US20130043014A1 - Heat exchanger and vehicle air conditioner equipped with the same - Google Patents

Heat exchanger and vehicle air conditioner equipped with the same Download PDF

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Publication number
US20130043014A1
US20130043014A1 US13/695,106 US201113695106A US2013043014A1 US 20130043014 A1 US20130043014 A1 US 20130043014A1 US 201113695106 A US201113695106 A US 201113695106A US 2013043014 A1 US2013043014 A1 US 2013043014A1
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US
United States
Prior art keywords
flat tubes
heat exchanger
refrigerant
refrigerant circulation
flat
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.)
Abandoned
Application number
US13/695,106
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English (en)
Inventor
Koji Nakado
Yasunobu Joboji
Katsuhiro Saito
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JOBOJI, YASUNOBU, NAKADO, KOJI, SAITO, KATSUHIRO
Publication of US20130043014A1 publication Critical patent/US20130043014A1/en
Abandoned legal-status Critical Current

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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 heat exchanger and a vehicle air conditioner equipped with the same.
  • 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.
  • PTL 1 discloses a multiflow-type refrigerant condenser designed to obtain maximum heat radiation performance in consideration of both airflow resistance and tube pressure loss.
  • PTL 1 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 heat exchanger whose air pressure loss (airflow resistance) is small and whose exchanged heat is large, as well as a vehicle air conditioner equipped with the same.
  • the heat exchanger of the present invention and the vehicle air conditioner equipped with the same adopt the following solutions.
  • a heat exchanger comprises 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, wherein (W ⁇ t 1 ⁇ t 2 ) ⁇ Hp ⁇ Hf/N is set to 3.95 or greater and 10.0 or less, where de is the equivalent diameter of the plurality of the refrigerant circulation holes, W is the width of each of the flat tubes, t 1 is the wall thickness 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, t 2 is the wall thickness of each of the flat tubes at the other end in the widthwise direction corresponding to the distance from the refrigerant circulation le closest to the other end, Hp is the height of each of the flat tubes in the stacking direction, Hf is the height of the fins in the stacking direction, and N
  • 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.
  • a vehicle air conditioner according to a second aspect of the present invention is equipped with any one of the above heat exchangers.
  • the heat exchanger of the present invention is suitable for use as a condenser of a vehicle air conditioner.
  • a heat exchanger whose air pressure loss is small and whose exchanged heat is large, as well as a vehicle air conditioner equipped with the same, can be provided.
  • FIG. 1 is a front view of a condenser of a vehicle air conditioner according to an embodiment of the present invention.
  • FIG. 2 is a transverse cross-sectional view of a flat tube in FIG. 1 .
  • FIG. 3 is a front view of corrugated fins in FIG. 1 .
  • FIG. 4 is a graph showing the simulation results of the condenser shown in FIG. 1 plotted against a polynomial.
  • FIG. 5 is a graph showing the simulation results of the condenser shown in FIG. 1 plotted against an equivalent diameter.
  • 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 15 a and troughs 15 b 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/APa 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 is the fin pitch (see FIG. 3 ), and 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 .
  • 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:
  • fin pitch Pf 1.6 mm or more and 2.0 mm or less.
  • t 1 the wall thickness of each of the flat tubes 14 at one end in the widthwise direction corresponding to the distance from the refrigerant circulation hole 20 closest to the one end (the left end in FIG. 2 )
  • t 2 the wall thickness of each of the flat tubes 14 at the other end in the widthwise direction corresponding to the distance from the refrigerant circulation hole 20 closest to the other end (the right end in FIG. 3 )
  • Hp the height of each of the flat tubes 14 in the stacking direction (in the vertical direction)
  • Hf the height of the corrugated fins 15 in the stacking direction (in the vertical direction)
  • N the number of refrigerant circulation holes 20 .
  • the reason why the wall thickness at one end, t 1 , and the wall thickness at the other end, t 2 , are subtracted from the flat tube width N is that heat exchange is substantially not performed in the region of the thicknesses t 2 and t 2 .
  • 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 ⁇ t 1 ⁇ t 2 ) ⁇ Hp ⁇ Hf/N.
  • the figure shows cases where the flat tube width is 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. 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)
US13/695,106 2010-09-01 2011-08-17 Heat exchanger and vehicle air conditioner equipped with the same Abandoned US20130043014A1 (en)

Applications Claiming Priority (3)

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
JP2010-195658 2010-09-01
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

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11226161B2 (en) * 2017-12-21 2022-01-18 Hanon Systems Heat exchanger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US20050016716A1 (en) * 2003-04-30 2005-01-27 Valeo, Inc. Heat exchanger
US6880627B2 (en) * 1999-12-09 2005-04-19 Denso Corporation Refrigerant condenser used for automotive air conditioner
US20060016583A1 (en) * 2000-11-02 2006-01-26 Behr Gmbh & Co. Condenser and tube therefor
US7117936B2 (en) * 2002-07-09 2006-10-10 Valeo Thermal Systems Japan Corporation Tube for heat exchanger

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5572795A (en) * 1978-11-21 1980-05-31 Nippon Denso Co Ltd Corrugated fin type heat exchanger
JPS63243688A (ja) * 1986-11-04 1988-10-11 Showa Alum Corp 凝縮器
JPH02287094A (ja) * 1989-04-26 1990-11-27 Zexel Corp 熱交換器
JP3113100B2 (ja) * 1992-11-05 2000-11-27 株式会社デンソー 多穴管押出用ダイス及び多穴管
JP2001324290A (ja) * 1999-06-04 2001-11-22 Denso Corp 冷媒蒸発器
AU2002221036A1 (en) * 2000-11-24 2002-06-03 Showa Denko K K Heat exchanger tube and heat exchanger
KR100906769B1 (ko) * 2002-01-31 2009-07-10 한라공조주식회사 오뚜기형 유로를 갖는 열교환기용 튜브 및 이를 이용한열교환기
JP2006336873A (ja) * 2002-10-02 2006-12-14 Showa Denko Kk 熱交換器用チューブ及び熱交換器
JP3821113B2 (ja) * 2003-05-23 2006-09-13 株式会社デンソー 熱交換用チューブ
US6904963B2 (en) * 2003-06-25 2005-06-14 Valeo, Inc. Heat exchanger
JP3922288B2 (ja) * 2005-03-14 2007-05-30 株式会社デンソー 冷媒凝縮器
JP4898300B2 (ja) * 2006-05-30 2012-03-14 昭和電工株式会社 エバポレータ
JP5205095B2 (ja) * 2008-03-25 2013-06-05 昭和電工株式会社 オイルクーラ
CN101510533B (zh) * 2009-03-24 2011-06-15 赵耀华 新型微电子器件散热器
CN101515572B (zh) * 2009-03-24 2012-04-18 赵耀华 用于led及大功率散热器件的散热器
CN201434549Y (zh) * 2009-06-25 2010-03-31 大洋昭和汽车空调(大连)有限公司 奥迪b8平台车用冷凝器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US6880627B2 (en) * 1999-12-09 2005-04-19 Denso Corporation Refrigerant condenser used for automotive air conditioner
US20060016583A1 (en) * 2000-11-02 2006-01-26 Behr Gmbh & Co. Condenser and tube therefor
US7117936B2 (en) * 2002-07-09 2006-10-10 Valeo Thermal Systems Japan Corporation Tube for heat exchanger
US20050016716A1 (en) * 2003-04-30 2005-01-27 Valeo, Inc. Heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11226161B2 (en) * 2017-12-21 2022-01-18 Hanon Systems Heat exchanger

Also Published As

Publication number Publication date
EP2613116A1 (en) 2013-07-10
WO2012029542A1 (ja) 2012-03-08
EP2613116B1 (en) 2019-01-09
CN103038596A (zh) 2013-04-10
EP2613116A4 (en) 2015-01-14
JP5562769B2 (ja) 2014-07-30
JP2012052732A (ja) 2012-03-15
CN103038596B (zh) 2015-03-25

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