EP1128148A2 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP1128148A2
EP1128148A2 EP01103635A EP01103635A EP1128148A2 EP 1128148 A2 EP1128148 A2 EP 1128148A2 EP 01103635 A EP01103635 A EP 01103635A EP 01103635 A EP01103635 A EP 01103635A EP 1128148 A2 EP1128148 A2 EP 1128148A2
Authority
EP
European Patent Office
Prior art keywords
tubes
tube
ratio
less
long diameter
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.)
Granted
Application number
EP01103635A
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English (en)
French (fr)
Other versions
EP1128148B1 (de
EP1128148A3 (de
Inventor
Hiroshi Kokubunji
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 EP1128148A2 publication Critical patent/EP1128148A2/de
Publication of EP1128148A3 publication Critical patent/EP1128148A3/de
Application granted granted Critical
Publication of EP1128148B1 publication Critical patent/EP1128148B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—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

Definitions

  • the present invention relates to a heat exchanger for cooling a coolant (the cooling water) of a liquid-cooled internal combustion engine, such as a water-cooled engine, by exchanging heat between the coolant and the air, or in particular to a heat exchanger effectively applicable to a large vehicle such as a truck or a bus having a large heat release requirement.
  • a coolant the cooling water
  • a liquid-cooled internal combustion engine such as a water-cooled engine
  • the radiator has a structure including a plurality of flat tubes with the cooling water flowing therein, a header tank arranged at each of the longitudinal ends of the tube and cooling fins.
  • the heat exchange capacity of the radiator is determined substantially by the following parameters.
  • the engine of a large vehicle has a high heating value, and therefore requires a radiator of high radiation capacity. This requirement is generally met by increasing the size of the radiator and thereby increasing the first and second radiation areas, as obvious from the parameters described above.
  • the limited equipment space generally makes it difficult to increase the radiation areas by increasing the number of the tubes and the cooling fins. In many cases, therefore, the first and second radiation areas are increased by increasing the long diameter of the tubes.
  • the object of the present invention is to provide a heat exchanger not increased in production cost and suitable for the large vehicles.
  • a heat exchanger comprising a plurality of tubes (110) having a flat section with a coolant flowing therein, a plurality of cooling fins (120) arranged between the tubes (110) for increasing the radiation area by contacting the outer surface of the tubes (110), a first header tank (130) arranged at a longitudinal end of the tubes (110) for supplying by distributing the coolant to the tubes (110), and a second header tank (140) arranged at the other longitudinal end of the tubes (110) for recovering by collecting the coolant flowing out of the tubes (110), wherein the tubes (110) each have therein a partitioning wall (111) for partitioning the internal space (110a) of the tube (110) into a plurality of spaces (110b, 110c) along the long diameter thereof, and the inner wall of the tubes (110) is formed with a plurality of protrusions (112) extending inward of the tube (110).
  • the heat transfer coefficient between the coolant and the tubes (110) can be prevented from decreasing. Therefore, the radiation capacity of the heat exchanger (100) can be increased while suppressing the increase in the number of the parts and the production cost of the heat exchanger, and a heat exchanger suitable for large vehicles can be produced.
  • a heat exchanger wherein, desirably, the ratio of the short diameter (H) to the long diameter (L) of the tubes (110) is not less than 0.035 but not more than 0.1, the ratio of the distance (d1) between the partitioning wall (111) and a given one of the protrusions (112) to the long diameter (L) of the tubes (110) is not less than 0.15 but not more than 0.3, the ratio of the size (A) of the portion of the protrusions (112) parallel to the long diameter (L) of the tubes (110) to the long diameter (L) of the tubes (110) is not less than 0.05 but not more than 0.15, the ratio of the distance (d2) between the protrusions (112) to the long diameter (L) of the tubes (110) is not less than 0.15 but not more than 0.25, and the ratio of the extension (h) of the protrusions (112) to the short diameter (H) of the tubes (110) is not less than 0.15 but not more
  • a heat exchanger wherein, desirably, the ratio of the short diameter (H) to the long diameter (L) of the tubes (110) is not less than 0.05 but not more than 0.09, the ratio of the distance (d1) between the partitioning wall (111) and the protrusions (112) to the long diameter (L) of the tubes (110) is not less than 0.2 but not more than 0.25, the ratio of the size (A) of the portion of the protrusions (112) parallel to the long diameter (L) of the tubes (110) to the long diameter (L) of the tubes (110) is not less than 0.07 but not more than 0.12, the ratio of the distance (d2) between the protrusions (112) to the long diameter (L) of the tubes (110) is not less than 0.2 but not more than 0.23, and the ratio of the extension (h) of the protrusions (112) to the short diameter (H) of the tubes (110) is not less than 0.18 but not more than 0.2.
  • FIG. 1 is a perspective view of a radiator 100 according to this embodiment.
  • the large vehicle is defined as a truck or an omnibus having mounted thereon a large engine of not less than 7000 cc in displacement or not less than 200 thousand W in heating value.
  • reference numeral 110 designates a plurality of tubes in which the cooling water flows.
  • a corrugated cooling fin (hereinafter referred to simply as the fin) 120 for increasing the radiation area by contacting the outer surface of each tube 110 is arranged between the tubes 110.
  • Both the tubes 110 and the fins 120 are made of aluminum, and integrated with each other by brazing, thereby constituting a heat exchange core for exchanging heat between the cooling water and the air.
  • a first header tank 130 for supplying, by distributing, the cooling water to the tubes 110 is arranged at a longitudinal'end (the upper end in this embodiment) of the tubes 110, and a second header tank 140 for recovering the cooling water flowing out of the tubes 110 is arranged at the other longitudinal end (the lower end in this embodiment) of the tubes 110.
  • Fig. 2 shows a section (the section at right angles to the length of the tube 110) of the tube 110.
  • This tube 110 is formed by bending a plate material, made of aluminum, covered with a brazing material on the surface thereof.
  • the brazing material is lower in melting point than aluminum (core member) and corresponds to Japanese Industrial Standards (JIS) A4045 according to this embodiment.
  • the tube 110 has a flat cross section, and partitioning walls 111a to 111c protruded by bending a part or an end of the plate material inward of the tube 110 are formed at the substantial central portion along the long diameter of the tube 110. These partitioning walls 111a to 111c are laid one on another along the long diameter of the tube 110 and brazed into a single wall with the surfaces thereof parallel to the short diameter of the tube 110 kept in contact with each other.
  • the space 110a in the tube 110 is segmented into two spaces 110b, 110c along the length of the tube 110 by the partitioning walls 111a to 111c (which are collectively called the partitioning wall 111).
  • the internal wall of the tube 110 is formed with a plurality of inward protrusions (dimples) 112 over the whole area along the length of the tube 110.
  • the dimples 112 are formed by press machining (plastic machining).
  • Fig. 3 is a diagram for briefly explaining the steps of the process for fabricating the tube 110.
  • the production process includes a blanking step shown in Fig. 3(a), a U-bending step shown in Fig. 3(b), a bending step shown in Fig. 3(c), a dimple shaping step shown in Fig. 3(d), a U-shaping step shown in Fig. 3(e), a bending step shown in Fig. 3(f) and the final step shown in Fig. 3(g), which steps are carried out in the above order.
  • the portion corresponding to the extend dimension of the tube 110 is cut out of a plate material (see Fig. 3(a)), and a portion corresponding to the partitioning wall 111b is formed by U-bending. Then, the portions corresponding to the partitioning walls 111a, 111c are formed by bending (see Fig. 3(c)), after which the dimples 112 are formed by pressing (see Fig. 3(d)). The resulting plate material is bent as shown in Fig. 3(e), 3(f) and 3(g) and in that order thereby to form the spaces 110b, 110c.
  • the space 110a in one tube 110 is segmented into a plurality of (two, in this embodiment) spaces by the partitioning walls 111. Therefore, the substantial sectional area of the flow path having a great effect on the flow velocity in each tube 110 can be reduced without increasing the total number of the tubes 110.
  • the radiation capacity of the radiator 100 can be increased while at the same time suppressing the increase in the number of the parts and the production cost of the radiator 100 and, therefore, a radiator suitable for large vehicles can be produced.
  • a temperature boundary layer and a velocity boundary layer are generated originating from the ends of the partitioning wall 111 along the length of the tube 110 and each of the dimples 112.
  • the two types of boundary layers, the temperature foundary layer and the velocity foundary layer, (which hereinafter will be referred to as the first boundary layer) generated by the partitioning wall 111 and the two types of boundary layers (which hereinafter will be referred to as the second boundary layer) generated by the dimples 112 interfere with each other. Therefore, the thickness of the first and second boundary layers can be prevented from increasing (growing).
  • the cooling water flow can be positively agitated and therefore the heat transfer coefficient between the cooling water and the tubes 110 can be increased for a higher radiation capacity.
  • the solid line indicates the heat transfer coefficient between the cooling water in the tube 110 and the tube 110
  • the dashed line indicates the heat transfer coefficient between the cooling water in the tube 110 assumed to lack the partitioning wall 111 and the particular tube 110
  • the one-dot chain indicates the heat transfer coefficient between the cooling water assumed to lack the partitioning wall 111 and the dimples 112 and the particular tube 110.
  • the heat transfer coefficient between the cooling water and the tube 110 increases for an improved radiation capacity.
  • characters Rew designates the Raynolds number for the water, Nuw the Nusselt number for the water, and Prw the Prandtl number for the water.
  • the graphs of Figs. 6A to 6D show the relation between the radiation capacity and the ratio of the distance dl between the partitioning wall 111 and a given dimple 112 to the long diameter L of the tube 110 (which ratio will hereinafter be referred to as a dimple position d1/L), the ratio of the size A of the portion of a dimple 112 parallel to the long diameter of the tube 110 to the long diameter L of the tube 110 (which ratio will hereinafter be referred to as a dimple length A/L), the ratio of the distance d2 between a plurality of the dimples 112 to the long diameter L of the tube 110 (which ratio will hereinafter be referred to as a dimple pitch d2/L), and the ratio of the size h of the protrusion of the dimple 112 to the short diameter H of the tube 110 (which ratio will hereinafter be referred to as the dimple height h/H).
  • the heat release is expressed as the ratio thereof to the heat release of a simple flat, smooth tube free
  • the flatness H/L is not less than 0.05 but not more than 0.09
  • the long diameter L and the short diameter H are measured in terms of the outer diameters of the tube 110, the distance dl is the length from the inner wall surface of the partitioning wall 111 to the center of the dimple 112, and the distance d2 between a plurality of the dimples 112 is measured as a center distance between the dimples 112.
  • the flow velocity is increased by the partitioning wall 111 and a turbulent flow of the cooling water is obtained in the tube 110 in collaboration with the agitating action of the dimples 112.
  • the flow velocity of the cooling water flowing into the tube 110 is excessively low, however, it is difficult to obtain a turbulent flow of the cooling water even in this embodiment.
  • the heat exchanger is desirably used in a state where the flow velocity of the cooling water is approximately not lower than 1.5 m/sec but not higher than 6 m/sec.
  • the heat release is expressed as the ratio thereof to that of a simple flat, smooth tube in the absence of the dimples 112 and the partitioning wall 111.
  • the internal long diameter of the tube 110 is substantially reduced, and therefore the tube 110 is prevented from being deformed in the direction along the short diameter thereof.
  • the reduction in flow velocity and the stress on the fins 120 which otherwise might be caused by the expansive deformation of the tube 110 along the short diameter thereof are alleviated. Therefore, the durability (reliability) of the radiator 100 can be improved while at the same time preventing the radiation capacity from being deteriorated.
  • the partitioning wall 111 is formed integrally of a single plate material, the increase in the production cost of the tube 110 can be suppressed.
  • the volumes of the two spaces 110b, 110c may be differentiated from each other.
  • the interior of the tube 110 may be segmented into three or more spaces instead of the two spaces 110b, 110c.
  • the shape of the partitioning wall 111 is not limited to the one shown in Fig. 2 but, as shown in Fig. 8, for example, the partitioning wall 111b may be omitted so that the partitioning wall 111 includes only the partitioning walls 111a, 111c.
  • Figs. 9 and 10 show the steps of the process for fabricating the tube 110 according to another embodiment.
  • the partitioning wall 111 for segmenting the tube 110 into a plurality of spaces 110b is constituted of a groove portion 111d formed on one side of a plate material and an insertion portion 111e formed on the other side thereof.
  • a rise portion 111f is formed on the plate material by a roller (protrusion forming process).
  • Figs. 9(c) 9(d) and 9(e) in that order, one side and the other side of the plate material are bent thereby to form the groove portion 111d and the insertion portion 111e (end forming process).
  • protrusions (dimples) 112 are formed at the same time.
  • the plate material is bent (curved) as shown in Figs. 10(a), 10(b), 10(c) and 10(d) in that order, so that the insertion portion 111e is assembled by being inserted in the groove portion 111d (insertion forming process).
  • the tube 110 having the partitioning wall 111 is formed.
  • the present invention is not confined to the aforementioned embodiments in which the dimples 112 are formed in staggered arrangement on the two opposed sides of the inner wall along the direction of the short diameter of the tube 110.
  • the dimples 112 may be formed only on one side of the inner wall of the tube 110.
EP20010103635 2000-02-25 2001-02-22 Wärmetauscher Expired - Lifetime EP1128148B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000054428 2000-02-25
JP2000054428 2000-02-25

Publications (3)

Publication Number Publication Date
EP1128148A2 true EP1128148A2 (de) 2001-08-29
EP1128148A3 EP1128148A3 (de) 2002-03-20
EP1128148B1 EP1128148B1 (de) 2004-04-21

Family

ID=18575681

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20010103635 Expired - Lifetime EP1128148B1 (de) 2000-02-25 2001-02-22 Wärmetauscher

Country Status (3)

Country Link
EP (1) EP1128148B1 (de)
BR (1) BR0100661A (de)
DE (1) DE60102847T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041101A1 (de) * 2004-08-24 2006-03-02 Behr Gmbh & Co. Kg Flachrohr für einen Wärmeübertrager, insbesondere für Kraftfahrzeuge und Verfahren zur Herstellung eines Flachrohres

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7182128B2 (en) * 2005-03-09 2007-02-27 Visteon Global Technologies, Inc. Heat exchanger tube having strengthening deformations
DE102007004993A1 (de) 2007-02-01 2008-08-07 Modine Manufacturing Co., Racine Herstellungsverfahren für Flachrohre und Walzenstraße

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01184399A (ja) * 1988-01-18 1989-07-24 Nippon Denso Co Ltd 熱交換器用チューブ
JPH06185885A (ja) * 1992-07-24 1994-07-08 Furukawa Electric Co Ltd:The 偏平多穴凝縮伝熱管
EP0632245A1 (de) * 1993-07-01 1995-01-04 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Wasser/Luft-Wärmetauscher aus Aluminium für Kraftfahrzeuge
JPH0719774A (ja) * 1993-06-30 1995-01-20 Zexel Corp 熱交換器の偏平チューブ
JPH08178568A (ja) * 1994-12-26 1996-07-12 Showa Alum Corp 熱交換器用金属製チューブ材及びその製造方法
DE19548495A1 (de) * 1995-12-22 1997-06-26 Valeo Klimatech Gmbh & Co Kg Wärmetauscherblock für Wärmetauscher für Kraftfahrzeuge und Verfahren zu dessen Herstellung
JPH1047875A (ja) * 1996-08-07 1998-02-20 Denso Corp 熱交換器、熱交換器用チューブ及び熱交換器の製造方法
JPH10153393A (ja) * 1996-11-22 1998-06-09 Calsonic Corp 熱交換器用扁平伝熱管
DE19819248C1 (de) * 1998-04-29 1999-04-29 Valeo Klimatech Gmbh & Co Kg Flachrohr eines Heizungswärmetauschers oder Kühlers eines Kraftfahrzeugs

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01184399A (ja) * 1988-01-18 1989-07-24 Nippon Denso Co Ltd 熱交換器用チューブ
JPH06185885A (ja) * 1992-07-24 1994-07-08 Furukawa Electric Co Ltd:The 偏平多穴凝縮伝熱管
JPH0719774A (ja) * 1993-06-30 1995-01-20 Zexel Corp 熱交換器の偏平チューブ
EP0632245A1 (de) * 1993-07-01 1995-01-04 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Wasser/Luft-Wärmetauscher aus Aluminium für Kraftfahrzeuge
JPH08178568A (ja) * 1994-12-26 1996-07-12 Showa Alum Corp 熱交換器用金属製チューブ材及びその製造方法
DE19548495A1 (de) * 1995-12-22 1997-06-26 Valeo Klimatech Gmbh & Co Kg Wärmetauscherblock für Wärmetauscher für Kraftfahrzeuge und Verfahren zu dessen Herstellung
JPH1047875A (ja) * 1996-08-07 1998-02-20 Denso Corp 熱交換器、熱交換器用チューブ及び熱交換器の製造方法
JPH10153393A (ja) * 1996-11-22 1998-06-09 Calsonic Corp 熱交換器用扁平伝熱管
DE19819248C1 (de) * 1998-04-29 1999-04-29 Valeo Klimatech Gmbh & Co Kg Flachrohr eines Heizungswärmetauschers oder Kühlers eines Kraftfahrzeugs

Non-Patent Citations (6)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 013, no. 473 (M-884), 26 October 1989 (1989-10-26) -& JP 01 184399 A (NIPPON DENSO CO LTD), 24 July 1989 (1989-07-24) *
PATENT ABSTRACTS OF JAPAN vol. 018, no. 538 (M-1686), 13 October 1994 (1994-10-13) -& JP 06 185885 A (FURUKAWA ELECTRIC CO LTD:THE;OTHERS: 01), 8 July 1994 (1994-07-08) *
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 04, 31 May 1995 (1995-05-31) -& JP 07 019774 A (ZEXEL CORP), 20 January 1995 (1995-01-20) *
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 11, 29 November 1996 (1996-11-29) -& JP 08 178568 A (SHOWA ALUM CORP), 12 July 1996 (1996-07-12) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 06, 30 April 1998 (1998-04-30) -& JP 10 047875 A (DENSO CORP), 20 February 1998 (1998-02-20) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 11, 30 September 1998 (1998-09-30) -& JP 10 153393 A (CALSONIC CORP), 9 June 1998 (1998-06-09) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041101A1 (de) * 2004-08-24 2006-03-02 Behr Gmbh & Co. Kg Flachrohr für einen Wärmeübertrager, insbesondere für Kraftfahrzeuge und Verfahren zur Herstellung eines Flachrohres

Also Published As

Publication number Publication date
DE60102847T2 (de) 2005-03-31
EP1128148B1 (de) 2004-04-21
DE60102847D1 (de) 2004-05-27
EP1128148A3 (de) 2002-03-20
BR0100661A (pt) 2001-10-09

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