WO2019009080A1 - Refroidisseur intermédiaire - Google Patents

Refroidisseur intermédiaire Download PDF

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Publication number
WO2019009080A1
WO2019009080A1 PCT/JP2018/023552 JP2018023552W WO2019009080A1 WO 2019009080 A1 WO2019009080 A1 WO 2019009080A1 JP 2018023552 W JP2018023552 W JP 2018023552W WO 2019009080 A1 WO2019009080 A1 WO 2019009080A1
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WO
WIPO (PCT)
Prior art keywords
cooling water
cooling medium
low temperature
high temperature
flow passage
Prior art date
Application number
PCT/JP2018/023552
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English (en)
Japanese (ja)
Inventor
彰洋 大井
幸貴 西山
和貴 鈴木
Original Assignee
株式会社デンソー
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 株式会社デンソー filed Critical 株式会社デンソー
Priority to CN201880044606.1A priority Critical patent/CN110832178A/zh
Priority to DE112018003460.7T priority patent/DE112018003460B4/de
Publication of WO2019009080A1 publication Critical patent/WO2019009080A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0418—Layout of the intake air cooling or coolant circuit the intake air cooler having a bypass or multiple flow paths within the heat exchanger to vary the effective heat transfer surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0462—Liquid cooled heat exchangers
    • 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 disclosure relates to an intercooler that cools supercharged intake air pressurized by a supercharger.
  • an intercooler that cools supercharged intake air by heat exchange between supercharged air that is supercharged to an engine by a supercharger and two types of cooling water having different temperatures
  • a high temperature cooling water flow passage through which high temperature cooling water flows is disposed on the upstream side in the flow direction of the supercharging intake, and a low temperature in which low temperature cooling water flows to the downstream flow direction of the supercharging intake
  • a cooling water flow path is arranged.
  • fins for promoting heat exchange between the cooling water and the supercharged intake air are disposed in the high temperature cooling water flow passage and the low temperature cooling water flow passage.
  • the supercharged intake air can be pre-cooled by the high-temperature cooling water before being cooled by the low-temperature cooling water, the cooling performance of the supercharged intake air cooling system can be improved.
  • the present disclosure has an object of suppressing channel clogging due to foreign matter accumulation in an intercooler that cools supercharged intake air with two types of cooling media having different temperatures.
  • the intercooler cools the supercharged intake by performing heat exchange between the supercharged intake that is supercharged to the engine by the supercharger and the cooling medium.
  • the intercooler includes a heat exchange unit that exchanges heat between the cooling medium flowing inside the flow passage pipe and the supercharged intake air flowing outside the flow passage pipe.
  • the cooling medium includes a first cooling medium and a second cooling medium having a temperature higher than that of the first cooling medium.
  • a first cooling medium flow passage through which the first cooling medium flows so as to cross the flow direction of the supercharging intake, and a second cooling medium flowing so as to cross the flow direction of the supercharging intake.
  • a coolant flow path is formed.
  • the second coolant channel is disposed upstream of the first coolant channel in the flow direction of the supercharged intake air.
  • a fin is provided inside the first coolant channel, and no fin is provided inside the second coolant channel.
  • the heat transfer area is expanded, and the effect of promoting heat exchange between the first coolant and the supercharged intake can be obtained.
  • the second coolant channel where the fins are not disposed, the water flow resistance can be reduced, and the boiling point of the second coolant can be increased.
  • the second cooling medium flowing through the second cooling medium flow path is less likely to boil, and the generation of foreign matter resulting from the boiling of the second cooling medium can be suppressed.
  • the second cooling medium channel is wide. Therefore, even if foreign matter is generated in the second cooling medium, deposition of foreign matter in the flow path can be suppressed, and blockage of the flow path by foreign matter can be avoided as much as possible.
  • FIG. 1 is a block diagram illustrating an overview of a supercharged intake air cooling system of a vehicle according to at least one embodiment of the present disclosure.
  • FIG. 5 is a plan view of an intercooler in accordance with at least one embodiment of the present disclosure.
  • FIG. 1 is a perspective view of an intercooler in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a perspective view of a portion of an intercooler in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a perspective view of a fin in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure.
  • FIG. 5 is a schematic view illustrating the interior of a flow passage tube in accordance with at least one embodiment of the present disclosure. It is a perspective view which shows the fin of a modification.
  • a supercharger (not shown) for supercharging intake air to the engine 10 is provided in an intake system of an engine (internal combustion engine) 10 of the vehicle.
  • the supercharger is provided to compensate for the maximum output of the engine 10. That is, in the vehicle according to the present embodiment, the engine 10 is reduced in amount of exhaust gas for the purpose of improving fuel consumption, and the reduction of the maximum output due to the reduction of the amount of exhaust gas is compensated by the supercharger.
  • An intercooler 20 for cooling the engine intake air is provided downstream of the supercharger in the intake system in the intake flow direction.
  • the intercooler 20 cools the supercharged intake air compressed by the supercharger and plays a role in improving the charging efficiency of the engine intake air.
  • the intercooler 20 of the present embodiment is a two-temperature-type water-cooled intercooler that cools a supercharged intake air with two independent systems of cooling water having different temperatures.
  • the intercooler 20 is provided in the low temperature cooling water circuit 30 in which low temperature cooling water circulates, and the low temperature cooling water flows through the inside of the intercooler 20. Further, high temperature cooling water circulating through the high temperature cooling water circuit 40 also flows in the intercooler 20. Then, the intercooler 20 cools the supercharged intake air by heat exchanging the supercharged intake air compressed by the supercharger with the low temperature coolant and the high temperature coolant.
  • LLC antifreeze
  • water or the like can be used as the low temperature cooling water and the high temperature cooling water.
  • the low temperature cooling water circuit 30 is provided with a water pump 31 for circulating low temperature cooling water, and in the low temperature cooling water circuit 30, heat of the low temperature cooling water is dissipated between the water pump 31 and the intercooler 20 to release low temperature water
  • a first radiator (first radiator) 32 for cooling the cooling water is provided.
  • the high temperature coolant circuit 40 is provided with a water pump 41, a second radiator (second radiator) 42, and a heater core (heating heat exchanger) 43.
  • the water pump 41 circulates the high temperature coolant in the high temperature coolant circuit 40.
  • the second radiator 42 radiates the heat absorbed by the high temperature coolant from the engine 10 to the outside air.
  • the heater core 43 heats the blown air by heat exchange between the blown air blown into the vehicle compartment and the high temperature cooling water.
  • the intercooler 20, the second radiator 42 and the heater core 43 are arranged in parallel in the high temperature coolant circuit 40.
  • the low temperature cooling water of the present embodiment corresponds to the first cooling medium of the present disclosure
  • the high temperature cooling water of the present embodiment corresponds to the second cooling medium of the present disclosure.
  • the intercooler 20 of the first embodiment will be described in detail.
  • the intercooler 20 is provided with the duct 21, the flange 22, the tank 23, the cooling water pipe 24, and the heat exchange part 200, and is comprised.
  • the heat exchange unit 200 is provided inside the duct 21 and exchanges heat between the supercharged intake air and the cooling water.
  • the duct 21 is a tubular part through which the supercharged intake flows, and is provided with an inlet through which the supercharged intake flows and an outlet through which the supercharged intake flows.
  • Flanges 22 are respectively provided at the inlet and outlet of the duct 21.
  • a tank 23 is fixed to the inlet and the outlet of the duct 21 by a flange 22. Fixing of the flange 22 and the tank 23 can be performed, for example, by caulking.
  • the tank 23 is a cylindrical member through which supercharged intake flows.
  • the supercharged intake air flowing through the tank 23 connected to the inlet of the duct 21 flows into the inlet of the duct 21, and the supercharged intake air flowing out from the outlet of the duct 21 is connected to the outlet of the duct 21. Flow.
  • the duct 21 is provided with a cooling water pipe 24 to which a piping (not shown) through which the cooling water flows is connected.
  • the intercooler 20 is connected to the radiators 32, 42, the heater core 43, and the like through the piping.
  • the cooling water pipe 24 has a low temperature side inflow pipe 24 a for letting the low temperature cooling water flow into the heat exchange unit 200, a low temperature side outflow pipe 24 b for letting the low temperature cooling water flow out from the heat exchanging unit 200, and a high temperature cooling water flows into the heat exchanging unit 200. And a high temperature side outflow pipe 24 d for letting the high temperature cooling water flow out of the heat exchange unit 200.
  • the heat exchange unit 200 of the intercooler 20 of the present embodiment is configured as a so-called drone cup heat exchanger. As shown in FIG. 4, in the heat exchange unit 200, a plurality of flow passage pipes 201 and fins 202 joined between adjacent flow passage pipes 201 are alternately stacked and arranged.
  • the flow path pipe 201 is formed by joining a pair of opposing plate-like members 203 in time.
  • the flow passage pipe 201 has a flat cross-sectional shape.
  • all or part of the components are formed of a clad material in which a brazing material is clad on the surface of a core material made of, for example, aluminum.
  • a brazing material is clad on the surface of a core material made of, for example, aluminum.
  • Each component of the heat exchange unit 200 is brazed and joined by heating while the flux is applied to the surface of the clad material.
  • the heat exchange unit 200 is configured to exchange heat between the cooling water flowing inside the flow passage pipe 201 and the supercharged intake air flowing outside the flow passage pipe 201.
  • a space in which the fins 202 are disposed between the stacked flow path pipe 201 and the flow path pipe 201 constitutes a supercharged intake flow path through which the supercharged intake air flows.
  • the fin 202 is a corrugated fin formed by bending a thin plate material in a wave shape, and is joined to the flat outer surface side of the flow path pipe 201 to promote heat exchange for expanding the heat transfer area between the supercharged intake air and the cooling water. Make up the department.
  • a low temperature cooling water flow path 204 through which low temperature cooling water flows and a high temperature cooling water flow path 205 through which high temperature cooling water flows are formed.
  • the flow direction of the cooling water in the cooling water flow paths 204 and 205 is a direction intersecting the flow direction of the supercharging intake, specifically, a direction orthogonal to the flow direction of the supercharging intake.
  • the flow direction of the supercharged intake air in FIG. 5 is a direction from the lower side to the upper side.
  • the low temperature cooling water passage 204 corresponds to the first cooling medium passage of the present disclosure
  • the high temperature cooling water passage 205 corresponds to the second cooling medium passage of the present disclosure.
  • the low temperature cooling water flow passage 204 and the high temperature cooling water flow passage 205 are disposed in parallel in the flow passage pipe 201, and are disposed upstream and downstream in the flow direction of the supercharged intake air.
  • the high temperature cooling water flow passage 205 is disposed on the upstream side in the supercharging intake flow direction
  • the low temperature cooling water flow passage 204 is disposed on the downstream side in the supercharging intake flow direction. That is, in the present embodiment, the high temperature cooling water flows on the upstream side of the supercharging intake passage through which the supercharging intake passes, and the low temperature cooling water flows on the downstream side of the supercharging intake passage.
  • the flow path pipe 201 has a low temperature side inlet 204a for letting low temperature cooling water flow into the low temperature cooling water channel 204, a low temperature side outlet 204b for letting low temperature cooling water flow out from the low temperature cooling water channel 204, and a high temperature
  • a high temperature side inlet 205 a for introducing high temperature cooling water into the cooling water flow passage 205 and a high temperature side outlet 205 b for discharging high temperature cooling water from the high temperature cooling water flow passage 205 are provided.
  • the low temperature side inlet 204 a, the low temperature side outlet 204 b, the high temperature side inlet 205 a, and the high temperature side outlet 205 b are formed by forming through holes in the flow channel 201.
  • the low temperature cooling water flow passage 204 is provided with a low temperature side partition portion 204c that divides the flow passage, and a low temperature side U-turn portion 204d that makes low temperature cooling water U-turn.
  • the low temperature cooling water flow passage 204 is a first low temperature side flow passage portion 204e located upstream of the low temperature side U-turn portion 204d by the low temperature side partition portion 204c, and a second located downstream of the low temperature side U-turn portion 204d. It is divided into the low temperature side flow passage portion 204f.
  • the low temperature side U-turn portion 204d corresponds to the first U-turn portion of the present disclosure.
  • the low temperature cooling water flowing through the low temperature cooling water flow path 204 changes the flow direction at the low temperature side U-turn portion 204d. For this reason, the flow direction of the low temperature cooling water is opposite in the first low temperature side flow passage portion 204e and the second low temperature side flow passage portion 204f.
  • the first low temperature side flow passage portion 204e and the second low temperature side flow passage portion 204f are portions where the flow direction of the low temperature cooling water and the flow direction of the supercharged intake intersect.
  • the flow direction of the low temperature cooling water and the flow direction of the supercharging intake are orthogonal to each other.
  • the high temperature cooling water flow passage 205 is provided with a high temperature side partition portion 205c for dividing the flow passage, and a high temperature side U-turn portion 205d for making a high temperature cooling water U-turn.
  • the high temperature cooling water flow passage 205 is formed by the high temperature side partition portion 205c, the first high temperature side flow passage portion 205e located upstream of the high temperature side U-turn portion 205c, and the second high temperature side U-turn portion 205c located downstream It is divided into the high temperature side flow passage portion 205f.
  • the high temperature side U-turn portion 205d corresponds to the second U-turn portion of the present disclosure.
  • the high temperature cooling water flowing through the high temperature cooling water flow path 205 changes the flow direction at the high temperature side U-turn portion 205d. For this reason, in the high temperature coolant channel 205, the flow direction of the high temperature coolant is opposite in the first high temperature channel portion 205e and the second high temperature channel portion 205f.
  • the first high temperature side flow passage portion 205e and the second high temperature side flow passage portion 205f are portions where the flow direction of the high temperature cooling water and the flow direction of the supercharging intake intersect.
  • the flow direction of the high-temperature cooling water and the flow direction of the supercharging intake are orthogonal to each other.
  • the low temperature side inlet 204a, the low temperature side outlet 204b, the high temperature side inlet 205a, and the high temperature outlet 205b have one end in the longitudinal direction of the flow channel 201 (that is, the left end in FIG. 5).
  • Are located in These are disposed in the order of the high temperature side outlet portion 205b, the high temperature side inlet portion 205a, the low temperature side outlet portion 204b, and the low temperature side inlet portion 204a from the upstream side in the flow direction of the supercharged intake air.
  • the low temperature side U-turn portion 204 d and the high temperature side U-turn portion 205 d are disposed at the other end in the longitudinal direction of the flow path pipe 201 (that is, the right end in FIG. 5).
  • the length D HT in the supercharging intake flow direction in the portion where the high temperature cooling water flow passage 205 is formed in the flow passage pipe 201 is such that the low temperature cooling water flow passage 204 is formed in the flow passage pipe 201 It is shorter than the length D LT turbocharged flow direction at a site are.
  • the length D LT turbocharged flowing direction of the low temperature cooling water passage 204, the first low-temperature side flow passage portion 204e, turbocharged second low temperature side passage portion 204f and the low-temperature side partition part 204c It is almost equal to the sum of the lengths in the flow direction.
  • the length D HT of the high-temperature cooling water flow passage 205 in the supercharging intake flow direction is the supercharging intake air of the first high-temperature flow passage 205e, the second high-temperature flow passage 205f, and the high-temperature partition 205c. It is almost equal to the sum of the lengths in the flow direction.
  • a pillar portion 206 is provided on the low temperature side U-turn portion 204 d of the low temperature cooling water flow passage 204 and the high temperature side U turn portion 205 d of the high temperature cooling water flow passage 205.
  • the support portion 206 is formed in each of the pair of plate-like members 203 constituting the flow path pipe 201 so as to protrude into the flow path.
  • the pillars 206 formed at corresponding positions of the pair of plate-like members 203 are joined together.
  • the pair of plate members 203 are joined to each other in a state where a predetermined distance is maintained by the support portion 206. That is, the opposing inner surfaces of the flow path pipe 201 are joined by the support portion 206.
  • the bracing property of the pair of plate-like members 203 constituting the flow path pipe 201 can be improved by the support portion 206, and the strength of the flow path pipe 201 can be further improved.
  • fins 207 for dividing the low temperature cooling water channel 204 into a plurality of narrow channels are disposed inside the low temperature cooling water channel 204.
  • the fins 207 provided in the low temperature cooling water flow path 204 constitute a heat exchange promoting portion for expanding the heat transfer area between the low temperature cooling water and the supercharged intake air.
  • the fins 207 are respectively disposed in the first low temperature side flow passage portion 204 e and the second low temperature side flow passage portion 204 f of the low temperature cooling water flow passage 204.
  • the fins 207 of this embodiment are configured as straight fins.
  • the fin 207 of the straight fin structure has a corrugated shape in which the wall portion 207a and the top portion 207b are continuous, and a corrugated cross-sectional shape is formed in the continuous direction of the wave.
  • the plurality of wall portions 207a and the plurality of top portions 207b are respectively provided in parallel.
  • the plurality of wall portions 207a and the plurality of top portions 207b extend linearly along the flow direction of the low-temperature coolant, respectively.
  • the high temperature coolant channel 205 is not divided into a plurality of narrow channels by the fins.
  • the inner surface of the channel is formed flat in the first high temperature side channel portion 205e and the second high temperature side channel portion 205f. That is, in the high temperature cooling water flow channel 205, no protrusion, unevenness or the like is formed on the inner surface of the portion excluding the high temperature side U-turn portion 205d.
  • the fins 207 are provided inside the low temperature cooling water flow passage 204 to There is no fin inside. For this reason, in the low temperature cooling water flow path 204 in which the fin 207 is arrange
  • the water flow resistance can be reduced, and the boiling point of the high temperature cooling water can be raised.
  • the high temperature cooling water flowing through the high temperature cooling water flow path 205 is less likely to boil, and generation of foreign matter resulting from the boiling of the high temperature cooling water can be suppressed.
  • the fins are not provided in the high temperature coolant channel 205, the channel of the high temperature coolant is wider than in the case where the fins are provided. For this reason, even if foreign matter is generated in the high-temperature cooling water, deposition of foreign matter in the high-temperature cooling water passage 205 can be suppressed, and clogging of the passage by foreign matter can be avoided as much as possible.
  • the inner surfaces of the high temperature side flow passage portions 205 e and 205 f of the high temperature cooling water flow passage 205 are flat. For this reason, even if foreign matter is generated in the high-temperature cooling water, deposition of foreign matter in the flow path can be suppressed, and blockage of the flow path by foreign matter can be avoided as much as possible.
  • the length D HT of the high-temperature cooling water flow channel 205 in the supercharging intake flow direction is shorter than the length D LT of the low-temperature cooling water flow channel 204 in the supercharging intake flow direction.
  • the flow channel cross-sectional area of the cooling water flow channel 205 is smaller than the flow channel cross-sectional area of the low temperature cooling water flow channel 204. For this reason, the flow velocity of the cooling water is higher in the high temperature cooling water channel 205 than in the low temperature cooling water channel 204, and the water side heat transfer coefficient with respect to the water side heat transfer area in heat exchange between supercharged intake air and high temperature cooling water. It can be improved. As a result, in the high-temperature cooling water flow passage 205, it is possible to suppress a decrease in heat exchange performance due to the absence of the fins.
  • the bracing property can be improved by forming the support portion 206 in the low temperature cooling water flow channel 204 and the high temperature cooling water flow channel 205, and the strength of the flow channel 201 can be improved.
  • the U-turn portions 204d and 205d form a relatively large space by the cooling water flow paths 204 and 205, and when thermal stress is generated in the flow path pipe 201, the amount of deformation tends to be large.
  • the strength of the U-turn portions 204d and 205d can be secured.
  • the low temperature side partition portion 204 c and the low temperature side U-turn portion 204 d are not provided in the low temperature cooling water flow passage 204.
  • the low temperature side inlet portion 204 a and the low temperature side outlet portion 204 b are disposed at different end portions in the longitudinal direction of the flow passage pipe 201.
  • the low temperature side inlet portion 204 a is disposed at one end in the longitudinal direction of the flow channel tube 201 (that is, the left end portion in FIG. 7), and the low temperature side outlet portion 204 b is in the longitudinal direction of the flow channel tube 201. It is located at the other end (ie, the right end of FIG. 7).
  • low temperature cooling water flow path 204 of the second embodiment low temperature cooling water flows in one direction.
  • low temperature cooling water flows from the left side to the right side in the drawing.
  • the high temperature cooling water flow path 205 has the same configuration as that of the first embodiment, and is provided with a high temperature side partition portion 205c and a high temperature side U-turn portion 205d. For this reason, in the high temperature coolant channel 205, the high temperature coolant U-turns and flows.
  • the low temperature cooling water flows in one direction in the low temperature cooling water flow passage 204, and the high temperature cooling water flows in a U-turn and flows in the high temperature cooling water flow passage 202. Even in such a configuration, the same effect as that of the first embodiment can be obtained.
  • the third embodiment is different from the first embodiment in the configuration of the high-temperature cooling water passage 205.
  • the high temperature cooling water flow passage 205 is not provided with the high temperature side partition portion 205 c and the high temperature side U-turn portion 205 d. Further, in the high temperature cooling water flow passage 205, the high temperature side inlet portion 205 a and the high temperature side outlet portion 205 b are disposed at different end portions in the longitudinal direction of the flow passage pipe 201.
  • the high temperature side inlet portion 205 a is disposed at one end in the longitudinal direction of the flow channel tube 201 (that is, the left end in FIG. 8), and the high temperature side outlet portion 205 b is in the longitudinal direction of the flow channel tube 201. It is disposed at the other end (that is, the right end of FIG. 8).
  • the high temperature cooling water flow path 205 of the third embodiment the high temperature cooling water flows in one direction.
  • the high temperature coolant flows from the left side to the right side in the figure.
  • the low temperature cooling water passage 204 has the same configuration as that of the first embodiment, and is provided with a low temperature side partition portion 204c and a low temperature side U-turn portion 204d. For this reason, in the low temperature cooling water flow path 204, low temperature cooling water U-turns and flows.
  • the high temperature cooling water since the high temperature cooling water is configured to flow in one direction in the high temperature cooling water flow path 202, the high temperature cooling water as in the first and second embodiments described above performs a U-turn.
  • the flow passage cross-sectional area of the high-temperature cooling water can be increased as compared with the configuration in which the high temperature cooling water flows. For this reason, even if foreign matter is generated in the high-temperature cooling water, deposition of foreign matter in the flow path can be suppressed, and blockage of the flow path by foreign matter can be avoided as much as possible.
  • the fourth embodiment is different from the first embodiment in the configurations of the low temperature cooling water passage 204 and the high temperature cooling water passage 205.
  • two low temperature side partition parts 204c and 204g and two low temperature side U-turn parts 204d and 204h are provided in the low temperature cooling water flow path 204.
  • the low temperature cooling water passage 204 is divided into three passages 204e, 204f and 204i by two low temperature side partition parts 204c and 204g.
  • the low temperature cooling water flow passage 204 is downstream of the first low temperature side flow passage portion 204e located upstream of the first low temperature side U-turn portion 204d by the first low temperature side partition portion 204c and the first low temperature side U-turn portion 204d It is divided into the 2nd low temperature side channel part 204f located in the side. Further, the low temperature cooling water flow passage 204 is a second low temperature side flow passage portion 204f located upstream of the second low temperature side U-turn portion 204h by the second low temperature side partition portion 204g, and a second low temperature side U-turn portion 204h It is divided by the 3rd low temperature side channel part 204i located more downstream.
  • the low temperature cooling water flowing through the low temperature cooling water flow path 204 changes the flow direction twice in the two low temperature side U-turn portions 204d and 204h. For this reason, in the low temperature cooling water flow passage 204, the flow direction of the low temperature cooling water is opposite in the first low temperature passage portion 204e and the second low temperature passage portion 204f, and the second low temperature passage portion 204f The flow direction of the low temperature cooling water is opposite in the third low temperature side flow passage portion 204i.
  • the low temperature side inlet portion 204 a and the low temperature side outlet portion 204 b are disposed at different end portions in the longitudinal direction of the flow passage pipe 201.
  • the low temperature side inlet portion 204 a is disposed at one end in the longitudinal direction of the flow channel tube 201 (that is, the left end portion in FIG. 9), and the low temperature side outlet portion 204 b is in the longitudinal direction of the flow channel tube 201. It is disposed at the other end (that is, the right end in FIG. 9).
  • the high temperature cooling water passage 205 has the same configuration as that of the third embodiment, and the high temperature side partition portion 205c and the high temperature U-turn portion 205d are not provided. For this reason, in the high temperature coolant channel 205, the high temperature coolant flows in one direction.
  • the low temperature coolant flows U-turn twice and flows in the low temperature coolant channel 204, and the high temperature coolant flows in one direction in the high temperature coolant channel 202. Even in such a configuration, the same effects as those of the first and third embodiments can be obtained.
  • the fifth embodiment is different from the first embodiment in the configurations of the low temperature cooling water passage 204 and the high temperature cooling water passage 205.
  • three low temperature side partition parts 204c, 204g, 204j and three low temperature side U-turn parts 204d, 204h, 204k are provided in the low temperature cooling water channel 204.
  • the low temperature cooling water passage 204 is divided into four passages 204e, 204f, 204i and 204l by three low temperature side partition parts 204c, 204g and 204j.
  • the low temperature cooling water flow passage 204 is downstream of the first low temperature side flow passage portion 204e located upstream of the first low temperature side U-turn portion 204d by the first low temperature side partition portion 204c and the first low temperature side U-turn portion 204d It is divided into the 2nd low temperature side channel part 204f located in the side. Further, the low temperature cooling water flow passage 204 is a second low temperature side flow passage portion 204f located upstream of the second low temperature side U-turn portion 204h by the second low temperature side partition portion 204g, and a second low temperature side U-turn portion 204h It is divided by the 3rd low temperature side channel part 204i located more downstream.
  • the low temperature cooling water flow passage 204 is formed by the third low temperature side U-turn portion 204k located upstream of the third low temperature side U-turn portion 204k by the third low temperature side partition portion 204j, and the third low temperature side U-turn portion 204k. It is divided by the 4th low temperature side channel part 204l located more downstream.
  • the low temperature cooling water flowing through the low temperature cooling water flow path 204 changes the flow direction three times in the three low temperature side U-turn portions 204d, 204h and 204k. For this reason, in the low temperature cooling water flow passage 204, the flow direction of the low temperature cooling water is opposite in the first low temperature passage portion 204e and the second low temperature passage portion 204f, and the second low temperature passage portion 204f The flow direction of the low temperature cooling water is opposite in the third low temperature side flow passage portion 204i, and the flow direction of the low temperature cooling water is opposite in the third low temperature side flow passage portion 204i and the fourth low temperature side flow passage portion 204l. It is in the direction.
  • the low temperature side inlet 204a and the low temperature side outlet 204b are disposed at one end in the longitudinal direction of the flow channel 201 (that is, the left end in FIG. 10).
  • the high temperature cooling water passage 205 has the same configuration as that of the third embodiment, and the high temperature side partition portion 205c and the high temperature U-turn portion 205d are not provided. For this reason, in the high temperature coolant channel 205, the high temperature coolant flows in one direction.
  • the low temperature coolant flows U-turn three times in the low temperature coolant channel 204, and the high temperature coolant flows in one direction in the high temperature coolant channel 202. Even in such a configuration, the same effects as those of the first and third embodiments can be obtained.
  • the sixth embodiment is different from the first embodiment in the configurations of the low temperature cooling water passage 204 and the high temperature cooling water passage 205.
  • the low temperature cooling water flow passage 204 has the same configuration as that of the second embodiment, and the low temperature cooling water flow passage 204 has a low temperature side partition portion 204c and a low temperature side U-turn. The portion 204d is not provided. For this reason, in the low temperature cooling water flow passage 204 of the sixth embodiment, low temperature cooling water flows in one direction.
  • the high temperature cooling water flow passage 205 has the same configuration as that of the third embodiment, and the high temperature cooling water flow passage 205 is not provided with the high temperature side partition portion 205c and the high temperature side U-turn portion 205d. For this reason, in the high temperature coolant channel 205 of the sixth embodiment, the high temperature coolant flows in one direction.
  • the low temperature cooling water flows in one direction in the low temperature cooling water passage 204, and the high temperature cooling water flows in one direction in the high temperature cooling water passage 202. Even in such a configuration, the same effects as those of the first and third embodiments can be obtained.
  • the seventh embodiment is different from the first embodiment in the configuration of the high-temperature coolant channel 205.
  • the low temperature cooling water flow passage 204 and the high temperature cooling water flow passage 205 both make U-turn flow of cooling water.
  • the post portion 206 is not provided in the high temperature side U-turn portion d of the high temperature coolant channel 205.
  • the high temperature cooling water flow passage 205 is formed such that the inner surface of the high temperature side U-turn portion 205d is flat. That is, in the high temperature coolant channel 205 according to the seventh embodiment, the inner surface is formed flat over the entire channel.
  • the high temperature coolant channel 205 is formed such that the inner surface of the entire channel is flat. Even in such a configuration, the same effect as that of the first embodiment can be obtained.
  • the inner surface of the high temperature side U-turn portion 205d is formed flat in addition to the high temperature side flow passage portions 205e and 205f. Therefore, even if foreign matter is generated in the high-temperature cooling water, deposition of foreign matter in the flow path can be suppressed also in the high temperature side U-turn portion 205d, and blockage of the flow path by foreign matter can be avoided as much as possible. Become.
  • an eighth embodiment of the present disclosure will be described based on FIG. In the eighth embodiment, only parts different from the above embodiments will be described.
  • the eighth embodiment is different from the first embodiment in the configuration of the high-temperature cooling water passage 205.
  • the projection 205 g is formed to project toward the channel side.
  • the protrusion 205 g is indicated by a black circle.
  • the protrusions 205g are formed on the inner surfaces of the first high temperature side flow passage portion 205e, the second high temperature side flow passage portion 205f, and the high temperature side U-turn portion 205d. That is, in the high temperature coolant channel 205 according to the eighth embodiment, the projections 205g are formed on the inner surface over the entire channel.
  • the protrusion 205 g constitutes a turbulent flow generation unit that generates turbulent flow in the high temperature cooling water flowing through the high temperature cooling water flow channel 205.
  • the projecting portion 205g is provided over the entire high-temperature coolant passage 205. Even in such a configuration, the same effect as that of the first embodiment can be obtained.
  • the heat transfer efficiency between the high temperature cooling water and the supercharged intake air can be improved by providing the protrusion 205 g in the high temperature cooling water flow path 205. For this reason, in the high temperature cooling water flow path 205, it is possible to suppress a decrease in heat exchange performance due to the absence of the fins.
  • the ninth embodiment Next, a ninth embodiment of the present disclosure will be described based on FIG. In the ninth embodiment, only portions different from the above-described embodiments will be described.
  • the ninth embodiment is different from the first embodiment in the configuration of the high-temperature cooling water passage 205.
  • protrusions are formed on the high temperature side flow passage portions 205e and 205f, which are portions where the flow direction of high temperature cooling water and the flow direction of supercharging intake intersect.
  • a portion 205g is formed.
  • a support column portion 206 is provided on the high temperature side U-turn portion 205d.
  • the projections 205g are provided in the high temperature side channel portions 205e and 205f, and the support column 206 is provided in the high temperature U-turn portion 205d. Even in such a configuration, the same effect as that of the first embodiment can be obtained.
  • the projections 205g are provided on the high temperature side flow path portions 205e and 205f, so that the heat transfer efficiency between the high temperature cooling water and the supercharged intake can be improved, and the support portion is formed on the high temperature side U-turn portion 205d.
  • the strength of the high temperature side U-turn portion 205d can be secured.
  • the tank 23 through which the supercharged intake flows is connected to the duct 21 of the intercooler 20, and the heat exchange unit 200 is provided inside the duct 21 (see FIGS. 2 and 3).
  • the intercooler 20 may be configured differently.
  • the intercooler 20 may be inserted into the intake manifold.
  • the duct 21 constituting the flow path of the supercharged intake is unnecessary, and a plate for fixing to the wall surface of the intake manifold may be provided in the intercooler, and the heat exchange unit 200 may be fixed to this plate.
  • the heat exchange portion 200 of the intercooler 20 has a laminated structure (see FIG. 4) in which the fins 202 joined between the flow path pipe 201 and the flow path pipe 201 adjacent to each other are alternately laminated.
  • the present invention is not limited to this, and may be configured differently.
  • the heat exchange unit 200 of the intercooler 20 may be a core plate type in which the end of the tube is inserted into the pair of core plates.
  • the supercharged intake may pass through the inside of the tube and the cooling water may pass through the outside of the tube, and the coolant may pass through the inside of the tube and the supercharged intake may pass through the outside of the tube You may
  • the support portion 206 is provided only in the U-turn portion 205d of the high temperature cooling water flow channel 205.
  • the present invention is not limited to this.
  • the high temperature side flow channel portions 205e and 205f of the high temperature cooling water flow channel 205 A post 206 may be provided.
  • the fins 207 arranged in the low temperature cooling water flow path 204 are configured as straight fins (see FIG. 6).
  • the present invention is not limited to this.
  • the fins 207 may have different shapes.
  • the fins 207 may be configured as offset fins.
  • the fin 207 configured as an offset fin has a cross-sectional corrugated shape in which the wall portion 207a and the top portion 207b are continuous, and the wall portion 207a is provided with a large number of cut and raised portions 207c which are partially cut and raised. .
  • the wall portion 207a and the cut and raised portion 207c are alternately arranged in a staggered manner along the flow direction of the low temperature cooling water.
  • the fins 207 may be configured as wave fins not shown.
  • the wave fin has a cross-sectional wave shape in which the wall portion 207a and the top portion 207b are continuous, and the wall portion 207a and the top portion 207b are formed to meander along the flow direction of the low temperature cooling water.
  • the configuration in which the fins are not provided at all in the high temperature coolant channel 205 has been described, but the presence of relatively small fins in the high temperature coolant channel 205 is not excluded. That is, fins may be provided in the high-temperature cooling water passage 205 as long as the passage obstruction by the foreign matter in the high-temperature cooling water can be suppressed.

Landscapes

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

Abstract

L'invention concerne un refroidisseur intermédiaire qui échange de la chaleur entre l'air d'admission suralimenté et suralimenté par un compresseur de suralimentation dans un moteur (10) et un milieu de refroidissement pour refroidir l'air d'admission suralimenté. Le refroidisseur intermédiaire est pourvu d'une section d'échange de chaleur (200) destinée à échanger de la chaleur entre un milieu de refroidissement s'écoulant à l'intérieur d'un tuyau de passage d'écoulement (201) et de l'air d'admission suralimenté s'écoulant à l'extérieur du tuyau de passage d'écoulement. Le milieu de refroidissement comprend un premier milieu de refroidissement et un second milieu de refroidissement ayant une température supérieure à celle du premier milieu de refroidissement. Le tuyau de passage d'écoulement comporte, formé en son sein : un premier passage d'écoulement de milieu de refroidissement (204) à travers lequel le premier milieu de refroidissement s'écoule dans une direction croisant la direction d'écoulement de l'air d'admission suralimenté ; et un second passage d'écoulement de milieu de refroidissement (205) à travers lequel le second milieu de refroidissement s'écoule dans une direction croisant la direction d'écoulement de l'air d'admission suralimenté. Le second passage d'écoulement de milieu de refroidissement est disposé en amont du premier passage d'écoulement de milieu de refroidissement dans la direction d'écoulement d'air d'admission suralimenté. Des ailettes (207) sont disposées à l'intérieur du premier passage d'écoulement de milieu de refroidissement, et aucune ailette n'est disposée à l'intérieur du second passage d'écoulement de milieu de refroidissement.
PCT/JP2018/023552 2017-07-05 2018-06-21 Refroidisseur intermédiaire WO2019009080A1 (fr)

Priority Applications (2)

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CN201880044606.1A CN110832178A (zh) 2017-07-05 2018-06-21 中间冷却器
DE112018003460.7T DE112018003460B4 (de) 2017-07-05 2018-06-21 Ladeluftkühler

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JP2017131679A JP6708172B2 (ja) 2017-07-05 2017-07-05 インタークーラ
JP2017-131679 2017-07-05

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CN (1) CN110832178A (fr)
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CN110410195A (zh) * 2019-08-14 2019-11-05 广西玉柴机器股份有限公司 中冷器
GB2596327A (en) * 2020-06-25 2021-12-29 Denso Marston Ltd Heat exchanger

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WO2021145210A1 (fr) * 2020-01-17 2021-07-22 株式会社デンソー Échangeur de chaleur
KR20230133195A (ko) * 2022-03-10 2023-09-19 얀마 홀딩스 주식회사 엔진

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JP2001041678A (ja) * 1999-01-28 2001-02-16 Denso Corp 熱交換器
WO2013162822A1 (fr) * 2012-04-28 2013-10-31 Modine Manufacturing Company Échangeur thermique à bloc refroidisseur et procédé de production
JP2015155692A (ja) * 2014-01-14 2015-08-27 株式会社デンソー インタークーラ

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JP2013256936A (ja) * 2012-05-16 2013-12-26 Denso Corp 排気還流装置
CN104061059A (zh) * 2014-06-20 2014-09-24 南宁八菱科技股份有限公司 套管式水冷中冷器
CN204060908U (zh) * 2014-08-27 2014-12-31 沈阳华铁异型材有限公司 内燃机中冷器冷却管结构

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JPS60189770U (ja) * 1984-05-23 1985-12-16 カルソニックカンセイ株式会社 インタ−ク−ラ
JP2001041678A (ja) * 1999-01-28 2001-02-16 Denso Corp 熱交換器
WO2013162822A1 (fr) * 2012-04-28 2013-10-31 Modine Manufacturing Company Échangeur thermique à bloc refroidisseur et procédé de production
JP2015155692A (ja) * 2014-01-14 2015-08-27 株式会社デンソー インタークーラ

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110410195A (zh) * 2019-08-14 2019-11-05 广西玉柴机器股份有限公司 中冷器
GB2596327A (en) * 2020-06-25 2021-12-29 Denso Marston Ltd Heat exchanger
GB2596327B (en) * 2020-06-25 2024-03-20 Denso Marston Ltd Heat exchanger

Also Published As

Publication number Publication date
JP6708172B2 (ja) 2020-06-10
DE112018003460B4 (de) 2022-03-10
JP2019015200A (ja) 2019-01-31
CN110832178A (zh) 2020-02-21
DE112018003460T5 (de) 2020-03-19

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