WO2016098555A1 - 熱交換器 - Google Patents

熱交換器 Download PDF

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Publication number
WO2016098555A1
WO2016098555A1 PCT/JP2015/083261 JP2015083261W WO2016098555A1 WO 2016098555 A1 WO2016098555 A1 WO 2016098555A1 JP 2015083261 W JP2015083261 W JP 2015083261W WO 2016098555 A1 WO2016098555 A1 WO 2016098555A1
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WO
WIPO (PCT)
Prior art keywords
opening
exhaust
heat exchanger
fluid
plate
Prior art date
Application number
PCT/JP2015/083261
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
裕美 石川
直弘 竹本
裕久 大上
Original Assignee
フタバ産業株式会社
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 フタバ産業株式会社 filed Critical フタバ産業株式会社
Priority to CN201580068775.5A priority Critical patent/CN107003084A/zh
Priority to DE112015005686.6T priority patent/DE112015005686T5/de
Priority to US15/535,793 priority patent/US20170343302A1/en
Publication of WO2016098555A1 publication Critical patent/WO2016098555A1/ja

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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/02—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a heat exchanger
    • 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

Definitions

  • This disclosure relates to a heat exchanger.
  • Patent Document 1 There is known an exhaust heat recovery device that has a heat exchanger that exchanges heat from an internal combustion engine with a low-temperature fluid as a high-temperature fluid (see Patent Document 1 below).
  • the heat exchanger described in Patent Document 1 is a plate-stacked heat exchanger in which a plurality of plates having a flow space in which a low-temperature fluid flows are stacked.
  • the plate of the heat exchanger described in Patent Document 1 has a convex portion that is a portion protruding from the outer surface.
  • the surface area of the outer surface of the plate is increased by forming a convex portion on the outer surface of the plate, and the heat exchange rate between the low temperature fluid and the high temperature fluid is improved. .
  • one aspect of the present disclosure can provide a heat exchanger with an improved heat exchange rate from a high temperature fluid to a low temperature fluid.
  • One aspect of the present disclosure is a heat exchanger that performs heat exchange between a first fluid and a second fluid.
  • This heat exchanger includes a plurality of plates and fins.
  • the plurality of plates have a flow path through which the first fluid flows.
  • the fin connects adjacent plates among the plurality of plates.
  • the fin includes at least one first portion and at least one second portion.
  • the first part is a wall surface having at least one first opening.
  • the second part is a wall surface that forms a pair with the first part and is different from the first part.
  • the second portion has each of the second openings paired with at least one first opening.
  • the fin in one side of this indication has a corrugated cross-sectional shape by the set of the 1st part and the 2nd part.
  • the fins are arranged such that each of the first part and the second part is orthogonal to the flow direction of the second fluid.
  • the fin includes at least one opening pair which is a pair of a first opening and a second opening which form a pair. In at least one opening pair, at least a part of the paired first opening and second opening has a non-overlapping positional relationship in which they do not overlap along the flow direction of the second fluid.
  • the fin according to one aspect of the present disclosure extends so that the wall surface is orthogonal to the flow direction of the second fluid. Therefore, since the second fluid contacts the entire wall surface of the fin, the contact area can be increased.
  • the second fluid that has passed through the first opening of the fin collides with a region facing the first opening in the second portion. And in the area
  • the heat exchange rate from the high temperature fluid to the low temperature fluid can be further improved.
  • the heat exchanger according to one aspect of the present disclosure may be configured as a heat exchanger in which cylindrical plates are stacked along the axial direction.
  • the fins according to one aspect of the present disclosure may be arranged along the circumferential direction of the plate.
  • the flow direction of the second fluid can be a direction along the radial direction.
  • the first fluid flows along the circumferential direction of the plate.
  • the flow direction of the 2nd fluid can be made into the direction orthogonal to the flow direction of the 1st fluid.
  • the second direction of flow of the second fluid is set to a direction orthogonal to the direction of flow of the first fluid. This can be realized over the entire fluid flow range.
  • At least one opening pair of the heat exchanger may be configured such that the first opening and the second opening forming a pair are not overlapped along the flow direction of the second fluid. Good. According to such a heat exchanger, the area of the second portion where the second fluid that has passed through the first opening collides can be increased. Therefore, according to the heat exchanger in one side of this indication, it can control over a wider area that a boundary layer is formed in the circumference of the field which counters the 1st opening in the 2nd part.
  • all opening pairs may be non-overlapping positional relationship.
  • the area of the second portion where the second fluid that has passed through the first opening collides can be further increased. Therefore, according to the heat exchanger in one side of this indication, it can control over a wider area that a boundary layer is formed in the circumference of the field which counters the 1st opening in the 2nd part.
  • FIG. 2 is a cross-sectional view of the exhaust heat recovery device in a closed state, and is a cross-sectional view taken along the line II-II in FIG. It is a side view of a heat exchanger. It is a perspective view which shows the external appearance of a plate and a fin. It is a perspective view which shows the external appearance of a fin. It is a top view of a fin.
  • An exhaust heat recovery apparatus 1 shown in FIG. 1 is mounted on a moving body having an internal combustion engine 110.
  • the exhaust heat recovery apparatus 1 recovers heat from the exhaust 112 by exchanging heat with the exhaust 112 from the internal combustion engine 110 as a high-temperature fluid and the coolant 114 of the internal combustion engine 110 as a low-temperature fluid.
  • the exhaust 112 in the present embodiment is an example of the “second fluid” in the present disclosure
  • the coolant 114 is an example of the “first fluid” in the present disclosure.
  • the cooling liquid 114 in the present embodiment may be cooling water or an oil liquid.
  • the exhaust heat recovery apparatus 1 of this embodiment includes an exhaust part 2, a shell member 4, a heat exchange part 6 (see FIG. 2), an inflow part 8 (see FIG. 2), and a valve 10.
  • the exhaust unit 2 includes a path that guides the exhaust 112 from the internal combustion engine 110 to the downstream side.
  • the shell member 4 is a member that covers the outside of the exhaust part 2.
  • the heat exchange unit 6 includes a heat exchanger 30 (see FIG. 2) disposed between the exhaust unit 2 and the shell member 4, and the exhaust 112 as a high-temperature fluid and the inside of the plate 32 of the heat exchanger 30. Heat exchange with the flowing cryogenic fluid.
  • the inflow part 8 is a part into which the exhaust 112 flows from the exhaust part 2 to the heat exchange part 6.
  • the valve 10 is a well-known valve that opens and closes the path, and is disposed downstream of the inflow portion 8 along the flow path of the exhaust 112 in the exhaust portion 2.
  • the exhaust unit 2 includes an exhaust pipe 12.
  • the exhaust pipe 12 is a cylindrical member. Exhaust gas 112 from the internal combustion engine 110 flows into the exhaust pipe 12.
  • the shell member 4 includes an exhaust pipe 14, an outer shell member 20, a lid member 22, and a holding member 24.
  • the exhaust pipe 14 is a cylindrical member as a whole, and an upstream end 16 as one end portion has an opening having an inner diameter larger than the outer diameter of the exhaust pipe 12.
  • an exhaust downstream end 18, which is the end opposite to the upstream end of the exhaust pipe 12 is disposed in a non-contact state with the shell member 4.
  • the outer shell member 20 is a cylindrical member having an inner diameter larger than the diameter of the exhaust pipe 12.
  • the downstream end of the outer shell member 20 is connected to the upstream end 16 of the exhaust pipe 14.
  • the lid member 22 closes the opening on the upstream side of the outer shell member 20 along the flow path of the exhaust 112 in the exhaust pipe 12.
  • the outer shell member 20, the lid member 22, and the exhaust pipe 12 provide a heat exchange chamber 28 that is an annular space surrounded by the outer shell member 20, the lid member 22, and the exhaust pipe 12.
  • the heat exchanger 30 disposed in the heat exchange chamber 28 is a heat exchanger in which the cooling liquid 114 flows, and is disposed so as to cover the outer periphery of the exhaust pipe 12.
  • the heat exchanger 30 in the present embodiment includes a plurality of plates 32-1 to 32-N, an inflow pipe 44, an outflow pipe 46, and a plurality of fins 50-1 to 50-M. It has. That is, the heat exchanger 30 is a so-called plate stack type heat exchanger.
  • symbol N here is an identifier showing the number of the plates 32, and is a positive integer of 2 or more.
  • the symbol M in this embodiment is an identifier indicating the number of fins 50.
  • the code M is, for example, a positive integer that is “1” smaller than N.
  • Each plate 32 has a flow path through which the coolant 114 flows.
  • the fin 50 connects the plates 32 adjacent to each other among the plurality of plates 32.
  • the inflow pipe 44 is a pipe through which the cooling liquid 114 from the outside of the heat exchanger 30 flows into one plate 32.
  • the outflow pipe 46 is a pipe through which the cooling liquid 114 flows out from one plate 32 to the outside of the heat exchanger 30.
  • each plate 32 includes a first plate plate 34 and a second plate plate 36.
  • the first plate plate 34 is a ring-shaped member.
  • the first plate plate 34 has a wall portion that protrudes in the same direction from the periphery of the first plate plate 34.
  • the second plate plate 36 is a ring-shaped member.
  • the second plate plate 36 has a wall portion protruding in the same direction from the periphery of the second plate plate 36.
  • each of the plates 32 is configured by engaging the wall portion of the second plate plate 36 with the wall portion of the first plate plate 34.
  • Each plate 32 includes a gap between the inner surface of the first plate plate 34 and the inner surface of the second plate plate 36. The gap functions as a flow space in which a low-temperature fluid flows, that is, a flow path of the coolant 114.
  • Each plate 32 includes a first communication portion 38 and a second communication portion 39.
  • the 1st communicating part 38 is provided with the path
  • the second communication part 39 includes a path through which the coolant 114 flows from the downstream to the outflow pipe 46 along the flow path of the exhaust 112 in the exhaust part 2 to the adjacent plate 32.
  • the first communication part 38 and the second communication part 39 in the present embodiment include a first cylindrical part 40 and a second cylindrical part 42.
  • the first tubular portion 40 is a tubular portion that stands upright from the opening of the first plate plate 34 in the direction opposite to the wall portion.
  • the second cylindrical part 42 is a cylindrical part erected from the peripheral edge of the opening of the second plate plate 36 in the direction opposite to the wall part.
  • the 1st communication part 38 and the 2nd communication part 39 are joined by joining the 1st cylindrical part 40 with which the 1st plate board 34 is provided, and the 2nd cylindrical part 42 with which the 2nd plate board 36 is provided.
  • the 2nd cylindrical part 42 with which the 2nd plate board 36 said here is the 2nd cylindrical part 42 with which the 2nd plate board 36 adjacent to the outer surface of the 1st plate board 34 through the fin 50 is provided. .
  • the construction method of the first communication portion 38 and the second communication portion 39 is not limited to this, and if it is constructed so as to function as a flow path of the cooling liquid 114 between the plates 32, it is constructed in any way. May be.
  • each plate 32 is arranged so as to cover the outer periphery of the exhaust pipe 12.
  • Each plate 32 is disposed so as to have a gap 64 along the radial direction of the exhaust pipe 12 between the central peripheral edge along the radial direction of each plate 32 and the outer surface of the exhaust pipe 12.
  • each plate 32 is arranged such that a gap 66 along the radial direction of the exhaust pipe 12 is provided between the outer peripheral edge along the radial direction of each plate 32 and the inner surface of the outer shell member 20. .
  • the fin 50 is a member having a truncated arc shape connected to the two plates 32 adjacent to each other. As shown in FIGS. 5 and 6, the fin 50 includes first portions 52-1 to 52-L and second portions 54-1 to 54-L. In the fin 50, the 1st site
  • the sign “L” here is a positive integer of 1 or more.
  • the first part 52 is a rectangular plate-like part that functions as a wall surface of the fin 50.
  • Each of the first portions 52 includes at least one first opening 58 having a first opening 56.
  • part 52 may have the 1st opening 56 at equal intervals, and may have the 1st opening 56 at unequal intervals.
  • the second part 54 is a rectangular plate-like part that forms a pair with the first part 52 and functions as a wall surface different from the first part 52. Further, the second portion 54 includes at least one second opening 62 having a second opening 60 that is paired with the first opening 56. In the present embodiment, the second part may have the second openings 60 at regular intervals, or may have the second openings 60 at irregular intervals.
  • each first opening 56, the area of each second opening 60, the total area of the first opening 56, and the total area of the second opening 60 may be appropriately determined in relation to the pressure of the exhaust 112.
  • One side along the longitudinal direction of the first part 52 is connected to one side along the longitudinal direction of one second part 54.
  • the other side along the longitudinal direction of the first part 52 is connected to one side along the longitudinal direction of the different second part 54.
  • the fin 50 is connected to the plate 32 so that the arc of the fin 50 is along the circumferential direction of the plate 32.
  • one end of the triangular wave shape of the fin 50 is connected to the outer surface of one plate 32.
  • the remaining triangular vertices are connected to the outer surface of another plate 32 adjacent to that plate 32.
  • part 54 is arrange
  • the number of the first openings 56 included in one first portion 52 may be the same regardless of the position along the radial direction of the first portion 52, or the first portion 52 located on the outer peripheral side. It may be as much as possible.
  • the number of the second openings 60 included in the second part 54 is preferably the same as the number of the first openings 56 formed in the first part 52 corresponding to the second part 54.
  • the first opening 56 and the second opening 60 that form at least one opening pair 70 out of the opening pair 70 that is a pair of the first opening 56 and the second opening 60 that form a pair. At least a part of the non-overlapping positional relationship is non-overlapping along the flow direction of the exhaust 112.
  • the opening pair 70 referred to here is a first opening 56 and a second opening 60 included in the first portion 52 and the second portion 54 constituting a pair, and the first opening 56 and the second opening 60 satisfy a specified condition.
  • the prescribed condition referred to here may be the closest position from the first opening 56, or may be other conditions.
  • the non-overlapping positional relationship specifically means that the entirety of the second opening 60 is not along the normal direction of the first portion 52 from the first opening 56 that forms a pair as the opening pair 70. It is an overlap.
  • the non-overlapping positional relationship includes, for example, that the second opening 60 and the first opening 56 are staggered.
  • the positional relationship between the first openings 56 and the second openings 60 constituting all the opening pairs 70 is a non-overlapping positional relationship.
  • the gap 64, the first opening 56, the second opening 60, and the gap 66 function as a flow path for the exhaust 112.
  • the exhaust 112 flowing through the gap 64, the first opening 56, the second opening 60, and the gap 66 is used as a high-temperature fluid (second fluid), and the coolant 114 flowing in each plate 32 is used as the low-temperature fluid (first fluid). ), Heat exchange is performed. That is, in the present embodiment, the heat exchange chamber 28 in which the heat exchanger 30 is disposed functions as the heat exchange unit 6.
  • the holding member 24 shown in FIG. 2 is a member that holds the heat exchanger 30 disposed in the heat exchange chamber 28.
  • the introduction member 80 is a cylindrical member having a diameter larger than that of the exhaust pipe 12, and one end thereof is connected to the holding member 24.
  • the end of the introduction member 80 opposite to the side connected to the holding member 24 has a diffuser shape with an increased diameter.
  • the introduction member 80 is disposed so as to have an opening between the exhaust pipe 12.
  • the opening functions as an inlet of the exhaust 112 to the heat exchange unit 6.
  • the valve 10 includes at least a valve body 102 and a valve seat 104, and closes the exhaust part 2 (introduction member 80) when the valve body 102 contacts the valve seat 104.
  • the diffuser-shaped end portion of the introduction member 80 functions as the valve seat 104.
  • the valve seat 104 in the present disclosure is not limited to this, and may be provided exclusively.
  • a mesh-like mesh member 108 is attached to the inner peripheral surface of the valve seat 104.
  • the valve 10 in this embodiment opens the exhaust part 2 when the liquid temperature of the coolant 114 of the internal combustion engine 110 is higher than a predetermined temperature.
  • the valve 10 closes the exhaust part 2 when the temperature of the coolant 114 of the internal combustion engine 110 is lower than the specified temperature.
  • the fin 50 included in the heat exchanger 30 extends so that the wall surface is orthogonal to the flow direction of the exhaust 112. Therefore, the exhaust 112 is in contact with the entire wall surface of the fin 50. For this reason, the contact area between the fin 50 and the exhaust 112 can be widened, and the heat transfer from the exhaust 112 to the coolant 114 can be realized more efficiently.
  • the exhaust 112 that has passed through the first opening 56 of the fin 50 collides with a region facing the first opening 56 in the second portion 54. And in the area
  • the entire first opening 56 and second opening 60 associated as at least one opening pair 70 are non-overlapping along the flow direction of the exhaust 112, and all The opening pair 70 is in a non-overlapping positional relationship.
  • the heat exchanger 30 the area of the 2nd site
  • the heat exchange rate from the high temperature fluid to the low temperature fluid can be further improved.
  • the heat exchanger 30 has a cylindrical plate 32 laminated in the axial direction.
  • the fin 50 is arrange
  • the flow direction of the exhaust 112 can be a direction along the radial direction of the plate 32.
  • the coolant 114 flows along the circumferential direction of the plate 32.
  • the flow direction of the exhaust 112 can be set to a direction orthogonal to the flow direction of the coolant 114.
  • the flow direction of the exhaust 112 can be realized in the direction orthogonal to the flow direction of the coolant 114 over the entire radial direction of the plate 32.
  • the cross-sectional shape of the fin 50 is a triangular wave shape as a whole, but the cross-sectional shape of the fin 50 is not limited to this, and may be a sine wave shape or a rectangular wave shape. Or a saw-toothed wave shape. That is, the cross-sectional shape of the fin 50 may be any shape as long as the cross-sectional shape of the fin 50 as a whole is a waveform.
  • the non-overlapping positional relationship indicates that the first opening 56 and the second opening 60 constituting at least one opening pair 70 are non-overlapping along the flow direction of the exhaust 112.
  • the non-overlapping positional relationship is not limited to this, and at least a part of the first opening 56 and the second opening 60 constituting the at least one opening pair 70 may be non-overlapping. .
  • the opening pairs 70 having the non-overlapping positional relationship are all the opening pairs 70.
  • the opening pair 70 having the non-overlapping positional relationship is at least one of the opening pairs 70. It may be.
  • the opening between the exhaust downstream end 18 and the introduction member 88 functions as an inlet of the exhaust 142 from the exhaust pipe 12 to the heat exchange unit 6.
  • the inlet of the exhaust 142 to the exchange unit 6 may be a hole formed in the exhaust pipe 12 itself.
  • the exhaust heat recovery apparatus 1 in the above embodiment is mounted on a moving body having the internal combustion engine 110
  • the exhaust heat recovery apparatus in the present disclosure may not be mounted on the moving body. That is, the exhaust heat recovery device in the present disclosure is used without being mounted on a moving body as long as it recovers heat from the exhaust 112 by exchanging heat from the exhaust 112 from the internal combustion engine 110 as a high-temperature fluid. May be.
  • the low-temperature fluid in the exhaust heat recovery apparatus may not be the coolant 114 but may be other fluids that act as a low-temperature fluid.
  • the application object of the heat exchanger 30 was made into the exhaust heat recovery apparatus 1, the application object of the heat exchanger 30 is not restricted to the exhaust heat recovery apparatus 1.
  • the shape of the heat exchanger 30 is not limited to a cylindrical shape. That is, in the heat exchanger of the present disclosure, if the fins 50 that connect the adjacent plates 32 are provided so as to be orthogonal to the flow direction of the second fluid, the shapes of the plates 32 and the fins 50 are rectangular. There may be other shapes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2015/083261 2014-12-17 2015-11-26 熱交換器 WO2016098555A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201580068775.5A CN107003084A (zh) 2014-12-17 2015-11-26 热交换器
DE112015005686.6T DE112015005686T5 (de) 2014-12-17 2015-11-26 Wärmetauscher
US15/535,793 US20170343302A1 (en) 2014-12-17 2015-11-26 Heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014255334A JP2016114331A (ja) 2014-12-17 2014-12-17 熱交換器
JP2014-255334 2014-12-17

Publications (1)

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WO2016098555A1 true WO2016098555A1 (ja) 2016-06-23

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US (1) US20170343302A1 (zh)
JP (1) JP2016114331A (zh)
CN (1) CN107003084A (zh)
DE (1) DE112015005686T5 (zh)
WO (1) WO2016098555A1 (zh)

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Publication number Priority date Publication date Assignee Title
CN109996420B (zh) * 2017-12-29 2020-12-22 讯凯国际股份有限公司 组合式散热鳍片结构
JP7217654B2 (ja) * 2019-03-26 2023-02-03 日本碍子株式会社 熱交換器

Citations (3)

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JPS5030145A (zh) * 1973-07-19 1975-03-26
JP2014095482A (ja) * 2012-11-07 2014-05-22 Keihin Thermal Technology Corp 二重管式熱交換器
JP2014194319A (ja) * 2013-03-29 2014-10-09 Calsonic Kansei Corp 熱交換器

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