WO2020110524A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2020110524A1
WO2020110524A1 PCT/JP2019/041518 JP2019041518W WO2020110524A1 WO 2020110524 A1 WO2020110524 A1 WO 2020110524A1 JP 2019041518 W JP2019041518 W JP 2019041518W WO 2020110524 A1 WO2020110524 A1 WO 2020110524A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
exchange tube
heat
exhaust gas
temperature
Prior art date
Application number
PCT/JP2019/041518
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English (en)
Japanese (ja)
Inventor
友哉 中村
慧悟 米村
勇人 後藤
堯郎 丸山
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.)
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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 WO2020110524A1 publication Critical patent/WO2020110524A1/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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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

Definitions

  • the present invention relates to a heat exchanger that exchanges heat between two types of heat medium.
  • the exhaust gas emitted from the engine is cooled by cooling water and recirculated to the engine.
  • the 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 As a conventional technique related to the heat exchanger, there is a technique disclosed in Patent Document 1.
  • Patent Document 1 discloses an EGR cooler as a heat exchanger.
  • a plurality of heat exchange tubes are surrounded by a core case, and exhaust gas (first heat medium) flowing inside the heat exchange tubes and cooling water flowing around the outer circumference of the heat exchange tubes inside the core case. Heat exchange is performed by the (second heat medium).
  • the EGR cooler further includes a valve that opens and closes a part of the 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 that is inexpensive and small, and that can stabilize the temperature of the discharged first heat medium.
  • the heat exchange tube is surrounded by the core case, and the first heat medium flown inside the heat exchange tube is flown inside the core case at the outer circumference of the heat exchange tube.
  • the heat exchange tube includes a first heat exchange tube and a second heat exchange tube of different types, and a heat quantity of heat exchange performed in the first heat exchange tube is performed in the second heat exchange tube.
  • a heat exchanger is provided, which is characterized in that it is set to have a larger amount of heat of heat exchange.
  • the heat exchange tube includes a first heat exchange tube and a second heat exchange tube of different types, and the heat quantity of heat exchange performed in the first heat exchange tube is the same as that in the second heat exchange tube. Greater than the amount of heat exchanged. In the region where the flow rate of the first heat medium is low, the first heat exchange tube performs heat exchange with an excessive amount of heat with respect to the appropriate temperature.
  • the second heat exchange tube has a smaller amount of heat for heat exchange than the first heat exchange tube. Therefore, the temperature of the first heat medium discharged from the second heat exchange tube is closer to the temperature on the introduction side.
  • the first heat medium that has undergone heat exchange with an excessive amount of heat with respect to the appropriate temperature With the first heat medium that is closer to the temperature on the introduction side, the first heat medium that is discharged in the region where the flow rate is low
  • the temperature of is a suitable temperature.
  • the temperature of the first heat medium discharged from the first heat exchange tube is set to be an appropriate temperature.
  • the second heat exchange tube since the second heat exchange tube has a small amount of heat to cool, the first heat medium discharged from the second heat exchange tube has a high temperature in a region where the flow rate of the first heat medium is high.
  • the first heat medium in the second heat exchange tube becomes a resistance, and a larger amount of the first heat medium flows into the first heat exchange tube. Since the flow rate of the first heat medium flowing through the second heat exchange tube is small, the influence of the exhaust gas passing through the second heat exchange tube is relatively low. In the region where the flow rate is high, a small amount of the high temperature first heat medium that has passed through the second heat exchange tube is mixed with the first heat medium that has passed through the first heat exchange tube and has an appropriate temperature. Therefore, the temperature of the discharged first heat medium does not rise excessively, and is discharged to the outside of the heat exchanger with an appropriate temperature. No valve or external control is required to stabilize the temperature of the discharged first heat medium. It is possible to provide a heat exchanger that is inexpensive and small, and that can stabilize the temperature of the discharged first heat medium.
  • FIG. 3 is a diagram schematically showing an exhaust gas circulation path using the EGR cooler according to the first embodiment. It is a 2 arrow line view of FIG. FIG. 3 is a sectional view taken along line 3-3 of FIG. 2.
  • FIG. 3 is a front view of the EGR cooler shown in FIG. 2 with an exhaust gas introducing portion removed.
  • FIG. 5 is a diagram showing a relationship between a temperature and a flow rate of exhaust gas flowing through a first heat exchange tube and a second heat exchange tube shown in FIG. 4.
  • FIG. 5 is a diagram showing a relationship between a flow rate and a pressure of exhaust gas flowing through a first heat exchange tube and a second heat exchange tube shown in FIG. 4.
  • FIG. 7 is a front view of the EGR cooler according to the second embodiment with an exhaust gas introducing portion removed.
  • FIG. 9 is a front view of the EGR cooler according to the third embodiment with an exhaust gas introducing portion removed.
  • upstream refers to the upstream with respect to the flow direction of the exhaust gas (first heat medium).
  • Downstream refers to the downstream with reference to the flow direction of exhaust gas.
  • Fr is front (upstream)
  • Rr is rear (downstream)
  • Le is left
  • Ri right
  • Up Up
  • Dn down.
  • An EGR (Exhaust Gas Recirculation) cooler 20 (heat exchanger 20) is connected to, for example, an intake port 11 and an exhaust port 12 formed in a diesel engine 10 for a vehicle (hereinafter referred to as "engine 10"). Used.
  • a part of the exhaust gas (first heat medium) discharged from the exhaust port 12 is sent into the EGR cooler 20.
  • the exhaust gas sent is cooled by the cooling water (second heat medium) and is discharged from the EGR cooler 20.
  • the cooled exhaust gas is sent back into the engine 10 together with the air.
  • Generation of NOx (nitrogen oxide) can be suppressed by reducing the oxygen concentration of the air sent into the engine 10.
  • EGR cooler 20 is not limited to being mounted on a diesel engine, but can be applied to a gasoline engine. Furthermore, the invention is applicable to engines mounted on vehicles other than vehicles, and the applications are not limited to these.
  • the EGR cooler 20 includes an exhaust gas introducing member 21 (first heat medium introducing member 21) into which exhaust gas is introduced, an upstream end plate 22 connected to this exhaust gas introducing member 21, and this upstream end plate. 22 and a core case 30 having both ends open, a downstream end plate 24 attached to the downstream end of the core case 30, and an exhaust gas connected to the downstream end plate 24.
  • a discharge member 25 (first heat medium discharge member 25), a heat exchange tube 40 having an upstream end fixed to the upstream end plate 22 and a downstream end fixed to the downstream end plate 24,
  • a cooling water introducing pipe 27 (second heat medium introducing pipe 27) which is attached to a side surface of the core case 30 near the exhaust gas introducing member 21 and introduces cooling water, and the cooling water introduced from the cooling water introducing pipe 27 is discharged.
  • the cooling water discharge pipe 28 (second heat medium discharge pipe 28) attached to the side surface of the core case 30 is provided.
  • the exhaust gas introducing member 21 has an introducing member inlet 21a formed at the upstream end and an introducing member outlet 21b formed at the downstream end and connected to the upstream end plate 22.
  • the introduction member inlet 21a is offset downward with respect to the vertical center of the core case 30.
  • the exhaust gas introducing member 21 is provided with an introducing portion flange 21c for attaching to other parts.
  • the upstream end plate 22 has a rectangular plate-shaped upstream bottom 22a to which the heat exchange tube 40 is fixed, and an upstream side wall 22b extending from the end of the upstream bottom 22a toward the downstream side.
  • the upstream bottom 22a is provided with upstream insertion holes 22c and 22d for inserting the heat exchange tubes 40.
  • the core case 30 is joined to the end portion of the upstream side wall portion 22b.
  • the core case 30 is connected to the exhaust gas introducing member 21 via the upstream end plate 22 and is connected to the exhaust gas discharging member 25 via the downstream end plate 24.
  • the core case 30 is formed by stacking a substantially U-shaped left case half body 31 opening to the right and a substantially U-shaped right case half body 32 opening to the left. It becomes. The left case half 31 and the right case half 32 are joined together.
  • the left case half 31 has a left case bottom 31a extending in the vertical direction, and left case side walls 31b, 31b extending rightward from the upper and lower ends of the left case bottom 31a, respectively.
  • the tips of the left case side wall portions 31b and 31b respectively cover the tips of the right case half body 32.
  • the right case half 32 has a right case bottom 32a extending in the vertical direction, and right case side walls 32b, 32b extending leftward from the upper and lower ends of the right case bottom 32a, respectively.
  • the downstream end plate 24 has a rectangular plate-shaped downstream bottom 24a to which the heat exchange tube 40 is fixed, and a downstream side wall 24b extending from the end of the downstream bottom 24a toward the upstream side. Downstream insertion holes 24c and 24d for inserting the heat exchange tubes 40 are formed in the downstream bottom portion 24a.
  • the core case 30 is joined to the end portion of the downstream side wall portion 24b.
  • the exhaust gas exhaust member 25 has an exhaust member inlet 25a formed at the upstream end and connected to the downstream end plate 24, and an exhaust member outlet 25b formed at the downstream end.
  • the discharge member outlet 25b is offset downward with reference to the vertical center of the core case 30.
  • the exhaust gas exhaust member 25 is provided with an exhaust flange 25c for attaching to other parts.
  • the heat exchange tube 40 has a first heat exchange tube 41 having a flat shape that is long in the left-right direction and short in the up-down direction, and a second heat exchange tube 42 that has a cylindrical shape.
  • the first heat exchange tube 41 and the second heat exchange tube 42 are fixed to the same end plates 22 and 24, and are arranged in parallel.
  • the first heat exchange tubes 41 extend in the front-rear direction and are stacked in the vertical direction. These first heat exchange tubes 41 have the same configuration. More specifically, the first heat exchange tube 41 is formed by stacking two U-shaped tube bodies 41a and 41b with their openings facing each other.
  • the first heat exchange tube 41 contains a corrugated plate-shaped fin 41c.
  • the fin 41c is in contact with the tube bodies 41a and 41b.
  • the flow passage area of one first heat exchange tube 41 is larger than the flow passage area of the second heat exchange tube 42. Naturally, the total of the flow passage areas of the six first heat exchange tubes 41 is larger than the flow passage area of the second heat exchange tubes 42.
  • the tube bodies 41a and 41b may be formed of corrugated plates.
  • the second heat exchange tube 42 is arranged below the first heat exchange tube 41 and substantially at the center in the left-right direction.
  • the second heat exchange tube 42 is arranged at a position overlapping the introduction member inlet 21a when the exhaust gas introduction member 21 is viewed from the upstream side. In other words, the second heat exchange tube 42 faces the introduction member inlet 21a.
  • the second heat exchange tube 42 is arranged at a position overlapping the exhaust member outlet 25b when the exhaust gas exhaust member 25 is viewed from the downstream side. In other words, the second heat exchange tube 42 faces the discharge member outlet 25b.
  • the cooling water introduction pipe 27 and the cooling water discharge pipe 28 are both attached to the left case bottom portion 31a of the left case half body 31, and are attached to opposite end portions with respect to the exhaust gas flow direction. ing.
  • the exhaust gas discharged from the engine 10 is introduced into the core case 30 from the exhaust gas introduction member 21.
  • the introduced exhaust gas passes through the first heat exchange tube 41 and the second heat exchange tube 42.
  • the cooling water introduced from the cooling water introducing pipe 27 into the core case 30 flows on the outer periphery of each heat exchange tube 41, 42.
  • the exhaust gas passing through the heat exchange tubes 41, 42 is cooled by the cooling water flowing on the outer circumference.
  • the cooled exhaust gas is discharged from the exhaust gas discharge member 25 and returned to the engine 10.
  • the cooling water that has absorbed the heat of the exhaust gas is discharged from the cooling water discharge pipe 28 to the outside of the core case 30.
  • FIG. 5 shows the relationship between the flow rate of exhaust gas and the temperature of exhaust gas.
  • the horizontal axis represents the exhaust gas flow rate [g/s], and the vertical axis represents the exhaust gas temperature [°C].
  • Tmin shown on the vertical axis is the lower limit value of the temperature allowed as the temperature of the exhaust gas discharged from the EGR cooler 20.
  • Tmax shown on the vertical axis is the upper limit of the temperature allowed as the temperature of the exhaust gas discharged from the EGR cooler 20.
  • T 1 indicates the temperature of the exhaust gas that has passed through the first heat exchange tube 41.
  • T 2 indicates the temperature of the exhaust gas that has passed through the second heat exchange tube 42.
  • T 3 is the temperature of the exhaust gas in which the exhaust gas passing through the first heat exchange tube 41 and the exhaust gas passing through the second heat exchange tube 42 are mixed (hereinafter referred to as “mixed exhaust gas”). Shows.
  • 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 T 1 of the exhaust gas that has passed through the first heat exchange tube 41 is below the lower limit value Tmin of the allowable temperature in the region where the flow rate is low. It can be said that the exhaust gas passing through the first heat exchange tube 41 is excessively cooled in the region where the flow rate is low.
  • the temperature T 2 of the exhaust gas that has passed through the second heat exchange tube 42 is higher than the temperature T 1 of the exhaust gas that has passed through the first heat exchange tube 41 in all regions.
  • the temperature T 0 of the exhaust gas when introduced into the EGR cooler 20 is the same for both the exhaust gas passing through the first heat exchange tube 41 and the exhaust gas passing through the second heat exchange tube 42. Therefore, it can be said that the heat amount of heat exchange performed in the first heat exchange tube 41 is larger than the heat amount of heat exchange performed in the second heat exchange tube 42.
  • the temperature T 2 of the exhaust gas that has passed through the second heat exchange tube 42 is higher than Tmax, which is the upper limit of the allowable temperature, in all regions.
  • the temperature T 3 of the mixed exhaust gas is between the allowable temperature Tmin and Tmax in all regions. In the region where the flow rate is low, the exhaust gas that has passed through the first heat exchange tube 41 and the exhaust gas that has passed through the second heat exchange tube 42 are mixed, so that the temperature T 3 of the mixed exhaust gas is allowed. It is considered that the temperature has reached a temperature between Tmin and Tmax which is the temperature to be controlled. The reason why the temperature T 3 of the mixed exhaust gas does not exceed the allowable temperature Tmax in the region where the flow rate is high will be described later.
  • the difference between the lowest temperature and the highest temperature is ⁇ T 1 .
  • the difference between the lowest temperature and the highest temperature is ⁇ T 3 . Comparing ⁇ T 1 and ⁇ T 3 , ⁇ T 3 is smaller. That is, ⁇ T 1 > ⁇ T 3 , and it can be said that the temperature of the mixed exhaust gas is more stable than that of the exhaust gas that has passed through the first heat exchange tube 41.
  • the exhaust gas that has passed through the first heat exchange tube 41 and the exhaust gas that has passed through the second heat exchange tube 42 having a smaller amount of heat for heat exchange than the first heat exchange tube 41 are mixed.
  • the temperature T 3 of the mixed exhaust gas becomes between the allowable temperature Tmin and Tmax, and the temperature of the exhaust gas also stabilizes.
  • FIG. 6 shows the relationship between the pressure of the exhaust gas introduced into the EGR cooler and the flow rate of the exhaust gas that has passed through each heat exchange tube.
  • the horizontal axis represents the pressure [N/m 2 ] of the exhaust gas introduced into the EGR cooler, and the vertical axis represents the flow rate [g/s] of the exhaust gas that has passed through each heat exchange tube.
  • Q 1 indicates the flow rate of the exhaust gas that has passed through the first heat exchange tube 41.
  • Q 2 indicates the flow rate of the exhaust gas that has passed through the second heat exchange tube 42.
  • the flow rate of the exhaust gas flowing inside increases as the pressure of the exhaust gas rises. In all the regions, the flow rate of the exhaust gas passing through the first heat exchange tube 41 is higher than the flow rate of the exhaust gas passing through the second heat exchange tube 42.
  • ⁇ Q which is the difference between the flow rate of exhaust gas flowing through the first heat exchange tube 41 and the flow rate of exhaust gas flowing through the second heat exchange tube 42.
  • ⁇ Qmin the difference in the flow rate of the exhaust gas
  • ⁇ Qmax the difference in exhaust gas flow rate
  • the heat exchange tube 40 is surrounded by the core case 30, and the EGR cooler 20 that cools the exhaust gas flowing inside the heat exchange tube 40 by the cooling water that flows around the heat exchange tube 40 and inside the core case 30.
  • the heat exchange tube 40 includes a first heat exchange tube 41 and a second heat exchange tube 42 which are different in type, and the heat quantity of the heat exchange performed in the first heat exchange tube 41 is the second heat exchange tube 42. It is set to be larger than the heat quantity of the heat exchange performed in.
  • the first heat exchange tube 41 performs heat exchange with an excessive amount of heat with respect to the appropriate temperature.
  • the second heat exchange tube 42 has a smaller amount of heat for heat exchange than the first heat exchange tube 41. Therefore, the temperature T 2 of the exhaust gas discharged from the second heat exchange tube 42 is closer to the temperature T 0 on the introduction side.
  • Exhaust gas exhaust gas that has passed through the first heat exchange tube 41
  • exhaust gas that has undergone heat exchange with an excessive amount of heat relative to the appropriate temperature and exhaust gas that has a temperature closer to the introduction side (passes through the second heat exchange tube 42)
  • the exhaust gas is mixed, so that the temperature T 3 of the exhaust gas discharged becomes a proper temperature in the region where the flow rate is small.
  • the temperature of exhaust gas discharged from the first heat exchange tube 41 is set to be an appropriate temperature.
  • the second heat exchange tube 42 since the second heat exchange tube 42 has a small amount of heat for cooling, the exhaust gas discharged from the second heat exchange tube 42 has a high temperature in a region where the flow rate of the exhaust gas is high.
  • the exhaust gas in the second heat exchange tube 42 becomes a resistance, and a larger amount of exhaust gas flows into the first heat exchange tube 41. Since the flow rate of the exhaust gas flowing through the second heat exchange tube 42 is small, the influence of the exhaust gas passing through the second heat exchange tube 42 is relatively low.
  • the flow passage area of the first heat exchange tube 41 is larger than the flow passage area of the second heat exchange tube 42.
  • the amount of heat exchanged in the first heat exchange tube 41 can be further increased. In a region where the flow rate is high, the influence of the exhaust gas that has passed through the second heat exchange tube 42 can be reduced.
  • the first heat exchange tube 41 has a flat shape and has the fins 41c housed therein.
  • the second heat exchange tube 42 has a cylindrical shape.
  • the second heat exchange tube 42 By having a flat shape and housing the fins 41c inside, heat exchange in the first heat exchange tube 41 can be promoted.
  • the second heat exchange tube 42 through which the high-temperature first heat medium flows, is formed into a cylindrical shape, so that the portion to which the load is applied is dispersed and the protection performance can be improved.
  • the exhaust gas introducing member 21 for introducing the first heat medium into the heat exchange tube 40 is connected to the core case 30, With reference to the flow direction of the exhaust gas, the exhaust gas introduction member 21 has an introduction member inlet 21a through which the exhaust gas passes at an upstream end, The second heat exchange tube 42 faces the introduction member inlet 21a.
  • FIG. 7 shows an EGR cooler 20A (heat exchanger 20A) according to the second embodiment.
  • the number of the second heat exchange tubes 42 is changed from that of the EGR cooler 20 according to the first embodiment (see FIG. 4).
  • Other basic configurations are the same as those of the EGR cooler 20 according to the first embodiment.
  • the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.
  • the EGR cooler 20A according to the second embodiment has three second heat exchange tubes 42A. By varying the area where heat exchange takes place, the characteristics of the temperature T 3 of the mixed exhaust gas shown in FIG. 6 can be adjusted.
  • the EGR cooler 20A described above also exhibits the effects prescribed by the present invention. ⁇ Example 3>
  • FIG. 8 shows an EGR cooler 20B (heat exchanger 20B) according to the third embodiment.
  • the shape of the second heat exchange tube 42 is changed from that of the EGR cooler 20 according to the first embodiment (see FIG. 4).
  • Other basic configurations are the same as those of the EGR cooler 20 according to the first embodiment.
  • the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.
  • the EGR cooler 20B according to the third embodiment has a flat second heat exchange tube 42B. By varying the area where heat exchange takes place, the characteristics of the temperature T 3 of the mixed exhaust gas shown in FIG. 6 can be adjusted.
  • the EGR cooler 20B described above also exhibits the effects prescribed by the present invention.
  • the heat exchanger of the present invention is 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 the examples as long as the operations and effects are exhibited.
  • the heat exchanger of the present invention is suitable for an EGR cooler.
  • EGR cooler heat exchanger 21... Exhaust gas introducing member (first heat medium introducing member) 21a... Introducing member inlet 30... Core case 40... Heat exchange tube 41... First heat exchange tube 42... Second heat exchange tube

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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)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

L'invention concerne un échangeur de chaleur (20) doté d'un tube échangeur de chaleur (40), entouré par un boîtier de partie centrale (30), qui refroidit un premier fluide caloporteur s'écoulant à l'intérieur du tube d'échange de chaleur (40) par un second fluide caloporteur s'écoulant à l'intérieur du boîtier de partie centrale (30) sur la périphérie externe du tube échangeur de chaleur (40). Le tube échangeur de chaleur (40) comprend des premier et second tubes échangeurs de chaleur (41, 42) de différents types, et la quantité de chaleur échangée dans le premier tube échangeur de chaleur (41) est réglée pour être plus grande que la quantité de chaleur échangée dans le second tube échangeur de chaleur (42).
PCT/JP2019/041518 2018-11-28 2019-10-23 Échangeur de chaleur WO2020110524A1 (fr)

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Application Number Priority Date Filing Date Title
JP2018222709A JP6944432B2 (ja) 2018-11-28 2018-11-28 熱交換器
JP2018-222709 2018-11-28

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WO2020110524A1 true WO2020110524A1 (fr) 2020-06-04

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JP2021055856A (ja) * 2019-09-27 2021-04-08 株式会社ユタカ技研 熱交換器

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JP2002181467A (ja) * 2000-12-12 2002-06-26 Maruyasu Industries Co Ltd 多管式熱交換器
JP2004346920A (ja) * 2003-05-26 2004-12-09 Nissan Diesel Motor Co Ltd Ｅｇｒクーラー
JP2005180268A (ja) * 2003-12-18 2005-07-07 Isuzu Motors Ltd エンジンのｅｇｒクーラー
JP2009506287A (ja) * 2005-08-27 2009-02-12 ベール ゲーエムベーハー ウント コー カーゲー 排ガス熱交換器
JP2012127312A (ja) * 2010-12-17 2012-07-05 Hino Motors Ltd Ｅｇｒクーラ

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