[go: up one dir, main page]

WO2013118527A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

Info

Publication number
WO2013118527A1
WO2013118527A1 PCT/JP2013/050225 JP2013050225W WO2013118527A1 WO 2013118527 A1 WO2013118527 A1 WO 2013118527A1 JP 2013050225 W JP2013050225 W JP 2013050225W WO 2013118527 A1 WO2013118527 A1 WO 2013118527A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
fin
case
heat exchanger
stainless steel
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.)
Ceased
Application number
PCT/JP2013/050225
Other languages
French (fr)
Japanese (ja)
Inventor
文彦 石黒
井口　雅夫
英文 森
榎島　史修
智則 佐々木
和雄 片山
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries 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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of WO2013118527A1 publication Critical patent/WO2013118527A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • 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
    • F28F1/24—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 transversely
    • F28F1/32—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 transversely the means having portions engaging further tubular elements
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F28F21/083—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys from stainless steel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the present invention relates to a heat exchanger, and more particularly, to a heat exchanger including a tube through which a working fluid passes and fins for heat exchange fixed to the tube.
  • the heat exchanger includes a heat transfer tube formed of stainless steel and aluminum plate fins. A number of collars corresponding to the number of heat transfer tubes are formed on the plate fins. The plurality of heat medium tubes inserted in the respective collars are arranged in parallel to each other. The heat transfer tube inserted into the collar is brazed to the collar.
  • Stainless steel plate fins are provided near the connection of the heat transfer tube, and a U-shaped bend tube that connects the heat transfer tube is brazed to the connection of the heat transfer tube on the outside of the stainless plate fin. Has been. Further, a stainless steel plate is brazed to the flat portion formed on the aluminum plate fin.
  • the heat exchanger of Patent Document 1 has a problem in heat resistance because the plate fins are made of aluminum.
  • the heat exchanger cannot be used in an environment where the temperature is high, for example, 400 ° C. or higher.
  • An object of the present invention is to provide a heat exchanger capable of preventing a brazed portion between a tube and a fin and breakage or cracking of the fin due to occurrence of a difference in thermal expansion amount in the tube.
  • an aspect of the present invention includes a plurality of straight pipe portions arranged in parallel to each other, a tube through which a working fluid is passed, and a plurality of straight pipe portions into which the plurality of straight pipe portions are respectively inserted.
  • a heat exchanger having a through hole and a fin brazed to the plurality of straight pipe portions.
  • the heat exchanger is configured to exchange heat between the heating fluid around the fin and the working fluid.
  • the tube and the fin are made of stainless steel, and the linear expansion coefficient of the stainless steel forming the tube is smaller than the linear expansion coefficient of the stainless steel forming the fin.
  • the fin when the working fluid flows through the tube, heat exchange with the heating fluid is performed through the tube and the fin.
  • a difference in thermal expansion occurs between the plurality of straight pipe portions. Due to the difference in the amount of thermal expansion in the tube, even if the tube is deformed to pull the portion between the straight tube portions of the fin, the fin has a larger coefficient of linear expansion than the tube, so it deforms following the deformation of the fin. be able to.
  • the stress acting on the part between the straight pipe parts of the fin and the brazed part between the tube and the fin is reduced, and the part between the straight pipe part of the fin and the brazed part between the tube and the fin are reduced. Can prevent damage.
  • the heat exchanger of this embodiment is a vehicle-mounted heat exchanger mounted on a vehicle.
  • the heat exchanger is an in-vehicle heat exchanger provided in a Rankine cycle circuit that uses waste heat of an engine as an internal combustion engine mounted on a vehicle and converts the heat energy of the waste heat into mechanical energy.
  • the heat exchanger 11 shown in FIG. 1 is installed in the exhaust pipe 10 through which the combustion gas of the engine (shown by the white arrow in FIG. 1) flows.
  • the heat exchanger 11 includes a tube 12 through which a refrigerant as a working fluid passes, a large number of fins 13 brazed to the tube 12, and a case 14 that houses the tubes 12 and the fins 13.
  • a known refrigerant that changes from a liquid phase to a gas phase in the heat exchanger 11 is used.
  • the tube 12 is a single continuous tube that is horizontally passed from the upper part of the case 14 to the inside of the case 14, repeatedly folded inside and outside the case 14, and passed from the lower part of the case 14 to the outside. Yes.
  • the tube 12 includes an inlet pipe portion 15 located at an upper portion of the case 14, a straight pipe portion 16 disposed horizontally in the case 14, an internal bent pipe portion 17 folded in the case 14, An external curved pipe portion 18 that is folded back outside, and an outlet pipe portion 19 that is located at the lower portion of the case 14 are provided.
  • a plurality of straight pipe portions 16 are arranged in multiple stages in the vertical direction in the case 14.
  • the straight pipe part 16 in which the refrigerant flows from the inlet pipe part 15 or the external curved pipe part 18 to the internal curved pipe part 17 is arranged at a position downstream of the combustion gas in the case 14.
  • the straight pipe part 16 through which the refrigerant flows from the inner curved pipe part 17 to the outer curved pipe part 18 or the outlet pipe part 19 is arranged at a position upstream of the combustion gas in the case 14.
  • the tube 12 is formed of ferritic stainless steel (SUS430, linear expansion coefficient: 10.8 ⁇ 10 ⁇ 6 [1 / K]).
  • the case 14 includes a top plate 20, a bottom plate 21, and a pair of side plates 22 and 23. A plurality of through holes 24 through which the tube 12 is inserted are formed in one side plate 22. The other side plate 23 is disposed so as to face the internal curved pipe portion 17.
  • the case 14 accommodates the straight pipe portion 16 and the internal bent pipe portion 17 of the tube 12 and supports the tube 12 and the fins 13.
  • the case 14 is formed of austenitic stainless steel (SUS304, linear expansion coefficient: 17.3 ⁇ 10 ⁇ 6 [1 / K]).
  • Each fin 13 is a metal plate formed of austenitic stainless steel (SUS304, linear expansion coefficient: 17.3 ⁇ 10 ⁇ 6 [1 / K]). Each fin 13 is formed with a plurality of through holes 25 through which the straight pipe portion 16 is inserted.
  • the flow path of the combustion gas between the side plates 22 and 23 of the case 14 is partitioned by a large number of fins 13, and the surface of the fin 13 is orthogonal to the flow direction of the combustion gas.
  • a gap is formed between adjacent fins 13. As the combustion gas flows through this gap, the heat of the combustion gas is transmitted to the fins 13.
  • FIG. 2 a part of the inlet pipe part 15 of the tube 12, a part of the straight pipe part 16, the inner curved pipe part 17 and the outer curved pipe part 18 are shown, and the outlet pipe part 19 and the bottom plate 21 are shown. Not.
  • an internal curved pipe portion 17 is connected to the upstream straight pipe portion 16 connected to the inlet pipe portion 15.
  • the downstream straight pipe part 16 connected to the internal curved pipe part 17 is arranged in parallel with the upstream straight pipe part 16 and connected to the external curved pipe part 18 outside the case 14.
  • a brazing material is filled between the tube 12 inserted into the through hole 24 of the side plate 22 and the side plate 22. As shown in FIG. 2, the tube 12 is fixed to the side plate 22 at the brazing point AA filled with the brazing material.
  • a brazing material is filled between the straight pipe portion 16 of the tube 12 inserted into the through hole 25 of the fin 13 and the fin 13.
  • the brazing point located so as to face the top plate 20 is defined as a brazing point B1.
  • a brazing point positioned so as to face the pipe portion 16 is defined as a brazing point B2.
  • the brazing point positioned so as to face the upstream straight pipe portion 16 is defined as a brazing point B3.
  • a brazing point located on the side opposite to the point B3 is defined as a brazing point B4.
  • the fin 13 is fixed to the upstream straight pipe portion 16 at the brazing locations B1 and B2 filled with the brazing material, and is fixed to the downstream straight pipe portion 16 at the brazing locations B3 and B4. .
  • a rising portion 26 formed during burring is provided around the through hole 25 of the fin 13.
  • the rising portion 26 formed on the fin 13 makes it easy to support the tube 12 and also makes it easy to set the gaps between the adjacent fins 13 at equal intervals.
  • the brazing material between the straight pipe portion 16 and the fin 13 has a function of improving the heat transfer performance between the fin 13 and the tube 12 in addition to a function of fixing the fin 13 and the tube 12.
  • the fin 13 includes a portion 13AA between the adjacent through holes 25, that is, a portion 13AA between the straight pipe portions 16 adjacent to each other.
  • the part 13AA of the fin 13 is also a part formed between the brazing points B2 and B3.
  • the upper end of the fin 13 is joined to the top plate 20 via a brazing material, and the lower end of the fin 13 is joined to the bottom plate 21 via a brazing material.
  • the fin 13 is fixed to the top plate 20 at a brazing point C where the upper end of the fin 13 and the top plate 20 are joined.
  • the fin 13 is fixed to the bottom plate 21 at a brazing point where the lower end of the fin 13 and the bottom plate 21 are joined.
  • the brazing material at the brazing point C of the top plate 20 and the brazing point of the bottom plate 21 has a function of preventing vibration of the fins 13 due to the flow of combustion gas.
  • brazing materials used in the brazing points AA, B1 to B4, and C are the same material, and the mechanical strength of these brazing materials is smaller than that of the tube 12, the fin 13 and the case 14.
  • the combustion gas of the engine passes through the exhaust pipe 10 and passes through the heat exchanger 11.
  • the combustion gas passing through the heat exchanger 11 flows along the surfaces of the numerous fins 13.
  • the fin 13 is heated by the high-temperature combustion gas.
  • the refrigerant flows through the tube 12 of the heat exchanger 11.
  • the refrigerant exchanges heat with the combustion gas through the fins 13, the brazing material joining the tubes 12 and the fins 13 and the tubes 12.
  • the refrigerant passing through the tube 12 is in a liquid phase when introduced into the heat exchanger 11 from the inlet pipe portion 15, but changes from the liquid phase to the gas phase when heated by heat exchange with the combustion gas.
  • the refrigerant changed to the gas phase exits the heat exchanger 11 and passes through the outlet pipe portion 19.
  • the tube 12 is made of ferritic stainless steel having a smaller linear expansion coefficient than the austenitic stainless steel forming the fins 13. Therefore, the thermal expansion amount of the tube 12 is smaller than the thermal expansion amount of the fin 13.
  • the tube 12 has a difference in thermal expansion amount depending on the part.
  • the upstream straight pipe portion 16 When exchanging heat between the working fluid and the heating fluid, the upstream straight pipe portion 16 close to the inlet pipe portion 15 of the tube 12 shown in FIG. A difference occurs in the amount of thermal expansion in the straight pipe portion 16 on the near downstream side. If the thermal expansion amount of the downstream straight pipe portion 16 is larger than the thermal expansion amount of the upstream straight pipe portion 16, the downstream straight pipe portion 16 extends more in the longitudinal direction than the upstream straight pipe portion 16. .
  • the difference in the amount of thermal expansion between the straight pipe portions 16 tries to pull the portion 13AA between the brazing points B2 and B3 in the fin 13.
  • the linear expansion coefficient of the fin 13 is larger than the linear expansion coefficient of the tube 12
  • the portion 13AA of the fin 13 can be deformed following the deformation of the tube 12.
  • the stress acting on the part 13AA and the brazing points B2 and B3 in the fin 13 is reduced, and cracks and breaks in the part 13AA and the brazing points B2 and B3 in the fin 13 can be prevented.
  • the case 14 is made of austenitic stainless steel having a linear expansion coefficient larger than that of the ferritic stainless steel, but since it is cooled to the outside air, the difference in thermal expansion between the tube 12 and the case 14 is small. For this reason, the stress at the brazing point AA between the tube 12 and the case 14 is reduced, and damage to the brazing point AA is prevented.
  • the case 14 is formed of the same material as the fin 13, the temperature of the case 14 is lower than the temperature of the fin 13, so that a difference occurs in the amount of thermal expansion between the case 14 and the fin 13.
  • the heat exchanger according to this embodiment has the following operational effects.
  • the tube 12, the fin 13 and the case 14 of the heat exchanger are made of stainless steel, the tube 12, the fin 13 and the case 14 are excellent in heat resistance and corrosion resistance. Therefore, high-temperature (about 800 ° C.) combustion gas can be used as the heating fluid. For this reason, even if the internal combustion engine is a diesel engine or a gasoline engine, the combustion gas of the engine can be used as a heating fluid.
  • the linear expansion coefficient of the tube 12 is smaller than the linear expansion coefficient of the case 14. For this reason, even if the tube 12 has a higher temperature than the case 14, the difference in thermal expansion between the tube 12 and the case 14 can be reduced, and the tube 12 is brazed to support the case 14. The stress to the location AA can be reduced.
  • the manufacturing cost of the heat exchanger 11 can be reduced as compared with the case where the fin 13 and the case 14 are formed of different materials. .
  • the heat exchanger 11 can be used as a steam generator for the Rankine cycle circuit.
  • the heat exchanger of the present embodiment is different from the first embodiment in the case material.
  • the configuration of the heat exchanger of the present embodiment is the same as that of the first embodiment except that the material forming the case is different, and the description of the first embodiment is used and common symbols are used.
  • the case 14 of the heat exchanger 11 of the present embodiment is made of the same ferritic stainless steel (SUS430, linear expansion coefficient: 10.8 ⁇ 10 ⁇ 6 [1 / K]).
  • the amount of thermal expansion between the case 14 and the tube 12 is the same, and when the temperature difference between the tube 12 and the case 14 is small, the difference in the amount of thermal expansion between the tube 12 and the case 14. Can be reduced, and the stress at the brazing point AA can be reduced.
  • the heat exchanger 11 of the present embodiment has the same operational effects as the operational effects (1) to (3) and (6) of the first embodiment.
  • the case 14 is made of the same ferritic stainless steel as the tube 12, the linear expansion coefficient of the case 14 is smaller than the linear expansion coefficient of the austenitic stainless steel. Therefore, compared with the case where the material of the tube 12 and the case 14 is austenitic stainless steel, the difference in the amount of thermal expansion between the tube 12 and the case 14 can be reduced. Moreover, since the tube 12 and the case 14 are formed of the same material, the manufacturing cost of the heat exchanger 11 can be suppressed as compared with the case where the tube 12 and the case 14 are formed of different materials.
  • the heat exchanger of the third embodiment is different from the first embodiment in the materials of the tubes and fins.
  • the configuration of the heat exchanger of the present embodiment is the same as that of the first embodiment except that the materials forming the tubes and the fins are different, and the description of the first embodiment is used and common reference numerals are used.
  • the tube 12 of the heat exchanger 11 of this embodiment is formed of martensitic stainless steel (SUS410, linear expansion coefficient: 10.1 ⁇ 10 ⁇ 6 [1 / K]).
  • the fin 13 is made of ferritic stainless steel (SUS430, linear expansion coefficient: 10.8 ⁇ 10 ⁇ 6 [1 / K]).
  • the case 14 is made of austenitic stainless steel (SUS304, linear expansion coefficient: 17.3 ⁇ 10 ⁇ 6 [1 / K]).
  • the linear expansion coefficient of martensitic stainless steel is smaller than that of ferritic stainless steel, and that of ferritic stainless steel is smaller than that of austenitic stainless steel.
  • the material is set so that the linear expansion coefficient increases in the order of the tube 12, the fin 13, and the case 14. Therefore, even if there is a difference in the amount of thermal expansion between the straight pipe portions 16 adjacent to each other in the tube 12, as in the first embodiment, cracks and breaks at the portion 13AA of the fin 13 and the brazed portion near the portion 13AA. Can be prevented. Moreover, the difference in the amount of thermal expansion between the fin 13 and the case 14 can be reduced, and the stress at the brazing point C can be reduced.
  • the fin 13 having a larger linear expansion coefficient than that of the tube 12 and capable of becoming a high temperature is thermally expanded larger than that of the tube 12, so that the fin 13 is deformed more than the tube 12.
  • the case 14 formed of a material having a larger linear expansion coefficient than that of the fin 13 can reduce the difference in thermal expansion amount between the fin 13 and the case 14. Therefore, even when the fin 13 and the case 14 are brazed, damage to the brazed portion C between the fin 13 and the case 14 can be prevented.
  • SUS304 is used as the austenitic stainless steel, but SUS316 or SUS316L may be used.
  • SUS430 is used as the ferritic stainless steel, but SUS444 having a small linear expansion coefficient may be used.
  • the case and the fin are fixed to each other by brazing, but the case and the fin are not necessarily fixed to each other. In this case, it is preferable that measures for preventing the vibration of the fins are taken by another means.
  • the refrigerant that changes phase by heat exchange is used as the working fluid, but the working fluid is not limited to the refrigerant that changes phase.
  • the working fluid for example, a fluid that maintains a liquid phase even when heat exchange with the heating fluid may be used.
  • the heating fluid is not limited to the combustion gas, and may be any fluid that can heat the working fluid by heat exchange.
  • the heat exchanger is a heat exchanger used in a Rankine cycle circuit, but the heat exchanger of the present invention can be used as a heat exchanger other than the Rankine cycle circuit.
  • the heat exchanger was used as the vehicle-mounted heat exchanger, it is not limited to a vehicle-mounted heat exchanger, For example, the heat exchanger installed on the ground may be sufficient.
  • phyllite stainless steel is used as the tube material and austenitic stainless steel is used as the fin material.
  • the tube material may be martensitic stainless steel
  • the fin (and case) material may be austenitic stainless steel.
  • the material of the tube and the fin may be at least stainless steel, and the tube may be a combination of materials whose linear expansion coefficient is smaller than that of the fin.

Landscapes

  • 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)

Description

熱交換器Heat exchanger

　この発明は、熱交換器に関し、特に、作動流体を通すチューブと、チューブに固定された熱交換のためのフィンとを備えた熱交換器に関する。 The present invention relates to a heat exchanger, and more particularly, to a heat exchanger including a tube through which a working fluid passes and fins for heat exchange fixed to the tube.

　従来の熱交換器として、例えば、特許文献１に開示されたアルミニウム－ステンレス製型の熱交換器が知られている。その熱交換器は、ステンレス鋼により形成された熱媒管と、アルミニウム製のプレートフィンとを備えている。プレートフィンには熱媒管の数に対応する多数のカラーが形成されている。それぞれのカラーに挿入された複数の熱媒管は互いに平行となるように配置されている。カラーに挿入された熱媒管はカラーにろう付けされている。 As a conventional heat exchanger, for example, an aluminum-stainless steel type heat exchanger disclosed in Patent Document 1 is known. The heat exchanger includes a heat transfer tube formed of stainless steel and aluminum plate fins. A number of collars corresponding to the number of heat transfer tubes are formed on the plate fins. The plurality of heat medium tubes inserted in the respective collars are arranged in parallel to each other. The heat transfer tube inserted into the collar is brazed to the collar.

　熱媒管の接続部近傍には、ステンレス製のプレートフィンが設けられ、ステンレス製のプレートフィンの外側には熱媒管を接続するＵ字状のベンド管が熱媒管の接続部にろう付けされている。また、アルミニウム製のプレートフィンに形成された平面部にはステンレス製の板がろう付けされている。 Stainless steel plate fins are provided near the connection of the heat transfer tube, and a U-shaped bend tube that connects the heat transfer tube is brazed to the connection of the heat transfer tube on the outside of the stainless plate fin. Has been. Further, a stainless steel plate is brazed to the flat portion formed on the aluminum plate fin.

実開平６－３０６７８号公報Japanese Utility Model Publication No. 6-30678

　しかしながら、特許文献１の熱交換器では、アルミニウム製のプレートフィンにろう付けされた複数の熱媒管の間で温度が異なると、熱媒管の間で熱膨張量に差が生じる。このとき、プレートフィンにおける熱膨張量に差が生じた熱媒管の間の部位には熱膨張量の差に基づく引っ張りの応力が作用する。そのため、プレートフィンにおける熱膨張量の差が生じた熱媒管の間の部位や、熱媒管とカラーとの間のろう付け箇所に破断や亀裂が生じるおそれがあるという問題がある。 However, in the heat exchanger of Patent Document 1, if the temperature is different among a plurality of heat medium tubes brazed to aluminum plate fins, a difference in the amount of thermal expansion occurs between the heat medium tubes. At this time, tensile stress based on the difference in the amount of thermal expansion acts on the portion between the heat transfer medium tubes where the difference in the amount of thermal expansion in the plate fins occurs. Therefore, there exists a problem that there exists a possibility that a fracture | rupture or a crack may arise in the location between the heat-medium pipe | tubes in which the difference of the thermal expansion amount in a plate fin produced, and the brazing location between a heat-medium pipe | tube and a collar | collar.

　また、特許文献１の熱交換器は、プレートフィンがアルミニウム製であるため耐熱性に問題がある。該熱交換器は、例えば、４００℃以上の高温となる環境では使用不可能である。 Also, the heat exchanger of Patent Document 1 has a problem in heat resistance because the plate fins are made of aluminum. The heat exchanger cannot be used in an environment where the temperature is high, for example, 400 ° C. or higher.

　本発明の目的は、チューブにおける熱膨張量の差の発生によるチューブとフィンとの間のろう付け箇所やフィンの破断や亀裂を防止することができる熱交換器の提供にある。 An object of the present invention is to provide a heat exchanger capable of preventing a brazed portion between a tube and a fin and breakage or cracking of the fin due to occurrence of a difference in thermal expansion amount in the tube.

　上記目的を達成するために、本発明の一態様は、互いに並列に配置される複数の直管部を有するとともに、作動流体を通すチューブと、前記複数の直管部がそれぞれ挿入される複数の通孔を有するとともに、前記複数の直管部にろう付けされたフィンと、を備える熱交換器を提供する。熱交換器は、前記フィンの周囲の加熱流体と前記作動流体との間で熱交換を行うように構成される。前記チューブおよび前記フィンはステンレス鋼により形成され、前記チューブを形成するステンレス鋼の線膨張率は、前記フィンを形成するステンレス鋼の線膨張率より小さい。 In order to achieve the above object, an aspect of the present invention includes a plurality of straight pipe portions arranged in parallel to each other, a tube through which a working fluid is passed, and a plurality of straight pipe portions into which the plurality of straight pipe portions are respectively inserted. Provided is a heat exchanger having a through hole and a fin brazed to the plurality of straight pipe portions. The heat exchanger is configured to exchange heat between the heating fluid around the fin and the working fluid. The tube and the fin are made of stainless steel, and the linear expansion coefficient of the stainless steel forming the tube is smaller than the linear expansion coefficient of the stainless steel forming the fin.

　本発明によれば、作動流体がチューブ内を流れるとき、チューブおよびフィンを通じて加熱流体と熱交換が行われる。作動流体と加熱流体との間の熱交換の際、複数の直管部の間において熱膨張量に差が生じる。このチューブにおける熱膨張量の差により、フィンにおける直管部間の部位を引っ張ろうとする変形がチューブに生じても、フィンはチューブよりも線膨張率が大きいためフィンの変形に追従して変形することができる。その結果、フィンにおける直管部間の部位や、チューブとフィンとの間のろう付け箇所に作用する応力が軽減され、フィンにおける直管部間の部位およびチューブとフィンとの間のろう付け箇所の損傷を防止することができる。 According to the present invention, when the working fluid flows through the tube, heat exchange with the heating fluid is performed through the tube and the fin. During heat exchange between the working fluid and the heating fluid, a difference in thermal expansion occurs between the plurality of straight pipe portions. Due to the difference in the amount of thermal expansion in the tube, even if the tube is deformed to pull the portion between the straight tube portions of the fin, the fin has a larger coefficient of linear expansion than the tube, so it deforms following the deformation of the fin. be able to. As a result, the stress acting on the part between the straight pipe parts of the fin and the brazed part between the tube and the fin is reduced, and the part between the straight pipe part of the fin and the brazed part between the tube and the fin are reduced. Can prevent damage.

本発明の第１の実施形態に係る熱交換器の概要を示す斜視図である。It is a perspective view which shows the outline | summary of the heat exchanger which concerns on the 1st Embodiment of this invention. 第１の実施形態に係る熱交換器の要部を破断して示す縦断面図である。It is a longitudinal cross-sectional view which fractures | ruptures and shows the principal part of the heat exchanger which concerns on 1st Embodiment.

（第１の実施形態）
　以下、本発明の第１の実施形態に係る熱交換器について図面を参照して説明する。 (First embodiment)
Hereinafter, a heat exchanger according to a first embodiment of the present invention will be described with reference to the drawings.

　本実施形態の熱交換器は、車両に搭載される車載用熱交換器である。熱交換器は、特に、車両に搭載された内燃機関としてのエンジンの廃熱を利用し、廃熱の熱エネルギーを機械的エネルギーに変換するランキンサイクル回路に設けられる車載用熱交換器である。 The heat exchanger of this embodiment is a vehicle-mounted heat exchanger mounted on a vehicle. In particular, the heat exchanger is an in-vehicle heat exchanger provided in a Rankine cycle circuit that uses waste heat of an engine as an internal combustion engine mounted on a vehicle and converts the heat energy of the waste heat into mechanical energy.

　図１に示す熱交換器１１は、エンジンの燃焼ガス（図１の白抜矢印により示す）が流通する排気管１０内に設置されている。熱交換器１１は、作動流体としての冷媒を通すチューブ１２と、チューブ１２にろう付けされた多数のフィン１３と、チューブ１２およびフィン１３を収容するケース１４とを備えている。 The heat exchanger 11 shown in FIG. 1 is installed in the exhaust pipe 10 through which the combustion gas of the engine (shown by the white arrow in FIG. 1) flows. The heat exchanger 11 includes a tube 12 through which a refrigerant as a working fluid passes, a large number of fins 13 brazed to the tube 12, and a case 14 that houses the tubes 12 and the fins 13.

　本実施形態の作動流体として、熱交換器１１において液相から気相へ変化する公知の冷媒が用いられている。 As the working fluid of the present embodiment, a known refrigerant that changes from a liquid phase to a gas phase in the heat exchanger 11 is used.

　チューブ１２は連続する一本の管であり、ケース１４の上部からケース１４の内部に水平方向へ通され、ケース１４の内部および外部で折り返し繰り返されて、ケース１４の下部から外部へ通されている。チューブ１２は、ケース１４の上部に位置する入口管部１５と、ケース１４内にて水平に配設された直管部１６と、ケース１４内で折り返される内部曲管部１７と、ケース１４の外部で折り返される外部曲管部１８と、ケース１４の下部に位置する出口管部１９とを備えている。 The tube 12 is a single continuous tube that is horizontally passed from the upper part of the case 14 to the inside of the case 14, repeatedly folded inside and outside the case 14, and passed from the lower part of the case 14 to the outside. Yes. The tube 12 includes an inlet pipe portion 15 located at an upper portion of the case 14, a straight pipe portion 16 disposed horizontally in the case 14, an internal bent pipe portion 17 folded in the case 14, An external curved pipe portion 18 that is folded back outside, and an outlet pipe portion 19 that is located at the lower portion of the case 14 are provided.

　本実施形態では、ケース１４内に複数の直管部１６が上下方向に多段に配置されている。直管部１６のうち、冷媒が入口管部１５または外部曲管部１８から内部曲管部１７へ流れる直管部１６は、ケース１４において燃焼ガスの下流側の位置に配置されている。また、冷媒が内部曲管部１７から外部曲管部１８又は出口管部１９流れる直管部１６は、ケース１４において燃焼ガスの上流側の位置に配置されている。表１に示すように、本実施形態では、チューブ１２はフェライト系ステンレス鋼（ＳＵＳ４３０、線膨張率：１０．８×１０－６［１／Ｋ］）により形成されている。 In the present embodiment, a plurality of straight pipe portions 16 are arranged in multiple stages in the vertical direction in the case 14. Of the straight pipe part 16, the straight pipe part 16 in which the refrigerant flows from the inlet pipe part 15 or the external curved pipe part 18 to the internal curved pipe part 17 is arranged at a position downstream of the combustion gas in the case 14. Further, the straight pipe part 16 through which the refrigerant flows from the inner curved pipe part 17 to the outer curved pipe part 18 or the outlet pipe part 19 is arranged at a position upstream of the combustion gas in the case 14. As shown in Table 1, in this embodiment, the tube 12 is formed of ferritic stainless steel (SUS430, linear expansion coefficient: 10.8 × 10 −6 [1 / K]).

Figure JPOXMLDOC01-appb-T000001
Figure JPOXMLDOC01-appb-T000001

　フェライト系ステンレス鋼
　　ＳＵＳ４３０、線膨張率：１０．８×１０－６［１／Ｋ］
　オーステナイト系ステンレス鋼
　　ＳＵＳ３０４、線膨張率：１７．３×１０－６［１／Ｋ］
　マルテンサイト系ステンレス鋼
　　ＳＵＳ４１０、線膨張率：１０．１×１０－６［１／Ｋ］
　ケース１４は、天板２０と底板２１と一対の側板２２、２３とを備えている。一方の側板２２にはチューブ１２を挿通する複数の通孔２４が形成されている。他方の側板２３は内部曲管部１７と対向するように配置されている。ケース１４は、チューブ１２の直管部１６、及び内部曲管部１７を収容し、チューブ１２およびフィン１３を支持する。本実施形態では、ケース１４はオーステナイト系ステンレス鋼（ＳＵＳ３０４、線膨張率：１７．３×１０－６［１／Ｋ］）により形成されている。 Ferritic stainless steel SUS430, linear expansion coefficient: 10.8 × 10 −6 [1 / K]
Austenitic stainless steel SUS304, linear expansion coefficient: 17.3 × 10 −6 [1 / K]
Martensitic stainless steel SUS410, linear expansion coefficient: 10.1 × 10 −6 [1 / K]
The case 14 includes a top plate 20, a bottom plate 21, and a pair of side plates 22 and 23. A plurality of through holes 24 through which the tube 12 is inserted are formed in one side plate 22. The other side plate 23 is disposed so as to face the internal curved pipe portion 17. The case 14 accommodates the straight pipe portion 16 and the internal bent pipe portion 17 of the tube 12 and supports the tube 12 and the fins 13. In this embodiment, the case 14 is formed of austenitic stainless steel (SUS304, linear expansion coefficient: 17.3 × 10 −6 [1 / K]).

　ケース１４内に配置されるチューブ１２の直管部１６には、多数のフィン１３が装着されている。各フィン１３はオーステナイト系ステンレス鋼（ＳＵＳ３０４、線膨張率：１７．３×１０－６［１／Ｋ］）により形成された金属板である。各フィン１３には直管部１６をそれぞれ挿通する複数の通孔２５が形成されている。 A large number of fins 13 are attached to the straight pipe portion 16 of the tube 12 disposed in the case 14. Each fin 13 is a metal plate formed of austenitic stainless steel (SUS304, linear expansion coefficient: 17.3 × 10 −6 [1 / K]). Each fin 13 is formed with a plurality of through holes 25 through which the straight pipe portion 16 is inserted.

　ケース１４の側板２２、２３間の燃焼ガスの流路は、多数のフィン１３により仕切られ、フィン１３の面は燃焼ガスの流れ方向と直交する。 The flow path of the combustion gas between the side plates 22 and 23 of the case 14 is partitioned by a large number of fins 13, and the surface of the fin 13 is orthogonal to the flow direction of the combustion gas.

　互いに隣り合うフィン１３の間には隙間が形成されている。この隙間に燃焼ガスが流通することにより、燃焼ガスの熱がフィン１３に伝達する。 A gap is formed between adjacent fins 13. As the combustion gas flows through this gap, the heat of the combustion gas is transmitted to the fins 13.

　図２を参照してチューブ１２とケース１４との間の固定、チューブ１２とフィン１３との間の固定およびフィン１３とケース１４との間の固定について説明する。 The fixing between the tube 12 and the case 14, the fixing between the tube 12 and the fin 13, and the fixing between the fin 13 and the case 14 will be described with reference to FIG.

　なお、図２では、チューブ１２の入口管部１５の一部、直管部１６、内部曲管部１７および外部曲管部１８の一部が図示され、出口管部１９および底板２１は図示されていない。 In FIG. 2, a part of the inlet pipe part 15 of the tube 12, a part of the straight pipe part 16, the inner curved pipe part 17 and the outer curved pipe part 18 are shown, and the outlet pipe part 19 and the bottom plate 21 are shown. Not.

　図２では、入口管部１５と接続される上流側の直管部１６には、内部曲管部１７が接続されている。内部曲管部１７に接続される下流側の直管部１６は、上流側の直管部１６と並列に配置されて、ケース１４の外側の外部曲管部１８と接続されている。 In FIG. 2, an internal curved pipe portion 17 is connected to the upstream straight pipe portion 16 connected to the inlet pipe portion 15. The downstream straight pipe part 16 connected to the internal curved pipe part 17 is arranged in parallel with the upstream straight pipe part 16 and connected to the external curved pipe part 18 outside the case 14.

　側板２２の通孔２４に挿通したチューブ１２と側板２２との間には、ろう材が充填されている。図２に示すように、ろう材が充填されたろう付け箇所ＡＡにおいてチューブ１２は側板２２に固定されている。 A brazing material is filled between the tube 12 inserted into the through hole 24 of the side plate 22 and the side plate 22. As shown in FIG. 2, the tube 12 is fixed to the side plate 22 at the brazing point AA filled with the brazing material.

　フィン１３の通孔２５に挿入されたチューブ１２の直管部１６とフィン１３との間にろう材が充填されている。図２では、上流側の直管部１６とフィン１３との間のろう付け箇所のうち、天板２０と対向するように位置するろう付け箇所をろう付け箇所Ｂ１と定義し、下流側の直管部１６と対向するように位置するろう付け箇所をろう付け箇所Ｂ２と定義する。また、下流側の直管部１６とフィン１３との間のろう付け箇所のうち、上流側の直管部１６と対向するように位置するろう付け箇所をろう付け箇所Ｂ３と定義し、ろう付け箇所Ｂ３と反対側に位置するろう付け箇所をろう付け箇所Ｂ４と定義する。 A brazing material is filled between the straight pipe portion 16 of the tube 12 inserted into the through hole 25 of the fin 13 and the fin 13. In FIG. 2, of the brazing points between the straight pipe portion 16 on the upstream side and the fins 13, the brazing point located so as to face the top plate 20 is defined as a brazing point B1. A brazing point positioned so as to face the pipe portion 16 is defined as a brazing point B2. Of the brazing points between the downstream straight pipe portion 16 and the fins 13, the brazing point positioned so as to face the upstream straight pipe portion 16 is defined as a brazing point B3. A brazing point located on the side opposite to the point B3 is defined as a brazing point B4.

　フィン１３は、ろう材が充填されているろう付け箇所Ｂ１、Ｂ２において上流側の直管部１６に固定されるとともに、ろう付け箇所Ｂ３、Ｂ４において下流側の直管部１６に固定されている。 The fin 13 is fixed to the upstream straight pipe portion 16 at the brazing locations B1 and B2 filled with the brazing material, and is fixed to the downstream straight pipe portion 16 at the brazing locations B3 and B4. .

　通孔２５をバーリング加工により形成することから、図２に示すようにフィン１３の通孔２５の周囲には、バーリング加工時に形成される立ち上がり部２６が設けられている。フィン１３に形成された立ち上がり部２６は、チューブ１２を支持し易くするほか、互いに隣り合うフィン１３の間の隙間を等間隔に設定し易くする。 Since the through hole 25 is formed by burring, as shown in FIG. 2, a rising portion 26 formed during burring is provided around the through hole 25 of the fin 13. The rising portion 26 formed on the fin 13 makes it easy to support the tube 12 and also makes it easy to set the gaps between the adjacent fins 13 at equal intervals.

　直管部１６とフィン１３との間のろう材は、フィン１３とチューブ１２とを固定する機能のほか、フィン１３とチューブ１２との間の伝熱性能を向上する機能を有する。 The brazing material between the straight pipe portion 16 and the fin 13 has a function of improving the heat transfer performance between the fin 13 and the tube 12 in addition to a function of fixing the fin 13 and the tube 12.

　フィン１３は、互いに隣り合う通孔２５間の部位１３ＡＡ、つまり、互いに隣り合う直管部１６間の部位１３ＡＡを備えている。フィン１３の部位１３ＡＡは、ろう付け箇所Ｂ２、Ｂ３間に形成されている部位でもある。 The fin 13 includes a portion 13AA between the adjacent through holes 25, that is, a portion 13AA between the straight pipe portions 16 adjacent to each other. The part 13AA of the fin 13 is also a part formed between the brazing points B2 and B3.

　フィン１３の上端はろう材を介して天板２０に接合されており、フィン１３の下端はろう材を介して底板２１に接合されている。図２に示すように、フィン１３の上端と天板２０とを接合するろう付け箇所Ｃではフィン１３が天板２０に固定されている。図示はされないが、フィン１３の下端と底板２１とを接合するろう付け箇所ではフィン１３が底板２１に固定されている。天板２０のろう付け箇所Ｃおよび底板２１のろう付け箇所のろう材は、燃焼ガスの流通によるフィン１３の振動を防止する機能を有する。 The upper end of the fin 13 is joined to the top plate 20 via a brazing material, and the lower end of the fin 13 is joined to the bottom plate 21 via a brazing material. As shown in FIG. 2, the fin 13 is fixed to the top plate 20 at a brazing point C where the upper end of the fin 13 and the top plate 20 are joined. Although not shown, the fin 13 is fixed to the bottom plate 21 at a brazing point where the lower end of the fin 13 and the bottom plate 21 are joined. The brazing material at the brazing point C of the top plate 20 and the brazing point of the bottom plate 21 has a function of preventing vibration of the fins 13 due to the flow of combustion gas.

　なお、各ろう付け箇所ＡＡ、Ｂ１～Ｂ４、Ｃにおいて用いたろう材は同じ材料であり、これらのろう材の機械的強度はチューブ１２、フィン１３およびケース１４と比較して小さい。 Note that the brazing materials used in the brazing points AA, B1 to B4, and C are the same material, and the mechanical strength of these brazing materials is smaller than that of the tube 12, the fin 13 and the case 14.

　次に、本実施形態に係る熱交換器１１の作用について説明する。 Next, the operation of the heat exchanger 11 according to this embodiment will be described.

　車両に搭載されたエンジンが駆動されると、エンジンの燃焼ガスは排気管１０を通り、熱交換器１１を通過する。熱交換器１１を通過する燃焼ガスは、多数のフィン１３の面に沿って流れる。フィン１３は高温の燃焼ガスにより加熱される。 When the engine mounted on the vehicle is driven, the combustion gas of the engine passes through the exhaust pipe 10 and passes through the heat exchanger 11. The combustion gas passing through the heat exchanger 11 flows along the surfaces of the numerous fins 13. The fin 13 is heated by the high-temperature combustion gas.

　これに対して、熱交換器１１のチューブ１２には冷媒が流れている。冷媒はフィン１３、チューブ１２とフィン１３とを接合するろう材およびチューブ１２を介して燃焼ガスと熱交換を行う。チューブ１２を通る冷媒は、入口管部１５から熱交換器１１の内部へ導入されるとき液相であるが、燃焼ガスとの熱交換により加熱されると、液相から気相へ変化する。気相に変化した冷媒は、熱交換器１１の内部から出て出口管部１９を通る。 In contrast, the refrigerant flows through the tube 12 of the heat exchanger 11. The refrigerant exchanges heat with the combustion gas through the fins 13, the brazing material joining the tubes 12 and the fins 13 and the tubes 12. The refrigerant passing through the tube 12 is in a liquid phase when introduced into the heat exchanger 11 from the inlet pipe portion 15, but changes from the liquid phase to the gas phase when heated by heat exchange with the combustion gas. The refrigerant changed to the gas phase exits the heat exchanger 11 and passes through the outlet pipe portion 19.

　熱交換器１１の各部は、高温の燃焼ガスの熱を受けて熱膨張する。チューブ１２は、フィン１３を形成するオーステナイト系ステンレス鋼よりも線膨張率の小さいフェライト系ステンレス鋼により形成されている。そのため、チューブ１２の熱膨張量は、フィン１３の熱膨張量よりも小さい。 Each part of the heat exchanger 11 receives the heat of high-temperature combustion gas and thermally expands. The tube 12 is made of ferritic stainless steel having a smaller linear expansion coefficient than the austenitic stainless steel forming the fins 13. Therefore, the thermal expansion amount of the tube 12 is smaller than the thermal expansion amount of the fin 13.

　チューブ１２では、熱交換により基本的に直管部１６の長手方向への熱膨張による変形が大きくなる。また、チューブ１２では、出口管部１９に近い直管部１６を通る冷媒は入口管部１５に近い直管部１６を通る冷媒と比較して温度が高い。 In the tube 12, deformation due to thermal expansion in the longitudinal direction of the straight pipe portion 16 is basically increased by heat exchange. In the tube 12, the refrigerant passing through the straight pipe portion 16 close to the outlet pipe portion 19 has a higher temperature than the refrigerant passing through the straight pipe portion 16 close to the inlet pipe portion 15.

　このため、チューブ１２では出口管部１９に近い部分ほど熱膨張による変形が大きく入口管部１５に近い部分ほど熱膨張による変形が小さい。そのため、チューブ１２は部位により熱膨張量に差が生じる。 Therefore, in the tube 12, the portion closer to the outlet pipe portion 19 is more deformed due to thermal expansion, and the portion closer to the inlet pipe portion 15 is less deformed due to thermal expansion. Therefore, the tube 12 has a difference in thermal expansion amount depending on the part.

　作動流体と加熱流体との間の熱交換の際、図２に示すチューブ１２の入口管部１５に近い上流側の直管部１６と、上流側の直管部１６よりも出口管部１９に近い下流側の直管部１６において熱膨張量に差が生じる。下流側の直管部１６の熱膨張量が上流側の直管部１６の熱膨張量よりも大きいと、下流側の直管部１６が上流側の直管部１６よりも長手方向に大きく伸びる。 When exchanging heat between the working fluid and the heating fluid, the upstream straight pipe portion 16 close to the inlet pipe portion 15 of the tube 12 shown in FIG. A difference occurs in the amount of thermal expansion in the straight pipe portion 16 on the near downstream side. If the thermal expansion amount of the downstream straight pipe portion 16 is larger than the thermal expansion amount of the upstream straight pipe portion 16, the downstream straight pipe portion 16 extends more in the longitudinal direction than the upstream straight pipe portion 16. .

　これら直管部１６の間における熱膨張量の差は、フィン１３におけるろう付け箇所Ｂ２、Ｂ３間の部位１３ＡＡを引っ張ろうとする。ところが、フィン１３の線膨張率はチューブ１２の線膨張率よりも大きいため、フィン１３における部位１３ＡＡはチューブ１２の変形に追従して変形することができる。その結果、フィン１３における部位１３ＡＡや、ろう付け箇所Ｂ２、Ｂ３に作用する応力が軽減され、フィン１３における部位１３ＡＡおよびろう付け箇所Ｂ２、Ｂ３における亀裂や破断を防止することができる。 The difference in the amount of thermal expansion between the straight pipe portions 16 tries to pull the portion 13AA between the brazing points B2 and B3 in the fin 13. However, since the linear expansion coefficient of the fin 13 is larger than the linear expansion coefficient of the tube 12, the portion 13AA of the fin 13 can be deformed following the deformation of the tube 12. As a result, the stress acting on the part 13AA and the brazing points B2 and B3 in the fin 13 is reduced, and cracks and breaks in the part 13AA and the brazing points B2 and B3 in the fin 13 can be prevented.

　なお、図２に示す直管部１６以外の互いに隣り合う直管部１６の間に熱膨張量の差が生じる場合、同様に、フィン１３における熱膨張量の差が生じた直管部１６間の部位１３ＡＡが変形し、部位１３ＡＡや部位１３ＡＡ近傍のろう付け箇所における亀裂や破断は防止される。 In addition, when the difference of thermal expansion amount arises between mutually adjacent straight pipe parts 16 other than the straight pipe part 16 shown in FIG. 2, similarly, between the straight pipe parts 16 in which the difference of the thermal expansion amount in the fin 13 produced The part 13AA is deformed, and cracks and breaks at the brazed part near the part 13AA and the part 13AA are prevented.

　一方、ケース１４はフェライト系ステンレス鋼よりも線膨張率の大きいオーステナイト系ステンレスにより形成されているが、外気に冷やされるため、チューブ１２とケース１４との間の熱膨張量の差は小さい。このため、チューブ１２とケース１４との間のろう付け箇所ＡＡにおける応力は軽減され、ろう付け箇所ＡＡの損傷は防止される。また、ケース１４はフィン１３と同じ材料により形成されているが、ケース１４の温度はフィン１３の温度よりも低いため、ケース１４とフィン１３との間の熱膨張量に差が生じる。 On the other hand, the case 14 is made of austenitic stainless steel having a linear expansion coefficient larger than that of the ferritic stainless steel, but since it is cooled to the outside air, the difference in thermal expansion between the tube 12 and the case 14 is small. For this reason, the stress at the brazing point AA between the tube 12 and the case 14 is reduced, and damage to the brazing point AA is prevented. Although the case 14 is formed of the same material as the fin 13, the temperature of the case 14 is lower than the temperature of the fin 13, so that a difference occurs in the amount of thermal expansion between the case 14 and the fin 13.

　本実施形態に係る熱交換器は、以下の作用効果を奏する。 The heat exchanger according to this embodiment has the following operational effects.

　（１）作動流体と加熱流体との間の熱交換の際、入口管部１５に近い直管部１６と、この直管部１６よりも出口管部１９に近い直管部１６とにおいて熱膨張量に差が生じる。そのため、フィン１３における隣接する通孔２５と通孔２５との間の部位１３ＡＡを引っ張ろうとする変形がチューブ１２に生じても、フィン１３の線膨張率はチューブ１２の線膨張率よりも大きいため、フィン１３における部位１３ＡＡはチューブ１２の変形に追従して変形する。その結果、フィン１３における部位１３ＡＡや、ろう付け箇所Ｂ２、Ｂ３に作用する応力が軽減され、フィン１３における部位１３ＡＡおよびろう付け箇所Ｂ２、Ｂ３の損傷を防止することができる。 (1) When heat is exchanged between the working fluid and the heating fluid, thermal expansion occurs in the straight pipe portion 16 close to the inlet pipe portion 15 and the straight pipe portion 16 closer to the outlet pipe portion 19 than the straight pipe portion 16. There is a difference in quantity. Therefore, even if the tube 13 is deformed to pull the portion 13AA between the adjacent through holes 25 in the fin 13 and the linear expansion coefficient of the fin 13 is larger than the linear expansion coefficient of the tube 12. The portion 13AA of the fin 13 is deformed following the deformation of the tube 12. As a result, the stress acting on the portion 13AA of the fin 13 and the brazing locations B2, B3 is reduced, and damage to the portion 13AA and the brazing locations B2, B3 of the fin 13 can be prevented.

　（２）熱交換器のチューブ１２、フィン１３、及びケース１４がステンレス鋼により形成されているので、チューブ１２、フィン１３、及びケース１４は耐熱性及び耐食性にすぐれている。そのため、高温（約８００℃）の燃焼ガスを加熱流体として用いることができる。このため、内燃機関がディーゼルエンジンやガソリンエンジンであってもエンジンの燃焼ガスを加熱流体として用いることができる。 (2) Since the tube 12, the fin 13 and the case 14 of the heat exchanger are made of stainless steel, the tube 12, the fin 13 and the case 14 are excellent in heat resistance and corrosion resistance. Therefore, high-temperature (about 800 ° C.) combustion gas can be used as the heating fluid. For this reason, even if the internal combustion engine is a diesel engine or a gasoline engine, the combustion gas of the engine can be used as a heating fluid.

　（３）ケース１４は、オーステナイト系ステンレス鋼により形成され、チューブ１２はフェライト系ステンレス鋼により形成されるから、チューブ１２の線膨張率はケース１４の線膨張率よりも小さい。このため、チューブ１２がケース１４よりも高温となる条件であっても、チューブ１２とケース１４との間の熱膨張量の差を小さくすることができ、チューブ１２をケース１４に支持するろう付け箇所ＡＡへの応力を軽減することができる。 (3) Since the case 14 is formed of austenitic stainless steel and the tube 12 is formed of ferritic stainless steel, the linear expansion coefficient of the tube 12 is smaller than the linear expansion coefficient of the case 14. For this reason, even if the tube 12 has a higher temperature than the case 14, the difference in thermal expansion between the tube 12 and the case 14 can be reduced, and the tube 12 is brazed to support the case 14. The stress to the location AA can be reduced.

　（４）フィン１３とケース１４とが同一材料により形成されているため、フィン１３とケース１４とを互いに異なる材料により形成する場合と比較すると、熱交換器１１の製造コストを抑制することができる。 (4) Since the fin 13 and the case 14 are formed of the same material, the manufacturing cost of the heat exchanger 11 can be reduced as compared with the case where the fin 13 and the case 14 are formed of different materials. .

　（５）作動流体としての冷媒は燃焼ガスとの熱交換により液相から気相へ変化することから、熱交換器１１をランキンサイクル回路の蒸気発生器として使用することができる。 (5) Since the refrigerant as the working fluid changes from the liquid phase to the gas phase by heat exchange with the combustion gas, the heat exchanger 11 can be used as a steam generator for the Rankine cycle circuit.

　（第２の実施形態）
　次に、本発明の第２の実施形態に係る熱交換器について説明する。 (Second Embodiment)
Next, a heat exchanger according to a second embodiment of the present invention will be described.

　本実施形態の熱交換器は、ケースの材料が第１の実施形態と相違する。本実施形態の熱交換器の構成は、ケースを形成する材料が異なる点を除き第１の実施形態と同一であり、第１の実施形態の説明を援用し、共通の符号を用いる。 The heat exchanger of the present embodiment is different from the first embodiment in the case material. The configuration of the heat exchanger of the present embodiment is the same as that of the first embodiment except that the material forming the case is different, and the description of the first embodiment is used and common symbols are used.

　表１に示すように、本実施形態の熱交換器１１のケース１４はチューブ１２を形成している材料と同じフェライト系ステンレス鋼（ＳＵＳ４３０、線膨張率：１０．８×１０－６［１／Ｋ］）により形成されている。 As shown in Table 1, the case 14 of the heat exchanger 11 of the present embodiment is made of the same ferritic stainless steel (SUS430, linear expansion coefficient: 10.8 × 10 −6 [1 / K]).

　従って、ケース１４とチューブ１２との間の熱膨張量は同じであり、チューブ１２とケース１４との間の温度差が小さい場合には、チューブ１２とケース１４との間の熱膨張量の差を小さくすることができ、ろう付け箇所ＡＡにおける応力を軽減することができる。 Accordingly, the amount of thermal expansion between the case 14 and the tube 12 is the same, and when the temperature difference between the tube 12 and the case 14 is small, the difference in the amount of thermal expansion between the tube 12 and the case 14. Can be reduced, and the stress at the brazing point AA can be reduced.

　本実施形態の熱交換器１１では、第１の実施形態の作用効果（１）～（３）、（６）と同等の作用効果を奏する。 The heat exchanger 11 of the present embodiment has the same operational effects as the operational effects (1) to (3) and (6) of the first embodiment.

　ケース１４はチューブ１２と同じフェライト系ステンレス鋼により形成されているので、ケース１４の線膨張率はオーステナイト系ステンレスの線膨張率よりも小さい。従って、チューブ１２とケース１４との材料をオーステナイト系ステンレスとした場合と比較すると、チューブ１２とケース１４との間の熱膨張量の差を小さくすることができる。また、チューブ１２とケース１４とが同一材料により形成されることから、チューブ１２とケース１４とを互いに異なる材料により形成する場合と比較すると、熱交換器１１の製造コストを抑制することができる。 Since the case 14 is made of the same ferritic stainless steel as the tube 12, the linear expansion coefficient of the case 14 is smaller than the linear expansion coefficient of the austenitic stainless steel. Therefore, compared with the case where the material of the tube 12 and the case 14 is austenitic stainless steel, the difference in the amount of thermal expansion between the tube 12 and the case 14 can be reduced. Moreover, since the tube 12 and the case 14 are formed of the same material, the manufacturing cost of the heat exchanger 11 can be suppressed as compared with the case where the tube 12 and the case 14 are formed of different materials.

　（第３の実施形態）
　次に、本発明の第３の実施形態に係る熱交換器について説明する。 (Third embodiment)
Next, a heat exchanger according to a third embodiment of the present invention will be described.

　第３の実施形態の熱交換器は、チューブおよびフィンの材料が第１の実施形態と相違する。 The heat exchanger of the third embodiment is different from the first embodiment in the materials of the tubes and fins.

　本実施形態の熱交換器の構成は、チューブおよびフィンを形成する材料が異なる点を除き第１の実施形態と同一であり、第１の実施形態の説明を援用し、共通の符号を用いる。 The configuration of the heat exchanger of the present embodiment is the same as that of the first embodiment except that the materials forming the tubes and the fins are different, and the description of the first embodiment is used and common reference numerals are used.

　表１に示すように、本実施形態の熱交換器１１のチューブ１２はマルテンサイト系ステンレス鋼（ＳＵＳ４１０、線膨張率：１０．１×１０－６［１／Ｋ］）により形成されている。また、フィン１３はフェライト系ステンレス鋼（ＳＵＳ４３０、線膨張率：１０．８×１０－６［１／Ｋ］）より形成されている。そして、ケース１４はオーステナイト系ステンレス鋼（ＳＵＳ３０４、線膨張率：１７．３×１０－６［１／Ｋ］）により形成されている。 As shown in Table 1, the tube 12 of the heat exchanger 11 of this embodiment is formed of martensitic stainless steel (SUS410, linear expansion coefficient: 10.1 × 10 −6 [1 / K]). The fin 13 is made of ferritic stainless steel (SUS430, linear expansion coefficient: 10.8 × 10 −6 [1 / K]). The case 14 is made of austenitic stainless steel (SUS304, linear expansion coefficient: 17.3 × 10 −6 [1 / K]).

　マルテンサイト系ステンレス鋼の線膨張率はフェライト系ステンレス鋼の線膨張率よりも小さく、フェライト系ステンレス鋼の線膨張率はオーステナイト系ステンレス鋼の線膨張率より小さい。 The linear expansion coefficient of martensitic stainless steel is smaller than that of ferritic stainless steel, and that of ferritic stainless steel is smaller than that of austenitic stainless steel.

　つまり、チューブ１２、フィン１３、ケース１４の順で線膨張率が大きくなるように材料が設定されている。従って、チューブ１２における互いに隣り合う直管部１６に熱膨張量の差が生じても、第１の実施形態と同様に、フィン１３における部位１３ＡＡや、部位１３ＡＡ近傍のろう付け箇所における亀裂や破断を防止することができる。また、フィン１３とケース１４との間の熱膨張量の差を小さくすることができ、ろう付け箇所Ｃにおける応力を軽減することができる。 That is, the material is set so that the linear expansion coefficient increases in the order of the tube 12, the fin 13, and the case 14. Therefore, even if there is a difference in the amount of thermal expansion between the straight pipe portions 16 adjacent to each other in the tube 12, as in the first embodiment, cracks and breaks at the portion 13AA of the fin 13 and the brazed portion near the portion 13AA. Can be prevented. Moreover, the difference in the amount of thermal expansion between the fin 13 and the case 14 can be reduced, and the stress at the brazing point C can be reduced.

　本実施形態の熱交換器１１では、第１の実施形態の作用効果（１）、（２）、（５）と同等の作用効果を奏する。 In the heat exchanger 11 of this embodiment, there exists an effect equivalent to the effect (1), (2), (5) of 1st Embodiment.

　また、チューブ１２よりも大きい線膨張率を有し高温となり得るフィン１３はチューブ１２よりも大きく熱膨張するため、フィン１３はチューブ１２以上に変形する。さらに、フィン１３よりも大きい線膨張率を有する材料により形成されるケース１４は、フィン１３とケース１４との間の熱膨張量の差を小さくすることができる。従って、フィン１３とケース１４とがろう付けされている場合であっても、フィン１３とケース１４との間のろう付け箇所Ｃの損傷を防止することができる。 Further, the fin 13 having a larger linear expansion coefficient than that of the tube 12 and capable of becoming a high temperature is thermally expanded larger than that of the tube 12, so that the fin 13 is deformed more than the tube 12. Furthermore, the case 14 formed of a material having a larger linear expansion coefficient than that of the fin 13 can reduce the difference in thermal expansion amount between the fin 13 and the case 14. Therefore, even when the fin 13 and the case 14 are brazed, damage to the brazed portion C between the fin 13 and the case 14 can be prevented.

　なお、上記各実施形態は、本発明の一実施形態を示すものであり、本発明は、上記の実施形態に限定されるものではなく、下記のように発明の趣旨の範囲内で種々の変更が可能である。 Each of the above embodiments shows an embodiment of the present invention, and the present invention is not limited to the above embodiment, and various modifications are possible within the scope of the invention as follows. Is possible.

　○上記各実施形態では、オーステナイト系ステンレス鋼として、ＳＵＳ３０４を用いたが、ＳＵＳ３１６、ＳＵＳ３１６Ｌを用いてもよい。 In each of the above embodiments, SUS304 is used as the austenitic stainless steel, but SUS316 or SUS316L may be used.

　○上記各実施形態では、フェライト系ステンレス鋼として、ＳＵＳ４３０を用いたが、線膨張率の小さいＳＵＳ４４４を用いてもよい。 In each of the above embodiments, SUS430 is used as the ferritic stainless steel, but SUS444 having a small linear expansion coefficient may be used.

　○上記各実施形態では、ケースとフィンとがろう付けにより互いに固定されるが、必ずしもケースとフィンとが互いに固定されなくてもよい。この場合、フィンの振動防止の対策が別の手段により講じられていることが好ましい。 In each of the above embodiments, the case and the fin are fixed to each other by brazing, but the case and the fin are not necessarily fixed to each other. In this case, it is preferable that measures for preventing the vibration of the fins are taken by another means.

　○上記各実施形態では、作動流体として熱交換により相変化する冷媒を用いたが、作動流体は相変化する冷媒に限定されない。作動流体は、例えば、加熱流体と熱交換されても液相を保つ流体を用いてもよい。また、加熱流体は燃焼ガスに限らず、熱交換により作動流体を加熱することができる流体であればよく気体に限らず液体であってもよい。 In each of the above embodiments, the refrigerant that changes phase by heat exchange is used as the working fluid, but the working fluid is not limited to the refrigerant that changes phase. As the working fluid, for example, a fluid that maintains a liquid phase even when heat exchange with the heating fluid may be used. Further, the heating fluid is not limited to the combustion gas, and may be any fluid that can heat the working fluid by heat exchange.

　○上記各実施形態では、熱交換器をランキンサイクル回路に用いる熱交換器としたが、本発明の熱交換器はランキンサイクル回路以外の熱交換器として使用することができる。また、上記各実施形態では熱交換器を車載用熱交換器としたが、車載用熱交換器に限定されず、例えば、地上に設置される熱交換器であってもよい。 In each of the above embodiments, the heat exchanger is a heat exchanger used in a Rankine cycle circuit, but the heat exchanger of the present invention can be used as a heat exchanger other than the Rankine cycle circuit. Moreover, in each said embodiment, although the heat exchanger was used as the vehicle-mounted heat exchanger, it is not limited to a vehicle-mounted heat exchanger, For example, the heat exchanger installed on the ground may be sufficient.

　○上記第１及び第２の実施形態では、チューブの材料としてフィライト系ステンレス鋼を用い、フィンの材料としてオーステナイト系ステンレス鋼を用いたが、この材料の組み合わせ以外の組み合わせでもよい。例えば、チューブの材料をマルテンサイト系ステンレス鋼とし、フィン（およびケース）の材料をオーステナイト系ステンレス鋼としてもよい。チューブおよびフィンの材料が少なくともステンレス鋼であって、チューブがフィンよりも線膨張率が小さくなる材料の組み合わせであればよい。 In the first and second embodiments, phyllite stainless steel is used as the tube material and austenitic stainless steel is used as the fin material. However, combinations other than this combination may be used. For example, the tube material may be martensitic stainless steel, and the fin (and case) material may be austenitic stainless steel. The material of the tube and the fin may be at least stainless steel, and the tube may be a combination of materials whose linear expansion coefficient is smaller than that of the fin.

Claims (5)

　熱交換器であって、
　互いに並列に配置される複数の直管部を有するとともに、作動流体を通すチューブと、
　前記複数の直管部がそれぞれ挿入される複数の通孔を有するとともに、前記複数の直管部にろう付けされたフィンと、を備え、
　前記熱交換器は、前記フィンの周囲の加熱流体と前記作動流体との間で熱交換を行うように構成され、
　前記チューブおよび前記フィンはステンレス鋼により形成され、
　前記チューブを形成するステンレス鋼の線膨張率は、前記フィンを形成するステンレス鋼の線膨張率より小さい、熱交換器。 A heat exchanger,
A tube having a plurality of straight pipe portions arranged in parallel to each other and passing a working fluid;
A plurality of through holes into which the plurality of straight pipe portions are respectively inserted, and fins brazed to the plurality of straight pipe portions,
The heat exchanger is configured to exchange heat between the heated fluid around the fins and the working fluid;
The tube and the fin are formed of stainless steel,
A heat exchanger in which the linear expansion coefficient of the stainless steel forming the tube is smaller than the linear expansion coefficient of the stainless steel forming the fin. 　前記フィンおよび前記チューブを収容するケースを更に備え、
　前記チューブは、前記ケースの内部を通過するようにろう付けで前記ケースに支持され、
　前記ケースは、ステンレス鋼により形成され、
　前記チューブを形成するステンレス鋼の線膨張率は、前記ケースを形成するステンレス鋼の線膨張率より小さい、請求項１記載の熱交換器。 A case for accommodating the fin and the tube;
The tube is supported by the case by brazing so as to pass through the inside of the case,
The case is made of stainless steel,
The heat exchanger according to claim 1, wherein a linear expansion coefficient of the stainless steel forming the tube is smaller than a linear expansion coefficient of the stainless steel forming the case. 　前記ケースおよび前記フィンは同一材料により形成されている、請求項２記載の熱交換器。 The heat exchanger according to claim 2, wherein the case and the fin are formed of the same material. 　前記ケースを形成するステンレス鋼の線膨張率は、前記フィンを形成するステンレス鋼の線膨張率より大きい、請求項２記載の熱交換器。 The heat exchanger according to claim 2, wherein a linear expansion coefficient of the stainless steel forming the case is larger than a linear expansion coefficient of the stainless steel forming the fin. 　前記作動流体は、前記加熱流体との熱交換により液相から気相へ変化する冷媒である、請求項１～４のいずれか一項記載の熱交換器。 The heat exchanger according to any one of claims 1 to 4, wherein the working fluid is a refrigerant that changes from a liquid phase to a gas phase by heat exchange with the heating fluid.
PCT/JP2013/050225 2012-02-07 2013-01-09 Heat exchanger Ceased WO2013118527A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-023643 2012-02-07
JP2012023643A JP2013160469A (en) 2012-02-07 2012-02-07 Heat exchanger

Publications (1)

Publication Number Publication Date
WO2013118527A1 true WO2013118527A1 (en) 2013-08-15

Family

ID=48947296

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/050225 Ceased WO2013118527A1 (en) 2012-02-07 2013-01-09 Heat exchanger

Country Status (2)

Country Link
JP (1) JP2013160469A (en)
WO (1) WO2013118527A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016003843A (en) * 2014-06-19 2016-01-12 新日鐵住金株式会社 Fin tube
CN106346153A (en) * 2016-11-01 2017-01-25 中国兵器科学研究院宁波分院 Manufacturing method of stainless steel cooler for Stirling engine
JP2019116985A (en) * 2017-12-26 2019-07-18 株式会社ノーリツ Process of manufacture of heat exchanger, heat exchanger intermediate unit and heat exchanger
EP3531057A1 (en) * 2018-02-23 2019-08-28 Unison Industries LLC Heat exchanger assembly
WO2025216328A1 (en) * 2024-04-12 2025-10-16 Ｉｎｎｏｖｉｄｅａ合同会社 Heat exchanger and air conditioner using same

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7004207B2 (en) * 2017-12-26 2022-01-21 株式会社ノーリツ Heat exchanger and its manufacturing method

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002106970A (en) * 2000-09-27 2002-04-10 Toho Gas Co Ltd Latent heat recovery heat exchanger and combustion equipment equipped therewith
JP2005055153A (en) * 2003-08-07 2005-03-03 Toyota Motor Corp Heat exchanger
JP2006046757A (en) * 2004-08-03 2006-02-16 Babcock Hitachi Kk Anticorrosive heat transfer tube with fin and exhaust gas heater
JP2006105464A (en) * 2004-10-04 2006-04-20 Toyota Motor Corp Heat exchanger and heat exchange device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002106970A (en) * 2000-09-27 2002-04-10 Toho Gas Co Ltd Latent heat recovery heat exchanger and combustion equipment equipped therewith
JP2005055153A (en) * 2003-08-07 2005-03-03 Toyota Motor Corp Heat exchanger
JP2006046757A (en) * 2004-08-03 2006-02-16 Babcock Hitachi Kk Anticorrosive heat transfer tube with fin and exhaust gas heater
JP2006105464A (en) * 2004-10-04 2006-04-20 Toyota Motor Corp Heat exchanger and heat exchange device

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016003843A (en) * 2014-06-19 2016-01-12 新日鐵住金株式会社 Fin tube
CN106346153A (en) * 2016-11-01 2017-01-25 中国兵器科学研究院宁波分院 Manufacturing method of stainless steel cooler for Stirling engine
JP2019116985A (en) * 2017-12-26 2019-07-18 株式会社ノーリツ Process of manufacture of heat exchanger, heat exchanger intermediate unit and heat exchanger
JP7004208B2 (en) 2017-12-26 2022-02-04 株式会社ノーリツ How to make a heat exchanger
EP3531057A1 (en) * 2018-02-23 2019-08-28 Unison Industries LLC Heat exchanger assembly
JP2019158329A (en) * 2018-02-23 2019-09-19 ユニゾン・インダストリーズ，エルエルシー Heat exchanger assembly
US11536521B2 (en) 2018-02-23 2022-12-27 Unison Industries, Llc Heat exchanger assembly with a manifold additively manufactured onto a core and method of forming
US11927405B2 (en) 2018-02-23 2024-03-12 Unison Industries, Llc Heat exchanger assembly with unitary body and manifold and methods of formng same
WO2025216328A1 (en) * 2024-04-12 2025-10-16 Ｉｎｎｏｖｉｄｅａ合同会社 Heat exchanger and air conditioner using same

Also Published As

Publication number Publication date
JP2013160469A (en) 2013-08-19

Similar Documents

Publication Publication Date Title
WO2013118527A1 (en) Heat exchanger
US20070181294A1 (en) Exhaust gas heat exchanger and method of operating the same
BRPI0807410A2 (en) Heat Exchanger and Method
US8915292B2 (en) Exhaust gas heat exchanger and method of operating the same
US20070017661A1 (en) Heat exchanger
US10697706B2 (en) Heat exchanger
JP2020016418A (en) Heat exchanger, and water heating system including the same
CN104729154A (en) Heat exchanger
WO2007122765A1 (en) Single can-type composite heat source machine
JP7484074B2 (en) Heat exchanger and hot water device equipped with same
JP2017194261A (en) Heat exchanger
US8136578B2 (en) Heat exchanger for EGR-gas
JP4246749B2 (en) 1 can type combined heat source machine
JP2012137251A (en) Multitubular heat exchanger
US20070000652A1 (en) Heat exchanger with dimpled tube surfaces
JP4270661B2 (en) Multi-tube type EGR gas cooling device and manufacturing method thereof
JP3845565B2 (en) Heat exchanger
JP2014070849A (en) Heat exchanger
JP2007155321A (en) Small high-temperature heat exchanger such as recovery heat exchanger
JP6099003B2 (en) Heat exchanger and hot water device provided with the same
WO2014054412A1 (en) Heat exchanger
CN216048370U (en) Gas water heater and heat exchanger
EP4023998B1 (en) A tube for a heat exchanger
JP5829597B2 (en) Finned tube heat exchanger
EP4023991A1 (en) A tube for a heat exchanger

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13746819

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13746819

Country of ref document: EP

Kind code of ref document: A1