[go: up one dir, main page]

WO2019058847A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

Info

Publication number
WO2019058847A1
WO2019058847A1 PCT/JP2018/030888 JP2018030888W WO2019058847A1 WO 2019058847 A1 WO2019058847 A1 WO 2019058847A1 JP 2018030888 W JP2018030888 W JP 2018030888W WO 2019058847 A1 WO2019058847 A1 WO 2019058847A1
Authority
WO
WIPO (PCT)
Prior art keywords
hole
heat exchanger
tubes
reduction process
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/030888
Other languages
English (en)
Japanese (ja)
Inventor
石井　裕
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Holdings Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Holdings Corp filed Critical Sanden Holdings Corp
Publication of WO2019058847A1 publication Critical patent/WO2019058847A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow 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
    • F28F17/00—Removing ice or water from heat-exchange apparatus

Definitions

  • the present invention relates to a heat exchanger.
  • An object of the present invention is to suppress frost formation more effectively.
  • the heat exchanger according to one aspect of the present invention is Let directions orthogonal to each other be a first direction, a second direction, and a third direction, A plurality of through holes are provided extending in the first direction and spaced in the second direction, and a plurality of through holes provided in the first direction and spaced in the third direction are formed in each of the through holes.
  • Piping members through which the heat medium flows A plurality of plate members fixed between adjacent piping members, extending in a third direction and spaced apart in the first direction; Heat exchange is performed between the heat medium flowing through the through hole of the piping member and the air flowing in the third direction around the piping member and around the plate member, With respect to the through holes formed on the windward side, reduction processing is performed to make the cross-sectional area smaller than that of the through holes formed on the windward side.
  • the flow rate of the heat medium decreases on the windward side, and the temperature difference with the air is suppressed, so frost formation can be suppressed more effectively.
  • FIG. 1 is a diagram showing a heat exchanger.
  • the heat exchanger 11 functions as an evaporator in a heat pump cycle and a refrigeration circuit, such as a car air conditioner and a showcase.
  • the aluminum heat exchanger 11 includes a pair of upper and lower headers 12, a plurality of tubes 13 (pipe members), and a plurality of fins 14 (plate members).
  • the pair of headers 12 extend in the lateral direction and are spaced apart in the longitudinal direction.
  • the header 12 is formed by a cylindrical pipe whose both ends are closed, and the inside is divided by the partition wall 17 into compartments aligned in the lateral direction.
  • the upper header 12 is internally divided into a section 12A at one end in the lateral direction and a section 12B at the other end in the lateral direction, and an inlet 15 is provided in the section 12A at the one end in the lateral direction.
  • the lower header 12 is internally divided into a section 12C at one end in the lateral direction and a section 12D at the other end in the lateral direction, and a discharge port 16 is provided in the section 12D at the other end in the lateral direction.
  • Each tube 13 extends in the longitudinal direction, and the upper end and the lower end are respectively connected to the header 12 and provided at equal intervals along the lateral direction.
  • the tube 13 has a laterally thin flat shape, and both ends thereof are in communication with the inside of the header 12 and brazed to the header 12.
  • 13a to 13l are sequentially arranged from one end in the lateral direction to the other end.
  • the tube 13 d and the tube 13 e are partitioned by the partition wall 17, and in the lower header 12, the tube 13 h and the tube 13 i are partitioned by the partition wall 17.
  • Each fin 14 is fixed by brazing between adjacent tubes 13.
  • a flow path is formed by the header 12 and the tube 13, through which a refrigerant (heat medium) flows. That is, first, it flows into the section 12A on one end side in the lateral direction of the upper header 12 through the inflow port 15, is distributed to the tubes 13a to 13d, and then flows into the section 12C on one end side in the lateral direction of the lower header 12. Next, after being distributed to the tubes 13e to 13h, they flow into the section 12B on the other end side in the lateral direction in the upper header 12 and then are distributed to the tubes 13i to 13l and then to the other end side in the lateral direction on the lower header 12. It flows into the compartment 12 D and is discharged through the discharge port 16. Thus, as the coolant flows through each tube 13, it exchanges heat with the air flowing around the tubes 13 and the fins 14. That is, the refrigerant evaporates and evaporates to raise the temperature by heat absorption, whereby one air is cooled.
  • a refrigerant heat medium
  • FIG. 2 is a view showing a tube and a fin.
  • (A) in the figure is a view of the tube 13 and the fins 14 as viewed from the windward side in the width direction.
  • the fins 14 are corrugated fins in which thin plates are formed in a rectangular wave shape. Thereby, it becomes possible to integrate and form a plurality of thin plates provided at intervals in the longitudinal direction.
  • Each region surrounded by the fins 14 and the tube 13 serves as a ventilation passage 21 for flowing air in the width direction.
  • (B) in the figure is a view of the tube 13 and the fins 14 as viewed from the longitudinal direction, and the tube 13 is shown in cross section.
  • the tube 13 is formed with a plurality of through holes 22 extending in the longitudinal direction and aligned along the width direction, and the coolant flows through the through holes 22.
  • One end on the windward side in the width direction in the fin 14 is flush and unified so as to be aligned with one end of the tube 13.
  • FIG. 3 is a view showing a tube.
  • the tubes 13a disposed on the upstream side through which the refrigerant flows are shown, but the tubes 13b, 13c, and 13d have the same configuration.
  • (A) in the figure is a view of the header 12 and the tube 13a viewed from the lateral direction
  • (b) in the figure is a view showing an AA cross section
  • (c) in the figure is a BB cross section FIG.
  • a compressed portion 31 is formed by pressing from both sides along the horizontal direction.
  • the closed part 32 which completely closed the flow path is formed.
  • FIG. 4 is an enlarged view of the end of the tube.
  • An insertion hole 33 is formed in the header 12, and one end side of the tube 13 a is inserted into the insertion hole 33.
  • a compression portion 34 is formed by pressing from both sides along the width direction.
  • the compression part 31 is formed in the range in which the compression part 34 is formed.
  • the die for press processing is designed so that the compression unit 31 and the compression unit 34 can be simultaneously processed.
  • a mold for originally pressing the tube 13a from both sides along the lateral direction is required, and a structure capable of press-forming the compression section 31 may be added thereto. .
  • FIG. 5 is a view schematically showing the state of frost formation.
  • the tubes 13a to 13f are illustrated, the through holes 22 through which the refrigerant flows are hatched, and the through holes 22 through which the refrigerant does not flow are illustrated in white.
  • the refrigerant does not flow because the through hole 22 on the upwind side is blocked, and the refrigerant flows to the through hole 22 on the downwind side than that.
  • the through-hole 22 on the upwind side acts as a heat insulating part because the refrigerant does not flow, and the temperature difference with air is suppressed, so it is possible to suppress frost formation on the tips of the tubes 13a to 13d.
  • frost 35 gradually adheres to the fins 14 positioned between the tubes 13a and 13b, between 13b and 13c, and between 13c and 13d, but in a small amount.
  • the refrigerant also flows through the through hole 22 on the upwind side, but heat exchange with air has already been performed on the upstream side, and the refrigerant temperature rises. Since the temperature difference with air is suppressed, frosting is unlikely to occur originally.
  • frost 36 which gradually adheres to the fins 14 located between the tubes 13d and 13e and between 13e and 13f.
  • FIG. 6 is the figure which showed typically the mode of the frost formation in a comparative example.
  • the tubes 13a to 13f are shown, and the through holes 22 through which the refrigerant flows are shown by hatching, and the refrigerant flows through all the through holes 22 including the through hole 22 on the windward side. Therefore, the frost 37 easily adheres to the tips of the upstream tubes 13a to 13d. Furthermore, the frost 38 easily adheres to the fins 14 positioned between the tubes 13a and 13b, between 13b and 13c, and between 13c and 13d, so that the air passage 21 is easily closed. As described above, by forming the compression portion 31 on the upstream side tubes 13a to 13d and closing the through hole 22 formed on the windward side, frost formation can be effectively suppressed.
  • the compression part 31 is formed only to the through-hole 22 formed in the windward side, it is possible to minimize the decrease in the heat exchange efficiency.
  • the compression section 31 is formed only by the tubes 13a to 13d on the upstream side among the plurality of tubes 13a to 13l, the decrease in heat exchange efficiency can be minimized.
  • the compression section 31 is formed by pressing the windward ends of the tubes 13a to 13d from both sides along the width direction, the processing can be easily performed. Further, if the compression section 31 and the compression section 34 are simultaneously press-processed, the number of steps and the cost will not be increased.
  • the compression portion 31 is formed only at the end portion on the upstream side along the longitudinal direction in the through hole 22, it can be processed more easily than forming the compression portion 31 over the entire length.
  • the closed portion 32 is formed only at the upstream end of the through hole 22 along the longitudinal direction, but the present invention is not limited to this.
  • the closed portion 32 is formed over the entire length of the through hole 22
  • FIG. 7 is a view showing a through hole in which a closed portion is formed over the entire length.
  • the compression portion 31 is formed over the entire length in the longitudinal direction of the tube 13 a, and thus the closed portion 32 is formed over the entire length of the through hole 22. This makes it possible to completely suppress the entry of the refrigerant.
  • the compressed portion 31 is formed to form the closed portion 32 which completely closes the through hole 22.
  • the present invention is not limited to this. That is, the through hole 22 formed on the windward side may be reduced only to make the cross-sectional area smaller than that of the through hole 22 formed on the windward side.
  • FIG. 8 is a view showing a through hole whose cross-sectional area is reduced.
  • a reduction part 41 whose cross-sectional area is reduced is formed in the inside of the compression part 31, only in the through hole 22 on the windward side.
  • a reduction part 41 whose cross-sectional area is reduced is formed.
  • the contraction portion 41 does not completely block the flow path, the flow rate of the refrigerant is reduced, which also suppresses the temperature difference from the air, and frost formation can be effectively suppressed.
  • one end on the windward side in the width direction in the fin 14 is flush and unified so as to be aligned with one end of the tube 13, but is not limited to this. That is, the fin 14 may be formed with an extending portion 42 extended on the windward side of the ventilation passage 21 along the width direction.
  • FIG. 9 is a view showing a fin in which an extension is formed.
  • the extension amounts (lengths) of the extensions 42 are uniform. There is no extension on the leeward side in the width direction of the fins 14. As described above, by forming the extension portion 42, even if the frosts 35 and 36 are gradually attached to the front end, it is possible to suppress that the air passage 21 is blocked.
  • the compression portion 31 is formed by pressing the tube 13 from both sides along the lateral direction, but the invention is not limited thereto. That is, since it is only necessary to close the through hole 22, the through hole 22 on the upwind side may be closed by the brazing material 43, for example.
  • FIG. 10 is a view showing a through hole closed by a brazing material. The brazing material 43 is brazed to the through-hole 22 on the upwind side, and the flow path is completely blocked. Thus, it is sufficient that the flow path can be closed without crushing the through hole 22.
  • all the tubes 13a to 13l may be made common, and only the upstream tubes 13a to 13d may be closed with the brazing material 43. As a result, it is not necessary to change the press die between the tubes 13a to 13d on the upstream side and the tubes 13e to 13l on the downstream side, and the cost increase can be suppressed.
  • the compression portion 31 is formed only on the upstream side tubes 13a to 13d, but the invention is not limited to this, and the compression portion 31 may be formed on all the tubes 13a to 13l. Good. As a result, it is not necessary to change the press die between the tubes 13a to 13d on the upstream side and the tubes 13e to 13l on the downstream side, and the cost increase can be suppressed.
  • the header 12 extends in the lateral direction, and the tube 13 extends in the longitudinal direction.
  • the present invention is not limited thereto.
  • the header 12 extends in the longitudinal direction and the tube 13 extends in the lateral direction It may be

Landscapes

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

Abstract

Le problème décrit par la présente invention est d'empêcher une formation de givre de manière plus efficace. La solution selon l'invention porte sur l'exécution d'un traitement de réduction au moyen duquel les aires de section transversale de trous traversants 22 formés du côté au vent sont rendues plus petites que celles des trous traversants 22 formés du côté sous le vent.
PCT/JP2018/030888 2017-09-19 2018-08-22 Échangeur de chaleur Ceased WO2019058847A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017178915A JP2019052823A (ja) 2017-09-19 2017-09-19 熱交換器
JP2017-178915 2017-09-19

Publications (1)

Publication Number Publication Date
WO2019058847A1 true WO2019058847A1 (fr) 2019-03-28

Family

ID=65811084

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/030888 Ceased WO2019058847A1 (fr) 2017-09-19 2018-08-22 Échangeur de chaleur

Country Status (2)

Country Link
JP (1) JP2019052823A (fr)
WO (1) WO2019058847A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012072955A (ja) * 2010-09-29 2012-04-12 Mitsubishi Heavy Ind Ltd 熱交換器
WO2013008464A1 (fr) * 2011-07-14 2013-01-17 パナソニック株式会社 Échangeur de chaleur d'extérieur et climatiseur destiné à un véhicule

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012072955A (ja) * 2010-09-29 2012-04-12 Mitsubishi Heavy Ind Ltd 熱交換器
WO2013008464A1 (fr) * 2011-07-14 2013-01-17 パナソニック株式会社 Échangeur de chaleur d'extérieur et climatiseur destiné à un véhicule

Also Published As

Publication number Publication date
JP2019052823A (ja) 2019-04-04

Similar Documents

Publication Publication Date Title
CN112204312B (zh) 空气调节装置的室外机及空气调节装置
US9459053B2 (en) Heat exchanger and air-conditioning apparatus
JP7026830B2 (ja) アルミニウム製押出扁平多穴管及び熱交換器
JP2007232246A (ja) 熱交換器
JP6399774B2 (ja) 冷蔵庫
JP5936297B2 (ja) 熱交換器
JP3068761B2 (ja) 熱交換器
EP3608618B1 (fr) Échangeur thermique et dispositif à cycle de réfrigération
US20230101157A1 (en) Heat exchanger and air-conditioning apparatus
WO2021095567A1 (fr) Tuyau de transfert de chaleur et échangeur de chaleur
US20120198882A1 (en) Evaporator
WO2017158795A1 (fr) Échangeur de chaleur et climatiseur
CN111902683B (zh) 热交换器及制冷循环装置
WO2018040037A1 (fr) Échangeur de chaleur à micro-canal et réfrigérateur refroidi par air
WO2018040036A1 (fr) Échangeur de chaleur à micro-canal et réfrigérateur à refroidi par air
JP2005201492A (ja) 熱交換器
JP2016148480A (ja) 熱交換器
WO2019058847A1 (fr) Échangeur de chaleur
WO2019031155A1 (fr) Échangeur de chaleur
US20240200886A1 (en) Heat Exchanger
JP2002372340A (ja) 凝縮器
JP5815128B2 (ja) 熱交換器、及び空気調和機
KR20050002569A (ko) 열교환기
WO2018040034A1 (fr) Échangeur de chaleur à micro-canal et réfrigérateur refroidi par air
JP2015045471A (ja) エバポレータ

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: 18859432

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: 18859432

Country of ref document: EP

Kind code of ref document: A1