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WO2001006193A1 - Echangeur de chaleur du type serpentin - Google Patents

Echangeur de chaleur du type serpentin Download PDF

Info

Publication number
WO2001006193A1
WO2001006193A1 PCT/JP2000/002262 JP0002262W WO0106193A1 WO 2001006193 A1 WO2001006193 A1 WO 2001006193A1 JP 0002262 W JP0002262 W JP 0002262W WO 0106193 A1 WO0106193 A1 WO 0106193A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
serpentine
tube
header pipe
approximately
Prior art date
Application number
PCT/JP2000/002262
Other languages
English (en)
Japanese (ja)
Inventor
Kunihiko Nishishita
Original Assignee
Zexel Valeo Climate Control Corporation
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 Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Priority to EP00915405A priority Critical patent/EP1195569A4/fr
Publication of WO2001006193A1 publication Critical patent/WO2001006193A1/fr

Links

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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • F28F1/128—Fins with openings, e.g. louvered fins

Definitions

  • the present invention is used for an evaporator used in a refrigeration cycle using carbon dioxide as a refrigerant, a heat pump type refrigeration cycle, used as an evaporator condenser depending on the direction of the refrigerant flow, and is required to withstand pressure. More particularly, the present invention relates to a serpentine heat exchanger. Background art
  • Japanese Utility Model Laid-Open Publication No. 57-40983 discloses that a tube meandering continuously is gathered at one end, and both ends of the tube are formed in a single collecting member.
  • the connection pipe is connected to the hole and the exit hole, and the connection pipe is connected to the entry hole and the exit hole of the assembly member.
  • Japanese Utility Model Application Laid-Open No. 57-82690 discloses a heat exchanger in which flat tubes are bent at appropriate intervals at multiple stages and fins are interposed therebetween.
  • a connector having a flat portion in which the flat surface of the flat tube is horizontal is provided in the flat tube at the upper and lower ends at the time of manufacture of the heat exchanger, and a connector is provided in each of the horizontal portions of the flat tube. It has a connection device.
  • Japanese Utility Model Laid-Open No. 57-1798993 discloses a two-way symmetric refrigerant passage by joining both ends of a left tube and a right tube to an entrance block located in the center. And a connection plate is provided near the tip of the inlet pipe and the outlet pipe. Disclosed is an automotive capacitor bonded to a vehicle.
  • an object of the present invention is to provide a serpentine heat exchanger having the most efficient dimensions. Disclosure of the invention
  • the present invention provides an inlet header pipe through which a refrigerant flows, an outlet header pipe through which a refrigerant flows out, and a plurality of steps folded at a predetermined interval to form a space between the inlet side header pipe and the outlet side header pipe.
  • a serpentine heat exchanger comprising at least one communicating serpentine tube and corrugated fins disposed between a plurality of folded refrigerant passages formed by the satentine tube;
  • the width of the heat exchanger in the ventilation direction of the air flowing through the tofin is formed within a range of approximately 35 mm or more and 65 mm or less, and the fin height of the corrugated fin is approximately 5 mm or more and 13 mm or less.
  • the distance between the folded refrigerant passages of the first pentane tube is formed in accordance with the fin height. This makes it possible to reduce the dimension of the serpentine tube in the stacking direction of the folded refrigerant passages and the fins and the width of the heat exchanger in the ventilation direction while maintaining the heat exchanger capacity at or above a predetermined level.
  • the theme can be achieved.
  • the present invention provides, in each of the corrugated fins, one of the corrugated fins. It is desirable that the fin pitch between the bent portion abutting on the tube element and the next bent portion abutting on one of the tube elements is approximately 2.8 mm or more and 5.0 mm or less. It is desirable that the thickness of the corrugated fin be approximately 0.06 mm or more and 0.15 mm or less. As a result, an optimal corrugated fin can be set in the serpentine heat exchanger having the dimensions described above.
  • the corrugated fin includes a bent portion that contacts the tube element, a vent portion that contacts one tube element, and a flat portion located between the vent portion that contacts the other tube element.
  • a plurality of chambers extending in a direction perpendicular to the ventilation direction are formed sequentially in the ventilation direction, and the inclination angle of the louvers with respect to the ventilation direction is approximately 24 °. It is desirable that the angle be at least 40 ° or less. As a result, a corrugated fin having an optimum louver can be obtained.
  • the distance between the end of the louver and the tube element is desirably within a range of approximately 0.2 mm or more and 1.5 mm or less. It is desirable that the thickness be approximately 1.6 mm or more and 3.9 mm or less. As a result, the drainage of the corrugated fin can be improved.
  • the serpentine heat exchanger is disposed substantially at the center in the laminating direction, and has one inlet pipe communicating with a refrigerant inlet portion extending downstream in the ventilation direction, and is disposed at both ends in the laminating direction.
  • a pair of outlet-side header pipes communicating with the refrigerant outlet portion extending upstream in the direction, wherein the service tine tube communicates with the inlet-side header pipe and one of the outlet-side header pipes.
  • FIG. 1 is a front view showing a configuration of a serpentine heat exchanger according to a first embodiment of the present invention
  • FIG. 2 is a circuit diagram shown in FIG. Fig. 3 is a side view of the heat exchanger
  • Fig. 3 is a characteristic diagram showing the relationship between the width Cw of the heat exchanger in the ventilation direction and the capacity Fa of the heat exchanger.
  • a) is a side view showing the configuration of the corrugated fin
  • FIG. 4 (b) is a cross-sectional view thereof
  • FIG. 5 is a partially enlarged cross-sectional view of the corrugated fin
  • FIG. 7 is an explanatory view showing a mounting state and a side view of the goat fin
  • FIG. 7 is a characteristic diagram showing a relationship between a fin height F h of the corrugated fin and a heat exchanger capacity Fa.
  • Fig. 8 is a characteristic diagram showing the relationship between the fin pitch Fp of the corrugated fin and the heat exchanger capacity Fa, and
  • Fig. 9 shows the corrugated fin angle Ra and the heat exchange capacity Fa.
  • FIG. 10 is a characteristic diagram showing a relationship with the exchange capacity F a, and FIG. 10 shows a Suntine type according to a second embodiment of the present invention.
  • FIG. 11 is a front view showing the heat exchanger
  • FIG. 11 is a bottom view of the serpentine heat exchanger according to the second embodiment
  • FIG. 12 is a serpentine heat exchanger according to the second embodiment.
  • FIG. 2 is a side view of the heat exchanger.
  • the serpentine heat exchanger 1 shown in FIGS. 1 and 2 is provided on one side and has a refrigerant inflow pipe extending downstream in the ventilation direction (shown in FIG. 2).
  • An inlet header pipe 2 that communicates with the pump 3
  • an outlet header pipe 4 that is arranged on the other side and communicates with a refrigerant outlet pipe 5 that extends upstream in the ventilation direction, While communicating between the side header pipes 4, the plurality of folded portions 6A located on one side and the other side, and between the folded portion 6A on one side and the folded portion 6A on the other side are connected.
  • at least a corrugated fin 7 disposed between each of the folded refrigerant passages 6 B adjacent to the serpentine tube 6. .
  • a pair of end plates 8 and 9 are provided at both ends of the folded refrigerant passage 6B and the Korgut fin 7 in the stacking direction, and the folded refrigerant passage 6B and each of the end plates 8 and 9 are provided.
  • a korgut fin 7 is also arranged between the front end plates 8 and 9.
  • the serpentine tube 6 is desirably formed of a Zn sprayed tube or a Zn sprayed tube + a highly corrosion resistant tube.
  • a width C wm 50 mm in the ventilation direction is obtained as a point having the maximum heat exchanger capacity, and when the maximum heat exchanger capacity is 100%, the heat exchanger is 80% or more.
  • the width in the wind direction of F a C w was obtained in the range of approximately 35 mm or more and 65 mm or less.
  • the corrugated fin 7 is abutted and joined to one of the folded refrigerant passages 6B adjacent to the surface tubing 6.
  • Vent section 11b which is in contact with the vent section 11a and the other folded refrigerant passage 6B, and a flat section connecting the vent section 11a and the other vent section 11b. 1 and a predetermined fin height Fh corresponding to the distance between the adjacent folded refrigerant passages 6B, and the apex of the vent portion 11a to be abutted and joined to the one folded refrigerant passage 6B.
  • Fp fine pitch
  • the fin height Fh corresponds to the width between the adjacent folded refrigerant passages 6B of the serpentine tube 6, and is used to reduce the dimension of the folded refrigerant passage 6B and the corrugated fin 7 in the stacking direction. It is desirable to reduce the fin height F h, but there is a problem that decreasing the fin height F h increases ventilation resistance. For this reason, the relationship between the fin height Fh and the heat exchanger capacity Fa is experimentally determined, and when the optimal fin height is determined, the characteristic diagram shown in FIG. 7 is obtained. A fin height Fhm of 9 mm was obtained.
  • the appropriate range F hs of the fin height F h is approximately 5.0 mm or more and 13 mm or less.
  • the vent portions 6A and 6B are bent so as to have this width. .
  • the tube height Th is desirably in a range of approximately 1.6 mm or more and 3.9 mm or less.
  • the fine pitch Fp and the heat exchanger capacity Fa Fig. 8 is a characteristic diagram obtained by experiments, and it can be seen that the maximum capacity is obtained when the fine pitch Fp is 3.9 mm.
  • the range in which the heat exchanger capacity Fa is 80% or more of the maximum at the maximum is the appropriate range Fps of the fine pitch Fp, as in the case described above, the appropriate range Fps is as shown in FIG. According to the characteristic diagram shown by, it is approximately 2.8 mm or more and 5.0 mm or less.
  • the corrugated fin 7 has a louver 10 that extends perpendicularly to the ventilation direction and is formed by cutting and raising a plurality of pieces sequentially in the ventilation direction.
  • the air passing along the corrugated fins 7 can pass along the louvers 10 so as to cross the Korgut fins 7, thereby improving the heat exchange efficiency in the Korgut fins 7.
  • increasing the inclination angle (louver angle) Ra of the louver with respect to the flat portion 12 of the corrugated fin 7 can increase the heat exchange capacity, while increasing the louver angle Ra.
  • the optimum louver angle Ra exists.
  • an appropriate louver angle range Ras that can obtain 80% or more capacity is approximately 24 ° or more.
  • the thickness of the fin plate Ft is preferably as thin as possible in terms of cost. However, in order to increase the fin strength, a thickness greater than a predetermined value is required. Is set within the range of approximately 0.06 mm or more and 0.15 mm or less. It is desirable to specify. Further, the distance D r between the end of the lun 10 formed in the corrugated fin 7 and the top of the fin vent 11 a, lib is approximately 0.2 mm or more and 1.5 mm or less. It is desirable that By setting the distance Dr within this range, the drainage of the fins can be improved, and the fin strength when the fins are formed in a corrugated shape can be maintained. In addition, it is possible to improve the bonding property between the corrugated fin 7 and the solder tube 6 by brazing.
  • a serpentine heat exchanger 20 shown in FIGS. 10 to 12 has a corrugated fin 7 having a plurality of louver groups 1 OA each including a plurality of louvers, and a schematic drawing of the corrugated fin 7 in the stacking direction.
  • One inflow header pipe 21 disposed at one end in the center, a pair of outflow header pipes 22 and 23 disposed at the other end of both ends in the laminating direction, and the inflow header pipe
  • a first sagittal pentine tube 25 that communicates 21 with one of the outflow header pipes 22 and folds a plurality of stages between the one end and the other end, and the other end of the inflow header pipe 21
  • a second serpentine tube 26 that is connected to the outflow side header pipe 23 and that is folded back in a plurality of stages between the one end and the other end.
  • first serpentine tube 25 is constituted by a folded portion 25A and a folded refrigerant passage 25B extending between the folded portions 25A.
  • second serpentine tube 2 6 also includes a folded portion 26A and a folded refrigerant passage 26B extending between the folded portions 26A.
  • the inlet-side header pipe 21 extends through the extension pipe 27 that extends downstream in the ventilation direction of the heat sink type heat exchanger 20 and is bent. 8 and connected to a pipe (not shown) extending from an expansion valve or the like located upstream of the refrigeration cycle, for example.
  • outlet side header pipes 22 and 23 are formed of a pair of It communicates with the refrigerant outlet 31 via the extension pipes 29 and 30 and is connected to an accumulator or an internal heat exchanger located on the downstream side of the refrigeration cycle via a pipe (not shown). .
  • the first and second serpentine tubes 25 and 26 constitute two refrigerant flow paths flowing in parallel from the inlet header pipe 21 to the outlet pipes 22 and 23 to the outlet side. Since the flow path resistance of the refrigerant can be reduced, the width of the serpentine tubes 25 and 26 can be reduced, so that the width of the serpentine heat exchanger in the stacking direction can be further reduced. It can be formed. Therefore, in this embodiment, two parallel refrigerant flow paths are formed, but a plurality of refrigerant flow paths may be formed as necessary. The dimensions of each element described above are also effective in the serpentine heat exchanger according to this embodiment. Industrial applicability
  • the heat exchange capacity and the ventilation resistance of the heat exchanger are obtained by experiments, and the heat exchanger capacity (heat exchange capacity / ventilation resistance) is obtained from these results.
  • the dimensions of each element of the serpentine heat exchanger are set within a range where this value is equal to or greater than a predetermined value, so that the heat exchanger can be downsized while maintaining the performance of the heat exchanger. Therefore, downsizing of the air conditioner for a vehicle on which the heat exchanger is mounted is achieved, and furthermore, downsizing of the vehicle, securing of the interior space of the vehicle, and the like are achieved.

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

Abstract

L'invention concerne un échangeur de chaleur du type serpentin, comprenant au moins un tuyau collecteur côté entrée, un tuyau collecteur côté sortie, au moins un serpentin qui s'étend depuis le tuyau collecteur côté entrée, replié en étages multiples à intervalles déterminés, jusqu'au tuyau collecteur côté sortie, et des ailettes ondulées placées entre les passages de réfrigérant repliés en étages multiples, formés par les serpentins. La largeur de l'échangeur de chaleur dans le sens d'écoulement de l'air dans les ailettes ondulées est d'environ au moins 35 mm à au plus 65 mm, la hauteur des ailettes ondulées étant d'environ au moins 5 mm à au plus 13 mm, l'intervalle entre les passages de réfrigérant repliés des serpentins correspondant à la hauteur des ailettes.
PCT/JP2000/002262 1999-07-15 2000-04-07 Echangeur de chaleur du type serpentin WO2001006193A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00915405A EP1195569A4 (fr) 1999-07-15 2000-04-07 Echangeur de chaleur du type serpentin

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11201579A JP2001027484A (ja) 1999-07-15 1999-07-15 サーペンタイン型熱交換器
JP11/201579 1999-07-15

Publications (1)

Publication Number Publication Date
WO2001006193A1 true WO2001006193A1 (fr) 2001-01-25

Family

ID=16443405

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2000/002262 WO2001006193A1 (fr) 1999-07-15 2000-04-07 Echangeur de chaleur du type serpentin

Country Status (3)

Country Link
EP (1) EP1195569A4 (fr)
JP (1) JP2001027484A (fr)
WO (1) WO2001006193A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7650935B2 (en) 2001-12-21 2010-01-26 Behr Gmbh & Co. Kg Heat exchanger, particularly for a motor vehicle
WO2024125064A1 (fr) * 2022-12-12 2024-06-20 湖北亿纬动力有限公司 Module de batterie à refroidissement double face

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6439300B1 (en) * 1999-12-21 2002-08-27 Delphi Technologies, Inc. Evaporator with enhanced condensate drainage
JP3775302B2 (ja) * 2002-01-23 2006-05-17 株式会社デンソー 熱交換器
US7281387B2 (en) * 2004-04-29 2007-10-16 Carrier Commercial Refrigeration Inc. Foul-resistant condenser using microchannel tubing
DE112005003260T5 (de) * 2004-12-24 2008-01-03 Showa Denko K.K. Wärmetauscher
KR100886379B1 (ko) 2006-04-05 2009-03-02 한양대학교 산학협력단 다패스 열교환기용 최적의 패스 수를 선정하기 위한 방법
JP5663413B2 (ja) 2011-06-17 2015-02-04 カルソニックカンセイ株式会社 サーペンタイン型熱交換器
JP5780205B2 (ja) * 2012-05-10 2015-09-16 株式会社デンソー 燃料気化器
KR101509937B1 (ko) * 2013-10-11 2015-04-07 현대자동차주식회사 열전소자가 구비된 열교환기 및 그 제조방법
DE202017102436U1 (de) * 2016-08-08 2017-11-24 Bundy Refrigeration International Holding B.V. Wärmetauscher mit Mikrokanal-Struktur oder Flügelrohr-Struktur
JP7164291B2 (ja) * 2017-10-06 2022-11-01 東芝ライフスタイル株式会社 冷蔵庫

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JPS59170783U (ja) * 1983-04-25 1984-11-15 松下冷機株式会社 熱交換器
JPS63134267U (fr) * 1987-02-26 1988-09-02
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JPH02109178U (fr) * 1989-01-31 1990-08-30
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器

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JPS62134493A (ja) * 1985-12-05 1987-06-17 Showa Alum Corp 熱交換器
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JPH02287094A (ja) * 1989-04-26 1990-11-27 Zexel Corp 熱交換器
JP3459271B2 (ja) * 1992-01-17 2003-10-20 株式会社デンソー 自動車用空調装置のヒータコア
JPH0674669A (ja) * 1992-08-25 1994-03-18 Showa Alum Corp 熱交換器
JP3044440B2 (ja) * 1993-10-22 2000-05-22 株式会社ゼクセル 積層型エバポレータ
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JPS59170783U (ja) * 1983-04-25 1984-11-15 松下冷機株式会社 熱交換器
JPS63134267U (fr) * 1987-02-26 1988-09-02
JPS6419290A (en) * 1987-07-10 1989-01-23 Hitachi Ltd Heat exchanger
JPH02109178U (fr) * 1989-01-31 1990-08-30
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7650935B2 (en) 2001-12-21 2010-01-26 Behr Gmbh & Co. Kg Heat exchanger, particularly for a motor vehicle
WO2024125064A1 (fr) * 2022-12-12 2024-06-20 湖北亿纬动力有限公司 Module de batterie à refroidissement double face

Also Published As

Publication number Publication date
EP1195569A1 (fr) 2002-04-10
JP2001027484A (ja) 2001-01-30
EP1195569A4 (fr) 2005-06-08

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