EP2613116B1 - Method for determining a configuration of a heat exchanger - Google Patents

Method for determining a configuration of a heat exchanger Download PDF

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Publication number
EP2613116B1
EP2613116B1 EP11821559.9A EP11821559A EP2613116B1 EP 2613116 B1 EP2613116 B1 EP 2613116B1 EP 11821559 A EP11821559 A EP 11821559A EP 2613116 B1 EP2613116 B1 EP 2613116B1
Authority
EP
European Patent Office
Prior art keywords
flat tubes
refrigerant
refrigerant circulation
flat
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.)
Not-in-force
Application number
EP11821559.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2613116A1 (en
EP2613116A4 (en
Inventor
Koji Nakado
Yasunobu Joboji
Katsuhiro Saito
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.)
Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2613116A1 publication Critical patent/EP2613116A1/en
Publication of EP2613116A4 publication Critical patent/EP2613116A4/en
Application granted granted Critical
Publication of EP2613116B1 publication Critical patent/EP2613116B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • 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 method for determining a configuration of a heat exchanger.
  • a vehicle air conditioner is provided with a condenser (heat exchanger) that condenses refrigerant by exchanging heat with air.
  • a condenser of a typical multiflow type that is frequently used is configured such that flat tubes and corrugated fins are alternately stacked.
  • the flat tubes have a plurality of refrigerant circulation holes therein, and the protrusions of the corrugated fins are fixed to the flat surfaces of the flat tubes to allow air to pass over the surfaces of the corrugated fins.
  • Conceivable ways to improve the performance of this type of condenser include reducing the fin pitch and reducing the size of refrigerant circulation holes formed in the flat tubes.
  • JP3922288B discloses a multiflow-type refrigerant condenser designed to obtain maximum heat radiation performance in consideration of both airflow resistance and tube pressure loss.
  • Prior art US 2004/0261983 A1 and US 2001/0004935 A1 disclose methods for determining a configuration of a heat exchanger comprising flat tubes with refrigerant circulation holes, and fins fixed to said flat tubes, wherein the fins and the flat tubes are alternately stacked to form said heat exchanger.
  • JP3922288B does not consider the size of the refrigerant condenser in the airflow direction (in the widthwise direction of the tubes) at all. That is, it does not rigorously examine changes in state quantity (for example, airflow resistance and heat exchange in the airflow direction) due to air passing through the fins. Accordingly, the performance of a heat exchanger that depends on the airflow resistance cannot be rigorously evaluated using the specifications of the refrigerant condenser configuration described in the literature.
  • the present invention is made in consideration of such circumstances, and an object thereof is to provide a method for determining a configuration of a heat exchanger whose air pressure loss (airflow resistance) is small and whose exchanged heat is large.
  • a method for determining a configuration of a heat exchanger comprising flat tubes, each having therein a plurality of refrigerant circulation holes, and fins fixed to the flat surfaces of the flat tubes, on the surfaces of which air passes, wherein the flat tubes and the fins are alternately stacked to form the heat exchanger, the method comprising setting variables in a polynomial defined by (W - t1 - t2) ⁇ Hp ⁇ Hf / N so that the result is greater than or equal to 3.95 and less than or equal to 10.0, where de is the equivalent diameter of the plurality of the refrigerant circulation holes in mm, which means the diameter when the plurality of the refrigerant holes are converted to a single equivalent cylinder, W is the width of each of the flat tubes in mm, t1 is the wall thickness in mm of each of the flat tubes at one end in the widthwise direction corresponding to the distance from the refrigerant circulation hole closest to the one end, t2 is the wall thickness in mm of each of the
  • the polynomial using the flat tube width W was used to evaluate the heat exchange performance of the heat exchanger. This allows also state changes due to air passing through the fins (for example, airflow resistance and heat exchange in the airflow direction) to be considered, thus allowing the heat exchange performance to be reflected more rigorously.
  • the configuration of the heat exchanger is determined in consideration of not only the configuration of the flat tubes, such as the flat tube width W and the flat tube height Hp, but also the fin height Hf. This allows the air pressure loss to be considered more rigorously.
  • Dividing the polynomial by the number of refrigerant circulation holes, N, allows evaluation of the performance per refrigerant circulation hole.
  • the flat tubes are manufactured by extrusion.
  • the equivalent diameter de is set to 0.55 or more and 0.76 or less.
  • the fins have a corrugated shape whose pitch is set to 1.6 mm or more and 2.0 mm or less.
  • the heat exchanger configured according to the method of the present invention is suitable for use as a condenser of a vehicle air conditioner.
  • a method for determining the configuration of a heat exchanger whose air pressure loss is small and whose exchanged heat is large can be provided.
  • Fig. 1 shows a front view of a condenser (heat exchanger) 1 according to this embodiment.
  • the condenser 1 cools a high-temperature, high-pressure superheated gas refrigerant discharged from a compressor (not shown) in a refrigeration cycle of a vehicle air conditioner to condense it.
  • the condenser 1 is disposed in the frontmost part in a vehicle engine compartment as a component of a condenser-radiator fan module (CRFM).
  • An engine cooling radiator (not shown) and a cooling fan (not shown) are disposed in sequence behind the condenser 1.
  • the condenser 1 is cooled by cooling air (outside air) blown by the cooling fan.
  • the condenser 1 includes a first header tank 11 and second header tank 12 pair disposed with a certain distance therebetween.
  • the header tanks 11 and 12 are cylindrical in shape and are disposed with the longitudinal direction thereof oriented in the substantially vertical direction.
  • a core portion 13 that performs heat exchange between air and the refrigerant is disposed between the header tanks 11 and 12.
  • the condenser 1 is of a multiflow type in which refrigerant flows through a plurality of parallel channels provided between the header tanks 11 and 12.
  • the core portion 13 is equipped with flat tubes 14 extending horizontally between the header tanks 11 and 12 and corrugated fins 15 fixed to the flat surfaces of the flat tubes 14.
  • the flat tubes 14 and the corrugated fins 15 are alternately stacked in the vertical direction to form the core portion 13.
  • Fig. 2 shows a transverse cross-section of the flat tubes 14.
  • each flat tube 14 has therein a plurality of independent refrigerant circulation holes 20 formed in the longitudinal direction.
  • the flat tubes 14 having the plurality of refrigerant circulation holes 20 can be manufactured by extruding a material made of an aluminum alloy.
  • the flat tubes 14 are connected to the first header tank 11 at one end in the longitudinal direction and are connected to the second header tank 12 at the other end.
  • the refrigerant circulates between the header tanks 11 and 12 through the plurality of refrigerant circulation holes 20.
  • Fig. 3 shows a front view of the corrugated fins 15.
  • the corrugated fins 15 have a corrugated shape.
  • the corrugated fins 15 can be manufactured by pressing a plate material made of an aluminum alloy.
  • the peaks 15a and troughs 15b of the corrugated fins 15 are joined to the flat surfaces of the flat tubes 14 by brazing. Air flows over the surfaces of the corrugated fins 15 to accelerate heat exchange between the air and the refrigerant.
  • the height of the corrugated fins 15 is Hf, and the fin pitch is Pf.
  • the interior of the first header tank 11 is separated into two chambers 17 and 18 by a separator 16, and the gas refrigerant coming from the compressor is introduced into the upper first chamber 17.
  • the gas refrigerant flows into the second header tank 12 via the upper flat tubes 14 communicating with the first chamber 17, makes a U-turn in the second header tank 12, and thereafter flows into the lower second chamber 18 via the remaining lower flat tubes 14.
  • the gas refrigerant is cooled and condensed by exchanging heat with air passing through the space between the flat tubes 14, so that the refrigerant becomes a gas-liquid two-phase flow in the refrigerant circulation holes 20 of the flat tubes 14 as the refrigerant condenses.
  • this embodiment adopts Q/Fa/ ⁇ Pa corresponding to exchanged heat Q [W] relative to frontal surface area Fa [m 2 ] and air pressure loss ⁇ Pa [Pa]. Adopting this heat exchange performance index allows the pressure loss of air passing through the condenser 1 (specifically, the corrugated fins 15) to be taken into account. That is, the larger the exchanged heat Q and the smaller the air pressure loss ⁇ Pa are, the larger the value the index takes.
  • Pf the fin pitch (see Fig. 3 )
  • A, B, C, and D are constants.
  • the simulation also considers the pressure loss of the refrigerant flowing in the refrigerant passage holes 20 of the flat tubes 14. Specifically, the refrigerant pressure loss is calculated from the tube friction coefficient of the refrigerant circulation holes 20, the physical properties of the gas refrigerant and the liquid refrigerant, and so on. If the refrigerant pressure loss is large, the change in state quantity in a p (pressure) - h (enthalpy) chart of the refrigerant during heat exchange (while the refrigerant is condensed) shifts downward to the left from an ideal horizontal line (that is, the pressure and the temperature are constant), and the average temperature CTm of the refrigerant during condensation decreases.
  • the decrease in average temperature CTm will decrease the exchanged heat Q, which is proportional to the difference between the average temperature CTm and the air temperature Tai (CTm - Tai). Accordingly, the smaller the refrigerant pressure loss is, the larger the exchanged heat Q becomes, and thus, the larger the value the foregoing heat exchange performance index will take.
  • the simulation adopts the following conditions:
  • the expression is divided by the number of refrigerant circulation holes, N, to evaluate the performance of the individual refrigerant circulation holes 20.
  • Fig. 4 shows the simulation results.
  • the vertical axis indicates the heat exchange performance index Q/Fa/ ⁇ Pa described above
  • the horizontal axis indicates the polynomial (W - t1 - t2) ⁇ Hp ⁇ Hf / N.
  • the figure shows cases where the flat tube width is 12 mm, 14 mm, 15 mm, and 16 mm. As can be seen from the figure, the maximum points of all the curves are contained in the region where the polynomial is 3.95 or greater and 10 or less. Accordingly, setting the polynomial to 3.95 or greater and 10 or less allows a high-performance condenser 1 to be provided.
  • the polynomial of this embodiment was calculated for the condenser specified in PTL 1.
  • Fig. 5 shows the simulation results.
  • the vertical axis indicates the heat exchange performance index Q/Fa/ ⁇ Pa described above
  • the horizontal axis indicates the equivalent diameter de of the plurality of refrigerant circulation holes 20 formed in each of the flat tubes 14.
  • the equivalent diameter de means the diameter when the plurality of refrigerant circulation holes 20 formed in a single flat tube 14 is converted to a single equivalent cylinder.
  • the figure shows cases where the flat tube width is 12 mm, 14 mm, 15 mm, and 16 mm.
  • the maximum points of all the curves are contained in the range where the equivalent diameter de is 0.5 or more and 0.8 or less, preferably, 0.55 or more and 0.76 or less. Accordingly, setting the equivalent diameter de as described above allows a high-performance condenser 1 to be provided.
  • This embodiment provides the following operational advantages.
  • the polynomial using the flat tube width W is used. This allows also state changes due to air passing through the corrugated fins 15 (for example, airflow resistance and heat exchange in the airflow direction) to be considered, thus allowing the heat exchange performance to be reflected more rigorously.
  • the configuration of the heat exchanger is determined in consideration of not only the configuration of the flat tubes, such as the flat tube width W and the flat tube height Hp, but also the fin height Hf. This allows the air pressure loss to be considered more rigorously.
  • Dividing the polynomial by the number of refrigerant circulation holes, N, allows evaluation of the performance per refrigerant circulation hole.
  • the performance is evaluated using the exchanged heat Q relative to the frontal surface area Fa and the air pressure loss ⁇ Pa as a heat exchange performance index and using the foregoing polynomial.
  • the air pressure loss is sufficiently considered. This allows evaluation of the performance in a state close to the actual operating state.

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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)
  • Air-Conditioning For Vehicles (AREA)
EP11821559.9A 2010-09-01 2011-08-17 Method for determining a configuration of a heat exchanger Not-in-force EP2613116B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010195658A JP5562769B2 (ja) 2010-09-01 2010-09-01 熱交換器およびこれを備えた車両用空調装置
PCT/JP2011/068610 WO2012029542A1 (ja) 2010-09-01 2011-08-17 熱交換器およびこれを備えた車両用空調装置

Publications (3)

Publication Number Publication Date
EP2613116A1 EP2613116A1 (en) 2013-07-10
EP2613116A4 EP2613116A4 (en) 2015-01-14
EP2613116B1 true EP2613116B1 (en) 2019-01-09

Family

ID=45772646

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11821559.9A Not-in-force EP2613116B1 (en) 2010-09-01 2011-08-17 Method for determining a configuration of a heat exchanger

Country Status (5)

Country Link
US (1) US20130043014A1 (ja)
EP (1) EP2613116B1 (ja)
JP (1) JP5562769B2 (ja)
CN (1) CN103038596B (ja)
WO (1) WO2012029542A1 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102400223B1 (ko) * 2017-12-21 2022-05-23 한온시스템 주식회사 열교환기
CN111692894B (zh) * 2019-12-30 2021-11-16 浙江三花智能控制股份有限公司 微通道扁管及微通道换热器
EP3786565B1 (en) 2019-05-05 2022-08-31 Hangzhou Sanhua Research Institute Co., Ltd. Microchannel flat tube and microchannel heat exchanger

Citations (1)

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Publication number Priority date Publication date Assignee Title
US20040261983A1 (en) * 2003-06-25 2004-12-30 Zaiqian Hu Heat exchanger

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Also Published As

Publication number Publication date
US20130043014A1 (en) 2013-02-21
EP2613116A1 (en) 2013-07-10
JP5562769B2 (ja) 2014-07-30
EP2613116A4 (en) 2015-01-14
JP2012052732A (ja) 2012-03-15
CN103038596B (zh) 2015-03-25
WO2012029542A1 (ja) 2012-03-08
CN103038596A (zh) 2013-04-10

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