EP0762070A1 - Kühlrohre für Wärmetauscher - Google Patents

Kühlrohre für Wärmetauscher Download PDF

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Publication number
EP0762070A1
EP0762070A1 EP96110844A EP96110844A EP0762070A1 EP 0762070 A1 EP0762070 A1 EP 0762070A1 EP 96110844 A EP96110844 A EP 96110844A EP 96110844 A EP96110844 A EP 96110844A EP 0762070 A1 EP0762070 A1 EP 0762070A1
Authority
EP
European Patent Office
Prior art keywords
tube
walls
reinforcing
communication holes
heat exchanger
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.)
Granted
Application number
EP96110844A
Other languages
English (en)
French (fr)
Other versions
EP0762070B1 (de
Inventor
Yuji Yamamoto
Shinji Ito
Yuichi Furukawa
Koichi Take
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.)
Altemira Co Ltd
Original Assignee
Showa Aluminum 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 Showa Aluminum Corp filed Critical Showa Aluminum Corp
Publication of EP0762070A1 publication Critical patent/EP0762070A1/de
Application granted granted Critical
Publication of EP0762070B1 publication Critical patent/EP0762070B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/048—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C23/00—Extruding metal; Impact extrusion
    • B21C23/02—Making uncoated products
    • B21C23/04—Making uncoated products by direct extrusion
    • B21C23/08—Making wire, rods or tubes
    • B21C23/10—Making finned tubes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/15—Making tubes of special shape; Making tube fittings
    • B21C37/151—Making tubes with multiple passages
    • 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
    • F28D1/0308—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 the conduits being formed by paired plates touching each other
    • F28D1/0316—Assemblies of conduits in parallel
    • 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
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—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
    • 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 tubes for passing a refrigerant therethrough, i.e., refrigerant tubes, for heat exchangers, and more particularly to refrigerant tubes for condensers and evaporators for use in air-cooling systems for motor vehecles.
  • the object of the present invention is to provide a refrigerant tube for use in heat exchangers which achieves a high heat exchange efficiency.
  • the refrigerant to be passed through the parallel refrigerant passages flows through the communication holes widthwise of the tube to spread to every part of all the passages, whereby portions of the refrigerant become mixed together. Accordingly no temperature difference occurs in the refrigerant between the passages, with the result that the refrigerant undergoes condensation at the upstream side and at the downstream side alike, flowing uniformly to achieve an improved heat exchange efficiency.
  • the opening ratio which is the proportion of all the communication holes in the reinforcing wall to this wall influences thermal conductance. When within the range of 10 to 40 %, the opening ratio results in satisfactory thermal conductance, whereby the heat exchange efficiency of the refrigerant tube can be further improved.
  • the opening ratio is limited to the range of 10 to 40% because if the ratio is less than 10%, the thermal conductance does not increase and further because the conductance no longer increases even if the ratio exceeds 40%, entailing an increase only in coefficient of friction.
  • the opening ratio in the range of 10 to 40% is preferably 10 to 30%, more preferably about 20%.
  • the communication holes are so sized in cross section as to permit the refrigerant to smoothly flow therethrough between the adjacent passages, to be free of the likelihood of becoming clogged with a flow of solder during brazing and to in no way impair the pressure resistance of the tube.
  • the pitch of the communication holes is such that the holes will not lower the pressure resistance of the tube while permitting the refrigerant to smoothly flow across the reinforcing walls.
  • the communication holes formed in the plurality of reinforcing walls are preferably in a staggered arrangement when seen from above.
  • FIG. 19 shows a condenser comprising flat refrigerant tubes embodying the invention.
  • the condenser comprises a pair of headers 61, 62 arranged at left and right in parallel and spaced apart from each other, parallel flat refrigerant tubes 63 each joined at its opposite ends to the two headers 61, 62, corrugated fins 64 arranged in air flow clearances between the adjacent refrigerant tubes 63 and brazed to the adjacent refrigerant tubes 63, an inlet pipe 65 connected to the upper end of the left header 61, an outlet pipe 66 connected to the lower end of the right 62, a left partition 67 provided inside the left header 61 and positioned above the midportion thereof, and a right partition 68 provided inside the right header 62 and positioned below the midportion thereof, the number of refrigerant tubes 63 between the inlet pipe 65 and the left partition 67, the number of refrigerant tubes 63 between the left partition 67 and the right partition 68 and the number of regrigerant tubes
  • the refrigerant tubes 63 for use in the above condenser are concerned with the present invention.
  • Refrgigerant tubes embodying the invention will be described below.
  • the following embodiments are all 10 to 40% in opening ratio which is the proportion of all communication holes in each reinforcing wall to the reinforcing wall.
  • the communication holes formed in a plurality of reinforcing walls are all in a staggered arrangement.
  • a refrigerant tube T1 for heat exchangers is formed by a flat aluminum tube 7 having parallel refrigerant passages 6 in its interior and comprising flat upper and lower walls 1, 2, left and right vertical side walls 3, 4 connected respectively between the left side edges of the upper and lower walls 1, 2 and between the right side edges thereof, and a plurality of reinforcing walls 5 connected between the upper and lower walls 1, 2, extending longitudinally of the tube and spaced apart from one another by a predetermined distance.
  • the reinforcing walls 5 are each formed with a plurality of rectangular communiction holes 8 for causing the parallel refrigerant passages 6 to communicate with each other therethrough,
  • the reinforcing walls 5 are formed by parallel ridges 11 projecting inward from the lower wall 2 and joined to the inner surface of the upper wall 1.
  • the rectangular communication holes 8 are formed by rectangular cutouts 12 provided in the upper edge of each ridge 11 at a predetermined spacing and having their openings closed by the upper wall 1.
  • the refrigerant tube T1 is produced by the following method.
  • the lower roll 17 is provided, at its respective outer ends, with large-diameter portions 18 each having an outer end face flush with that of the second small-diameter portion 16 and having a smaller width than the portion 16.
  • the peripheral surfaces of the rolling rolls 13, 17 form a flat portion 19 providing the lower wall 2 by thinning the sheet blank to a specified thickness.
  • the rolls 13, 17 also form ridges 11 projecting from the flat portion 19 integrally therewith by means of the annular grooves 14.
  • Further formed at the respective side edges of the flat portion 19 are upright portions 20 each including an inner stepped part 20a with the same height as the ridges 11, and a thin wall 20b extending upward from the outer edge of the stepped part 20a.
  • the multiplicity of protrusions 23 are in a staggered arrangement so that the cutouts 12 are formed in the upper edges of the parallel ridges 11 in a staggered arrangement when seen from above.
  • the side walls 28, 29 are formed by the following method.
  • Upright portions 36 having the same height as the reinforcing walls 5 are provided respectively at opposite sides of the lower aluminum sheet 35, and a slope 38 slanting outwardly upward is formed at the bottom edge of each upright portion 36.
  • a depending portion 37 is formed at each of opposite sides of the upper aluminum sheet 34, the portion 37 being in contact with with the outer side face of the upright portion 36 and projecting downward slightly beyond the lower surface of the lower wall 2.
  • the downward projections 37a of the depending portions 37 are crimped onto the respective slopes 38 of the lower aluminum sheet 35, and the portions where the upper and lower aluminum sheets 34, 35 are in contact with each other are brazed.
  • FIG. 10 shows this embodiment, i.e., a refrigerant tube T3 for use in heat exchangers, which comprises a flat aluminum tube 39.
  • the tube 39 is prepared from an aluminum sheet 40 in the form of a brazing sheet having a brazing filler metal layer on one surface thereof, by folding the sheet at the midportion of its width like a hairpin with the brazing layer out so as to form a hollow portion, bending opposite side edges to an arcuate shape and joining the side edges in butting contact with each other.
  • the tube 39 therefore has circular-arc left and right side walls 41, 42.
  • the butt joint 43 thus made is oblique in cross section so as to form the joint 43 over an increased area.
  • Each of reinforcing walls 44 is formed by joining a downward ridge 44a inwardly projecting from the upper wall 1 to an upward ridge 44b inwardly projecting from the lower wall 2.
  • Each of trapezoidal communication holes 5 is formed by the combination of a pair of trapezoidal cutouts 45a, 45b. Such cutouts 45a, 45b are formed respectively in the lower edge of the downward ridge 44a and the upper edge of the upward ridge 44b at a predetermined spacing.
  • FIG. 11 shows this embodiment, i.e., a heat exchange refrigerant tube T4, which has two kinds of reinforcing walls 46.
  • the walls 46 of one kind are each formed by a downward ridge 46a inwardly projecting from an upper wall 1 and joined to a flat inner surface of a lower wall 2.
  • the walls 46 of the other kind are each formed by an upward ridge 46b inwardly projecting from the lower wall 2 and joined to a flat inner surface of the upper wall 1.
  • the two kinds of walls 46 are arranged alternately.
  • Trapezoidal communication holes 47 are formed by trapezoidal cutouts 47a, 47b provided respectively in the lower edge of the downward ridge 46a and in the upper edge of the upward ridge 46b and have their openings closed by one of the upper and lower walls 1, 2.
  • the present embodiment is the same as Embodiment 3.
  • FIG. 12 shows this embodiment, i.e., a heat exchanger refrigerant tube T5.
  • the tube T5 has reinforcing walls 48 which are formed by downward ridges 48a inwardly projecting from an upper wall 1 and joined to a flat inner surface of a lower wall 2.
  • Trapezoidal communication holes 49 are formed by providing trapezoidal cutouts 49a in the lower edges of the ridges 48a at a predetermined spacing and closing the openings of the cutouts 49a with the lower wall 2.
  • the present embodiment is the same as Embodiment 3 except for this feature.
  • FIG. 13 shows this embodiment, i.e., a heat exchange refrigerant tube T4, which comprises a flat aluminum tube 50.
  • the tube 50 is prepared from upper and lower two aluminum sheets 51, 53 by bending opposite side edges of the sheets to an arcuate shape toward each other so as to form a hollow portion, butting the sheets against each other edge to edge and joining the butted edges.
  • the present embodiment is the same as Embodiment 3.
  • the left and right butt joints 53, 54 are oblique in cross section as is the case with Embodiment 3.
  • the aluminum sheet having the ridges, etc. and used in the foregoing embodiments can be replaced by an aluminum extrudate of specified cross section.
  • Example 2 The same refrigerant tube as that of Example 1 except that the tube is 0.8 mm in the height of communication holes and 40% in opening ratio.
  • the refrigerant tubes of Example 1 and Comparative Example were used to determine the relationship between the average quality X of refrigerant (the fraction of vapor mass in refrigerant) and the thermal conductance hA (h: heat transfer coefficient, A: the area of heat transfer surface inside the refrigerant tube).
  • the method of determination was as follows. The refrigerant tube was placed in a cooling water channel, a refrigerant comprising HFC134a was passed through the tube, and cooling water was passed through the channel.
  • the mass velocity G of the refrigerant was set at 400 kg/m 2 ⁇ s, the refrigerant inlet temperature at 65 o C, and the heat flux between the refrigerant and the cooling water at 8 kW/m 2 .
  • the flow rate of the cooling water was so set as to give a Reynolds number of 1500.
  • the thermal conductance hA was measured at varying values of average quality X.
  • the refrigerant tubes of Examples 1 to 4 and Comparative Example were used to determine, by the same method as in Evaluation Test 1, the relationship between the opening ratio and the heat transfer coefficient h at an average quality X of refrigrant of 20%, 50% or 80%, and the relationship between the opening ratio and the coefficient of friction f when the average quality X of refrigerant was 50% (Reynolds number: 10 4 ).
  • FIG. 17 shows the result.
  • FIG. 17 indicates that at any value of average quality X, the heat transfer coefficient h is greater when the reinforcing walls are formed with communication holes than when no holes are formed, and that the heat transfer coefficient h is especially great at an opening ratio of 20%.
  • FIG. 19 Three kinds of condensers of the multiflow type shown in FIG. 19 were fabricated using the refrigerant tube of Example 2 or Comparative Example. More specifically, 37 refrigerant tubes, and corrugated fins, 22 mm in width, 7 mm in height and 1 mm in fin pitch, were used for making a core portion measuring 326 mm in width, 330.5 mm in height and 0.108 m 2 in front area, and opposite ends of each tube were connected to right and left headers. No partition was provided in opposite headers in the condenser of the type I (single pass).
  • the condenser of the type II had a partition inside the left header above the midportion thereof, another partition inside the right header below the midportion thereof, 20 refrigerant tubes positioned above the partition of the left header, 11 refrigerant tubes arranged between the two partitions, and 6 refrigerant tubes positioned below the partition of the tight header (three passes).
  • the condenser of the type III had two partitions positioned respectively in an upper portion and a lower portion of the left header, two partitions positioned inside the right header, one at an intermediate level between the two partitions of the left header and the other at a level below the lower partition of the left header, 12 refrigerant tubes positioned above the upper partition of the left header, 9 refirgerant tubes between the upper partition of the left header and the upper partition of the right header, 7 refrigerant tubes positioned between the upper partition of the right header and the lower partition of the left header, 5 refrigerant tubes positioned between the lower partition of the left header and the lower partition of the right header, and 4 refrigerant tubes positioned below the lower partition of the right header (five passes).
  • the condensers were checked for the relationship between the refrigerant pressure loss ⁇ Pr and the quantity of heat radiated per unit front area, Q/Fa.
  • FIG. 18 shows the result.
  • FIG. 18 shows that the capacitor comprising the refrigerant tube wherein the reinforcing walls are formed with communication holes at an opening ratio of 20% exhibits an improved performance over the condenser comprising the refrigerant tube having no communication holes in the reinforcing walls and achieves an improvement even when the pressure loss is the same.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP96110844A 1995-07-07 1996-07-04 Kühlrohre für Wärmetauscher Expired - Lifetime EP0762070B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP172007/95 1995-07-07
JP17200795 1995-07-07
JP7172007A JPH0926278A (ja) 1995-07-07 1995-07-07 熱交換器用冷媒流通管およびこれを用いたカー・クーラ用コンデンサ

Publications (2)

Publication Number Publication Date
EP0762070A1 true EP0762070A1 (de) 1997-03-12
EP0762070B1 EP0762070B1 (de) 2001-02-28

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96110844A Expired - Lifetime EP0762070B1 (de) 1995-07-07 1996-07-04 Kühlrohre für Wärmetauscher

Country Status (17)

Country Link
EP (1) EP0762070B1 (de)
JP (1) JPH0926278A (de)
KR (1) KR100414852B1 (de)
CN (1) CN1111717C (de)
AR (1) AR002691A1 (de)
AT (1) ATE199456T1 (de)
AU (1) AU711980B2 (de)
BR (1) BR9602985A (de)
CA (1) CA2180598C (de)
CZ (1) CZ293383B6 (de)
DE (1) DE69611868T2 (de)
ES (1) ES2154366T3 (de)
IN (1) IN188905B (de)
MX (1) MX9602646A (de)
MY (1) MY119070A (de)
TW (1) TW296425B (de)
ZA (1) ZA965732B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0838641A3 (de) * 1996-10-24 1999-09-22 Showa Aluminum Corporation Verdampfer
WO2008064228A1 (en) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Multichannel evaporator with flow mixing microchannel tubes

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DE10201511A1 (de) * 2002-01-17 2003-07-31 Behr Gmbh & Co Geschweißtes Mehrkammerrohr
EP1546628A4 (de) * 2002-08-09 2012-01-11 Showa Denko Kk Flachrohr und verfahren zur herstellung eines wärmetauschers unter verwendung des flachen rohrs
TWI468535B (zh) * 2012-11-20 2015-01-11 Truan Sheng Lui 粗大鋁結晶抑制矽擴散方法
JP6243232B2 (ja) * 2014-01-17 2017-12-06 株式会社ティラド 熱交換器用フィンの製造方法およびそのフィン並びに熱交換器
CN103968700B (zh) * 2014-05-26 2016-08-24 赵耀华 一种高效换热水管以及热管辐射采暖/制冷系统
CN108253827B (zh) * 2016-12-28 2020-06-23 神讯电脑(昆山)有限公司 铝挤型热板及其制造方法
CN109097074B (zh) * 2018-10-15 2023-09-19 中冶焦耐(大连)工程技术有限公司 一种单路供水底部水冷熄焦车及其工作方法
CN109357545B (zh) * 2018-11-28 2024-05-31 博格华纳排放系统（宁波）有限公司 一种车用冷却器
CN110670799B (zh) * 2019-10-10 2021-11-09 李居强 带腔体的结构板及其制作方法
CN111192221B (zh) * 2020-01-07 2024-04-16 中南大学 基于深度卷积生成对抗网络的铝电解火眼图像修补方法
US11255610B2 (en) * 2020-01-22 2022-02-22 Cooler Master Co., Ltd. Pulse loop heat exchanger and manufacturing method of the same
JP7532788B2 (ja) * 2020-02-05 2024-08-14 株式会社レゾナック 電池モジュール
JP7561878B2 (ja) * 2020-12-28 2024-10-04 三菱電機株式会社 除湿装置

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DE2209325B2 (de) * 1970-05-18 1977-12-08 Noranda Metal Industries Ine, Bellingham, Wash. (V.StA.) Waermeaustauschrohr
DE3731669A1 (de) * 1987-09-21 1989-04-06 Sueddeutsche Kuehler Behr Flaches waermetauscherrohr
EP0338704A1 (de) * 1988-04-13 1989-10-25 Mitsubishi Aluminum Kabushiki Kaisha Wärmeaustauscherkern

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JP2718193B2 (ja) * 1989-07-08 1998-02-25 株式会社デンソー 熱交換器
JP3364665B2 (ja) * 1993-03-26 2003-01-08 昭和電工株式会社 熱交換器用冷媒流通管
US5323851A (en) * 1993-04-21 1994-06-28 Wynn's Climate Systems, Inc. Parallel flow condenser with perforated webs

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Publication number Priority date Publication date Assignee Title
DE2209325B2 (de) * 1970-05-18 1977-12-08 Noranda Metal Industries Ine, Bellingham, Wash. (V.StA.) Waermeaustauschrohr
DE3731669A1 (de) * 1987-09-21 1989-04-06 Sueddeutsche Kuehler Behr Flaches waermetauscherrohr
EP0338704A1 (de) * 1988-04-13 1989-10-25 Mitsubishi Aluminum Kabushiki Kaisha Wärmeaustauscherkern

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0838641A3 (de) * 1996-10-24 1999-09-22 Showa Aluminum Corporation Verdampfer
WO2008064228A1 (en) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Multichannel evaporator with flow mixing microchannel tubes
US7802439B2 (en) 2006-11-22 2010-09-28 Johnson Controls Technology Company Multichannel evaporator with flow mixing multichannel tubes

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DE69611868D1 (de) 2001-04-05
MY119070A (en) 2005-03-31
CZ9602008A3 (en) 1997-04-16
ZA965732B (en) 1997-01-23
TW296425B (de) 1997-01-21
ATE199456T1 (de) 2001-03-15
CA2180598A1 (en) 1997-01-08
ES2154366T3 (es) 2001-04-01
CZ293383B6 (cs) 2004-04-14
KR970007278A (ko) 1997-02-21
EP0762070B1 (de) 2001-02-28
MX9602646A (es) 1997-06-28
CN1140828A (zh) 1997-01-22
IN188905B (de) 2002-11-16
AU711980B2 (en) 1999-10-28
CN1111717C (zh) 2003-06-18
AR002691A1 (es) 1998-03-25
AU5834496A (en) 1997-01-23
KR100414852B1 (ko) 2004-03-31
CA2180598C (en) 2007-06-05
JPH0926278A (ja) 1997-01-28
DE69611868T2 (de) 2001-06-13
BR9602985A (pt) 1998-04-28

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