US20020007646A1 - Condenser - Google Patents

Condenser Download PDF

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Publication number
US20020007646A1
US20020007646A1 US09/884,802 US88480201A US2002007646A1 US 20020007646 A1 US20020007646 A1 US 20020007646A1 US 88480201 A US88480201 A US 88480201A US 2002007646 A1 US2002007646 A1 US 2002007646A1
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United States
Prior art keywords
path
paths
cross
sectional area
condenser
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Abandoned
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US09/884,802
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English (en)
Inventor
Hideaki Manaka
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.)
Resonac Holdings Corp
Original Assignee
Showa Denko KK
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
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Assigned to SHOWA DENKO K.K. reassignment SHOWA DENKO K.K. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MANAKA, HIDEAKI
Publication of US20020007646A1 publication Critical patent/US20020007646A1/en
Abandoned legal-status Critical Current

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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • 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
    • F25B39/04—Condensers
    • 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
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

Definitions

  • the present invention relates to a condenser suitably used for, for example, a refrigeration system for car air-conditioners.
  • a conventional multi-flow type condenser for use in car air-conditioners includes a pair of vertical headers 1 and 1 disposed apart from each other and a plurality of horizontal flat tubes 2 as heat exchanging tubes disposed between the headers at certain intervals in the direction of up-and-down with their opposite ends connected with the headers.
  • One of the headers 1 is provided with a refrigerant inlet 1 a at the upper end portion thereof, and the other header 1 is provided with a refrigerant outlet 1 b at the lower portion thereof.
  • the headers 1 are provided with partitions 5 each disposed at a predetermined portion for dividing the inside of the header to thereby group the aforementioned plurality of flat tubes 2 into a plurality of paths P 1 to P 3 .
  • the refrigerant introduced from the refrigerant inlet 1 a passes downwardly through each path P 1 to P 3 in sequence in a meandering manner, and then flows out of the refrigerant outlet 1 b .
  • the refrigerant exchanges heat with the ambient air to be condensed into a liquefied refrigerant.
  • the inventors of the present application analyzed the stagnation of the liquefied refrigerant in the aforementioned condenser by using a thermography. According to the results of the analysis, as shown in FIGS. 9 and 10, the liquefied refrigerant RL tends to stagnate at the downstream lower portion in each path P 1 -P 3 .
  • the liquefied refrigerant RL stays at the bottom of the header portion connecting the first and second paths P 1 and P 2 , which may cause the so-called liquid stagnation.
  • the liquefied refrigerant RL impedes the refrigerant circulation, resulting in an increased refrigerant flow resistance.
  • a condenser includes a pair of right and left headers, a plurality of heat exchanging tubes disposed between the headers with opposite ends thereof connected with the headers, at least one partition provided in one of the headers to group the plurality of heat exchanging tubes into a plurality of paths, a refrigerant inlet provided at a lower portion of one of the headers and a refrigerant outlet provided at an upper portion of one of the headers.
  • a refrigerant introduced from the refrigerant inlet passes upwardly through the plurality of paths in sequence in a meandering manner, and flows out of the refrigerant outlet.
  • a cross-sectional area of each of the paths decreases stepwise towards a downstream side of the paths for each path, and that a reduction rate of a cross-sectional area of a downstream side path of adjacent two paths to a cross-sectional area of an upstream side path thereof is 20% or more.
  • the plurality of paths is comprised of three or more paths including a first path, a second path and a third path through which the refrigerant introduced from the refrigerant inlet passes in sequence, a reduction rate of a cross-sectional area of the second path to a cross-sectional area of the first path is 50% or more, and a reduction rate of a cross-sectional area of the third path to a cross-sectional area of the second path is 40% or more.
  • the aforementioned refrigerant blow-up effect by the refrigerant turning portion connecting the adjacent paths can fully be obtained, which can assuredly prevent the stagnation of the liquefied refrigerant in the refrigerant turning portion.
  • a condenser includes a plurality of paths arranged one on the other, each of the paths including a plurality of heat exchanging tubes, a header portion connected to corresponding ends of adjacent upper and lower paths, a refrigerant inlet provided at a lowermost path; and a refrigerant outlet provided at an uppermost path.
  • a refrigerant introduced from the refrigerant inlet goes upwardly from the lowermost path towards the uppermost path while making a U-turn in the header portion, and flows out of the refrigerant outlet.
  • a reduction rate of a cross-sectional area of a downstream side path of adjacent two paths to a cross-sectional area of an upstream side path thereof is 20% or more.
  • the liquefied refrigerant is pushed up by the blow-up effect of the rising refrigerant, and flows into the heat exchanging tubes constituting the downstream side path (upper side path) smoothly. This prevents a stagnation of the liquefied refrigerant, which keeps a large effective heat transferring area of the heat exchanging portion and enables an equally distributed smooth refrigerant flow in each path.
  • a condenser includes a first header portion with a refrigerant inlet, a lowermost first path including a plurality of heat exchanging tubes whose one end being connected with the first header portion, a final header portion with a refrigerant outlet, an uppermost final path including a plurality of heat exchanging tubes whose one end being connected with the final header portion, one or a plurality of middle paths each including a plurality of heat exchanging tubes, and a plurality of middle header portions each connecting corresponding one ends of adjacent paths.
  • a refrigerant introduced from the refrigerant inlet flows upwardly through the plurality of paths in sequence in a meandering manner via each of the header portions, and flows out of the refrigerant. Furthermore, a reduction rate of a cross-sectional area of a downstream side path of adjacent two paths to a cross-sectional area of an upstream side path thereof is 20% or more.
  • FIG. 1 is a front view showing a condenser for use in car air-conditioners according to an embodiment of the present invention
  • FIG. 2 is a schematic front view showing a refrigerant circuit arrangement of the condenser according to the embodiment
  • FIG. 3 is an enlarged cross-sectional view showing a first refrigerant turning portion and therearound of the condenser according to the embodiment
  • FIG. 4 is a schematic cross-sectional view showing a refrigerant circuit arrangement of a condenser for use in car air-conditioners according to a second embodiment of the present invention
  • FIG. 5 is a schematic cross-sectional view showing a refrigerant circuit arrangement of a condenser for use in car air-conditioners according to a third embodiment of the present invention
  • FIG. 6 is a schematic cross-sectional view showing a refrigerant circuit arrangement of a condenser for use in car air-conditioners according to a comparative example
  • FIG. 7 is a graph showing a relationship between a refrigerant flow resistance and a refrigerant circulation amount of the inventive and comparative condensers
  • FIG. 8 is a partially omitted front view showing a conventional condenser for use in car air-conditioners
  • FIG. 9 is a schematic front view showing a refrigerant circuit arrangement of the conventional condenser.
  • FIG. 10 is a schematic cross-sectional view showing a first refrigerant turning portion and therearound of the conventional condenser.
  • FIGS. 1 and 2 show a multi-flow type condenser for use in car air-conditioners according to an embodiment of the present invention.
  • this condenser has a pair of right and left headers 11 and 11 disposed at a certain distance. Between these headers 11 and 11 , a plurality of flat tubes 12 as heat exchanging tubes are horizontally disposed at certain intervals in the vertical direction with their opposites ends connected to the headers 11 and 11 . Furthermore, corrugate fins 13 are arranged between adjacent flat tubes 12 and disposed on the outermost flat tubes 12 . Furthermore, on the outside of each outermost corrugate fin 13 , a belt-shaped side plate 14 is disposed for protecting the outermost corrugated fin 13 .
  • a refrigerant inlet 11 a is provided at the lower side of one of headers 11 (right header).
  • a refrigerant outlet 11 b is provided at the upper side of the other header 11 (left header).
  • a partition 16 which divides the interior of the header 11 in the longitudinal direction thereof is provided, to thereby group the aforementioned plurality of flat tubes 12 into three paths, the first path P 1 (lowermost path), the second path P 2 (middle path) and the third path P 3 (uppermost path).
  • the header portion of the left header 11 which connects the first path P 1 with the second paths P 1 and P 2 constitutes a first refrigerant turning portion T 1
  • the header portion of the right header 11 which connects the second P 2 with the third paths P 3 constitutes a second refrigerant turning portion T 2 .
  • each header portion constituting the turning portion T 1 and T 2 may be formed by a separate individual header pipe.
  • each path P 1 -P 3 is decreased in cross-sectional area stepwise towards the downstream side path (upper side path) for each path.
  • the reduction rate of the cross-sectional area of the downstream side path (upper side path) of the two adjacent paths to the upstream side path (lower side path) thereof should be set to 20% or more, and it is preferable that the reduction rate is set to 30% or more.
  • the aforementioned reduction rate (%) can be obtained by the following formula: (1 ⁇ PL/PU) ⁇ 100(%), where “PU” is a cross-sectional area of the upstream side path and “PL” is that of the downstream side path.
  • the aforementioned reduction rate is set to 25% or more in any two adjacent paths. It is more preferable that the reduction rate of the cross-sectional area of the second path to the cross-sectional area of the first path is 50% or more and that the reduction rate of the cross-sectional area of the third path to the cross-sectional area of the second path is 40% or more.
  • the condenser of this embodiment all of the flat tubes 12 have the same structure, and therefore the cross-sectional area of each path P 1 -P 3 is in proportion to the number of tubes of each path P 1 -P 3 . Therefore, the reduction rate of the cross-sectional area between adjacent paths corresponds to the reduction rate of the number of tubes between the adjacent paths.
  • the first path P 1 includes 22 flat tubes
  • the second path P 2 includes 9 flat tubes
  • the third path P 3 includes 5 flat tubes. Accordingly, the reduction rate of the cross-sectional areas between the first and second paths P 1 and P 2 is 59.1%, and that between the second and third paths P 2 and P 3 is 44.4%.
  • the reduction rate of the cross-sectional areas between adjacent paths may be set such that each path is constituted by the same number of tubes having different cross-sectional area.
  • the total number of the paths is not especially limited, it is preferable that the total number is set to 2 to 5, more preferably 3 or 4. The most suitable total number is 3. If the total number of paths is set too much, the reduction rate of the cross-sectional areas between adjacent paths, i.e., the reduction rate of the tube number between the adjacent paths in the aforementioned embodiment, becomes too small, which causes a trouble in securing the aforementioned reduction rate. Thus, an effective refrigerant blow-up effect may not be obtained.
  • the cross-sectional area of each path is decreased stepwise for every path towards the downstream side (upper side).
  • the heat exchange core may include adjacent paths each having the same cross-sectional area. Therefore, it should be understood that the present invention covers such a condenser including adjacent paths each having the same cross-sectional area, unless otherwise clearly defined.
  • the refrigerant introduced from the refrigerant inlet 11 a passes upwardly through the first to third paths P 1 -P 3 in sequence in a meandering manner, and flows out of the refrigerant outlet 11 b . While passing through these paths, the refrigerant exchanges heat with the ambient air to be gradually condensed and liquefied.
  • the liquefaction of the gaseous refrigerant introduced from the refrigerant inlet 11 a starts at the end portion of the first path P 1 , for example, and the liquefied refrigerant RL flows out of the tube-outlets of the first path P 1 and tends to flow downwards in the first refrigerant turning portion T 1 , as shown in FIG. 3.
  • the gaseous refrigerant RG flows out of the tube-outlets of the first path P 1 , and goes up vigorously in the first turning portion T 1 . This rising gaseous refrigerant RG pushes up the aforementioned liquefied refrigerant RL.
  • the liquefied refrigerant RL goes up in the first refrigerant turning portion T 1 together with the gaseous refrigerant RG, and this rising mixture of refrigerant will be evenly distributed into each flat tube 12 constituting the second path P 2 smoothly.
  • the cross-sectional area of the second path P 2 is set to the aforementioned specific reduction rate to that of the first path P 1 , the flow velocity of the gaseous refrigerant rising in the first refrigerant turning portion T 1 between the first and second paths P 1 and P 2 can be secured enough. Therefore, a sufficient blow-up effect in the refrigerant turning portion T 1 can be obtained by the rising refrigerant, which in turn can prevent assuredly the stagnation of the liquefied refrigerant RL in the bottom portion of the refrigerant turning portion T 1 .
  • a condenser was manufactured in accordance with the aforementioned embodiment shown in FIGS. 1 and 2.
  • This condenser has three paths, i.e., the lowermost first path P 1 , the middle second path P 2 and the uppermost third path P 3 .
  • the first, second and third paths P 1 , P 2 and P 3 include twenty-two (22) tubes, nine (9) tubes and five (5) tubes, respectively.
  • the reduction rate of the cross-sectional area of the second path P 2 to that of the first path P 1 is 59.1%
  • the reduction rate of the cross-sectional area of the third path P 3 to that of the second path P 2 is 44.4%
  • the first, second and third paths P 1 , P 2 and P 3 include eighteen ( 1 a ) tubes, nine (9) tubes and five (5) tubes, respectively.
  • Another structure is the same as the condenser of the first example. In this condenser, the reduction rate of the cross-sectional area of the second path P 2 to that of the first path P 1 is 50%, and the reduction rate of the cross-sectional area of the third path P 3 to that of the second path P 2 is 44.4%
  • a condenser having four paths i.e., the lowermost first path P 1 , the lower middle second path P 2 , the upper middle third path P 3 and the uppermost fourth path P 4 .
  • the first, second, third and fourth paths P 1 , P 2 , P 3 and P 4 include thirteen (13) tubes, nine (9) tubes, six (6) tubes and four (4) tubes, respectively.
  • Another structure is the same as the condenser of the first example.
  • the reduction rate of the cross-sectional area of the second path P 2 to that of the first path P 1 is 30.8%
  • the reduction rate of the cross-sectional area of the third path P 3 to that of the second path P 2 is 33.3%
  • the reduction rate of the cross-sectional area of the fourth path P 4 to that of the third path P 3 is 33.3%.
  • the reference numeral T 4 denotes a fourth refrigerant turning portion (the same numeral will be used in FIG. 6)
  • a condenser having four paths i.e., the uppermost first path P 1 , the upper middle second path P 2 , the lower middle third path P 3 and the lowermost fourth path P 4 .
  • the first, second, third and fourth paths P 1 , P 2 , P 3 and P 4 include thirteen (13) tubes, nine (9) tubes, six (6) tubes and four (4) tubes, respectively.
  • Another structure is the same as the condenser of the first example.
  • This condenser according to the comparative example has a symmetrical configuration rotated by 180 degrees to the aforementioned condenser according to the third example.
  • the reduction rate of the cross-sectional area of the second path P 2 to that of the first path P 1 is 30.8%
  • the reduction rate of the cross-sectional area of the third path P 3 to that of the second path P 2 is 33.3%
  • the reduction rate of the cross-sectional area of the fourth path P 4 to that of the third path P 3 is 33.3%.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Valve Device For Special Equipments (AREA)
  • Oscillators With Electromechanical Resonators (AREA)
US09/884,802 2000-06-20 2001-06-19 Condenser Abandoned US20020007646A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000183966 2000-06-20
JP2000-183966 2000-06-20

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US20020007646A1 true US20020007646A1 (en) 2002-01-24

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US09/884,802 Abandoned US20020007646A1 (en) 2000-06-20 2001-06-19 Condenser

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US (1) US20020007646A1 (de)
EP (1) EP1167910B1 (de)
AT (1) ATE317100T1 (de)
DE (1) DE60116922T2 (de)
ES (1) ES2257360T3 (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070044948A1 (en) * 2005-08-31 2007-03-01 Jing-Ron Lu Water-cooled cooler for CPU of PC
US20100165572A1 (en) * 2003-03-19 2010-07-01 American Power Conversion Corporation Data center cooling
US20110108259A1 (en) * 2009-11-06 2011-05-12 Twin Air B.V. Holland Oil Cooler For A Motorized Vehicle
US20120000635A1 (en) * 2009-03-13 2012-01-05 Carrier Corporation Manifold assembly for distributing a fluid to a heat exchanger
US20120255703A1 (en) * 2009-10-19 2012-10-11 Sharp Kabushiki Kaisha Heat exchanger and air conditioner incorporating same
DE102011007216A1 (de) * 2011-04-12 2012-10-18 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
JP2013002774A (ja) * 2011-06-20 2013-01-07 Sharp Corp パラレルフロー型熱交換器及びそれを搭載した空気調和機
US20130213922A1 (en) * 2003-04-15 2013-08-22 Nestle Waters Management & Technology Container for product with thin wall
US20130219932A1 (en) * 2010-08-19 2013-08-29 Behr Gmbh & Co. Kg Coolant condenser assembly
US20150040603A1 (en) * 2012-01-30 2015-02-12 Valeo Systemes Thermiques Assembly Including A Heat Exchanger And A Mounting On Which Said Exchanger Is Mounted
US20160109192A1 (en) * 2013-05-24 2016-04-21 Sanden Holdings Corporation Interior heat exchanger
CN105727683A (zh) * 2016-05-09 2016-07-06 洛阳瑞昌石油化工设备有限公司 一种烟气冷凝静电处理装置和处理工艺
US20160327343A1 (en) * 2015-05-08 2016-11-10 Lg Electronics Inc. Heat exchanger of air conditioner
WO2018148760A1 (en) 2017-02-13 2018-08-16 Evapco, Inc. Multi-cross sectional fluid path condenser
US20180299205A1 (en) * 2015-10-12 2018-10-18 Charbel Rahhal Heat exchanger for residential hvac applications
CN110382977A (zh) * 2017-02-13 2019-10-25 艾威普科公司 多横截面流体路径冷凝器
CN113518535A (zh) * 2020-03-27 2021-10-19 春鸿电子科技(重庆)有限公司 液冷排模块
CN113707969A (zh) * 2020-05-08 2021-11-26 恒大新能源技术(深圳)有限公司 液冷板、电池包及流量控制方法

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DE102004001786A1 (de) * 2004-01-12 2005-08-04 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für überkritischen Kältekreislauf
EP1557630A1 (de) 2004-01-23 2005-07-27 BEHR Lorraine S.A.R.L. Wärmeübertrager
FR2915793B1 (fr) * 2007-05-03 2015-05-01 Valeo Systemes Thermiques Echangeur de chaleur ameliore pour circuit de climatisation de vehicule automobile
FR2928448B1 (fr) * 2008-03-04 2015-05-01 Valeo Systemes Thermiques Refroidisseur de gaz ameliore
DE102008038498A1 (de) * 2008-08-20 2010-02-25 Behr Gmbh & Co. Kg Wärmetauscher für ein Kraftfahrzeug
JP5732258B2 (ja) * 2010-02-16 2015-06-10 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
JP5717475B2 (ja) * 2010-04-16 2015-05-13 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
JP5717474B2 (ja) * 2010-04-16 2015-05-13 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
JP5609916B2 (ja) * 2012-04-27 2014-10-22 ダイキン工業株式会社 熱交換器
DE102013204294A1 (de) * 2013-03-12 2014-10-02 Behr Gmbh & Co. Kg Kondensatorbaugruppe für Kältemittel

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US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US5529116A (en) * 1989-08-23 1996-06-25 Showa Aluminum Corporation Duplex heat exchanger
US5682944A (en) * 1992-11-25 1997-11-04 Nippondenso Co., Ltd. Refrigerant condenser
EP0769666B1 (de) * 1995-10-18 2003-03-12 Calsonic Kansei Corporation Verflüssiger mit einem Flüssigkeitsbehälter
JP3131774B2 (ja) * 1997-09-26 2001-02-05 漢拏空調株式会社 車両エアコン用の多重流動型凝縮器

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100165572A1 (en) * 2003-03-19 2010-07-01 American Power Conversion Corporation Data center cooling
US20130213922A1 (en) * 2003-04-15 2013-08-22 Nestle Waters Management & Technology Container for product with thin wall
US20070044948A1 (en) * 2005-08-31 2007-03-01 Jing-Ron Lu Water-cooled cooler for CPU of PC
US20120000635A1 (en) * 2009-03-13 2012-01-05 Carrier Corporation Manifold assembly for distributing a fluid to a heat exchanger
US9562722B2 (en) * 2009-03-13 2017-02-07 Carrier Corporation Manifold assembly for distributing a fluid to a heat exchanger
US20120255703A1 (en) * 2009-10-19 2012-10-11 Sharp Kabushiki Kaisha Heat exchanger and air conditioner incorporating same
US20110108259A1 (en) * 2009-11-06 2011-05-12 Twin Air B.V. Holland Oil Cooler For A Motorized Vehicle
US9970694B2 (en) * 2010-08-19 2018-05-15 Mahle International Gmbh Coolant condenser assembly
US20130219932A1 (en) * 2010-08-19 2013-08-29 Behr Gmbh & Co. Kg Coolant condenser assembly
DE102011007216A1 (de) * 2011-04-12 2012-10-18 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
JP2013002774A (ja) * 2011-06-20 2013-01-07 Sharp Corp パラレルフロー型熱交換器及びそれを搭載した空気調和機
US20150040603A1 (en) * 2012-01-30 2015-02-12 Valeo Systemes Thermiques Assembly Including A Heat Exchanger And A Mounting On Which Said Exchanger Is Mounted
US9834061B2 (en) * 2012-01-30 2017-12-05 Valeo Systemes Thermiques Assembly including a heat exchanger and a mounting on which said exchanger is mounted
US20160109192A1 (en) * 2013-05-24 2016-04-21 Sanden Holdings Corporation Interior heat exchanger
US20160327343A1 (en) * 2015-05-08 2016-11-10 Lg Electronics Inc. Heat exchanger of air conditioner
CN106123403A (zh) * 2015-05-08 2016-11-16 Lg电子株式会社 空气调节器的热交换器
US20180299205A1 (en) * 2015-10-12 2018-10-18 Charbel Rahhal Heat exchanger for residential hvac applications
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ATE317100T1 (de) 2006-02-15
EP1167910A2 (de) 2002-01-02
DE60116922T2 (de) 2006-09-14
EP1167910A3 (de) 2003-11-26
ES2257360T3 (es) 2006-08-01
EP1167910B1 (de) 2006-02-01

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