WO2021059921A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2021059921A1
WO2021059921A1 PCT/JP2020/033519 JP2020033519W WO2021059921A1 WO 2021059921 A1 WO2021059921 A1 WO 2021059921A1 JP 2020033519 W JP2020033519 W JP 2020033519W WO 2021059921 A1 WO2021059921 A1 WO 2021059921A1
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WO
WIPO (PCT)
Prior art keywords
flow path
heat exchange
exhaust gas
heat
exchange tube
Prior art date
Application number
PCT/JP2020/033519
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English (en)
Japanese (ja)
Inventor
友哉 中村
章弘 川又
Original Assignee
株式会社ユタカ技研
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 株式会社ユタカ技研 filed Critical 株式会社ユタカ技研
Publication of WO2021059921A1 publication Critical patent/WO2021059921A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • 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
    • F28D7/16—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 in parallel spaced relation
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a heat exchanger that exchanges heat between two types of heat media.
  • the exhaust gas discharged from the engine is cooled by cooling water and recirculated to the engine.
  • Exhaust gas is cooled by an EGR (Exhaust Gas Recirculation) cooler.
  • the EGR cooler can be said to be a heat exchanger that exchanges heat between the exhaust gas and the cooling water.
  • Patent Document 1 discloses an EGR cooler as a heat exchanger.
  • the EGR cooler a plurality of heat exchange tubes are surrounded by a core case, and the exhaust gas (first heat medium) flowing inside the heat exchange tubes and the cooling flowing inside the core case on the outer periphery of the heat exchange tubes. Heat exchange is performed with water (second heat medium).
  • the EGR cooler also includes a valve that opens and closes some heat exchange tubes.
  • the temperature of the exhaust gas returned to the engine can be stabilized at the target temperature regardless of the flow rate of the exhaust gas.
  • the temperature of the first heat medium discharged from the heat exchanger can be stabilized.
  • An object of the present invention is to provide a heat exchanger capable of stabilizing the temperature of the first heat medium to be discharged while being inexpensive and compact.
  • a first aspect of the present invention includes a plurality of flat heat exchange tubes through which a first heat medium flows, and a core case containing the plurality of heat exchange tubes.
  • a heat exchanger in which a second heat medium flowing around the outer periphery of the heat exchange tube and the first heat medium exchange heat inside the core case.
  • the plurality of heat exchange tubes include at least one specific heat exchange tube. Inside the specific heat exchange tube, there are a fin-equipped flow path having fins, and a finless flow path that exchanges heat with a smaller amount of heat than the fin-equipped flow path because it does not have the fins.
  • Heat exchangers are provided characterized by being partitioned in.
  • the specific heat exchange tube is thicker than the general heat exchange tube. ..
  • the cross section of the finless flow path is square.
  • two fin-equipped flow paths are provided for one specific heat exchange tube, and the fins constituting each fin-equipped flow path have the same shape. And The finless flow path is located between the two finned flow paths.
  • the plurality of heat exchange tubes include at least one specific heat exchange tube.
  • the inside of this specific heat exchange tube is divided into a flow path with fins having fins and a flow path without fins that exchange heat with a smaller amount of heat than the flow path with fins because it does not have fins. Has been done.
  • the temperature of the first heat medium discharged from the finless flow path is closer to the temperature on the introduction side.
  • the first heat medium which has undergone heat exchange of an excessive amount of heat with respect to the appropriate temperature
  • the first heat medium closer to the temperature on the introduction side the first heat medium is discharged in a region where the flow rate is low.
  • the temperature of the heat medium of the above becomes an appropriate temperature.
  • the temperature of the first heat medium discharged from the finned flow path is set to be an appropriate temperature.
  • the finless flow path since the finless flow path has a small amount of heat for cooling, the first heat medium discharged from the finless flow path has a high temperature in a region where the flow rate of the first heat medium is large.
  • the first heat medium in the finless flow path becomes a resistance, and more first heat medium flows into the finned flow path.
  • the influence of the exhaust gas passing through the finless flow path is relatively low.
  • a small amount of the high-temperature first heat medium that has passed through the finless flow path is mixed with the first heat medium that has passed through the finned flow path and has been adjusted to an appropriate temperature. Therefore, the temperature of the first heat medium to be discharged does not rise excessively and is discharged to the outside of the heat exchanger at an appropriate temperature.
  • the finless flow path is provided inside the heat exchange tube. Therefore, the heat exchanger can be miniaturized as compared with the case where a tube having a small amount of heat for heat exchange is separately provided.
  • a general heat exchange tube other than the specific heat exchange tube is used.
  • the specific heat exchange tube is thicker than the general heat exchange tube. Therefore, the flow path area of the finless flow path of the specific heat exchange tube becomes large. On the other hand, the thickness of the general heat exchange tube is maintained. That is, even when the flow path area of the finless flow path is set large, it is possible to prevent the heat exchanger from becoming large.
  • the cross section of the finless flow path is square.
  • the circumference of the square is shorter than the circumference of the rectangle. Therefore, the pipe friction loss of the first heat medium flowing through the finless flow path can be reduced.
  • two fin-equipped flow paths are provided for one specific heat exchange tube, and the fins constituting each fin-equipped flow path have the same shape. Therefore, the number of fin parts can be reduced.
  • a finless flow path is located between the two finned flow paths. Since the finless flow path is located closer to the center, it becomes easy to guide the gas introduced inside the heat exchanger to the finless flow path.
  • FIG. 1A is a perspective view of a heat exchanger according to an embodiment.
  • FIG. 1B is an exploded perspective view of the heat exchanger shown in FIG. 1A. It is a cross section of line 2-2 of FIG. 1 (a).
  • FIG. 3A is a cross-sectional view of a specific heat exchange tube constituting a part of the heat exchanger shown in FIG.
  • FIG. 3B is a perspective view of a specific heat exchange tube forming a part of the heat exchanger shown in FIG. It is a cross section of line 4-4 of FIG. 1 (a). It is a cross section of line 5-5 of FIG. 1 (a).
  • upstream and downstream are based on the flow direction of the exhaust gas (first heat medium).
  • the EGR (Exhaust Gas Recirculation) cooler 10 (heat exchanger 10) has a rectangular body 16 composed of five heat exchange tubes 11 to 15, a tubular core case 20 surrounding the body 16, and a core case 20.
  • the core case 20 is composed of a pair of U-shaped case halves 50 and 60 whose opening sides face each other.
  • the first case half body 50 has a flat plate-shaped first base portion 51 extending in the exhaust gas flow direction, and a first case half body extending from both ends of the first base portion 51 to the second case half body. It is composed of a wall half body 52 and a second wall half body 53.
  • the first base 51 has a water introduction hole 51a for introducing cooling water (second heat medium) and a water discharge hole 51b for discharging cooling water.
  • the second case half body 60 has a flat plate-shaped second base 61 extending in the exhaust gas flow direction and a third case half body 60 extending from both ends of the second base 61 to the first case half body 50. It is composed of a wall half body 62 and a fourth wall half body 63.
  • the first wall portion 52 and the third wall portion 62 constitute the first wall portion 21.
  • the second wall portion 53 and the fourth wall portion 63 constitute the second wall portion 22.
  • the first base 51, the second base 61, the first wall 21, and the second wall 22 form a tubular core case 20 having both ends open.
  • the main body 16 is formed by laminating the first heat exchange tubes 11 to the fifth heat exchange tubes 15.
  • a third heat exchange tube 13 (specific heat exchange tube) located at the center of the stacking direction and not provided with fins in a part thereof will be described.
  • the third heat exchange tube 13 is composed of a flat tube 83 composed of a pair of U-shaped tube halves 81 and 82, and two fins 90 and 90 housed in the tube 83. Become.
  • the third heat exchange tube 13 has a symmetrical configuration with respect to the center in the width direction (longitudinal direction of the cross section) of the third heat exchange tube 13.
  • the first tube half body 81 has a flat first flat portion 84 and two first edge portions 85 extending from both ends of the first flat portion 84 toward the second tube half body 82. , 85 and.
  • the second tube half body 82 has a flat second flat portion 86 and two second edge portions 87 extending from both ends of the second flat portion 86 toward the first tube half body 81. , 87 and.
  • the first edge portion 85 and the second edge portion 87 form a side wall portion 88.
  • Each fin 90 has a pulse wavy shape as a whole, and has a plurality of first contact portions 91 that are in contact with the first flat portion 84 and a plurality of second contacts that are in contact with the second flat portion 86.
  • the heat of the exhaust gas that extends between the abutting portion 92 of the above, the end portion 91a of each of the first abutting portions 91, and the end portion 92a of each of the second abutting portions 92 and flows inside the tube 83. It is composed of a plurality of heat absorbing portions 93 that absorb the heat.
  • the fin 90 may be provided with an uneven portion or a cut-up portion.
  • the heat absorbing portion 93 located on the innermost side in the width direction of the third heat exchange tube 13 is designated as the partition wall portion 94. It can be said that the inside of the third heat exchange tube 13 is divided into three by two partition walls 94.
  • the inside of the third heat exchange tube 13 is a first flow path F1 (flow path with fins) between one side wall portion 88 of the tube 83 and one partition wall portion 94, and the other of the tube 83.
  • second flow path F2 flow path without fins
  • the width of the second flow path F2 that is, the dimension W1 between the two partition walls 94, is larger than the pitch W2 of the fins 90 (the distance between the endothermic portions 93 adjacent to each other).
  • the flow path area of the first flow path F1 is larger than the flow path area of the second flow path F2.
  • the heat exchange tubes 11, 12, 14, and 15 (general heat exchange tubes) other than the third heat exchange tube 13 have the same configuration as each other.
  • the configuration of the second heat exchange tube 12 will be described. This description also applies to other heat exchange tubes 11, 14, 15.
  • the second heat exchange tube 12 is composed of a flat tube 73 composed of a pair of U-shaped tube halves 71 and 72, and a wavy single fin 74 housed in the tube 73. Become.
  • the first tube half body 71 has a flat first flat portion 75 and two first edge portions 76 extending from both ends of the first flat portion 75 toward the second tube half body 72. , 76 and.
  • the second tube half body 72 has a flat second flat portion 77 and two second edge portions 78 extending from both ends of the second flat portion 77 toward the first tube half body 71. , 78 and.
  • the third heat exchange tube 13 is thicker than the second heat exchange tube 12.
  • the internal height H1 of the third heat exchange tube 13 (the dimension in the direction in which the heat absorbing portion 93 extends) is higher than the internal height H2 of the second heat exchange tube 12.
  • the size L1 of the opening on the introduction side of the third heat exchange tube 13 is wider than the size L2 of the flow path in the third heat exchange tube 13 with reference to the thickness direction of the tube.
  • the end portion 84a on the exhaust gas introduction side is offset to the adjacent fourth heat exchange tube 14 side.
  • the end portion 86a on the exhaust gas introduction side of the second flat portion 86 is offset to the adjacent second heat exchange tube 12 side.
  • the heat exchange tubes 11, 12, 14, and 15 have the same configuration.
  • the end portion 75a on the exhaust gas introduction side of the first flat portion 75 is offset to the adjacent third heat exchange tube 13 side.
  • the end 77a on the exhaust gas introduction side of the second flat portion 77 is offset to the adjacent first heat exchange tube 11 side. The ends adjacent to each other are in contact with each other.
  • the support member (end plate) that supports the five heat exchange tubes 11 to 15 becomes unnecessary.
  • the gap between the heat exchange tubes 11 to 15 adjacent to each other serves as a flow path for the cooling water to flow.
  • the end portion 75a of the first flat portion 75 located at one corner (lower side) is in contact with the first wall portion half body 52.
  • the end portion 77a of the second flat portion 77 located at the other corner (upper side) is in contact with the second wall portion half body 53.
  • each heat exchange tube 11 to 15 on the exhaust gas discharge side has the same configuration. The description is omitted.
  • the gas introduction member 30 includes a flat plate-shaped introduction side bottom portion 31 having an introduction hole 31a into which exhaust gas can be introduced, and an introduction side peripheral wall portion 32 extending from the peripheral edge of the introduction side bottom portion 31 in the exhaust gas flow direction. Have. The introduction side peripheral wall portion 32 overlaps one end of the core case 20.
  • the gas discharge member 40 includes a flat plate-shaped discharge side bottom 41 having a discharge hole 41a capable of discharging exhaust gas, and a discharge side peripheral wall portion 42 extending from the peripheral edge of the discharge side bottom 41 in a direction opposite to the flow direction of the exhaust gas. And have.
  • the discharge side peripheral wall portion 42 overlaps the other end of the core case 20.
  • the exhaust gas discharged from the engine is introduced into the core case 20 from the gas introduction member 30.
  • the introduced exhaust gas passes through the two flow paths F1 and the flow path F2.
  • the cooling water introduced into the core case 20 flows from the water introduction hole 51a to the outer periphery of the heat exchange tubes 11 to 15.
  • the exhaust gas passing through each of the heat exchange tubes 11 to 15 is cooled by the cooling water flowing on the outer circumference.
  • the cooled exhaust gas is discharged from the gas discharge member 40 and returned to the engine.
  • the cooling water that has absorbed the heat of the exhaust gas is discharged to the outside of the core case 20 from the water discharge hole 51b.
  • FIG. 6 shows the relationship between the flow rate of the exhaust gas and the temperature of the exhaust gas.
  • the horizontal axis shows the flow rate [g / s] of the exhaust gas
  • the vertical axis shows the temperature [° C] of the exhaust gas.
  • Tmin shown on the vertical axis is the lower limit of the temperature allowed as the temperature of the exhaust gas discharged from the EGR cooler.
  • Tmax shown on the vertical axis is an upper limit of the temperature allowed as the temperature of the exhaust gas discharged from the EGR cooler.
  • T1 and T1 indicate the temperature of the exhaust gas that has passed through the respective flow paths F1.
  • T2 indicates the temperature of the exhaust gas that has passed through the flow path F2.
  • T3 indicates the temperature of a gas in which the exhaust gas passing through the flow path F1 and the exhaust gas passing through the flow path F2 are mixed (hereinafter, referred to as “mixed gas”).
  • the temperature of the exhaust gas is low in the region where the flow rate is low, and the temperature of the exhaust gas is high in the region where the flow rate is high.
  • the temperature T1 of the exhaust gas that has passed through the flow path F1 is below the lower limit Tmin of the allowable temperature in the region where the flow rate is small. It can be said that the exhaust gas passing through the flow path F1 is excessively cooled in the region where the flow rate is low.
  • the temperature T2 of the exhaust gas that has passed through the flow path F2 is higher than the temperature T1 of the exhaust gas that has passed through the flow path F1 in all regions.
  • the temperature T0 of the exhaust gas when it is introduced into the EGR cooler is the same for the exhaust gas passing through the flow path F1 and the exhaust gas passing through the flow path F2. Therefore, it can be said that the amount of heat exchanged by the flow path F1 is larger than the amount of heat exchanged by the flow path F2.
  • T2 of the exhaust gas that has passed through the flow path F2 exceeds Tmax, which is the upper limit of the allowable temperature, in all regions.
  • the temperature T3 of the mixed gas is between Tmin and Tmax, which is an acceptable temperature in all regions.
  • the difference between the lowest temperature and the highest temperature is defined as ⁇ T1.
  • the difference between the lowest temperature and the highest temperature is defined as ⁇ T3. Comparing ⁇ T1 and ⁇ T3, ⁇ T3 is smaller. That is, it can be said that ⁇ T1> ⁇ T3, and the temperature of the mixed gas was more stable than that of the exhaust gas that passed through the flow path F1.
  • the exhaust gas that has passed through the flow path F1 and the exhaust gas that has passed through the flow path F2, which has a smaller amount of heat exchange than the flow path F1 are mixed.
  • the temperature T3 of the mixed gas becomes between Tmin and Tmax, which is an allowable temperature, and the temperature of the exhaust gas also stabilizes.
  • FIG. 7 shows the relationship between the pressure of the exhaust gas introduced into the EGR cooler and the flow rate of the exhaust gas passing through each heat exchange tube.
  • the horizontal axis shows the pressure [N / m 2 ] of the exhaust gas introduced into the EGR cooler, and the vertical axis shows the flow rate [g / s] of the exhaust gas passing through each heat exchange tube.
  • Q1 shows the flow rate of the exhaust gas that has passed through the flow path F1.
  • Q2 indicates the flow rate of the exhaust gas that has passed through the flow path F2.
  • the flow rate of the exhaust gas flowing inside increases as the pressure of the exhaust gas increases. In all regions, the flow rate of the exhaust gas that has passed through the flow path F1 is higher than the flow rate of the exhaust gas that has passed through the flow path F2.
  • ⁇ Q which is the difference between the flow rate of the exhaust gas flowing through the flow path F1 and the flow rate of the exhaust gas flowing through the flow path F2.
  • ⁇ Qmin the difference in the exhaust gas flow rate
  • ⁇ Qmax the difference in the exhaust gas flow rate
  • the heat exchange tubes 11 to 15 are surrounded by the core case 20, and the exhaust gas flowing inside the heat exchange tubes 11 to 15 is the cooling water that flows inside the core case 20 on the outer periphery of the heat exchange tubes 11 to 15.
  • the heat exchange tubes 11 to 15 include different types of flow paths F1 and F2, and the amount of heat exchanged by the flow path F1 is the heat performed by the flow path F2. It is set to be more than the amount of heat for replacement.
  • the temperature of the exhaust gas discharged from the flow path F1 is set to be an appropriate temperature in the region where the flow rate of the exhaust gas is large.
  • the flow path F2 since the flow path F2 has a small amount of heat for cooling, the exhaust gas discharged from the flow path F2 has a high temperature in a region where the flow rate of the exhaust gas is large.
  • the exhaust gas in the flow path F2 becomes a resistance, and more exhaust gas flows into the flow path F1. Since the flow rate of the exhaust gas flowing through the flow path F2 is small, the influence of the exhaust gas passing through the flow path F2 is relatively low.
  • the flow path F2 is provided inside the third heat exchange tube 13. Therefore, the EGR cooler 10 can be downsized as compared with the case where a tube having a small amount of heat exchange is provided separately.
  • the flow path area of the flow path F1 is larger than the flow path area of the flow path F2.
  • the amount of heat exchanged in the flow path F1 can be further increased. In a region where the flow rate is large, the influence of the exhaust gas passing through the flow path F2 can be reduced.
  • Each of the exhaust holes 41a overlaps with the second flow path F2 when viewed from the direction along the flow of the exhaust gas.
  • the second flow path F2 is located inside the discharge hole 41a (introduction hole 31a). Therefore, a predetermined amount of exhaust gas can be reliably guided to the flow path F2.
  • the temperature of the gas discharged from the EGR cooler 10 can be more reliably raised to a temperature higher than a predetermined temperature. Thereby, the stability of the temperature of the exhaust gas can be improved.
  • the third heat exchange tube 13 is thicker than the second heat exchange tube 12.
  • the internal height H1 of the third heat exchange tube 13 (the dimension in the direction in which the heat absorbing portion 93 extends) is higher than the internal height H2 of the second heat exchange tube 12.
  • the flow path area of the flow path F2 of the third heat exchange tube 13 becomes larger.
  • the thicknesses of the heat exchange tubes 11, 12, 14 and 15 are maintained. That is, even when the flow path area of the flow path F2 is set large, it is possible to prevent the EGR cooler 10 from becoming large.
  • Two flow paths F1 are provided for the third heat exchange tube 13, and the fins 90 constituting each flow path F1 have the same shape. Therefore, the number of parts can be reduced.
  • the flow path F2 is located between the two flow paths F1. Since the flow path F2 is located in the center, the gas introduced inside the EGR cooler 10 can be easily guided to the flow path F2.
  • FIG. 8 shows a third heat exchange tube 13A according to a modified example.
  • the configurations of the four fins 90A provided inside are different.
  • the configurations common to the examples are designated by the same reference numerals as those in the examples, and the description thereof will be omitted.
  • the two fins 90A and 90A adjacent to each other are symmetrical with respect to the center in the width direction.
  • the two fins 90A and 90A adjacent to each other are symmetrical with respect to the center in the height direction.
  • Each fin 90A has a plurality of first contact portions 91A that are in contact with the tube 83, and a plurality of second contact portions 92A that are in contact with the fins 90A that are symmetrically arranged in the height direction.
  • a plurality of endothermic portions that extend between the end of the first abutting portion 91A and the end of the second abutting portion 92 and absorb the heat of the exhaust gas flowing inside the third heat exchange tube 13. It consists of 93A.
  • the one located on the innermost side is referred to as the inner endothermic portion 94A.
  • the two inner heat absorbing portions 94A adjacent to each other in the height direction constitute a partition wall portion 95A that partitions the inside of the tube 83.
  • the inside of the third heat exchange tube 13A is divided into three by two partition walls 95A and 95A (only the code of one partition wall 95A is shown).
  • the inside of the third heat exchange tube 13A includes a first flow path f1 (flow path with fins) between one side wall portion 88 of the tube 83 and one partition wall portion 95A, and the other of the tube 83.
  • First flow path f1 flow path with fins
  • second flow path f2 flow path without fins
  • the modified example has the following unique effects in addition to the effects of the examples.
  • the two fins 90A and 90A provided in the third heat exchange tube 13A are laminated in the height direction.
  • the height can be adjusted by laminating the fins 90A. Since the fin 90A is highly versatile, the manufacturing cost can be reduced.
  • the distance W3 between the partition walls 95A and 95A is equal to the height H3 inside the third heat exchange tube 13. That is, the cross section of the flow path f2 is square. In general, when comparing a rectangle and a square of the same area, the circumference of the square is shorter than the circumference of the rectangle. Therefore, the pipe friction loss of the exhaust gas flowing through the flow path F2 can be reduced.
  • the heat exchanger of the present invention was applied to the EGR cooler in the embodiment, it can be applied to other uses. Further, it can be used not only for heat exchange between gas and liquid but also for heat exchange between gas and gas.
  • the present invention is not limited to Examples and Modifications as long as it exerts actions and effects.
  • the components of the embodiment and the components of the modified example may be appropriately combined, and the number of heat exchange tubes may be appropriately changed.
  • the heat exchanger of the present invention is suitable for an EGR cooler.
  • EGR cooler heat exchanger
  • Second heat exchange tube generally heat exchange tube
  • Third heat exchange tube specific heat exchange tube
  • Core case 90 ... Fins 91 ... First contact portion 92 ... Second contact portion 93 ... Endothermic portion
  • F1 ... First flow path (flow path with fins)
  • F2 Second flow path (flow path without fins)

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Une pluralité de tubes échangeurs de chaleur comprennent au moins un tube échangeur de chaleur spécifique (13). L'intérieur du tube échangeur de chaleur spécifique (13) est divisé en trajets d'écoulement (F1) qui comportent une ailette (90) et un trajet d'écoulement (F2) qui permet une plus petite quantité d'échange de chaleur que les trajets d'écoulement (F1) en raison de l'absence d'ailette (90).
PCT/JP2020/033519 2019-09-27 2020-09-04 Échangeur de chaleur WO2021059921A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019176523A JP7136757B2 (ja) 2019-09-27 2019-09-27 熱交換器
JP2019-176523 2019-09-27

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WO2021059921A1 true WO2021059921A1 (fr) 2021-04-01

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WO (1) WO2021059921A1 (fr)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5323491U (fr) * 1977-06-10 1978-02-27
JP2004263616A (ja) * 2003-02-28 2004-09-24 Toyo Radiator Co Ltd Ｅｇｒクーラ用の偏平チューブ
US20050274501A1 (en) * 2004-06-09 2005-12-15 Agee Keith D Decreased hot side fin density heat exchanger
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JP2011214786A (ja) * 2010-03-31 2011-10-27 Yutaka Giken Co Ltd 熱交換器
JP2012241597A (ja) * 2011-05-18 2012-12-10 Toyota Motor Corp 排気冷却器
JP2015036542A (ja) * 2013-08-12 2015-02-23 現代自動車株式会社 Ｅｇｒガス及びエンジンオイル冷却装置とその制御方法

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JP2004263616A (ja) * 2003-02-28 2004-09-24 Toyo Radiator Co Ltd Ｅｇｒクーラ用の偏平チューブ
US20050274501A1 (en) * 2004-06-09 2005-12-15 Agee Keith D Decreased hot side fin density heat exchanger
JP2006038304A (ja) * 2004-07-23 2006-02-09 Usui Kokusai Sangyo Kaisha Ltd 流体攪拌用フィンおよびその製造方法並びに該フィンを内装した伝熱管および熱交換器または熱交換型ガス冷却装置
US20090166020A1 (en) * 2004-07-28 2009-07-02 Smith Paul R Automotive heat exchanger assemblies having internal fins and methods of making the same
JP2007078194A (ja) * 2005-09-09 2007-03-29 Usui Kokusai Sangyo Kaisha Ltd 熱交換器用伝熱管
US20080264609A1 (en) * 2007-04-26 2008-10-30 Behr Gmbh & Co. Kg Heat exchanger for exhaust gas cooling; method for operating a heat exchanger; system with a heat exchanger for exhaust gas cooling
KR100897269B1 (ko) * 2007-12-14 2009-05-14 현대자동차주식회사 자동차의 배기 가스 재순환장치
JP2011214786A (ja) * 2010-03-31 2011-10-27 Yutaka Giken Co Ltd 熱交換器
JP2012241597A (ja) * 2011-05-18 2012-12-10 Toyota Motor Corp 排気冷却器
JP2015036542A (ja) * 2013-08-12 2015-02-23 現代自動車株式会社 Ｅｇｒガス及びエンジンオイル冷却装置とその制御方法

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