US20120305228A1 - Condenser - Google Patents

Condenser Download PDF

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Publication number
US20120305228A1
US20120305228A1 US13/480,948 US201213480948A US2012305228A1 US 20120305228 A1 US20120305228 A1 US 20120305228A1 US 201213480948 A US201213480948 A US 201213480948A US 2012305228 A1 US2012305228 A1 US 2012305228A1
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United States
Prior art keywords
heat exchange
header tank
refrigerant
exchange tubes
header
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
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US13/480,948
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English (en)
Inventor
Kouta Arino
Kazumi Tokizaki
Tatsuya Hanafusa
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.)
Mahle Behr Thermal Systems Japan Ltd
Original Assignee
Keihin Thermal Technology Corp
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Filing date
Publication date
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Assigned to KEIHIN THERMAL TECHNOLOGY CORPORATION reassignment KEIHIN THERMAL TECHNOLOGY CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ARINO, KOUTA, HANAFUSA, TATSUYA, TOKIZAKI, KAZUMI
Publication of US20120305228A1 publication Critical patent/US20120305228A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • F28F9/268—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators by permanent joints, e.g. by welding
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0442—Condensers with an integrated receiver characterised by the mechanical fixation of the receiver to the header
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0444—Condensers with an integrated receiver where the flow of refrigerant through the condenser receiver is split into two or more flows, each flow following a different path through the condenser receiver
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0446—Condensers with an integrated receiver characterised by the refrigerant tubes connecting the header of the condenser to the receiver; Inlet or outlet connections to receiver
    • 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 condenser suitable for use in, for example, a car air conditioner mounted on an automobile.
  • FIGS. 1 and 2 will be referred to as “upper,” “lower,” “left,” and “right,” respectively.
  • a condenser for a car air conditioner is known (see Japanese Patent Application Laid-Open (kokai) No. 2001-33121).
  • the known condenser has a condensation part and a super-cooling part provided such that the former is located above the latter.
  • the condenser includes a plurality of heat exchange tubes disposed in parallel such that their length direction coincides with the left-right direction and they are spaced apart from one another in the vertical direction; fins each disposed between adjacent heat exchange tubes; and header tanks which are disposed such that their length direction coincides with the vertical direction and to which left and right end portions of the heat exchange tubes are connected, respectively. All the heat exchange tubes have the same length.
  • One heat exchange path formed by a plurality of heat exchange tubes successively arranged in the vertical direction is provided in each of the condensation part and the super-cooling part.
  • the heat exchange path provided in the condensation part serves as a refrigerant condensation path for condensing refrigerant
  • the heat exchange path provided in the super-cooling part serves as a refrigerant super-cooling path for super-cooling the refrigerant.
  • the two header tanks, to which all the heat exchange tubes are connected, are provided at the left and right ends of the condenser such that one header tank is provided at each of the left and right ends of the condenser.
  • each of the two header tanks is divided into upper and lower header sections by a partition provided at a vertical position between the refrigerant condensation path and the refrigerant super-cooling path.
  • Left and right end portions of the heat exchange tubes of the refrigerant condensation path are connected to the upper header sections of the two header tanks, and left and right end portions of the heat exchange tubes of the refrigerant super-cooling path are connected to the lower header sections of the two header tanks.
  • a refrigerant inlet is provided at the upper header section of one header tank, and a refrigerant outlet is provided at the lower header section of the header tank.
  • a liquid receiver which separates gas and liquid from each other and stores the liquid is joined to the other header tank, and a refrigerant communication is established between the interior of the liquid receiver and the interiors of the upper and lower header sections of the other header tank.
  • refrigerant flows into the liquid receiver from the upper header section of the other header tank, and the gas and liquid portions of the refrigerant are separated from each other in the liquid receiver. After that, the liquid portion; i.e., liquid-predominant mixed phase refrigerant, flows into the lower header section of the other header tank.
  • the heat exchange tubes have the same length; the interior of each of the two header tanks is divided into upper and lower header sections by a partition provided at a vertical position between the refrigerant condensation path and the refrigerant super-cooling path; the left and right end portions of the heat exchange tubes of the refrigerant condensation path are connected to the upper header sections of the two header tanks; and the left and right end portions of the heat exchange tubes of the refrigerant super-cooling path are connected to the lower header sections of the two header tanks.
  • the condensation part and the super-cooling part have the same length as measured in the left-right direction.
  • the areas of the heat exchange portions of the condensation part and the super-cooling part become insufficient, and further improvement of the refrigerant condensation efficiency and the refrigerant super-cooling efficiency cannot be attained.
  • the present applicant has proposed a condenser for a car air conditioner which can further improve the refrigerant condensation efficiency and the refrigerant super-cooling efficiency (see the pamphlet of WO2010/047320).
  • the proposed condenser has a condensation part and a super-cooling part provided such that the former is located above the latter.
  • the condenser includes a plurality of heat exchange tubes disposed in parallel such that their length direction coincides with the left-right direction and they are spaced apart from one another in the vertical direction; and header tanks which are disposed such that their length direction coincides with the vertical direction and to which left and right end portions of the heat exchange tubes are connected, respectively.
  • the condensation part has a first tube group composed of two heat exchange paths each serving as a refrigerant condensation path.
  • the super-cooling part has a second tube group located below the first tube group and composed of a single heat exchange path serving as a refrigerant super-cooling path.
  • a first header tank and a second header tank are provided at one of the left and right ends of the condenser, and a third header tank is provided at the other of the left and right ends of the condenser.
  • the heat exchange tubes of the refrigerant condensation paths are connected to the first header tank.
  • the heat exchange tubes of the refrigerant condensation path located furthest downstream with respect to the refrigerant flow direction and the heat exchange tubes of the refrigerant super-cooling path are connected to the second header tank. All the heat exchange tubes are connected to the third header tank.
  • the second header tank is disposed on the outer side of the first header tank with respect to the left-right direction, and the upper end of the second header tank is located above the lower end of the first header tank.
  • the second header thank has a function of separating gas and liquid from each other and storing the liquid.
  • the portions of the heat exchange tubes connected to the second header tank have projection portions which project outward in the left and right direction in relation to the ends of the heat exchange tubes connected to the first header, the ends being located on the side toward the first header tank, and fins are disposed between adjacent projection portions.
  • a heat exchange section is formed by the projection portions of the exchange tubes connected to the second header tank and the fins disposed between adjacent projection portions. Accordingly, the area of the heat exchange section increases as compared with the heat exchanger disclosed in the publication, and refrigerant condensation efficiency and refrigerant super-cooling efficiency are improved.
  • a condenser is generally required to have a wide stable range which appears when refrigerant is charged into the condenser and in which a constant degree of super cooling is attained such that the condenser has a super-cooling characteristic which is more stable against load fluctuation and/or leakage of refrigerant. Therefore, even the condenser which is disclosed in the pamphlet and which has improved refrigerant condensation efficiency and refrigerant super-cooling efficiency as compared with the heat exchanger disclosed in the publication is required to increase the width of the stable range in which a constant degree of super cooling is attained.
  • an object of the present invention is to provide a condenser which can increase the width of the stable range while securing its performance to the greatest degree.
  • the present invention comprises the following modes.
  • a condenser which has a condensation part and a super-cooling part provided such that the condensation part is located above the super-cooling part and which comprises a plurality of heat exchange tubes disposed in parallel such that their length direction coincides with a left-right direction and they are spaced apart from one another in a vertical direction; and header tanks which are disposed such that their length direction coincides with the vertical direction and to which left and right end portions of the heat exchange tubes are connected, each of the condensation part and the super-cooling part including at least one heat exchange path formed by a plurality of heat exchange tubes successively arranged in the vertical direction, the condenser configured such that all refrigerant having flowed through the heat exchange tubes of the condensation part flows into the heat exchange tubes of the super-cooling part,
  • a first header tank to which all the heat exchange tubes of the condensation part are connected and a second header tank to which all the heat exchange tubes of the super-cooling part are connected are provided at one of left and right ends of the condenser;
  • the first header tank has one communication section which communicates with the second header tank through a communication part and to which all the heat exchange tubes forming one heat exchange path are connected;
  • the communication part is provided at a height below the uppermost heat exchange tube among all the heat exchange tubes connected to the communication section;
  • the second header tank is disposed on the outer side of the first header tank with respect to the left-right direction; an upper end of the second header tank is located above a lower end of the first header tank;
  • the second header tank has a function of separating gas and liquid from each other and storing the separated liquid; and all the refrigerant having passed through the heat exchange tubes of the condensation part flows into the communication section of the first header tank and flows into the second header tank through the communication part.
  • condensation part has one heat exchange path
  • first header tank has one communication section to which all the heat exchange tubes forming the heat exchange path of the condensation part are connected; and the communication part establishes a refrigerant communication between the second header tank and a portion of the communication section of the first header tank, the portion extending downward from an approximate center of the communication section with respect to the vertical direction.
  • a condenser according to par. 1), wherein the condensation part has two or more heat exchange paths; the condenser is configured such that refrigerant flows from a heat exchange path at one end with respect to the vertical direction toward a heat exchange path at the other end with respect to the vertical direction; the first header tank has one communication section to which all the heat exchange tubes forming a furthest downstream heat exchange path of the condensation part are connected; and the communication part establishes a refrigerant communication between the second header tank and a portion of the communication section of the first header tank, the portion extending downward from an approximate center of the communication section with respect to the vertical direction.
  • a first header tank to which all the heat exchange tubes of the condensation part are connected and a second header tank to which all the heat exchange tubes of the super-cooling part are connected are provided at one of left and right ends of the condenser;
  • the first header tank has one communication section which communicates with the second header tank through a communication part and to which all the heat exchange tubes forming one heat exchange path are connected;
  • the communication part is provided at a height below the uppermost heat exchange tube among all the heat exchange tubes connected to the communication section;
  • the second header tank is disposed on the outer side of the first header tank with respect to the left-right direction; an upper end of the second header tank is located above a lower end of the first header tank;
  • the second header tank has a function of separating gas and liquid from each other and storing the separated liquid; and all the refrigerant having passed through the heat exchange tubes of the condensation part flows into the communication section of the first header tank and flows into the second header tank through the communication part.
  • the refrigerant when refrigerant within the communication section of the first header tank reaches the communication part during charging thereof, the refrigerant flows into the second header tank through the communication part and then flows into the heat exchange tubes of the refrigerant super-cooling path. Therefore, as compared with the case where the refrigerant within the communication section flows into the second header tank after reaching the uppermost heat exchange tube among all the heat exchange tubes connected to the communication section, the interiors of the heat exchange tubes forming the refrigerant super-cooling path can be filled with liquid-phase refrigerant at an early stage.
  • the width of a stable range within which a constant degree of super cooling is attained i.e., the width of a range regarding the refrigerant charge amount within which a constant degree of super cooling is attained, increases.
  • a super-cooling characteristic which is more stable against load fluctuation and/or leakage of refrigerant can be attained, and the performance of a car air conditioner using this condenser can be maintained for a long period of time.
  • the length of the heat exchange tubes of all the heat exchange paths of the super-cooling part becomes greater than the length of the heat exchange tubes of all the heat exchange paths of the condensation part, as compared with the condenser disclosed in the above-mentioned publication, the area of the heat exchange section increases, and the refrigerant super-cooling efficiency increases.
  • the first header tank to which all the heat exchange tubes of the condensation part are connected and the second header tank to which all the heat exchange tubes of the super-cooling part are connected are provided at one of the left and right ends as in the condenser of par. 1), if a refrigerant communication is not established between the first header tank and the second header tank via the communication part, it is impossible to separate gas and liquid in the second header tank and fill the interiors of the heat exchange tubes of the super-cooling part with the obtained liquid-predominant mixed phase refrigerant as in the condenser described in the above-mentioned pamphlet.
  • FIG. 1 is a front view specifically showing the overall structure of a first embodiment of a condenser according to the present invention
  • FIG. 2 is a front view schematically showing the condenser of FIG. 1 ;
  • FIG. 3 is an enlarged sectional view taken along line A-A of FIG. 1 ;
  • FIG. 4 is an exploded perspective view showing a main portion of the condenser of FIG. 1 ;
  • FIG. 5 is a view corresponding to FIG. 3 and showing a first modification of a communication part
  • FIG. 6 is a perspective view showing a communication member of the communication part of FIG. 5 .
  • FIG. 7 is a view corresponding to FIG. 3 and showing a second modification of the communication part
  • FIG. 8 is a perspective view showing a communication member of the communication part of FIG. 7 .
  • FIG. 9 is a view corresponding to FIG. 3 and showing a third modification of the communication part
  • FIG. 10 is an exploded perspective view showing a portion of a condenser which includes the communication part of FIG. 9 ;
  • FIG. 11 is a view corresponding to FIG. 3 and showing a fourth modification of the communication part
  • FIG. 12 is a view corresponding to FIG. 3 and showing a fifth modification of the communication part
  • FIG. 13 is a view corresponding to FIG. 3 and showing a sixth modification of the communication part
  • FIG. 14 is an exploded perspective view showing a portion of a condenser which includes the communication part of FIG. 13 ;
  • FIG. 15 is a front view schematically showing a second embodiment of the condenser according to the present invention.
  • FIG. 16 is a front view schematically showing a third embodiment of the condenser according to the present invention.
  • FIG. 17 is a front view schematically showing a fourth embodiment of the condenser according to the present invention.
  • FIG. 18 is a front view schematically showing a fifth embodiment of the condenser according to the present invention.
  • aluminum as used in the following description encompasses aluminum alloys in addition to pure aluminum.
  • FIG. 1 specifically shows the overall structure of a first embodiment of a condenser according to the present invention.
  • FIG. 2 schematically shows the condenser of FIG. 1 .
  • FIGS. 3 and 4 show the structure of a main portion of the condenser of FIG. 1 .
  • individual heat exchange tubes are not illustrated, and corrugate fins, side plates, a refrigerant inlet member, and a refrigerant outlet member are also not illustrated.
  • a condenser 1 has a condensation part 1 A and a super-cooling part 1 B provided such that the former is located above the latter.
  • the condenser 1 includes a plurality of flat heat exchange tubes 2 A, 2 B formed of aluminum, three header tanks 3 , 4 , 5 formed of aluminum, corrugate fins 6 A, 6 B formed of aluminum, and side plates 7 formed of aluminum.
  • the heat exchange tubes 2 A, 2 B are disposed such that their width direction coincides with an air passage direction, their length direction coincides with a left-right direction, and they are spaced from one another in a vertical direction.
  • the header tanks 3 , 4 , 5 are disposed such that their length direction coincides with the vertical direction, and left and right end portions of the heat exchange tubes 2 A, 2 B are brazed to the header tanks 3 , 4 , 5 .
  • Each of the corrugate fins 6 A, 6 B is disposed between and brazed to adjacent heat exchange tubes 2 A, 2 B, or is disposed on the outer side of the uppermost or lowermost heat exchange tube 2 A, 2 B and brazed to the corresponding heat exchange tube 2 A, 2 B.
  • the side plates 7 are disposed on the corresponding outer sides of the uppermost and lowermost corrugate fins 6 A, 6 B, and are brazed to these corrugate fins 6 A, 6 B.
  • Each of the condensation part 1 A and super-cooling part 1 B of the condenser 1 includes at least one (only one in the present embodiment) heat exchange path P 1 , P 2 formed by a plurality of heat exchange tubes 2 A, 2 B successively arranged in the vertical direction.
  • the heat exchange path P 1 provided in the condensation part 1 A serves as a refrigerant condensation path.
  • the heat exchange path P 2 provided in the super-cooling part 1 B serves as a refrigerant super-cooling path.
  • the flow direction of refrigerant is the same among all the heat exchange tubes 2 A, 2 B which form the respective heat exchange paths P 1 , P 2 .
  • the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form a certain heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form another heat exchange path adjacent to the certain heat exchange path.
  • the heat exchange path P 1 of the condensation part 1 A will be referred to as the first heat exchange path
  • the heat exchange path P 2 of the super-cooling part 1 B will be referred to as the second heat exchange path.
  • the first header tank 3 and the second header tank 4 are individually provided at the left end of the condenser 1 .
  • Left end portions of all the heat exchange tubes 2 A, which form the first heat exchange path P 1 provided in the condensation part 1 A, are connected to the first header tank 3 through brazing.
  • Left end portions of the heat exchange tubes 2 B, which form the second heat exchange path P 2 provided in the super-cooling part 1 B, are connected to the second header tank 4 through brazing.
  • the upper end of the second header tank 4 is located above the lower end of the first header tank 3 .
  • the upper end of the second header tank 4 is located at substantially the same height as the upper end of the first header tank 3 .
  • the lower end of the second header tank 4 is located below the lower end of the first header tank 3 .
  • the heat exchange tubes 2 B which form the second heat exchange path P 2 , are brazed to a portion of the second header tank 4 located below the first header tank 3 .
  • the inner volume of the second header tank 4 is determined such that a portion of gas-liquid mixed phase refrigerant having flowed into the second header tank 4 ; i.e., liquid-predominant mixed phase refrigerant, accumulates in a lower region within the second header tank 4 because of gravitational force, and the gas phase component of the gas-liquid mixed phase refrigerant accumulates in an upper region within the second header tank 4 because of gravitational force, whereby gas and liquid are separated from each other.
  • the second header tank 4 serves as a liquid receiving section which separates gas and liquid from each other through utilization of gravitational force and stores the liquid.
  • the heat exchange tubes 2 A connected to the first header tank 3 will be referred to as the first heat exchange tubes
  • the heat exchange tubes 2 B connected to the second header tank 4 will be referred to as the second heat exchange tubes.
  • the corrugate fins 6 A disposed between the adjacent first heat exchange tubes 2 A, that between the uppermost first heat exchange tube 2 A and the upper side plate 7 , and that between the lowermost first heat exchange tube 2 A and the uppermost second heat exchange tube 2 B will be referred to as the first corrugate fins.
  • the corrugate fins 6 B disposed between the adjacent second heat exchange tubes 2 B, and that between the lowermost second heat exchange tube 2 B and the lower side plate 7 will be referred to as the second corrugate fins.
  • the third header tank 5 is disposed at the right end of the condenser 1 . Right end portions of all the heat exchange tubes 2 A, 2 B which form the first and second heat exchange paths P 1 , P 2 are connected to the third header tank 5 .
  • the third header tank 5 has a transverse cross-sectional shape identical with that of the first header tank 3 .
  • the interior of the third header tank 5 is divided into an upper header section 9 and a lower header section 11 by an aluminum partition plate 8 provided at a height between the first heat exchange path P 1 and the second heat exchange path P 2 .
  • a refrigerant inlet 12 is formed in the upper header section 9 of the third header tank 5 at a vertically middle position, and a refrigerant outlet 13 is formed in the lower header section 11 .
  • a refrigerant inlet member 14 communicating with the refrigerant inlet 12 and a refrigerant outlet member 15 communicating with the refrigerant outlet 13 are joined to the third header tank 5 .
  • the first header tank 3 has one communication section 17 to which all the first heat exchange tubes 2 A of the first heat exchange path P 1 provided in the condensation part 1 A are connected and which communicates with the second header tank 4 via a communication part 16 . That is, the entire interior of the first header tank 3 serves as the communication section 17 .
  • the communication part 16 is provided at a height below the uppermost first heat exchange tube 2 A among all the first heat exchange tubes 2 A connected to the communication section 17 (in the present embodiment, at a position which is below the vertically middle position of the communication section 17 and close to the lower end thereof.
  • the communication part 16 includes a through hole 18 formed in the circumferential wall of the first header tank 3 , a through hole 19 formed in the circumferential wall of the second header tank 4 , and a communication member 21 formed of aluminum.
  • the communication member 21 is disposed between the first header tank 3 and the second header tank 4 , is brazed to the two header tanks 3 , 4 , and has a flow channel 22 for establishing a refrigerant communication between the through hole 18 of the first header tank 3 and the through hole 19 of the second header tank 4 .
  • the communication member 21 has a first concave arcuate surface 21 a which is provided on its right side surface and which matches the outer circumferential surface of the first header tank 3 , and a second concave arcuate surface 21 b which is provided on its left side surface and which matches the outer circumferential surface of the second header tank 4 . Opposite ends of the flow channel 22 are open to the two concave arcuate surfaces 21 a and 21 b.
  • the condenser 1 is manufactured by brazing all the components thereof together.
  • the condenser 1 constitutes a refrigeration cycle in cooperation with a compressor, an expansion valve (pressure reducer), and an evaporator; and the refrigeration cycle is mounted on a vehicle as a car air conditioner.
  • gas phase refrigerant of high temperature and high pressure compressed by the compressor flows into the upper header section 9 of the third header tank 5 through the refrigerant inlet member 14 and the refrigerant inlet 12 .
  • the gas phase refrigerant is condensed while flowing leftward within the first heat exchange tubes 2 A of the first heat exchange path P 1 , and flows into the communication section 17 of the first header tank 3 .
  • the refrigerant having flowed into the communication section 17 of the first header tank 3 flows into the second header tank 4 through the through hole 18 of the first header tank 3 , the flow channel 22 of the communication member 21 , and the through hole 19 of the second header tank 4 , which constitute the communication part 16 .
  • the refrigerant having flowed into the second header tank 4 is gas-liquid mixed phase refrigerant.
  • a portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, accumulates in a lower region within the second header thank 4 because of gravitational force, and flows into the second heat exchange tubes 2 B of the second heat exchange path P 2 .
  • the liquid-predominant mixed phase refrigerant having flowed into the second heat exchange tubes 2 B of the second heat exchange path P 2 is super-cooled while flowing rightward within the second heat exchange tubes 2 B. After that, the super-cooled refrigerant enters the lower header section 11 of the third header tank 5 , and flows out through the refrigerant outlet 13 and the refrigerant outlet member 15 . The refrigerant is then fed to the evaporator via the expansion valve.
  • the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank 4 stays in an upper region of the second header tank 4 .
  • FIGS. 5 to 14 show modifications of the communication part for establishing a refrigerant communication between the communication section 17 of the first header tank 3 and the second header tank 4 .
  • a communication part 30 shown in FIGS. 5 and 6 includes the through hole 18 formed in the circumferential wall of the first header tank 3 , the through hole 19 formed in the circumferential wall of the second header tank 4 , and a communication member 31 formed of aluminum and having the shape of a cylindrical tube.
  • the communication member 31 is brazed to the first header tank 3 and the second header tank 4 , and has a flow channel 32 for establishing a refrigerant communication between the through hole 18 of the first header tank 3 and the through hole 19 of the second header tank 4 .
  • the communication member 31 has an annular bead 33 which is formed at a center portion of the communication member 31 with respect to the length direction and is located between the two header tanks header tanks 3 and 4 .
  • a first insertion portion 34 inserted into the through hole 18 of the first header tank 3 is provided on the right side of the annular bead 33 of the communication member 31
  • a second insertion portion 35 inserted into the through hole 19 of the second header tank 4 is provided on the left side of the annular bead 33 of the communication member 31 .
  • a communication part 40 shown in FIGS. 7 and 8 includes the through hole 18 formed in the circumferential wall of the first header tank 3 , the through hole 19 formed in the circumferential wall of the second header tank 4 , and a communication member 41 formed of aluminum.
  • the communication member 41 is disposed between the first header tank 3 and the second header tank 4 , is brazed to the two header tanks 3 and 4 , and has a flow channel 42 for establishing a refrigerant communication between the through hole 18 of the first header tank 3 and the through hole 19 of the second header tank 4 .
  • the communication member 41 has a first concave arcuate surface 41 a which is provided on its right side surface and which matches the outer circumferential surface of the first header tank 3 , and a second concave arcuate surface 41 b which is provided on its left side surface and which matches the outer circumferential surface of the second header tank 4 . Opposite ends of the flow channel 42 are open to the two concave arcuate surfaces 41 a and 41 b.
  • a first extension portion 43 is provided at a lower half portion of the communication member 41 .
  • the first extension portion 43 extends in one of the air flow directions and along the outer circumferential surface of the first header tank 3 , and is brazed to the first header tank 3 .
  • a second extension portion 44 is provided at an upper half portion of the communication member 41 .
  • the second extension portion 44 extends in the same direction as the extension direction of the first extension portion 43 and along the outer circumferential surface of the second header tank 4 , and is brazed to the second header tank 4 .
  • a first protrusion 46 is formed on the right side surface of the first extension portion 43 , and is fitted into a blind hole 45 formed on the outer circumferential surface of the first header tank 3 .
  • a second protrusion 48 is formed on the left side surface of the second extension portion 44 , and is fitted into a blind hole 47 formed on the outer circumferential surface of the second header tank 4 .
  • a communication part 50 shown in FIGS. 9 and 10 includes the through hole 18 formed in the circumferential wall of the first header tank 3 , the through hole 19 formed in the circumferential wall of the second header tank 4 , and a tubular portion 51 which is integrally formed on the circumferential wall of the second header tank 4 such that the tubular portion 51 surrounds the through hole 19 and projects outward.
  • the tubular portion 51 is inserted into the through hole 18 of the first header tank 3 , and is brazed to the first header tank 3 .
  • the interior of the tubular portion 51 serves as a flow channel 52 for establishing a refrigerant communication between the through holes 18 and 19 of the two header tanks 3 and 4 .
  • a communication part 55 shown in FIG. 11 includes the through hole 18 formed in the circumferential wall of the first header tank 3 , the through hole 19 formed in the circumferential wall of the second header tank 4 , and a tubular portion 56 which is integrally formed on the circumferential wall of the first header tank 3 such that the tubular portion 56 surrounds the through hole 18 and projects outward.
  • the tubular portion 56 is inserted into the through hole 19 of the second header tank 4 , and is brazed to the second header tank 4 .
  • the interior of the tubular portion 56 serves as a flow channel 57 for establishing a refrigerant communication between the through holes 18 and 19 of the two header tanks 3 and 4 .
  • a communication part 60 shown in FIG. 12 includes the through hole 18 formed in the circumferential wall of the first header tank 3 , the through hole 19 formed in the circumferential wall of the second header tank 4 , a first tubular portion 61 which is integrally formed on the circumferential wall of the first header tank 3 such that the first tubular portion 61 surrounds the through hole 18 and projects outward, and a second tubular portion 62 which is integrally formed on the circumferential wall of the second header tank 4 such that the second tubular portion 62 surrounds the through hole 19 and projects outward.
  • the second tubular portion 62 is fitted onto the circumference of the first tubular portion 61 of the first header tank 3 , and is brazed to the first tubular portion 61 .
  • the interiors of the two tubular portions 61 and 62 serve as flow channels 63 and 64 for establishing a refrigerant communication between the through holes 18 and 19 of the two header tanks 3 and 4 .
  • a communication part 65 shown in FIGS. 13 and 14 includes the through hole 18 formed in the circumferential wall of the first header tank 3 , an outward bulging portion 66 formed on the circumferential wall of the second header tank 4 and brazed to the first header tank 3 , and a through hole 67 formed in the bulging top wall of the outward bulging portion 66 and communicating with the through hole 18 of the first header tank 3 .
  • a concave arcuate surface 66 a which fits the outer circumferential surface of the first header tank 3 is provided on the outer surface of the bulging top wall of the outward bulging portion 66 .
  • FIGS. 15 to 18 show other embodiments of the condenser of the present invention.
  • Each of FIGS. 15 to 18 schematically shows a condenser, and shows none of the individual heat exchange tubes, the corrugate fins, the side plates, the refrigerant inlet member, and the refrigerant outlet member.
  • a condensation part 70 A and a super-cooling part 70 B are provided such that the former is located above the latter.
  • the condensation part 70 A includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 A successively arranged in the vertical direction.
  • the condensation part 70 A includes three heat exchange paths P 1 , P 2 , P 3 which are juxtaposed in the vertical direction.
  • the super-cooling part 70 B includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 B successively arranged in the vertical direction.
  • the super-cooling part 70 B includes one heat exchange path P 4 .
  • the heat exchange paths P 1 , P 2 , P 3 provided in the condensation part 70 A serve as refrigerant condensation paths.
  • the heat exchange path P 4 provided in the super-cooling part 70 B serves as a refrigerant super-cooling path.
  • the flow direction of refrigerant is the same among all the heat exchange tubes 2 A, 2 B which form the respective heat exchange paths P 1 , P 2 , P 3 , P 4 .
  • the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form a certain heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form another heat exchange path adjacent to the certain heat exchange path.
  • the three heat exchange paths provided in the condensation part 70 A will be referred to as the first, second, and third heat exchange paths P 1 , P 2 , P 3 from the upper side.
  • the heat exchange path P 4 of the super-cooling part 70 B will be referred to as the fourth heat exchange path P 4 .
  • Left end portions of all the heat exchange tubes 2 A, which form the first to third heat exchange paths P 1 , P 2 , P 3 are connected to the first header tank 3 through brazing.
  • Left end portions of all the heat exchange tubes 2 B, which form the fourth heat exchange path P 4 are connected to a portion of the second header tank 4 through brazing, the portion being located below the first header tank 3 .
  • the heat exchange tubes 2 A connected to the first header tank 3 will be referred to as the first heat exchange tubes
  • the heat exchange tubes 2 B connected to the second header tank 4 will be referred to as the second heat exchange tubes.
  • the interior of the first header tank 3 which is disposed at the left end of the condenser 70 and to which left end portions of all the heat exchange tubes 2 A of the first through third heat exchange paths P 1 , P 2 , P 3 provided in the condenser section 70 A are connected through brazing, is divided into an upper header section 72 and a lower header section 73 by an aluminum partition plate 71 provided at a height between the second heat exchange path P 2 and the third heat exchange path P 3 .
  • the interior of the third header tank 5 which is disposed at the right end of the condenser 70 and to which right end portions of all the heat exchange tubes 2 A, 2 B of the first through fourth heat exchange paths P 1 , P 2 , P 3 , P 4 are connected through brazing, is divided into an upper header section 76 , an intermediate header section 77 , and a lower header section 78 by aluminum partition plates 74 , 75 provided at a height between the first heat exchange path P 1 and the second heat exchange path P 2 and a height between the third heat exchange path P 3 and the fourth heat exchange path P 4 , respectively.
  • the refrigerant inlet 12 is formed in the upper header section 76 of the third header tank 5
  • the refrigerant outlet 13 is formed in the lower header section 78 of the third header tank 5 .
  • a refrigerant inlet member (not shown) communicating with the refrigerant inlet 12 and a refrigerant outlet member (not shown) communicating with the refrigerant outlet 13 are joined to the third header tank 5 .
  • the lower header section 73 of the first header tank 3 has one communication section 79 to which all the first heat exchange tubes 2 A of the third heat exchange path P 3 are connected and which communicates with the second header tank 4 via the communication part 16 .
  • the third heat exchange path P 3 is located furthest downstream with respect to the refrigerant flow direction.
  • the communication part 16 is provided at a height below the uppermost first heat exchange tube 2 A among all the first heat exchange tubes 2 A of the third heat exchange path P 3 connected to the communication section 79 (in the present embodiment, at a position which is below the vertically middle position of the communication section 79 and close to the lower end thereof).
  • the structure of the remaining portion is identical with that of the condenser shown in FIGS. 1 to 4 .
  • gas phase refrigerant of high temperature and high pressure compressed by the compressor flows into the upper header section 76 of the third header tank 5 through the refrigerant inlet member and the refrigerant inlet 12 .
  • the gas phase refrigerant is condensed while flowing leftward within the first heat exchange tubes 2 A of the first heat exchange path P 1 , and flows into the upper header section 72 of the first header tank 3 .
  • the refrigerant having flowed into the upper header section 72 of the first header tank 3 is condensed while flowing rightward within the first heat exchange tubes 2 A of the second heat exchange path P 2 , and flows into the intermediate header section 77 of the third header tank 5 .
  • the refrigerant having flowed into the intermediate header section 77 of the third header tank 5 is condensed while flowing leftward within the first heat exchange tubes 2 A of the third heat exchange path P 3 , and flows into the communication section 79 of the lower header section 73 of the first header tank 3 .
  • the refrigerant having flowed into the communication section 79 of the lower header section 73 of the first header tank 3 flows into the second header tank 4 through the through hole 18 of the first header tank 3 , the flow channel 22 of the communication member 21 , and the through hole 19 of the second header tank 4 , which constitute the communication part 16 .
  • the refrigerant having flowed into the second header tank 4 is gas-liquid mixed phase refrigerant.
  • a portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, accumulates in a lower region within the second header thank 4 because of gravitational force, and flows into the second heat exchange tubes 2 B of the fourth heat exchange path P 4 .
  • the liquid-predominant mixed phase refrigerant having flowed into the second heat exchange tubes 2 B of the fourth heat exchange path P 4 is super-cooled while flowing rightward within the second heat exchange tubes 2 B. After that, the super-cooled refrigerant enters the lower header section 78 of the third header tank 5 , and flows out through the refrigerant outlet 13 and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
  • the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank 4 stays in an upper region of the second header tank 4 .
  • a condensation part 80 A and a super-cooling part 80 B are provided such that the former is located above the latter.
  • the condensation part 80 A includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 A successively arranged in the vertical direction.
  • the condensation part 80 A includes three heat exchange paths P 1 , P 2 , P 3 which are juxtaposed in the vertical direction.
  • the super-cooling part 80 B includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 B successively arranged in the vertical direction.
  • the super-cooling part 80 B includes one heat exchange path P 4 .
  • the heat exchange paths P 1 , P 2 , P 3 provided in the condensation part 80 A serve as refrigerant condensation paths.
  • the heat exchange path P 4 provided in the super-cooling part 80 B serves as a refrigerant super-cooling path.
  • the flow direction of refrigerant is the same among all the heat exchange tubes 2 A, 2 B which form the respective heat exchange paths P 1 , P 2 , P 3 , P 4 .
  • the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form a certain heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form another heat exchange path adjacent to the certain heat exchange path.
  • the three heat exchange paths provided in the condensation part 80 A will be referred to as the first, second, and third heat exchange paths P 1 , P 2 , P 3 from the lower side.
  • the heat exchange path P 4 of the super-cooling part 80 B will be referred to as the fourth heat exchange path P 4 .
  • Left end portions of all the heat exchange tubes 2 A, which form the first to third heat exchange paths P 1 , P 2 , P 3 are connected to the first header tank 3 through brazing.
  • Left end portions of all the heat exchange tubes 2 B, which form the fourth heat exchange path P 4 are connected to a portion of the second header tank 4 through brazing, the portion being located below the first header tank 3 .
  • the heat exchange tubes 2 A connected to the first header tank 3 will be referred to as the first heat exchange tubes
  • the heat exchange tubes 2 B connected to the second header tank 4 will be referred to as the second heat exchange tubes.
  • the interior of the first header tank 3 which is disposed at the left end of the condenser 80 and to which left end portions of all the heat exchange tubes 2 A of the first through third heat exchange paths P 1 , P 2 , P 3 provided in the condenser section 80 A are connected through brazing, is divided into a lower header section 82 and an upper header section 83 by an aluminum partition plate 81 provided at a height between the second heat exchange path P 2 and the third heat exchange path P 3 .
  • the interior of the third header tank 5 which is disposed at the right end of the condenser 80 and to which right end portions of all the heat exchange tubes 2 A, 2 B forming the first through fourth heat exchange paths P 1 , P 2 , P 3 , P 4 are connected through brazing, is divided into an intermediate header section 86 , an upper header section 87 , and a lower header section 88 by aluminum partition plates 84 , 85 provided at a height between the first heat exchange path P 1 and the second heat exchange path P 2 and a height between the first heat exchange path P 1 and the fourth heat exchange path P 4 , respectively.
  • the refrigerant inlet 12 is formed in the intermediate header section 86 of the third header tank 5
  • the refrigerant outlet 13 is formed in the lower header section 88 of the third header tank 5 .
  • a refrigerant inlet member (not shown) communicating with the refrigerant inlet 12 and a refrigerant outlet member (not shown) communicating with the refrigerant outlet 13 are joined to the third header tank 5 .
  • the upper header section 83 of the first header tank 3 has one communication section 89 to which all the first heat exchange tubes 2 A of the third heat exchange path P 3 are connected and which communicates with the second header tank 4 via the communication part 16 .
  • the third heat exchange path P 3 is located furthest downstream with respect to the refrigerant flow direction.
  • the communication part 16 is provided at a height below the uppermost first heat exchange tube 2 A among all the first heat exchange tubes 2 A of the third heat exchange path P 3 connected to the communication section 89 (in the present embodiment, at a position which is below the vertically middle position of the communication section 89 and close to the lower end thereof).
  • the structure of the remaining portion is identical with that of the condenser shown in FIGS. 1 to 4 .
  • gas phase refrigerant of high temperature and high pressure compressed by the compressor flows into the intermediate header section 86 of the third header tank 5 through the refrigerant inlet member and the refrigerant inlet 12 .
  • the gas phase refrigerant is condensed while flowing leftward within the first heat exchange tubes 2 A of the first heat exchange path P 1 , and flows into the lower header section 82 of the first header tank 3 .
  • the refrigerant having flowed into the lower header section 82 of the first header tank 3 is condensed while flowing rightward within the first heat exchange tubes 2 A of the second heat exchange path P 2 , and flows into the upper header section 87 of the third header tank 5 .
  • the refrigerant having flowed into the upper header section 87 of the third header tank 5 is condensed while flowing leftward within the first heat exchange tubes 2 A of the third heat exchange path P 3 , and flows into the communication section 89 of the upper header section 83 of the first header tank 3 .
  • the refrigerant having flowed into the communication section 89 of the upper header section 83 of the first header tank 3 flows into the second header tank 4 through the through hole 18 of the first header tank 3 , the flow channel 22 of the communication member 21 , and the through hole 19 of the second header tank 4 , which constitute the communication part 16 .
  • the refrigerant having flowed into the second header tank 4 is gas-liquid mixed phase refrigerant.
  • a portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, accumulates in a lower region within the second header thank 4 because of gravitational force, and flows into the second heat exchange tubes 2 B of the fourth heat exchange path P 4 .
  • the liquid-predominant mixed phase refrigerant having flowed into the second heat exchange tubes 2 B of the fourth heat exchange path P 4 is super-cooled while flowing rightward within the second heat exchange tubes 2 B. After that, the super-cooled refrigerant enters the lower header section 88 of the third header tank 5 , and flows out through the refrigerant outlet 13 and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
  • the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank 4 stays in an upper region of the second header tank 4 .
  • a condensation part 90 A and a super-cooling part 90 B are provided such that the former is located above the latter.
  • the condensation part 90 A includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 A successively arranged in the vertical direction.
  • the condensation part 90 A includes two heat exchange paths P 1 , P 2 which are juxtaposed in the vertical direction.
  • the super-cooling part 90 B includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 B successively arranged in the vertical direction.
  • the super-cooling part 90 B includes one heat exchange path P 3 .
  • the heat exchange paths P 1 , P 2 provided in the condensation part 90 A serve as refrigerant condensation paths.
  • the heat exchange path P 3 provided in the super-cooling part 90 B serves as a refrigerant super-cooling path.
  • the flow direction of refrigerant is the same among all the heat exchange tubes 2 A, 2 B which form the respective heat exchange paths P 1 , P 2 , P 3 .
  • the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form a certain heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form another heat exchange path adjacent to the certain heat exchange path.
  • the two heat exchange paths provided in the condensation part 90 A will be referred to as the first and second heat exchange paths P 1 , P 2 from the upper side.
  • the heat exchange path P 3 provided in the super-cooling part 90 B will be referred to as the third heat exchange path P 3 .
  • Left end portions of all the heat exchange tubes 2 A, which form the first and second heat exchange paths P 1 , P 2 are connected to the first header tank 3 through brazing.
  • Left end portions of all the heat exchange tubes 2 B, which form the third heat exchange path P 3 are connected to a portion of the second header tank 4 through brazing, the portion being located below the first header tank 3 .
  • the heat exchange tubes 2 A connected to the first header tank 3 will be referred to as the first heat exchange tubes
  • the heat exchange tubes 2 B connected to the second header tank 4 will be referred to as the second heat exchange tubes.
  • the first and second heat exchange paths P 1 , P 2 serve as refrigerant condensation paths
  • the third heat exchange path P 3 serves as a refrigerant super-cooling path.
  • the interior of the first header tank 3 which is disposed at the left end of the condenser 90 and to which left end portions of all the heat exchange tubes 2 A of the first and second heat exchange paths P 1 , P 2 provided in the condenser section 90 A are connected through brazing, is divided into an upper header section 92 and a lower header section 93 by an aluminum partition plate 91 provided at a height between the first heat exchange path P 1 and the second heat exchange path P 2 .
  • the upper end of the first header tank 3 is located below the upper end of the second header tank 4 , which is disposed at the left end of the condenser 90 and to which left end portions of all the heat exchange tubes 2 B of the third heat exchange path P 3 provided in the super-cooling part 90 B are connected through brazing.
  • the refrigerant inlet 12 is formed in a portion of the upper header section 92 of the first header tank 3 , the portion projecting upward in relation to the second header tank 4 .
  • a refrigerant inlet member (not shown) communicating with the refrigerant inlet 12 is joined to the first header tank 3 .
  • the interior of the third header tank 5 which is disposed at the right end of the condenser 90 and to which right end portions of all the heat exchange tubes 2 A, 2 B of the first through third heat exchange paths P 1 , P 2 , P 3 are connected through brazing, is divided into an upper header section 95 and a lower header section 96 by an aluminum partition plate 94 provided at a height between the second heat exchange path P 2 and the third heat exchange path P 3 .
  • the refrigerant outlet 13 is formed in the lower header section 96 of the third header tank 5 .
  • a refrigerant outlet member (not shown) communicating with the refrigerant outlet 13 is joined to the third header tank 5 .
  • the lower header section 93 of the first header tank 3 has one communication section 97 to which all the first heat exchange tubes 2 A of the second heat exchange path P 2 are connected and which communicates with the second header tank 4 via the communication part 16 .
  • the second heat exchange path P 2 is located furthest downstream with respect to the refrigerant flow direction.
  • the communication part 16 is provided at a height below the uppermost first heat exchange tube 2 A among all the first heat exchange tubes 2 A of the second heat exchange path P 2 connected to the communication section 97 (in the present embodiment, at a position which is below the vertically middle position of the communication section 97 and close to the lower end thereof).
  • the structure of the remaining portion is identical with that of the condenser shown in FIGS. 1 to 4 .
  • gas phase refrigerant of high temperature and high pressure compressed by the compressor flows into the upper header section 92 of the first header tank 3 through the refrigerant inlet member and the refrigerant inlet 12 .
  • the gas phase refrigerant is condensed while flowing rightward within the first heat exchange tubes 2 A of the first heat exchange path P 1 , and flows into the upper header section 95 of the third header tank 5 .
  • the refrigerant having flowed into the upper header section 95 of the third header tank 5 is condensed while flowing leftward within the first heat exchange tubes 2 A of the second heat exchange path P 2 , and flows into the communication section 97 of the lower header section 93 of the first header tank 3 .
  • the refrigerant having flowed into the communication section 97 of the lower header section 93 of the first header tank 3 flows into the second header tank 4 through the through hole 18 of the first header tank 3 , the flow channel 22 of the communication member 21 , and the through hole 19 of the second header tank 4 , which constitute the communication part 16 .
  • the refrigerant having flowed into the second header tank 4 is gas-liquid mixed phase refrigerant.
  • a portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, accumulates in a lower region within the second header thank 4 because of gravitational force, and flows into the second heat exchange tubes 2 B of the third heat exchange path P 3 .
  • the liquid-predominant mixed phase refrigerant having flowed into the second heat exchange tubes 2 B of the third heat exchange path P 3 is super-cooled while flowing rightward within the second heat exchange tubes 2 B. After that, the super-cooled refrigerant enters the lower header section 96 of the third header tank 5 , and flows out through the refrigerant outlet 13 and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
  • the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank 4 stays in an upper region of the second header tank 4 .
  • a condensation part 100 A and a super-cooling part 100 B are provided such that the former is located above the latter.
  • the condensation part 100 A includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 A successively arranged in the vertical direction.
  • the condensation part 100 A includes two heat exchange paths P 1 , P 2 which are juxtaposed in the vertical direction.
  • the super-cooling part 100 B includes at least one heat exchange path formed by a plurality of heat exchange tubes 2 B successively arranged in the vertical direction.
  • the super-cooling part 100 B includes one heat exchange path P 3 .
  • the heat exchange paths P 1 , P 2 provided in the condensation part 100 A serve as refrigerant condensation paths.
  • the heat exchange path P 3 provided in the super-cooling part 100 B serves as a refrigerant super-cooling path.
  • the flow direction of refrigerant is the same among all the heat exchange tubes 2 A, 2 B which form the respective heat exchange paths P 1 , P 2 , P 3 .
  • the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form a certain heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes 2 A, 2 B which form another heat exchange path adjacent to the certain heat exchange path.
  • the two heat exchange paths provided in the condensation part 100 A will be referred to as the first and second heat exchange paths P 1 , P 2 .
  • the heat exchange path P 3 of the super-cooling part 100 B will be referred to as the third heat exchange path P 3 .
  • Left end portions of all the heat exchange tubes 2 A, which form the first and second heat exchange paths P 1 , P 2 are connected to the first header tank 3 through brazing.
  • Left end portions of all the heat exchange tubes 2 B, which form the third heat exchange path P 3 are connected to a portion of the second header tank 4 through brazing, the portion being located below the first header tank 3 .
  • the heat exchange tubes 2 A connected to the first header tank 3 will be referred to as the first heat exchange tubes
  • the heat exchange tubes 2 B connected to the second header tank 4 will be referred to as the second heat exchange tubes.
  • the first and second heat exchange paths P 1 , P 2 serve as refrigerant condensation paths
  • the third heat exchange path P 3 serves as a refrigerant super-cooling path.
  • the interior of the first header tank 3 which is disposed at the left end of the condenser 100 and to which left end portions of all the heat exchange tubes 2 A of the first and second heat exchange paths P 1 , P 2 provided in the condenser section 100 A are connected through brazing, is divided into a lower header section 102 and an upper header section 103 by an aluminum partition plate 101 provided at a height between the first heat exchange path P 1 and the second heat exchange path P 2 .
  • the refrigerant inlet 12 is formed in the lower header section 102 of the first header tank 3 .
  • a refrigerant inlet member (not shown) communicating with the refrigerant inlet 12 is joined to the first header tank 3 .
  • the interior of the third header tank 5 which is disposed at the right end of the condenser 100 and to which right end portions of all the heat exchange tubes 2 A, 2 B of the first through third exchange paths P 1 , P 2 , P 3 are connected through brazing, is divided into an upper header section 105 and a lower header section 106 by an aluminum partition plate 104 provided at a height between the first heat exchange path P 1 and the third heat exchange path P 3 .
  • the refrigerant outlet 13 is formed in the lower header section 106 of the third header tank 5 .
  • a refrigerant outlet member (not shown) communicating with the refrigerant outlet 13 is joined to the third header tank 5 .
  • the upper header section 103 of the first header tank 3 has one communication section 107 to which all the first heat exchange tubes 2 A of the second heat exchange path P 2 are connected and which communicates with the second header tank 4 via the communication part 16 .
  • the second heat exchange path P 2 is located furthest downstream with respect to the refrigerant flow direction.
  • the communication part 16 is provided at a height below the uppermost first heat exchange tube 2 A among all the first heat exchange tubes 2 A of the second heat exchange path P 2 connected to the communication section 107 (in the present embodiment, at a position which is below the vertically middle position of the communication section 107 and close to the lower end thereof).
  • the structure of the remaining portion is identical with that of the condenser shown in FIGS. 1 to 4 .
  • gas phase refrigerant of high temperature and high pressure compressed by the compressor flows into the lower header section 102 of the first header tank 3 through the refrigerant inlet member and the refrigerant inlet 12 .
  • the gas phase refrigerant is condensed while flowing rightward within the first heat exchange tubes 2 A of the first heat exchange path P 1 , and flows into the upper header section 105 of the third header tank 5 .
  • the refrigerant having flowed into the upper header section 105 of the third header tank 5 is condensed while flowing leftward within the first heat exchange tubes 2 A of the second heat exchange path P 2 , and flows into the communication section 107 of the upper header section 103 of the first header tank 3 .
  • the refrigerant having flowed into the communication section 107 of the upper header section 103 of the first header tank 3 flows into the second header tank 4 through the through hole 18 of the first header tank 3 , the flow channel 22 of the communication member 21 , and the through hole 19 of the second header tank 4 , which constitute the communication part 16 .
  • the refrigerant having flowed into the second header tank 4 is gas-liquid mixed phase refrigerant.
  • a portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, accumulates in a lower region within the second header thank 4 because of gravitational force, and flows into the second heat exchange tubes 2 B of the third heat exchange path P 3 .
  • the liquid-predominant mixed phase refrigerant having flowed into the second heat exchange tubes 2 B of the third heat exchange path P 3 is super-cooled while flowing rightward within the second heat exchange tubes 2 B. After that, the super-cooled refrigerant enters the lower header section 106 of the third header tank 5 , and flows out through the refrigerant outlet 13 and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
  • the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank 4 stays in an upper region of the second header tank 4 .
  • any of the communication parts 30 , 40 , 50 , 55 , 60 , 65 shown in FIGS. 5 to 14 may be used in order to establish a refrigerant communication between the communication section 79 , 89 , 97 , 107 of the first header tank 3 and the second header tank 4 .
  • a desiccant or a filter may be disposed in the second header tank 4 .

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3483546A1 (en) * 2017-11-09 2019-05-15 Valeo Autosystemy SP. Z.O.O. A condenser
US10801372B2 (en) 2014-10-31 2020-10-13 Modine Manufacturing Company Cooling module and method for rejecting heat from a coupled engine system and rankine cycle waste heat recovery system
US20230082035A1 (en) * 2020-02-19 2023-03-16 Hanon Systems Heat exchanger having flow distribution tank structure for thermal stress dispersion

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012247148A (ja) * 2011-05-30 2012-12-13 Keihin Thermal Technology Corp コンデンサ
JP2014145504A (ja) * 2013-01-28 2014-08-14 T Rad Co Ltd 凝縮器
DE102013211963A1 (de) * 2013-06-24 2014-12-24 Behr Gmbh & Co. Kg Kondensatorbaugruppe
JP6272041B2 (ja) * 2014-01-15 2018-01-31 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
JP6259703B2 (ja) * 2014-04-10 2018-01-10 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
JP6322529B2 (ja) * 2014-09-11 2018-05-09 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
FR3028605B1 (fr) * 2014-11-14 2019-04-05 Valeo Systemes Thermiques Dispositif de fixation pour echangeur de chaleur
JP2019138487A (ja) * 2018-02-06 2019-08-22 株式会社デンソー 凝縮器
EP3620727A1 (de) * 2018-09-06 2020-03-11 Valeo Klimasysteme GmbH Kondensator mit einlegeteil für eine klimaanlage, insbesondere für ein kraftfahrzeug
CN110228348A (zh) * 2019-06-11 2019-09-13 上海加冷松芝汽车空调股份有限公司 一种换热器及汽车空调系统
FR3126763B1 (fr) * 2021-09-03 2024-01-19 Valeo Systemes Thermiques Echangeur de chaleur pour boucle de fluide refrigerant
WO2024201594A1 (ja) * 2023-03-24 2024-10-03 三菱電機株式会社 室外機およびそれを備えた冷凍サイクル装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4977956A (en) * 1988-07-11 1990-12-18 Sanden Corporation Heat exchanger
US5884503A (en) * 1996-10-14 1999-03-23 Calsonic Corporation Condenser with liquid tank and manufacturing method the same
US5974828A (en) * 1996-10-23 1999-11-02 Valeo Thermique Moteur Condenser with removable reservoir for a refrigeration circuit, in particular
US6341647B1 (en) * 1999-02-03 2002-01-29 Denso Corporation Separator-integrated condenser for vehicle air conditioner
US20030116308A1 (en) * 1999-05-31 2003-06-26 Mitsubishi Heavy Industries Ltd. Heat exchanger
US7334429B2 (en) * 2002-08-31 2008-02-26 Behr Gmbh & Co. Kg Refrigerant condenser for motor vehicle air-conditioning systems
WO2010047320A1 (ja) * 2008-10-20 2010-04-29 昭和電工株式会社 コンデンサ

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001033121A (ja) * 1999-07-16 2001-02-09 Denso Corp 受液器一体型熱交換器、および受液器
US6694773B1 (en) * 2003-01-29 2004-02-24 Calsonickansei North America, Inc. Condenser system with nondetachably coupled receiver
JP4069804B2 (ja) * 2003-05-28 2008-04-02 株式会社デンソー 熱交換器および受液器一体型凝縮器
JP2006266570A (ja) * 2005-03-23 2006-10-05 Calsonic Kansei Corp 車両用冷却装置
JP4803199B2 (ja) * 2008-03-27 2011-10-26 株式会社デンソー 冷凍サイクル装置
JP2012247148A (ja) * 2011-05-30 2012-12-13 Keihin Thermal Technology Corp コンデンサ

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4977956A (en) * 1988-07-11 1990-12-18 Sanden Corporation Heat exchanger
US5884503A (en) * 1996-10-14 1999-03-23 Calsonic Corporation Condenser with liquid tank and manufacturing method the same
US5974828A (en) * 1996-10-23 1999-11-02 Valeo Thermique Moteur Condenser with removable reservoir for a refrigeration circuit, in particular
US6341647B1 (en) * 1999-02-03 2002-01-29 Denso Corporation Separator-integrated condenser for vehicle air conditioner
US20030116308A1 (en) * 1999-05-31 2003-06-26 Mitsubishi Heavy Industries Ltd. Heat exchanger
US7334429B2 (en) * 2002-08-31 2008-02-26 Behr Gmbh & Co. Kg Refrigerant condenser for motor vehicle air-conditioning systems
WO2010047320A1 (ja) * 2008-10-20 2010-04-29 昭和電工株式会社 コンデンサ
US20110186277A1 (en) * 2008-10-20 2011-08-04 Showa Denko K.K. Condenser

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10801372B2 (en) 2014-10-31 2020-10-13 Modine Manufacturing Company Cooling module and method for rejecting heat from a coupled engine system and rankine cycle waste heat recovery system
EP3483546A1 (en) * 2017-11-09 2019-05-15 Valeo Autosystemy SP. Z.O.O. A condenser
WO2019092092A1 (en) * 2017-11-09 2019-05-16 Valeo Autosystemy Sp. Z O.O. A condenser
US20230082035A1 (en) * 2020-02-19 2023-03-16 Hanon Systems Heat exchanger having flow distribution tank structure for thermal stress dispersion
US12305939B2 (en) * 2020-02-19 2025-05-20 Hanon Systems Heat exchanger having flow distribution tank structure for thermal stress dispersion

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