JP2019015200A - Intercooler - Google Patents

Abstract

In an intercooler that cools supercharged intake air with two types of cooling media having different temperatures, flow path blockage due to foreign matter accumulation is suppressed. In an intercooler including a heat exchanging section (200) for exchanging heat between a cooling medium flowing inside a flow path pipe (201) and supercharged intake air flowing outside the flow path pipe (201), the cooling medium includes first cooling. A first cooling medium that includes a medium and a second cooling medium having a temperature higher than that of the first cooling medium, and the first cooling medium flows in the flow path pipe 201 so as to intersect the flow direction of the supercharged intake air. A medium flow path 204 and a second cooling medium flow path 205 through which the second cooling medium flows so as to intersect with the flow direction of the supercharged intake air are formed. The second cooling medium flow path 205 is the first cooling medium. It is arranged upstream of the flow path 204 in the flow direction of the supercharged intake air. A fin 207 is provided inside the first cooling medium flow path 204, and inside the second cooling medium flow path 205. Is not provided with fins. [Selection] Fig. 5

Description

  The present invention relates to an intercooler that cools supercharged intake air pressurized by a supercharger.

  2. Description of the Related Art Conventionally, an intercooler that cools supercharged intake air by exchanging heat between supercharged air that is supercharged to an engine by a supercharger and two types of cooling water having different temperatures is known (for example, a patent) Reference 1). In the intercooler described in Patent Document 1, a high-temperature cooling water passage through which high-temperature cooling water flows is arranged upstream in the flow direction of supercharged intake air, and low-temperature cooling water flows through downstream in the flow direction of supercharging intake air. A cooling water flow path is arranged. Further, fins for promoting heat exchange between the cooling water and the supercharged intake air are arranged in the high-temperature cooling water channel and the low-temperature cooling water channel.

  According to this, at the time of engine start, the low temperature cooling water can be warmed up early by the heat of the high temperature cooling water. Furthermore, since the supercharged intake air can be pre-cooled with the high-temperature cooling water before being cooled with the low-temperature cooling water, the cooling performance of the supercharged intake air cooling system can be improved.

JP2015-1555692A

  In the intercooler described in Patent Document 1, in the high-temperature cooling water flow path, the cooling water and the high-temperature supercharging intake air exchange heat, so that the temperature of the cooling water may rise to near the boiling point. In particular, in the case of a configuration in which the cooling water channel is narrowed, the water flow resistance increases, the water pressure near the cooling water channel outlet decreases, and the boiling point of the cooling water decreases. For this reason, there is a concern about boiling of the cooling water in the high-temperature cooling water flow path where the cooling water temperature is likely to rise.

  When the cooling water boils, foreign substances derived from components contained in the cooling water are generated, and the foreign substances may accumulate in the water flow path, leading to a problem that the flow path is blocked. Further, in the case of a configuration in which the cooling water flow path is narrowed, the flow path is likely to be blocked by foreign matter accumulation.

  In view of the above points, an object of the present invention is to suppress channel blockage due to foreign matter accumulation in an intercooler that cools supercharged intake air with two types of cooling media having different temperatures.

  In order to achieve the above object, in the first aspect of the present invention, the supercharged intake air is cooled by exchanging heat between the supercharged intake air supercharged to the engine (10) by the supercharger and the cooling medium. The heat exchanger (200) for exchanging heat between the cooling medium flowing inside the flow path pipe (201) and the supercharged intake air flowing outside the flow path pipe. A first cooling medium and a second cooling medium having a temperature higher than that of the first cooling medium are included, and the first cooling medium flows in the flow path pipe so as to intersect the flow direction of the supercharged intake air. A cooling medium flow path (204) and a second cooling medium flow path (205) through which the second cooling medium flows so as to intersect the flow direction of the supercharged intake air are formed. The first cooling medium flow path is disposed upstream of the supercharging intake air flow direction, and the first cooling medium flow path Inside the medium channel is provided fin (207) is, inside the second coolant flow, characterized in that the fin is not provided.

  Thereby, in the 1st cooling medium flow path in which the fin is arrange | positioned, a heat transfer area can be expanded and the effect which accelerates | stimulates the heat exchange of a 1st cooling medium and supercharging intake air can be acquired. On the other hand, in the second cooling medium flow path in which the fins are not arranged, the water flow resistance can be reduced and the boiling point of the second cooling medium can be increased. As a result, the second cooling medium flowing through the second cooling medium channel is less likely to boil, and the generation of foreign matter due to the boiling of the second cooling medium can be suppressed.

  In addition, since the fins are not provided in the second cooling medium flow path, the flow path of the second cooling medium is widened. For this reason, even if a foreign material is generated in the second cooling medium, it is possible to suppress the foreign material from accumulating in the flow channel, and it is possible to prevent the flow channel from being blocked by the foreign material as much as possible.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

It is a block diagram which shows the outline | summary of the supercharging intake air cooling system of the vehicle in 1st Embodiment. It is a top view of the intercooler in a 1st embodiment. It is a perspective view of the intercooler in a 1st embodiment. It is a perspective view which shows the principal part of the intercooler in 1st Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 1st Embodiment. It is a perspective view which shows the fin in 1st Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 2nd Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 3rd Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 4th Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 5th Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 6th Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 7th Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 8th Embodiment. It is a schematic diagram which shows the inside of the flow-path pipe | tube in 9th Embodiment. It is a perspective view which shows the fin of a modification.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to the drawings. This 1st Embodiment demonstrates the example which applied the intercooler of this invention to the supercharging intake air cooling system of the vehicle.

  As shown in FIG. 1, a supercharger (not shown) for supercharging intake air to the engine 10 is provided in an intake system of a vehicle engine (internal combustion engine) 10. This supercharger is provided to supplement the maximum output of the engine 10. That is, in the vehicle according to the present embodiment, the engine 10 has a small displacement for the purpose of improving fuel efficiency, and the supercharger compensates for the decrease in the maximum output accompanying this small displacement.

  In the intake system, an intercooler 20 for cooling the engine intake air is provided on the downstream side of the intake air flow from the supercharger. The intercooler 20 serves to cool the supercharged intake air compressed by the supercharger and improve the charging efficiency of the engine intake air. The intercooler 20 of this embodiment is a two-temperature water-cooled intercooler that cools the supercharged intake air with two independent cooling waters having different temperatures.

  The intercooler 20 is provided in a low-temperature cooling water circuit 30 through which low-temperature cooling water circulates, and the low-temperature cooling water flows through the intercooler 20. In addition, high-temperature cooling water circulating in the high-temperature cooling water circuit 40 also circulates inside the intercooler 20. The intercooler 20 cools the supercharged intake air by exchanging heat between the supercharged intake air compressed by the supercharger and the low-temperature cooling water and the high-temperature cooling water. As the low-temperature cooling water and the high-temperature cooling water, LLC (antifreeze), water, or the like can be used.

  The low-temperature cooling water circuit 30 is provided with a water pump 31 that circulates the low-temperature cooling water. In the low-temperature cooling water circuit 30, the heat of the low-temperature cooling water is radiated to the outside air between the water pump 31 and the intercooler 20, and the temperature is low. 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 cooling water in the high temperature cooling water circuit 40. The second radiator 42 radiates the heat absorbed by the high-temperature cooling water from the engine 10 to the outside air. The heater core 43 heats the blown air by exchanging heat 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 cooling water circuit 40.

  Since the high-temperature cooling water absorbs heat from the engine 10, the temperature of the high-temperature cooling water becomes higher than the temperature of the low-temperature cooling water when circulating inside the intercooler 20. The low temperature cooling water of the present embodiment corresponds to the first cooling medium of the present invention, and the high temperature cooling water of the present embodiment corresponds to the second cooling medium of the present invention.

  Next, the intercooler 20 of the first embodiment will be described in detail. As shown in FIGS. 2 and 3, the intercooler 20 includes a duct 21, a flange 22, a tank 23, a cooling water pipe 24, and a heat exchange unit 200. 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 cylindrical part through which the supercharged intake air flows, and is provided with an inlet port through which the supercharged intake air flows and an outlet port through which the supercharged intake air flows out. A flange 22 is provided at each of the inlet and outlet of the duct 21. A tank 23 is fixed to the inlet and outlet of the duct 21 by a flange 22. The flange 22 and the tank 23 can be fixed by caulking, for example.

  The tank 23 is a cylindrical member through which supercharged intake air flows. The supercharged intake air that flows through the tank 23 connected to the inlet of the duct 21 flows into the inlet of the duct 21, and the supercharged air that flows out of the outlet of the duct 21 passes through the tank 23 connected to the outlet of the duct 21. Flowing.

  The duct 21 is provided with a cooling water pipe 24 to which piping (not shown) through which cooling water flows is connected. The intercooler 20 is connected to the radiators 32 and 42, the heater core 43, and the like through the pipe. The cooling water pipe 24 includes a low temperature side inflow pipe 24 a that causes low temperature cooling water to flow into the heat exchange unit 200, a low temperature side outflow pipe 24 b that causes low temperature cooling water to flow out from the heat exchange unit 200, and high temperature cooling water that flows into the heat exchange unit 200. The high temperature side inflow pipe 24c to be discharged and the high temperature side outflow pipe 24d to flow out the high temperature cooling water from the heat exchange unit 200 are included.

  The heat exchange unit 200 of the intercooler 20 of the present embodiment is configured as a so-called drone cup type heat exchanger. As shown in FIG. 4, in the heat exchanging unit 200, a plurality of flow path tubes 201 and fins 202 joined between adjacent flow path tubes 201 are alternately stacked. The channel tube 201 is formed by joining a pair of opposing plate-like members 203 in the middle. The channel tube 201 has a flat cross-sectional shape.

  All or some of the components of the heat exchange unit 200 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. By heating with the flux applied to the surface of the clad material, each component of the heat exchange unit 200 is brazed and joined.

  The heat exchanging unit 200 is configured to exchange heat between the cooling water flowing inside the flow path pipe 201 and the supercharged intake air flowing outside the flow path pipe 201. A space in which the fins 202 are disposed between the flow path pipes 201 and the stacked flow path pipes 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 into a corrugated shape, and is joined to the flat outer surface side of the flow channel pipe 201, and promotes heat exchange to expand the heat transfer area between the supercharged intake air and the cooling water. Parts.

  As shown in FIG. 5, a low-temperature cooling water channel 204 through which low-temperature cooling water flows and a high-temperature cooling water channel 205 through which high-temperature cooling water flows are formed in the channel pipe 201. The flow direction of the cooling water in these cooling water flow paths 204 and 205 is a direction that intersects the flow direction of the supercharged intake air, specifically, a direction that is orthogonal to the flow direction of the supercharged intake air. 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 channel 204 corresponds to the first cooling medium channel of the present invention, and the high-temperature cooling water channel 205 corresponds to the second cooling medium channel of the present invention.

  In the channel pipe 201, the low-temperature cooling water channel 204 and the high-temperature cooling water channel 205 are arranged in parallel, and are arranged on the upstream side and the downstream side in the flow direction of the supercharged intake air. Specifically, the high-temperature cooling water flow path 205 is disposed on the upstream side in the supercharging intake air flow direction, and the low-temperature cooling water flow path 204 is disposed on the downstream side in the supercharging intake air flow direction. That is, in the present embodiment, the high-temperature cooling water flows through the upstream side of the supercharging intake passage through which the supercharging intake air passes, and the low-temperature cooling water flows through the downstream side of the supercharging intake passage.

  As shown in FIG. 5, the channel pipe 201 includes a low temperature side inlet portion 204 a that allows low temperature cooling water to flow into the low temperature cooling water channel 204, a low temperature side outlet portion 204 b that causes low temperature cooling water to flow out of the low temperature cooling water channel 204, and a high temperature. A high temperature side inlet portion 205 a that allows the high temperature cooling water to flow into the cooling water passage 205 and a high temperature side outlet portion 205 b that allows the high temperature cooling water to flow out of the high temperature cooling water passage 205 are provided. The low temperature side inlet portion 204a, the low temperature side outlet portion 204b, the high temperature side inlet portion 205a, and the high temperature side outlet portion 205b are configured by forming a through hole in the flow channel pipe 201.

  The low-temperature cooling water flow path 204 is provided with a low-temperature side partitioning section 204c that partitions the flow path and a low-temperature side U-turn section 204d that U-turns the low-temperature cooling water. The low-temperature cooling water flow path 204 includes a first low-temperature side flow path section 204e positioned upstream from the low-temperature side U-turn section 204d and a second low-temperature-side partition section 204c positioned downstream from the low-temperature side U-turn section 204d. It is partitioned by a low temperature side flow path portion 204f. The low temperature side U-turn part 204d corresponds to the first U-turn part of the present invention.

  The low-temperature cooling water flowing through the low-temperature cooling water flow path 204 changes its 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 between the first low-temperature side flow path portion 204e and the second low-temperature side flow path portion 204f.

  In the low temperature cooling water flow path 204, the first low temperature side flow path section 204e and the second low temperature side flow path section 204f are portions where the flow direction of the low temperature cooling water and the flow direction of the supercharging intake air intersect. In the present embodiment, the flow direction of the low-temperature cooling water and the flow direction of the supercharging intake air are orthogonal to each other in the first low-temperature side flow path part 204e and the second low-temperature side flow path part 204f.

  The high-temperature cooling water flow path 205 is provided with a high-temperature side partition part 205c that partitions the flow path and a high-temperature side U-turn part 205d that U-turns the high-temperature cooling water. The high temperature cooling water flow path 205 is divided by a high temperature side partition part 205c into a first high temperature side flow path part 205e located upstream from the high temperature side U turn part 205c and a second high temperature side flow part 205c located downstream from the high temperature side U turn part 205c. It is partitioned by the high temperature side flow path part 205f. The high temperature side U-turn portion 205d corresponds to the second U-turn portion of the present invention.

  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 cooling water flow path 205, the flow direction of the high temperature cooling water is opposite between the first high temperature side flow path part 205e and the second high temperature side flow path part 205f.

  In the high temperature cooling water flow path 205, the first high temperature side flow path section 205e and the second high temperature side flow path section 205f are portions where the flow direction of the high temperature cooling water and the flow direction of the supercharging intake air intersect. In the present embodiment, the flow direction of the high-temperature cooling water and the flow direction of the supercharging intake air are orthogonal to each other in the first high-temperature side flow path portion 205e and the second high-temperature side flow path portion 205f.

  In the present embodiment, the low temperature side inlet portion 204a, the low temperature side outlet portion 204b, the high temperature side inlet portion 205a, and the high temperature side outlet portion 205b are one end in the longitudinal direction of the flow channel 201 (that is, the left end in FIG. 5). Part). These are arranged in 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 supercharging intake air flow direction. Further, the low temperature side U-turn portion 204d and the high temperature side U-turn portion 205d are disposed at the other end portion (that is, the right end portion in FIG. 5) in the longitudinal direction of the flow channel tube 201.

In the present embodiment, the length D _HT in the supercharging intake air flow direction in the portion of the flow channel 201 where the high temperature cooling water flow channel 205 is formed is equal to the length D _HT in the flow channel 201 where the low temperature cooling water flow channel 204 is formed. It is shorter than the length D _LT turbocharged flow direction at a site are. In the present embodiment, 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. In the present embodiment, the length D _HT turbocharged flow direction of the high-temperature cooling water flow path 205, first high-temperature side flow passage portion 205e, turbocharged second hot side flow path portion 205f and the high-temperature side partition part 205c It is almost equal to the sum of the lengths in the flow direction.

  A supporting column 206 is provided in the low temperature side U-turn part 204 d of the low temperature cooling water flow path 204 and the high temperature side U turn part 205 d of the high temperature cooling water flow path 205. The column part 206 is formed on each of the pair of plate-like members 203 constituting the flow path pipe 201 so as to protrude into the flow path. The column portions 206 formed at positions corresponding to the pair of plate-like members 203 are joined to each other. The pair of plate-like members 203 are joined to each other in a state where a predetermined interval is maintained by the support column portion 206. That is, the opposing inner surfaces of the flow channel tube 201 are joined by the support column 206. The support portion 206 can improve the brazing property of the pair of plate-like members 203 constituting the flow channel pipe 201 and can further improve the strength of the flow channel tube 201.

  Fins 207 that divide the low-temperature cooling water flow path 204 into a plurality of narrow flow paths are disposed inside the low-temperature cooling water flow path 204. The fins 207 provided in the low-temperature cooling water flow path 204 constitute a heat exchange promoting unit for expanding the heat transfer area between the low-temperature cooling water and the supercharged intake air. The fins 207 are disposed in the first low temperature side flow path portion 204e and the second low temperature side flow path portion 204f of the low temperature cooling water flow path 204, respectively.

  As shown in FIG. 6, the fin 207 of this embodiment is configured as a straight fin. The fin 207 having a straight fin structure has a wave shape in which the wall portion 207a and the top portion 207b are continuous, and a corrugated cross-sectional shape is formed in the direction in which the waves continue. 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 each extend linearly along the flow direction of the low-temperature cooling water.

  Returning to FIG. 5, no fins are arranged inside the high-temperature cooling water flow path 205. For this reason, the high-temperature cooling water channel 205 is not divided into a plurality of narrow channels by the fins.

  In the high-temperature cooling water flow channel 205, the inner surface of the flow channel is formed flat in the first high temperature-side flow channel portion 205e and the second high temperature side flow channel portion 205f. In other words, in the high-temperature cooling water flow path 205, no protrusions or irregularities are formed on the inner surface of the portion excluding the high-temperature side U-turn part 205d.

  According to this embodiment described above, in the intercooler 20 that cools the supercharged intake air with two types of cooling water having different temperatures, the fins 207 are provided inside the low-temperature cooling water flow path 204, There are no fins inside. For this reason, in the low-temperature cooling water flow path 204 in which the fins 207 are arranged, the heat transfer area is enlarged, and an effect of promoting heat exchange between the low-temperature cooling water and the supercharging intake air can be obtained.

  On the other hand, in the high-temperature cooling water flow path 205 in which fins are not disposed, the water flow resistance can be reduced and the boiling point of the high-temperature cooling water can be increased. Thereby, the high-temperature cooling water flowing through the high-temperature cooling water flow path 205 becomes difficult to boil, and the generation of foreign matters due to the boiling of the high-temperature cooling water can be suppressed.

  Moreover, since the fin is not provided in the high temperature cooling water flow path 205, the flow path of the high temperature cooling water is wider than in the case where the fin is provided. For this reason, even if a foreign material is generated in the high-temperature cooling water, it is possible to suppress the foreign material from accumulating in the high-temperature cooling water flow channel 205 and to prevent the flow channel from being blocked by the foreign material as much as possible.

  In the present embodiment, the inner surfaces of the high temperature side flow path portions 205e and 205f of the high temperature cooling water flow path 205 are flat. For this reason, even if a foreign substance occurs in the high-temperature cooling water, it is possible to suppress the foreign substance from accumulating in the flow path, and it is possible to avoid the blockage of the flow path by the foreign substance as much as possible.

Further, in this embodiment, it is shorter than the turbocharged towards the flow direction of the length D _HT is turbocharged flowing direction of the low temperature cooling water flow path 204 length D _LT of the high-temperature cooling water passage 205, hot The channel cross-sectional area of the cooling water channel 205 is smaller than the channel cross-sectional area of the low-temperature cooling water channel 204. For this reason, the flow rate 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 is increased in heat exchange between the supercharged intake air and the high-temperature cooling water. Can be improved. As a result, 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 fins.

  Moreover, in this embodiment, the support | pillar part 206 is formed in the low temperature cooling water flow path 204 and the high temperature cooling water flow path 205, so that brazing can be improved and the strength of the flow path pipe 201 is improved. Can do. Further, the U-turn portions 204d and 205d constitute a relatively large space with the cooling water channels 204 and 205, and the amount of deformation tends to increase when thermal stress is generated in the channel tube 201. The strength of the U-turn portions 204d and 205d can be ensured by providing the column portion 206 on the U-turn portions 204d and 205d.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. In the second embodiment, only parts different from the first embodiment will be described. The second embodiment is different from the first embodiment in the configuration of the low-temperature cooling water flow path 204.

  As shown in FIG. 7, in the second embodiment, the low-temperature cooling water flow path 204 is not provided with the low-temperature side partition portion 204 c and the low-temperature side U-turn portion 204 d. Further, in the low-temperature cooling water flow path 204, the low-temperature side inlet portion 204 a and the low-temperature side outlet portion 204 b are disposed at different ends in the longitudinal direction of the flow path pipe 201. The low temperature side inlet portion 204a is disposed at one end portion (that is, the left end portion in FIG. 7) in the longitudinal direction of the flow channel tube 201, and the low temperature side outlet portion 204b is disposed in the longitudinal direction of the flow channel tube 201. It arrange | positions at the other edge part (namely, right edge part of FIG. 7).

  For this reason, in the low-temperature cooling water flow path 204 of the second embodiment, the low-temperature cooling water flows in one direction. In the example shown in FIG. 7, in the low-temperature cooling water flow path 204, the low-temperature cooling water flows in the direction from the left side to the right side in the drawing.

  The high temperature cooling water channel 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 cooling water flow path 205, the high temperature cooling water flows in a U-turn.

  In the second embodiment described above, the low-temperature cooling water flow path 204 is configured so that the low-temperature cooling water flows in one direction, and the high-temperature cooling water flow path 202 is configured to flow in a U-turn. Even in such a configuration, the same effects as those of the first embodiment can be obtained.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. In the third embodiment, only parts different from the above embodiments will be described. The third embodiment differs from the first embodiment in the configuration of the high-temperature cooling water flow path 205.

  As shown in FIG. 8, in the third embodiment, the high temperature side cooling water flow path 205 is not provided with the high temperature side partition portion 205c and the high temperature side U-turn portion 205d. In the high-temperature cooling water flow channel 205, the high-temperature side inlet portion 205 a and the high-temperature side outlet portion 205 b are disposed at different ends in the longitudinal direction of the flow channel 201. The high temperature side inlet 205a is disposed at one end in the longitudinal direction of the flow channel 201 (that is, the left end of FIG. 8), and the high temperature side outlet 205b is disposed in the longitudinal direction of the flow channel 201. It arrange | positions at the other edge part (namely, right edge part of FIG. 8).

  For this reason, in the high temperature cooling water flow path 205 of the third embodiment, high temperature cooling water flows in one direction. In the example shown in FIG. 8, in the high-temperature cooling water flow path 205, the high-temperature cooling water flows in the direction from the left side to the right side in the drawing.

  The low-temperature cooling water flow path 204 has the same configuration as that of the first embodiment, and is provided with a low-temperature side partition part 204c and a low-temperature side U-turn part 204d. For this reason, in the low-temperature cooling water flow path 204, the low-temperature cooling water flows in a U-turn.

  In the third embodiment described above, the low-temperature cooling water flow path 204 is configured such that the low-temperature cooling water flows in a U-turn and the high-temperature cooling water flow path 202 flows in one direction. Even in such a configuration, the same effects as those of the first embodiment can be obtained.

  In the third embodiment, since the high-temperature cooling water flow path 202 is configured so that the high-temperature cooling water flows in one direction, the high-temperature cooling water as in the first and second embodiments makes a U-turn. Compared with the structure which flows, the flow-path cross-sectional area of high temperature cooling water can be enlarged. For this reason, even if a foreign substance occurs in the high-temperature cooling water, it is possible to suppress the foreign substance from accumulating in the flow path, and it is possible to avoid the blockage of the flow path by the foreign substance as much as possible.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. In the fourth embodiment, only portions different from the above embodiments will be described. The fourth embodiment is different from the first embodiment in the configuration of the low-temperature cooling water flow path 204 and the high-temperature cooling water flow path 205.

  As shown in FIG. 9, in the fourth embodiment, the low temperature cooling water flow path 204 is provided with two low temperature side partition portions 204c and 204g and two low temperature side U-turn portions 204d and 204h. The low-temperature cooling water flow path 204 is divided into three flow paths 204e, 204f, and 204i by two low-temperature side partition portions 204c and 204g.

  The low-temperature cooling water flow path 204 is downstream of the first low-temperature side U-turn section 204d and the first low-temperature-side flow path section 204e located upstream from the first low-temperature-side U-turn section 204d by the first low-temperature side partition section 204c. It is partitioned by a second low temperature side flow path portion 204f located on the side. The low-temperature cooling water flow path 204 includes a second low-temperature side flow path section 204f located upstream of the second low-temperature side U-turn section 204h and a second low-temperature side U-turn section 204h by the second low-temperature side partition section 204g. It is partitioned by a third low temperature side flow path portion 204i located further downstream.

  The low-temperature cooling water flowing through the low-temperature cooling water flow path 204 changes its flow direction twice by the two low-temperature U-turn portions 204d and 204h. For this reason, in the low temperature cooling water flow path 204, the flow direction of the low temperature cooling water is opposite between the first low temperature side flow path section 204e and the second low temperature side flow path section 204f, and the second low temperature side flow path section 204f. In the third low temperature side flow path portion 204i, the flow direction of the low temperature cooling water is opposite.

  Further, in the low-temperature cooling water flow path 204, the low-temperature side inlet portion 204 a and the low-temperature side outlet portion 204 b are disposed at different ends in the longitudinal direction of the flow path pipe 201. The low temperature side inlet portion 204a is disposed at one end portion 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 204b is disposed in the longitudinal direction of the flow channel tube 201. It arrange | positions at the other edge part (namely, right edge part of FIG. 9).

  The high temperature cooling water channel 205 has the same configuration as that of the third embodiment, and the high temperature side partition portion 205c and the high temperature side U-turn portion 205d are not provided. For this reason, in the high temperature cooling water channel 205, the high temperature cooling water flows in one direction.

  In the fourth embodiment described above, the low-temperature cooling water flow path 204 is configured such that the low-temperature cooling water flows in a U-turn twice and the high-temperature cooling water flow path 202 flows in one direction. Even in such a configuration, the same effects as those of the first and third embodiments can be obtained.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG. In the fifth embodiment, only parts different from the above embodiments will be described. The fifth embodiment is different from the first embodiment in the configuration of the low-temperature cooling water flow path 204 and the high-temperature cooling water flow path 205.

  As shown in FIG. 10, in the fifth embodiment, the low temperature cooling water flow path 204 is provided with three low temperature side partition portions 204c, 204g, 204j and three low temperature side U-turn portions 204d, 204h, 204k. . The low-temperature cooling water flow path 204 is partitioned into four flow paths 204e, 204f, 204i, and 204l by three low-temperature side partition portions 204c, 204g, and 204j.

  The low-temperature cooling water flow path 204 is downstream of the first low-temperature side U-turn section 204d and the first low-temperature-side flow path section 204e located upstream from the first low-temperature-side U-turn section 204d by the first low-temperature side partition section 204c. It is partitioned by a second low temperature side flow path portion 204f located on the side. The low-temperature cooling water flow path 204 includes a second low-temperature side flow path section 204f located upstream of the second low-temperature side U-turn section 204h and a second low-temperature side U-turn section 204h by the second low-temperature side partition section 204g. It is partitioned by a third low temperature side flow path portion 204i located further downstream. Further, the low temperature cooling water flow path 204 includes a third low temperature side flow path section 204i located upstream of the third low temperature side U turn section 204k and a third low temperature side U turn section 204k by the third low temperature side partition section 204j. It is partitioned by a fourth low temperature side flow path portion 204l located further downstream.

  The low-temperature cooling water flowing through the low-temperature cooling water flow path 204 changes the flow direction three times at the three low-temperature side U-turn portions 204d, 204h, and 204k. For this reason, in the low temperature cooling water flow path 204, the flow direction of the low temperature cooling water is opposite between the first low temperature side flow path section 204e and the second low temperature side flow path section 204f, and the second low temperature side flow path section 204f. And the flow direction of the low-temperature cooling water is opposite in the third low-temperature side flow path portion 204i, and the flow direction of the low-temperature cooling water is opposite in the third low-temperature side flow path portion 204i and the fourth low-temperature side flow path portion 204l. It is in the direction.

  Further, in the low-temperature cooling water flow path 204, the low-temperature side inlet portion 204a and the low-temperature side outlet portion 204b are arranged at one end portion in the longitudinal direction of the flow channel pipe 201 (that is, the left end portion in FIG. 10).

  The high temperature cooling water channel 205 has the same configuration as that of the third embodiment, and the high temperature side partition portion 205c and the high temperature side U-turn portion 205d are not provided. For this reason, in the high temperature cooling water channel 205, the high temperature cooling water flows in one direction.

  In the fifth embodiment described above, the low-temperature cooling water channel 204 is configured such that the low-temperature cooling water flows U-turns three times, and the high-temperature cooling water channel 202 flows in one direction. Even in such a configuration, the same effects as those of the first and third embodiments can be obtained.

(Sixth embodiment)
Next, a sixth embodiment of the present invention will be described with reference to FIG. In the sixth embodiment, only parts different from the above embodiments will be described. The sixth embodiment is different from the first embodiment in the configuration of the low-temperature cooling water flow path 204 and the high-temperature cooling water flow path 205.

  As shown in FIG. 11, in the sixth embodiment, the low-temperature cooling water flow path 204 has the same configuration as that of the second embodiment, and the low-temperature cooling water flow path 204 includes a low-temperature side partition portion 204 c and a low-temperature side U-turn. The part 204d is not provided. For this reason, in the low-temperature cooling water flow path 204 of the sixth embodiment, the low-temperature cooling water flows in one direction.

  The high-temperature cooling water flow path 205 has the same configuration as that of the third embodiment, and the high-temperature cooling water flow path 205 is not provided with the high-temperature side partition part 205c and the high-temperature side U-turn part 205d. For this reason, in the high temperature cooling water flow path 205 of the sixth embodiment, the high temperature cooling water flows in one direction.

  In the sixth embodiment described above, the low-temperature cooling water channel 204 is configured to flow in one direction, and the high-temperature cooling water channel 202 is configured to flow in one direction. Even in such a configuration, the same effects as those of the first and third embodiments can be obtained.

(Seventh embodiment)
Next, a seventh embodiment of the present invention will be described with reference to FIG. In the seventh embodiment, only parts different from the above embodiments will be described. The seventh embodiment differs from the first embodiment in the configuration of the high-temperature cooling water flow path 205.

  As shown in FIG. 12, in the seventh embodiment, as in the first embodiment, the low-temperature cooling water flow path 204 and the high-temperature cooling water flow path 205 are both configured to flow in a U-turn. Further, in the seventh embodiment, the support column part 206 is not provided in the high temperature side U-turn part d of the high temperature cooling water flow path 205. For this reason, in the high temperature cooling water flow path 205, in addition to the high temperature side flow path parts 205e and 205f, the inner surface of the high temperature side U-turn part 205d is formed flat. That is, the inner surface of the high-temperature cooling water channel 205 of the seventh embodiment is formed flat across the entire channel.

  In the seventh embodiment described above, the high-temperature cooling water channel 205 is formed so that the inner surface of the entire channel is flat. Even in such a configuration, the same effects as those of the first embodiment can be obtained.

  In the seventh embodiment, in addition to the high temperature side flow path portions 205e and 205f, the inner surface of the high temperature side U-turn portion 205d is formed flat. For this reason, even if foreign matter is generated in the high-temperature cooling water, it is possible to prevent foreign matter from accumulating in the flow path even at the high temperature side U-turn portion 205d, and to prevent the flow path from being blocked by the foreign matter as much as possible. Become.

(Eighth embodiment)
Next, an eighth embodiment of the present invention will be described with reference to 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 flow path 205.

  As shown in FIG. 13, in the eighth embodiment, in the high-temperature cooling water flow channel 205, the protruding portion 205 g is formed to protrude to the flow channel side. In FIG. 13, the protrusion 205g is indicated by a black circle.

  The protruding portion 205g is formed on the inner surfaces of the first high temperature side flow path portion 205e, the second high temperature side flow path portion 205f, and the high temperature side U-turn portion 205d. That is, the high-temperature cooling water flow path 205 of the eighth embodiment has a protrusion 205g formed on the inner surface over the entire flow path. The protruding portion 205g constitutes a turbulent flow generation unit that generates turbulent flow in the high-temperature cooling water flowing through the high-temperature cooling water flow path 205.

  In the eighth embodiment described above, the protrusion 205 g is provided over the entire high-temperature cooling water flow path 205. Even in such a configuration, the same effects as those of the first embodiment can be obtained.

  Further, since the protrusion 205g is provided in the high temperature cooling water flow path 205, the heat transfer efficiency between the high temperature cooling water and the supercharging intake air can be improved. For this reason, in the high temperature cooling water flow path 205, the fall of the heat exchange performance by not having a fin can be suppressed.

(Ninth embodiment)
Next, a ninth embodiment of the present invention will be described with reference to FIG. In the ninth embodiment, only parts different from the above embodiments will be described. The ninth embodiment differs from the first embodiment in the configuration of the high-temperature cooling water flow path 205.

  As shown in FIG. 14, in the ninth embodiment, in the high-temperature cooling water flow channel 205, the high-temperature flow channel portions 205 e and 205 f are projected at the portions where the flow direction of the high-temperature cooling water and the flow direction of the supercharging intake air intersect. A portion 205g is formed. Further, in the high-temperature cooling water flow path 205, a support column part 206 is provided in the high-temperature side U-turn part 205d.

  In the ninth embodiment described above, in the high-temperature cooling water flow channel 205, the high-temperature side flow channel portions 205e and 205f are provided with the protrusions 205g, and the high-temperature side U-turn portion 205d is provided with the support column portion 206. Even in such a configuration, the same effects as those of the first embodiment can be obtained.

  Further, since the protrusions 205g are provided on the high-temperature side flow path portions 205e and 205f, the heat transfer efficiency between the high-temperature cooling water and the supercharging intake air can be improved, and the support portion is provided on the high-temperature side U-turn portion 205d. By providing 206, the strength of the high temperature side U-turn part 205d can be ensured.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention. Further, the means disclosed in each of the above embodiments may be appropriately combined within a practicable range.

  (1) In each of the above embodiments, a configuration in which a tank 23 through which supercharged intake air flows is connected to a duct 21 of an intercooler 20 and a heat exchanging unit 200 is provided inside the duct 21 (see FIGS. 2 and 3). However, the present invention is not limited to this, and the intercooler 20 may be configured differently. For example, the intercooler 20 may be configured to be inserted into the intake manifold. In this case, the duct 21 constituting the supercharged intake air flow path is unnecessary, and a plate for fixing to the wall surface of the intake manifold may be provided in the intercooler, and the heat exchanging unit 200 may be fixed to this plate.

  (2) In each of the above-described embodiments, the laminated structure in which the fins 202 that join the heat exchanger 200 of the intercooler 20 between the channel pipe 201 and the adjacent channel pipe 201 are alternately stacked (see FIG. 4). However, the present invention is not limited to this, and a different configuration may be used. For example, the heat exchanging unit 200 of the intercooler 20 may be a core plate type in which end portions of tubes are inserted into a pair of core plates. In this case, the supercharging intake may pass through the inside of the tube and the cooling water may pass through the outside of the tube, the cooling water may pass through the inside of the tube, and the supercharging intake may pass through the outside of the tube. It may be.

  (3) In the first embodiment, the column portion 206 is provided only in the U-turn portion 205d of the high-temperature cooling water flow channel 205. However, the present invention is not limited to this, and the high-temperature side flow channel portion 205e of the high-temperature cooling water flow channel 205 is provided. , 205f may be provided with a column portion 206.

  (4) In each of the above embodiments, the fins 207 arranged in the low-temperature cooling water flow path 204 are configured as straight fins (see FIG. 6). However, the present invention is not limited to this, and the fins 207 may have different shapes.

  For example, as shown in FIG. 15, the fins 207 may be configured as offset fins. The fin 207 configured as an offset fin has a cross-sectional wave shape in which a wall portion 207a and a top portion 207b are continuous, and the wall portion 207a is provided with a number of partially raised portions 207c. . The wall portions 207a and the cut-and-raised portions 207c are alternately arranged in a staggered manner along the flow direction of the low-temperature cooling water.

  Further, the fin 207 may be configured as a wave fin (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.

  (5) In each of the above embodiments, the configuration in which the fins are not provided at all inside the high-temperature cooling water flow path 205 has been described. However, this excludes the presence of relatively small fins inside the high-temperature cooling water flow path 205. is not. That is, fins may be provided in the high-temperature cooling water flow path 205 as long as the flow path blockage by foreign matter in the high-temperature cooling water can be suppressed.

DESCRIPTION OF SYMBOLS 10 Engine 20 Intercooler 200 Heat exchange part 201 Flow path pipe 204 Low temperature cooling water flow path (1st cooling medium flow path)
204d, 204h, 204k Low temperature side U-turn part (first U-turn part)
205 High temperature cooling water flow path (second cooling medium flow path)
205d High temperature side U-turn part (2nd U-turn part)
205g Protrusion part 206 Post part 207 Fin

Claims (13)

An intercooler that cools the supercharged intake air by performing heat exchange between the supercharged intake air that is supercharged to the engine (10) by the supercharger and the cooling medium,
A heat exchange section (200) for exchanging heat between the cooling medium flowing inside the flow path pipe (201) and the supercharged intake air flowing outside the flow path 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,
In the flow path pipe, a first cooling medium flow path (204) through which the first cooling medium flows so as to intersect the flow direction of the supercharged intake air, and the flow direction of the supercharged intake air, A second cooling medium flow path (205) through which the second cooling medium flows is formed,
The second cooling medium flow path is disposed upstream of the first cooling medium flow path in the flow direction of the supercharged intake air,
An intercooler in which fins (207) are provided inside the first cooling medium flow path, and fins are not provided in the second cooling medium flow path. A length (D _HT ) in the flow direction of the supercharged intake air at a portion where the second cooling medium flow path is formed in the flow path pipe is the first cooling medium flow path formed in the flow path pipe. 2. The intercooler according to claim 1, wherein the intercooler is shorter than a length (D _LT ) in a flow direction of the supercharged intake air at a site where the supercharged intake air flows.   The intercooler according to claim 1 or 2, wherein the first cooling medium flow path has a first U-turn portion (204d, 204f, 204h) for making a U-turn of the first cooling medium.   The intercooler according to claim 3, wherein the first cooling medium flow path has two first U-turn portions (204d, 204f).   The intercooler according to claim 3, wherein the first cooling medium flow path has three first U-turn portions (204d, 204f, 204h).   3. The intercooler according to claim 1, wherein the first cooling medium flow path flows in one direction.   The intercooler according to any one of claims 1 to 6, wherein the second cooling medium flow path has a second U-turn portion (205d) for making a U-turn of the second cooling medium.   The intercooler according to any one of claims 1 to 6, wherein the second cooling medium flow path flows the second cooling medium in one direction.   The intercooler according to any one of claims 1 to 8, wherein an inner surface of the second cooling medium flow path is formed in a flat shape.   The intercooler according to any one of claims 1 to 8, wherein the second cooling medium flow path has a protrusion (205g) formed on an inner surface thereof.   The intercooler according to any one of claims 1 to 8, wherein the second cooling medium flow path is formed with a column portion (206) that joins opposed inner surfaces with a predetermined distance therebetween. . The second coolant flow path is
A strut portion (206) is formed on the second U-turn portion to join the opposing inner surfaces with a predetermined distance therebetween,
The intercooler according to claim 7, wherein an inner surface of a portion (205e, 205f) where the flow direction of the second cooling medium and the flow direction of the supercharging intake air intersect is formed in a flat shape. The second coolant flow path is
A strut portion (206) is formed on the second U-turn portion to join the opposing inner surfaces with a predetermined distance therebetween,
The intercooler according to claim 7, wherein a protrusion (205g) is formed on an inner surface of a portion (205e, 205f) where the flow direction of the second cooling medium and the flow direction of the supercharging intake air intersect.

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