JP2018084194A - Cooling circuit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling circuit capable of securing strength of an intercooler.SOLUTION: A cooling circuit 20 includes an intercooler 13 and a pump 21. The intercooler 13 includes: an inflow port 50 to which cooling water pressure-fed from the pump 21 flows in; a heat exchange section 40 in which the cooling water that has flowed in from the inflow port 50 flows to exchange heat between the cooling water and supercharged intake air; and a discharge port 51 for discharging the cooling water that has passed through the heat exchange section 40. In order to apply flow passage resistance to the cooling water, a bore diameter of the discharge port 51 is made smaller than that of the inflow port 50.SELECTED DRAWING: Figure 2

Description

  The present disclosure relates to a cooling circuit that circulates a cooling medium in an intercooler that cools supercharged intake air pressurized by a supercharger.

  Conventionally, there is an intercooler described in Patent Document 1. The intercooler described in Patent Literature 1 cools supercharged air that is supercharged to the engine by a supercharger using cooling water. More specifically, the intercooler has an inflow port through which cooling water flows, a cooling water channel through which cooling water that flows in from the inflow port flows, and a discharge port through which the cooling water that has passed through the cooling water channel is discharged. The inflow port and the discharge port are arranged to face one end of the intercooler. The cooling water channel is formed in a U shape, and includes a first water channel extending from the inlet to the other end of the intercooler, a second water channel extending from the outlet to the other end of the intercooler, and the first water channel and the second water channel. It has a connecting water channel that connects the water channels. That is, in the intercooler described in Patent Document 1, the cooling water channel that flows in from the inflow port flows in the order of the first water channel, the connection water channel, and the second water channel, and then is discharged from the discharge port.

  In the intercooler described in Patent Document 1, a portion where the first water channel and the second water channel are disposed serves as a heat exchange unit that performs heat exchange with the supercharged air. In this intercooler, the supercharged air flows in a direction from the heat exchanging part where the second water channel is arranged toward the heat exchanging part where the first water channel is arranged. That is, the portion where the first water channel is disposed functions as an upstream heat exchange unit, and the portion where the second water channel is disposed functions as a downstream heat exchange unit. When the supercharged air passes through the upstream heat exchange section and the downstream heat exchange section, the supercharged air is cooled by exchanging heat with the cooling water flowing inside them.

JP2015-1555692A

  By the way, in the intercooler described in Patent Document 1, since the supercharged air flows from the upstream heat exchange section, the temperature of the cooling water flowing through the upstream heat exchange section, that is, the temperature of the cooling water flowing through the second water channel is likely to rise. . In particular, the temperature of the cooling water is most likely to rise at the end on the discharge port side in the second water channel. Further, due to the pressure loss when the cooling water flows from the inlet to the outlet, the water pressure of the cooling water is the lowest at the end on the outlet side in the second water channel. Therefore, the boiling point of the cooling water is lowest at the end of the second water channel on the discharge port side.

  Thus, at the end on the discharge port side in the second water channel, the temperature of the cooling water is most likely to rise and the boiling point of the cooling water is the lowest, so that there is a concern that the cooling water will boil. When the cooling water boils, the temperature of the tubular member constituting the second water channel may be excessively increased. This is a factor that causes a decrease in the strength of the intercooler.

  The present disclosure has been made in view of such circumstances, and an object thereof is to provide a cooling circuit capable of ensuring the strength of the intercooler.

  The cooling circuit (20) that solves the above problem includes an intercooler (13), a pump (21), and a resistance portion (47, 48, 51, 53, 461). The intercooler cools the supercharged intake air by heat exchange between the supercharged intake air that is supercharged to the engine (11) by the supercharger (12) and the cooling medium that flows inside. The pump pumps the cooling medium to the intercooler. The resistance portion imparts flow path resistance to the cooling medium. The intercooler has an inlet (50, 52) into which a cooling medium pumped from the pump flows in, and a heat exchange unit that exchanges heat between the cooling medium and the supercharged intake air while the cooling medium flowing in from the inlet flows. (40, 70) and discharge ports (51, 53) for discharging the cooling medium that has passed through the heat exchange section. The resistance portion is disposed in a portion from the end on the discharge port side to the inflow port of the pump in the heat exchange portion.

  According to this configuration, since the pressure of the cooling medium flowing near the discharge port of the heat exchange unit in the intercooler is increased by the resistance unit, the boiling point of the cooling medium flowing near the discharge port of the heat exchange unit can be increased. Thereby, since it becomes difficult for a cooling medium to boil, the excessive temperature rise of the member of the intercooler arrange | positioned in the vicinity of the discharge port of a heat exchange part can be suppressed. Therefore, the strength of the intercooler can be improved.

  In addition, the code | symbol in the bracket | parenthesis as described in the said means and a claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

  According to the present disclosure, it is possible to provide a cooling circuit that can ensure the strength of the intercooler.

FIG. 1 is a block diagram showing a schematic configuration of an intake system of an engine. FIG. 2 is a block diagram showing a schematic configuration of the cooling circuit of the first embodiment. FIG. 3 is a perspective view showing a perspective structure of the intercooler according to the first embodiment. 4 is a cross-sectional view showing a cross-sectional structure taken along line IV-IV in FIG. FIG. 5 is an enlarged view showing an enlarged structure of the outer fin according to the first embodiment. FIG. 6 is a plan view illustrating a planar structure of the intercooler according to the first embodiment. FIG. 7 is a graph showing the transition of the cooling water pressure relative to positions P1 to P8 in the cooling circuit of the first embodiment in comparison with the transition of the cooling water pressure of the conventional cooling circuit. FIG. 8 is a graph showing the relationship between the total pressure loss and the pump discharge pressure in the cooling circuit of the modification of the first embodiment. FIG. 9 is a graph showing the transition of the cooling water pressure with respect to positions P1 to P8 in the cooling circuit of the modification of the first embodiment in comparison with the transition of the cooling water pressure of the conventional cooling circuit. FIG. 10 is a plan view showing a planar structure of the intercooler of the second embodiment. FIG. 11 is a graph showing the transition of the cooling water pressure relative to positions P1 to P8 in the cooling circuit of the second embodiment in comparison with the transition of the cooling water pressure of the conventional cooling circuit. FIG. 12 is a plan view showing a planar structure of an intercooler according to a first modification of the second embodiment. FIG. 13 is a plan view illustrating a planar structure of an intercooler according to a second modification of the second embodiment. FIG. 14 is a side view showing the side structure of the intercooler of the third embodiment. FIG. 15 is a plan view illustrating a planar structure of the intercooler according to the third embodiment. FIG. 16 is a plan view showing a planar structure of an intercooler according to a modification of the third embodiment. FIG. 17 is a plan view showing a planar structure of the intercooler of the fourth embodiment. FIG. 18 is a block diagram showing a schematic configuration of the cooling circuit of the fourth embodiment. FIG. 19 is a plan view showing a planar structure of an intercooler according to another embodiment.

<First Embodiment>
Hereinafter, a first embodiment of a cooling circuit will be described with reference to the drawings. In order to facilitate the understanding of the description, the same constituent elements in the drawings will be denoted by the same reference numerals as much as possible, and redundant description will be omitted. First, an intake system of a vehicle engine to which the cooling circuit of the present embodiment is applied will be described.

  As shown in FIG. 1, a supercharger 12 for supercharging intake air to an engine 11 is provided in an intake system 10 of a vehicle engine of the present embodiment. The supercharger 12 is provided to supplement the maximum output of the engine 11. In the vehicle of this embodiment, the engine 11 has a small displacement for the purpose of improving fuel consumption, and the supercharger 12 compensates for the decrease in the maximum output accompanying this small displacement.

  An intercooler 13 that cools the intake air to the engine 11 is provided downstream of the supercharger 12 in the intake system 10. The intercooler 13 has a function of improving the charging efficiency of intake air into the engine 11 by cooling the supercharged intake air compressed by the supercharger 12 and supplying it to the engine 11.

  As shown in FIG. 2, the cooling water circulating in the cooling circuit 20 circulates inside the intercooler 13. In the present embodiment, the cooling water corresponds to the cooling medium. The intercooler 13 cools the supercharged intake air by exchanging heat between the supercharged intake air compressed by the supercharger 12 and the cooling water.

  The cooling circuit 20 is provided with a pump 21 for circulating cooling water. The pump 21 is a mechanical pump that is driven based on power transmitted from the engine 11 or an electric pump that is driven by electricity. A radiator 22 that cools the cooling water by dissipating the heat of the cooling water to the outside air is provided between the pump 21 and the intercooler 13 in the cooling circuit 20.

Next, the structure of the intercooler 13 will be described in detail.
As shown in FIG. 3, the intercooler 13 is formed in a substantially rectangular parallelepiped shape. The intercooler 13 includes a support part 30 and a heat exchange part 40.

  The support part 30 includes an upper support part 31 and a lower support part 32. The lower support portion 32 is made of a plate material bent into a concave shape. The upper support portion 31 is made of a plate material that is assembled to the lower support portion 32 so as to close the recessed opening portion of the lower support portion 32. In the space surrounded by the upper support portion 31 and the lower support portion 32, the heat exchanging portion 40 is accommodated. The heat exchange unit 40 is assembled to the support unit 30 so as to be sandwiched between the upper support unit 31 and the lower support unit 32.

  An inlet 50 and a discharge port 51 are provided at one end of the upper support 31 in the longitudinal direction so as to face each other in the lateral direction of the upper support 31. That is, the inflow port 50 and the discharge port 51 are disposed at one end portion 130 of the intercooler 13. The hole diameter of the discharge port 51 is smaller than the hole diameter of the inflow port 50. As shown in FIG. 2, cooling water pumped from the pump 21 flows into the inflow port 50. The cooling water that flows in from the inflow port 50 flows to the heat exchange unit 40. The cooling water that has passed through the heat exchanging unit 40 is discharged from the discharge port 51 and flows to the radiator 22.

As shown in FIGS. 3 and 4, between the upper support portion 31 and the lower support portion 32, an air inlet 33 that guides intake air from the supercharger 12 to the heat exchange portion 40, and the heat exchange portion 40. An air outlet 34 is provided for guiding the supercharged intake air that has passed through the engine 11 to the engine 11 shown in FIG.
The heat exchange unit 40 is configured as a so-called drone cup type heat exchanger. As shown in FIG. 4, the heat exchanging unit 40 has a structure in which a plurality of flow channel tubes 41 and a plurality of outer fins 42 are alternately stacked. The outer fin 42 is joined between the adjacent flow path pipes 41 and 41.

  The heat exchanging unit 40 is configured to exchange heat between the cooling water flowing inside the plurality of flow path pipes 41 and the supercharged intake air flowing outside the plurality of flow path pipes 41. A space in which the outer fins 42 are arranged between the two adjacent channel pipes 41 and 41 among the plurality of channel pipes 41 constitutes a supercharged intake channel through which the supercharged intake air flows. The outer fin 42 promotes heat exchange between the cooling water and the supercharging intake air.

  As shown in FIGS. 4 and 5, the outer fin 42 is a corrugated fin obtained by forming a plate into a wave shape. The outer fin 42 has a wave shape in which top portions 420 and valley portions 421 are alternately arranged. The outer fin 42 is configured as a louver fin in which a louver 423 is formed on a middle part 422 between the top part 420 and the valley part 421. The top 420 and the valley 421 of the outer fin 42 are joined to the outer fin 42 adjacent to the outer fin 42 by brazing. In FIG. 5, the louver 423 is not shown.

As shown in FIG. 4, the plurality of flow path pipes 41 are heat exchange portions formed in a flat shape by joining a pair of plates 410 and 411.
Specifically, the plate 410 is made of a plate-like member in which concave portions 410a and 410b are formed. The concave portions 410 a and 410 b of the plate 410 are closed by a flat plate 411.

  Between the recessed part 410a and the plate 411, the 1st heat exchange flow path 431 through which cooling water flows is comprised. As shown in FIG. 6, the first heat exchange channel 431 is formed so as to extend from one end portion 130 of the intercooler 13 to the other end portion 131 on the opposite side to the one end portion 130 of the intercooler 13. . As shown in FIGS. 4 and 6, first inner fins 441 are disposed inside the first heat exchange flow path 431. The first inner fin 441 is a corrugated fin formed in a wave shape so as to divide the first heat exchange channel 431 into a plurality of channels in the flow direction of the supercharged intake air. Note that “PT1” in FIG. 6 indicates the fin pitch of the first inner fin 441.

  As shown in FIG. 4, a second heat exchange channel 432 through which cooling water flows is configured between the recess 410 b and the plate 411. As shown in FIG. 6, the second heat exchange channel 432 is also formed so as to extend from one end portion 130 of the intercooler 13 to the other end portion 131. As shown in FIGS. 4 and 6, the second inner fin 442 is disposed in the second heat exchange flow path 432. The second inner fin 442 is a corrugated fin formed in a wave shape so as to divide the second heat exchange channel 432 into a plurality of channels in the flow direction of the supercharged intake air. The fin pitch PT2 of the second inner fin 442 is set to the same value as the fin pitch PT1 of the first inner fin 441.

  As shown in FIGS. 3 and 6, through holes 412 that penetrate the respective plates 410 are formed in the plurality of flow channel pipes 41 corresponding to the positions of the inflow ports 50 of the support portion 30. The through hole 412 is in communication with the first heat exchange channel 431 of the channel tube 41. The space formed by connecting the through holes 412 of each plate 410 functions as a distribution tank unit that distributes the cooling water flowing in from the inlet 50 to the first heat exchange channels 431 of the plurality of channel tubes 41. To do. Hereinafter, for convenience, the through hole 412 is also referred to as a “distribution tank portion 412”.

  The plurality of flow channel pipes 41 are formed with through holes 413 penetrating each plate 410 corresponding to the position of the discharge port 51 of the support portion 30. The through hole 413 is in communication with the second heat exchange flow path 432 of the flow path pipe 41. The space formed by connecting the through holes 413 of each plate 410 functions as a collective tank unit that collects the cooling water that has passed through the second heat exchange channels 432 of the plurality of channel tubes 41. Hereinafter, for convenience, the through hole 413 is also referred to as a “collection tank portion 413”.

  As shown in FIG. 6, the plurality of flow channel pipes 41 include an end portion of the first heat exchange flow channel 431 opposite to the inlet 50 and an outlet 51 of the second heat exchange flow channel 432. A U-turn portion 433 is provided so as to be connected to the opposite end portion. The U-turn part 433 includes a cooling water channel bent in a U shape.

Next, an operation example of the cooling circuit 20 of this embodiment will be described.
As shown in FIG. 2, in the cooling circuit 20, when the pump 21 is driven based on the power output from the engine 11, the cooling water is pumped from the pump 21 to the inlet 50 of the intercooler 13.

  As shown in FIG. 6, the cooling water flowing in from the inflow port 50 is distributed to the first heat exchange channels 431 of the plurality of channel tubes 41 via the distribution tank unit 412. That is, the cooling water flows through the first heat exchange channels 431 of the plurality of channel tubes 41. The cooling water that has passed through the first heat exchange channel 431 flows into the second heat exchange channel 432 after its flow direction is changed by the U-turn portion 433 toward the discharge port 51. The cooling water that has passed through the second heat exchange flow paths 432 of the plurality of flow path pipes 41 is collected in the collecting tank section 413 and then discharged from the discharge port 51.

  On the other hand, in the intercooler 13, the supercharged intake air flows between the plurality of flow path pipes 41, 41 from the air inlet 33 toward the air outlet 34. That is, in the intercooler 13, the supercharged intake air flows in the direction from the second heat exchange channel 432 toward the first heat exchange channel 431. When the supercharged air flows between the flow path pipes 41, 41, heat exchange is performed between the cooling water flowing through the first heat exchange flow path 431 and the second heat exchange flow path 432 and the supercharged air. More specifically, the supercharged intake air performs heat exchange with the cooling water flowing through the second heat exchange flow path 432 closer to the air inlet 33 and then cooled through the first heat exchange flow path 431 closer to the air outlet 34. Exchange heat with water. The supercharged intake air is cooled by heat exchange between the supercharged intake air and the cooling water. On the other hand, since the cooling water absorbs the heat of the supercharged intake air, the temperature of the cooling water rises from the inlet 50 toward the outlet 51.

  As shown in FIG. 2, in the cooling circuit 20, the cooling water whose temperature has risen by passing through the intercooler 13 flows to the radiator 22. In the radiator 22, the cooling water is cooled by performing heat exchange between the outside air sucked from the outside of the vehicle and the cooling water. The cooling water cooled in the radiator 22 flows to the pump 21 and is pumped again from the pump 21 to the intercooler 13. That is, in the cooling circuit 20, the cooling water circulates in the order of "pump 21 → intercooler 13 → radiator 22 → pump 21 → ...".

  By the way, in the intercooler 13, since the supercharging intake air flows from the second heat exchange channel 432 to the first heat exchange channel 431, the temperature of the cooling water flowing through the second heat exchange channel 432 is likely to rise. In particular, the temperature of the cooling water is most likely to rise at the end on the discharge port 51 side downstream of the second heat exchange flow path 432. Further, due to the pressure loss when the cooling water flows from the inlet 50 of the intercooler 13 to the outlet 51, the water pressure of the cooling water is the lowest at the end of the second heat exchange channel 432 on the outlet 51 side.

  FIG. 7 shows the transition of the water pressure of the cooling water at the positions P1 to P8 of the cooling circuit 20. Note that the positions P1 to P8 in FIG. 7 correspond to the positions P1 to P8 shown in FIG. That is, the position P1 indicates the position of the outlet portion of the pump 21. The position P2 indicates the position of the end of the first heat exchange channel 431 on the inlet 50 side. The position P3 indicates the position of the intermediate part of the U-turn part 433. The position P4 indicates the position of the end of the second heat exchange channel 432 on the discharge port 51 side. The position P5 indicates the position of the discharge port 51 of the intercooler 13. A position P6 indicates the position of the inlet portion of the radiator 22. The position P7 shows a part of the outlet portion of the radiator 22. The position P8 indicates the position of the inlet portion of the pump 21.

Hereinafter, for convenience, an intercooler having a structure in which the hole diameter of the inflow port 50 and the hole diameter of the discharge port 51 are the same is referred to as a “conventional intercooler”. A cooling circuit in which this conventional intercooler is used is referred to as a “conventional cooling circuit”.
In the conventional cooling circuit, the water pressure of the cooling water changes as shown by a two-dot chain line in FIG. That is, the water pressure of the cooling water basically decreases as it goes from the position P1 to the position P8. Further, in the intercooler 13, the water pressure of the cooling water decreases as it goes from the position P2 to the position P4. And in the intercooler 13, the water pressure of a cooling water becomes the lowest in the position P4. That is, at the position P4 of the intercooler 13, the boiling point of the cooling water is the lowest.

In this way, at the end of the second heat exchange channel 432 on the discharge port 51 side, the temperature of the cooling water is most likely to rise and the boiling point of the cooling water is the lowest, so there is a concern that the cooling water will boil. .
In this regard, if the hole diameter of the discharge port 51 of the intercooler 13 is smaller than the hole diameter of the inflow port 50 as in the cooling circuit 20 of the present embodiment, the discharge port 51 gives flow resistance to the cooling water. Functions as a resistance unit. Thereby, the water pressure of the cooling water changes as shown by a solid line in FIG. That is, the water pressure of the cooling water at the positions P1 to P4 upstream of the position P5 of the discharge port 51 can be increased. Therefore, since the water pressure of the cooling water flowing near the position P4 of the intercooler 13 can be increased, the boiling point of the cooling water can be increased. Thereby, the cooling water flowing near the position P4 of the intercooler 13 becomes difficult to boil.

According to the cooling circuit 20 of the present embodiment described above, the operations and effects shown in the following (1) and (2) can be obtained.
(1) Since the cooling water flowing in the vicinity of the position P4 of the intercooler 13 becomes difficult to boil, it is possible to suppress overheating of the members of the intercooler 13 disposed in the vicinity of the position P4. As a result, the strength of the intercooler 13 can be ensured.

(2) In the intercooler 13, the discharge port 51 having a hole diameter smaller than the hole diameter of the inflow port 50 functions as a resistance portion that imparts flow path resistance to the cooling water. Thereby, the water pressure of the cooling water flowing near the position P4 of the intercooler 13 can be easily increased.
(Modification)
Next, a modification of the cooling circuit 20 of the first embodiment will be described.

In the conventional cooling circuit, as shown in FIG. 8, the flow rate of the cooling water is determined by the balance point A1 between the total pressure loss PL10 of the cooling circuit 20 and the discharge pressure DP10 of the pump 21. That is, the flow rate of the cooling water is “FR10”.
On the other hand, when the discharge port 51 is caused to function as a resistance portion that imparts flow path resistance to the cooling water as in the cooling circuit 20 of the first embodiment, the total pressure loss of the cooling circuit 20 changes from the value PL10 to the value PL11. To do. As a result, the balance point between the total pressure loss PL11 of the cooling circuit 20 and the discharge pressure DP10 of the pump 21 becomes “A2”. Therefore, the flow rate of the cooling water decreases from “FR10” to “FR11”.

  In order to avoid this, in the cooling circuit 20 of the present modification, the discharge pressure of the pump 21 is increased from “DP10” to “DP11”. As a result, the balance point between the total pressure loss PL11 of the cooling circuit 20 and the discharge pressure DP11 of the pump 21 becomes “A3”, so that the flow rate of the cooling water can be set to “FR10”. That is, the amount of cooling water equivalent to the conventional cooling circuit can be ensured. 9 shows the transition of the cooling water pressure at the positions P1 to P8 of the cooling circuit 20 when the discharge pressure of the pump 21 is increased from “DP10” to “DP11”. The comparison with the cooling circuit 20 is shown.

Second Embodiment
Next, a second embodiment of the cooling circuit 20 will be described. Hereinafter, the description will focus on the differences from the cooling circuit 20 of the first embodiment.
As shown in FIG. 10, in the intercooler 13 of the present embodiment, the length of the second inner fin 442 in the cooling water flow direction is shorter than the length of the first inner fin 441 in the cooling water flow direction. ing.

According to the cooling circuit 20 of the present embodiment described above, the operation and effect shown in the following (3) can be further obtained.
(3) If the second inner fin 442 is made shorter than the first inner fin 441 as in the cooling circuit 20 of the present embodiment, the second heat exchange is performed rather than the pressure loss of the cooling water in the first heat exchange flow path 431. The pressure loss of the cooling water in the flow path 432 becomes smaller. As a result, even when the discharge pressure of the pump 21 is set to a value equivalent to the discharge pressure of the pump used in the conventional cooling circuit, as shown in FIG. It can be raised above the cooler. Therefore, it becomes difficult for the cooling water flowing near the position P4 of the intercooler 13 to boil. Therefore, since the excessive temperature rise of the member of the intercooler 13 arrange | positioned in the position P4 vicinity can be suppressed, the intensity | strength of the intercooler 13 is securable.

(First modification)
Next, a first modification of the cooling circuit 20 of the second embodiment will be described.
As shown in FIG. 12, in the intercooler 13 of the present modification, the fin pitch PT <b> 2 of the second inner fin 442 is longer than the fin pitch PT <b> 1 of the first inner fin 441. Even in such a configuration, the pressure loss of the cooling water in the second heat exchange flow path 432 is smaller than the pressure loss of the cooling water in the first heat exchange flow path 431. Therefore, as shown in (3) above. Actions and effects similar to the actions and effects obtained can be obtained.

(Second modification)
Next, a second modification of the cooling circuit 20 of the second embodiment will be described.
As shown in FIG. 13, in the intercooler of this modification, the inner fin 442 is not provided in the second heat exchange flow path 432. In other words, the inner fin 441 is provided only in the first heat exchange channel 431. According to such a configuration, the pressure loss of the cooling water in the second heat exchange channel 432 can be further reduced, so that the discharge pressure of the pump 21 can be further reduced.

<Third Embodiment>
Next, a third embodiment of the cooling circuit 20 will be described. Hereinafter, the description will focus on the differences from the cooling circuit 20 of the first embodiment.
As shown in FIGS. 14 and 15, the intercooler 13 of this embodiment includes an inflow pipe 45 connected to the inflow port 50 and a discharge pipe 46 connected to the discharge port 51.

The inflow pipe 45 is formed in an L shape. The flow path diameter of the inflow pipe 45 is set to the same length φ1 over the entire length.
The discharge pipe 46 includes a first flow path portion 461 that extends in an L shape from the discharge port 51 and a second flow path portion 462 that extends linearly from the first flow path portion 461. The channel diameter of the second channel part 462 is set to the length φ1. The channel diameter of the first channel portion 461 is set to a length φ2 shorter than the length φ1. In the present embodiment, the first flow path portion 461 corresponds to a narrow tube portion formed narrower than the inflow pipe 45.

According to the cooling circuit 20 of the present embodiment described above, the operation and effect shown in the following (4) can be further obtained.
(4) According to the cooling circuit 20 of the present embodiment, the cooling water discharged from the discharge port 51 as compared with the case where the flow path diameter of the first flow path portion 461 of the discharge pipe 46 is set to the length φ1. Can be increased by the first flow path portion 461 of the discharge pipe 46. As a result, the water pressure of the cooling water flowing near the position P4 of the intercooler 13 can be further increased. That is, the first flow path portion 461 of the discharge pipe 46 functions as a resistance portion that imparts flow path resistance to the cooling water. Thereby, since the boiling point of the cooling water of the cooling water flowing in the vicinity of the position P4 of the intercooler 13 can be further increased, the cooling water is more difficult to boil. Therefore, it is possible to further suppress overheating of the members of the intercooler 13 disposed in the vicinity of the position P4.

(Modification)
Next, a modification of the cooling circuit 20 of the third embodiment will be described.
As shown in FIG. 16, in the intercooler 13 of this modification, the first flow path portion 461 of the discharge pipe 46 is formed to be flatter than the inflow pipe 45. That is, in the present modification, the first flow path portion 461 corresponds to a flat portion. Even with such a configuration, it is possible to obtain actions and effects similar to the actions and effects shown in (4) above.

<Fourth embodiment>
Next, a fourth embodiment of the cooling circuit 20 will be described. Hereinafter, the difference from the cooling circuit 20 of the third embodiment will be mainly described.
As shown in FIG. 17, in the intercooler 13 of this modification, the inflow pipe 45 and the discharge pipe 46 have the same flow path diameter over the entire length.

The cooling circuit 20 has a throttle pipe 47 connected to the discharge pipe 46. In the present embodiment, the throttle pipe 47 corresponds to a resistance portion that is disposed in the cooling medium flow path from the discharge pipe 46 to the pump 21 and imparts flow path resistance to the cooling water.
According to the cooling circuit 20 of the present embodiment described above, the operation and effect shown in the following (6) can be obtained as the operation and effect in place of the operation and effect shown in the above (5).

  (6) According to the cooling circuit 20 of the present embodiment, the flow resistance of the cooling water increases when the cooling water discharged from the discharge port 51 flows through the throttle pipe 47. As a result, the water pressure of the cooling water flowing near the position P4 of the intercooler 13 can be further increased. Thereby, since the boiling point of the cooling water flowing in the vicinity of the position P4 of the intercooler 13 can be further increased, the cooling water is less likely to boil. Therefore, it is possible to further suppress overheating of the members of the intercooler 13 disposed in the vicinity of the position P4.

(First modification)
Next, a first modification of the cooling circuit 20 of the fourth embodiment will be described.
As shown in FIG. 18, the cooling circuit 20 of this modification includes an electromagnetic valve 48 instead of the throttle pipe 47. The opening / closing operation of the solenoid valve 48 is controlled by the ECU 60. The ECU 60 is configured around a microcomputer having a CPU, a memory, and the like. The ECU 60 imparts flow path resistance to the cooling water by setting the opening degree of the electromagnetic valve 48 to a predetermined opening degree. Even with such a configuration, it is possible to obtain actions and effects similar to the actions and effects shown in (6) of the fourth embodiment.

(Second modification)
Next, a second modification of the cooling circuit 20 of the fourth embodiment will be described.
As indicated by a broken line in FIG. 18, the output signal of the temperature sensor 61 is taken into the ECU 60 of this modification. The temperature sensor 61 detects the temperature of the position P4 of the intercooler 13, that is, the temperature of the cooling water flowing through the end on the discharge port 51 side in the second heat exchange flow path 432, and according to the detected temperature of the cooling water. Output the signal. In this modification, the temperature sensor 61 corresponds to a temperature detection unit.

  The ECU 60 detects the temperature of the cooling water based on the output signal of the temperature sensor 61 and adjusts the opening of the electromagnetic valve 48 based on the detected temperature of the cooling water. For example, the ECU 60 reduces the opening of the electromagnetic valve 48 based on the fact that the temperature of the cooling water is equal to or higher than a predetermined temperature. Or ECU60 makes the opening degree of the solenoid valve 48 smaller, so that the temperature of cooling water rises. In this modification, the ECU 60 corresponds to the control unit.

  According to such a configuration, the pressure of the cooling water flowing in the vicinity of the position P4 of the intercooler 13 can be adjusted according to the temperature of the position P4 of the intercooler 13, so that the cooling water is more difficult to boil. Therefore, it is possible to further suppress overheating of the members of the intercooler 13 disposed in the vicinity of the position P4.

<Other embodiments>
In addition, each embodiment can also be implemented with the following forms.
The intercooler 13 may be a two-stage cooling type intercooler. Specifically, as illustrated in FIG. 19, the intercooler 13 includes a heat exchange unit 70 in addition to the heat exchange unit 40. The heat exchanging unit 70 is disposed upstream of the heat exchanging unit 40 in the flow direction of the supercharged intake air. Similar to the heat exchange unit 40, the heat exchange unit 70 includes a first heat exchange channel 731, a second heat exchange channel 732, and a U-turn unit 733. Further, the intercooler 13 has an inflow port 52 and an exhaust port 53 corresponding to the heat exchange unit 70. Cooling water different from the cooling water flowing through the heat exchanging unit 40 flows through the heat exchanging unit 70. As the cooling water flowing through the heat exchanging unit 70, for example, cooling water of a cooling circuit that circulates cooling water through the pump, radiator, heater core, and engine 11 can be used. In such a two-stage cooling type intercooler 13, the hole diameter of the discharge port 51 is made smaller than the hole diameter of the inflow port 50, and the hole diameter of the discharge port 53 is made smaller than the hole diameter of the inflow port 52. Good. Moreover, it is also possible to employ | adopt the structure like 2nd-4th embodiment with respect to the heat exchange part 70. FIG.

-The heat exchange part 40 is not restricted to a drone cup type thing, For example, it may consist of a laminated structure of a tube.
-As a cooling medium which circulates through the cooling circuit 20, not only cooling water but arbitrary fluids, such as an antifreeze, can be used.

  -This indication is not limited to said specific example. Any of the above specific examples that are appropriately modified by those skilled in the art are also included in the scope of the present disclosure as long as they have the features of the present disclosure. Each element included in each of the specific examples described above, and the arrangement, conditions, shape, and the like thereof are not limited to those illustrated, and can be appropriately changed. Each element included in each of the specific examples described above can be appropriately combined as long as no technical contradiction occurs.

11: Engine 12: Supercharger 13: Intercooler 20: Cooling circuit 21: Pump 40, 70: Heat exchange section 45: Inflow pipe 46: Discharge pipe 47: Restriction pipe (resistor section)
48: Solenoid valve (resistor)
50, 52: Inlet 51, 53: Discharge port (resistance part)
61: Temperature sensor (temperature detector)
60: ECU (control unit)
431, 471: first heat exchange flow path 432, 472: second heat exchange flow path 433, 733: U-turn flow path 441: first inner fin 442: second inner fin 461: first flow path section (narrow tube section) Flat part)

Claims (10)

An intercooler (13) that cools the supercharged intake air by heat exchange between the supercharged air that is supercharged to the engine (11) by the supercharger (12) and a cooling medium that flows inside;
A pump (21) for pumping a cooling medium to the intercooler;
A resistance portion (47, 48, 51, 53, 461) for imparting flow path resistance to the cooling medium,
The intercooler is
An inlet (50, 52) into which the cooling medium pumped from the pump flows;
A heat exchange section (40, 70) that exchanges heat between the cooling medium and the supercharged intake air as the cooling medium flowing in from the inflow port flows;
A discharge port (51, 53) for discharging the cooling medium that has passed through the heat exchange section;
The resistance portion is
A cooling circuit disposed in a portion from the end on the discharge port side to the inlet of the pump in the heat exchange unit. The inlet and the outlet are provided at one end of the intercooler,
The heat exchange part is
A first heat exchange channel (431) provided to extend from the inlet to the other end of the intercooler, and through which the cooling medium flowing in from the inlet flows;
A U-turn flow path (433) that changes the flow direction of the cooling medium that has passed through the first heat exchange flow path toward the discharge port;
A second heat exchange channel (432) provided to extend from the U-turn part to one end of the intercooler, and leading the cooling medium that has passed through the U-turn part to the discharge port,
The first heat exchange channel is provided with a first inner fin (441),
The second heat exchange channel is provided with a second inner fin (442),
The cooling circuit according to claim 1, wherein a length of the second inner fin in the flow direction of the cooling medium is shorter than a length of the first inner fin in the flow direction of the cooling medium. The inlet and the outlet are provided at one end of the intercooler,
The heat exchange part is
A first heat exchange channel (431) provided to extend from the inlet to the other end of the intercooler, and through which the cooling medium flowing in from the inlet flows;
A U-turn part (433) that changes the flow direction of the cooling medium that has passed through the first heat exchange flow path toward the discharge port;
A second heat exchange channel (432) provided to extend from the U-turn part to one end of the intercooler, and leading the cooling medium that has passed through the U-turn part to the discharge port,
The cooling circuit according to claim 1, wherein an inner fin is provided only in the first heat exchange channel. The inlet and the outlet are provided at one end of the intercooler,
The heat exchange part is
A first heat exchange channel (431) provided to extend from the inlet to the other end of the intercooler, and through which the cooling medium flowing in from the inlet flows;
A U-turn part (433) that changes the flow direction of the cooling medium that has passed through the first heat exchange flow path toward the discharge port;
A second heat exchange channel (432) provided to extend from the U-turn part to one end of the intercooler, and leading the cooling medium that has passed through the U-turn part to the discharge port,
The first heat exchange channel is provided with a first inner fin (441),
The second heat exchange channel is provided with a second inner fin (442),
The cooling circuit according to claim 1, wherein a fin pitch of the second inner fin is longer than a fin pitch of the first inner fin. The cooling circuit according to any one of claims 1 to 4, wherein the resistance portion includes the discharge port (51, 53) having a hole diameter smaller than a hole diameter of the inflow port. The intercooler is
An inlet pipe (45) connected to the inlet;
A discharge pipe (46) connected to the discharge port;
The cooling circuit according to any one of claims 1 to 4, wherein the discharge pipe has a narrow tube portion (461) formed narrower than the inflow pipe as the resistance portion. The intercooler is
An inlet pipe (45) connected to the inlet;
A discharge pipe (46) connected to the discharge port;
The cooling circuit according to any one of claims 1 to 4, wherein the discharge pipe has a flat portion (461) formed flatter than the inflow pipe as the resistance portion. The intercooler further includes a discharge pipe (46) connected to the discharge port,
The said resistance part (47,48) is arrange | positioned at the cooling-medium flow path from the said discharge pipe to the said pump, and provides flow-path resistance to the cooling medium which flows through the said cooling-medium flow path. The cooling circuit according to one item. The resistance portion is composed of an electromagnetic valve (48) capable of changing a flow path diameter of the cooling medium flow path,
A temperature detection unit (61) for detecting the temperature of the cooling medium flowing through the end on the discharge port side in the heat exchange unit;
The cooling circuit according to claim 8, further comprising: a control unit (60) that controls the electromagnetic valve based on a temperature of the cooling medium detected by the temperature detection unit. The cooling circuit according to any one of claims 1 to 9, wherein the intercooler includes a two-stage cooling type intercooler.

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