US20260009602A1 - Heat exchanger - Google Patents

Heat exchanger

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Publication number
US20260009602A1
US20260009602A1 US19/325,135 US202519325135A US2026009602A1 US 20260009602 A1 US20260009602 A1 US 20260009602A1 US 202519325135 A US202519325135 A US 202519325135A US 2026009602 A1 US2026009602 A1 US 2026009602A1
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US
United States
Prior art keywords
primary
region
refrigerant
tubes
communication holes
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.)
Pending
Application number
US19/325,135
Other languages
English (en)
Inventor
Takaaki NAKAI
Tomohiko Nakamura
Ichio Kamei
Kengo Kazari
Yusuke Kito
Tatsuhiko Nishino
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.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Publication of US20260009602A1 publication Critical patent/US20260009602A1/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0256—Arrangements for coupling connectors with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • 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

Definitions

  • the present disclosure relates to a heat exchanger.
  • a previously proposed heat exchanger includes a plurality of tubes, a first header tank and a second header tank.
  • the tubes conduct a refrigerant and are arranged in a first row and a second row.
  • the tubes in the first row and the tubes in the second row are exposed in the first header tank and the second header tank.
  • a longitudinal partition is provided in the first header tank to divide the first header tank along a longitudinal direction into a refrigerant inlet chamber, in which the tubes in the first row are exposed, and a refrigerant outlet chamber, in which the tubes in the second row are exposed.
  • a heat exchanger may include a primary header tank, a plurality of primary tubes, a primary turn tank, a secondary turn tank, a plurality of secondary tubes and a secondary header tank.
  • the primary header tank may be configured to receive a refrigerant in a superheated gas state from an upstream-side flow passage located on an upstream side of the heat exchanger in a flow direction of the refrigerant.
  • the plurality of primary tubes may be configured to receive the refrigerant distributed from the primary header tank.
  • the primary turn tank may be configured to receive the refrigerant from the plurality of primary tubes.
  • the secondary turn tank may be configured to receive the refrigerant from the primary turn tank.
  • the plurality of secondary tubes may be configured to receive the refrigerant distributed from the secondary turn tank.
  • the secondary header tank may be configured to receive the refrigerant in a subcooled liquid state from the plurality of secondary tubes and then output the refrigerant into a downstream-side flow passage located on a downstream side of the heat exchanger in the flow direction of the refrigerant.
  • An internal flow path which extends from the plurality of primary tubes to the plurality of secondary tubes via the primary turn tank and the secondary turn tank, may have a primary region and at least one secondary region that are arranged one after another in a stacking direction, in which the plurality of primary tubes are stacked and the plurality of secondary tubes are stacked.
  • a pressure loss of the primary region and a pressure loss of the at least one secondary region may be different from each other when a flow rate of the refrigerant in the primary region is the same as a flow rate of the refrigerant in the at least one secondary region.
  • FIG. 1 is a perspective view showing an overall structure of a heat exchanger according to a first embodiment.
  • FIG. 2 is a perspective view showing the heat exchanger illustrated in FIG. 1 in an exploded state.
  • FIG. 3 is a plan view showing the heat exchanger illustrated in FIG. 2 in a developed state.
  • FIG. 4 is a view showing (A) a cross-section taken along line IVA-IVA of FIG. 3 and (B) a cross-section taken along line IVB-IVB in FIG. 3 .
  • FIG. 5 is a p-h diagram in which a refrigeration cycle is illustrated.
  • FIG. 6 is a plan view showing a heat exchanger of a comparative example in a developed state.
  • FIG. 7 is a plan view showing the heat exchanger of the comparative example in the developed state.
  • FIG. 8 is a view showing (A) a cross-section of a structure of a secondary turn tank of the comparative example and (B) a cross-section of a structure of a primary turn tank of the comparative example.
  • FIG. 9 is a plan view showing a modification of the heat exchanger of the first embodiment in a developed state.
  • FIG. 10 is a plan view showing a heat exchanger of a second embodiment in a developed state.
  • FIG. 11 is a plan view showing a heat exchanger of a third embodiment in a developed state.
  • FIG. 12 is a view showing (A) a cross-section taken along line VIIIA-VIIIA of FIG. 11 and (B) a cross-section taken along line VIIIB-VIIIB in FIG. 11 .
  • FIG. 13 is a plan view showing a heat exchanger of a fourth embodiment in a developed state.
  • FIG. 14 is a view showing (A) a cross-section taken along line XA-XA of FIG. 13 and (B) a cross-section taken along line XB-XB in FIG. 13 .
  • FIG. 15 is a cross-sectional view showing a structure of a secondary turn tank of the heat exchanger of the fourth embodiment.
  • FIG. 16 is a plan view showing a heat exchanger of a fifth embodiment in a developed state.
  • FIG. 17 is a diagram showing examples of a tube used in the heat exchanger illustrated in FIG. 16 .
  • FIG. 18 is a plan view showing a heat exchanger of a sixth embodiment in a developed state.
  • FIG. 19 is a perspective view showing an overall structure of a heat exchanger of a seventh embodiment.
  • FIG. 20 is a cross-sectional perspective view of a turn tank illustrated in FIG. 19 .
  • FIG. 21 is a view showing (A) a cross-section taken along line XVIA-XVIA in FIG. 20 and (B) a cross-section taken along line XVIB-XVIB in FIG. 20 .
  • FIG. 22 is a cross-sectional view showing a modification of FIG. 21 .
  • FIG. 23 is a graph showing a relationship between Nsc/Nall and a left-right temperature difference ⁇ T of air blown out from the heat exchanger.
  • FIG. 24 is a graph showing a relationship between a total opening cross-sectional area AS of communication holes and a pressure loss PL of the refrigerant.
  • a previously proposed heat exchanger includes a plurality of tubes, a first header tank and a second header tank.
  • the tubes conduct a refrigerant and are arranged in a first row and a second row.
  • the tubes in the first row and the tubes in the second row are exposed in the first header tank and the second header tank.
  • a longitudinal partition is provided in the first header tank to divide the first header tank along a longitudinal direction into a refrigerant inlet chamber, in which the tubes in the first row are exposed, and a refrigerant outlet chamber, in which the tubes in the second row are exposed.
  • a superheated gas refrigerant flowing into the heat exchanger undergoes heat exchange, goes through a gas-liquid two-phase state, and flows out as a subcooled liquid refrigerant.
  • the superheated gas refrigerant flows into the refrigerant inlet chamber and is subjected to heat exchange while passing through the tubes in the first row, thereby becoming the refrigerant in the gas-liquid two-phase state.
  • the refrigerant is further subjected to heat exchange while passing through the tubes in the second row via the second header tank, and then the refrigerant reaches the refrigerant outlet chamber as the subcooled liquid refrigerant.
  • the tubes in the first row and the tubes in the second row are arranged on the upstream side and the downstream side, respectively, with respect to a flow direction of the airflow.
  • the tubes in the second row, through which the subcooled liquid refrigerant having the low temperature flows, and the tubes in the first row, through which the superheated gas refrigerant having the high temperature flows are arranged to overlap in the flow direction of the airflow so that the temperature of the air discharged from the condenser is adjusted to become uniform along the condenser.
  • the superheated gas refrigerant which flows into the refrigerant inlet chamber, is passively distributed along the longitudinal direction of the refrigerant inlet chamber and flows into the tubes in the first row. Therefore, when the longitudinal length of the refrigerant inlet chamber is increased, a pressure loss in the refrigerant inlet chamber increases, and a flow rate of a shortcut flow of the refrigerant near the inlet, where the superheated gas refrigerant flows into the refrigerant inlet chamber, is increased.
  • the amount of the superheated gas refrigerant, which reaches the side opposite to the inlet of the refrigerant inlet chamber, is decreased, and deterioration in the temperature distribution in a tube stacking direction, in which the tubes are stacked, is expected.
  • a heat exchanger that includes: a primary header tank that is configured to receive a refrigerant in a superheated gas state from an upstream-side flow passage located on an upstream side of the heat exchanger in a flow direction of the refrigerant; a plurality of primary tubes that are configured to receive the refrigerant distributed from the primary header tank; a primary turn tank that is configured to receive the refrigerant from the plurality of primary tubes; a secondary turn tank that is configured to receive the refrigerant from the primary turn tank; a plurality of secondary tubes that are configured to receive the refrigerant distributed from the secondary turn tank; and a secondary header tank that is configured to receive the refrigerant in a subcooled liquid state from the plurality of secondary tubes and then output the refrigerant into a downstream-side flow passage located on a downstream side of the heat exchanger in the flow direction of the refrigerant.
  • An internal flow path which extends from the plurality of primary tubes to the plurality of secondary tubes via the primary turn tank and the secondary turn tank, has a primary region and at least one secondary region that are arranged one after another in a stacking direction, in which the plurality of primary tubes are stacked and the plurality of secondary tubes are stacked.
  • a pressure loss of the primary region and a pressure loss of the at least one secondary region are different from each other when a flow rate of the refrigerant in the primary region is the same as a flow rate of the refrigerant in the at least one secondary region.
  • a heat exchanger 2 includes a primary header tank 21 , a primary core 22 , a primary turn tank 23 , a secondary turn tank 24 , a secondary core 25 and a secondary header tank 26 .
  • the heat exchanger 2 is configured to perform heat exchange between air, which serves as a first fluid, and a refrigerant, which serves as a second fluid.
  • the heat exchanger 2 is used, for example, as a condenser for heating a cabin of a vehicle.
  • the heat exchanger 2 serving as the condenser, is incorporated into a refrigeration cycle (not shown).
  • the heat exchanger 2 which is incorporated into the refrigeration cycle, is connected to an upstream-side flow passage, which is located on an upstream side of the heat exchanger 2 in a flow direction of the refrigerant, and a downstream-side flow passage of the refrigeration cycle, which is located on downstream side of the heat exchanger 2 in the flow direction of the refrigerant.
  • the primary header tank 21 has a flow inlet 211 .
  • the flow inlet 211 is configured to receive the refrigerant (serving as the second fluid) from the upstream-side flow passage of the refrigeration cycle.
  • the refrigerant which is supplied into the flow inlet 211 , flows into the primary header tank 21 .
  • the refrigerant, which is supplied into the primary header tank 21 flows into the primary core 22 .
  • the refrigerant, which is supplied into the primary core 22 exchanges heat with the air (serving as the first fluid) and flows into the primary turn tank 23 .
  • the refrigerant, which is supplied into the secondary turn tank 24 flows into the secondary core 25 .
  • the refrigerant, which is supplied into the secondary core 25 exchanges heat with the air (serving as the first fluid) and flows into the secondary header tank 26 .
  • the secondary header tank 26 has a flow outlet 261 .
  • the flow outlet 261 is configured to discharge the refrigerant into the downstream-side flow passage of the refrigeration cycle.
  • the refrigerant, which is supplied into the secondary header tank 26 is discharged from the flow outlet 261 into the downstream-side flow passage.
  • a direction, in which the air flows through the primary core 22 and the secondary core 25 is defined as an x-direction, and an x-axis is set along the x-direction.
  • a direction, which is perpendicular to the x-direction and is a longitudinal direction of each of the primary header tank 21 , the secondary header tank 26 , the primary turn tank 23 and the secondary turn tank 24 is defined as a y-direction, and a y-axis is set along the y-direction.
  • a direction, which is perpendicular to both the x-direction and the y-direction is defined as a z-direction.
  • the z-direction is directed from the lower side toward the upper side in FIG. 1 and is directed from the primary turn tank 23 toward the primary header tank 21 and is also directed from the secondary turn tank 24 toward the secondary header tank 26 . Furthermore, a z-axis is set along the z-direction. In the following description, the x-direction, the y-direction and the z-direction defined above are used. It should be noted that the z-direction is a direction from the lower side toward the upper side in FIG. 1 , and this direction does not necessarily correspond to the vertical direction in an actual installation.
  • the primary header tank 21 and the secondary header tank 26 may be disposed on the lower side in the vertical direction, and the primary turn tank 23 and the secondary turn tank 24 may be disposed on the upper side in the vertical direction.
  • FIG. 2 is a perspective view illustrating the inside of the heat exchanger 2 shown in FIG. 1 in an exploded manner.
  • FIG. 2 illustrates a state in which the primary header tank 21 , the primary core 22 and the primary turn tank 23 are separated from the secondary header tank 26 , the secondary core 25 and the secondary turn tank 24 , and are rotated 90 degrees about the Z-axis from the state shown in FIG. 1 .
  • the XYZ axes for the primary header tank 21 , the primary core 22 and the primary turn tank 23 are shown in the vicinity of the primary header tank 21 , the primary core 22 and the primary turn tank 23 .
  • the XYZ axes for the secondary header tank 26 , the secondary core 25 and the secondary turn tank 24 are shown in the vicinity of the secondary header tank 26 , the secondary core 25 and the secondary turn tank 24 .
  • the primary core 22 includes a plurality of primary tubes 221 , a plurality of primary fins 222 and a pair of side plates 223 .
  • Each of the primary tubes 221 is configured to conduct the second fluid, which is the refrigerant, through the inside thereof.
  • One end of each of the primary tubes 221 is in communication with the inside of the primary header tank 21 , and the other end of each of the primary tubes 221 is in communication with the inside of the primary turn tank 23 .
  • the primary tubes 221 and the primary fins 222 are alternately stacked.
  • the pair of side plates 223 are provided to hold the primary tubes 221 and the primary fins 222 , which are stacked in a stacking direction, between the pair of side plates 223 in the stacking direction.
  • the primary fins 222 are bent in a wavy shape.
  • the primary fins 222 form air flow passages through which the air (the first fluid) flows.
  • a refrigerant flow passage through which the refrigerant (the second fluid) flows is provided inside each primary tube 221 .
  • Each primary fin 222 is in contact with the adjacent primary tubes 221 and is configured to allow heat exchange therebetween. Accordingly, each primary fin 222 and the adjacent primary tubes 221 are configured to enable heat exchange between the air flowing along the primary fin 222 and the refrigerant flowing through the primary tubes 221 .
  • the primary turn tank 23 includes a partition wall 23 w .
  • the partition wall 23 w is a wall that contacts the secondary turn tank 24 .
  • the partition wall 23 w has a plurality of communication holes 23 f 1 , 23 f 2 , 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 , 23 r 1 , 23 r 2 which extend through the partition wall 23 w .
  • the communication holes 23 f 1 , 23 f 2 , 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 , 23 r 1 , 23 r 2 are configured to conduct the refrigerant therethrough.
  • All of the communication holes 23 f 1 , 23 f 2 , 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 , 23 r 1 , 23 r 2 have an identical circular shape. It should be noted that the communication holes 23 f 1 , 23 f 2 , 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 , 23 r 1 , 23 r 2 are all illustrated as having the identical circular shape merely for the sake of explanation, and the shape of the communication holes is not particularly limited. For example, the communication holes may take various shapes, including semicircular or rectangular shapes.
  • the communication holes 23 f 1 , 23 f 2 are included in a secondary region Tf.
  • the communication holes 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 are included in a primary region Tc.
  • the communication holes 23 r 1 , 23 r 2 are included in a secondary region Tr.
  • the number of the communication holes 23 f 1 , 23 f 2 formed in the secondary region Tf is smaller than the number of the communication holes 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 formed in the primary region Tc.
  • the number of the communication holes 23 r 1 , 23 r 2 formed in the secondary region Tr is smaller than the number of the communication holes 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 formed in the primary region Tc.
  • an opening ratio of the primary region Tc is larger than an opening ratio of the secondary region Tf and is also larger than an opening ratio of the secondary region Tr.
  • a pressure loss in each of the pair of secondary regions Tf, Tr is higher than a pressure loss in the primary region Tc, and the primary region Tc is interposed between the pair of secondary regions Tf, Tr.
  • the secondary turn tank 24 includes a partition wall 24 w .
  • the partition wall 24 w is a wall that contacts the primary turn tank 23 .
  • the partition wall 24 w has a plurality of communication holes 24 f 1 , 24 f 2 , 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 , 24 r 1 , 24 r 2 which extend through the partition wall 24 w .
  • the communication holes 24 f 1 , 24 f 2 , 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 , 24 r 1 , 24 r 2 are configured to conduct the refrigerant therethrough. All of the communication holes 24 f 1 , 24 f 2 , 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 , 24 r 1 , 24 r 2 have an identical circular shape.
  • the communication holes 24 f 1 , 24 f 2 are included in the secondary region Tf.
  • the communication holes 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 are included in the primary region Tc.
  • the communication holes 24 r 1 , 24 r 2 are included in the secondary region Tr.
  • the number of the communication holes 24 f 1 , 24 f 2 formed in the secondary region Tf is smaller than the number of the communication holes 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 formed in the primary region Tc.
  • the number of the communication holes 24 r 1 , 24 r 2 formed in the secondary region Tr is smaller than the number of the communication holes 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 formed in the primary region Tc.
  • an opening ratio of the primary region Tc is larger than an opening ratio of the secondary region Tf and is also larger than an opening ratio of the secondary region Tr.
  • a pressure loss in each of the pair of secondary regions Tf, Tr is higher than a pressure loss in the primary region Tc, and the primary region Tc is interposed between the pair of secondary regions Tf, Tr.
  • the communication hole 23 f 1 in the secondary region Tf is in communication with the communication hole 24 f 1 .
  • the communication hole 23 f 2 is in communication with the communication hole 24 f 2 .
  • the communication hole 23 c 1 is in communication with the communication hole 24 c 1 .
  • the communication hole 23 c 2 is in communication with the communication hole 24 c 2
  • the communication hole 23 c 3 is in communication with the communication hole 24 c 3
  • the communication hole 23 c 4 is in communication with the communication hole 24 c 4 .
  • the communication hole 23 r 1 is in communication with the communication hole 24 r 1
  • the communication hole 23 r 2 is in communication with the communication hole 24 r 2 .
  • a region of the secondary region Tf in which the communication holes 23 f 1 , 23 f 2 , 24 f 1 , 24 f 2 are provided, is referred to as a secondary outer region Tf 1
  • a remaining region of the secondary region Tf which is other than the secondary outer region Tf 1
  • a secondary inner region Tf 2 a region of the secondary region Tf
  • a region of the secondary region Tr in which the communication holes 23 r 1 , 23 r 2 , 24 r 1 , 24 r 2 are provided, is referred to as a secondary outer region Tr 1
  • a remaining region of the secondary region Tr which is other than the secondary outer region Tr 1
  • the secondary inner region Tf 2 is interposed between the secondary outer region Tf 1 and the primary region Tc
  • the secondary inner region Tr 2 is interposed between the secondary outer region Tr 1 and the primary region Tc.
  • the primary region Tc is interposed between the secondary region Tf and the secondary region Tr.
  • FIG. 3 is a plan view showing, in an unfolded planar form, the heat exchanger 2 that is shown in a perspective view in FIG. 2 .
  • the XYZ axes for the primary header tank 21 , the primary core 22 , and the primary turn tank 23 are shown in the vicinity of the primary header tank 21 , the primary core 22 and the primary turn tank 23 .
  • the XYZ axes for the secondary header tank 26 , the secondary core 25 and the secondary turn tank 24 are shown in the vicinity of the secondary header tank 26 , the secondary core 25 and the secondary turn tank 24 .
  • FIG. 4 is a cross-sectional view showing a cross-sectional structure taken along line IVA-IVA in FIG. 3 .
  • FIG. 4 is a cross-sectional view showing a cross-sectional structure taken along line IVB-IVB in FIG. 3 .
  • the entire interior of the primary turn tank 23 is continuous in the Y-direction, which is the longitudinal direction.
  • the entire interior of the secondary turn tank 24 is also continuous in the Y-direction, which is the longitudinal direction of the secondary turn tank 24 .
  • FIG. 5 is a p-h diagram in which pressure p is plotted on the vertical axis, and enthalpy h is plotted on the horizontal axis, and the refrigeration cycle is illustrated thereon.
  • a section of a curve, which is located on the left side of a critical point P 10 is referred to as a saturated liquid line M 11
  • another section of the curve, which is located on the right side of the critical point P 10 is referred to as a saturated vapor line M 12 .
  • the refrigeration cycle includes a compression process, a condensation process, an expansion process and an evaporation process.
  • the compression process is a process where the refrigerant gas evaporated in the evaporation process is compressed to become the superheated gas refrigerant which has the high temperature and the high pressure.
  • the condensation process is a process where heat is removed from the superheated gas refrigerant to convert it into a subcooled liquid refrigerant.
  • the expansion process is a process where the pressure of the subcooled liquid refrigerant, which has the high pressure, is reduced.
  • the evaporation process is a process where heat is applied to the liquid refrigerant to evaporate it.
  • an evaporator is a heat exchanger used in the evaporation process of the refrigeration cycle shown in FIG. 5 .
  • the refrigerant in a gas-liquid two-phase state which is generated in the expansion process, is supplied into the evaporator.
  • the refrigerant in the gas-liquid two-phase state exchanges heat with the air, whereby the state of the refrigerant changes as indicated by an arrow L 11 . That is, the refrigerant in the gas-liquid two-phase state absorbs heat from the air and changes into a gas-phase refrigerant, which remains at a low temperature and low pressure.
  • An intersection point, at which the arrow L 11 and the saturated vapor line M 12 intersect, indicates a point where the state of the refrigerant changes from the gas-liquid two-phase state to the gas state.
  • only two states of the refrigerant namely the gas-liquid two-phase state and the gas state, basically exist in the evaporator. Therefore, when attempting to equalize the temperature distribution of the air blown from the evaporator, it is generally sufficient to equalize the refrigerant flow rate in the region of the evaporator where the refrigerant is in the gas state, that is, the so-called superheated gas region.
  • the heat exchanger 2 of the present embodiment shown in FIGS. 1 to 4 functions as the condenser that performs the condensation process. Accordingly, the refrigerant, which becomes the gas state through the compression process and thereby has the high temperature and the high pressure, flows into the heat exchanger 2 . In the heat exchanger 2 , the refrigerant in the gas state exchanges heat with the air, whereby the state of the refrigerant changes as indicated by an arrow L 12 . That is, as the refrigerant in the gas state releases the heat to the air, the state of the refrigerant sequentially changes from the gas state to the gas-liquid two-phase state and then to the liquid state.
  • An intersection point, at which the arrow L 12 and the saturated vapor line M 12 intersect, indicates a point where the state of the refrigerant changes from the gas state to the gas-liquid two-phase state.
  • An intersection point, at which the arrow L 12 and the saturated vapor line M 11 intersect, indicates a point where the state of the refrigerant changes from the gas-liquid two-phase state to the liquid state.
  • the heat exchanger 2 of the present embodiment which functions as the condenser, has a practical difficulty in making the temperature distribution of the air uniform, as compared with the evaporator.
  • a superheated gas region is generated, for example, as indicated by a dotted line SH in FIG. 3 .
  • the refrigerant in the gas state which has a high flow velocity, flows into this superheated gas region SH through the flow inlet 211 . Therefore, in order to adjust the refrigerant flow rate in the superheated gas region, for example, by providing a throttle or the like in the primary header tank 21 , there is a concern that the pressure loss of the refrigerant in the gas state may increase.
  • the inability to employ the means such as the throttle or the like in the primary header tank 21 is also a factor that makes it difficult to achieve a uniform temperature distribution of the air in the heat exchanger 2 .
  • the heat exchanger 200 of the comparative example shown in FIGS. 6 and 7 has the same structure as the heat exchanger 2 shown in FIGS. 1 to 4 , except that a plurality of communication holes 231 are uniformly arranged along the partition wall 23 w of the primary turn tank 23 , and a plurality of communication holes 241 are uniformly arranged along the partition wall 24 w of the secondary turn tank 24 . It should be noted that, in the heat exchanger 200 shown in FIGS. 6 and 7 , elements identical to those of the heat exchanger 2 shown in FIGS. 1 to 4 are denoted by the same reference signs, and redundant descriptions are omitted.
  • the temperature distribution of the secondary core 25 which is disposed on the upstream side of the primary core 22 in the x-direction that is the flow direction of the air, changes according to the flow rate of the refrigerant.
  • the flow rate of the refrigerant, which flows through the near-side region 254 increases, whereas the flow rate of the refrigerant, which flows through the far-side region 255 , decreases. Therefore, since a subcooled liquid region SC 10 is formed in the far-side region 255 of the secondary core 25 , a temperature distribution is formed in the secondary core 25 such that the temperature in the far-side region 255 is excessively lower than the temperature in the near-side region 254 and the temperature in an intermediate region 256 .
  • the pressure loss of the refrigerant in the primary header tank 21 becomes small. Therefore, in the primary core 22 shown in FIG. 7 , the amount of the refrigerant, which flows as the shortcut flow through the near-side region 224 located adjacent to the flow inlet 211 , decreases, and in the primary header tank 21 , the amount of the refrigerant, which flows to the far-side that is far from the flow inlet 221 , increases due to inertia.
  • the flow rate of the refrigerant flowing through an intermediate region 226 which is located between the near-side region 224 and the far-side region 225 , becomes smaller compared to the near-side region 224 and the far-side region 225 .
  • the flow rate of the refrigerant, which flows through the near-side region 254 , and the flow rate of the refrigerant, which flows through the far-side region 255 increase, whereas the flow rate of the refrigerant, which flows through the intermediate region 256 , decreases.
  • a temperature distribution is formed in the secondary core 25 such that the temperature in the intermediate region 256 is excessively lower than the temperature in the near-side region 254 and the temperature in the far-side region 255 .
  • the temperature distribution which corresponds to the flow rate of the refrigerant, is formed.
  • a plurality of partition walls 243 are formed inside the secondary turn tank 24 to partition each of the plurality of communication holes 241
  • a plurality of partition walls 233 are also formed inside the primary turn tank 23 to partition each of the plurality of communication holes 231 .
  • the refrigerant is not pressure-equalized inside each of the turn tanks 23 , 24 . Accordingly, variations in the flow rate distribution of the refrigerant, as shown in FIGS. 6 and 7 , are more likely to become pronounced, and as a result, the temperature distribution in the secondary core 25 may further deteriorate.
  • the superheated gas refrigerant which flows into the primary header tank 21 , is distributed to the plurality of primary tubes 221 and flows toward the primary turn tank 23 .
  • a superheated gas region SH is formed in a region of the primary core 22 located adjacent to the primary header tank 21 .
  • the entire interior of each of the turn tanks 23 , 24 is continuous in the Y-direction, which is the longitudinal direction of the turn tank 23 , 24 . Accordingly, when the refrigerant flows into the primary turn tank 23 from the plurality of primary tubes 221 , the pressure of the refrigerant in the primary turn tank 23 tends to become equalized inside the primary turn tank 23 .
  • the flow rate of the refrigerant is controlled based on the arrangement of the communication holes in the primary turn tank 23 and the arrangement of the communication holes in the secondary turn tank 24
  • a change in the state of the refrigerant occurs due to a change in its density.
  • the heat exchanger 2 of the present embodiment is configured such that the pressure loss in the respective secondary regions Tf, Tr shown in FIG. 3 becomes higher than the pressure loss in the primary region Tc.
  • the refrigerant which flows into the primary turn tank 23 , flows into the secondary turn tank 24 through the communication holes 23 f 1 , 23 f 2 , 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 , 23 r 1 , 23 r 2 and the communication holes 24 f 1 , 24 f 2 , 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4 , 24 r 1 , 24 r 2 .
  • the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr decreases compared to the flow rate of the refrigerant, which flows through the primary region Tc, and a subcooled liquid region SC is formed in each of the secondary regions Tf, Tr.
  • a pair of subcooled liquid regions SC are formed on two opposite sides of the primary region Tc.
  • the primary region Tc which corresponds to the communication holes 23 c 1 , 23 c 2 , 23 c 3 , 23 c 4 , 24 c 1 , 24 c 2 , 24 c 3 , 24 c 4
  • the secondary outer region Tf 1 which corresponds to the communication holes 23 f 1 , 23 f 2 , 24 f 1 , 24 f 2
  • the secondary outer region Tr 1 which corresponds to the communication holes 23 r 1 , 23 r 2 , 24 r 1 , 24 r 2
  • the flow rate of the refrigerant in the respective secondary inner regions Tf 2 , Tr 2 becomes smaller than the flow rate of the refrigerant in each of the primary region Tc, the secondary outer region Tf 1 and the secondary outer region Tr 1 .
  • the subcooled liquid regions SC are formed in the portions of the secondary core 25 that respectively correspond to the secondary inner regions Tf 2 , Tr 2 .
  • the communication holes are formed in the turn tanks 23 , 24 as shown in FIG. 3 to control the flow rate of the refrigerant in the secondary core 25 , thereby intentionally forming the subcooled liquid regions SC in the secondary core 25 as illustrated in FIG. 3 .
  • the subcooled liquid regions SC tend to be formed in the portions of the secondary core 25 that respectively correspond to the secondary inner regions Tf 2 , Tr 2 . That is, variations in the flow rate of the refrigerant are less likely to cause deviation in the location of the subcooled liquid region shown in FIGS. 6 and 7 . Furthermore, in the heat exchanger 2 of the present embodiment, local deterioration in the temperature distribution, as shown in FIGS. 6 and 7 , is suppressed, and therefore the temperature distribution of the secondary core 25 in the Y-direction tends to become more uniform. As a result, the temperature of the air blown out from the heat exchanger 2 tends to become more uniform.
  • the refrigeration cycle is controlled so that the temperature of the refrigerant discharged from the flow outlet 261 reaches a target temperature.
  • the temperature distribution of the air blown out from, for example, the heat exchanger 200 of the comparative example shown in FIG. 7 tends to deteriorate.
  • the temperature of the intermediate region 256 may become excessively low compared to the temperatures of the near-side region 254 and the far-side region 255 .
  • the flows of the refrigerant that have passed through the near-side region 254 , the far-side region 255 and the intermediate region 256 , respectively, of the secondary core 25 are mixed in the secondary header tank 26 , and the mixed flow of the refrigerant is discharged from the flow outlet 261 . Accordingly, the temperature of the mixed flow of the refrigerant discharged from the flow outlet 261 becomes the average temperature of the flows of the refrigerant that have passed through the near-side region 254 , the far-side region 255 and the intermediate region 256 , respectively, of the secondary core 25 .
  • the temperature of the intermediate region 256 in the secondary core 25 of the heat exchanger 200 of the comparative example shown in FIG. 7 may reach approximately 30° C. when the temperature of the near-side region 254 and the temperature of the far-side region 255 are approximately 50° C.
  • the temperature distribution in the secondary core 25 tends to be more uniform compared to the heat exchanger 200 of the comparative examples shown in FIGS. 6 and 7 . Accordingly, even when the temperature of the refrigerant discharged from the flow outlet 261 is controlled to the target temperature, it is unlikely that regions exhibiting a large temperature difference will occur in the secondary core 25 .
  • the temperature of each of the subcooled liquid regions SC shown in FIG. 3 is approximately 38° C., while the temperatures of the other regions are approximately 40° C.
  • the temperature distribution in the secondary core 25 tends to be more uniform, the temperature distribution of the air blown out from the heat exchanger 200 also tends to be more uniform as a result.
  • the flow inlet 211 is formed at a center portion of the primary header tank 21 .
  • the flow inlet 211 is formed to extend in the z-direction from the center portion of the primary header tank 21 .
  • the flow outlet 261 is formed at a center portion of the secondary header tank 26 .
  • the flow inlet 211 is formed on a side surface (end surface) of the primary header tank 21
  • the flow outlet 261 is formed on a side surface (end surface) of the secondary header tank 26 .
  • the heat exchanger 2 of the present embodiment has a one-pass structure with a 1-1 turn configuration, in which the refrigerant flows in a single direction through the primary core 22 and the secondary core 25 .
  • a flow passage cross-sectional area can be increased compared to, for example, a heat exchanger in which the refrigerant flows back and forth multiple times in the primary core 22 and the secondary core 25 , thereby reducing the pressure loss of the refrigerant.
  • a bypass branch which bypasses the heat exchanger 2 during battery cooling, can be employed.
  • such a method is difficult to adopt because it increases the cost.
  • FIG. 9 shows a modification of the heat exchanger 2 .
  • the number of the communication holes in the secondary region Tf is smaller than the number of the communication holes in the secondary region Tr.
  • the number of the communication holes in the secondary region Tr is smaller than the number of the communication holes in the primary region Tc.
  • FIG. 10 is a plan view corresponding to FIG. 3 , showing the heat exchanger 2 A.
  • the heat exchanger 2 A is a modified version of the heat exchanger 2 , in which the primary turn tank 23 and the secondary turn tank 24 are replaced with a primary turn tank 23 A and a secondary turn tank 24 A.
  • the primary turn tank 23 A includes a partition wall 23 w A.
  • the partition wall 23 w A is a wall that contacts the secondary turn tank 24 A.
  • the partition wall 23 w A has a plurality of communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A, 23 c 1 A, 23 c 2 A, 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A.
  • the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A, 23 c 1 A, 23 c 2 A, 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A are configured to conduct the refrigerant therethrough.
  • the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A, 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A respectively have an identical circular shape.
  • the communication holes 23 c 1 A, 23 c 2 A are openings, each of which has a larger cross-sectional area than the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A, 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A, and the communication holes 23 c 1 A, 23 c 2 A respectively have, for example, an elliptical shape.
  • each of the communication holes 23 c 1 A, 23 c 2 A only needs to be an opening having a larger cross-sectional area than the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A, 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A.
  • the elliptical shape of the communication holes 23 c 1 A, 23 c 2 A is merely an example, and various shapes may be adopted, including, for example, a semi-elliptical shape or a rectangular shape.
  • the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A are included in the secondary region Tf.
  • the communication holes 23 c 1 A, 23 c 2 A are included in the primary region Tc.
  • the communication holes 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A are included in the secondary region Tr.
  • a total opening cross-sectional area of the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A formed in the secondary region Tf is smaller than a total opening cross-sectional area of the communication holes 23 c 1 A, 23 c 2 A formed in the primary region Tc.
  • a total opening cross-sectional area of the communication holes 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A formed in the secondary region Tr is smaller than the total opening cross-sectional area of the communication holes 23 c 1 A, 23 c 2 A formed in the primary region Tc.
  • an opening ratio of the primary region Tc is larger than an opening ratio of the secondary region Tf and is also larger than an opening ratio of the secondary region Tr.
  • a pressure loss in each of the pair of secondary regions Tf, Tr is higher than a pressure loss in the primary region Tc, and the primary region Tc is interposed between the pair of secondary regions Tf, Tr.
  • the secondary turn tank 24 A includes a partition wall 24 w A.
  • the partition wall 24 w A is a wall that contacts the primary turn tank 23 A.
  • the partition wall 24 w A has a plurality of communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A, 24 c 1 A, 24 c 2 A, 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A.
  • the communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A, 24 c 1 A, 24 c 2 A, 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A are configured to conduct the refrigerant therethrough.
  • the communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A, 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A respectively have an identical circular shape.
  • the communication holes 24 c 1 A, 24 c 2 A are openings, each of which has a larger cross-sectional area than the communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A, 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A, and have, for example, an elliptical shape.
  • the communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A are included in the secondary region Tf.
  • the communication holes 24 c 1 A, 24 c 2 A are included in the primary region Tc.
  • the communication holes 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A are included in the secondary region Tr.
  • a total opening cross-sectional area of the communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A formed in the secondary region Tf is smaller than a total opening cross-sectional area of the communication holes 24 c 1 A, 24 c 2 A formed in the primary region Tc.
  • a total opening cross-sectional area of the communication holes 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A formed in the secondary region Tr is smaller than the total opening cross-sectional area of the communication holes 24 c 1 A, 24 c 2 A formed in the primary region Tc.
  • an opening ratio of the primary region Tc is larger than an opening ratio of the secondary region Tf and is also larger than an opening ratio of the secondary region Tr.
  • a pressure loss in each of the pair of secondary regions Tf, Tr is higher than a pressure loss in the primary region Tc, and the primary region Tc is interposed between the pair of secondary regions Tf, Tr.
  • the communication hole 23 f 1 A in the secondary region Tf is in communication with the communication hole 24 f 1 A.
  • the communication hole 23 f 2 A is in communication with the communication hole 24 f 2 A
  • the communication hole 23 f 3 A is in communication with the communication hole 24 f 3 A
  • the communication hole 23 f 4 A is in communication with the communication hole 24 f 4 A.
  • the communication hole 23 c 1 A is in communication with the communication hole 24 c 1 A.
  • the communication hole 23 c 2 A is in communication with the communication hole 24 c 2 A.
  • the communication hole 23 r 1 A is in communication with the communication hole 24 r 1 A
  • the communication hole 23 r 2 A is in communication with the communication hole 24 r 2 A
  • the communication hole 23 r 3 A is in communication with the communication hole 24 r 3 A
  • the communication hole 23 r 4 A is in communication with the communication hole 24 r 4 A.
  • the superheated gas refrigerant which flows into the primary header tank 21 , is distributed to the plurality of primary tubes 221 and flows toward the primary turn tank 23 A. As a result of this flow, a superheated gas region SH is formed in a region of the primary core 22 located adjacent to the primary header tank 21 .
  • the refrigerant which flows into the primary turn tank 23 A, flows into the secondary turn tank 24 A via the communication holes 23 f 1 A, 23 f 2 A, 23 f 3 A, 23 f 4 A, 23 c 1 A, 23 c 2 A, 23 r 1 A, 23 r 2 A, 23 r 3 A, 23 r 4 A and the communication holes 24 f 1 A, 24 f 2 A, 24 f 3 A, 24 f 4 A, 24 c 1 A, 24 c 2 A, 24 r 1 A, 24 r 2 A, 24 r 3 A, 24 r 4 A.
  • the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr decreases compared to the flow rate of the refrigerant, which flows through the primary region Tc, and a subcooled liquid region SC is formed in each of the secondary regions Tf, Tr.
  • a pair of subcooled liquid regions SC are formed on two opposite sides of the primary region Tc.
  • FIG. 11 is a plan view corresponding to FIG. 3 , showing the heat exchanger 2 B.
  • the heat exchanger 2 B is a modified version of the heat exchanger 2 , in which the primary turn tank 23 and the secondary turn tank 24 are replaced with a primary turn tank 23 B and a secondary turn tank 24 B.
  • the primary turn tank 23 B includes a partition wall 23 w B.
  • the partition wall 23 w B is a wall that contacts the secondary turn tank 24 B.
  • the partition wall 23 w B has a plurality of communication holes 231 which extend through the partition wall 23 w B.
  • the number of the communication holes 231 is, for example, fourteen.
  • the communication holes 231 are configured to conduct the refrigerant therethrough. All of the communication holes 231 have an identical circular shape. It should be noted that the communication holes 231 are all illustrated as having the identical circular shape merely for the sake of explanation, and the shape of the communication holes is not particularly limited. For example, the communication holes may take various shapes, including semicircular or rectangular shapes.
  • an opening ratio of the primary region Tc is the same as an opening ratio of the secondary region Tf and is also the same as an opening ratio of the secondary region Tr.
  • the primary turn tank 23 B includes a projection 232 a and a projection 232 b .
  • the projection 232 a is formed in the secondary region Tf.
  • the projection 232 b is formed in the secondary region Tr.
  • the secondary turn tank 24 B includes a partition wall 24 w B.
  • the partition wall 24 w B is a wall that contacts the primary turn tank 23 B.
  • the partition wall 24 w B has a plurality of communication holes 241 which extend through the partition wall 24 w B.
  • the number of the communication holes 241 is, for example, fourteen.
  • the communication holes 241 are configured to conduct the refrigerant therethrough. All of the communication holes 241 have an identical circular shape.
  • an opening ratio of the primary region Tc is the same as an opening ratio of the secondary region Tf and is also the same as an opening ratio of the secondary region Tr.
  • the secondary turn tank 24 B includes a projection 242 a and a projection 242 b .
  • the projection 242 a is formed in the secondary region Tf.
  • the projection 242 b is formed in the secondary region Tr.
  • FIG. 12 is a cross-sectional view taken along line VIIIA-VIIIA of the secondary turn tank 24 B in FIG. 11 .
  • FIG. 12 is a cross-sectional view taken along line VIIIB-VIIIB of the secondary turn tank 24 B in FIG. 11 .
  • the projection 242 a locally reduces the internal volume of the secondary turn tank 24 B.
  • a pressure loss in each of the pair of secondary regions Tf, Tr is higher than a pressure loss in the primary region Tc, and the primary region Tc is interposed between the pair of secondary regions Tf, Tr.
  • the refrigerant which flows into the primary turn tank 23 B, flows into the secondary turn tank 24 B via the communication holes 231 and the communication holes 241 . Since a pressure loss in each of the secondary regions Tf, Tr, in which the projections 232 a , 232 b , 242 a , 242 b are formed, becomes higher than a pressure loss in the primary region Tc, the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr, decreases compared to the flow rate of the refrigerant, which flows through the primary region Tc, and a subcooled liquid region SC is formed in each of the secondary regions Tf, Tr. A pair of subcooled liquid regions SC are formed on two opposite sides of the primary region Tc.
  • FIG. 13 is a plan view corresponding to FIG. 3 , showing the heat exchanger 2 C.
  • the heat exchanger 2 C is a modified version of the heat exchanger 2 , in which the primary turn tank 23 and the secondary turn tank 24 are replaced with a primary turn tank 23 C and a secondary turn tank 24 C.
  • the primary turn tank 23 C includes a flow restrictor 232 C instead of the projections 232 a , 232 b of the primary turn tank 23 B described with reference to FIG. 11 .
  • the secondary turn tank 24 C includes a flow restrictor 242 C instead of the projections 242 a , 242 b of the secondary turn tank 24 B described with reference to FIG. 11 .
  • FIG. 14 is a cross-sectional view taken along line XA-XA of the secondary turn tank 24 C in FIG. 13 .
  • (B) of FIG. 14 is a cross-sectional view taken along line XB-XB of the secondary turn tank 24 C in FIG. 13 .
  • the flow restrictor 242 C is a member shaped in a flat plate form that is perpendicular to the Y-direction, and the flow restrictor 242 C has a through-hole 242 Ca at its center.
  • the flow restrictor 242 C locally reduces the internal volume of the secondary turn tank 24 B.
  • the superheated gas refrigerant which flows into the primary header tank 21 , is distributed to the plurality of primary tubes 221 and flows toward the primary turn tank 23 C. As a result of this flow, a superheated gas region SH is formed in a region of the primary core 22 located adjacent to the primary header tank 21 .
  • the refrigerant which flows into the primary turn tank 23 C, flows into the secondary turn tank 24 C via the communication holes 231 and the communication holes 241 . Since the flow restrictors 232 C, 242 C are provided, the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr, decreases relative to the flow rate of the refrigerant, which flows through the primary region Tc, and a subcooled liquid region SC is formed in each of the secondary regions Tf, Tr. A pair of subcooled liquid regions SC are formed on two opposite sides of the primary region Tc.
  • the secondary turn tank 24 C of the heat exchanger 2 C adopts a structure shown in FIG. 15 .
  • a plurality of flow restrictors 244 C, 245 C, 246 C, 247 C are formed in the secondary turn tank 24 C.
  • the flow restrictor 244 C is formed between the secondary outer region Tf 1 and the secondary inner region Tf 2 .
  • the flow restrictor 245 C is formed between the secondary inner region Tf 2 and the primary region Tc.
  • the flow restrictor 246 C is formed between the primary region Tc and the secondary inner region Tr 2 .
  • the flow restrictor 247 C is formed between the secondary inner region Tr 2 and the secondary outer region Tr 1 .
  • FIG. 16 is a plan view corresponding to FIG. 3 , showing the heat exchanger 2 D.
  • the heat exchanger 2 D is a modified version of the heat exchanger 2 , in which the primary turn tank 23 and the secondary turn tank 24 are replaced with a primary turn tank 23 D and a secondary turn tank 24 D.
  • the heat exchanger 2 D is the modified version of the heat exchanger 2 , in which the primary tubes 221 are replaced with a plurality of types of primary tubes 221 Df, 221 Dc, 221 Dr.
  • the heat exchanger 2 D is the modified version of the heat exchanger 2 , in which the secondary tubes 251 are replaced with a plurality of types of secondary tubes 251 Df, 251 Dc, 251 Dr.
  • the primary turn tank 23 D is obtained by removing the projections 232 a , 232 b from the primary turn tank 23 B described with reference to FIG. 11 .
  • the secondary turn tank 24 D is obtained by removing the projections 242 a , 242 b from the secondary turn tank 24 B described with reference to FIG. 11 .
  • the primary tubes 221 Df and the secondary tubes 251 Df are provided in the secondary region Tf.
  • the primary tubes 221 Dc and the secondary tubes 251 Dc are provided in the primary region Tc.
  • the primary tubes 221 Dr and the secondary tubes 251 Dr are provided in the secondary region Tr.
  • An internal flow passage of each of the primary tubes 221 Df is narrower (i.e., with a smaller cross-sectional area) than an internal flow passage of each of the primary tubes 221 Dc.
  • An internal flow passage of each of the primary tubes 221 Dr is narrower (i.e., with a smaller cross-sectional area) than the internal flow passage of each of the primary tubes 221 Dc.
  • An internal flow passage of each of the secondary tubes 251 Df is narrower (i.e., with a smaller cross-sectional area) than an internal flow passage of each of the secondary tubes 251 Dc.
  • An internal flow passage of each of the secondary tubes 251 Dr is narrower (i.e., with a smaller cross-sectional area) than the internal flow passage of each of the secondary tubes 251 Dc.
  • FIG. 17 illustrates four examples of the internal flow passage configurations of the primary tubes 221 Df, 221 Dc, 221 Dr and of the secondary tubes 251 Df, 251 Dc, 251 Dr.
  • Examples 1 and 2 are examples in which the tubes are formed by extrusion molding.
  • the internal flow passage of the primary tube 221 Dc and the internal flow passage of the secondary tube 251 Dc respectively have an identical shape.
  • the internal flow passage of the primary tube 221 Df and the internal flow passage of the secondary tube 251 Df also respectively have an identical shape and are narrower (i.e., with a smaller cross-sectional area) than those of the primary tube 221 Dc and the secondary tube 251 Dc.
  • the internal flow passage of the primary tube 221 Dr and the internal flow passage of the secondary tube 251 Dr also respectively have an identical shape, and are narrower (i.e., with a smaller cross-sectional area) than those of the primary tube 221 Dc and the secondary tube 251 Dc.
  • Example 2 the internal flow passage of the primary tube 221 Dc and the internal flow passage of the secondary tube 251 Dc respectively have an identical shape.
  • Example 2 among a plurality of sub-passages of the internal flow passage of each of the primary tube 221 Df and the secondary tube 251 Df, some sub-passages, which have the same shape as those of the primary tube 221 Dc and the secondary tube 251 Dc, are arranged at a center region, and the other sub-passages that are narrower than those in the center region are arranged on both sides of the center region.
  • some sub-passages which have the same shape as those of the primary tube 221 Dc and the secondary tube 251 Dc, are arranged at a center region, and the other sub-passages that are narrower than those in the center region are arranged on both sides of the center region.
  • Examples 3 and 4 are examples of tubes of an inner-fin type.
  • Example 3 a plurality of wavy fin segments of the inner fin of each of the primary tube 221 Dc and the secondary tube 251 Dc are arranged at an equal pitch.
  • a plurality of wavy fin segments of the inner fin of each of the primary tube 221 Df and the secondary tube 251 Df are also arranged at an equal pitch, and this pitch is smaller than that of the primary tube 221 Dc and the secondary tube 251 Dc.
  • the internal flow passages of the primary tube 221 Df and the secondary tube 251 Df are narrower (i.e., with a smaller cross-sectional area) than those of the primary tube 221 Dc and the secondary tube 251 Dc.
  • the internal flow passages of the primary tube 221 Dr and the secondary tube 251 Dr are also narrower (i.e., with a smaller cross-sectional area) than those of the primary tube 221 Dc and the secondary tube 251 Dc.
  • Example 4 a plurality of wavy fin segments of the inner fin of each of the primary tube 221 Dc and the secondary tube 251 Dc are arranged at an equal pitch.
  • Example 4 among a plurality of wavy fin segments of the inner fin of each of the primary tube 221 Df and the secondary tube 251 Df, some wavy fin segments having the same shape as those of the wavy fin segments of the primary tube 221 Dc and the secondary tube 251 Dc are arranged in a center region, and the other fin segments having a smaller pitch than the pitch in the center region are arranged on two opposite sides of the center region.
  • the internal flow passages of the primary tube 221 Df and the secondary tube 251 Df are narrower (i.e., with a smaller cross-sectional area) than those of the primary tube 221 Dc and the secondary tube 251 Dc.
  • the internal flow passages of the primary tube 221 Dr and the secondary tube 251 Dr are also narrower (i.e., with a smaller cross-sectional area) than those of the primary tube 221 Dc and the secondary tube 251 Dc.
  • the superheated gas refrigerant which flows into the primary header tank 21 , is distributed to the plurality of primary tubes 221 Df, 221 Dc, 221 Dr and flows toward the primary turn tank 23 D. As a result of this flow, a superheated gas region SH is formed in a region of the primary core 22 located adjacent to the primary header tank 21 .
  • the refrigerant which flows into the primary turn tank 23 D, flows into the secondary turn tank 24 D via the communication holes 231 and the communication holes 241 .
  • the refrigerant, which flows into the secondary turn tank 24 D, is distributed to the secondary tubes 251 Df, 251 Dc, 251 Dr and flows toward the secondary header tank 26 .
  • each of the primary tubes 221 Df, 221 Dr is narrower than that of the primary tube 221 Dc
  • the internal flow passage of each of the secondary tubes 251 Df, 251 Dr is narrower than that of the secondary tube 251 Dc. Therefore, the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr, decreases relative to the flow rate of the refrigerant, which flows through the primary region Tc, and a subcooled liquid region SC is formed in each of the secondary regions Tf, Tr.
  • a pair of subcooled liquid regions SC are formed on two opposite sides of the primary region Tc.
  • FIG. 18 is a plan view corresponding to FIG. 3 , showing the heat exchanger 2 E.
  • the heat exchanger 2 E is a modified version of the heat exchanger 2 , in which the primary turn tank 23 and the secondary turn tank 24 are replaced with the primary turn tank 23 D and the secondary turn tank 24 D. Since the primary turn tank 23 D and the secondary turn tank 24 D are previously described with reference to FIG. 16 , the description of the primary turn tank 23 D and the secondary turn tank 24 D is omitted.
  • the heat exchanger 2 E differs from the heat exchanger 2 in that the intervals of the primary tubes 221 and the secondary tubes 251 are changed.
  • the intervals of the primary tubes 221 and the secondary tubes 251 which are disposed in the primary region Tc, are reduced compared to the intervals of the primary tubes 221 and the secondary tubes 251 , which are disposed in the secondary regions Tf, Tr.
  • the intervals of the primary tubes 221 and the secondary tubes 251 which are disposed in the secondary regions Tf, Tr, are increased compared to the intervals of the primary tubes 221 and the secondary tubes 251 , which are disposed in the primary region Tc.
  • the primary fins 222 Ec and the secondary fins 252 Ec which are disposed in the primary region Tc, have smaller widths in the axial direction of the Y-axis than the primary fins 222 Ef, 222 Er and the secondary fins 252 Ef, 252 Er, which are disposed in the secondary regions Tf, Tr.
  • the superheated gas refrigerant which flows into the primary header tank 21 , is distributed to the plurality of primary tubes 221 and flows toward the primary turn tank 23 D. As a result of this flow, a superheated gas region SH is formed in a region of the primary core 22 located adjacent to the primary header tank 21 .
  • the refrigerant which flows into the primary turn tank 23 D, flows into the secondary turn tank 24 D via the communication holes 231 and the communication holes 241 .
  • the refrigerant, which flows into the secondary turn tank 24 D, is distributed to the secondary tubes 251 and flows toward the secondary header tank 26 .
  • the intervals of the primary tubes 221 , which are disposed in the secondary regions Tf, Tr, are increased compared to the intervals of the primary tubes 221 , which are disposed in the primary region Tc, and the intervals of the secondary tubes 251 , which are disposed in the secondary regions Tf, Tr, are increased compared to the intervals of the secondary tubes 251 , which are disposed in the primary region Tc. Therefore, the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr, decreases relative to the flow rate of the refrigerant, which flows through the primary region Tc, and a subcooled liquid region SC is formed in each of the secondary regions Tf, Tr. A pair of subcooled liquid regions SC are formed on two opposite sides of the primary region Tc.
  • FIG. 19 is a perspective view corresponding to FIG. 1 , showing the heat exchanger 2 F.
  • the heat exchanger 2 F differs from the heat exchanger 2 in that the primary turn tank 23 and the secondary turn tank 24 are replaced with a single turn tank 23 F.
  • the turn tank 23 F includes a primary turn tank portion (a primary turn tank) 23 Ff and a secondary turn tank portion (a secondary turn tank) 23 Fs.
  • the primary turn tank portion 23 Ff corresponds to the primary turn tank 23 .
  • the secondary turn tank portion 23 Fs corresponds to the secondary turn tank 24 .
  • the turn tank 23 F is a unitary turn tank in which the primary turn tank portion 23 Ff and the secondary turn tank portion 23 Fs are integrated.
  • the turn tank 23 F includes a plurality of communicating portions that connect between the primary turn tank portion 23 Ff and the secondary turn tank portion 23 Fs and are configured to conduct the refrigerant between the primary turn tank portion 23 Ff and the secondary turn tank portion 23 Fs.
  • FIG. 20 is a perspective cross-sectional view showing a cross section where the communicating portions 231 F are not provided.
  • the turn tank 23 F is formed by combining a first portion 23 Fa and a second portion 23 Fb together.
  • the first portion 23 Fa includes a coupling portion 23 Fa 1 , a wall portion 23 Fa 2 , a wall portion 23 Fa 3 , a wall portion 23 Fa 4 and a wall portion 23 Fa 5 .
  • the coupling portion 23 Fa 1 and the wall portions 23 Fa 2 , 23 Fa 3 are respectively shaped in a flat plate form that extends in the y-direction and are arranged to have an x-y plane.
  • the coupling portion 23 Fa 1 is held between the wall portion 23 Fa 2 and the wall portion 23 Fa 3 in the x-direction.
  • the wall portion 23 Fa 2 and the wall portion 23 Fa 3 are displaced from the coupling portion 23 Fa 1 toward a minus side in the z-direction.
  • the wall portions 23 Fa 4 , 23 Fa 5 are respectively shaped in a flat plate form that extends in the y-direction and are arranged to have a y-z plane.
  • the wall portion 23 Fa 4 is joined to and is located on a side of the wall portion 23 Fa 2 , which is opposite to the coupling portion 23 Fa 1 .
  • the wall portion 23 Fa 5 is joined to and is located on a side of the wall portion 23 Fa 3 , which is opposite to the coupling portion 23 Fa 1 .
  • the second portion 23 Fb includes a coupling portion 23 Fb 1 , a wall portion 23 Fb 2 , a wall portion 23 Fb 3 , a wall portion 23 Fb 4 and a wall portion 23 Fb 5 .
  • the coupling portion 23 Fb 1 and the wall portions 23 Fb 2 , 23 Fb 3 are respectively shaped in a flat plate form that extends in the y-direction and are arranged to have the x-y plane.
  • the coupling portion 23 Fb 1 is held between the wall portion 23 Fb 2 and the wall portion 23 Fb 3 in the x-direction.
  • the wall portion 23 Fb 2 and the wall portion 23 Fb 3 are displaced from the coupling portion 23 Fb 1 toward a positive side in the z-direction.
  • the wall portions 23 Fb 4 , 23 Fb 5 are respectively shaped in a flat plate form that extends in the y-direction and are arranged to have the y-z plane.
  • the wall portion 23 Fb 4 is joined to and is located on a side of the wall portion 23 Fb 2 , which is opposite to the coupling portion 23 Fb 1 .
  • the wall portion 23 Fb 5 is joined to and is located on a side of the wall portion 23 Fb 3 , which is opposite to the coupling portion 23 Fb 1 .
  • the turn tank 23 F is formed.
  • the primary turn tank portion 23 Ff is mainly formed by the wall portions 23 Fa 3 , 23 Fa 5 , 23 Fb 3 , 23 Fb 5 .
  • the secondary turn tank portion 23 Fs is mainly formed by the wall portions 23 Fa 2 , 23 Fa 4 , 23 Fb 2 , 23 Fb 4 .
  • a plurality of communicating portions 231 F are provided so as to connect and communicate between the primary turn tank portion 23 Ff and the secondary turn tank portion 23 Fs.
  • FIG. 21 shows a cross-section taken along line XVIA-XVIA in FIG. 20 , showing the communicating portion 231 F.
  • This cross-section is a cross-section taken along line XVIA-XVIA in a z-x plane in FIG. 20 .
  • (B) of FIG. 21 shows a XVIB-XVIB cross-section of the communicating portion 231 F in FIG. 20 .
  • the XVIB-XVIB cross-section is a cross-section taken along line XVIB-XVIB in the y-z plane.
  • each of the communicating portions 231 F has an outer shell 231 Fa.
  • the outer shell 231 Fa is shaped in a semicylindrical form.
  • a communication hole 231 Fb is formed between the outer shell 231 Fa and the coupling portion 23 Fa 1 .
  • Each of the communication holes 231 Fb is formed to communicate between the primary turn tank portion 23 Ff and the secondary turn tank portion 23 Fs.
  • the arrangement of the communication holes 231 Fb may be the same as the arrangement of the communication holes described in the first to sixth embodiments.
  • the primary region Tc and the secondary regions Tf, Tr can be formed in a manner similar to any one of the first to sixth embodiments.
  • the flow passage cross-sectional area of the communication hole 231 Fb can be reduced by a method such as partially compressing the inside of the outer shell 231 Fa. Examples of how to reduce the flow passage cross-sectional area will be described with reference to FIG. 22 .
  • the outer shell 231 Fa is compressed from above to form an outer shell 231 FAa, which defines a communication hole 231 FAb having a reduced cross-sectional area.
  • the outer shell 231 Fa is further compressed from above and from both lateral sides to form an outer shell 231 FBa, which defines a communication hole 231 FBb having a further reduced cross-sectional area.
  • a heat exchanger 2 , 2 A, 2 B, 2 C, 2 D, 2 E comprising:
  • the primary region Tc and the at least one secondary region Tf, Tr are arranged one after another in the axial direction of the y-axis, i.e., the stacking direction, in which the plurality of primary tubes 221 , 221 Df, 221 Dc, 221 Dr are stacked and the plurality of secondary tubes 251 , 251 Df, 251 Dc, 251 Dr are stacked, it is possible to adjust the flow rate of the refrigerant in a direction that intersects a direction in which air flows. For example, by suppressing the flow rate of the refrigerant to promote heat exchange of the refrigerant, it is possible to form a subcooled liquid region at a desired location, thereby maintaining a favorable temperature distribution.
  • the subcooled liquid region can be formed on each side, thereby maintaining the favorable temperature distribution between the left and right sides.
  • the flow rate of the refrigerant, which flows through each of the secondary regions Tf, Tr decreases relative to the flow rate of the refrigerant, which flows through the primary region Tc, and subcooled liquid regions SC are formed in the secondary regions Tf, Tr, respectively. Since the subcooled liquid regions SC are formed in correspondence with the secondary regions Tf, Tr, the pair of subcooled liquid regions Sc are formed on the two opposite sides, respectively, of the primary region Tc.
  • the secondary region Tf is located adjacent to a region where the refrigerant flows into the primary header tank 21 , even when the flow rate of the refrigerant, which flows into the primary header tank 21 , is low, it is possible to suppress an excessive flow of the refrigerant toward the secondary region Tf which flows as the shortcut flow.
  • the secondary region Tr is formed on the side opposite to the side where the refrigerant flows into the primary header tank 21 , even when the flow rate of the refrigerant, which flows into the primary header tank 21 , is high, it is possible to suppress an excessive flow of the refrigerant toward the secondary region Tr.
  • the refrigerant is distributed uniformly to the respective tubes.
  • a duct is provided on an upstream side of the heat exchanger 2 , 2 A, 2 B, 2 C, 2 D, 2 E, and the duct has a rectangular shape, the air tends to flow more strongly near the center of the heat exchanger 2 , 2 A, 2 B, 2 C, 2 D, 2 E.
  • the amount of heat exchange in the primary region Tc becomes larger than the amount of heat exchange in each of the secondary regions Tf, Tr, resulting in a subcooled state in the primary region Tc.
  • a pressure corresponding to ⁇ gh is required to lift the heavier liquid in the primary region Tc.
  • a certain pressure loss is needed.
  • the pressure loss in each of the secondary regions Tf, Tr is increased to allow the refrigerant to flow into the primary region Tc.
  • the configuration, in which the pair of secondary regions Tf, Tr are provided on the two opposite sides of the primary region Tc, is merely one example, and the secondary regions Tf, Tr may be provided in any manner as long as the secondary regions Tf, Tr are arranged alongside the primary region Tc in the axial direction of the Y-axis.
  • the heat exchanger 2 , 2 A, 2 B according to aspect 1 or 2, wherein the primary region Tc and the at least one secondary region Tf, Tr are formed in at least one of the primary turn tank 23 , 23 A, 23 B or the secondary turn tank 24 , 24 A, 24 B.
  • the primary region Tc and the at least one secondary region Tf, Tr are provided in the at least one of the primary turn tank 23 , 23 A, 23 B or the secondary turn tank 24 , 24 A, 24 B, the primary region Tc and the at least one secondary region Tf, Tr can be formed easily without requiring any special tubes.
  • the primary region Tc and the at least one secondary region Tf, Tr are formed in the partition wall 23 w , 23 w A, 24 w , 24 w A, the primary region Tc and the at least one secondary region Tf, Tr can be easily formed by processing only the partition wall 23 w , 23 w A, 24 w , 24 w A.
  • the primary region Tc and the at least one secondary region Tf, Tr can be easily formed by setting different numbers of communication holes in the primary region Tc and in the at least one secondary region Tf, Tr in the partition wall 23 w , 24 w . Furthermore, by adjusting the numbers of the communication holes formed in the partition wall 23 w , 24 w , a difference in the flow rate of the refrigerant can also be adjusted, so that the formation position and the formation manner of the at least one secondary region Tf, Tr relative to the primary region Tc can be more easily adjusted.
  • the case where the virtual communication holes are uniformly arranged in the primary region Tc and the pair of secondary regions Tf, Tr refers to, for example, a state similar to the arrangement of the communication holes 241 illustrated in FIG. 16 .
  • a state in which the communication holes are actually arranged in the primary region Tc and the pair of secondary regions Tf, Tr, and which also satisfies the condition of aspect 5, refers to, for example, a state similar to the state illustrated in FIG. 3 .
  • Nall is 14.
  • the one of the plurality of communication holes located at the outer end of the primary region Tc is the communication hole 23 c 1 , 24 c 1 or the communication hole 23 c 4 , 24 c 4 .
  • the another one of the plurality of communication holes located at the inner end of the one of the pair of secondary regions Tf, Tr is the communication hole 23 f 2 , 24 f 2 or the communication hole 23 r 1 , 24 r 1 . If the communication holes were uniformly arranged between the communication hole 23 c 1 and the communication hole 23 f 2 , the number of these communication holes would be two. Similarly, if the communication holes were uniformly arranged between the communication hole 23 c 4 and the communication hole 23 r 1 , the number of these communication holes would be two.
  • the outer end of the primary region Tc refers, in other words, to an end portion of the primary region Tc on the secondary region Tf side or an end portion of the primary region Tc on the secondary region Tr side.
  • the inner end of the secondary region Tf refers, in other words, to an end portion of the secondary region Tf on the primary region Tc side, or an end portion of the secondary region Tr on the primary region Tc side.
  • FIGS. 23 and 24 are graphs respectively showing results of experiments conducted by the inventors of the present application.
  • a graph shown in FIG. 23 illustrates a relationship between Nsc/Nall, which is plotted on the horizontal axis, and a left-right temperature difference ⁇ T of the air blown out from the heat exchanger 2 , which is plotted on the vertical axis.
  • Nsc/Nall which is plotted on the horizontal axis
  • ⁇ T left-right temperature difference
  • the left-right temperature difference ⁇ T of the air blown out from the heat exchanger 2 is defined as a difference between the temperature of the air blown out after exchanging heat with a portion of the heat exchanger 2 located on the left side of the center portion in the Y-axis direction, and the temperature of the air blown out after exchanging heat with a portion of the heat exchanger 2 located on the right side of the center portion in the Y-axis direction.
  • a solid line L 20 indicates a case where the height of the cores 22 , 25 in the Z-direction is small
  • a dot-dash line L 21 indicates a case where the height of the cores 22 , 25 in the Z-direction is large.
  • the left-right temperature difference ⁇ T of the heat exchanger 2 becomes equal to or less than a threshold value ⁇ Ta.
  • the threshold value ⁇ Ta indicates an allowable value of a difference between the temperature of air blown toward a driver's seat side and the temperature of air blown toward a passenger's seat side, among air blown into a vehicle cabin through the heat exchanger 2 .
  • the left-right temperature difference ⁇ T of the heat exchanger 2 rapidly decreases. In other words, the left-right temperature difference ⁇ T of the heat exchanger 2 is reduced, meaning that the thermal uniformity is improved.
  • the graph shown in FIG. 24 illustrates a relationship between a total opening cross-sectional area AS of the communication holes 241 actually provided in the primary region Tc and the secondary regions Tf, Tr, plotted on the horizontal axis, and the pressure loss PL of the refrigerant, plotted on the vertical axis.
  • the pressure loss PL of the refrigerant can be made smaller than the threshold value PLa.
  • the threshold value PLa is, for example, an allowable value of the pressure loss of the refrigerant that enables sufficient cooling performance in a case where a battery of an electric vehicle is cooled using a refrigeration cycle employing the heat exchanger 2 of the present embodiment.
  • the primary region Tc and the at least one secondary region Tf, Tr can be easily defined. Furthermore, by adjusting the total cross-sectional areas of the communication holes formed in the partition wall 23 w , 24 w , a difference in the flow rate of the refrigerant can also be adjusted, so that the formation position and the formation manner of the at least one secondary region Tf, Tr relative to the primary region Tc can be more easily adjusted.
  • the total cross-sectional area of the communication holes refers to the sum of the opening cross-sectional areas of the communication holes formed in the region.
  • the heat exchanger 2 B, 2 C according to aspect 3, wherein an internal cross-sectional area of the at least one of the primary turn tank 23 B, 23 C or the secondary turn tank 24 B, 24 C is formed to vary at least in part along the stacking direction (the axial direction of the Y-axis), and thereby the primary region Tc and the at least one secondary region Tf, Tr are formed accordingly.
  • the heat exchanger 2 C according to aspect 8, wherein the internal cross-sectional area of the at least one of the primary turn tank 23 C or the secondary turn tank 24 C is varied by providing a flow restrictor 232 C, 242 C inside the at least one of the primary turn tank 23 C or the secondary turn tank 24 C.
  • the heat exchanger according to aspect 8 wherein the internal cross-sectional area of the at least one of the primary turn tank 23 B or the secondary turn tank 24 B is varied by varying an inner wall shape of the at least one of the primary turn tank 23 B or the secondary turn tank 24 B.
  • the inner wall shape can be varied by providing the projection 232 a , 242 a described with reference to FIGS. 11 and 12 .
  • the heat exchanger 2 D, 2 E according to aspect 1 or 2 wherein the primary region Tc and the at least one secondary region Tf, Tr are formed in the plurality of primary tubes and/or the plurality of secondary tubes.
  • an internal flow passage of each of the primary tubes 221 Df, 221 Dr and/or an internal flow passage of each of the secondary tubes 251 Df, 251 Dr arranged in the at least one secondary region Tf, Tr is narrower than an internal flow passage of each of the primary tubes 221 Dc and/or an internal flow passage of each of the secondary tubes ( 251 Dc arranged in the primary region Tc.
  • a difference in pressure loss is formed by varying the internal flow passages of the tubes, so the primary region Tc and the at least one secondary region Tf, Tr can be formed by a simple means such as changing the tubes.
  • a number of the primary tubes 221 and/or the secondary tubes 251 arranged in the at least one secondary region Tf, Tr is smaller than a number of the primary tubes 221 and/or the secondary tubes 251 arranged in the primary region Tc.
  • the primary region Tc and the at least one secondary region Tf, Tr can be formed by a simple means such as varying the number of tubes, while using ordinary tubes and making no modification to the turn tanks.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US19/325,135 2023-03-16 2025-09-10 Heat exchanger Pending US20260009602A1 (en)

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JP4574321B2 (ja) * 2003-10-29 2010-11-04 昭和電工株式会社 熱交換器
JP4734021B2 (ja) * 2004-05-11 2011-07-27 昭和電工株式会社 熱交換器
JP5585543B2 (ja) * 2011-06-17 2014-09-10 株式会社デンソー 車両用冷却装置
FR2977304B1 (fr) * 2011-06-28 2013-07-19 Valeo Systemes Thermiques Echangeur de chaleur, boitier et circuit de climatisation comprenant un tel echangeur
JP5660068B2 (ja) * 2012-03-22 2015-01-28 株式会社デンソー 冷媒蒸発器
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