WO2001067010A1 - Echangeur de chaleur de refroidissement - Google Patents

Echangeur de chaleur de refroidissement Download PDF

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Publication number
WO2001067010A1
WO2001067010A1 PCT/JP2000/008617 JP0008617W WO0167010A1 WO 2001067010 A1 WO2001067010 A1 WO 2001067010A1 JP 0008617 W JP0008617 W JP 0008617W WO 0167010 A1 WO0167010 A1 WO 0167010A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
tubes
tank
heat exchanger
heat exchange
Prior art date
Application number
PCT/JP2000/008617
Other languages
English (en)
Japanese (ja)
Inventor
Souichi Kato
Mutsumi Fukushima
Muneo Sakurada
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
Publication of WO2001067010A1 publication Critical patent/WO2001067010A1/fr

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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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0391—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 plate-like or laminated conduits a single plate being bent to form one or more conduits
    • 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
    • F25B39/02—Evaporators
    • 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
    • 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
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays

Definitions

  • the present invention relates to a heat exchanger for cooling an evaporator used for an air conditioner for a vehicle, for example.
  • a cooling heat exchanger constituting a refrigeration cycle of a vehicle air conditioner As shown in Japanese Patent Application Laid-Open No. H11-21838, a plurality of refrigerant passages formed by joining molding plates face-to-face are disclosed. It generally has a tube provided, a tank communicating with the refrigerant passage of the tube, and corrugated fins alternately stacked with the tank.
  • the refrigerant flowing through the tubes evaporates, thereby cooling the tubes, cooling the air passing between the tubes through the tubes and the fins, while condensing moisture in the air.
  • Condensed water is generated on the tube and fin surfaces. This condensed water flies out of the cooling heat exchanger due to the wind from the blower on the upstream side in the ventilation direction, causing problems such as the condensed water reaching the vehicle interior.
  • the refrigerant evaporator according to the above-mentioned patent application publication also has grooves extending along the longitudinal direction of the tube at the downstream end in the ventilation direction and the upstream end in the ventilation direction, and at a substantially central portion in the ventilation direction. Also, by forming a concave portion between the refrigerant passages of the tube in a concave shape, a drain groove extending along the longitudinal direction of the tube is provided, and condensed water does not move downstream in the ventilation direction along the tube surface. It has become.
  • the applicant of the present invention has adopted a method in which one brazing sheet is formed by roll homing, pressing, etc., instead of a tube formed by joining two molded plates face to face.
  • the formed tubes are exclusively used.
  • those having only one heat exchange medium passage are provided with a plurality of heat exchangers arranged side by side in the ventilation direction and alternately stacked in multiple stages with fins.
  • Heat exchangers using tubes formed by such roll homing and press working have also been required to be smaller and lighter due to space savings in vehicles in recent years.
  • an object of the present invention is to provide a cooling heat exchanger that can efficiently drain condensed water generated on the surfaces of tubes and fins downward. Disclosure of the invention
  • a cooling heat exchanger includes a tube having a heat exchange medium passage therein and a plurality of tubes arranged in the ventilation direction, and fins alternately stacked with the tubes. And at least one tank disposed at one end of the tube. The drainage channel is provided by leaving a gap between the drain and the pit.
  • the condensed water generated in the fins and tubes moves to the leeward side on the tube surface due to the wind pressure, but the condensed water is moved to the leeward side of the cooling heat exchanger by the drainage channel formed between the tubes. Is prevented from moving down to the bottom of the drainage channel and drained, so the amount of condensate collected on the downstream side of the cooling heat exchanger is reduced, and there is a risk of clogging and flying. I am reducing it.
  • the cooling heat exchanger includes a tube having an interior partitioned into a plurality of heat exchange medium passages by a partition portion, fins alternately stacked with the tube, and one end of the tube. And a drain that penetrates the tube in the stacking direction of the tubes is provided at a partition that divides the heat exchange medium passage from the heat exchange medium passage.
  • the condensed water generated in the fins and tubes moves to the leeward side on the tube surface due to the wind pressure, but the condensed water flows to the leeward side of the cooling heat exchanger by the drainage channel formed in the tube. And the water drops down at the end of the drainage channel and is drained, reducing the amount of condensed water that collects on the downstream side of the cooling heat exchanger, and may cause clogging and water splashing. Is reduced.
  • the cooling heat exchanger includes one or more tubes having a heat exchange medium passage therein, fins alternately stacked with the tubes, and a tank disposed at one end of the tubes. At least, a drainage channel is provided between the tubes or tubes and opened in the stacking direction of the tubes. A louver is formed in the fin, and the center of the fin in the ventilation direction is a portion where the louver is not formed. One bar is not formed The width of the portion in the ventilation direction is smaller than the width of the drainage channel of the tube in the ventilation direction.
  • louver located between the drainage channels serves as a guide and moves to the drainage channel side and can be drained downward from the drainage channel, the drainage of the cooling heat exchanger can be improved. —Can be layered.
  • the cooling heat exchanger is formed by processing a single brazing sheet to form a tube.
  • the tube has a winding structure on the side along the short direction, They are arranged so that the fastening structure is on the upstream side in the ventilation direction.
  • the wind-up side of the tube becomes thicker due to the winding structure, so that the corrosion resistance against corrosion caused by the attachment of dust and the like flying from the windward side should be improved. It is possible to extend the life of the tube.
  • the tank has an inlet side and an outlet side of the heat exchange medium arranged in parallel in the ventilation direction, and the inlet side and the outlet side are communicated via a heat exchange medium passage of the tube.
  • the tank has a connecting portion that connects the inlet side portion and the outlet side portion while arranging the inlet side portion and the outlet side portion at an interval, and connecting the inlet side portion and the outlet side portion.
  • the portion may be provided with a drainage channel penetrating in the longitudinal direction of the tube.
  • the cooling heat exchanger may be a one-tank type having only the tank, but the cooling heat exchanger may be provided on a side opposite to a side where the tank is disposed, through a heat exchange medium passage communicating with an inlet side of the tank. It may be a double tank type having a tank that allows the heat exchange medium to be turned back to the heat exchange medium passage communicating with the outlet side of the tank. In one or both of the single tank type and the double tank type, the tank may be integrally formed by extrusion molding.
  • the heat exchange medium does not directly bypass the inlet side and the outlet side in the entrance / exit tank, and a deep-drawing tank section having a substantially U-shaped cross section is opened on one side.
  • a tank is formed by joining the end plate and the end plate that closes the opening, it is possible to avoid the problem that the heat exchange medium leaks to the outside from the gap due to poor joining.
  • problems such as freezing destruction caused by infiltration of condensed water into a poor brazing portion such as a pinhole generated at a joint portion.
  • FIG. 1 is a perspective view showing a configuration of a cooling heat exchanger according to the present invention.
  • FIG. 2 is a partial cross-sectional view showing the configuration of the above tank.
  • FIG. 3 is an explanatory diagram showing a state in which a cross section of the tank shown in FIG. 2 is viewed from the front.
  • FIG. 4 is an explanatory view showing an arrangement of two tubes and fins arranged in parallel in the ventilation direction and a configuration of a drainage channel.
  • FIG. 5 is an explanatory diagram showing a positional relationship between a drainage channel between tubes and a louver of a fin.
  • FIG. 6 is an explanatory diagram showing a state in which the condensed water reaches the tube located on the downstream side by the configuration of the drainage channel shown in FIG.
  • FIG. 7 is an explanatory diagram showing an arrangement of tubes and fins having two heat exchangers and a configuration of a drainage channel.
  • FIG. 8 FIG. 4 is an explanatory diagram showing a state in which condensed water reaches the side surface of a heat exchange medium passage located downstream and falls down at the end of the drainage channel by adopting the configuration of the drainage channel shown.
  • the cooling heat exchanger 1 shown in FIGS. 1 to 5 is, for example, a two-tank type laminated evaporator used in a vehicle, and has a tank 2 provided at one end in the longitudinal direction, and a tank 2 provided at one end in the longitudinal direction.
  • a tank 3 provided at one end opposite to the above, tubes 14 and 15 connected to the tank 2 and the tank 3 to communicate the tank 2 and the tank 3, and tubes 14 and 15
  • It is a two-pass type that is composed of corrugated fins 16 alternately stacked in multiple stages and end plates 17 and 17 arranged on both sides in the stacking direction.
  • the tank 2 and the tank 3 are, as shown in FIG. 1, a cylindrical body 5 made of an aluminum alloy and having a tube connection hole 4 for connecting to the tubes 14 and 15 described below.
  • the tubular member 5 is formed integrally with the closing member 6 by extrusion molding.
  • a poor connection between the deep drawing tank member and the closing member such as a conventional tank including a substantially bowl-shaped deep drawing tank member having one opening and a closing member closing the opening. Therefore, the heat exchange medium does not leak from the gap at the side of the tank. In addition, it is possible to avoid problems such as freeze destruction caused by infiltration of condensed water into a poorly brazed portion such as a pinhole generated at a joint portion.
  • the opening on both sides of the tank 2 is closed by one closing plate 6.
  • the turn-back tank is capable of turning back the closed heat exchange medium, as shown in FIGS. 2 and 3
  • the center of the inside of the tubular body 5 is a tube 14, as shown in FIGS. 15
  • Two partitions 7, 7 extending along the stacking direction are completely separated into an inlet side 8 and an outlet side 9 by two partition walls 7, 7, and a connecting part is provided between the inlet side 8 and the outlet side 9.
  • the partition walls 7, 7 of the tank 3 are formed integrally with the cylindrical body 5 by extrusion molding. With this, the partition wall is formed as a separate member, so that the joint between the tank 3 and the inner peripheral surface of the tank 5 is formed through the gap. The performance of the heat exchanger is not deteriorated by bypassing the heat exchange medium directly between the side and the outlet side.
  • An inlet pipe 12 is connected to an end of the inlet 8, and an outlet pipe 13 is connected to an end of the outlet 9.
  • zinc (Zn) is sprayed on the surface of the tanks 2 and 3 later by a method of spraying or extruding by two layers.
  • a sacrificial layer is formed by a method of forming a layer containing zinc on the surface by means of, for example, to improve corrosion resistance.
  • tubes 14 and 15 are obtained by bending a single brazing sheet in multiple stages by roll homing or pressing, and follow the ventilation direction.
  • a heat exchange medium passage 20 at least surrounded by a pair of flat surfaces 18 and 18 and a flat surface 19 located on the leeward side and extending in the stacking direction.
  • the windward side of the tubes 14 and 15 is formed at one end with a winding portion 21 formed by winding the vicinity of the end portion, and at the other end with the base end side of the winding portion 21.
  • the contact portion 22 to be contacted and the heat exchange medium By forming a closing part 23 that closes the downstream opening of the body passage 20, a winding-up structure is obtained.
  • the tubes 14 and 15 are arranged side by side. Since the windward side of 15 is thicker, it is possible to improve the corrosion resistance against the corrosion caused by the attachment of dust etc. blown from the windward side, and to prolong the life of the tubes 14 and 15 This is possible.
  • the inner fins 24 may be accommodated in each heat exchange medium passage 20 as shown in FIGS. 4 and 5.
  • a plurality of beads may be formed inside a surface perpendicular to the ventilation direction.
  • the tubes 14 and 15 may be formed by extrusion molding or by joining two molding plates face-to-face. In the case of extrusion molding, the tubes have a plurality of heat exchange medium passages. It is good.
  • the drainage channel 25 is provided by leaving an interval between the tubes 14 and 15 with appropriate dimensions so that the condensed water that has come down can fall before reaching the tubes 15.
  • the fin 16 is formed with a louver 26 in which a part thereof is cut and raised in the tube stacking direction in order to improve the heat exchange capacity. ing.
  • the width (LW) of the part where the louver 26 in the ventilation direction center of the fin 16 is not formed is, as shown in FIG. 5, the width of the drainage channel 25 between the tubes 14 and 15. The dimension is smaller than the width (SW) in the ventilation direction.
  • the connecting portion 10 connecting the inlet side portion 8 and the outlet side portion 9 of the tank 3 has a longitudinal direction corresponding to the tubes 14 and 15. A drain hole 27 penetrating through the connecting portion 10 is formed.
  • the condensed water flowing on the surface of the tube 14 due to the wind pressure, as shown by the imaginary line, is a tube 15 on the further downstream side.
  • water does not flow downstream of the cooling heat exchanger 1 in the ventilation direction, and as shown by the solid line, the tube 14 ends at the downstream end in the ventilation direction, that is, at the end of the drainage channel 25. Fall down.
  • the louver 26 located in the drainage channel 25 serves as a guide and serves as a drainage channel. 2 Move to the 5th end and drain down from the drainage channel.
  • the condensed water that has fallen downward is discharged from the cooling heat exchanger 1 through a drain hole 27 formed in a connecting portion 10 connecting the inlet side portion 8 and the outlet side portion 9 of the tank 3.
  • the condensed water of the cooling heat exchanger 1 can be drained more easily.
  • the configuration of the tube and the configuration of the drainage channel of the cooling heat exchanger 1 are not limited to those described above.
  • the cooling heat exchanger 1 using a tube having a different configuration will be described with reference to FIGS.
  • the same components as those in the previous embodiment are denoted by the same reference numerals, and description thereof is omitted.
  • the tube 28 shown in FIG. 7 has a flat surface 19 which is formed by bending a single brazing sheet in multiple stages by roll homing or pressing, and is located on the leeward side and extends along the laminating direction.
  • the above-mentioned winding structure is provided on the upstream side in the ventilation direction, and it is joined at the center in the ventilation direction.
  • the partition 29 has a drainage channel 30 penetrating the partition 29 in the direction in which the tubes 28 are stacked.
  • the water moves further on the side of the heat exchange medium passage 20 on the leeward side as shown by the imaginary line, and thus is shown by the solid line without flowing to the downstream side of the cooling heat exchanger 1 in the ventilation direction.
  • the width (LW) of the fin 16 at the center where the louver 26 is not formed is as shown in FIG.
  • the dimension may be smaller than the width (SW) in the ventilation direction of the drainage channel 30 between the drainage channels, thereby further improving the drainage of condensed water.
  • a drainage channel 25 is provided between the tubes 14 and 15, and a drainage channel is formed in the partition portion 29 of the heat exchange medium passages 20 and 20 of the tube 28.
  • the drainage channels 25 and 30 can be condensed water. It can perform the drainage function below.
  • a drain channel penetrating the end plate 17 in the laminating direction is provided on the end plate 17 at a position corresponding to the position of the drain channel 25, 30. It is desirable to provide.
  • the condensed water generated in the fins and the tubes moves to the leeward side on the tube surface due to the wind pressure, but forms in the drainage channel or the tube formed between the tubes.
  • the condensed water is prevented from moving to the lowermost end of the cooling heat exchanger by the drainage channel, and falls down at the end of the drainage channel to be drained.
  • the amount of condensed water that collects on the stream side is reduced, reducing the risk of clogging and flying.
  • a louver is formed on the fin, and the center of the fin in the ventilation direction is a portion where no louver is formed.
  • the width of the portion where the louver is not formed is the width of the drainage channel of the tube in the ventilation direction.
  • the size of the louver is smaller than that of the fin, so that one end of the louver faces between the drainage channels due to the arrangement of the fin bar and the drainage channel. Even if it moves upward on the leeward side due to wind pressure, the louver located between the water passages serves as a guide and moves to the drainage channel side, and it is possible to drain the water downward from the drainage channel.
  • the drainage of the vessel can be further improved.
  • condensed water hardly stays on the fin surface, clogging due to condensed water is suppressed even if the fin pitch is reduced to ensure its performance while miniaturizing the cooling heat exchanger. You can also.
  • the wrapping portion of the tube is arranged so as to be on the upstream side in the ventilation direction, so that the wrapping portion forms an upstream portion of the tube. Because the side is thicker, it is resistant to corrosion caused by the attachment of dust etc. Corrosion resistance to the tube can be improved, and the life of the tube can be extended.
  • the inlet side and the outlet side are arranged at an interval, and a connection connecting the inlet side and the outlet side is provided.
  • the inlet / outlet tank is integrally formed by extrusion molding, the heat exchange medium does not directly bypass between the inlet side and the outlet side of the inlet / outlet tank, and one side is opened.
  • a tank is formed by joining a deep drawing tank portion having a substantially U-shaped cross section and an end plate that closes this opening, it is possible to avoid a problem that the heat exchange medium leaks from the gap to the outside due to poor joining.
  • problems such as freezing destruction caused by infiltration of condensed water into a poorly brazed portion such as a pinhole generated at a joint.

Abstract

La présente invention concerne un échangeur de chaleur (1) de refroidissement, comportant une pluralité de tubes (14, 15) parallèles dans le sens de la ventilation et pourvus d'un trajet (20) de milieu d'échange de chaleur, des réservoirs (2, 3) disposés au moins d'un côté des tubes (14, 15), un espace étant formé entre le tube (14) et le tube (15) pour fournir un trajet de décharge (25) à travers lequel l'eau de condensation produite aux surfaces des tubes et des ailettes est efficacement déchargée du trajet de décharge vers le bas, de manière à empêcher l'eau de condensation d'atteindre le coté abrité de l'échangeur de chaleur de refroidissement, d'éclabousser le coté abrité de l'échangeur thermique de refroidissement, ou d'augmenter la résistance à la ventilation due à l'encrassement.
PCT/JP2000/008617 2000-03-10 2000-12-06 Echangeur de chaleur de refroidissement WO2001067010A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000066776A JP3700144B2 (ja) 2000-03-10 2000-03-10 冷却用熱交換器
JP2000-66776 2000-03-10

Publications (1)

Publication Number Publication Date
WO2001067010A1 true WO2001067010A1 (fr) 2001-09-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2000/008617 WO2001067010A1 (fr) 2000-03-10 2000-12-06 Echangeur de chaleur de refroidissement

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JP (1) JP3700144B2 (fr)
WO (1) WO2001067010A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014168760A1 (fr) * 2013-04-10 2014-10-16 Carrier Corporation Unité d'échange thermique à banc multiple à tube plié
US20190120521A1 (en) * 2017-10-20 2019-04-25 Mahle International Gmbh Collecting tank of a heat exchanger
CN110345799A (zh) * 2018-04-08 2019-10-18 浙江盾安热工科技有限公司 扁管组件及包含该扁管组件的换热器

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4547205B2 (ja) * 2004-07-30 2010-09-22 カルソニックカンセイ株式会社 蒸発器
WO2006064823A1 (fr) * 2004-12-16 2006-06-22 Showa Denko K.K. Evaporateur
JP2006194576A (ja) * 2004-12-16 2006-07-27 Showa Denko Kk エバポレータ
US7726389B2 (en) 2004-12-28 2010-06-01 Showa Denko K.K. Evaporator
US8371366B2 (en) * 2006-10-03 2013-02-12 Showa Denko K.K. Heat exchanger
KR100901629B1 (ko) 2008-02-27 2009-06-08 주식회사 두원공조 증발기
CN205747595U (zh) * 2015-01-09 2016-11-30 特灵国际有限公司 热交换器以及制冷系统
CN105066518B (zh) * 2015-08-04 2018-01-05 广东美的制冷设备有限公司 一种双排平行流蒸发器及其具有该蒸发器的空调装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5820863Y2 (ja) * 1978-08-09 1983-05-02 昭和アルミニウム株式会社 蒸発器
JPS58214783A (ja) * 1982-06-09 1983-12-14 Mitsubishi Electric Corp 熱交換器
JPH0410530Y2 (fr) * 1984-09-04 1992-03-16

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5820863Y2 (ja) * 1978-08-09 1983-05-02 昭和アルミニウム株式会社 蒸発器
JPS58214783A (ja) * 1982-06-09 1983-12-14 Mitsubishi Electric Corp 熱交換器
JPH0410530Y2 (fr) * 1984-09-04 1992-03-16

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014168760A1 (fr) * 2013-04-10 2014-10-16 Carrier Corporation Unité d'échange thermique à banc multiple à tube plié
CN105121988A (zh) * 2013-04-10 2015-12-02 开利公司 折叠管多组热交换单元
US20190120521A1 (en) * 2017-10-20 2019-04-25 Mahle International Gmbh Collecting tank of a heat exchanger
CN110345799A (zh) * 2018-04-08 2019-10-18 浙江盾安热工科技有限公司 扁管组件及包含该扁管组件的换热器

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Publication number Publication date
JP2001255039A (ja) 2001-09-21
JP3700144B2 (ja) 2005-09-28

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