EP1447636A1 - Wärmetauscher - Google Patents

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Publication number
EP1447636A1
EP1447636A1 EP03100286A EP03100286A EP1447636A1 EP 1447636 A1 EP1447636 A1 EP 1447636A1 EP 03100286 A EP03100286 A EP 03100286A EP 03100286 A EP03100286 A EP 03100286A EP 1447636 A1 EP1447636 A1 EP 1447636A1
Authority
EP
European Patent Office
Prior art keywords
header tank
inlet
return
heat exchanger
chamber
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Withdrawn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
EP03100286A
Other languages
English (en)
French (fr)
Inventor
Tim A. Cowell
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to EP03100286A priority Critical patent/EP1447636A1/de
Publication of EP1447636A1 publication Critical patent/EP1447636A1/de
Withdrawn legal-status Critical Current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
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/08—Reinforcing means for header boxes

Definitions

  • the present invention relates to a heat exchanger, in particular a heat exchanger for an automotive vehicle.
  • Such heat exchangers generally comprise two hollow header tanks with a plurality of flat tubes arranged therebetween.
  • a refrigerant inlet is connected to the first header tank and a refrigerant outlet is either connected to the first or second header tank, depending on the refrigerant flow configuration of the heat exchanger.
  • the header tanks comprise slots for receiving the ends of the flat tubes therein, such that refrigerant can flow from one header tank to the other.
  • the header tank consists of a tube with generally circular cross-section.
  • This design proves to be very satisfactory with traditional pressures of commonly used refrigerants, such as e.g. R134a.
  • refrigerants such as e.g. R134a.
  • a pressure between 2.5 and 6 bar has been used at the low-pressure side
  • a pressure between 15 and 30 bar has been used at the high-pressure side.
  • CO 2 the more environmentally friendly CO 2 as refrigerant.
  • high-pressure systems as e.g. CO 2 systems
  • the low pressure is between 35 and 80 bar and the high pressure is between 80 and 170 bar.
  • the wall thickness of the header tanks has been increased. This however results in an increase in size and weight of the heat exchanger, which is considered a disadvantage in the automotive industry.
  • EP-A-0 608 439 proposes a heat exchanger comprising a number of heat exchange modules, each module comprising a first and second header tank of generally circular cross-section and a plurality of flat tubes therebetween.
  • the first header tanks are in fluid communication with an inlet manifold for receiving refrigerant from the refrigeration circuit and for delivering the refrigerant to the individual first header tanks.
  • the second header tanks are in fluid communication with an outlet manifold for collecting refrigerant received from the individual second header tanks and for returning the refrigerant to the refrigeration circuit. Due to the smaller diameter of the header tanks, the latter are able to allow much higher refrigerant pressures.
  • a disadvantage of this design is that a number of parallel flow paths are created through the first header tanks, the flat tubes and the second header tanks. Due to the effects of a pressure drop, the flow rates in the different available flow paths can be different. This leads to a loss of performance of the heat exchanger. Furthermore, it will be appreciated that the manufacture of a heat exchanger consisting of a number of smaller heat exchangers is rather costly.
  • header tank is formed by an extruded element comprising a number of parallel tubes of generally circular cross-section. Slots are arranged in the extruded element so as to receive the flat tubes therein. The slots are arranged such that, when the flat tubes are arranged in the slots, a communication passage exists between neighbouring parallel tubes constituting the header tank for balancing the refrigerant flow between them.
  • This design allows a more regular flow pattern of the refrigerant through the heat exchanger and hence better performance.
  • a major disadvantage of this design is the fact that the slots for receiving the flat tubes are not easily formed. Consequently, the manufacture of these heat exchangers is rather expensive.
  • the object of the present invention is to provide an improved heat exchanger, which does not have the above-mentioned disadvantages. This object is achieved by a heat exchanger as claimed in claim 1.
  • the present invention proposes a heat exchanger, in particular for an automotive vehicle, comprising an inlet header tank, a return header tank and an outlet header tank, the inlet header tank comprising an inlet port for receiving refrigerant from a refrigeration circuit and the outlet header tank comprising an outlet port for returning refrigerant to the refrigeration circuit.
  • the heat exchanger further comprises a plurality of flat tubes extending between the inlet and outlet header tanks and the return header tank and being in fluid connection therewith, for leading refrigerant from the inlet header tank to the outlet header tank via the return header tank.
  • a partition wall is arranged in the return header tank, the partition wall dividing the return header tank into a first chamber and a second chamber, the partition wall comprising openings therein for fluidly connecting the first chamber to the second chamber.
  • the above partition wall is an easy and effective means for reinforcing the return header tank, while allowing refrigerant to flow from one chamber to the other.
  • the reinforcement of the return header tank is of particular interest when the refrigerant used in the refrigeration circuit is at high pressure, as is e.g. the case in CO 2 systems.
  • the partition wall in the return header tank extends longitudinally therethrough, such that the first and second chambers are arranged side-by-side in a longitudinal direction of the return header tank.
  • Refrigerant in the heat exchanger flows through the flat tubes from the inlet header tank to the first chamber of the return header tank in a first plane.
  • the refrigerant then passes through the openings in the partition wall from the first chamber to the second chamber.
  • Refrigerant finally flows through the flat tubes from the second chamber of the return header tank to the outlet header tank in a second plane.
  • the first and second planes are parallel to each other.
  • a face-U flow configuration is achieved, in which air blown through the heat exchanger first encounters one plane of refrigerant and then the other plane of refrigerant.
  • the heat transfer between the refrigerant in the heat exchanger and the air passing inbetween the flat tubes is improved, whereby, in turn, the efficiency of the heat exchanger is improved.
  • the return header tank is preferably folded from one sheet of metal having two parallel longitudinal edges, wherein the partition wall is formed by at least one of the longitudinal edges extending into the return header tank.
  • a folded header tank can be very easily produced.
  • the manufacture of such folded header tanks is significantly cheaper than extruded header tanks.
  • the end of the longitudinal edge extends to the inner wall of the folded header tank and is preferably brazed thereto. For further strength, both longitudinal edges can extend into the return header tank.
  • openings in the partition wall can be very easily achieved.
  • these openings are e.g. punched into the sheet of metal before the latter is folded into a folded return header tank.
  • the partition wall is inserted between walls of the return header tank.
  • the inlet and outlet header tanks are preferably two separate tubes, a first tube defining the inlet header tank and a second tube defining the outlet header tank.
  • the inlet and outlet header tanks can be formed by a single tube with a divider therein for dividing the single tube into the inlet header tank and the outlet header tank. It will however be appreciated that, when two separate tubes are used, heat transfer between refrigerant in the inlet header tank and refrigerant in the outlet header tank is kept to a minimum, thereby improving the efficiency of the heat exchanger.
  • One set of flat tubes can be arranged between the inlet and outlet header tanks and the return header tank, each flat tube comprising at least two flow channels, wherein a first flow channel is in fluid connection with the inlet header tank and with the first chamber of the return header tank; and a second flow channel is in fluid connection with the second chamber of the return header tank and with the outlet header tank.
  • the flat tubes can e.g. be folded tubes formed from a metal sheet, wherein longitudinal edges of the sheet are folded inwards so as to separate the interior of the formed tube into two separate flow channels, such as e.g. B-tubes.
  • the flat tubes are extruded tubes.
  • Two sets of flat tubes can be arranged between the inlet and outlet header tanks and the return header tank, wherein a first set of flat tubes is in fluid connection with the inlet header tank and with the first chamber of the return header tank; and a second set of flat tubes is in fluid connection with the second chamber of the return header tank and with the outlet header tank.
  • Fig. 1 shows a heat exchanger 10 with face-U flow configuration comprising an inlet header tank 12, an outlet header tank 13 and a return header tank 14.
  • a plurality of flat tubes 16 are arranged between the inlet and outlet header tanks 12, 13 and the return header tank 14 for leading refrigerant from the inlet header tank 12 to the return header tank 14 and from there to the outlet header tank 13.
  • the ends of the flat tubes 16 are connected to the header tanks 12, 13, 14 through slots in the respective header tanks.
  • Corrugated fins 18 are arranged between individual flat tubes 16 in order to improve the heat transfer between the refrigerant in the flat tubes 16 and the air passing through the heat exchanger 10.
  • the inlet and outlet header tanks 12, 13 are formed by a single tube with a divider 28 therein for dividing the single tube into the inlet and outlet header tanks 12, 13.
  • the inlet header tank 12 comprises an inlet port 24 for receiving refrigerant from a refrigeration circuit (not shown) and the outlet header tank 13 comprises an outlet port 26 for returning refrigerant to the refrigeration circuit.
  • the return header tank 14 is divided into a first chamber 30 and a second chamber 32 by means of a partition wall 34.
  • Fig.2 is a section view through a heat exchanger according to a second embodiment of the invention.
  • Refrigerant from the refrigeration circuit enters the inlet header tank 12 via the inlet port 24.
  • the refrigerant is distributed over the whole length of the inlet header tank 12 and supplied to first flow channels 36 of the flat tubes 16, which lead the refrigerant to the return header tank 14.
  • the refrigerant passes from the first chamber 30 to the second chamber 32 through openings 38 arranged in the partition wall 34.
  • the second chamber 32 of the return header tank 14 the refrigerant is led to the outlet header tank 13 via second flow channels 36' of the flat tubes 16.
  • Each flat tube 16 comprises at least two separate flow channels 36, 36' therein, one for leading the refrigerant in one direction and one for leading the refrigerant in the opposite direction.
  • the flat tubes 16 can be extruded tubes or folded tubes such as e.g. B-tubes.
  • FIG.3 A perspective view of the return header tank 14 of Fig.2 is shown in Fig.3.
  • This return header tank 14 is formed from a folded sheet of metal, wherein one of the longitudinal edges of the sheet has been folded inwards to form the partition wall 34 within the folded header tank.
  • the partition wall 34 separates the interior of the folded header tank into the first chamber 30 and a second chamber 32.
  • a plurality of openings 38 is arranged in the partition wall 34. It will be appreciated that the openings 38 can very easily be arranged in the edge portion of the sheet of metal before folding.
  • Fig.3 also shows the slots 40 arranged in the wall of the return header tank 14 for receiving the flat tubes 16 therein.
  • the cross-section of the slots 40 corresponds to the cross-section of the flat tubes 16.
  • the inlet and outlet header tanks 12, 13 are connected to the return header tank via two sets of flat tubes 16, 16'.
  • the first set of flat tubes 16 leads the refrigerant in one direction out of the inlet header tank 12.
  • the second set of flat tubes 16' leads the refrigerant in the opposite direction, i.e. into the outlet header tank 13.
  • the heat exchanger shown in Figs 2 and 4 comprises separate inlet and outlet header tanks 12, 13.
  • the return header tank 14 is divided into first and second chambers 30, 32 by means of a partition wall 34 arranged therein.
  • the partition wall 34 comprises openings 38 to allow refrigerant to flow from the first chamber 30 into the second chamber 32.
  • the partition wall 34 of Fig.5 is configured as a separate element that can be inserted into the return header tank 14 and then secured therein.

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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)
EP03100286A 2003-02-11 2003-02-11 Wärmetauscher Withdrawn EP1447636A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03100286A EP1447636A1 (de) 2003-02-11 2003-02-11 Wärmetauscher

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03100286A EP1447636A1 (de) 2003-02-11 2003-02-11 Wärmetauscher

Publications (1)

Publication Number Publication Date
EP1447636A1 true EP1447636A1 (de) 2004-08-18

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ID=32669014

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03100286A Withdrawn EP1447636A1 (de) 2003-02-11 2003-02-11 Wärmetauscher

Country Status (1)

Country Link
EP (1) EP1447636A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005114066A1 (en) * 2004-04-28 2005-12-01 Modine Korea, Llc Header pipe of evaporator for automobile
DE102006018681A1 (de) * 2005-04-22 2006-10-26 Visteon Global Technologies, Inc., Van Buren Township Wärmetauscher für ein Fahrzeug
EP2144029A1 (de) * 2008-07-11 2010-01-13 Behr France Hambach S.A.R.L. Wärmeübertrager insbesondere eines Kraftfahrzeuges zum Kühlen eines Kältemittels und Verfahren zum Kühlen eines Kältemittels
CN103486774A (zh) * 2013-09-24 2014-01-01 浙江基力思汽车空调有限公司 一种卷压式集管平行流蒸发器
WO2014116351A1 (en) * 2013-01-28 2014-07-31 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
JP2016102628A (ja) * 2014-11-28 2016-06-02 株式会社ケーヒン・サーマル・テクノロジー 蒸発器
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0608439A1 (de) 1988-01-28 1994-08-03 Modine Manufacturing Company Verdampfer mit Kondensatansammlung
DE19826881A1 (de) * 1998-06-17 1999-12-23 Behr Gmbh & Co Wärmeübertrager, insbesondere Verdampfer
US6155340A (en) 1997-05-12 2000-12-05 Norsk Hydro Heat exchanger
US20020066553A1 (en) * 2000-11-07 2002-06-06 Ewald Fischer Heat exchanger and method for producing a heat exchanger
WO2002079708A2 (en) * 2001-03-29 2002-10-10 Showa Denko K.K. Header for use in heat exchangers, heat exchanger and method for manufacturing the same
WO2002103263A1 (en) * 2001-06-18 2002-12-27 Showa Dendo K.K. Evaporator, manufacturing method of the same, header for evaporator and refrigeration system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0608439A1 (de) 1988-01-28 1994-08-03 Modine Manufacturing Company Verdampfer mit Kondensatansammlung
US6155340A (en) 1997-05-12 2000-12-05 Norsk Hydro Heat exchanger
DE19826881A1 (de) * 1998-06-17 1999-12-23 Behr Gmbh & Co Wärmeübertrager, insbesondere Verdampfer
US20020066553A1 (en) * 2000-11-07 2002-06-06 Ewald Fischer Heat exchanger and method for producing a heat exchanger
WO2002079708A2 (en) * 2001-03-29 2002-10-10 Showa Denko K.K. Header for use in heat exchangers, heat exchanger and method for manufacturing the same
WO2002103263A1 (en) * 2001-06-18 2002-12-27 Showa Dendo K.K. Evaporator, manufacturing method of the same, header for evaporator and refrigeration system

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005114066A1 (en) * 2004-04-28 2005-12-01 Modine Korea, Llc Header pipe of evaporator for automobile
GB2429271A (en) * 2004-04-28 2007-02-21 Modine Korea Llc Header pipe of evaporator for automobile
GB2429271B (en) * 2004-04-28 2008-12-31 Modine Korea Llc Header pipe of evaporator for automobile
DE102006018681A1 (de) * 2005-04-22 2006-10-26 Visteon Global Technologies, Inc., Van Buren Township Wärmetauscher für ein Fahrzeug
EP2144029A1 (de) * 2008-07-11 2010-01-13 Behr France Hambach S.A.R.L. Wärmeübertrager insbesondere eines Kraftfahrzeuges zum Kühlen eines Kältemittels und Verfahren zum Kühlen eines Kältemittels
WO2014116351A1 (en) * 2013-01-28 2014-07-31 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
CN104937364A (zh) * 2013-01-28 2015-09-23 开利公司 具有歧管组件的多管束换热单元
CN104937364B (zh) * 2013-01-28 2019-03-08 开利公司 具有歧管组件的多管束换热单元
US10247481B2 (en) 2013-01-28 2019-04-02 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
CN103486774A (zh) * 2013-09-24 2014-01-01 浙江基力思汽车空调有限公司 一种卷压式集管平行流蒸发器
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
JP2016102628A (ja) * 2014-11-28 2016-06-02 株式会社ケーヒン・サーマル・テクノロジー 蒸発器

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