EP0448183A2 - Condenseur - Google Patents

Condenseur Download PDF

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Publication number
EP0448183A2
EP0448183A2 EP91201248A EP91201248A EP0448183A2 EP 0448183 A2 EP0448183 A2 EP 0448183A2 EP 91201248 A EP91201248 A EP 91201248A EP 91201248 A EP91201248 A EP 91201248A EP 0448183 A2 EP0448183 A2 EP 0448183A2
Authority
EP
European Patent Office
Prior art keywords
headers
cooling medium
tubes
height
core
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP91201248A
Other languages
German (de)
English (en)
Other versions
EP0448183A3 (fr
Inventor
Hironaka Sasaki
Ryoichi Hoshino
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.)
Showa Aluminum Can Corp
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=14795773&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0448183(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Showa Aluminum Corp filed Critical Showa Aluminum Corp
Publication of EP0448183A2 publication Critical patent/EP0448183A2/fr
Publication of EP0448183A3 publication Critical patent/EP0448183A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F28F9/0243—Header boxes having a circular cross-section
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the present invention relates to a condenser particularly adapted for use in automobile air conditioning systems.
  • a "serpentine" type of condenser is well known and widely used, in which is made up of a multi-bored flat tube, commonly called “harmonica” tube, bent in zigzag form, and corrugated fins sandwiched between the bent tube walls. In this way a core is constituted.
  • the cooling medium path in a condenser is roughly classified into two sections, that is, and inlet side section and an outlet side section.
  • the cooling medium In the inlet side section the cooling medium is still in a gaseous state, and in the outlet side section it becomes liquid.
  • the area for heat exchange of the inlet side paths should be as large as possible.
  • that of the outlet side paths can be relatively small.
  • the "serpentine" type condenser consists of a single cooling medium path provided by a single pipe, an increase in the area for heat exchange in the inlet side section increases that of the outlet side section. As a whole the size of the condenser become large.
  • the inventors have made an invention relating to a "multi-flow" type condenser instead of the serpentine type, which is disclosed in Japanese Patent Publication (unexamined) No. 63-34466.
  • the multi-flow type condenser includes a plurality of tubes arranged in parallel and corrugated fins sandwiched therebetween, and headers connected to opposite ends of the tubes.
  • the headers have partitions which divide their inner spaces into at least two sections including an inlet side group of paths and an outlet side group of paths, thereby causing the cooling medium to flow in at least one zigzag pattern.
  • the total cross-sectional area of the inlet side group of paths progressively diminishes toward the outlet side group.
  • the inlet side section has an optimum area for accommodating the cooling medium in a gaseous state
  • the outlet side section has an optimum area for accommodating that in a liquid state.
  • the cooling medium undergoes a larger pressure loss, and the efficiency of heat exchange decreases because of the relatively small area for heat exchange. If, however, the area in the outlet side section is excessively reduced as compared with that of the inlet side section, pressure loss is likely to increase on the flow of the cooling medium. The area for heat exchange of the inlet side section becomes too large, thereby slowing down the flow rate of the cooling medium.
  • an object of the present invention is to provide a condenser having cooling medium paths divided in an inlet side section and an outlet side section in an optimum proportion, thereby increasing the efficiency of heat exchange and reducing the pressure loss of a cooling medium.
  • a condenser comprises a core and a pair of headers disposed parallel with each other, the core comprising: a plurality of tubes connected at ends thereof to the headers in fluid connection therewith and corrugated fins each disposed in an air flow path formed between the tubes wherein the headers are cylindrical pipes, is characterized in that the tubes are flat tubes each having inside thereof at least one reinforcing wall extending longitudinally of the flat tubes, the flat tubes each having their ends inserted in slits of the headers and soldered thereto in liquid-tight state, that each flat tube has the following dimensions:
  • the illustrated condenser includes a plurality of flat tubes 1 stacked in parallel and corrugated fins 2 sandwiched between the flat tubes 1.
  • the terminating ends of the flat tubes 1 are connected to headers 3 and 4.
  • Each flat tube is made of extruded aluminum, having a flat configuration as clearly shown in Figs. 2 to 4.
  • the flat tubes can be multi-bored flat tubes, commonly called “harmonica tube” or else, electrically seamed tubes can be used.
  • Each corrugated fin 2 has a width identical with that of the flat tube 1.
  • the fins 2 and the flat tubes 1 are brazed to each other.
  • the fins 2 are provided with louvers 2a on the surface.
  • the headers 3, 4 are made up of electrically seamed pipes of aluminum, and each have holes 5 of the same shape as the cross-section of the flat tubes 1 so as to accept the tube ends 1a.
  • the inserted tube ends 1a are brazed in the holes 5.
  • the headers 3 and 4 are connected to an inlet pipe 6 and an outlet pipe 7, respectively.
  • the inlet pipe 6 allows a cooling medium to enter the header 3, and the outlet pipe 8 allows the used cooling medium to discharge.
  • the headers 3 and 4 are closed with covers 7 and 9, respectively.
  • the reference numerals 13 and 14 denote side places attached to the outermost corrugated fins 2.
  • the header 3 has its inner space divided by a partition 10 into two sections, and the header 4 also has two sections divided by a partition 11.
  • the whole cooling medium path 12 is divided into an inlet side group (A), an intermediate group (B) and an outlet side group (C) as shown Figs. 1 and 6.
  • the cooling medium flows in zigzag patterns throughout the groups (A), (B) and (C).
  • the intermediate group (B) has a smaller number of flat tubes 1 (that is, paths) than the inlet side group (A), which means that the cross-sectional area of the intermediate group (C) of paths is smaller than that of the group (A).
  • the outlet side group (C) has a smaller number of flat tubes 1 (that is, the number of cooling medium paths) than the intermediate group (B), which means that the cross-sectional area of the outlet side group (C) of paths is smaller than that of the group (B).
  • the entire cross-sectional area of the outlet side group (C) is 30 to 60% of that of the inlet side group (A). If the percentage is less than 30%, the cross-sectional area of the outlet side group (C) becomes small to increase the pressure loss in the cooling medium. At the same time, the cross-sectional area of the inlet side group becomes large to slow down the flow rate of the cooling medium, thereby reducing the efficiency of heat exchange. If the percentage exceeds 60%, the cross-sectional area of the inlet side group (A) becomes small to increase the pressure loss in the cooling medium. In addition, the area for heat transfer is reduced, thereby reducing the efficiency of heat exchange.
  • the entire cross-sectional area of the outlet side group (C) is 35 to 50% of that of the inlet side group (A). As shown in Figs. 7 and 8, this more restricted range exhibits the highest efficiency of heat exchange and the lowest pressure loss in the cooling medium.
  • the cooling medium is introduced into the inlet side group (A) through the inlet pipe 6 and flows therethrough. Then the cooling medium turns from the right-hand header 4 and enters the intermediate group (B). Then it turns from the left-hand header 3 and enters the outlet side group (C). Finally the cooling medium is discharged through the outlet pipe 8. In this way the cooling medium flows in zigzag patterns. Air enters the air paths constituted by the corrugated fins 2 in the direction (W) in Fig. 2. Heat exchange is effected between the air and the cooling medium flowing through the groups (A), (B) and (C).
  • the cooling medium passes through the inlet side group (A), it is still in a gaseous state and has a relatively large volume, which is effectively accommodated in the capacity provided by the paths of the group (A) and keeps contact with the flat tubes 1 in a wide range so that the gaseous cooling medium smoothly condenses and reduces its volume.
  • the cooling medium flows through the outlet side group by way of the intermediate group (B), it becomes completely liquid, and has such a reduced volume as to be accommodated in a relatively small cross-sectional area of the outlet side group (C).
  • the pressure loss is minimized, thereby enhancing the efficiency of heat exchange.
  • the illustrated embodiment has three groups (A), (B) and (C), but the number (N) of groups is not limited to it. Preferably the number (N) is 2 to 5 groups for the reason explained below:
  • Figs. 9 to 11 show the results obtained by experiments in which condensers having twenty-four flat tubes are employed, each having a different number of groups.
  • a cooling medium is introduced into each of the condensers at the same flow rate.
  • Each graph shows the resulting rate of heat exchange and pressure loss in the cooling medium, and changes in the rate of heat exchange and pressure loss with respect to the ratio of the outlet side group to the inlet side group.
  • the inlet side group, the intermediate group and the outlet side group have the same cross-sectional area.
  • Fig. 9 shows the rates of heat exchange achieved when the speed of wind Vf is 2m/sec and when it is 3m/sec each in front of the condenser. It will be understood from Fig.
  • the number (N) of the groups is 2 to 5, the rate of heat exchange is high, and the pressure loss in the cooling medium is low. Thus the ratio between them is well balanced. As described above, it is arranged to ensure that the cross-sectional area of the outlet side group (C) is arranged to have 30 to 60% of that of the inlet side group (A). In addition, the number (N) of the group is arranged to be 2 to 5, which enhances the efficiency of the heat exchange as a result of the reduced pressure loss.
  • each flat tube 1 is in the range of 6.0 to 20mm, the height (Ht) thereof is in the range of 1.5 to 7.0mm, the height (Hp) of the cooling medium paths 12 in the flat tubes 1 is 1.0mm or more. It is also arranged that the height (Hf) of the corrugated fins 2 or a distance between the adjacent flat tubes 1 is in the range of 6 to 16mm and that the fin pitch (Fp) is in the range of 1.6 to 4.0mm.
  • the width (Wt) of each flat tube 1 is in the range of 6.0 to 20mm, the height (Ht) thereof is in the range of 1.5 to 7.0mm, the height (Hp) of the cooling medium paths 12 in the flat tubes 1 is 1.0mm or more. It is also arranged that the height (Hf) of the corrugated fins 2 or a distance between the adjacent flat tubes 1 is in the range of 6 to 16mm and that the fin pitch (Fp) is in the range of 1.6 to 4.0mm.
  • the width (Wt) of the flat tubes 1 is less than 6.0mm, the corrugated fins 2 sandwiched therebetween will be accordingly narrow in width.
  • the narrow width of the corrugated fins 2 limit the size and number of the louvers 2a, which decreases the efficiency of heat exchange.
  • the flat tubes 1 are 20mm or more, the corrugated fins 2 sandwiched therebetween will accordingly become large.
  • the large fins increases a drag on the flowing air.
  • the large fins increases the weight of the condenser. It is therefore preferred that the width (Wt) of the flat tubes is in the range of 6.0 to 16mm, more preferably, 10 to 14mm.
  • each flat tube 1 is preferably in the range of 1.5 to 7.0mm. If it exceeds 7.0mm, the pressure loss in the air flow increases. If it is less than 1.5mm, it is difficult to increase the height (Hp) of the air paths by 1.0mm or more because of the limited thickness of the flat tubes. It is preferred that it is in the range of 1.5 to 5.0mm; more preferably, 2.5to 4.0mm.
  • the height (Hp) of the cooling medium flow paths in the flat tubes 1 is preferably 1.0mm or more. If it is less than 1.0mm, the pressure loss in the cooling medium increases, thereby decreasing the rates of heat transfer. It is preferred that it is in the range of 1.5 to 2.0mm.
  • the height (Hf) of the corrugated fins 2 is in the range of 6.0 to 16mm. If it is less than 6mm, the pressure loss in the air will increase as shown in Fig. 14. If it exceeds 16mm, the number of total fins decreases, thereby reducing the efficiency of heat exchange.
  • the optimum range is 8.0 to 12mm.
  • the fin pitches is preferably in the range of 1.6 to 4.0mm. If they are less than 1.6mm, the louvers 2a interfere with the flow of the air, thereby increasing the pressure loss in the air flow. If they exceed 4.0mm, the efficiency of heat exchange decreases. It is therefore preferred that the range is 1.6 to 3.2mm; more preferably, 2.0 to 3.2mm.
  • the condensers of the present invention are constructed with the flat tubes, the corrugated fins and the headers in which the widths and heights of the flat tubes, the heights of the cooling medium flow paths, the heights and pitches of the fin are determined at optimum values, thereby reducing the pressure losses which the air and the cooling medium undergo. As a result the efficiency of heat exchanges is enhanced.
  • the cross-sectional area of the cooling medium paths 12 progressively diminishes from the inlet side group to the outlet side group through the intermediate group.
  • the inlet side group and the intermediate group have the same cross-sectional area which is larger than that of the outlet side group.
  • the reduction in the cross-sectional area is effected by reducing the number of the flat tubes, but it is possible to reduce the cross-sectional areas of the individual flat tubes without changing the number thereof.
  • the headers 3 and 4 are provided at their erected postures between which the flat tubes 1 are horizontally stacked one above another, but it is possible to modify it to an embodiment in which the headers 3 and 4 are positioned up and down between. which the flat tubes are vertically arranged in parallel.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Valve Device For Special Equipments (AREA)
  • Oscillators With Electromechanical Resonators (AREA)
  • Vending Machines For Individual Products (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
EP19910201248 1988-09-14 1989-05-25 Condenseur Withdrawn EP0448183A3 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP12082088 1988-09-14
JP120820/88 1988-09-14
EP89305294A EP0359358B2 (fr) 1988-09-14 1989-05-25 Condenseur

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP89305294A Division EP0359358B2 (fr) 1988-09-14 1989-05-25 Condenseur
EP89305294.4 Division 1989-05-25

Publications (2)

Publication Number Publication Date
EP0448183A2 true EP0448183A2 (fr) 1991-09-25
EP0448183A3 EP0448183A3 (fr) 1991-10-16

Family

ID=14795773

Family Applications (2)

Application Number Title Priority Date Filing Date
EP19910201248 Withdrawn EP0448183A3 (fr) 1988-09-14 1989-05-25 Condenseur
EP89305294A Expired - Lifetime EP0359358B2 (fr) 1988-09-14 1989-05-25 Condenseur

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP89305294A Expired - Lifetime EP0359358B2 (fr) 1988-09-14 1989-05-25 Condenseur

Country Status (6)

Country Link
EP (2) EP0448183A3 (fr)
KR (2) KR0184854B1 (fr)
AT (1) ATE136639T1 (fr)
AU (1) AU618840B2 (fr)
CA (1) CA1334796C (fr)
DE (1) DE68926202T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003048670A1 (fr) * 2001-11-30 2003-06-12 Modine Manufacturing Company Echangeur de chaleur produisant un refroidissement surcritique d'un fluide de travail dans un cycle de refroidissement transcritique

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4020591C2 (de) * 1990-06-28 1995-12-07 Diesel Kiki Co Mehrfachdurchfluß-Kondensator
FR2665757B1 (fr) * 1990-08-08 1997-01-17 Valeo Thermique Moteur Sa Condenseur de fluide refrigerant a circulation verticale, et procede de fabrication.
JP3044436B2 (ja) * 1994-04-21 2000-05-22 株式会社ゼクセル 積層型熱交換器
AU5121598A (en) 1997-05-12 1998-12-08 Norsk Hydro Asa Heat exchanger
WO2002081998A1 (fr) 2001-04-04 2002-10-17 Norsk Hydro Asa Collecteur d'echangeur thermique
KR100913141B1 (ko) 2004-09-15 2009-08-19 삼성전자주식회사 마이크로채널튜브를 이용한 증발기
FR2928448B1 (fr) * 2008-03-04 2015-05-01 Valeo Systemes Thermiques Refroidisseur de gaz ameliore
PL2369284T3 (pl) * 2010-03-23 2018-06-29 Akg-Thermotechnik Gmbh & Co.Kg Wymiennik ciepła, zwłaszcza kondensacyjnej suszarki do bielizny
JP5609916B2 (ja) * 2012-04-27 2014-10-22 ダイキン工業株式会社 熱交換器
KR101425042B1 (ko) * 2012-07-26 2014-08-01 엘지전자 주식회사 실외 열교환기
ES1139060Y (es) 2012-09-14 2015-08-07 Revent Int Ab Horno de aire caliente
EP2722629A1 (fr) 2012-10-16 2014-04-23 Behr GmbH & Co. KG Condensateur

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6334466A (ja) 1986-07-29 1988-02-15 昭和アルミニウム株式会社 凝縮器

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1958226A (en) * 1932-04-06 1934-05-08 Fedders Mfg Co Inc Condenser for refrigerating apparatus
FR2478807A1 (fr) * 1980-03-21 1981-09-25 Deville Ste Indle Boite collectrice de raccordement pour appareil d'echanges thermiques
DE3752324T2 (de) * 1986-07-29 2001-03-29 Showa Aluminium Co Ltd Kondensator
NL8700641A (nl) * 1987-03-18 1988-10-17 Radson Bv Ketelelement.
DE3860582D1 (de) * 1987-03-25 1990-10-18 Johann Schoenhammer Gegenstromwaermetauscher.
DE3725602A1 (de) * 1987-08-01 1989-02-09 Sueddeutsche Kuehler Behr Flachrohr fuer einen waermetauscher
DE3730117C1 (de) * 1987-09-08 1988-06-01 Norsk Hydro As Verfahren zum Herstellen eines Waermetauschers,insbesondere eines Kraftfahrzeugkuehlers und Rohrprofil zur Verwendung bei einem derartigen Verfahren

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6334466A (ja) 1986-07-29 1988-02-15 昭和アルミニウム株式会社 凝縮器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003048670A1 (fr) * 2001-11-30 2003-06-12 Modine Manufacturing Company Echangeur de chaleur produisant un refroidissement surcritique d'un fluide de travail dans un cycle de refroidissement transcritique

Also Published As

Publication number Publication date
KR0184854B1 (en) 1999-05-01
EP0359358B1 (fr) 1996-04-10
AU618840B2 (en) 1992-01-09
CA1334796C (fr) 1995-03-21
EP0359358A1 (fr) 1990-03-21
DE68926202D1 (de) 1996-05-15
DE68926202T3 (de) 2002-05-16
KR900005136A (ko) 1990-04-13
DE68926202T2 (de) 1996-09-05
AU4091589A (en) 1990-03-22
ATE136639T1 (de) 1996-04-15
EP0448183A3 (fr) 1991-10-16
KR960009342B1 (en) 1996-07-18
EP0359358B2 (fr) 2001-10-24

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