ダンフォス・マイクロ・チャンネル・ヒート・エクスチェンジャー・（ジャシン）・カンパニー・リミテッド 熱交換器
WO2019176089A1 (fr) * 2018-03-16 2019-09-19 東芝キヤリア株式会社 Échangeur de chaleur et dispositif à cycle frigorifique
EP3633306A4 (fr) * 2017-07-03 2020-06-03 Daikin Industries, Ltd. Échangeur de chaleur
US11274838B2 (en) 2017-07-05 2022-03-15 Hitachi-Johnson Controls Air Conditioning, Inc. Air-conditioner outdoor heat exchanger and air-conditioner including the same

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101454713B1 (ko) * 2012-12-31 2014-10-27 갑을오토텍(주) 듀얼 냉동시스템의 응축기 구조
CN103206811B (zh) * 2013-04-07 2015-09-30 广东美的制冷设备有限公司 平行流换热器及空调器
KR20140142802A (ko) * 2013-06-04 2014-12-15 삼성전자주식회사 실외 열교환기 및 공기조화기
JP6171765B2 (ja) * 2013-09-11 2017-08-02 ダイキン工業株式会社 熱交換器
JP6171766B2 (ja) * 2013-09-11 2017-08-02 ダイキン工業株式会社 熱交換器
JP6098451B2 (ja) * 2013-09-11 2017-03-22 ダイキン工業株式会社 熱交換器および空気調和機
US10184703B2 (en) * 2014-08-19 2019-01-22 Carrier Corporation Multipass microchannel heat exchanger
JP2016164062A (ja) * 2015-02-27 2016-09-08 株式会社デンソー 車両用空調装置
JP6366837B2 (ja) 2015-06-17 2018-08-01 三菱電機株式会社 冷媒回路及び空気調和機
CN105135754B (zh) * 2015-09-28 2017-06-16 江苏宝奥兰空调设备有限公司 一种板式换热器及制冷系统
CN105263301B (zh) * 2015-11-12 2017-12-19 深圳市研派科技有限公司 一种液冷散热系统及其液体散热排
CN107084452A (zh) * 2017-06-06 2017-08-22 青岛易图令科技有限公司 空调室外机及空调
JP6897478B2 (ja) * 2017-10-11 2021-06-30 株式会社デンソー 熱交換器
CN110779353A (zh) * 2019-11-18 2020-02-11 珠海格力电器股份有限公司 换热结构及换热器
JP7470909B2 (ja) * 2020-02-03 2024-04-19 東芝ライフスタイル株式会社 マイクロチャネル熱交換器および空気調和機
JP2022056998A (ja) * 2020-09-30 2022-04-11 三菱重工サーマルシステムズ株式会社 熱交換器、及び車両用空調装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4559994A (en) * 1983-05-18 1985-12-24 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg Passenger vehicle heat exchanger arrangement
FR2634546A1 (fr) * 1988-07-20 1990-01-26 Valeo Dispositif d'echangeur de chaleur pour plusieurs circuits de refroidissement utilisant un meme fluide caloporteur
JPH0330085U (fr) * 1989-07-31 1991-03-25
JPH05312492A (ja) * 1992-05-14 1993-11-22 Showa Alum Corp 熱交換器
US20080023182A1 (en) * 2006-07-25 2008-01-31 Henry Earl Beamer Dual mode heat exchanger assembly

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0674609A (ja) * 1992-08-31 1994-03-18 Showa Alum Corp 熱交換器
JP3454647B2 (ja) * 1996-11-07 2003-10-06 東芝キヤリア株式会社 空気調和機
KR100518856B1 (ko) * 2003-09-04 2005-09-30 엘지전자 주식회사 플랫 튜브 열 교환기
CN101788236A (zh) * 2009-05-25 2010-07-28 浙江创新汽车空调有限公司 复合节能型汽车热交换器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4559994A (en) * 1983-05-18 1985-12-24 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg Passenger vehicle heat exchanger arrangement
FR2634546A1 (fr) * 1988-07-20 1990-01-26 Valeo Dispositif d'echangeur de chaleur pour plusieurs circuits de refroidissement utilisant un meme fluide caloporteur
JPH0330085U (fr) * 1989-07-31 1991-03-25
JPH05312492A (ja) * 1992-05-14 1993-11-22 Showa Alum Corp 熱交換器
US20080023182A1 (en) * 2006-07-25 2008-01-31 Henry Earl Beamer Dual mode heat exchanger assembly

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015039894A1 (fr) * 2013-09-17 2015-03-26 Volkswagen Aktiengesellschaft Échangeur thermique
CN105518406A (zh) * 2013-09-17 2016-04-20 大众汽车有限公司 热交换器
CN105518406B (zh) * 2013-09-17 2018-01-16 大众汽车有限公司 热交换器
JP2017519961A (ja) * 2014-05-28 2017-07-20 ダンフォス・マイクロ・チャンネル・ヒート・エクスチェンジャー・（ジャシン）・カンパニー・リミテッド 熱交換器
US10591227B2 (en) 2014-05-28 2020-03-17 Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. Heat exchanger including a mixing and redistribution header
EP3633306A4 (fr) * 2017-07-03 2020-06-03 Daikin Industries, Ltd. Échangeur de chaleur
US11274838B2 (en) 2017-07-05 2022-03-15 Hitachi-Johnson Controls Air Conditioning, Inc. Air-conditioner outdoor heat exchanger and air-conditioner including the same
WO2019176089A1 (fr) * 2018-03-16 2019-09-19 東芝キヤリア株式会社 Échangeur de chaleur et dispositif à cycle frigorifique

Also Published As

Publication number Publication date
CN103620336A (zh) 2014-03-05
JP2013015289A (ja) 2013-01-24
JP5073849B1 (ja) 2012-11-14
CN103620336B (zh) 2016-05-18

Similar Documents

Publication Publication Date Title
JP5073849B1 (ja) 熱交換器及びそれを搭載した空気調和機
US9651317B2 (en) Heat exchanger and air conditioner
US10465955B2 (en) Heat exchanger and air conditioning apparatus
CN108139089B (zh) 空气调节机的室外机及室内机
KR101462176B1 (ko) 열교환기
US10309701B2 (en) Heat exchanger and air conditioner
JP5858478B2 (ja) パラレルフロー型熱交換器及びそれを搭載した空気調和機
US10041710B2 (en) Heat exchanger and air conditioner
KR20160131577A (ko) 공기조화기의 열교환기
JP2013002688A (ja) パラレルフロー型熱交換器及びそれを搭載した空気調和機
JP2013002774A (ja) パラレルフロー型熱交換器及びそれを搭載した空気調和機
JP2011102650A (ja) 熱交換器及びそれを搭載した空気調和機
JP6466047B1 (ja) 熱交換器及び空気調和装置
JP6120978B2 (ja) 熱交換器及びそれを用いた空気調和機
WO2018154972A1 (fr) Unité d'échange de chaleur
KR101989096B1 (ko) 공기조화기의 열교환기
JP2010112580A (ja) 熱交換器
JP6661880B2 (ja) 空気調和機
JP2020112274A (ja) 熱交換器
JP5940895B2 (ja) パラレルフロー型熱交換器及びそれを搭載した空気調和機
JP2011214759A (ja) 空気調和装置の室外ユニット
JP5763436B2 (ja) パラレルフロー型熱交換器及びそれを搭載した空気調和機
JP2012042128A (ja) 熱交換器及びそれを搭載した空気調和機
WO2018061359A1 (fr) Échangeur de chaleur et dispositif à cycle frigorifique
JP6537868B2 (ja) 熱交換器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12807897

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12807897

Country of ref document: EP

Kind code of ref document: A1