WO2015107815A1 - Tuyau de transfert thermique pour échangeur thermique, et échangeur thermique - Google Patents

Tuyau de transfert thermique pour échangeur thermique, et échangeur thermique Download PDF

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Publication number
WO2015107815A1
WO2015107815A1 PCT/JP2014/082869 JP2014082869W WO2015107815A1 WO 2015107815 A1 WO2015107815 A1 WO 2015107815A1 JP 2014082869 W JP2014082869 W JP 2014082869W WO 2015107815 A1 WO2015107815 A1 WO 2015107815A1
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WIPO (PCT)
Prior art keywords
heat exchanger
exhaust gas
fins
fin
heat
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Application number
PCT/JP2014/082869
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English (en)
Japanese (ja)
Inventor
義正 鳥居
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株式会社ミクニ
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Publication of WO2015107815A1 publication Critical patent/WO2015107815A1/fr

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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
    • 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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present invention relates to a heat exchanger tube for a heat exchanger and a heat exchanger.
  • the temperature of the exhaust gas on the upstream side of the exhaust gas passage is higher than the temperature of the exhaust gas on the downstream side.
  • the fin thickness is small in the vicinity of the exhaust gas inlet side, that is, if the heat capacity of the fin is small, the cooling of the fin itself that has become high temperature due to contact / heat exchange with the exhaust gas does not sufficiently proceed, and the fin temperature Is maintained at a high temperature. Therefore, in this case, there is a possibility that the fins are deformed due to thermal distortion or blistering.
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a heat exchanger tube for a heat exchanger that can suppress the deformation of fins near the exhaust gas inlet and a heat exchanger used therefor.
  • the above-mentioned subject is achieved by the following present invention. That is, The heat exchanger tube for a heat exchanger according to the present invention is disposed in a heat transfer tube main body having an exhaust gas flow passage having an exhaust gas inlet at one end and an exhaust gas outlet at the other end, and a heat transfer tube main body. Fins, and in the average flow direction of the exhaust gas flowing in the exhaust gas flow path, the average thickness of the fins located in the upstream portion in the heat transfer tube main body is located on the downstream side of the upstream portion. It is characterized by being larger than the thickness.
  • One embodiment of the heat exchanger tube for a heat exchanger of the present invention is such that the total area of the main surfaces of all the fins existing in the unit length section in the average flow direction of the exhaust gas is smaller than that on the downstream side of the upstream portion.
  • the upstream part is preferably smaller.
  • the average thickness of the fins is gradually or gradually decreased as going from the upstream side to the downstream side in the average flow direction of the exhaust gas. Is preferred.
  • the fins are intermittently arranged along the average flow direction of the exhaust gas.
  • the material constituting the fin is preferably aluminum or an aluminum alloy.
  • the heat exchanger of the present invention is characterized in that it includes at least a heat transfer tube for heat exchanger and an outer tube provided with a cooling liquid inlet and a cooling liquid outlet.
  • a heat exchanger tube for a heat exchanger that can suppress the deformation of fins in the vicinity of an exhaust gas inlet and a heat exchanger used therefor.
  • FIG. 3 (A) shows a cross-sectional view when the cross-sectional shape of the fin is rectangular
  • FIG. 3 (B) is a cross-sectional view when the cross-sectional shape of the fin is trapezoidal. Is shown.
  • FIG. 1 is an exploded perspective view showing an example of a heat exchanger tube for a heat exchanger according to the present embodiment.
  • the X direction, Y direction, and Z direction shown in FIG. 1 mean directions orthogonal to each other, and the central axis AX of the heat exchanger heat transfer tube and the average flow direction F of the exhaust gas are parallel to the X direction. These points are the same in FIG. 2 and subsequent figures.
  • the X direction may be referred to as an upstream direction or a downstream direction
  • the Y direction may be referred to as a width direction or a horizontal direction
  • the Z direction may be referred to as a height direction or a vertical direction.
  • the average flow direction F of the exhaust gas is not the local flow direction of the exhaust gas in the heat exchanger tube, but the entire exhaust gas flowing in the heat exchanger tube. This means an average flow direction in this case, and it can be rephrased as a direction substantially parallel to the path moving from the exhaust gas inlet side to the exhaust gas outlet side in the substantially central portion of the exhaust gas flow path.
  • a heat exchanger 10 shown in FIG. 1 includes a heat exchanger heat transfer tube 20 and an outer tube 30 that houses the heat exchanger heat transfer tube 20 and is provided with a cooling liquid inlet 32 and a cooling liquid outlet 34. It is equipped with. The positional relationship between the cooling liquid inlet 32 and the cooling liquid outlet 34 may be reversed.
  • the heat exchanger heat transfer tube 20 includes a heat transfer tube main body 100 in which an exhaust gas passage GCN having one end serving as an exhaust gas inlet 102 and the other end serving as an exhaust gas outlet 104 is provided. Yes.
  • the heat transfer tube main body 100 includes a first casing 110 made of a flat plate-like first plate 130 and a substantially rectangular parallelepiped second casing 120.
  • the second housing 120 is provided with an opening 122 on the upper surface thereof, and the lower surface thereof is composed of a flat plate (second plate 140), and is a pair positioned on both sides in the longitudinal direction of the second housing 120.
  • second plate 140 flat plate
  • casing 110 (1st plate 130) is arrange
  • the first plate 130 and the second plate 140 constitute a part of the outer peripheral surface of the heat transfer tube main body 100.
  • the outer heat shield tube 20 is sealed between the outer peripheral side of the heat exchanger heat transfer tube 20 and the outer periphery of the outer tube 30. A space is formed. For this reason, when a cooling liquid such as cooling water is supplied from the cooling liquid inlet 32 during heat exchange, cooling flows between the outer peripheral side of the heat exchanger heat transfer tube 20 and the inner peripheral side of the outer tube 30. The working liquid comes into contact with the outer peripheral surface of the heat transfer tube main body 100 (for example, the outer peripheral surface 130B of the first plate 130 and the outer peripheral surface 140B of the second plate 140).
  • a plurality of fins 132 and 142 are arranged in the heat transfer tube main body 100.
  • the first fin 132 is provided so as to stand upright with respect to the inner peripheral surface 130 ⁇ / b> A of the first plate 130
  • the second fin 142 is the inner peripheral surface of the second plate 140. It is provided so as to stand upright (not shown in FIG. 1).
  • These fins 132 and 142 are flat members that are substantially parallel to the average exhaust gas flow direction F (the direction parallel to the X direction and from the exhaust gas inlet 102 toward the exhaust gas outlet 104). .
  • FIG. 2 is an enlarged cross-sectional view showing an example of the heat exchanger tube for heat exchanger according to the present embodiment.
  • the heat exchanger tube for heat exchanger shown in FIG. FIG. 2 shows an example of an enlarged cross-sectional view when viewed from the upper side of the paper surface in FIG. 1.
  • 2 shows a cross-sectional view of the second fin 142, the first fin 132 is not shown, but the same position as the second fin 142 in the drawing (FIG. 2).
  • the first fins 132 are present on the front side of the sheet) so as to be plane-symmetric with the second fins 142 with respect to the XY plane.
  • the height of each second fin 142 shown in FIG. 2 is the same.
  • the average flow direction F of the exhaust gas is parallel to the second housing 120 constituting the heat transfer tube main body 100 of the heat exchanger heat transfer tube 20A.
  • a total of eight second fins 142 are arranged, with two pieces per row in the direction forming the four and four pieces per row in the direction (width direction) orthogonal to the average flow direction F of the exhaust gas.
  • the cross-sectional shape of each of the second fins 142 forms a linear band shape, and the second casing 142 is configured so that each of the second fins 142 is parallel to the average flow direction F of the exhaust gas. 120.
  • the “average fin thickness” means the average thickness of the fins 132 and 142 in the width direction of the fins 132 and 142 (direction perpendicular to the average exhaust gas flow direction F). .
  • the cross-sectional shape (cross-sectional shape of the YZ plane) of the fin 142L when the heat exchanger heat transfer tube 20A is cut between A1 and A2 is a rectangular shape as shown in FIG. is doing.
  • the fin 142L is arrange
  • the average thickness T of the fin 142L means the short side length of the fin 142.
  • the cross-sectional shape of the fins 132 and 142 in the YZ plane a cross-sectional shape other than that illustrated in FIG. 3A can also be employed as appropriate.
  • the fins 132 and 142 have a cross-sectional shape in the height direction.
  • Cross-sectional shapes with different thicknesses 132 and 142 can also be employed.
  • the average thickness T of the fins 132 and 142 is the height direction of the cross-sectional shape of the fins 132 and 142 in the cross-sectional area S of the fins 132 and 142 in a plane (YZ plane) orthogonal to the average flow direction F of the exhaust gas. Is approximately obtained as a value divided by the length L. For example, as illustrated in FIG.
  • a value obtained by dividing the cross-sectional area S by the height L of the cross-sectional shape of the fin 142X (the height of the fin 142X) is obtained as the average thickness T of the fin 142X.
  • the fins 142M are also provided in the second row L2 so as to correspond to the fins 142L constituting the first row L1 in a 1: 1 ratio.
  • the gap G2 between the two fins 142M adjacent in the width direction in the second row L2 is larger than the gap G1 between the two fins 142L adjacent in the width direction in the first row L1. Therefore, even when the gap G1 is designed to be as small as possible in terms of pressure loss, heat exchange efficiency, etc., the gap G2 is too large when viewed as the heat exchanger tube 20A for the heat exchanger as a whole. The exchange efficiency is poor.
  • the main surface of the fin means a pair of surfaces having the substantially largest area among the surfaces constituting the surface of the fin, for example, as shown in FIGS. 1 and 2. In the example, a pair of surfaces parallel to the ZX plane is the main surface.
  • FIG. 4 is an enlarged cross-sectional view showing another example of the heat exchanger tube for heat exchanger 20 of the present embodiment, and specifically shows a modification of the heat exchanger tube for heat exchanger 20A shown in FIG.
  • the heat exchanger heat transfer tube 20B (20) shown in FIG. 4 increases the number of fins 142M constituting the second row L2 from four to six with respect to the heat exchanger heat transfer tube 20A shown in FIG. Except for the fact that G1 and the gap G2 are made substantially the same, the configuration is the same as the heat exchanger tube 20A for heat exchanger shown in FIG. That is, regarding the total area of all the fins existing in the unit length section UL in the average flow direction F of the exhaust gas, in the example shown in FIG.
  • the fins arranged in the upstream portion (four in total)
  • the total area of the main surface of 142L is the same as the total area of the main surface of the fins 142M (a total of four) arranged in the downstream part downstream of the upstream part.
  • the fins are disposed in the downstream portion downstream of the upstream portion rather than the total area of the main surfaces of the fins 142 ⁇ / b> L disposed in the upstream portion (total four).
  • the total area of the main surface of the (six) fins 142M is 1.5 times larger. In other words, the total area of the main surface is smaller in the upstream portion than in the upstream portion (in the example shown in FIG. 4, the downstream portion where the fin 142M in the second row is located).
  • the fin 142L located in the upstream portion has a large thickness, so the number of arrangement is limited, and the total of the main surface is limited. Since the area is also small, it is unavoidable that the heat exchange efficiency is lowered.
  • the fin 142M located on the downstream side of the fin 142L located in the upstream portion has a relatively smaller thickness, the number of fins 142M arranged can be increased as illustrated in FIG. In particular, the total area of the main surface can be increased. Therefore, in the heat exchanger heat transfer tube 20B illustrated in FIG. 4, the heat exchange efficiency of the fin 142L located in the upstream portion is lower than that in the upstream portion as compared with the heat exchanger heat transfer tube 20A illustrated in FIG. 2. It can supplement by the fin 142M located in the downstream.
  • FIG. 5 is an enlarged cross-sectional view showing another example of the heat exchanger tube for heat exchanger 20 of the present embodiment, and specifically shows a modification of the heat exchanger tube for heat exchanger 20A shown in FIG.
  • the heat exchanger heat transfer tube 20C (20) shown in FIG. 5 four fins 142L are arranged in the first row L1 from the upstream side to the downstream side, and four fins 142M are arranged in the second row L2.
  • the four fins 142M are arranged in the third row L3, and the four fins 142S (142) are arranged in the fourth row L4. That is, in the example shown in FIG. 5, the length of each fin 142 with respect to the exhaust gas flow direction F is halved with respect to the example shown in FIG.
  • the fourth embodiment is characterized in that it has a configuration in which fins 142S in the fourth row are added, and the rest is the same as the example shown in FIG.
  • the thickness of each fin 142 has the largest fin 142L of the 1st row
  • the fin 142M is the next largest, and the fin 142S of the fourth row L4 located in the downstream portion is the smallest.
  • the gap G2 and the gap G3 between the two fins 142M adjacent in the width direction of the midstream portion downstream from the upstream portion, and the upstream At least one kind of gap selected from the gap G4 between the two fins 142S adjacent in the width direction of the downstream part downstream of the part and the middle stream part is made narrower, and the fins 142M and / or fins 142S are made more narrow. You may arrange many sheets densely.
  • the total area of the main surfaces of the fins 142M or fins 142S constituting each row is compared with that of the upstream portion per unit length section UL in the average flow direction F of the exhaust gas in the midstream portion and the downstream portion. Can be relatively increased. Therefore, in this case, the heat exchange efficiency of the heat exchanger heat transfer tube 20C (20) can be further improved.
  • the average thickness T of the fins 142 is stepped as illustrated in FIG. 2, FIG. 4 to FIG. 5 or FIG. 6 to be described later as it goes from the upstream side to the downstream side along the average flow direction F of the exhaust gas. It is preferable that the thickness becomes thinner or gradually becomes thinner.
  • the fin 142 per unit length section UL in the average flow direction F of the exhaust gas is increased by increasing the number of fins 142 disposed or the density of the fins 142 as the thickness of the fins 142 decreases toward the downstream side.
  • the total area of the main surface can be increased. In this case, it becomes easy to further improve the heat exchange efficiency.
  • the portion excluding the upstream portion in the heat transfer tube main body 100 that is, the downstream side of the upstream portion is an average of the exhaust gas as long as it does not exceed the thickness of the fin 142L positioned in the upstream portion.
  • the thickness of the fin 142 may increase again.
  • the fins 142M in the third row L3 and the fins 142S in the fourth row L4 may be replaced with each other.
  • FIG. 6 is an enlarged cross-sectional view showing another example of the heat exchanger tube for heat exchanger 20 of the present embodiment, and specifically shows a modification of the heat exchanger tube for heat exchanger 20A shown in FIG.
  • a heat exchanger tube 20D (20) for a heat exchanger shown in FIG. 6 includes, as shown in FIG. 2, a fin 142L arranged at the upstream portion in the heat transfer tube main body 100 and a fin 142M located at the downstream side of the fin 142L. Except that four fins 142LM (142) connected and integrated are provided, the heat exchanger tube 20A has substantially the same configuration as the heat exchanger tube 20A for heat exchanger shown in FIG. In heat exchanger tube 20D for heat exchangers shown in FIG.
  • heat exchanger tube 20D for heat exchangers shown in FIG. 6 can suppress the deformation
  • the fins 142 may be arranged continuously along the average flow direction F of the exhaust gas, like the fins 142LM illustrated in FIG. 6, and the fins 142L, 142M, and FIG. 4 illustrated in FIG.
  • the fins 142L and 142M illustrated in FIG. 5 or the fins 142L, 142M, 142M, and 142S illustrated in FIG. 5 may be intermittently disposed along the average flow direction F of the exhaust gas.
  • the heat absorbed by the fin 142 due to contact with the exhaust gas is transmitted along the direction not approaching the outer peripheral surface of the heat transfer tube main body 100 in contact with the cooling liquid, that is, along the longitudinal direction of the fin 142 in the XY cross section. Can be suppressed.
  • FIG. 7 is a schematic cross-sectional view showing an example of a cross-sectional structure in a cross section obtained by cutting the heat exchanger tube for heat exchanger 20 of the present embodiment along a plane (YZ plane) orthogonal to the average flow direction F of exhaust gas.
  • FIG. 3 is a diagram showing an example of a cross-sectional structure between reference numerals A1-A2 in FIG. 2, that is, a cross-sectional structure in the YZ plane of the heat exchanger heat transfer tube 20A. As shown in FIG.
  • the first fins 132 ⁇ / b> L (132) are provided so as to stand upright with respect to the inner peripheral surface 130 ⁇ / b> A of the first plate 130, and the second fins 142 ⁇ / b> L are formed on the second plate 140. It is provided to stand upright with respect to the inner peripheral surface 140A.
  • the first fin 132L is formed integrally with the first pre and 130, and the second fin 142L is also formed integrally with the second plate 140.
  • tip part 142T of the 2nd fin 142L are facing so that the clearance gap X may be formed.
  • the heat of the exhaust gas flowing between the fins 132L and 142L is transmitted to the first plate 130 side via the first fins 132L, and the second heat is supplied via the second fins 142L. It is transmitted to the plate 140 side.
  • the heat transferred to the plates 130 and 140 is transferred to the cooling liquid (not shown in the drawing) that contacts the outer peripheral surface 130B of the first plate 130 and the outer peripheral surface 140B of the second plate 140.
  • the cross-sectional structure in the YZ plane as illustrated in FIG. 7 is not particularly limited, and a cross-sectional structure other than that illustrated in FIG. Can do.
  • a cross-sectional structure in which the second fins 142 provided so as to stand upright from 140A alternately overlap in the width direction of the plates 130 and 140 may be employed.
  • the front end portion 142T of the first fin 132 and the inner peripheral surface 140A of the second plate 140 face each other, and the front end portion 142T of the second fin 142 and the inner peripheral surface of the first plate 130 are opposed to each other. 130A will face.
  • the material constituting the first plate 130, the second plate 140, the first fins 132, and the second fins 142 has appropriate corrosion resistance and heat resistance against exhaust gas, and appropriate heat.
  • Any material having conductivity can be used without any particular limitation.
  • an iron-based material such as stainless steel represented by SUS, aluminum, or an aluminum alloy is used.
  • the entire heat exchanger tube 20 for the heat exchanger is the same including the first plate 130, the second plate 140, the first fin 132, the second fin 142, and other members other than these members. It is preferable that it is comprised from these materials.
  • the fins 132 and 142 having a small average thickness T are arranged on the upstream side in the average flow direction F of the exhaust gas, thermal distortion may occur. Furthermore, when the material constituting the fins 132 and 142 having a small average thickness T is made of aluminum or an aluminum alloy, blistering may occur in addition to thermal strain. Therefore, these thermal distortions and blisters cause deformation of the fins 132 and 142 having a small average thickness T as a result.
  • the fins 132L and 142L having the largest average thickness T are arranged on the upstream side in the average flow direction F of the exhaust gas. For this reason, it is very easy to suppress the deformation of the fins 132L and 142L regardless of the material of the fins 132L and 142L and the cause of the deformation.
  • the second fin 142 may be physically or chemically joined to the inner peripheral surface 140A of the second plate 140 by welding or adhesion, or mechanically joined by fitting or the like. Also good. However, it is particularly preferable that the second plate 140 and the second fin 142 are integrally formed by casting such as die casting. Thereby, since there is no bonding interface between the second plate 140 and the second fin 142, the heat transfer resistance due to the existence of the bonding interface can be made zero, and the heat of the second fin 142 can be reduced. Can be smoothly transmitted to the second plate 140 side. This also applies to the first fins 132 and the first plate 130. Further, from the viewpoint that the first plate 130 and the first fin 132 can be integrally formed by using die casting, and the second plate 140 and the second fin 142 can be integrally formed. It is very preferable to use aluminum or an aluminum alloy as the material constituting the material.
  • the shape of the exhaust gas passage GCN of the exhaust gas formed in the heat exchanger tube 20 is the exhaust gas inlet 102 in the XY plane direction. From the exhaust gas outlet 104 to the exhaust gas outlet 104.
  • the shape of the exhaust gas flow path GCN in the XY plane direction may be any shape as long as a flow path connecting the exhaust gas inlet 102 and the exhaust gas outlet 104 can be formed.
  • the gas flow path GCN may be formed in a U shape.
  • the positional relationship between the exhaust gas inlet 102 and the exhaust gas outlet 104 may be reversed depending on the relative relationship with the outer tube 30.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'objet de l'invention est de supprimer la déformation d'une ailette à proximité d'une entrée de gaz d'échappement. L'invention propose un tuyau de transfert thermique pour un échangeur thermique ainsi qu'un échangeur thermique l'utilisant, ledit tuyau de transfert thermique étant caractérisé en ce qu'il comprend au moins un corps de tuyau de transfert thermique dans lequel est prévu un canal de gaz d'échappement (GCN), une extrémité du canal de gaz d'échappement étant une entrée de gaz d'échappement (102) et l'autre extrémité étant une sortie de gaz d'échappement (104), et des ailettes (142L, 142M) disposées dans le corps de tuyau de transfert thermique, et caractérisé en ce que l'épaisseur moyenne de l'ailette (142L) positionnée dans une section en amont à l'intérieur du tuyau de transfert thermique dans le sens d'écoulement moyen (F) du gaz d'échappement s'écoulant dans le canal de gaz d'échappement (GCN) est supérieure à l'épaisseur moyenne de l'ailette (142M) positionnée en aval par rapport à la section en amont.
PCT/JP2014/082869 2014-01-14 2014-12-11 Tuyau de transfert thermique pour échangeur thermique, et échangeur thermique WO2015107815A1 (fr)

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JP2014-004011 2014-01-14
JP2014004011A JP2015132421A (ja) 2014-01-14 2014-01-14 熱交換器用伝熱管および熱交換器

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US10533769B2 (en) * 2017-07-28 2020-01-14 Viessmann Werke Gmbh & Co Kg Heating device

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JPS6042594A (ja) * 1983-08-18 1985-03-06 Seiichi Konaka フイン付熱交換装置
JPS6268112A (ja) * 1985-09-19 1987-03-28 Isuzu Motors Ltd 車両用熱発電装置
JPH0578917U (ja) * 1992-04-07 1993-10-26 日立金属株式会社 耐熱部材
JPH0914795A (ja) * 1995-06-30 1997-01-17 Sanyo Electric Co Ltd 冷媒加熱機
JP2002235992A (ja) * 2000-12-06 2002-08-23 Osaka Gas Co Ltd 熱交換器およびその熱交換器を用いた燃焼装置
JP2002313384A (ja) * 2001-02-07 2002-10-25 Calsonic Kansei Corp 燃料電池用熱交換器
JP2007078194A (ja) * 2005-09-09 2007-03-29 Usui Kokusai Sangyo Kaisha Ltd 熱交換器用伝熱管
JP2007211748A (ja) * 2006-02-13 2007-08-23 Toyota Motor Corp 熱交換器及び熱発電装置
JP2007225190A (ja) * 2006-02-23 2007-09-06 Maruyasu Industries Co Ltd 熱交換器
JP2010214379A (ja) * 2009-03-13 2010-09-30 Furukawa-Sky Aluminum Corp 高温ろう付け用薄肉ブレージングシートフィン材およびそれを使用した熱交換器の製造方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6042594A (ja) * 1983-08-18 1985-03-06 Seiichi Konaka フイン付熱交換装置
JPS6268112A (ja) * 1985-09-19 1987-03-28 Isuzu Motors Ltd 車両用熱発電装置
JPH0578917U (ja) * 1992-04-07 1993-10-26 日立金属株式会社 耐熱部材
JPH0914795A (ja) * 1995-06-30 1997-01-17 Sanyo Electric Co Ltd 冷媒加熱機
JP2002235992A (ja) * 2000-12-06 2002-08-23 Osaka Gas Co Ltd 熱交換器およびその熱交換器を用いた燃焼装置
JP2002313384A (ja) * 2001-02-07 2002-10-25 Calsonic Kansei Corp 燃料電池用熱交換器
JP2007078194A (ja) * 2005-09-09 2007-03-29 Usui Kokusai Sangyo Kaisha Ltd 熱交換器用伝熱管
JP2007211748A (ja) * 2006-02-13 2007-08-23 Toyota Motor Corp 熱交換器及び熱発電装置
JP2007225190A (ja) * 2006-02-23 2007-09-06 Maruyasu Industries Co Ltd 熱交換器
JP2010214379A (ja) * 2009-03-13 2010-09-30 Furukawa-Sky Aluminum Corp 高温ろう付け用薄肉ブレージングシートフィン材およびそれを使用した熱交換器の製造方法

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