US20070119581A1 - Heat exchanger tube - Google Patents

Heat exchanger tube Download PDF

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Publication number
US20070119581A1
US20070119581A1 US10/573,077 US57307704A US2007119581A1 US 20070119581 A1 US20070119581 A1 US 20070119581A1 US 57307704 A US57307704 A US 57307704A US 2007119581 A1 US2007119581 A1 US 2007119581A1
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United States
Prior art keywords
heat exchanger
flow passages
exchanger tube
tube according
brazing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/573,077
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English (en)
Inventor
Soichi Kato
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.)
Valeo Thermal Systems Japan Corp
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Valeo Thermal Systems Japan Corp
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Assigned to VALEO THERMAL SYSTEMS JAPAN CORPORATION reassignment VALEO THERMAL SYSTEMS JAPAN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KATO, SOICHI
Publication of US20070119581A1 publication Critical patent/US20070119581A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0391—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 plate-like or laminated conduits a single plate being bent to form one or more conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like 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
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to heat exchanger tubes in which a medium flowing through their passages conducts heat exchange with heat conducted to the tubes.
  • a heat exchanger such as a radiator, an evaporator or the like used for a refrigerating cycle is known that it is configured by alternately stacking flat heat exchanger tubes and corrugated radiating fins to form a core and connecting ends of the tubes to tanks.
  • a refrigerant is taken into the heat exchanger from one of the tanks, flowed through the heat exchanger tubes while performing heat exchange with heat conducted to the core, and discharged out of the other of the tanks.
  • Such a heat exchanger is produced by assembling the component members such as heat exchanger tubes, fins, tanks and the like into one body and brazing the assembled body in a furnace.
  • the heat exchanger tubes of the heat exchanger of the above type are also disclosed in the following Patent Documents 1 through 33.
  • the heat exchanger tubes have the corrugated inner fins disposed within the tube body portion which configures the outer shell of the flow passages where the medium flows, so that the heat exchange efficiency of the medium can be improved. And, it is possible to improve the compression strength of the tubes by brazing the inner fins to the inner surface of the tube body portion.
  • the present invention has been made in view of the above circumstances and an object of the invention is to provide heat exchanger tubes which are configured more reasonably based on the current production technology.
  • the invention recited in claim 1 of the present application is a heat exchanger tube comprising: a tube body portion constituting an outer shell of flow passages for flowing a medium, and corrugated inner fins for dividing the flow passages, wherein tops of the inner fins are flat tubes brazed to the inner surface of the tube body portion and in which the medium performs heat exchange with heat conducted to the tubes, wherein a brazing material which is required for brazing the tops of the inner fins and the inner surface of the tube body portion is not clad to a first material constituting the tube body portion but clad to a second material constituting the inner fins.
  • the invention recited in claim 2 of the present application is the heat exchanger tube according to claim 1 , wherein a thickness of a clad layer of the brazing material in the second material is 5 to 10% in ratio with respect to the thickness of the second material.
  • the invention recited in claim 3 of the present application is the heat exchanger tube according to claim 1 or 2 , wherein the second material has a thickness of 0.1 mm or less.
  • the invention recited in claim 4 of the present application is the heat exchanger tube according to claim 3 , wherein the second material has a thickness of 0.05 to 0.07 mm.
  • the invention recited in claim 5 of the present application is the heat exchanger tube according to any one of claims 1 through 4 , wherein the first material has a thickness of 0.25 mm or less.
  • the invention recited in claim 6 of the present application is the heat exchanger tube according to claim 5 , wherein the first material has a thickness of 0.18 to 0.24 mm.
  • the invention recited in claim 7 of the present application is the heat exchanger tube according to any one of claims 1 through 6 , wherein the tube has a thickness of 1.2 mm or less.
  • the invention recited in claim 8 of the present application is the heat exchanger tube according to claim 7 , wherein the tube has a thickness of 0.8 to 1.2 mm.
  • the invention recited in claim 9 of the present application is the heat exchanger tube according to any one of claims 1 through 8 , wherein the tube has a width of 16 mm or less.
  • the invention recited in claim 10 of the present application is the heat exchanger tube according to claim 9 , wherein the tube has a width of 12 to 16 mm.
  • the invention recited in claim 11 of the present application is the heat exchanger tube according to any one of claims 1 through 10 , wherein the flow passages divided by the inner fins have an equivalent diameter of 0.559 mm or less.
  • the invention recited in claim 12 of the present application is the heat exchanger tube according to claim 11 , wherein the flow passages divided by the inner fins have an equivalent diameter of 0.254 mm to 0.559 mm.
  • the invention recited in claim 13 of the present application is the heat exchanger tube according to any one of claims 1 through 12 , wherein the tops of the inner fins have a pitch of 1.0 mm or less.
  • the invention recited in claim 14 of the present application is the heat exchanger tube according to any one of claims 1 through 13 , wherein an Al—Zn alloy layer is formed on the surface of the first material which becomes an outer shell of the tube.
  • the invention recited in claim 15 of the present application is the heat exchanger tube according to any one of claims 1 through 14 , wherein the tops of the inner fins are flat.
  • the invention recited in claim 16 of the present application is the heat exchanger tube according to any one of claims 1 through 15 , wherein ends of the second material in its breadth direction are brazed with the first material by the brazing material which is clad to the second material.
  • the invention recited in claim 17 of the present application is the heat exchanger tube according to claim 16 , wherein both ends of the first material in its breadth direction are engaged and brazed with an end of the second material in its breadth direction sandwiched at one end of the tube in its breadth direction so as not to separate from each other.
  • the invention recited in claim 18 of the present application is the heat exchanger tube according to any one of claims 1 through 17 , wherein the portion between the tops of the inner fins is not perpendicular with respect to the central axis of the tube in its breadth direction.
  • the invention recited in claim 19 of the present application is the heat exchanger tube according to any one of claims 1 through 18 , wherein the tube is a constituting member of the heat exchanger, and the heat exchanger is produced by assembling the tubes and other constituting members into one body and brazing the assembled body in a furnace, and the brazing material clad to the second material melts when brazed in the furnace earlier than the brazing material which melts from the other constituting members and penetrates into the flow passages thereby to prevent the flow passages from being clogged.
  • the invention recited in claim 20 of the present application is the heat exchanger tube according to claim 19 , wherein the brazing material clad to the second material has a melting point lower than that of the brazing material which melts from the other constituting members and penetrates into the flow passages.
  • the invention recited in claim 21 of the present application is the heat exchanger tube according to claim 19 , wherein the brazing material clad to the second material melts earlier than the brazing material which melts from the other constituting members and penetrates into the flow passages because the tube has a thermal resistance lower than that of the other constituting members.
  • the invention recited in claim 22 of the present application is the heat exchanger tube according to any one of claims 19 through 21 , wherein among plural flow passages divided by the inner fins, an equivalent diameter of the flow passage, which is positioned at the lowest position when brazing in the furnace, or individual equivalent diameters of the flow passage positioned at the lowest position and flow passages positioned nearby when brazing in the furnace are larger than a whole average of the equivalent diameters of the plural flow passages divided by the inner fins.
  • the invention recited in claim 23 of the present application is a heat exchanger tube comprising: a tube body portion constituting an outer shell of flow passages for flowing a medium, and corrugated inner fins for dividing the flow passages, wherein the tops of the inner fins are flat tube brazed to the inner surface of the tube body portion and in which the medium performs heat exchange with heat conducted to the tube, wherein the tube has a thickness of 1.2 mm or less, the tube has a width of 16 mm or less, a first material constituting the tube body portion has a thickness of 0.25 mm or less, a second material constituting the inner fins has a thickness of 0.10 mm or less, and the flow passages divided by the inner fins have an equivalent diameter of 0.559 mm or less.
  • the invention recited in claim 24 of the present application is the heat exchanger tube according to claim 23 , wherein the second material has a thickness of 0.05 to 0.07 mm.
  • the invention recited in claim 25 of the present application is the heat exchanger tube according to claim 23 or 24 , wherein the first material has a thickness of 0.18 to 0.24 mm.
  • the invention recited in claim 26 of the present application is the heat exchanger tube according to any one of claims 23 through 25 , wherein the tube has a thickness of 0.8 to 1.2 mm.
  • the invention recited in claim 27 of the present application is the heat exchanger tube according to any one of claims 23 through 26 , wherein the tube has a width of 12 to 16 mm.
  • the invention recited in claim 28 of the present application is the heat exchanger tube according to any one of claims 23 through 27 , wherein the flow passages divided by the inner fins have an equivalent diameter of 0.254 mm to 0.559 mm.
  • the invention recited in claim 29 of the present application is the heat exchanger tube according to any one of claims 23 through 28 , wherein the tops of the inner fins have a pitch of 1.0 mm or less.
  • the invention recited in claim 30 of the present application is the heat exchanger tube according to any one of claims 23 through 29 , wherein an Al-Zn alloy layer is formed on the surface of the first material which becomes an outer shell of the tube.
  • the invention recited in claim 31 of the present application is the heat exchanger tube according to any one of claims 23 through 30 , wherein the tops of the inner fins are flat.
  • the invention recited in claim 32 of the present application is the heat exchanger tube according to any one of claims 23 through 31 , wherein ends of the second material in its breadth direction are brazed to the first material.
  • the invention recited in claim 33 of the present application is the heat exchanger tube according to claim 32 , wherein both ends of the first material in its breadth direction are engaged and brazed with an end of the second material in its breadth direction sandwiched at one end of the tube in its breadth direction so as not to separate from each other.
  • the invention recited in claim 34 of the present application is the heat exchanger tube according to any one of claims 23 through 33 , wherein the portion between the tops of the inner fins is not perpendicular with respect to the central axis of the tube in its breadth direction.
  • the invention recited in claim 35 of the present application is the heat exchanger tube according to any one of claims 23 through 34 , wherein the tube is a constituting member of the heat exchanger, and the heat exchanger is produced by assembling the tubes and other constituting members into one body and brazing the assembled body in a furnace, the brazing material which is required for brazing the tops of the inner fins and the inner surface of the tube body portion is disposed within the flow passages, and the brazing material disposed within the flow passages melts when brazed in the furnace earlier than the brazing material which melts from the other constituting members and penetrates into the flow passages thereby to prevent the flow passages from being clogged.
  • the invention recited in claim 36 of the present application is the heat exchanger tube according to claim 35 , wherein the brazing material disposed within the flow passages has a melting point lower than that of the brazing material which melts from the other constituting members and penetrates into the flow passages.
  • the invention recited in claim 37 of the present application is the heat exchanger tube according to claim 35 , wherein the brazing material disposed within the flow passages melts earlier than the brazing material which melts from the other constituting members and penetrates into the flow passages because the tube has a thermal resistance which is lower than that of the other constituting members.
  • the invention recited in claim 38 of the present application is the heat exchanger tube according to any one of claims 35 through 37 , wherein among plural flow passages divided by the inner fins, an equivalent diameter of the flow passage, which is positioned at the lowest position when brazing in the furnace, or individual equivalent diameters of the flow passages positioned at the lowest position and flow passages positioned nearby when brazing in the furnace are larger than a whole average of the equivalent diameters of the plural flow passages divided by the inner fins.
  • the invention recited in claim 39 of the present application is a heat exchanger tube comprising: a tube body portion constituting an outer shell of flow passages for flowing a medium, and a flow passage dividing body for dividing the flow passages the flow passage dividing body being a tube brazed to the inner surface of the tube body portion, and the medium performing heat exchange with heat conducted to the tube, wherein the tube is a constituting member of a heat exchanger, and the heat exchanger is produced by assembling the tube and other constituting members into one body and brazing the assembled body in a furnace, a brazing material which is required for brazing the flow passage dividing body and the inner surface of the tube body portion is disposed within the flow passages, and the brazing material disposed within the flow passages melts when brazed in the furnace earlier than the brazing material which melts from the other constituting members and penetrates into the flow passages thereby to prevent the flow passages from being clogged.
  • the invention recited in claim 40 of the present application is the heat exchanger tube according to claim 39 , wherein the flow passage dividing body is a corrugated inner fins, and the tops of the inner fins are brazed to the inner surface of the tube body portion.
  • the invention recited in claim 41 of the present application is the heat exchanger tube according to claim 39 , wherein the flow passage dividing body is beads obtained by shaping a material constituting the tube body portion, and the tops of the beads are brazed to the inner surface of the tube body portion.
  • the invention recited in claim 42 of the present application is the heat exchanger tube according to any one of claims 39 through 41 , wherein the brazing material disposed within the flow passages has a melting point lower than that of the brazing material which melts from the other constituting members and penetrates into the flow passages.
  • the invention recited in claim 43 of the present application is the heat exchanger tube according to any one of claims 39 through 41 , wherein the brazing material disposed within the flow passages melts earlier than the brazing material which melts from the other constituting members and penetrates into the flow passages because the tube has a thermal resistance which is lower than that of the other constituting members.
  • the invention recited in claim 44 of the present application is the heat exchanger tube according to any one of claims 39 through 43 , wherein the flow passages divided by the flow passage dividing body have an equivalent diameter of 0.559 mm or less.
  • the invention recited in claim 45 of the present application is the heat exchanger tube according to claim 44 , wherein the flow passages divided by the flow passage dividing body have an equivalent diameter of 0.254 mm to 0.559 mm.
  • the invention recited in claim 46 of the present application is the heat exchanger tube according to any one of claims 39 through 45 , wherein among plural flow passages divided by the flow passage dividing body, an equivalent diameter of the flow passages, which is positioned at the lowest position when brazing in the furnace, or individual equivalent diameters of the flow passage positioned at the lowest position and flow passages positioned near by when brazing in the furnace are larger than a whole average of the equivalent diameters of the plural flow passages divided by the inner fins.
  • FIG. 1 is an explanatory diagram showing a heat exchanger according to an embodiment of the present invention (First embodiment).
  • FIG. 2 is an explanatory diagram and an enlarged view of an essential portion showing sections of a heat-exchanger tube, before brazing thereof, according to the embodiment of the present invention (First embodiment).
  • FIG. 3 is an explanatory diagram showing a section of a second material according to the embodiment of the present invention (First embodiment).
  • FIG. 4 is an enlarged diagram of an essential portion showing a section of a heat-exchanger tube, before brazing thereof, according to an embodiment of the present invention (Second embodiment).
  • FIG. 5 is an enlarged diagram of an essential portion showing a section of a heat-exchanger tube, before brazing thereof, according to an embodiment of the present invention (Third embodiment).
  • FIG. 6 is an enlarged diagram of an essential portion showing a section of a heat-exchanger tube, before brazing thereof, according to the embodiment of the present invention (Third embodiment).
  • FIG. 7 is an enlarged diagram of an essential portion showing a section of a heat-exchanger tube, before brazing thereof, according to the embodiment of the present invention (Third embodiment).
  • FIG. 8 is an explanatory diagram showing a section of a heat-exchanger tube, before brazing thereof, according to an embodiment of the present invention (Fourth embodiment).
  • a heat exchanger 1 shown in FIG. 1 is a radiator for a refrigerating cycle for in-car air conditioning mounted on an automobile.
  • This heat exchanger 1 comprises a core 10 which is formed by alternately stacking heat exchanger tubes 100 and radiating fins 20 , and a pair of tanks 30 with which both ends of the individual heat exchanger tubes 100 in their longitudinal direction are in communicative connection.
  • Reinforcing members 40 each is disposed on upper and lower sides of the core 10 , and both ends of the individual reinforcing members 40 in their longitudinal direction are supported by the tanks 30 .
  • An inlet 31 and an outlet 32 for a medium are disposed at the required portions of the tanks 30 , so that the medium which has entered through the inlet 31 flows through the heat exchanger tubes 100 while performing heat exchange with heat conducted to the core 10 and flows out through the outlet 32 .
  • Constituting members of the heat exchanger 1 such as the fins 20 , the tanks 30 , the inlet 31 , the outlet 32 , the side plates 40 and the heat exchanger tubes 100 are formed of an aluminum or aluminum alloy member. They are assembled into one body by means of a jig, and the assembled body undergoes a heat treatment in a furnace to be brazed into one body. To braze in the furnace, a brazing material and flux are disposed on the required portions of the individual members.
  • the heat exchanger tube 100 of this embodiment shown in FIG. 2 has a tube body portion 200 which forms the outer shell of flow passages 101 for flowing the medium and corrugated inner fins 300 for dividing the flow passages 101 and the tops of the inner fins 300 are flat and brazed to the inner surface of the tube body portion 200 .
  • This heat exchanger tube 100 has a thickness t tube of 1.2 mm or less. It is desirable that the heat exchanger tube 100 has a thickness t tube of 0.8 to 1.2 mm. And, the heat exchanger tube 100 has a width w tube of 16 mm or less. It is desirable that the heat exchanger tube 100 has a width w tube of 12 to 16 mm. Besides, the individual flow passages 101 divided by the inner fins 200 each having an equivalent diameter of 0.559 mm or less. It is desirable that the flow passage 101 has an equivalent diameter of 0.254 mm to 0.559 mm.
  • the tube body portion 200 is formed by roll forming a first material of an aluminum or aluminum alloy strip. Both ends 201 of the first material in its breadth direction are mutually engaged and brazed at one end 102 of the heat exchanger tube 100 in its breadth direction so that they are not separated from each other. And, the other end 103 of the heat exchanger tube 100 in its breadth direction is a portion where substantially a center of the first material is bent.
  • the inner fins 300 are formed by roll forming a second material of an aluminum or aluminum alloy strip. Pitch P between the tops of the inner fins is 1.0 mm or less. The inner fins 300 are inserted between the first materials in an appropriate stage of the roll forming of the tube body portion 200 and disposed within the tube body portion 200 .
  • the brazing material which is required for brazing the tops 310 of the inner fins 300 , which are a flow passage dividing body to the inner surface of the tube body portion 200 , is not clad to the first material which forms the tube body portion 200 but to the second material which forms the inner fins 300 .
  • the tops 310 of the inner fins 300 and the inner surface of the tube body portion 200 are brazed, at least one of the first material and the second material is clad with the brazing material, and the structure of cladding only the second material with the brazing material is adopted in this embodiment.
  • the reason for this is to suppress the use of brazing material to a minimum required quantity. Its concept will be described below.
  • the brazing material containing silicon is indispensable for brazing but becomes a cause of eroding the core material after brazing. Therefore, it is desirable that the brazing material is suppressed to a quantity as small as possible.
  • a material clad with the brazing material is produced by stacking and rolling the core material and the brazing material at a prescribed ratio, so that the thickness of the clad layer of the brazing material has a lower limit with respect to the thickness of the material.
  • the lower limit of the thickness of the clad layer is about 5% with respect to the thickness of the material.
  • the thickness t 2 of the second material can be made thinner to some extent in view of the structure of the heat exchanger tube 100 .
  • the second material is desirably clad with the brazing material to determine the brazing material to a small quantity.
  • the ends 201 of the first material are brazed with the brazing material, which penetrates from the tanks 30 by capillary action, by brazing in the furnace described above.
  • the quantity of the brazing material to be used can be reduced, and the depth of a silicon diffusion layer of the first material can be decreased, so that the thickness of the first material can be made thinner.
  • the ends 301 of the second material in its breadth direction are brazed to the first material with the brazing material which is clad to the second material. Brazing of the ends 301 of the second material to the first material prevents the ends 301 of the second material from being fluctuated by the flowing medium, and the durability of the heat exchanger tubes 100 and the stability of the medium flow can be improved surely.
  • the thickness t 1 of the first material is 0.25 mm or less. It is desirable that the thickness t 1 of the first material is 0.18 to 0.24 mm. And, an Al—Zn alloy layer is disposed as a sacrifice layer for improving corrosion resistance of the heat exchanger tubes 100 on the surface of the first material which becomes the outer shell of the heat exchanger tube 100 .
  • the second material is formed by disposing a clad layer 300 b of the brazing material on both surfaces of a core material 300 a as shown in FIG. 3 , and its thickness t 2 is 0.1 mm or less. It is desirable that the thickness t 2 of the second material is 0.05 to 0.07 mm. And, the thickness of the clad layer 300 b of the brazing material in the second material is 5 to 10% in ratio with respect to the thickness t 2 of the second material.
  • the tops 310 of the inner fins 300 are flat, so that sufficient brazing areas are secured between the tops 310 of the inner fins 300 and the inner surface of the tube body portion 200 .
  • brazing strength and reliability of brazing are improved surely by configuring as described above.
  • friction between the tube body portion 200 and the inner fins 300 is increased because the tops 310 of the inner fins 300 are flat.
  • Width W flat of the flat portions of the tops 310 is 2.5 to 0.5 when the thickness t 2 of the material is 1.
  • a portion between the tops 310 and 310 of the inner fins 300 becomes non-perpendicular to a central axis L of the heat exchanger tube 100 in its breadth direction.
  • an intersection angle ⁇ between the portion between the tops 310 and 310 of the inner fins 300 and the central axis L in the breadth direction is 65 to 85°.
  • the intersection angle ⁇ is perpendicular and the heat exchanger tubes 100 is cut to a prescribed length before brazing, the inner fins 300 are largely deformed when a cutting blade is moved in parallel to the central axis L in the breadth direction. But, such a disadvantage is avoided in this embodiment by setting the intersection angle ⁇ to a favorable value.
  • the brazing material which is clad to the second material melts earlier than the brazing material, which melts from the other constituting members such as the tanks 30 constituting the heat exchanger 1 and penetrates into the flow passages 101 , thereby to prevent the flow passages 101 from being clogged. If the interior of the heat exchanger tube 100 is dry when the brazing material penetrates into the flow passages 101 from outside, the penetrated brazing material stays locally within the flow passages 101 because of an influence of its surface tension and the like, and the flow passages 101 are clogged.
  • the brazing material which is clad to the second material has a melting point lower than that of the brazing material which melts from the surfaces of the tanks 30 and penetrates into the flow passages 101 . Otherwise, the brazing material which is clad to the second material melts earlier than the brazing material which melts from the surface of the tanks 30 and penetrates into the flow passages 101 because a thermal resistance of the heat exchanger tubes 100 is smaller than that of the tanks 30 .
  • the equivalent diameter of the flow passage 101 which is positioned at the lowest position when brazing in the furnace, or the individual equivalent diameters of the flow passage 101 which is positioned at the lowest position and the flow passages 101 which are positioned nearby when brazing in the furnace are desirably determined to be larger than a whole average of the equivalent diameters of the plural flow passages 101 which are divided by the inner fins 300 .
  • the heat exchanger 1 is brazed in the furnace with the core 10 laid on its side, so that the equivalent diameter of the flow passage 101 which is positioned at one end 102 of the heat exchanger tube 100 in its breadth direction is determined larger, and if necessary, the equivalent diameter of the flow passage 101 positioned near the pertinent flow passage 101 is also determined to be large. Otherwise, the equivalent diameter of the flow passage 101 which is positioned at the other end 103 of the heat exchanger tube 100 in its breadth direction is determined to be large, and if necessary, the equivalent diameter of the flow passage 101 which is positioned near the pertinent flow passage 101 is also determined to be large.
  • a pitch P of the tops at the required portions of the inner fins 300 is determined to be larger than a pitch P of the tops at the other portion.
  • either end may be positioned on the lower side, so that it is also possible to secure generality in terms of brazing posture.
  • the heat exchanger tube 100 of this embodiment is configured very rationally and can be used favorably as a component part of the heat exchanger 1 .
  • Setting of the values of the individual portions of the heat exchanger tubes 100 was obtained by studying the performance of the heat exchanger tubes 100 based on the current manufacturing technology.
  • the heat exchanger tube 100 of this embodiment has both ends 201 of the first material in its breadth direction mutually engaged and brazed at one end 102 of the heat exchanger tube 100 in its breadth direction so that they are not separated from each other. And, the other end 301 of the second material is brazed with the end 201 of the first material.
  • the other basic structure is same with that of the above-described embodiment.
  • the end 301 of the second material may be brazed to the end 201 of the first material.
  • a third embodiment of the present invention will be described with reference to FIG. 5 through FIG. 7 .
  • the heat exchanger tube 100 of this embodiment has both ends 201 of the first material in its breadth direction mutually engaged and brazed at one end 102 of the heat exchanger tube 100 in its breadth direction with the end 301 of the second material in its breadth direction sandwiched so that they are not separated from each other.
  • the end 201 of the first material and the end 301 of the second material are brazed with the brazing material which is clad to the second material and the brazing material which penetrates from the tanks 30 .
  • a shape of the end 201 of the first material and a shape of the end 301 of the second material can be determined appropriately as shown in, for example, FIG. 6 and FIG. 7 , and are not limited to a particular shape.
  • the other basic structure is same with that of the above-described embodiment.
  • the end 301 of the second material may be configured to sandwich the end 201 of the first material.
  • the ends 201 of the first material can be mutually brazed with the brazing material which is clad to the second material.
  • the brazing material does not spread sufficiently if the heat exchanger tube 100 is relatively long, and defective brazing may be caused.
  • such a defect can be avoided by this embodiment, and the brazing of the ends 201 of the first material in its breadth direction can be improved surely in its reliability.
  • the end 301 of the second material in its breadth direction is sandwiched between both ends 201 of the first material in its breadth direction, so that the inner fins 300 can be positioned accurately within the heat exchanger tube 100 .
  • the size of the flow passage 101 at one end 102 and the other end 103 of the heat exchanger tube 100 can also be controlled accurately. And, a decrease in resistance to pressure due to displacement of the inner fins 300 can also be prevented.
  • beads 202 which are formed by shaping the required portions of the first material are disposed as a flow passage dividing body for dividing the flow passages 101 .
  • the tops of the beads 202 are brazed to the inner surface of tube body portion 200 .
  • the brazing material which is required for brazing the tube body portion 200 with the tops of the beads 202 , and the brazing material which is required for brazing the both ends 201 of the first material, are clad to one surface of the first material which becomes the inside of the flow passages.
  • the brazing material which is clad to the first material melts earlier than the brazing material which penetrates from outside into the flow passages 101 , so that the flow passages 101 are prevented from being clogged.
  • the other basic structure is same with that of the above-described embodiment.
  • the beads can also be disposed as the flow passage dividing body.
  • the brazing material is clad to the first material, and to braze in the furnace, it is configured so that the brazing material melts earlier than the brazing material, which melts from the other constituting members constituting the heat exchanger, and penetrates into the flow passages 101 .
  • the heat exchanger tubes of the present invention can be used as constituting members of, for example, a vehicle-mounted heat exchanger.
US10/573,077 2003-09-30 2004-09-16 Heat exchanger tube Abandoned US20070119581A1 (en)

Applications Claiming Priority (3)

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JP2003340601A JP2005106389A (ja) 2003-09-30 2003-09-30 熱交換チューブ
JP2003-340601 2003-09-30
PCT/JP2004/014005 WO2005033606A1 (ja) 2003-09-30 2004-09-16 熱交換チューブ

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US10/573,077 Abandoned US20070119581A1 (en) 2003-09-30 2004-09-16 Heat exchanger tube

Country Status (4)

Country Link
US (1) US20070119581A1 (ja)
EP (1) EP1681528A4 (ja)
JP (1) JP2005106389A (ja)
WO (1) WO2005033606A1 (ja)

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US20070095514A1 (en) * 2005-10-28 2007-05-03 Denso Corporation Tube for heat exchanger and method of manufacturing the same
US20080011464A1 (en) * 2006-07-11 2008-01-17 Denso Corporation Exhaust gas heat exchanger
US20080196865A1 (en) * 2007-02-15 2008-08-21 Denso Corporation Exhaust heat recovery apparatus
US20090056927A1 (en) * 2006-01-19 2009-03-05 Werner Zobel Flat tube, flat tube heat exchanger, and method of manufacturing same
US20090166016A1 (en) * 2007-12-30 2009-07-02 Zaiqian Hu Heat exchanger tubes and methods for enhancing thermal performance and reducing flow passage plugging
US20100024508A1 (en) * 2007-02-01 2010-02-04 Frank Opferkuch Tubes and method and apparatus for producing tubes
US20110005738A1 (en) * 2006-11-22 2011-01-13 Modine Manufacturing Company Soldered flat tube for condensers and/or evaporators
US20110284195A1 (en) * 2010-05-20 2011-11-24 Delphi Technologies, Inc. Fabricated tube for an evaporator
US20120031586A1 (en) * 2010-08-03 2012-02-09 Denso Corporation Condenser
US20150107812A1 (en) * 2011-03-31 2015-04-23 Valeo Systemes Thermiques Heat Exchanger Tube, And Corresponding Heat Exchanger Production Method
US20160223264A9 (en) * 2012-07-19 2016-08-04 Gränges Ab Compact aluminium heat exchanger with welded tubes for power electronics and battery cooling
US20170051982A1 (en) * 2014-05-09 2017-02-23 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same
US10267572B2 (en) 2012-06-29 2019-04-23 Mahle International Gmbh Flat tube and heat exchanger having a flat tube of said type
US11421944B2 (en) * 2017-05-02 2022-08-23 Valeo Systemes Thermiques Flat tube for a heat exchanger and a heat exchanger that is more resistant to debris

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JP2007125590A (ja) * 2005-11-04 2007-05-24 Denso Corp 熱交換器および熱交換器の製造方法
US7921559B2 (en) 2006-01-19 2011-04-12 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8434227B2 (en) 2006-01-19 2013-05-07 Modine Manufacturing Company Method of forming heat exchanger tubes
DE102006002627A1 (de) * 2006-01-19 2007-08-02 Modine Manufacturing Co., Racine Flachrohr, Wärmetauscher und Herstellungsverfahren
DE102006016711B4 (de) * 2006-04-08 2016-11-03 Modine Manufacturing Co. Flachrohr für Wärmetauscher
US8438728B2 (en) 2006-01-19 2013-05-14 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8281489B2 (en) 2006-01-19 2012-10-09 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8683690B2 (en) 2006-01-19 2014-04-01 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
KR101353386B1 (ko) * 2007-08-20 2014-01-21 한라비스테온공조 주식회사 열교환기용 튜브
JP5167930B2 (ja) * 2008-04-25 2013-03-21 株式会社デンソー 熱交換器
DE102008052785B4 (de) 2008-10-22 2022-06-02 Innerio Heat Exchanger GmbH Flachrohr und Herstellungsverfahren
DE102010023384B4 (de) 2010-06-10 2014-08-28 Modine Manufacturing Co. Herstellungsverfahren, insbesondere für Rohre und Abreißvorrichtung
EP2984433A1 (en) * 2013-04-10 2016-02-17 Carrier Corporation Folded tube multiple bank heat exchange unit
JP6843012B2 (ja) * 2017-07-14 2021-03-17 株式会社日本クライメイトシステムズ 熱交換器用チューブ

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US6186222B1 (en) * 1997-07-16 2001-02-13 The Furukawa Electric Co., Ltd Aluminum alloy tube and heat exchanger, and method of metal-spraying a filler alloy
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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070095514A1 (en) * 2005-10-28 2007-05-03 Denso Corporation Tube for heat exchanger and method of manufacturing the same
US20100243225A1 (en) * 2006-01-19 2010-09-30 Werner Zobel Flat tube, flat tube heat exchanger, and method of manufacturing same
US20090056927A1 (en) * 2006-01-19 2009-03-05 Werner Zobel Flat tube, flat tube heat exchanger, and method of manufacturing same
US8726508B2 (en) 2006-01-19 2014-05-20 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US20080011464A1 (en) * 2006-07-11 2008-01-17 Denso Corporation Exhaust gas heat exchanger
US20110005738A1 (en) * 2006-11-22 2011-01-13 Modine Manufacturing Company Soldered flat tube for condensers and/or evaporators
US20100024508A1 (en) * 2007-02-01 2010-02-04 Frank Opferkuch Tubes and method and apparatus for producing tubes
US8561451B2 (en) 2007-02-01 2013-10-22 Modine Manufacturing Company Tubes and method and apparatus for producing tubes
US20080196865A1 (en) * 2007-02-15 2008-08-21 Denso Corporation Exhaust heat recovery apparatus
US8056616B2 (en) * 2007-02-15 2011-11-15 Denso Corporation Exhaust heat recovery apparatus
US20090166016A1 (en) * 2007-12-30 2009-07-02 Zaiqian Hu Heat exchanger tubes and methods for enhancing thermal performance and reducing flow passage plugging
US8776874B2 (en) 2007-12-30 2014-07-15 Valeo, Inc. Heat exchanger tubes and methods for enhancing thermal performance and reducing flow passage plugging
US20110284195A1 (en) * 2010-05-20 2011-11-24 Delphi Technologies, Inc. Fabricated tube for an evaporator
US20120031586A1 (en) * 2010-08-03 2012-02-09 Denso Corporation Condenser
US9121629B2 (en) * 2010-08-03 2015-09-01 Denso Corporation Condenser
US20150107812A1 (en) * 2011-03-31 2015-04-23 Valeo Systemes Thermiques Heat Exchanger Tube, And Corresponding Heat Exchanger Production Method
US10989485B2 (en) * 2011-03-31 2021-04-27 Valeo Systemes Thermiques Heat exchanger tube, and corresponding heat exchanger production method
US10267572B2 (en) 2012-06-29 2019-04-23 Mahle International Gmbh Flat tube and heat exchanger having a flat tube of said type
US20160223264A9 (en) * 2012-07-19 2016-08-04 Gränges Ab Compact aluminium heat exchanger with welded tubes for power electronics and battery cooling
US20170051982A1 (en) * 2014-05-09 2017-02-23 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same
US10712097B2 (en) * 2014-05-09 2020-07-14 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same
US11421944B2 (en) * 2017-05-02 2022-08-23 Valeo Systemes Thermiques Flat tube for a heat exchanger and a heat exchanger that is more resistant to debris

Also Published As

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EP1681528A4 (en) 2013-06-12
EP1681528A1 (en) 2006-07-19
JP2005106389A (ja) 2005-04-21
WO2005033606A1 (ja) 2005-04-14

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