WO2005073655A1 - Echangeur thermique et systeme de conditionnement d'air - Google Patents

Echangeur thermique et systeme de conditionnement d'air Download PDF

Info

Publication number
WO2005073655A1
WO2005073655A1 PCT/JP2005/001243 JP2005001243W WO2005073655A1 WO 2005073655 A1 WO2005073655 A1 WO 2005073655A1 JP 2005001243 W JP2005001243 W JP 2005001243W WO 2005073655 A1 WO2005073655 A1 WO 2005073655A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
tubes
tube
refrigerant
heat
Prior art date
Application number
PCT/JP2005/001243
Other languages
English (en)
Japanese (ja)
Inventor
Shiro Ikuta
Syouzou Hataya
Nobuhide Kasagi
Yuji Suzuki
Naoki Shikazono
Daisuke Ookawa
Original Assignee
Calsonic Kansei Corporation
The University Of Tokyo
Iwamoto Co., Ltd.
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 Calsonic Kansei Corporation, The University Of Tokyo, Iwamoto Co., Ltd. filed Critical Calsonic Kansei Corporation
Priority to JP2005517524A priority Critical patent/JPWO2005073655A1/ja
Publication of WO2005073655A1 publication Critical patent/WO2005073655A1/fr

Links

Classifications

    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to, for example, an evaporator / condenser heat exchanger and an air conditioner including the same. More specifically, the present invention relates to a technology for further improving the heat exchange efficiency, reducing the size, and reducing the weight.
  • a heat exchanger used in a vehicle air conditioner includes a plurality of tubes for circulating a refrigerant, a tank for distributing the refrigerant to each of the tubes, and a cooling fin provided between the tubes.
  • the heat exchanger having this configuration includes cooling fins that are in contact with each tube in order to increase the area of the heat transfer surface in order to supplement the heat transfer performance on the air side with a small heat transfer coefficient.
  • the tube defines a plurality of refrigerant flow paths through which the refrigerant flows in order to improve the heat transfer performance on the refrigerant side and to have mechanical strength capable of withstanding high refrigerant pressure in the tube.
  • This tube is manufactured, for example, by extrusion or by brazing these three plates with an inner fin sandwiched between two plates.
  • this type of heat exchanger has a small heat transfer coefficient and a large thermal resistance on the air side, the fin pitch is reduced, or the cooling fins are provided with fine cut-and-raised slits. Improve thermal performance.
  • the air side heat transfer coefficient is improved, the heat transfer performance is reduced due to the heat conduction in the cooling fins, the so-called fin efficiency.
  • An object of the present invention is to provide a heat exchanger that achieves higher performance, smaller size, and lighter weight of the heat exchange efficiency of the heat exchanger, and an air conditioner including the same.
  • a feature of the invention provides the following heat exchanger.
  • the heat exchanger includes first and second tubes having a refrigerant passage through which the refrigerant flows.
  • the heat exchanger includes tanks attached to both ends of the first and second tubes, respectively, for distributing the refrigerant to the first and second tubes.
  • the first and second tubes have outer surfaces that act as heat transfer surfaces and exchange heat with the refrigerant.
  • the pitch between the first and second tubes is two to four times the thickness of each of the first and second tubes.
  • Each thickness of the first and second tubes may be 1 mm or less.
  • At least one of the first and second tubes may have an outer peripheral surface having an uneven portion.
  • the convex portion of the concave-convex portion may have a coolant channel.
  • the concave portion of the concave-convex portion may have a coolant channel.
  • the refrigerant flow path may be similar in cross section to the convex portion.
  • the pitch of the uneven portions may be three times or less the thickness of each of the first and second tubes.
  • a ratio of a length of the concave portion of the uneven portion to a length of the convex portion of the uneven portion may be W2 / W1 ⁇ 2.
  • the heat exchanger may be applied to an air conditioner.
  • the heat transfer surface that exchanges heat with the refrigerant without using the cooling fins is formed by the outer surface of the tube. This eliminates the problems of heat exchangers using cooling fins, such as fin efficiency, increased contact heat resistance, increased ventilation resistance, clogging due to dust, dew, and frost, and fin corrosion. . In addition, by optimizing the pitch between tubes, the heat transfer coefficient on the air side is further improved, and extremely high heat exchange efficiency is exhibited. Therefore, the heat exchanger of the present invention achieves higher performance, smaller size, and lighter weight because no cooling fin is used.
  • each tube Since the thickness of each tube is set to lmm or less, the thickness of the tube becomes larger than when the thickness exceeds 1mm.
  • the number of buses increases. Due to this increase, the total cross-sectional area of the refrigerant flow path formed in this tube is sufficiently ensured, and the flow path resistance of the refrigerant is greatly reduced.
  • the concave portion enlarges the flow path, reduces the wind speed, and reduces the ventilation resistance.
  • the uneven portion slightly reduces the heat transfer on the air side, the ratio of the heat transfer coefficient on the air side to the pressure coefficient is larger in a tube having unevenness than in a tube having no unevenness. This enables the heat exchanger to have higher performance, smaller size and lighter weight.
  • the heat exchanger of the invention is used as an evaporator, the condensed water is drawn into the recess and easily drained. This suppresses an increase in ventilation resistance, and does not cause a problem that water droplets scatter due to an increase in wind speed. Further, since this heat exchanger has a tube having an uneven outer surface, the mechanical strength is also greatly improved.
  • the cross section of the refrigerant flow path is made sufficiently large.
  • the total cross-sectional area of the refrigerant flow path is secured to such an extent that an increase in pressure loss in the pipe can be saved.
  • the tube has an outer peripheral surface having an uneven portion with a pitch (Wl + W2) that is three times or more the thickness (T), the flow separated from the upstream convex portion adheres to the downstream convex portion again. Weakens the effect of As a result, the rate of improvement in the heat transfer performance at the point of reattachment of the downstream convex portion where the heat transfer coefficient is improved is reduced. Pitches less than three times eliminate those problems.
  • a high-performance, small-sized and lightweight heat exchanger is used as an air conditioner for vehicles such as an evaporator, a radiator, an oil cooler, and a heater core. This will reduce the weight and energy consumption of the vehicle and increase the passenger's living space.
  • FIG. 1 is a perspective view showing a heat exchanger according to a first embodiment.
  • FIG. 2 is a sectional view taken along the line II-II in FIG. 1.
  • FIG. 3 is an enlarged sectional view of a main part of the tube shown in FIG. 2.
  • FIG. 4 shows the heat release and power (PT) obtained by dividing the tube spacing by the tube thickness (PT).
  • FIG. 4 is a characteristic diagram showing a change in the ratio with respect to (fan power).
  • FIG. 5 is a perspective view showing a heat exchanger according to a second embodiment.
  • FIG. 6 is a sectional view taken along the line VI-VI in FIG. 5.
  • FIG. 7 is an enlarged sectional view of a main part of the tube shown in FIG. 6.
  • FIG. 8 is a characteristic diagram showing a change in a ratio between a heat release amount and power (fan power) with respect to a value (PL) obtained by dividing a distance between uneven portions formed on a tube surface by a tube thickness (PL).
  • FIG. 9 is a diagram showing an example in which a heat exchanger to which the invention is applied is applied to an air conditioner.
  • FIG. 10 is a cross-sectional view of a tube showing another example of the tube of the present invention.
  • heat exchanger 1 of the embodiment includes a plurality of tubes 2 and a pair of tanks 3 and 4 for distributing a refrigerant to each tube 2.
  • the tanks 3 and 4 are arranged at predetermined intervals in parallel and facing each other. Both ends of each tube 2 are inserted, brazed, and integrally joined to the tanks 3 and 4 at a predetermined pitch interval.
  • the heat exchanger 1 has no cooling fins between the tubes 2, but has an air-side heat transfer surface that exchanges heat with the refrigerant on the outer surface of the tubes 2. That is, the heat exchanger 1 forms the air-side heat transfer surface on the outer surface of the tube 2.
  • the tube 2 functions as a long heat transfer tube having a flat cross section.
  • the tube 2 has a plurality of refrigerant flow paths 5 through which the refrigerant flows.
  • each refrigerant flow path 5 has holes penetrating at the upper and lower ends in the longitudinal direction of the tube 2.
  • the plurality of refrigerant channels 5 are positioned at predetermined pitch intervals in the lateral direction of the tube 2.
  • the tank 3 functions as a supply tank that supplies a refrigerant.
  • the tank 4 functions as a collection tank that collects the refrigerant that has passed through the tubes 2 and has undergone heat exchange.
  • the tanks 3 and 4 are closed at both ends in the longitudinal direction and formed as cylindrical bodies.
  • Tanks 3 and 4 are
  • the tube 2 has a tube insertion hole (not shown) for inserting the end of the tube 2 into the tank.
  • the tank 3 is attached to a refrigerant introduction pipe (not shown) for supplying the refrigerant into the tank 3.
  • the tank 4 is attached to a refrigerant discharge pipe (not shown) for collecting the refrigerant flowing through each tube 2.
  • the heat transfer surface that exchanges heat with the refrigerant without using cooling fins is constituted by the outer surface 2 a of the tube 2.
  • This outer surface 2a exchanges heat with the air flows Fl, F2.
  • This structure has problems with a heat exchanger using cooling fins, such as increased fin efficiency, contact heat resistance, increased ventilation resistance, clogging due to dust, dew, and frost, and fin corrosion. To eliminate.
  • a pitch interval (hereinafter simply referred to as a pitch P) for disposing each tube 2 is provided.
  • the thickness is set to 2 to 4 times the thickness T of the tube 2.
  • the pitch P at which the tubes 2 are arranged is set to be 2 to 4 times the thickness T of the tubes 2, the air-side heat transfer coefficient is further improved, and extremely high heat exchange efficiency is exhibited.
  • FIG. 4 is a characteristic showing a change in a ratio of heat release amount to power (fan power) (heat release amount / power) with respect to a value (PT) obtained by dividing a tube interval (pitch P) by a thickness T of the tube 2 (PT).
  • FIG. The vertical axis shows the ratio of heat release to power, and the larger the number, the better the heat exchange rate.
  • the horizontal axis shows PT. As can be seen from this characteristic diagram, setting PT between 2 and 4 greatly increases the heat exchange efficiency.
  • the thickness T of the tube 2 is set to lmm or less. Tubes 2 having a thickness T of 1 mm or less have more tubes 2 than those having a thickness of more than 1 mm. As a result, the total cross-sectional area of the refrigerant flow path 5 formed in the tube 2 can be sufficiently ensured, and the flow resistance of the refrigerant is greatly reduced.
  • the heat exchanger 1 of the present embodiment does not use cooling fins, so that higher performance, smaller size, and lighter weight can be realized.
  • the heat exchanger 10 of this embodiment basically has a plurality of tubes 20 and a refrigerant distributed to each tube 20, similarly to the heat exchanger 1 of the first embodiment.
  • one It consists of a pair of tanks 30, 40.
  • the air-side heat transfer surface that exchanges heat with the refrigerant is constituted by the outer surface 20a of the tube 20 (see FIG. 6).
  • the heat exchanger 10 has the same configuration as the heat exchanger 1 of the first embodiment, except for a tube 20 having a different shape, and a description of the same components will be omitted.
  • the pitch P at which the tubes are arranged is set to be two to four times the thickness of the tubes, similarly to the heat exchanger 1 of the first embodiment.
  • each tube 20 of the heat exchanger 10 has undulations 60a and 60b formed on its outer peripheral surface 20a. That is, the outer peripheral surface 20a of the tube 20 has a raised portion 60a and a recessed portion 60b formed on the front surface and the rear surface, respectively, and the concave portion 60b is formed between the adjacent refrigerant passages 50. Formed. As a result, the tube 20 becomes corrugated, and the irregular shape of the outer peripheral surface 20a matches each refrigerant flow path 50.
  • the coolant channels 50 are respectively positioned inside the convex portions 60a.
  • the coolant channel 50 is similar in cross section to the convex portion 60a.
  • the uneven portions 60a and 60b have a pitch (W1 + W2) that is three times or less the thickness T of the tube 20.
  • the thickness T of the tube 20 is defined as the maximum thickness of the tube.
  • the pitch (Wl + W2) of the uneven portions 60a and 60b, which is three times or less the thickness T of the tube 20, increases the heat exchange efficiency.
  • the pitch W of the uneven portions 60a and 60b more than three times the thickness T weakens the effect of the flow separated from the upstream convex portion to re-attach to the downstream convex portion, and improves the heat transfer coefficient. Reduce the rate of improvement in heat transfer performance at the point of side protrusion reattachment
  • FIG. 8 shows the ratio of the amount of heat radiation to the power (fan power) to the value (PL) obtained by dividing the pitch W of the uneven portions 60a and 60b formed on the surface of the tube 20 by the thickness T of the tube 20 (heat radiation).
  • FIG. 6 is a characteristic diagram showing a change in (/ power). The vertical axis is the ratio of heat release to power, the larger the number, the better the horizontal axis is PL. As can be seen from this characteristic diagram, a PL of 3 or less increases the heat exchange efficiency.
  • the concave and convex portions 60a and 60b formed on the outer peripheral surface 20a of the tube 20 expand the flow path by the concave portion 60b, reduce the wind speed, and reduce the ventilation resistance.
  • the unevenness 60a, 60b slightly reduces the heat transfer on the air side.
  • the ratio of the air-side heat transfer coefficient to the pressure coefficient is larger for a tube with irregularities than for a tube without irregularities. As a result, the performance, size, and weight of the heat exchanger 10 can be improved.
  • the heat exchanger 10 is used as an evaporator, condensed water is drawn into the recess 60b and easily drained. As a result, an increase in ventilation resistance can be suppressed, and the problem of water droplets scattering when the wind speed is increased is eliminated. Furthermore, in the heat exchanger 10, the mechanical strength of the tube 20 is greatly increased by making the outer shape of the tube 20 uneven.
  • the refrigerant flow path 50 was formed in accordance with the concave and convex portions 60a and 60b formed on the outer peripheral surface 20a of the tube 20. That is, the positions of the refrigerant passage 50 and the protrusion 60a coincide with each other, and are similar in cross section. Thereby, the cross section of the refrigerant flow path 50 can be made sufficiently large, and the total cross-sectional area of the refrigerant flow path 50 is set to such an extent that the heat exchange performance is enhanced.
  • the ratio of the length W1 of the convex portion 60a to the length W2 of the concave portion 60b is set to W2ZW1 ⁇ 2, a sufficient cross-sectional area inside the tube is ensured. In addition, the refrigerant side pressure loss is suppressed.
  • FIG. 9 shows an example in which the heat exchangers 1 and 10 to which the present invention is applied are applied to an air conditioner.
  • the heat exchangers 1 and 10 of the present embodiment were applied to the radiator 71, the evaporator 72, the heater core 73, and the like.
  • the heat exchangers 1 and 10 of the present invention may be applied to an oil cooler.
  • the heat exchanger of the present invention is not limited to a vehicle air conditioner, and may be applied to a home, business or portable air conditioner to achieve a significant compactness.
  • a high-performance, small-sized, and lightweight heat exchanger may be used as an air conditioner used for a vehicle such as an evaporator, a radiator, an oil cooler, and a heater core. This achieves weight reduction and energy saving of the vehicle and expansion of the passenger's living space.
  • the coolant channel 50 is formed in accordance with the concave and convex portions 60a and 60b formed on the outer peripheral surface 20a of the tube 20.
  • the air-side heat transfer performance is basically irrelevant to the coolant channel 50, and therefore, as shown in FIG. 10, the coolant channel 50 does not have to be formed in accordance with the uneven portions 60a and 60b. That is, the refrigerant passage 50 having a circular cross section is positioned in both the convex portion 60a and the concave portion 60b.
  • This structure is the same as the heat exchanger 10 of the second embodiment. The same effect is obtained.
  • the heat exchanger or air conditioner of the present invention is used, for example, in vehicles and homes, and is useful in achieving higher performance, smaller size, and lighter weight.

Landscapes

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

Abstract

Il est divulgué un échangeur thermique comprenant des premiers et des seconds tubes (2) ayant respectivement un canal de réfrigérant pour l'écoulement du réfrigérant. L'échangeur thermique comprend en outre des réservoirs (3, 4) fixes respectivement á chaque extrémité des premiers et des seconds tubes (2) pour distribuer le réfrigérant au premier et au second tubes (2). Le premier et le second tubes (2) présentent respectivement une surface externe qui sert de surface de transfert thermique et échange la chaleur avec le réfrigérant. Le pas (P) entre le premier tube et le second tube (2) est deux à quatre fois plus large que l'épaisseur des premiers et seconds tubes (2).
PCT/JP2005/001243 2004-01-29 2005-01-28 Echangeur thermique et systeme de conditionnement d'air WO2005073655A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2005517524A JPWO2005073655A1 (ja) 2004-01-29 2005-01-28 熱交換器及びこれを含む空調装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-021386 2004-01-29
JP2004021386 2004-01-29

Publications (1)

Publication Number Publication Date
WO2005073655A1 true WO2005073655A1 (fr) 2005-08-11

Family

ID=34823788

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2005/001243 WO2005073655A1 (fr) 2004-01-29 2005-01-28 Echangeur thermique et systeme de conditionnement d'air

Country Status (2)

Country Link
JP (1) JPWO2005073655A1 (fr)
WO (1) WO2005073655A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010008018A (ja) * 2008-06-30 2010-01-14 Showa Denko Kk インナーフィン付き熱交換管およびこれを用いた熱交換器
JP2011506903A (ja) * 2007-12-18 2011-03-03 アー − ヒート アライド ヒート イクスチェンジ テクノロジー アクチェンゲゼルシャフト 熱交換装置
JP2011508865A (ja) * 2007-12-18 2011-03-17 アー − ヒート アライド ヒート イクスチェンジ テクノロジー アクチェンゲゼルシャフト 熱交換装置
WO2015005352A1 (fr) * 2013-07-08 2015-01-15 三菱電機株式会社 Échangeur de chaleur, et dispositif de pompe à chaleur
WO2017159726A1 (fr) * 2016-03-16 2017-09-21 三菱電機株式会社 Échangeur de chaleur du type sans ailettes, unité extérieure de climatiseur d'air pourvu d'un échangeur de chaleur du type sans ailettes, et unité intérieure de climatiseur pourvu d'un échangeur de chaleur du type sans ailettes
WO2018168759A1 (fr) * 2017-03-16 2018-09-20 ダイキン工業株式会社 Échangeur de chaleur ayant une unité de tubes de transfert de chaleur
CN110392814A (zh) * 2017-03-16 2019-10-29 大金工业株式会社 具有传热管单元的热交换器
WO2022014515A1 (fr) 2020-07-17 2022-01-20 ダイキン工業株式会社 Échangeur de chaleur
WO2023105703A1 (fr) * 2021-12-09 2023-06-15 三菱電機株式会社 Dispositif de déshumidification

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
EP1248063A1 (fr) * 2001-03-28 2002-10-09 Behr GmbH & Co. Echangeur de chaleur

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
EP1248063A1 (fr) * 2001-03-28 2002-10-09 Behr GmbH & Co. Echangeur de chaleur

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011506903A (ja) * 2007-12-18 2011-03-03 アー − ヒート アライド ヒート イクスチェンジ テクノロジー アクチェンゲゼルシャフト 熱交換装置
JP2011508865A (ja) * 2007-12-18 2011-03-17 アー − ヒート アライド ヒート イクスチェンジ テクノロジー アクチェンゲゼルシャフト 熱交換装置
JP2010008018A (ja) * 2008-06-30 2010-01-14 Showa Denko Kk インナーフィン付き熱交換管およびこれを用いた熱交換器
WO2015005352A1 (fr) * 2013-07-08 2015-01-15 三菱電機株式会社 Échangeur de chaleur, et dispositif de pompe à chaleur
CN105452794A (zh) * 2013-07-08 2016-03-30 三菱电机株式会社 热交换器以及热泵装置
JPWO2015005352A1 (ja) * 2013-07-08 2017-03-02 三菱電機株式会社 ヒートポンプ装置
WO2017159726A1 (fr) * 2016-03-16 2017-09-21 三菱電機株式会社 Échangeur de chaleur du type sans ailettes, unité extérieure de climatiseur d'air pourvu d'un échangeur de chaleur du type sans ailettes, et unité intérieure de climatiseur pourvu d'un échangeur de chaleur du type sans ailettes
JPWO2017159726A1 (ja) * 2016-03-16 2018-10-04 三菱電機株式会社 フィンレス型の熱交換器、そのフィンレス型の熱交換器を備えた空気調和機の室外機、及びそのフィンレス型の熱交換器を備えた空気調和機の室内機
US10648742B2 (en) 2016-03-16 2020-05-12 Mitsubishi Electric Corporation Finless heat exchanger, outdoor unit of an air-conditioning apparatus including the finless heat exchanger, and indoor unit of an air-conditioning apparatus including the finless heat exchanger
WO2018168759A1 (fr) * 2017-03-16 2018-09-20 ダイキン工業株式会社 Échangeur de chaleur ayant une unité de tubes de transfert de chaleur
CN110392814A (zh) * 2017-03-16 2019-10-29 大金工业株式会社 具有传热管单元的热交换器
WO2022014515A1 (fr) 2020-07-17 2022-01-20 ダイキン工業株式会社 Échangeur de chaleur
EP4184105A4 (fr) * 2020-07-17 2023-12-06 Daikin Industries, Ltd. Échangeur de chaleur
US11913729B2 (en) 2020-07-17 2024-02-27 Daikin Industries, Ltd. Heat exchanger
WO2023105703A1 (fr) * 2021-12-09 2023-06-15 三菱電機株式会社 Dispositif de déshumidification

Also Published As

Publication number Publication date
JPWO2005073655A1 (ja) 2007-09-13

Similar Documents

Publication Publication Date Title
WO2005073655A1 (fr) Echangeur thermique et systeme de conditionnement d'air
JP4122578B2 (ja) 熱交換器
US7635019B2 (en) Heat exchanger
US7882708B2 (en) Flat pipe-shaped heat exchanger
KR100486923B1 (ko) 열교환기
EP2236972B1 (fr) Ailette pour échangeur thermique et échangeur thermique utilisant l'ailette
US7992401B2 (en) Evaporator
JP4946348B2 (ja) 空気熱交換器
JP2006322698A (ja) 熱交換器
JP2000179988A (ja) 冷媒蒸発器
JPH05196383A (ja) コルゲートフィン型熱交換器
JP4930413B2 (ja) 熱交換器
JP3855346B2 (ja) 熱交換器
JP2007093023A (ja) 熱交換器
JP2005106328A (ja) 熱交換装置
JP4122670B2 (ja) 熱交換器
JPH0829016A (ja) ヒートポンプ用室外熱交換器
JP2003185374A (ja) 最適化されたプレートを備える熱交換器のチューブ
US20060266503A1 (en) Heat transfer fin, heat exchanger, evaporator and condenser for use in car air-conditioner
AU2004239162A1 (en) Heat exchanger fin, heat exchanger, condensers, and evaporators
JP3674120B2 (ja) 熱交換器
JP2002048491A (ja) 冷却用熱交換器
JP2624336B2 (ja) フィン付熱交換器
EP2224198A1 (fr) Échangeur de chaleur du type à ailettes et tubes
JPH0410530Y2 (fr)

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2005517524

Country of ref document: JP

NENP Non-entry into the national phase

Ref country code: DE

WWW Wipo information: withdrawn in national office

Country of ref document: DE

122 Ep: pct application non-entry in european phase