EP1195569A1 - Schlangenförmiger wärmetauscher - Google Patents

Schlangenförmiger wärmetauscher Download PDF

Info

Publication number
EP1195569A1
EP1195569A1 EP00915405A EP00915405A EP1195569A1 EP 1195569 A1 EP1195569 A1 EP 1195569A1 EP 00915405 A EP00915405 A EP 00915405A EP 00915405 A EP00915405 A EP 00915405A EP 1195569 A1 EP1195569 A1 EP 1195569A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
serpentine
tube
side header
header pipe
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.)
Withdrawn
Application number
EP00915405A
Other languages
English (en)
French (fr)
Other versions
EP1195569A4 (de
Inventor
Kunihiko 39 Aza Higashihara NISHISHITA
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.)
Valeo Thermal Systems Japan Corp
Original Assignee
Zexel Valeo Climate Control 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 Zexel Valeo Climate Control Corp filed Critical Zexel Valeo Climate Control Corp
Publication of EP1195569A1 publication Critical patent/EP1195569A1/de
Publication of EP1195569A4 publication Critical patent/EP1195569A4/de
Withdrawn legal-status Critical Current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
    • F28D1/047—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 relates to a heat exchanger and, more specifically, a serpentine type heat exchanger that is required to have good pressure withstanding performance, which may be utilized as an evaporator in a refrigerating cycle in which carbon dioxide is used as a refrigerant, or as an evaporator or a condenser depending upon the direction of the refrigerant flow in a refrigerating cycle adopting a heat pump system.
  • Japanese Unexamined Utility Model Publication No. S 57-40893 discloses a heat exchanger achieved by setting the two ends of a tube formed in a continuous serpentine shape at a single position, connecting the two ends of the tube to an intake port and an output port formed at a single assembly member and connecting a connecting pipe to the intake port and the output port at the assembly member.
  • Japanese Unexamined Utility Model Publication No. S 57-82690 discloses a heat exchanger achieved by providing fins between a flat tube folded back over a plurality of stages with an appropriate distance set between the individual stages.
  • This heat exchanger includes a horizontal portion at which the flat surface of the flat tube positioned at the upper and lower ends during the hate exchanger production is allowed to extend horizontally and a connector linking device having a connector which is provided at each of the horizontal portions of the flat tube.
  • Japanese Unexamined Utility Model Publication No. S 57-178993 discloses a condenser for automobiles, having two refrigerant passage systems on the left side and the right side achieving symmetry that are formed by bonding both ends of a left tube and a right tube to an intake/outlet block provided at the center and a connecting plate provided near the front ends of an intake pipe and an outlet pipe with the intake pipe and the outlet pipe bonded to the intake/outlet block by securing the connecting plate to the intake/outlet block.
  • an object of the present invention is to provide a serpentine type heat exchanger having dimensions that achieve maximum efficiency.
  • the serpentine type heat exchanger comprising at least an inflow-side header pipe through which a refrigerant flows in, an outlet-side header pipe through which the refrigerant flows out, at least one serpentine tube that is folded back over a plurality of stages by maintaining a specific distance between the individual folded portions of the serpentine tube and communicates between the inflow-side header pipe and the outlet-side header pipe and corrugated fins provided between multiple-stage folded-back refrigerant passages formed by the serpentine tube, the width of the heat exchanger along the direction in which air flows through the corrugated fins is set within an approximate range of 35mm ⁇ 65mm, the fin height of the corrugated fins is set within an approximate range of 5mm ⁇ 13mm and the distance between the individual folded-back refrigerant passages formed by the serpentine tube is set in correspondence to the fin height.
  • the fin pitch representing the distance between a bent portion of each corrugated fin coming in contact with the tube element on one side and the next bent portion coming in contact with the same side of the tube element within an approximate range of 2.8mm ⁇ 5.0mm and to set the plate thickness of the corrugated fins within an approximate range of 0.06mm ⁇ 0.15mm.
  • the corrugated fins should each include bent portions coming in contact with the tube element and flat portions formed between the bent portions that are in contact with one tube element an the bent portions that are in contact with the tube element on the other side. It is desirable to provide a plurality of louvers at each flat portion. They should be formed sequentially along the direction of the airflow to extend outward along the direction perpendicular to the direction of the airflow with the angle at which the louvers incline relative to the direction of the airflow set within an approximate range of 24° ⁇ 40°, in order to obtain corrugated fins having ideal louvers.
  • the serpentine type heat exchanger may include one inflow-side header pipe provided at an approximate center along the laminating direction which communicates with a refrigerant inlet portion extending out toward the downstream side along the direction of the airflow and a pair of outlet-side header pipes provided at the two ends along the laminating direction and communicating with a refrigerant output portion extending out toward the upstream side along the direction of the airflow.
  • the serpentine tube may be constituted of a first serpentine tube that communicates between the inflow-side header pipe and one of the outlet-side header pipes and a second serpentine tube that communicates between the inflow-side header pipe and the other outlet-side header pipe. Since this structure reduces the passage resistance at the serpentine tube and improves the distribution of the refrigerant, an improvement is achieved in the heat exchanger performance.
  • a serpentine type heat exchanger 1 shown in FIGS. 1 and 2 comprises at least an inflow-side header pipe 2 that communicates with a refrigerant inflow pipe 3 provided on one side and extends out toward the downstream side along the direction of the airflow (see FIG.
  • a serpentine tube 6 that communicates between the inflow-side header pipe 2 and the outflow-side header pipe 4 and is constituted of a plurality of folded back portions 6A formed on the one side and also on the other side and a plurality of folded-back refrigerant passages 6B communicating between the folded back portions 6A on the one side and the folded back portions 6A on the other side and corrugated fins 7 provided between adjacent folded-back refrigerant passages 6B constituted of the serpentine tube 6.
  • a pair of end plates 8 and 9 are provided at the two ends along the direction in which the folded-back refrigerant passages 6B and the corrugated fins 7 are laminated, with corrugated fins 7 also provided between the outermost folded-back refrigerant passages 6B and the end plates 8 and 9. It is desirable to form the serpentine tube 6 by using a Zn spray-coated tube material or a material constituted of a Zn spray-coated tube material and a highly corrosion-resistant tube material.
  • the "refrigerating capability / airflow resistance" representing the factor Fa that indicates the heat exchanging capability achieves the characteristics presented in the characteristics diagram in FIG. 3.
  • This diagram indicates the maximum heat exchanging capability is achieved that a point at which the width Cwm along the airflow direction is 50mm and a heat exchanging capability of 80% or higher is achieved relative to the maximum heat exchanging capability set at 100% over an approximate range of the width Cw along the airflow direction between 35mm ⁇ 65mm.
  • the corrugated fins 7 are each constituted of bent portions 11a that are bonded in contact with one of adjacent folded-back refrigerant passages 6B of the serpentine tube 6, bent portions 11b bonded in contact with the other folded-back refrigerant passage 6B and flat portions 12 linking the bent portions 11a on the one side and the bent portions 11b on the other side, achieving a specific fin height Fh equivalent to the distance between the adjacent folded-back refrigerant passages 6B and a fin pitch Fp representing the distance between the apexes of the bent portions 11a bonded in contact to the folded-back refrigerant passage 6B on the one side.
  • the ideal range Fhs for the fin height Fh over which the heat exchanging capability Fa is at least 80 % of the maximum heat exchanging capability was approximately 5.0mm ⁇ 13mm. Accordingly, the distance between the adjacent folded-back refrigerant passages 6B must be set in conformance to the fin height Fh within this range and the bent portions 6A and 6B must be bent to achieve the distance.
  • the relationship between the fin pitch Fp and the heat exchanging capability Fa achieved in the serpentine type heat exchanger 1 having the width Cw along the airflow direction set to 50mm was ascertained through testing, and the resulting characteristics diagram presented in FIG. 8 indicates that the maximum capability is achieved when the fin pitch Fp is at 3.9mm.
  • the characteristics diagram in FIG. 8 also indicates that the ideal range Fps for the fin pitch Fp over which the heat exchanging capability Fa is at least 80 % of the maximum heat exchanging capability as described earlier is approximately 2.8mm ⁇ 5.0mm.
  • the corrugated fins 7 each include a plurality of louvers 10 projecting out perpendicularly to the airflow direction and sequentially raised along the airflow direction. Since the presence of the louvers 10 allows the air passing along the corrugated fins 7 to travel by intersecting the corrugated fins 7 along the louvers 10, an improvement is achieved in the heat exchanging efficiency at the corrugated fins 7. However, while a higher heat exchanging capability can be achieved by increasing the angle Ra of inclination of the louvers (louver angle) relative to the flat portion 12 of the corrugated fin 7, a larger louver angle Ra increases the airflow resistance, resulting in a lowered heat exchanging capability. Thus, an optimal louver angle Ra must be ascertained.
  • the serpentine type heat exchanging capability Fa was ascertained through testing conducted by varying the louver angle Ra in the heat exchanger 1 structured as described above and the relationship between the louver angle Ra and the heat exchanging capability Fa as indicated in the characteristics diagram presented in FIG. 9 was determined.
  • the louver angle Ram at which the maximum capability is achieved was determined to be 32°, and an ideal louver angle range Ras over which a heat exchanging capability of at least 80% relative to the maximum capability set at 100% was achieved was determined to be approximately 24° ⁇ 40°.
  • the fins need to have a specific minimum thickness in order to achieve sufficient fin strength, and accordingly, it is desirable to set the thin plate thickness Ft within an approximate range of 0.06mm ⁇ 0.15mm.
  • the distance Dr between the ends of the louvers 10 formed at the corrugated fins 7 and the apexes of the bent portions 11a and 11b of the fins should be set within an approximate range of 0.2mm ⁇ 1.5mm.
  • a serpentine type heat exchanger 20 shown in FIGS. 10 through 12 comprises at least corrugated fins 7 each having a plurality of louver groups 10A each constituted of a plurality of louvers, and a single inflow-side header pipe 21 provided at one side of the heat exchanger at an approximate center along the direction in which the corrugated fins 7 are laminated, a pair of outflow-side header pipes 22 and 23 provided at the other end of the heat exchanger at the two sides along the laminating direction, a first serpentine tube 25 that communicates between the inflow-side header pipe 21 and one of the outflows side header pipes, i.e., the outflow-side header pipe 22 and is folded back over a plurality of stages between the one side and the other side of the heat exchanger and a second serpentine tube 26 that communicates between the inflow-side header pipe 21 and the other outflow-side header pipe 23 and is it folded back over a plurality of stages between the one side and the other side of the heat exchanger.
  • the first serpentine tube 25 is constituted of folded back portions 25A and folded-back refrigerant passages 25B extending between the folded back portions 25A, and likewise, the second serpentine tube 26, too, is constituted of folded back portions 26A and folded-back refrigerant passages 26B extending between the folded back portions 26B.
  • the inflow-side header pipe 21 communicates with a refrigerant inlet portion 28 via an extension pipe 27 which distends out and bends toward the downstream side along the direction in which the air flows in the serpentine type heat exchanger 20 and is connected with a pipe (not shown) extending from, for instance, an expansion valve provided on the upstream side of the refrigerating cycle.
  • outlet-side header pipes 22 and 23 communicating with a refrigerant output portion 31 via a pair of extension pipes 29 and 30 which extend out and bend toward the upstream side along the airflow direction are connected to an accumulator, an internal heat exchanger or the like provided on the downstream side of the refrigerating cycle via pipes (not shown).
  • the refrigerant flow passage resistance can be reduced, which, in turn, allows a reduction in the width of the serpentine tubes 25 and 26, thereby achieving a further reduction in the width of the serpentine type heat exchanger along the laminating direction. While two parallel refrigerant flow paths are formed in the embodiment, more than two refrigerant flow paths may be formed as necessary. It is to be noted that the desirable dimensions of the individual elements explained earlier are also valid in the serpentine type heat exchanger in this embodiment.
  • the heat exchanging capability and the airflow resistance in the heat exchanger were ascertained through testing conducted on the serpentine type heat exchanger, the heat exchanging capability (heat exchanging capability/airflow resistance) was determined based upon these factors to set the dimension of the individual elements of the serpentine type heat exchanger within ranges over which the heat exchanging capability achieves a minimum specific value.
  • the heat exchanging capability heat exchanging capability/airflow resistance

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)
EP00915405A 1999-07-15 2000-04-07 Schlangenförmiger wärmetauscher Withdrawn EP1195569A4 (de)

Applications Claiming Priority (3)

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
JP20157999 1999-07-15
PCT/JP2000/002262 WO2001006193A1 (fr) 1999-07-15 2000-04-07 Echangeur de chaleur du type serpentin

Publications (2)

Publication Number Publication Date
EP1195569A1 true EP1195569A1 (de) 2002-04-10
EP1195569A4 EP1195569A4 (de) 2005-06-08

Family

ID=16443405

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00915405A Withdrawn EP1195569A4 (de) 1999-07-15 2000-04-07 Schlangenförmiger wärmetauscher

Country Status (3)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1111318B1 (de) * 1999-12-21 2005-07-27 Delphi Technologies, Inc. Verdampfer mit verbessertem Kondensatablauf
EP1945066A2 (de) * 2005-10-21 2008-07-23 Carrier Commercial Refrigeration, Inc. Verschmutzungsbeständiger kondensator mit mikrokanalrohren
US7650935B2 (en) 2001-12-21 2010-01-26 Behr Gmbh & Co. Kg Heat exchanger, particularly for a motor vehicle
DE202017102436U1 (de) * 2016-08-08 2017-11-24 Bundy Refrigeration International Holding B.V. Wärmetauscher mit Mikrokanal-Struktur oder Flügelrohr-Struktur

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3775302B2 (ja) * 2002-01-23 2006-05-17 株式会社デンソー 熱交換器
WO2006068262A1 (en) * 2004-12-24 2006-06-29 Showa Denko K.K. Heat exchanger
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
JP7164291B2 (ja) * 2017-10-06 2022-11-01 東芝ライフスタイル株式会社 冷蔵庫
WO2024125064A1 (zh) * 2022-12-12 2024-06-20 湖北亿纬动力有限公司 双面冷却电池模块

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1316119A (en) * 1969-10-10 1973-05-09 Associated Neg Ltd Heat exchangers
GB1497935A (en) * 1974-04-25 1978-01-12 Chausson Usines Sa Heat-exchangers cores each with a single row of tubes
DE3139154A1 (de) * 1980-10-01 1982-04-29 Furukawa Aluminium Co., Ltd., Tokyo Waermeaustauscher aus aluminiumlegierungen und rohrwerkstoff fuer den waermeaustauscher
JPS59107190A (ja) * 1982-12-10 1984-06-21 Nippon Radiator Co Ltd 熱交換器
US4570700A (en) * 1983-01-10 1986-02-18 Nippondenso Co., Ltd. Flat, multi-luminal tube for cross-flow-type indirect heat exchanger, having greater outer wall thickness towards side externally subject to corrosive inlet gas such as wet, salty air
JPS62134493A (ja) * 1985-12-05 1987-06-17 Showa Alum Corp 熱交換器
EP0374895A2 (de) * 1988-12-22 1990-06-27 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Verflüssiger für ein Kältemittel einer Fahrzeugklimaanlage
US4982579A (en) * 1989-03-31 1991-01-08 Showa Aluminum Corporation Evaporator
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器
US5076354A (en) * 1989-04-26 1991-12-31 Diesel Kiki Co., Ltd. Multiflow type condenser for car air conditioner
JPH0674669A (ja) * 1992-08-25 1994-03-18 Showa Alum Corp 熱交換器
US5311935A (en) * 1992-01-17 1994-05-17 Nippondenso Co., Ltd. Corrugated fin type heat exchanger
US5372188A (en) * 1985-10-02 1994-12-13 Modine Manufacturing Co. Heat exchanger for a refrigerant system
EP0650023A1 (de) * 1993-10-22 1995-04-26 Zexel Corporation Wärmetauscher mit mehreren Rohren
DE19729497A1 (de) * 1997-07-10 1999-01-14 Behr Gmbh & Co Flachrohr-Wärmeübertrager

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59170783U (ja) * 1983-04-25 1984-11-15 松下冷機株式会社 熱交換器
JPS63134267U (de) * 1987-02-26 1988-09-02
JPH0743236B2 (ja) * 1987-07-10 1995-05-15 株式会社日立製作所 熱交換器
JPH02109178U (de) * 1989-01-31 1990-08-30

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1316119A (en) * 1969-10-10 1973-05-09 Associated Neg Ltd Heat exchangers
GB1497935A (en) * 1974-04-25 1978-01-12 Chausson Usines Sa Heat-exchangers cores each with a single row of tubes
DE3139154A1 (de) * 1980-10-01 1982-04-29 Furukawa Aluminium Co., Ltd., Tokyo Waermeaustauscher aus aluminiumlegierungen und rohrwerkstoff fuer den waermeaustauscher
JPS59107190A (ja) * 1982-12-10 1984-06-21 Nippon Radiator Co Ltd 熱交換器
US4570700A (en) * 1983-01-10 1986-02-18 Nippondenso Co., Ltd. Flat, multi-luminal tube for cross-flow-type indirect heat exchanger, having greater outer wall thickness towards side externally subject to corrosive inlet gas such as wet, salty air
US5372188A (en) * 1985-10-02 1994-12-13 Modine Manufacturing Co. Heat exchanger for a refrigerant system
JPS62134493A (ja) * 1985-12-05 1987-06-17 Showa Alum Corp 熱交換器
EP0374895A2 (de) * 1988-12-22 1990-06-27 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Verflüssiger für ein Kältemittel einer Fahrzeugklimaanlage
US4982579A (en) * 1989-03-31 1991-01-08 Showa Aluminum Corporation Evaporator
US5076354A (en) * 1989-04-26 1991-12-31 Diesel Kiki Co., Ltd. Multiflow type condenser for car air conditioner
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器
US5311935A (en) * 1992-01-17 1994-05-17 Nippondenso Co., Ltd. Corrugated fin type heat exchanger
JPH0674669A (ja) * 1992-08-25 1994-03-18 Showa Alum Corp 熱交換器
EP0650023A1 (de) * 1993-10-22 1995-04-26 Zexel Corporation Wärmetauscher mit mehreren Rohren
DE19729497A1 (de) * 1997-07-10 1999-01-14 Behr Gmbh & Co Flachrohr-Wärmeübertrager

Non-Patent Citations (5)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 008, no. 224 (M-331), 13 October 1984 (1984-10-13) -& JP 59 107190 A (NIPPON RADIATOR KK), 21 June 1984 (1984-06-21) *
PATENT ABSTRACTS OF JAPAN vol. 011, no. 356 (M-644), 20 November 1987 (1987-11-20) -& JP 62 134493 A (SHOWA ALUM CORP), 17 June 1987 (1987-06-17) *
PATENT ABSTRACTS OF JAPAN vol. 015, no. 286 (M-1138), 19 July 1991 (1991-07-19) -& JP 03 102193 A (SHOWA ALUM CORP), 26 April 1991 (1991-04-26) *
PATENT ABSTRACTS OF JAPAN vol. 018, no. 331 (M-1626), 23 June 1994 (1994-06-23) -& JP 06 074669 A (SHOWA ALUM CORP), 18 March 1994 (1994-03-18) *
See also references of WO0106193A1 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1111318B1 (de) * 1999-12-21 2005-07-27 Delphi Technologies, Inc. Verdampfer mit verbessertem Kondensatablauf
US7650935B2 (en) 2001-12-21 2010-01-26 Behr Gmbh & Co. Kg Heat exchanger, particularly for a motor vehicle
EP1945066A2 (de) * 2005-10-21 2008-07-23 Carrier Commercial Refrigeration, Inc. Verschmutzungsbeständiger kondensator mit mikrokanalrohren
EP1945066A4 (de) * 2005-10-21 2012-07-04 Carrier Comm Refrigeration Inc Verschmutzungsbeständiger kondensator mit mikrokanalrohren
DE202017102436U1 (de) * 2016-08-08 2017-11-24 Bundy Refrigeration International Holding B.V. Wärmetauscher mit Mikrokanal-Struktur oder Flügelrohr-Struktur

Also Published As

Publication number Publication date
JP2001027484A (ja) 2001-01-30
WO2001006193A1 (fr) 2001-01-25
EP1195569A4 (de) 2005-06-08

Similar Documents

Publication Publication Date Title
US6273184B1 (en) Parallel-disposed integral heat exchanger
US7303003B2 (en) Heat exchanger
JP4122578B2 (ja) 熱交換器
US7726387B2 (en) Heat exchangers
CN101266092B (zh) 热交换器
US7992401B2 (en) Evaporator
US7635019B2 (en) Heat exchanger
JP4734021B2 (ja) 熱交換器
EP1195569A1 (de) Schlangenförmiger wärmetauscher
JP2006132920A (ja) 熱交換器
EP1239252B1 (de) Mehrstromwärmetauscher in Stapelbauweise
US9121629B2 (en) Condenser
JP4786234B2 (ja) 熱交換器
CN101349488A (zh) 蒸发器
CN101115963A (zh) 蒸发器
CN101270944B (zh) 热交换器
JP4774295B2 (ja) エバポレータ
US6786276B2 (en) Heat exchanger tube with optimized plates
US7174953B2 (en) Stacking-type, multi-flow, heat exchanger
CN100567876C (zh) 热交换器
CN112567192A (zh) 热交换器、热交换器单元及制冷循环装置
JP3674120B2 (ja) 熱交換器
JP2001324290A (ja) 冷媒蒸発器
JP2952593B1 (ja) 積層型熱交換器
JP2001012883A (ja) 熱交換器

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20020110

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB

A4 Supplementary search report drawn up and despatched

Effective date: 20050427

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20050713