EP2402701A1 - Echangeur thermique - Google Patents

Echangeur thermique Download PDF

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Publication number
EP2402701A1
EP2402701A1 EP10745943A EP10745943A EP2402701A1 EP 2402701 A1 EP2402701 A1 EP 2402701A1 EP 10745943 A EP10745943 A EP 10745943A EP 10745943 A EP10745943 A EP 10745943A EP 2402701 A1 EP2402701 A1 EP 2402701A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
tank
block
heat exchanger
flows
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Withdrawn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
EP10745943A
Other languages
German (de)
English (en)
Other versions
EP2402701A4 (fr
Inventor
Katsuhiro Saito
Yasunobu Joboji
Koji Nakado
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
Original Assignee
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
Publication of EP2402701A1 publication Critical patent/EP2402701A1/fr
Publication of EP2402701A4 publication Critical patent/EP2402701A4/fr
Withdrawn legal-status Critical Current

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    • 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
    • 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
    • F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
    • 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
    • F28F9/0217—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions the partitions being separate elements attached to header boxes
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels

Definitions

  • the present invention relates to a heat exchanger, and more particularly to a heat exchanger suitably used in an evaporator in a refrigeration cycle for an air conditioner mounted in an automobile.
  • a known heat exchanger that constitutes an evaporator (or condenser) used in a refrigeration cycle includes a core in which a plurality of tubes and a plurality of fins alternately stacked, and a tank to which ends of the tubes are connected.
  • a refrigerant is introduced into the heat exchanger from an inlet header provided in the tank, passes through the tubes while performing heat exchange with air using heat transferred to the core, and then is discharged to the outside from an outlet header provided in the tank.
  • An evaporator mounted in an automobile is required to have high performance and also be small and lightweight as described later.
  • a circulation amount Gr [kg/s] of a refrigerant flowing in a refrigeration cycle during operation is generally the same throughout a refrigerant channel.
  • the circulation amount Gr of the refrigerant is the same throughout the refrigerant channel.
  • the refrigerant is gradually vaporized while performing heat exchange with air.
  • the refrigerant on a side closer to an outlet is gasified, has lower density, and has higher flow rate.
  • pressure loss of the refrigerant is relatively higher on the side closer to the outlet.
  • an evaporator used in an automobile generally has a multi-flow structure in which a refrigerant is distributed from one tank to a plurality of tubes, and thus distribution of the refrigerant (particularly, a liquid component that influences cooling performance) needs to be uniform. If the refrigerant distribution is non-uniform, a heat transmission area A of a part with a few liquid component is small (cannot be effectively used), thereby reducing performance Q.
  • FIG. 9 shows a heat exchanger 100 disclosed in Patent Document 1.
  • the heat exchanger 100 includes a group of tubes 105 in two or more rows constituted by a plurality of heat exchange tubes (hereinafter referred to as tubes) 104 between an refrigerant flow-in/out side tank 102 and a refrigerant turn-side tank 103.
  • An inside of a refrigerant inlet header chamber 106 in the refrigerant flow-in/out side tank 102 is partitioned into two spaces 106a and 106b in a height direction by a dividing resistance plate 107.
  • the tubes 104 are connected to the refrigerant flow-in/out side tank 102 so as to face the first space 106a.
  • One refrigerant passing hole 108 is formed in a middle in a length direction of the dividing resistance plate 107.
  • the refrigerant having flowed into the first space 106a of the refrigerant inlet header chamber 106 in the refrigerant flow-in/out side tank 102 flows through the refrigerant passing hole 108 into the second space 106b, flows through the tubes 104 into the refrigerant turn-side tank 103. Then, the refrigerant changes its flow direction and flows through the tubes 104 into a refrigerant outlet header chamber 109 in the refrigerant flow-in/out side tank 102.
  • the refrigerant is fed into the second space 106b of the refrigerant inlet header chamber 106 in the refrigerant flow-in/out side tank 102, flows through one refrigerant passing hole 108 in the dividing resistance plate 107 into the first space 106a, and is divided from the first space 106a into all the tubes 104 communicating with the refrigerant inlet header chamber 106. Since only one refrigerant passing hole 108 is formed in the dividing resistance plate 107, the refrigerant gradually flows from the second space 106b into the first space 106a, reaches the entire first space 106a, and flows into all the tubes 104.
  • a ratio between a gas component and a liquid component in a refrigerant in the heat exchange tubes connected to the refrigerant inlet header chamber in the refrigerant flow-in/out side tank, that is, refrigerant distribution is made uniform, thereby increasing heat exchange performance of the heat exchanger.
  • a refrigerant circuit includes two blocks (a first block on a refrigerant inlet side and a second block on a refrigerant outlet side).
  • the refrigerant is equally distributed to all the tubes, and the ratio between the gas component and the liquid component in each tube tends to be non-uniform. This tendency is particularly noticeable in the second block on the outlet side in which vaporization of the refrigerant proceeds to increase the ratio of the gas component.
  • a dividing auxiliary resistance plate 110 that vertically partitions the refrigerant outlet header chamber 109 is provided.
  • the refrigerant circuit includes the two blocks in order to reduce pressure loss, but the dividing auxiliary resistance plate 110 is provided in the refrigerant outlet header chamber 109 in which most of the refrigerant is gasified for uniform refrigerant distribution.
  • pressure loss is eventually increased, and a sufficient effect of reducing pressure loss cannot be obtained in terms of increasing performance Q.
  • the present invention is achieved in view of such technical problems, and has an object to provide a heat exchanger that reduces pressure loss and can provide uniform refrigerant distribution in a second block.
  • a heat exchanger of the present invention is configured so that a refrigerant successively passes through a first block and a second block and flows out of the second block.
  • the first block includes a first tank having a refrigerant inlet through which the refrigerant flows in, a plurality of first tubes into which the refrigerant having flowed into the first tank is distributed and flows therein, and a second tank in which the refrigerant flowing in the first tubes merges.
  • the second block includes a third tank into which the refrigerant having merged in the second tank flows, a plurality of second tubes into which the refrigerant having flowed into the third tank is distributed and flows therein, and a fourth tank in which the refrigerant flowing in the second tube merges, and having a refrigerant outlet through which the merged refrigerant flows out.
  • a refrigerant passage through which the refrigerant flows from the second tank into the third tank is locally placed on the side opposite to the refrigerant inlet.
  • non-uniform refrigerant distribution that occurs in the first block is eliminated in the second block in such a manner that the refrigerant passage through which the refrigerant flows from the second tank into the third tank, that is, from the first block into the second block is locally placed on the side opposite to the refrigerant inlet (hereinafter referred to as a counter-inlet side).
  • a counter-inlet side the side opposite to the refrigerant inlet
  • the first block and the second block are placed in parallel with each other, the first tank and the fourth tank are placed on a vertically upper side, and the second tank and the third tank are placed on a vertically lower side.
  • the refrigerant is guided vertically downward from the first tank to the second tank, and the refrigerant is guided vertically upward from the third tank to the fourth tank.
  • the refrigerant flows from the second tank toward the third tank on the lower side, that is, from the counter-inlet side toward an inlet side, thereby enabling a liquid component to easily flow to an inlet side of the third tank, and providing uniform distribution of a gas component and the liquid component in the second block (second tubes).
  • the refrigerant passage through which the refrigerant flows from the second tank into the third tank is formed by providing a plurality of holes in a partition member provided between the second tank and the third tank. This can facilitate mixing of the gas component and the liquid component, and improve uniformity of refrigerant distribution in the second block (second tubes).
  • the third tank includes at least one resistor against the refrigerant therein, and the resistor is placed on a rear side of the refrigerant passage in a flow direction of the refrigerant.
  • a distribution amount of the liquid component in the refrigerant flowing in the third tank is particularly made uniform in the third tank.
  • the liquid component is under vaporization, and pressure loss can be reduced even with the resistor in the third tank.
  • the third tank may include a plurality of resistors.
  • the third tank includes a first resistor, and a second resistor placed on a rear side of the first resistor in the flow direction of the refrigerant, and an opening rate of the second resistor is equal to or lower than an opening rate of the first resistor. This is because gradually reducing a liquid component amount toward the refrigerant inlet side is preferable in more uniformly distributing the gas component and the liquid component.
  • a refrigerant channel area in the fourth tank that constitutes the second block is larger than a refrigerant channel area in the first tank that constitutes the first block.
  • a refrigerant channel area in the third tank that constitutes the second block is larger than a refrigerant channel area in the second tank that constitutes the first block.
  • a refrigerant channel area of the second tube that constitutes the second block is larger than a refrigerant channel area of the first tube that constitutes the first block.
  • non-uniform refrigerant distribution that occurs in the first block is eliminated in such a manner that the refrigerant passage through which the refrigerant flows from the second tank into the third tank, that is, from the first block into the second block is locally placed on the counter-inlet side.
  • refrigerant distribution in the second block is made uniform to improve heat exchange performance of the heat exchanger.
  • a heat exchanger 10 according to this embodiment is suitably used in an evaporator in a refrigeration cycle for an air conditioner mounted in an automobile.
  • the heat exchanger 10 includes a core 20 in which a plurality of first tubes 21 and second tubes 22 through which a refrigerant flows, and a plurality of fins 23 are alternately stacked, an upper tank 30 to which one end (upper end in the drawings) of each of the first tubes 21 and the second tubes 22 is connected, and a lower tank 40 to which the other end (lower end in the drawings) of each of the first tubes 21 and the second tubes 22 is connected.
  • the heat exchanger 10 performs heat exchange of the refrigerant using heat transferred to the core 20.
  • the first tubes 21 and the second tubes 22 are made of copper, a copper alloy, aluminum, or an aluminum alloy, and are members produced by extrusion molding or roll molding of a plate material and having a hollow portion and a rectangular section.
  • the first tubes 21 and the second tubes 22 are arranged in two rows in a width direction (Y direction in FIG. 2 ).
  • the upper ends of the first tubes 21 and the second tubes 22 are connected to the upper tank 30, and the lower ends of the first tubes 21 and the second tubes 22 are connected to the lower tank 40.
  • the upper tank 30, the first tubes 21, the second tubes 22, and the lower tank 40 are communicated with each other to allow passage of the refrigerant. This connection is generally performed by blazing.
  • the sectional shape of the first tube(s) 21 and the second tube(s) 22 is not limited to the rectangular shape, but may be a circular shape or other shapes.
  • the fin 23 is made of the same material as that of the first tube 21 and the second tube 22.
  • a corrugated fin molded by roll molding is used, but not limited to this, a plate fin may be used.
  • the first and second tubes 21, 22, and the fins 23 are alternately stacked in a longitudinal direction (X direction in FIG. 2 ) of the heat exchanger 10, and the both ends are sealed by side plates 24.
  • the side plate 24 functions as a reinforcing member of the core 20, and the both ends in a longitudinal direction thereof are supported by the upper tank 30 and the lower tank 40.
  • the upper tank 30 mainly includes a tank plate 31 and an end plate 32, and is assembled so that openings of the plates face each other.
  • an upper partition plate 33 is provided along a longitudinal direction.
  • the upper partition plate 33 partitions an inside of the upper tank 30 at a middle in a width direction.
  • One of partitioned sides constitutes a first tank T1, and the other constitutes a fourth tank T4.
  • the first tube 21 is connected to a lower surface of the first tank T1
  • the second tube 22 is connected to a lower surface of the fourth tank T4. Since the upper partition plate 33 is provided between the first tank T1 and the fourth tank T4, the refrigerant is not directly moved between the tanks T1 and T4.
  • a cap 34 is provided on one end side in the longitudinal direction of the upper tank 30.
  • the cap 34 has a refrigerant inflow hole h in and a refrigerant outflow hole h ex .
  • a cap 35 is provided on the other end side in the longitudinal direction of the upper tank 30. The cap 35 seals the other end in the longitudinal direction of the upper tank 30.
  • the lower tank 40 mainly includes a tank plate 41 and an end plate 42, and is assembled so that openings of the plates face each other.
  • a lower partition plate 43 is provided along a longitudinal direction.
  • the lower partition plate 43 partitions an inside of the lower tank 40 at a middle in a width direction.
  • One of partitioned sides constitutes a second tank T2, and the other constitutes a third tank T3.
  • the first tube 21 is connected to an upper surface of the second tank T2, and the second tube 22 is connected to an upper surface of the third tank T3.
  • the lower partition plate 43 has refrigerant passages 43h passing therethrough in a thickness direction.
  • the plurality of (seven in this example) refrigerant passages 43h are locally provided on one end side in a longitudinal direction of the lower partition plate 43.
  • the refrigerant passages 43h are placed on the opposite side of the refrigerant inflow hole h in that is a refrigerant inlet in the longitudinal direction of the heat exchanger 10.
  • the lower partition plate 43 is provided between the second tank T2 and the third tank T3, but the refrigerant flows from the second tank T2 into the third tank T3 through the plurality of refrigerant passages 43h locally placed on the opposite side of the refrigerant inlet (hereinafter referred to as a counter-inlet side).
  • the refrigerant passages 43h are preferably provided within a range of 20% or less of the entire length of the lower partition plate 43. Increasing a flow rate of the refrigerant having passed through the refrigerant passages 43h is effective for uniformly mixing the gas component and the liquid component in the refrigerant.
  • the refrigerant passages 43h are constituted by a plurality of circular holes, but may be one or more wide refrigerant passages having a longer diameter in the longitudinal direction of the lower partition plate 43. However, in order to uniformly mix the gas component and the liquid component, it is preferable to provide the plurality of refrigerant passages 43h having a small diameter as in this embodiment.
  • distribution adjusting plates (resistors) 46, 47 and 48 are provided in the third tank T3.
  • the distribution adjusting plates 46, 47 and 48 are placed in this order from the counter-inlet side at a predetermined interval.
  • the distribution adjusting plates 46, 47 and 48 have through holes 46h, 47h and 48h, respectively, through which the refrigerant passes.
  • the refrigerant having flowed through the refrigerant passages 43h into the third tank T3 successively passes through the through holes 46h, 47h and 48h and flows downward with the distribution adjusting plates 46, 47 and 48 as the resistors.
  • the distribution adjusting plates 46, 47 and 48 in the third tank T3 Without the distribution adjusting plates 46, 47 and 48 in the third tank T3, the liquid component in the refrigerant tends to flow to a downstream side, and the gas component tends to stay in an upstream side. When the liquid component is uneven in the longitudinal direction to provide non-uniform refrigerant distribution, sufficient vaporization performance cannot be obtained.
  • the distribution adjusting plates 46, 47 and 48 are particularly used as the resistors for the liquid component, and thus the liquid component and the gas component in the refrigerant are distributed as equally as possible over upstream and downstream regions of the third tank T3.
  • the distribution adjusting plates 46, 47 and 48 function as the resistors and thus cause pressure loss of the refrigerant.
  • the distribution adjusting plates 46, 47 and 48 are provided in the third tank T3 in which most of the liquid component is under vaporization, and thus the pressure loss can be minimized.
  • the three distribution adjusting plates 46, 47 and 48 are provided, but one distribution adjusting plate may be provided.
  • the distribution adjusting plate 46 (first distribution adjusting plate from an upstream end, "first resistor") provided for the above-described purpose is preferably provided in a position relatively close to the upstream end of the third tank T3. As a specific index, the distribution adjusting plate 46 is provided within a range of 30% or less of the entire length of the lower partition plate 43 from the upstream end.
  • An opening rate of the through holes 46h, 47h and 48h provided in the distribution adjusting plates 46, 47 and 48 is preferably within a range of 15% to 30%. This is because the liquid component and the gas component can be equally distributed over the upstream and downstream regions without increasing pressure loss of the refrigerant more than necessary.
  • the opening rate herein refers to a ratio of each of the through holes 46h, 47h and 48h to an area (sectional area) of a refrigerant channel in the third tank T3.
  • opening rates of through holes 47h and 48h in the second and thereafter distribution adjusting plate 47 (second resistor) and distribution adjusting plate 48 (second resistor) from an upstream end are preferably equal to or lower than opening rates of through holes 47h and 48h on an adjacent upstream side. This is because the opening rate is reduced in a position closer to the downstream side to retain, on the upstream side, the liquid component that tends to flow to the downstream side.
  • a cap 44 is provided on one end side in the longitudinal direction of the lower tank 40.
  • the cap 44 seals one end side in the longitudinal direction of the lower tank 40.
  • a cap 45 is provided on the other end side in the longitudinal direction of the lower tank 40. The cap 45 seals the other end side in the longitudinal direction of the lower tank 40.
  • the refrigerant channel is constituted by the first block and the second block, and the refrigerant flows in the heat exchanger 10 in order of the first block and the second block.
  • the first block includes the first tank T1, the first tube 21, and the second tank T2, and the second block includes the third tank T3, the second tube 22, and the fourth tank T4.
  • the refrigerant having brought into a gas-liquid two-phase state by an expansion valve placed on the upstream side with respect to the heat exchanger 10 flows through the refrigerant inflow hole h in (refrigerant inlet) into the first tank T1.
  • the refrigerant having flowed into the first tank T1 flows vertically downward in the first tube 21 and reaches the second tank T2. During flowing in the first tube 21, the refrigerant is subjected to heat exchange with air passing through the core 20 with the liquid component being vaporized.
  • the ratio between the gas component and the liquid component varies in the longitudinal direction of the heat exchanger 10. This is schematically shown in FIG. 7A .
  • the ratio of the liquid component in the refrigerant is shown by arrows.
  • the ratio of the liquid component is higher in the first tube 21 on the side closer to the refrigerant inlet. Since the liquid component has higher resistance to an inner wall of the first tank T1 than the gas component, the liquid component is hard to flow in a position farther from the refrigerant inlet.
  • the refrigerant having flowed into the second tank T2 flows through the refrigerant passage 43h into the third tank T3. Since the refrigerant passages 43h are locally provided on the counter-inlet side of the lower partition plate 43, the refrigerant having flowed in the first tube 21 in a position closer to the counter-inlet side among the first tubes 21 first flows through the refrigerant passages 43h into the third tank T3.
  • the refrigerant having flowed into the third tank T3 flows vertically upward in the second tube 22 and reaches the fourth tank T4.
  • the refrigerant is subjected to heat exchange with air passing through the core 20 while the liquid component is vaporized.
  • the refrigerant with the liquid component being vaporized during flowing through the heat exchanger 10 flows through the fourth tank T4, and is discharged from the refrigerant flow-out hole h ex toward a compressor placed on the downstream side.
  • the ratio of the liquid component of the refrigerant flowing vertically upward in the second tube 22 (second block) is higher in the second tube 22 on the side closer to the refrigerant inlet as shown in FIG. 7B because the state of the first tube 21 (first block) is taken over. This state is shown by dash-single-dot lines in FIG. 5B .
  • the refrigerant passages 43h are locally provided on the counter-inlet side of the lower partition plate 43, and thus the refrigerant having flowed in the first tube 21 in the position closer to the counter-inlet side among the first tubes 21 first flows through the refrigerant passages 43h into the third tank T3.
  • the second block as shown by solid lines in FIG. 5B , non-uniform distribution of the gas component and the liquid component in the longitudinal direction that has occurred in the first block ( FIGS. 5A and 7A ) is eliminated.
  • the dash-single-dot lines in FIG. 5B indicate the ratio of the liquid component when the refrigerant passages 43h are formed over the entire region in the longitudinal direction of the third tank T3.
  • the position and shape of the upper partition plate 33 may be adjusted so that the refrigerant channel area of the fourth tank T4 is larger than the refrigerant channel area of the first tank T1.
  • the position and shape of the lower partition plate 43 may be adjusted so that the refrigerant channel area of the third tank T3 is larger than the refrigerant channel area of the second tank T2. This can reduce pressure loss in the third tank T3 and the fourth tank T4 in which the ratio of the gas component is higher than in the first tank T1 and the second tank T2 without changing the external size of the heat exchanger 10. Further, as shown in FIG.
  • a width (refrigerant channel area) of the second tube 22 that constitutes the second block may be larger than a width (refrigerant channel area) of the first tube 21 that constitutes the first block. This can reduce pressure loss of the refrigerant in the second block in which the ratio of the gas component is higher than in the first block without changing the external size of the heat exchanger 10.
EP10745943A 2009-02-26 2010-02-22 Echangeur thermique Withdrawn EP2402701A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009044726A JP2010197008A (ja) 2009-02-26 2009-02-26 熱交換器
PCT/JP2010/001125 WO2010098056A1 (fr) 2009-02-26 2010-02-22 Echangeur thermique

Publications (2)

Publication Number Publication Date
EP2402701A1 true EP2402701A1 (fr) 2012-01-04
EP2402701A4 EP2402701A4 (fr) 2013-01-16

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EP10745943A Withdrawn EP2402701A4 (fr) 2009-02-26 2010-02-22 Echangeur thermique

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US (1) US20110220336A1 (fr)
EP (1) EP2402701A4 (fr)
JP (1) JP2010197008A (fr)
WO (1) WO2010098056A1 (fr)

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WO2019219076A1 (fr) * 2018-05-17 2019-11-21 杭州三花研究院有限公司 Échangeur de chaleur

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JP5829055B2 (ja) * 2011-06-03 2015-12-09 サンデンホールディングス株式会社 熱交換器
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KR101462176B1 (ko) * 2013-07-16 2014-11-21 삼성전자주식회사 열교환기
KR20150133035A (ko) * 2014-05-19 2015-11-27 한온시스템 주식회사 실외열교환기
DE112020000923T5 (de) * 2019-02-25 2021-11-04 Hanon Systems Wärmetauscher und fahrzeug-klimaanlage
WO2020245836A1 (fr) * 2019-06-04 2020-12-10 Pranav Vikas India Pvt. Limited Ensemble faisceau de chauffage ccf

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CN108253665A (zh) * 2016-12-28 2018-07-06 株式会社京滨冷暖科技 蒸发器
CN108253665B (zh) * 2016-12-28 2020-08-11 株式会社京滨冷暖科技 蒸发器
WO2019219076A1 (fr) * 2018-05-17 2019-11-21 杭州三花研究院有限公司 Échangeur de chaleur
EP3745069A4 (fr) * 2018-05-17 2021-09-15 Zhejiang Sanhua Intelligent Controls Co., Ltd. Échangeur de chaleur
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WO2010098056A1 (fr) 2010-09-02
US20110220336A1 (en) 2011-09-15
EP2402701A4 (fr) 2013-01-16

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