EP0805331A2 - Multiröhren-Wärmetauscher - Google Patents

Multiröhren-Wärmetauscher Download PDF

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Publication number
EP0805331A2
EP0805331A2 EP97302896A EP97302896A EP0805331A2 EP 0805331 A2 EP0805331 A2 EP 0805331A2 EP 97302896 A EP97302896 A EP 97302896A EP 97302896 A EP97302896 A EP 97302896A EP 0805331 A2 EP0805331 A2 EP 0805331A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tube
heat transfer
tank
end portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP97302896A
Other languages
English (en)
French (fr)
Other versions
EP0805331A3 (de
Inventor
Tomonari Morita
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP0805331A2 publication Critical patent/EP0805331A2/de
Publication of EP0805331A3 publication Critical patent/EP0805331A3/de
Withdrawn legal-status Critical Current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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—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

Definitions

  • the present invention relates to a multi-tube heat exchanger used to, for example, an air conditioner for vehicles, and more particularly to an improved connection structure between tubes and a pair of tanks in the heat exchanger.
  • a conventional multi-tube heat exchanger is constructed, for example, as shown in Figs. 8-10.
  • a plurality of heat transfer tubes 33 each having a circular cross section are fluidly interconnected between an upper tank 31 and a lower tank 32. Connecting portions between tubes 33 and tanks 31 and 32 are structured, for example, as shown in Figs. 9 and 10. Each end portion of each heat transfer tube 33 is drawn, and a taper portion 41 and a contracted diameter portion 42 are formed.
  • the respective contracted diameter portions 42 are inserted into holes 39 and 40 defined on walls 34 and 35 of upper and lower tanks 31 and 32, and the tanks 31 and 32 are communicated to each other via heat transfer tubes 33 by brazing the inner peripheries of the holes 39 and 40 and the outer surfaces of the contracted diameter portions 42 of the tubes 33.
  • heat medium for example, refrigerant
  • inlet pipe 37 heat medium introduced through an inlet pipe 37
  • outlet pipe 38 heat medium introduced through an outlet pipe 38.
  • Heat exchange is performed between the refrigerant flowing in heat transfer tubes 33 and air passing through gaps between the tubes 33.
  • each taper portion 41 decreases as it approaches a corresponding contracted diameter portion 42, because the greatest diameter of the taper portion 41 is formed larger than the inner diameter of hole 39 or 40, the length of insertion of each heat transfer tube 33 into upper or lower tank 31 or 32 through hole 39 or 40 is maintained at a predetermined constant length.
  • taper portion 41 and contracted diameter portion 42 are formed on an end portion of each heat transfer tube 33, and the inner diameter of this portion becomes small as compared with that of other portions of the tube 33, as shown in Fig. 10. Therefore, the pressure loss of heat medium (for example, refrigerant) flowing in each heat transfer tube 33 increases at this portion.
  • heat medium for example, refrigerant
  • the resistance P of a path having a path length"l" and an equivalent diameter (an inner diameter) "d” is represented by the following equation.
  • P ⁇ (1/d) ⁇ (u 2 /2g)
  • u is a flow rate
  • g is an acceleration of gravity
  • ⁇ is a coefficient.
  • G 3600 ⁇ A ⁇ u
  • A is a cross-sectional area of a path.
  • the path length "l" is defined as an insertion length into a tank and the insertion length is the same for every tube having an arbitrary inner diameter (an inner di thoughr: d n ), from the above-described equations (1) and (2), the resistance P n of a path defined by a tube diameter d n and a cross-sectional area A n of the path is represented by the following equation.
  • P n ⁇ (1/d n ) ⁇ (1/2g) ⁇ (G/3600A n ) 2
  • a n will be explained.
  • arrangement of tubes of a heat exchanger will be explained in reference to Fig. 12.
  • the outer diameter of a tube is indicated by D
  • an arrangement pitch of tubes in an air-flow direction is indicated by X
  • an arrangement pitch of tubes in a direction perpendicular to the air-flow direction is indicated by Y.
  • a number of tubes capable of being arranged in a unit area of a tank wall is considered at a condition where X/D and Y/D are constant, respectively, even in a case where the outer diameter of a tube varies. In this case, if the outer diameter of a tube becomes small, the number of tubes N n capable of being arranged in a unit area increases.
  • This "d n " is determined at a condition where the thickness of a tube is constant even if the outer diameter of the tube varies.
  • the thickness of a tube can be selected as a constant value in order to obtain a desired corrosion resistance even if the outer diameter of the tube varies.
  • the ratio of the path resistances is represented by the following equation.
  • P n /P 2.5 d 2.5 /d n (A 2.5 /A n ) 2
  • a multi-tube heat exchanger includes a pair of tanks spaced from each other and a plurality of heat transfer tubes each having a circular cross section and fluidly interconnected between the pair of tanks.
  • Each of the plurality of heat transfer tubes has a first radially expanded portion at a first end portion engaging an outer surface of a wall of a first tank of the pair of tanks.
  • Each heat transfer tube may have a second radially expanded portion at a second end portion engaging an outer surface of a wall of a second tank of the pair of tanks in addition to the first radially expanded portion.
  • the first or the second radially expanded portion may be formed as an annular protruded portion formed on an outer surface of the first or the second end portion.
  • the first or the second radially expanded portion may be formed as a radially expanded taper portion formed on a tip portion of the first or the second end portion.
  • the wall of the first or the second tank may be formed as a burr at a position connected with the first or the second end portion, and the radially expanded taper portion may be fitted onto an outer surface of the burr.
  • the present invention can be appropriately applied to a heat exchanger having heat transfer tubes with an inner diameter of not more than 2 mm.
  • a diameter contracted portion such as one in a conventional heat exchanger is not formed at an end portion of a heat transfer tube even if a radially expanded portion is formed, increase of pressure loss of a flowing heat medium in the tube can be prevented, particularly, effectively in a small-diameter tube such as one having a diameter of not more than 2 mm.
  • the radially expanded portion engages an outer surface of a wall of a tank, the insertion length of the tube end portion into the tank can be precisely regulated, or a structure where the tube end portion is not inserted into the tank can be employed.
  • a heat exchanger having a desired dimension can be obtained, and the pressure loss in the circuit of the heat exchanger can be further decreased, thereby achieving a high heat exchange performance.
  • the radially expanded portion is formed as an annular protruded portion formed on an outer surface of the tube end portion, a diameter contracted portion is not formed at all, increase of pressure loss can be effectively prevented. Because the annular protruded portion is engaged to the outer surface of the tank, the insertion length of the tube end portion into the tank is easily and precisely set at a predetermined length.
  • the tube end portion When the radially expanded portion is formed as a radially expanded taper portion formed on a tip portion of the tube end portion and the radially expanded taper portion is fitted onto an outer surface of a burr formed on a tank wall at a position connected with the tube end portion, the tube end portion can be connected to the burr on the tank wall without being projected into the tank and without forming a diameter contracted portion.
  • the flow in the tank can be smoothened as well as the pressure loss in the tank can be suppressed small, and therefore, increase of pressure loss as the whole of the heat exchanger can be prevented more effectively.
  • Fig. 1 is a perspective view of a multi-tube heat exchanger according to a first embodiment of the present invention.
  • Fig. 2 is an enlarged, partial, vertical sectional view of the heat exchanger depicted in Fig. 1, showing connecting portions of a heat transfer tube and tank walls.
  • Fig. 3 is an enlarged, partial, vertical sectional view of a connecting portion of an end portion of a heat transfer tube and a tank wall depicted in Fig. 2.
  • Fig. 4 is a side view of upper and lower dies and a jig for forming an radially expanded portion on a tube end portion of a tube depicted in Fig. 2.
  • Fig. 5 is a graph showing relationships between a pressure loss in a circuit and a circulation amount of refrigerant in the heat exchangers depicted in Figs. 1 and 8.
  • Fig. 6 is a partial, vertical sectional view of connecting portions of a heat transfer tube and tank walls in a heat exchanger according to a second embodiment of the present invention.
  • Fig. 7 is an enlarged, partial, vertical sectional view of a connecting portion of an end portion of a heat transfer tube and a tank wall depicted in Fig. 6.
  • Fig. 8 is an elevational view of a conventional heat exchanger.
  • Fig. 9 is an enlarged, partial, vertical sectional view of the heat exchanger depicted in Fig. 8, showing connecting portions of a heat transfer tube and tank walls.
  • Fig. 10 is an enlarged, partial, vertical sectional view of a connecting portion of an end portion of a heat transfer tube and a tank wall depicted in Fig. 9.
  • Fig. 11 is a graph showing a relationship between an inner diameter of a heat transfer tube and a ratio of path resistances.
  • Fig. 12 is a schematic plan view of arranged heat transfer tubes.
  • Heat exchanger 100 includes a pair of tanks 1 and 2, for example, an upper tank 1 and a lower tank 2.
  • a plurality of heat transfer tubes 3 each having a circular cross section and a small diameter (for example, refrigerant tubes) are fluidly interconnected between tanks 1 and 2.
  • at least heat transfer tubes 3 are made from an aluminum alloy, and fixed to tanks 1 and 2 by brazing.
  • Inlet pipe 12 and outlet pipe 13 are connected to tank 1.
  • a supporting plate 20 is provided at a position corresponding to a middle portion of each heat transfer tube 3 in the axial direction in order to support the tubes 3, this supporting plate 20 may be omitted.
  • Heat exchange medium for example, refrigerant
  • tank 1 is introduced into tank 1 through inlet pipe 12, and after circulation through heat exchanger 100, the heat exchange medium flows out of tank 1 through outlet pipe 13. Heat exchange is performed between the refrigerant flowing in heat transfer tubes 3 and air passing through gaps between the tubes 3.
  • annular protruded portion 6 provided as a radially expanded portion is formed at least on a first end portion 3a of heat transfer tube 3, in this embodiment, on each of first and second end portion 3a and 3b.
  • the annular protruded portions 6 engage the outer surfaces of a tank wall 4 of tank 1 and a tank wall 5 of tank 2, respectively.
  • These annular protruded portions 6 are formed on the outer surface of each heat transfer tube 3 at both end portions 3a and 3b.
  • Tube insertion holes 7 and 8 are defined on tank walls 4 and 5, respectively. End portions 3a and 3b of each heat transfer tube 3 are inserted into tube insertion holes 7 and 8, respectively, and are projected into tanks 1 and 2 at predetermined insertion lengths, respectively.
  • annular protruded portion 6 can be formed by holding a heat transfer tube 3 from both sides by an upper die 9 and a lower die 10 and pressing the tube end portion by a jig 11 in a direction shown by an arrow.
  • Fig. 5 shows a relationship between a pressure loss in a circuit and a circulation amount of refrigerant for comparing the performance of the heat exchanger depicted in Figs. 1-3 with the performance of the conventional heat exchanger depicted in Figs. 8-10.
  • each of heat transfer tubes 3 has an inner diameter of 2.4 mm at its tube end portion
  • each of heat transfer tubes 33 has an inner diameter of 1.8 mm at its diameter contracted tube end portion.
  • the inner diameter of a tube portion except tube end portions is the same in both of the heat exchanger 100 of this embodiment and the conventional heat exchanger.
  • the heat exchanger 100 of this embodiment indicates a pressure-loss property 51
  • the conventional heat exchanger indicates a pressure-loss property 52.
  • Figs. 6 and 7 show a structure of a connecting portion of tube end portions and tank walls in a multi-tube heat exchanger according to a second embodiment of the present invention.
  • a radially expanded taper portion 12 is formed as a radially expanded portion on each of tip portions of the tube end portions of each heat transfer tube 23.
  • Each heat transfer tubes 23 has an inner diameter of not more than 2 mm and is made from an aluminum alloy.
  • a burr 14 is formed at a position connected with each corresponding tube end portion. Burr 14 is formed as a shape along the shape of radially expanded taper portion 12.
  • Radially expanded taper portion 12 is fitted onto an outer surface 15 of burr 14, and an inner surface 13 of the radially expanded taper portion 12 and the outer surface 15 of burr 14 are brazed to each other.
  • a diameter contracted portion is not formed on a tube end portion of heat transfer tube 23 as in a conventional heat exchanger, increase of pressure loss at a connecting portion of the tube end portion and a tank wall can be effectively prevented. Further, in this embodiment, because the tube end portion is not inserted into the interior of a tank, the flow in the tank can be smoothened as well as the pressure loss in the tank can be suppressed small, the pressure loss in the whole circuit of the heat exchanger can be suppressed smaller.
  • multi-tube heat exchangers arranged with tanks 1 and 2 in a vertical direction have been explained in the above-described embodiments, the arrangement direction of tanks may be in a horizontal or other directions.
EP97302896A 1996-04-30 1997-04-28 Multiröhren-Wärmetauscher Withdrawn EP0805331A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP132600/96 1996-04-30
JP13260096A JPH09296994A (ja) 1996-04-30 1996-04-30 熱交換器

Publications (2)

Publication Number Publication Date
EP0805331A2 true EP0805331A2 (de) 1997-11-05
EP0805331A3 EP0805331A3 (de) 1998-07-08

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP97302896A Withdrawn EP0805331A3 (de) 1996-04-30 1997-04-28 Multiröhren-Wärmetauscher

Country Status (2)

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EP (1) EP0805331A3 (de)
JP (1) JPH09296994A (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2799826A1 (fr) * 1999-09-28 2001-04-20 Valeo Thermique Moteur Sa Echangeur de chaleur brase de structure compacte, en particulier pour vehicule automobile
EP1598626A1 (de) * 2004-05-19 2005-11-23 Outokumpu Oyj Hochdruck, Hochtemperatur Ladeluftkühler
WO2007082515A1 (de) * 2006-01-23 2007-07-26 Alstom Technology Ltd. Rohrbündel-wärmetauscher
US8177932B2 (en) 2009-02-27 2012-05-15 International Mezzo Technologies, Inc. Method for manufacturing a micro tube heat exchanger
US10094626B2 (en) 2015-10-07 2018-10-09 Arvos Ljungstrom Llc Alternating notch configuration for spacing heat transfer sheets
US10175006B2 (en) 2013-11-25 2019-01-08 Arvos Ljungstrom Llc Heat transfer elements for a closed channel rotary regenerative air preheater
US10197337B2 (en) 2009-05-08 2019-02-05 Arvos Ljungstrom Llc Heat transfer sheet for rotary regenerative heat exchanger
US10378829B2 (en) 2012-08-23 2019-08-13 Arvos Ljungstrom Llc Heat transfer assembly for rotary regenerative preheater

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105423777B (zh) * 2015-12-29 2018-02-13 山东利能换热器有限公司 联箱体壳管联通承压换热器
CN105627627B (zh) * 2016-01-21 2017-10-31 徐明海 一种桩基埋管换热器pe管与钢筋间自锁固定装置及方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2031668A5 (de) * 1969-02-03 1970-11-20 Chausson Usines Sa
EP0567410A1 (de) * 1992-04-24 1993-10-27 Valeo Thermique Moteur Wärmetauscher mit Röhren mit länglichem Querschnitt, insbesondere für Kraftfahrzeuge
DE4325427A1 (de) * 1993-07-29 1995-02-02 Behr Gmbh & Co Wärmetauscher, insbesondere Kraftfahrzeugkühler
EP0693666A2 (de) * 1994-07-22 1996-01-24 Mitsubishi Denki Kabushiki Kaisha Wärmetauscher für Klimaanlage und Verfahren zu dessen Herstellung
EP0802386A1 (de) * 1996-04-17 1997-10-22 Sanden Corporation Rohrbündel-Wärmetauscher

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2031668A5 (de) * 1969-02-03 1970-11-20 Chausson Usines Sa
EP0567410A1 (de) * 1992-04-24 1993-10-27 Valeo Thermique Moteur Wärmetauscher mit Röhren mit länglichem Querschnitt, insbesondere für Kraftfahrzeuge
DE4325427A1 (de) * 1993-07-29 1995-02-02 Behr Gmbh & Co Wärmetauscher, insbesondere Kraftfahrzeugkühler
EP0693666A2 (de) * 1994-07-22 1996-01-24 Mitsubishi Denki Kabushiki Kaisha Wärmetauscher für Klimaanlage und Verfahren zu dessen Herstellung
EP0802386A1 (de) * 1996-04-17 1997-10-22 Sanden Corporation Rohrbündel-Wärmetauscher

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2799826A1 (fr) * 1999-09-28 2001-04-20 Valeo Thermique Moteur Sa Echangeur de chaleur brase de structure compacte, en particulier pour vehicule automobile
EP1598626A1 (de) * 2004-05-19 2005-11-23 Outokumpu Oyj Hochdruck, Hochtemperatur Ladeluftkühler
US6997248B2 (en) 2004-05-19 2006-02-14 Outokumpu Oyj High pressure high temperature charge air cooler
WO2007082515A1 (de) * 2006-01-23 2007-07-26 Alstom Technology Ltd. Rohrbündel-wärmetauscher
US9534850B2 (en) 2006-01-23 2017-01-03 Arvos Technology Limited Tube bundle heat exchanger
US10914527B2 (en) 2006-01-23 2021-02-09 Arvos Gmbh Tube bundle heat exchanger
US8177932B2 (en) 2009-02-27 2012-05-15 International Mezzo Technologies, Inc. Method for manufacturing a micro tube heat exchanger
US10982908B2 (en) 2009-05-08 2021-04-20 Arvos Ljungstrom Llc Heat transfer sheet for rotary regenerative heat exchanger
US10197337B2 (en) 2009-05-08 2019-02-05 Arvos Ljungstrom Llc Heat transfer sheet for rotary regenerative heat exchanger
US10378829B2 (en) 2012-08-23 2019-08-13 Arvos Ljungstrom Llc Heat transfer assembly for rotary regenerative preheater
US11092387B2 (en) 2012-08-23 2021-08-17 Arvos Ljungstrom Llc Heat transfer assembly for rotary regenerative preheater
US10175006B2 (en) 2013-11-25 2019-01-08 Arvos Ljungstrom Llc Heat transfer elements for a closed channel rotary regenerative air preheater
US10094626B2 (en) 2015-10-07 2018-10-09 Arvos Ljungstrom Llc Alternating notch configuration for spacing heat transfer sheets

Also Published As

Publication number Publication date
JPH09296994A (ja) 1997-11-18
EP0805331A3 (de) 1998-07-08

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