JP7347138B2 - vehicle cooling water system - Google Patents

Description

The present disclosure relates to a vehicle cooling water system.

Conventionally, there is a cooling water system for a vehicle described in Patent Document 1 below. The cooling water system described in Patent Document 1 includes a high temperature side heat exchanger and a low temperature side heat exchanger that are arranged in an intake passage of a vehicle. The cooling water that flows through the cooling water circuit of the internal combustion engine flows through the high temperature side heat exchanger. Cooling water having a lower temperature than the cooling water flowing through the high temperature side heat exchanger flows through the low temperature side heat exchanger. The low-temperature heat exchanger is disposed downstream of the high-temperature heat exchanger in the flow direction of intake air. In the cooling water system described in Patent Document 1, high-temperature supercharged intake air supercharged through a supercharger flows through a high-temperature side heat exchanger and a low-temperature side heat exchanger in this order. When the supercharged intake air flows through the high temperature side heat exchanger, heat exchange is performed between the cooling water flowing through the high temperature side heat exchanger and the supercharged intake air, thereby removing the crude heat of the supercharged intake air. In addition, when the supercharged intake air from which crude heat has been removed flows through the low-temperature side heat exchanger, heat exchange occurs between the cooling water flowing through the low-temperature side heat exchanger and the supercharged intake air. is further cooled.

In the cooling water circuit for an internal combustion engine described in Patent Document 1, the cooling water discharged from the pump is distributed and flows to the internal combustion engine and the high temperature side heat exchanger, so that the cooling water flows through the internal combustion engine and the high temperature side heat exchanger. Receives heat from the vessel. Therefore, the high temperature side heat exchanger is provided in parallel with the internal combustion engine in the cooling water circuit. Cooling water that has received heat in the internal combustion engine passes through a thermostat and is supplied to the radiator. Further, the cooling water that has received heat in the high temperature side heat exchanger is also supplied to the radiator. After the cooling water radiates heat in the radiator, it is sucked into the pump.

British Patent Application Publication No. 2057564

In recent years, as exhaust gas and fuel efficiency regulations have become stricter, measures have been required to cope with low-temperature environments. As one of the countermeasures, there is a growing need to quickly warm up the intake air during cold start of the internal combustion engine. When heating intake air in the cooling water system described in Patent Document 1, there is a method of warming the intake air using a high temperature side heat exchanger. However, when trying to warm intake air using a high temperature side heat exchanger, the following problems arise.

When warming intake air with the cooling water system described in Patent Document 1, it is necessary to supply the cooling water that has received heat from the internal combustion engine to the high temperature side heat exchanger. When the internal combustion engine and the high temperature side heat exchanger are arranged in parallel, the cooling water that has received heat from the internal combustion engine will be supplied to the high temperature side heat exchanger after passing through the thermostat and the pump. In this case, part of the heat of the cooling water is released to the atmosphere before it reaches the high temperature side heat exchanger from the internal combustion engine, thereby reducing the temperature of the cooling water. Furthermore, it takes a certain amount of time for the cooling water that has received heat in the internal combustion engine to reach the high temperature side heat exchanger. Such a time lag in the arrival of the cooling water and a decrease in the temperature of the cooling water are factors that reduce the warming performance of intake air by the high temperature side heat exchanger.

The present disclosure has been made in view of these circumstances, and its purpose is to provide a cooling water system for a vehicle that can more accurately cool and warm up intake air.

A cooling water system for a vehicle that solves the above problem includes a first heat exchange section (31) and a second heat exchange section (41) arranged in an intake passage (110) of an internal combustion engine (11) of a vehicle, Heat exchange is performed between the cooling water flowing through each of the first heat exchange section and the second heat exchange section and the intake air flowing through the intake passage. The cooling water system includes a first cooling water circuit (30) that circulates cooling water to the first heat exchange section and the internal combustion engine, and a first cooling water circuit (30) that circulates cooling water at a lower temperature than the first heat exchange section to the second heat exchange section. 2 cooling water circuit (40). The first cooling water circuit has a first circulation state in which the first heat exchange section is arranged in parallel with the internal combustion engine for the flow of cooling water, and a first circulation state in which the first heat exchange section is arranged in parallel with the internal combustion engine for the flow of cooling water. and a second circulation state arranged downstream in series.

According to this configuration, when the first cooling water circuit is in the first circulation state, the cooling water flows in parallel to the first heat exchange section and the internal combustion engine. Compared to the case where the heat exchange section is arranged downstream of the internal combustion engine, it is possible to flow cooling water with a lower temperature to the first heat exchange section. Therefore, it is possible to cool the intake air more accurately. On the other hand, when the first cooling water circuit is in the second circulation state, the cooling water that has received heat from the internal combustion engine flows into the first heat exchange section, so that the first heat exchange section Compared to the case where the cooling water is arranged in parallel to the engine, it is possible to flow higher temperature cooling water to the first heat exchange section. Therefore, the intake air can be warmed up more accurately. Therefore, by setting the first cooling water circuit to the first circulation state when cooling the intake air, and setting the first cooling water circuit to the second circulation state when warming the intake air, it is possible to more accurately It becomes possible to cool and warm the intake air.

Another vehicle cooling water system that solves the above problem has a heat exchange section (31) disposed in the intake passage (110) of the internal combustion engine (11) of the vehicle, and the cooling water system that flows through the heat exchange section. Heat exchange occurs between the intake air flowing through the intake passage and the intake air flowing through the intake passage. The cooling water system includes a cooling water circuit (30) that circulates cooling water to the heat exchange section and the internal combustion engine. The cooling water circuit has a first circulation state in which the heat exchange section is arranged in parallel with the internal combustion engine for the flow of cooling water, and a first circulation state in which the heat exchange section is arranged in series downstream of the internal combustion engine for the flow of cooling water. It is possible to switch to a second circulation state.

According to this configuration, when the cooling water circuit is in the first circulation state, the cooling water flows in parallel to the first heat exchange section and the internal combustion engine. Compared to the case where the first heat exchange section is disposed downstream of the internal combustion engine, it is possible to flow cooling water with a lower temperature to the first heat exchange section. Therefore, it is possible to cool the intake air more accurately. On the other hand, when the cooling water circuit is in the second circulation state, the cooling water that has received heat from the internal combustion engine flows into the first heat exchange section. On the other hand, compared to the case where the cooling water is arranged in parallel, it becomes possible to flow higher temperature cooling water to the first heat exchange section. Therefore, the intake air can be warmed up more accurately. Therefore, by setting the cooling water circuit to the first circulation state when cooling the intake air, and setting the cooling water circuit to the second circulation state when warming the intake air, the intake air can be cooled more accurately. It becomes possible to warm up the air.

Note that the above-mentioned means and the reference numerals in parentheses described in the claims are examples showing correspondences with specific means described in the embodiments to be described later.

According to the vehicle cooling water system of the present disclosure, intake air can be cooled and warmed up more accurately.

FIG. 1 is a block diagram showing a schematic configuration of a vehicle cooling water system according to a first embodiment. FIG. 2 is a plan view showing the planar structure of the plate member of the two-temperature heat exchange module of the first embodiment. FIG. 3 is a block diagram showing the electrical configuration of the vehicle cooling water system according to the first embodiment. FIG. 4 is a block diagram showing an example of the operation of the vehicle cooling water system according to the first embodiment. FIG. 5 is a block diagram showing an example of the operation of the vehicle cooling water system according to the first embodiment. FIG. 6 is a plan view showing a planar structure of a plate member of a two-temperature heat exchange module according to a modification of the first embodiment. FIG. 7 is a block diagram showing a schematic configuration of a vehicle cooling water system according to the second embodiment. FIG. 8 is a block diagram showing an example of the operation of the vehicle cooling water system according to the second embodiment. FIG. 9 is a block diagram showing a schematic configuration of a vehicle cooling water system according to the third embodiment. FIG. 10 is a block diagram showing an example of the operation of the vehicle cooling water system according to the third embodiment. FIG. 11 is a block diagram showing a schematic configuration of a vehicle cooling water system according to the fourth embodiment. FIG. 12 is a block diagram showing an example of the operation of the vehicle cooling water system according to the fourth embodiment. FIG. 13 is a block diagram showing a schematic configuration of a vehicle cooling water system according to the fifth embodiment. FIG. 14 is a block diagram showing an example of the operation of the vehicle cooling water system according to the fifth embodiment. FIG. 15 is a block diagram showing a schematic configuration of a vehicle cooling water system according to the sixth embodiment. FIG. 16 is a block diagram showing an example of the operation of the vehicle cooling water system according to the sixth embodiment. FIG. 17 is a block diagram showing a schematic configuration of a vehicle cooling water system according to another embodiment.

Hereinafter, one embodiment of a vehicle cooling water system will be described with reference to the drawings. In order to facilitate understanding of the description, the same components in each drawing are denoted by the same reference numerals as much as possible, and redundant description will be omitted.
<First embodiment>
First, a fluid circuit system for a vehicle according to a first embodiment will be described. As shown in FIG. 1, the vehicle 10 of this embodiment includes an internal combustion engine 11 and a supercharger 20. The supercharger 20 includes a compressor wheel 21 and a turbine wheel 22 that are connected to each other. Compressor wheel 21 is arranged in intake passage 110 of internal combustion engine 11 . The turbine wheel 22 is arranged in the exhaust passage 111 of the internal combustion engine 11 . In the supercharger 20, the exhaust gas discharged from the internal combustion engine 11 into the exhaust passage 111 passes through the turbine wheel 22, thereby rotating the turbine wheel 22. As the compressor wheel 21 rotates in conjunction with the rotation of the turbine wheel 22, the air flowing through the intake passage 110 is compressed. Air compressed by the compressor wheel 21, so-called supercharged intake air, is supplied to the internal combustion engine 11, thereby making it possible to increase the output of the internal combustion engine 11.

A two-temperature heat exchange module 50 is arranged between the compressor wheel 21 and the internal combustion engine 11 in the intake passage 110. The two-temperature heat exchange module 50 is a composite heat exchanger that integrally includes a high temperature side heat exchange section 31 and a low temperature side heat exchange section 41. The high temperature side heat exchange section 31 and the low temperature side heat exchange section 41 are arranged in the intake passage 110. The low temperature side heat exchange section 41 is arranged downstream of the high temperature side heat exchange section 31 in the flow direction of the intake air. Cooling water circulating through the high temperature side cooling water circuit 30 flows into the high temperature side heat exchange section 31 . Cooling water circulating through the low temperature side cooling water circuit 40 flows into the low temperature side heat exchange section 41 .

In this embodiment, the high temperature side heat exchange section 31 corresponds to the first heat exchange section, and the low temperature side heat exchange section 41 corresponds to the second heat exchange section. Further, the high temperature side cooling water circuit 30 corresponds to a first cooling water circuit, and the low temperature side cooling water circuit 40 corresponds to a second cooling water circuit. A cooling water system 70 is configured by the high temperature side cooling water circuit 30 and the low temperature side cooling water circuit 40.

The two-temperature heat exchange module 50 is composed of a plurality of substantially rectangular plate members 500 shown in FIG. A high temperature side flow path 501 and a low temperature side flow path 502 are integrally formed in the plate member 500. Cooling water circulating in the high temperature side cooling water circuit 30 flows through the high temperature side flow path 501 . Cooling water circulating in the low temperature side cooling water circuit 40 flows through the low temperature side flow path 502 .

The high temperature side flow path 501 is formed to extend linearly in a direction perpendicular to the flow direction A of intake air, and has a so-called I-flow shape. A first communication hole 501a is formed at one end of the high temperature side flow path 501. A second communication hole 501b is formed at the other end of the high temperature side flow path 501. The first communication holes 501a of each plate member 500 communicate with each other to constitute a first high temperature side tank space S11. The second communication holes 501b of each plate member 500 communicate with each other to constitute a second high temperature side tank space S12. Either one of the first high-temperature side tank space S11 and the second high-temperature side tank space S12 functions as an inlet that causes the cooling water flowing through the high-temperature side cooling water circuit 30 to flow into the high-temperature side flow path 501, and The other one of them functions as an outlet through which cooling water flows out from the high temperature side flow path 501. In this embodiment, the high temperature side flow path 501 corresponds to the cooling water flow path.

The low temperature side flow path 502 includes straight flow paths 502c and 502d extending in a direction perpendicular to the flow direction A of intake air, and a turning portion 502e formed to connect one end of the straight flow paths 502c and 502d. It has a U flow shape. Therefore, the low temperature side flow path 502 is formed so that the flow direction of the cooling water flowing therein is rotated at least once. A third communication hole 502a is formed at the end of the straight channel 502c opposite to the end connected to the turning portion 502e. A fourth communication hole 502b is formed at the end of the straight flow path 502d opposite to the end connected to the turning portion 502e. The third communication holes 502a of each plate member 500 communicate with each other to constitute a first low temperature side tank space S21. The fourth communication holes 502b of each plate member 500 communicate with each other to constitute a second low temperature side tank space S22. The first low temperature side tank space S21 functions as an inlet that causes the cooling water circulating in the low temperature side cooling water circuit 40 to flow into the low temperature side flow path 502. The second low temperature side tank space S22 functions as an outlet through which cooling water flows out from the low temperature side flow path 502.

The two-temperature heat exchange module 50 is constructed by stacking a plurality of plate members 500 shown in FIG. 2 with a predetermined gap between them. Intake air flows through the gap between adjacent plate members 500, 500. In the two-temperature heat exchange module 50, when the cooling water flows through the high temperature side flow path 501, heat exchange is performed between the cooling water and the intake air flowing through the gap between the adjacent plate members 500, 500. In addition, in the two-temperature heat exchange module 50, when the cooling water flows through the low temperature side flow path 502, heat exchange is further performed between the intake air flowing through the gap between the adjacent plate members 500, 500 and the cooling water. be exposed.

In this way, in the two-temperature heat exchange module 50, the part where the high temperature side flow path 501 is provided is a high temperature side flow path where heat exchange is performed between the cooling water circulating in the high temperature side cooling water circuit 30 and the supercharging intake air. A side heat exchange section 31 is configured. Further, a portion where the low temperature side flow path 502 is provided constitutes a low temperature side heat exchange section 41 that exchanges heat between the cooling water circulating in the low temperature side cooling water circuit 40 and the supercharged intake air.

In the two-temperature heat exchange module 50, the temperature of the cooling water flowing through the low temperature side heat exchange section 41 is lower than the temperature of the cooling water flowing through the high temperature side heat exchange section 31. Therefore, the temperature of the cooling water flowing inside each heat exchange section 31, 41 is different.
Next, with reference to FIG. 1, the high temperature side cooling water circuit 30 and the low temperature side cooling water circuit 40 will be specifically described.

In addition to the high temperature side heat exchange section 31, the high temperature side cooling water circuit 30 is provided with an internal combustion engine 11, a high temperature side pump 32, a multi-way valve 33, an on/off valve 34, a thermostat 35, and a high temperature side radiator 36. . The high temperature side pump 32, the internal combustion engine 11, the on/off valve 34, the thermostat 35, and the high temperature side radiator 36 are connected in this order in an annular manner by the high temperature side annular flow path W10. Cooling water made of water, refrigerant, etc. is circulated in the high temperature side annular flow path W10. Note that LLC or the like can be used as the refrigerant.

The high temperature side radiator 36 is arranged near the grille opening of the vehicle 10. Air is supplied to the high-temperature side radiator 36 by the running wind of the vehicle 10 or the like. Cooling water that circulates in the high temperature side annular flow path W10 flows inside the high temperature side radiator 36. In the high temperature side radiator 36, the cooling water is cooled by heat exchange between the cooling water flowing inside the radiator 36 and the air flowing outside the radiator 36. The cooling water cooled in the high temperature side radiator 36 is drawn into the high temperature side pump 32 through the high temperature side annular flow path W10.

The high temperature side pump 32 takes in low temperature cooling water discharged from the high temperature side radiator 36 and discharges it to the internal combustion engine 11 . The high temperature side pump 32 is a mechanical pump driven by the power of the internal combustion engine 11. Note that as the high-temperature side pump 32, an electric pump that is driven based on the supply of electric power may be used. In this embodiment, the high temperature side pump 32 corresponds to the first cooling water circuit pump. The discharge pressure applied to the cooling water by the high temperature side pump 32 causes the cooling water to circulate within the high temperature side annular flow path W10. When the cooling water passes through the internal combustion engine 11, the cooling water absorbs the heat of the internal combustion engine 11, thereby cooling the internal combustion engine 11. The cooling water that has received heat in the internal combustion engine 11 flows into the high temperature side radiator 36 through the on/off valve 34 and the thermostat 35, and is cooled again in the high temperature side radiator 36.

The on/off valve 34 is arranged between the internal combustion engine 11 and the thermostat 35 in the high temperature side annular flow path W10. The on/off valve 34 is a solenoid valve. When the on-off valve 34 is open, cooling water is allowed to flow from the internal combustion engine 11 to the thermostat 35. When the on-off valve 34 is in the closed state, the flow of cooling water from the internal combustion engine 11 to the thermostat 35 is blocked.

The thermostat 35 is arranged between the on/off valve 34 and the high temperature side radiator 36 in the high temperature side annular flow path W10. A bypass flow path W11 is connected to the flow path section having the thermostat 35. The bypass passage W11 is a passage through which the cooling water that has passed through the internal combustion engine 11 and the on/off valve 34 bypasses the high temperature side radiator 36 and flows to the high temperature side pump 32. The thermostat 35 causes the cooling water to flow into the high temperature side radiator 36 when the temperature of the cooling water flowing in is equal to or higher than a predetermined temperature. When the temperature of the inflowing cooling water is less than a predetermined temperature, the thermostat 35 blocks the inflow of the cooling water to the high temperature side radiator 36 and allows the cooling water to flow into the bypass passage W11.

A branch flow path W12 is formed in the high temperature side cooling water circuit 30 so as to connect the upstream side portion of the high temperature side pump 32 and the downstream side portion of the internal combustion engine 11 in the high temperature side annular flow path W10. A high temperature side heat exchange section 31 and a multi-way valve 33 are arranged in the branch flow path W12. The multi-way valve 33 is arranged at a position closer to the high temperature side pump 32 than the high temperature side heat exchange section 31 in the branch flow path W12.

A branch flow path W13 is further connected to the multi-way valve 33. The branch flow path W13 is connected to a portion between the high temperature side pump 32 and the internal combustion engine 11 in the high temperature side annular flow path W10. The multi-way valve 33 has a first port 33a connected to the upstream side of the high temperature side pump 32, a second port 33b connected to the branch flow path W13, and a third port 33c connected to the high temperature side heat exchange section 31. ing. The multi-way valve 33 switches the connection state of the branch flow paths W12 and W13 by switching the open/close state of each port 33a, 33b, and 33c. In this embodiment, the multi-way valve 33 corresponds to a heat exchange section flow path switching valve.

The first high temperature side tank space S11 of the high temperature side heat exchange section 31 is connected to the third port 33c of the multi-way valve 33 via a branch flow path W12. The second high temperature side tank space S12 of the high temperature side heat exchange section 31 is connected to the downstream portion of the internal combustion engine 11 via a branch flow path W12.
The low temperature side cooling water circuit 40 includes a low temperature side pump 42 and a low temperature side radiator 43 in addition to the low temperature side heat exchange section 41 . The low temperature side heat exchange section 41, the low temperature side pump 42, and the low temperature side radiator 43 are connected in an annular manner by a low temperature side annular flow path W20. Cooling water made of water, refrigerant, etc. circulates in the low temperature side annular flow path W20. Note that LLC or the like can be used as the refrigerant.

The low temperature side radiator 43, like the high temperature side radiator 36, is arranged near the grille opening of the vehicle 10. Cooling water that circulates in the low-temperature annular flow path W20 flows inside the low-temperature side radiator 43. In the low temperature side radiator 43, the cooling water is cooled by heat exchange between the cooling water flowing inside the radiator 43 and the air flowing outside the radiator 43. The low-temperature cooling water cooled by the low-temperature side radiator 43 flows toward the low-temperature side pump 42 through the low-temperature side annular flow path W20.

The low temperature side pump 42 sucks low temperature cooling water discharged from the low temperature side radiator 43 and discharges it to the low temperature side heat exchange section 41 . The low temperature side pump 42 is an electric pump that is driven based on the supply of electric power. The discharge pressure applied to the cooling water by the low temperature side pump 42 causes the cooling water to circulate within the low temperature side annular flow path W20. In this embodiment, the low temperature side pump 42 corresponds to the second cooling water circuit pump.

The first low temperature side tank space S21 of the low temperature side heat exchange section 41 is connected to the low temperature side pump 42 via the low temperature side annular flow path W20. The second low temperature side tank space S22 of the low temperature side heat exchange section 41 is connected to the low temperature side radiator 43 via the low temperature side annular flow path W20. Therefore, the cooling water discharged from the low temperature side pump 42 flows into the low temperature side radiator 43 after exchanging heat with the supercharged intake air in the low temperature side heat exchange section 41 .

Next, the electrical configuration of the cooling water system 70 will be described with reference to FIG. 3.
As shown in FIG. 3, the cooling water system 70 further includes an intake air temperature sensor 51 and a control device 52. In this embodiment, the control device 52 corresponds to a control section.

The intake air temperature sensor 51 detects the temperature of the supercharged intake air flowing through the intake passage 110 and outputs a signal corresponding to the detected temperature of the supercharged intake air to the control device 52.
The control device 52 is mainly composed of a microcomputer including a CPU, memory, and the like. The control device 52 comprehensively controls the cooling water system 70 by executing a program recorded in advance in a memory. Specifically, the control device 52 controls the supercharged intake air by controlling the multi-way valve 33, the on/off valve 34, and the low temperature side pump 42 based on the temperature of the supercharged intake air detected by the intake air temperature sensor 51. The intake air cooling control that cools the supercharged intake air, and the intake air warming control that warms the supercharged intake air.

Next, specific procedures for the intake air cooling control and intake air warming control executed by the control device 52 will be described.
(Intake air cooling control)
The control device 52 executes intake air cooling control when the temperature of the supercharged intake air detected by the intake air temperature sensor 51 is equal to or higher than a predetermined temperature. At this time, the control device 52 closes the first port 33a of the multi-way valve 33, and opens the second port 33b and third port 33c. Further, the control device 52 opens the on/off valve 34 and drives the low temperature side pump 42. Thereby, a flow path as shown by the solid line in FIG. 4 is formed in the cooling water system 70. Note that in FIG. 4, the flow path indicated by a broken line indicates a flow path through which cooling water does not flow.

As shown in FIG. 4, when the intake air cooling control is executed, the cooling water discharged from the high temperature side pump 32 is supplied to the internal combustion engine 11 in the high temperature side cooling water circuit 30, and is also supplied to the internal combustion engine 11 via the multi-way valve 33. It is also supplied to the high temperature side heat exchange section 31. In the high temperature side heat exchange section 31, the cooling water that has passed through the multi-way valve 33 flows into the interior through the first high temperature side tank space S11, and then is discharged through the second high temperature side tank space S12. In this manner, in the high temperature side cooling water circuit 30, the high temperature side heat exchange section 31 is arranged in parallel with the internal combustion engine 11 with respect to the flow of cooling water. In this embodiment, the state in which such a flow path is formed corresponds to the first circulation state. The cooling water that has flowed through the internal combustion engine 11 and the high-temperature side heat exchange section 31 joins at the connection portion between the high-temperature side annular flow path W10 and the branch flow path W12, and then flows into the thermostat 35 through the on/off valve 34.

The thermostat 35 causes the cooling water to flow into the high temperature side radiator 36 when the temperature of the cooling water flowing in is equal to or higher than a predetermined temperature. This forms a flow path for cooling water that flows from the thermostat 35 to the high temperature pump 32 via the high temperature radiator 36. In this embodiment, this flow path corresponds to a radiator passage flow path that causes the cooling water that has passed through the internal combustion engine 11 to flow into the internal combustion engine 11 via the high temperature side radiator 36.

Note that, when the temperature of the inflowing cooling water is less than a predetermined temperature, the thermostat 35 blocks the inflow of the cooling water to the high temperature side radiator 36 and allows the cooling water to flow into the bypass passage W11. As a result, a flow path for cooling water that directly flows from the thermostat 35 to the high temperature side pump 32 is formed. In this embodiment, this flow path corresponds to a radiator detour flow path that allows the cooling water that has passed through the internal combustion engine 11 to flow into the internal combustion engine 11 without passing through the high temperature side radiator 36.

The cooling water that has passed through the high temperature side radiator 36 or the cooling water that has passed through the bypass flow path W11 flows into the internal combustion engine 11 and the high temperature side heat exchange section 31 through the high temperature side pump 32 again.
In the high temperature side cooling water circuit 30, the internal combustion engine 11 is cooled by heat exchange between the internal combustion engine 11 and the cooling water. In addition, in the high-temperature side heat exchange section 31, heat exchange is performed between the cooling water flowing therein and the supercharged intake air flowing through the intake passage 110, so that the cooling water absorbs the crude heat of the supercharged intake air. The supercharged intake air is cooled.

On the other hand, in the low temperature side cooling water circuit 40, since the low temperature side pump 42 is driven, the cooling water cooled in the low temperature side radiator 43 is supplied to the low temperature side heat exchange section 41. In the low temperature side heat exchange section 41, heat exchange is performed between the cooling water flowing therein and the supercharged intake air that has passed through the high temperature side heat exchange section 31, thereby further cooling the supercharged intake air.

(Intake warm-up control)
The control device 52 executes intake air warming control when the temperature of the supercharged intake air detected by the intake air temperature sensor 51 is less than a predetermined temperature. At this time, the control device 52 opens the first port 33a and the third port 33c of the multi-way valve 33, and closes the second port 33b. Further, the control device 52 closes the on/off valve 34 and stops the low temperature side pump 42. Thereby, a flow path as shown by the solid line in FIG. 5 is formed in the cooling water system 70. Note that in FIG. 5, the flow path indicated by a broken line indicates a flow path through which cooling water does not flow.

As shown in FIG. 5, when the intake air warming control is executed, in the high temperature side cooling water circuit 30, the cooling water discharged from the high temperature side pump 32 passes through the internal combustion engine 11, and then passes through the high temperature side heat exchange section 31 and the high temperature side cooling water circuit 30. A flow path is formed through the multi-way valve 33 to return to the high temperature side pump 32. In the high temperature side heat exchange section 31, the cooling water that has passed through the internal combustion engine 11 flows into the interior through the second high temperature side tank space S12, and then is discharged from the first high temperature side tank space S11. In this way, the high temperature side cooling water circuit 30 is in a state where the high temperature side heat exchange section 31 is arranged in series downstream of the internal combustion engine 11 with respect to the flow of the cooling water. In this embodiment, the state in which such a flow path is formed corresponds to the second circulation state. The flow direction of the cooling water in the high temperature side heat exchange section 31 is opposite during the intake air warming control and during the intake air cooling control.

In the high temperature side cooling water circuit 30 , cooling water that has received heat in the internal combustion engine 11 is supplied to the high temperature side heat exchange section 31 . In the high temperature side heat exchange section 31, heat exchange is performed between the cooling water flowing therein and the intake air flowing through the intake passage 110, thereby warming the intake air.
Note that since the low temperature side pump 42 is stopped during the intake air warming control, it is difficult for the intake air to exchange heat with the cooling water of the low temperature side cooling water circuit 40 in the low temperature side heat exchange section 41. That is, the intake air warmed in the high temperature side heat exchange section 31 is difficult to be recooled by the cooling water of the low temperature side cooling water circuit 40.

According to the cooling water system 70 of the present embodiment described above, the functions and effects shown in (1) to (6) below can be obtained.
(1) When the high temperature side cooling water circuit 30 is in the state shown in FIG. 4, since the cooling water flows in parallel to the high temperature side heat exchange section 31 and the internal combustion engine 11, as shown in FIG. Compared to the case where the high temperature side heat exchange section 31 is arranged on the downstream side of the internal combustion engine 11 with respect to the flow of cooling water, it becomes possible to flow cooling water with a lower temperature to the high temperature side heat exchange section 31. . Therefore, it becomes possible to cool the intake air more accurately. Moreover, since cooling water with high water pressure and low water temperature flows into the high temperature side heat exchange section 31, the robustness against boiling of the cooling water can also be improved.

On the other hand, when the high temperature side cooling water circuit 30 is in the state shown in FIG. Compared to the case where the high temperature side heat exchange section 31 is arranged in parallel with the internal combustion engine 11 with respect to the flow, it becomes possible to flow higher temperature cooling water to the high temperature side heat exchange section 31. Furthermore, during the intake air warming control, the overall flow path length of the high temperature side cooling water circuit 30 is shorter than during the intake air cooling control, so that the heat of the cooling water is less likely to be released to the atmosphere. Therefore, the intake air can be warmed up more accurately.

Therefore, by setting the high temperature side cooling water circuit 30 to the state shown in FIG. 4 during intake air cooling control and setting the high temperature side cooling water circuit 30 to the state shown in FIG. 5 during intake air warming control, more accurate It becomes possible to cool and warm the intake air.
(2) When the high temperature side cooling water circuit 30 is in the state shown in FIG. 11 and the high temperature side heat exchange section 31 with cooling water. This makes it possible to more accurately cool the internal combustion engine 11 and the supercharged intake air.

(3) When the high temperature side cooling water circuit 30 is in the state shown in FIG. The multi-way valve 33 is controlled so that the In this embodiment, the flow path formed by this multi-way valve 33 corresponds to the first flow path. Furthermore, when the high temperature side cooling water circuit 30 is in the state shown in FIG. The multi-way valve 33 is controlled as follows. In this embodiment, the flow path formed by this multi-way valve 33 corresponds to the second flow path. According to this configuration, the high temperature side heat exchange section 31 is arranged in parallel with the internal combustion engine 11 with respect to the flow of cooling water, and the high temperature side heat exchange section 31 is arranged in parallel with the internal combustion engine 11 with respect to the flow of cooling water. This makes it possible to easily realize a state in which the devices are arranged in series downstream of the device.

(4) The flow direction of the cooling water in the high temperature side heat exchange section 31 is reversed between the case where the high temperature side cooling water circuit 30 is in the state shown in FIG. 4 and the case where the high temperature side cooling water circuit 30 is in the state shown in FIG. As a result, even if foreign matter mixed in the cooling water becomes clogged inside the high temperature side heat exchange section 31, the foreign matter will be discharged from the high temperature side heat exchange section 31 by reversing the flow direction of the cooling water. It becomes easier.

(5) The low-temperature side pump 42 is in a driven state when the high-temperature side cooling water circuit 30 is in the state shown in FIG. 4, and is in a non-driving state when the high-temperature side cooling water circuit 30 is in the state shown in FIG. becomes. Thereby, in the intake air warming control, the intake air warmed in the high temperature side heat exchange section 31 is less likely to be cooled down in the low temperature side heat exchange section 41, so that it becomes possible to warm up the intake air more accurately.

(6) As shown in FIG. 2, the high temperature side heat exchange section 31 has a high temperature side flow path 501 through which cooling water flows orthogonally to the flow direction A of the intake air. According to this configuration, cooling water flows from the first high temperature side tank space S11 to the second high temperature side tank space S12 during intake air cooling, and when cooling water flows from the second high temperature side tank space S12 to the first high temperature side tank space during intake air warming. In the case where the cooling water flows toward the space S11, the high temperature side flow path 501 has a symmetrical structure with respect to the flow direction of the cooling water. Therefore, the effect on performance and water flow resistance can be suppressed to zero even if the flow direction of the cooling water is reversed between when the intake air is cooled and when the intake air is warmed up. Furthermore, the temperature distribution occurring on the intake outlet side, which is a weak point of the high temperature side flow path 501 having an I-flow shape, can also be resolved by making the low-temperature side flow path 502 have a U-flow structure.

(Modified example)
Next, a modification of the cooling water system 70 of the first embodiment will be described.
In the cooling water system 70 of this modification, the two-temperature heat exchange module 50 is configured by a plate member 500 shown in FIG. 6 . As shown in FIG. 6, in this plate member 500, the shape of the high temperature side flow path 501 is different from that of the plate member 500 shown in FIG.

Specifically, the high temperature side flow path 501 includes straight flow paths 501c and 501d extending in a direction perpendicular to the flow direction A of intake air, and a turning portion 501e formed to connect one end of the straight flow paths 501c and 501d. It has a U-shape similar to the low temperature side flow path 502. Therefore, the high temperature side flow path 501 is formed such that the flow direction of the cooling water flowing therein is reversed at least once. A first communication hole 501a is formed at the end of the straight channel 501c opposite to the end connected to the turning portion 501e. A second communication hole 501b is formed at the end of the straight flow path 501d opposite to the end connected to the turning portion 502e.

In the high temperature side flow path 501 of this modification, the first high temperature side tank space S11 on the upstream side in the intake air flow direction A becomes the inlet of cooling water when the intake air is cooled, and the first high temperature side tank space S11 on the downstream side in the intake air flow direction A when the intake air is warmed up. The second high temperature side tank space S12 serves as an inlet for cooling water. According to such a configuration, since the high-temperature inlet intake air is cooled with lower-temperature cooling water, boiling of the cooling water, which is a concern particularly when cooling the intake air, can be suppressed.

<Second embodiment>
Next, a second embodiment of the cooling water system 70 will be described. Hereinafter, differences from the cooling water system 70 of the first embodiment will be mainly explained.
As shown in FIG. 7, in the cooling water system 70 of this embodiment, a multi-way valve 37 is used instead of the on/off valve 34 and the thermostat 35. The multi-way valve 37 is arranged between the internal combustion engine 11 and the high temperature side radiator 36 in the high temperature side annular flow path W10. A bypass passage W11 is connected to the multi-way valve 37. The multi-way valve 37 has a first port 37a connected to a portion downstream of the connecting portion with the branched flow path W12 in the high temperature side annular flow path W10, a second port 37b connected to the bypass flow path W11, and a high temperature side radiator 36. It has a third port 37c connected to. The multi-way valve 37 switches the connection state of the high temperature side annular flow path W10 and the bypass flow path W11 by switching the open/close state of each port 37a to 37c. In this embodiment, the multi-way valve 37 corresponds to a radiator flow path switching valve.

Further, a water temperature sensor 53 that detects the temperature of the cooling water flowing into the first port 37a of the multi-way valve 37 is provided in the high temperature side annular flow path W10. As shown by the broken line in FIG. 3, the output signal of the water temperature sensor 53 is taken into the control device 52. The control device 52 further controls the multi-way valve 37 based on the temperature of the cooling water detected by the water temperature sensor 53.

Specifically, during intake air cooling control, if the temperature of the cooling water detected by the water temperature sensor 53 is higher than a predetermined temperature, the control device 52 controls the first port 37a and the third port 37c of the multi-way valve 37. is opened, and the second port 37b is closed. Thereby, a flow path as shown by the solid line in FIG. 7 is formed in the high temperature side cooling water circuit 30. In this embodiment, this flow path corresponds to a radiator passage flow path that causes the cooling water that has passed through the internal combustion engine 11 to flow into the internal combustion engine 11 and the high temperature side heat exchange section 31 via the high temperature side radiator 36.

During intake air cooling control, if the temperature of the cooling water detected by the water temperature sensor 53 is lower than a predetermined temperature, the control device 52 opens the first port 37a and the second port 37b of the multi-way valve 37. At the same time, the third port 37c is closed. Thereby, a cooling water flow path is formed such that the cooling water that has passed through the internal combustion engine 11 flows directly to the high temperature side pump 32 via the multi-way valve 37. In this embodiment, this flow path corresponds to a radiator detour flow path that allows the cooling water that has passed through the internal combustion engine 11 to flow into the internal combustion engine 11 and the high temperature side heat exchange section 31 without passing through the high temperature side radiator 36.

The control device 52 closes all ports 37a to 37c of the multi-way valve 37 during intake air cooling control. Thereby, a flow path as shown by the solid line in FIG. 8 is formed in the high temperature side cooling water circuit 30.
According to the cooling water system 70 of the present embodiment described above, it is possible to further obtain the action and effect shown in (7) below.

(7) By electrically controlling the multi-way valve 37 instead of the on/off valve 34 and thermostat 35 of the first embodiment by the control device 52, responsiveness can be improved compared to the thermostat 35. As a result, the fuel efficiency of the vehicle 10 is improved because rapid switching between intake air cooling and intake air warming becomes possible. Furthermore, since the number of parts can be reduced, costs can also be reduced.

<Third embodiment>
Next, a third embodiment of the cooling water system 70 will be described. Hereinafter, differences from the cooling water system 70 of the second embodiment will be mainly described.
As shown in FIG. 9, in the cooling water system 70 of this embodiment, one end of the branch flow path W12 is connected to the multi-way valve 37. The multi-way valve 37 further includes a fourth port 37d connected to the branch flow path W12.

During intake air cooling control, the control device 52 opens the first port 37a and the fourth port 37d of the multi-way valve 37, and opens the second port 37b and the fourth port 37d based on the temperature of the cooling water detected by the water temperature sensor 53. One of the third ports 37c is opened and the other is closed. Thereby, a flow path as shown by the solid line in FIG. 9 is formed in the high temperature side cooling water circuit 30. Note that FIG. 9 illustrates a case where the second port 37b is in a closed state and the third port 37c is in an open state. In this case, the cooling water that has passed through the internal combustion engine 11 and the cooling water that has passed through the high temperature side heat exchange section 31 join together at the multi-way valve 37 and then flow to the high temperature side radiator 36.

On the other hand, during the intake warming control, the control device 52 opens the first port 37a and the fourth port 37d of the multi-way valve 37, and closes the second port 37b and the third port 37c. As a result, a flow path as shown by the solid line in FIG. 10 is formed in the high temperature side cooling water circuit 30. That is, the cooling water that has passed through the internal combustion engine 11 passes through the multi-way valve 37 and flows into the high temperature side heat exchange section 31 .

According to the cooling water system 70 of the present embodiment described above, it is possible to further obtain the action and effect shown in (8) below.
(8) Since the multi-way valve 37 is provided at the confluence between the high-temperature side heat exchange section 31 and the internal combustion engine 11, the multi-way valve 37 opens and closes the flow path to switch between intake air cooling control and intake air warming control. It is possible to suppress the time lag associated with the backflow phenomenon that occurs at the same time. Therefore, responsiveness can be improved. Further, when connecting the high temperature side annular flow path W10 and the branch flow path W12, a branch pipe is required at the connection part, but such a branch pipe is not necessary in the cooling water system 70 of this embodiment. , it is also possible to reduce costs.

<Fourth embodiment>
Next, a fourth embodiment of the cooling water system 70 will be described. Hereinafter, differences from the cooling water system 70 of the third embodiment will be mainly explained.
As shown in FIG. 11, the high-temperature side cooling water circuit 30 of this embodiment has branched flow so as to connect the downstream part and the upstream part of the high-temperature side pump 32 in the high-temperature side annular flow path W10. A path W14 is formed. The branch flow path W14 is provided with an on/off valve 38 and a high temperature side heat exchange section 31.

One end of the branch passage W15 is connected to a portion of the branch passage W14 between the on/off valve 38 and the high temperature side heat exchange section 31. The other end of the branch flow path W15 is connected to the fourth port 37d of the multi-way valve 37.
When the part of the branch flow path W14 from the connection part with the high temperature side annular flow path W10 to the connection part with the branch flow path W15 is defined as a flow path part W140, the on/off valve 38 is disposed in the flow path part W140. There is. The on/off valve 38 is a solenoid valve. When the on/off valve 38 is open, cooling water is allowed to flow from the high temperature side pump 32 to the high temperature side heat exchange section 31. When the on/off valve 38 is in the closed state, the flow of cooling water from the high temperature side pump 32 to the high temperature side heat exchange section 31 is blocked.

As shown by the broken line in FIG. 3, the control device 52 controls the multi-way valve 37 and the on/off valve 38 to form a flow path as shown in FIGS. 11 and 12.
Specifically, during intake air cooling control, the control device 52 opens the first port 37a of the multi-way valve 37 and closes the fourth port 37d. Further, the control device 52 opens one of the second port 37b and the third port 37c, and closes the other, based on the temperature of the cooling water detected by the water temperature sensor 53. Furthermore, the controller 52 opens the on/off valve 38. As a result, a flow path as shown by the solid line in FIG. 11 is formed in the high temperature side cooling water circuit 30. Note that FIG. 11 illustrates a case where the second port 37b is in a closed state and the third port 37c is in an open state. In this case, the cooling water discharged from the high temperature side pump 32 flows into the internal combustion engine 11 via the high temperature side annular flow path W10, and also flows into the high temperature side heat exchange section 31 through the flow path portion W140 of the branch flow path W14. Inflow. In the high temperature side pump 32, cooling water flows in from the first high temperature side tank space S11, and cooling water is discharged from the second high temperature side tank space S12. The cooling water that has passed through the high temperature side heat exchange section 31 is returned to the upstream side of the high temperature side pump 32 through the branch flow path W14. In this way, during intake air cooling control, the high temperature side heat exchange section 31 is arranged in parallel with the internal combustion engine 11 with respect to the flow of cooling water.

On the other hand, during the intake warming control, the control device 52 opens the first port 37a and the fourth port 37d of the multi-way valve 37, and closes the second port 37b and the third port 37c. Further, the control device 52 closes the on/off valve 38. Thereby, a flow path as shown by the solid line in FIG. 12 is formed in the high temperature side cooling water circuit 30. That is, since the on/off valve 38 is in the closed state, the flow path portion W140 of the branch flow path W14 is blocked. Therefore, the cooling water discharged from the high temperature side pump 32 flows only into the internal combustion engine 11 without flowing toward the high temperature side heat exchange section 31. The cooling water that has passed through the internal combustion engine 11 flows into the high temperature side heat exchange section 31 by sequentially flowing through the multi-way valve 37, the branch flow path W15, and the branch flow path W14. In the high temperature side pump 32, cooling water flows in from the first high temperature side tank space S11, and cooling water is discharged from the second high temperature side tank space S12. The cooling water that has passed through the high temperature side heat exchange section 31 is returned to the upstream side of the high temperature side pump 32 through the branch flow path W14. In this way, during the intake air warming control, the high temperature side heat exchange section 31 is arranged in series on the downstream side of the internal combustion engine 11 with respect to the flow of cooling water.

According to the cooling water system 70 of the present embodiment described above, it is possible to further obtain the action and effect shown in (9) below.
(9) In both the intake air cooling control and the intake air warming control, cooling water flows from the first high temperature side tank space S11 to the second high temperature side tank space S12 in the high temperature side heat exchange section 31. . That is, in the high temperature side heat exchange section 31, a phenomenon in which the flow direction of the cooling water is reversed between the intake air cooling control and the intake air warming control does not occur. Therefore, by reversing the flow direction of the cooling water, thermal distortion occurring inside the high temperature side heat exchange section 31 can be suppressed, and the water flow resistance of the cooling water flowing inside the high temperature side heat exchange section 31 can be reduced. Changes can be suppressed.

<Fifth embodiment>
Next, a fifth embodiment of the cooling water system 70 will be described. Hereinafter, differences from the cooling water system 70 of the third embodiment will be mainly explained.
As shown in FIG. 13, the vehicle 10 includes a so-called exhaust gas recirculation (EGR) system 60 that returns part of the exhaust gas flowing through the exhaust passage 111 to the intake passage 110 for the purpose of suppressing NOx, etc. Some are equipped with The EGR system 60 includes an EGR passage 61 that connects an intake passage 110 and an exhaust passage 111, and an EGR cooler 62 that cools exhaust gas flowing through the EGR passage 61. Exhaust gas flowing through the exhaust passage 111 is returned to the intake passage 110 through the EGR passage 61. Hereinafter, the exhaust gas returned to the intake passage 110 through the EGR passage 61 will be referred to as "EGR gas." The EGR cooler 62 cools the EGR gas by exchanging heat between the EGR gas flowing through the EGR passage 61 and cooling water. In this embodiment, the EGR cooler 62 corresponds to the cooling section.

The cooling water system 70 of this embodiment further includes a flow path that supplies cooling water to the EGR cooler 62. Specifically, a branch flow path W15 is formed in the high temperature side cooling water circuit 30 so as to connect the upstream side portion of the high temperature side pump 32 and the multi-way valve 37. An EGR cooler 62 is arranged in the middle of the branch flow path W15. The multi-way valve 37 further includes a fifth port 37e to which one end of the branch flow path W15 is connected.

During the intake air cooling control, the control device 52 opens the first port 37a, the fourth port 37d, and the fifth port 37e of the multi-way valve 37, and also controls the temperature of the cooling water detected by the water temperature sensor 53. Then, one of the second port 37b and the third port 37c is opened, and the other is closed. As a result, a flow path as shown by the solid line in FIG. 13 is formed in the high temperature side cooling water circuit 30. Note that FIG. 13 illustrates a case where the second port 37b is in a closed state and the third port 37c is in an open state. In this case, a portion of the cooling water that has flowed into the multi-way valve 37 from the internal combustion engine 11 and the high temperature side heat exchange section 31 is supplied to the EGR cooler 62 through the branch flow path W15. Thereby, the EGR gas can be cooled by the cooling water flowing through the EGR cooler 62.

On the other hand, during the intake warming control, the control device 52 opens the first port 37a and the fourth port 37d of the multi-way valve 37, and closes the second port 37b and the third port 37c. Further, when the temperature of the exhaust gas detected by the exhaust gas temperature sensor provided in the exhaust passage 111 is lower than a predetermined temperature, the control device 52 closes the fifth port 37e, and controls the temperature of the exhaust gas detected by the exhaust gas temperature sensor to close the fifth port 37e. When the temperature is above a predetermined temperature, the fifth port 37e is opened. Thereby, a flow path as shown by the solid line in FIG. 14 is formed in the high temperature side cooling water circuit 30. Note that FIG. 14 illustrates a case where the fifth port 37e is in a closed state.

According to the cooling water system 70 of the present embodiment described above, it is possible to further obtain the action and effect shown in (10) below.
(10) In the EGR system 60 as shown in FIGS. 13 and 14, the exhaust gas containing a large amount of water vapor after combustion in the internal combustion engine 11 is returned to the intake passage 110, so troubles due to condensed water generated during intake air cooling, For example, there is a problem in that the intake pipe forming the intake passage 110 is susceptible to water hammer or corrosion. In this regard, in the cooling water system 70 of the present embodiment, the intake air can be rapidly warmed up by executing the intake air warming control, so that the robustness against the generation of condensed water can be improved. Furthermore, by improving the robustness against the generation of condensed water, it is possible to expand the temperature range of the intake air in which EGR gas can be returned to the intake passage 110, thereby more accurately improving the fuel efficiency of the vehicle 10. or reduce the amount of NOx.

<Sixth embodiment>
Next, a sixth embodiment of the cooling water system 70 will be described. Hereinafter, differences from the cooling water system 70 of the fifth embodiment will be mainly explained.
In the high temperature side cooling water circuit 30 of this embodiment, one end portion of the branch flow path W15 is connected to the high temperature side heat exchange section 31. Thereby, the EGR cooler 62 is arranged in series with the high temperature side heat exchange section 31 with respect to the flow of cooling water. Note that the multi-way valve 37 is not provided with the fourth port 37d.

During intake air cooling control, the control device 52 opens the first port 37a and the fifth port 37e of the multi-way valve 37, and opens the second port 37b and the fifth port 37e based on the temperature of the cooling water detected by the water temperature sensor 53. One of the third ports 37c is opened and the other is closed. As a result, a flow path as shown by the solid line in FIG. 15 is formed in the high temperature side cooling water circuit 30. Note that FIG. 15 illustrates a case where the second port 37b is in a closed state and the third port 37c is in an open state. In this case, the cooling water that has passed through the high temperature side heat exchange section 31 flows into the EGR cooler 62, and the cooling water that has passed through the EGR cooler 62 flows into the multi-way valve 37.

On the other hand, during intake warming control, the control device 52 opens the first port 37a and the fifth port 37e of the multi-way valve 37, and closes the second port 37b and third port 37c. As a result, a flow path as shown by the solid line in FIG. 16 is formed in the high temperature side cooling water circuit 30. In this case, the cooling water that has passed through the internal combustion engine 11 flows into the EGR cooler 62 through the multi-way valve 37. Further, the cooling water that has passed through the EGR cooler 62 flows into the high temperature side heat exchange section 31.

According to the cooling water system 70 of the present embodiment described above, it is possible to further obtain the functions and effects shown in (11) and (12) below.
(11) As shown in FIG. 15, the cooling water system 70 of this embodiment has a configuration in which the cooling water after passing through the high temperature side heat exchange section 31 flows into the EGR cooler 62 during intake air cooling control. . As a result, compared to the configuration in which the cooling water after passing through the internal combustion engine 11 flows into the EGR cooler 62 as shown in FIG. is supplied to the EGR cooler 62, so the cooling performance of the EGR cooler 62 can be improved.

(12) In the cooling water system 70 of this embodiment, as shown in FIG. 16, the cooling water that has passed through the EGR cooler 62 during intake air warming control flows into the high temperature side heat exchange section 31. Thereby, the cooling water that has received heat from the exhaust gas in the EGR cooler 62 is supplied to the high temperature side heat exchange section 31, so that the warm-up performance of the high temperature side heat exchange section 31 can be improved.

<Other embodiments>
Note that the above embodiment can also be implemented in the following forms.
・Intake air cooling control and intake air warming control do not necessarily have to be strictly stratified. For example, it is possible to remove crude heat from the supercharged intake air when executing intake air warming control, and it is possible to respond flexibly in consideration of fuel efficiency and controllability.

- The configuration of each embodiment can also be applied to a cooling water system 70 that does not have the low temperature side cooling water circuit 40, as shown in FIG.
- The control device 52 and the control method thereof described in the present disclosure are provided by configuring a processor and a memory programmed to perform one or more functions embodied by a computer program. It may also be realized by multiple dedicated computers. The controller 52 and its control method described in this disclosure may be implemented by a dedicated computer provided by configuring a processor that includes one or more dedicated hardware logic circuits. The control device 52 and the control method thereof described in the present disclosure are configured by a combination of a processor and memory programmed to perform one or more functions and a processor including one or more hardware logic circuits. It may also be implemented by one or more dedicated computers. A computer program may be stored as instructions executed by a computer on a computer-readable non-transitory tangible storage medium. Dedicated hardware logic circuits and hardware logic circuits may be implemented by digital circuits that include multiple logic circuits, or by analog circuits.

- The present disclosure is not limited to the above specific examples. Design changes made by those skilled in the art to the specific examples described above are also included within the scope of the present disclosure as long as they have the characteristics of the present disclosure. The elements included in each of the specific examples described above, as well as their arrangement, conditions, shapes, etc., are not limited to those illustrated, and can be changed as appropriate. The elements included in each of the specific examples described above can be appropriately combined as long as no technical contradiction occurs.

10: Vehicle 11: Internal combustion engine 30: High temperature side cooling water circuit (first cooling water circuit)
31: High temperature side heat exchange section (first heat exchange section)
32: High temperature side pump (first cooling water circuit pump)
33: Multi-way valve (flow path switching valve for heat exchange section)
36: High temperature side radiator 37: Multi-way valve (flow path switching valve for radiator)
40: Low temperature side cooling water circuit (second cooling water circuit)
41: Low temperature side heat exchange section (second heat exchange section)
42: Low temperature side pump (pump for second cooling water circuit)
52: Control device (control unit)
62: EGR cooler (cooling section)
70: Cooling water system 110: Intake passage 501: High temperature side flow path (cooling water flow path)

Claims (12)

It has a first heat exchange part (31) and a second heat exchange part (41) arranged in an intake passage (110) of an internal combustion engine (11) of a vehicle, the first heat exchange part and the second heat exchange part. A cooling water system for a vehicle in which heat exchange is performed between cooling water flowing through each of the sections and intake air flowing through the intake passage,
a first cooling water circuit (30) that circulates cooling water through the first heat exchange section and the internal combustion engine;
a second cooling water circuit (40) that circulates cooling water at a lower temperature than the first heat exchanger to the second heat exchanger;
The first cooling water circuit is
a first circulation state in which the first heat exchange section is arranged in parallel with the internal combustion engine with respect to the flow of cooling water;
A cooling water system for a vehicle, the cooling water system being switchable to a second circulation state in which the first heat exchanger is arranged in series downstream of the internal combustion engine with respect to the flow of cooling water. The first cooling water circuit is
Supplying cooling water to the first heat exchange section and the internal combustion engine when the first cooling water circuit is in the first circulation state, and when the first cooling water circuit is in the second circulation state. further comprising a first cooling water circuit pump (32) that supplies cooling water to the internal combustion engine,
The first cooling water circuit pump is
When the first cooling water circuit is set to the first circulating state, the first heat exchanger and the The vehicle cooling water system according to claim 1, which supplies cooling water to an internal combustion engine. The first cooling water circuit is
a first flow path connecting a downstream portion of the first cooling water circuit pump and the first heat exchange section; and an upstream portion of the first cooling water circuit pump and the first heat exchange section. a flow path switching valve (33) for a heat exchange section capable of switching between a second flow path connecting the
A control unit (52) that controls the flow path switching valve for the heat exchange unit,
The control unit includes:
controlling the heat exchange section flow path switching valve so that the first flow path is formed when the first cooling water circuit is in the first circulation state;
The cooling water for a vehicle according to claim 2 , wherein the heat exchanger flow path switching valve is controlled so that the second flow path is formed when the first cooling water circuit is in the second circulation state. system. The first cooling water circuit is
a radiator (36) that cools the cooling water by heat exchange between the cooling water and the air;
a radiator passage flow path that allows the cooling water that has passed through the internal combustion engine to flow into the internal combustion engine and the first heat exchange section via the radiator; a radiator flow path switching valve (37) capable of switching between the internal combustion engine and a radiator detour flow path that flows into the first heat exchange section;
The cooling water system for a vehicle according to any one of claims 1 to 3, further comprising a control section (52) that controls the radiator flow path switching valve based on the temperature of the cooling water. When the first cooling water circuit is in the first circulation state, the cooling water that has passed through the internal combustion engine and the cooling water that has passed through the first heat exchange section are combined at the radiator flow path switching valve. ,
When the first cooling water circuit is in the second circulation state, the cooling water that has passed through the internal combustion engine passes through the radiator flow path switching valve and flows into the first heat exchange section. vehicle cooling water system. The first cooling water circuit is
Any one of claims 1 to 5, wherein the flow direction of the cooling water in the first heat exchange section is reversed depending on whether the first circulation state is set or the second circulation state is set. Cooling water system of the vehicle according to paragraph 1. The first cooling water circuit is
The cooling water system for a vehicle according to any one of claims 1 to 6, further comprising a cooling unit (62) that uses cooling water to cool the exhaust gas returned from the exhaust passage of the vehicle to the intake passage. The cooling section includes:
The vehicle cooling water system according to claim 7, wherein the vehicle cooling water system is arranged in series with the first heat exchanger with respect to the flow of the cooling water. The second cooling water circuit is
further comprising a second cooling water circuit pump (42) that circulates cooling water to the second heat exchange section,
The second cooling water circuit pump is
When the first cooling water circuit is in the first circulation state, it is in a driving state,
The cooling water system for a vehicle according to any one of claims 1 to 8, wherein the first cooling water circuit is in a non-driving state when the first cooling water circuit is in the second circulating state. The first heat exchange section includes:
The cooling water system for a vehicle according to any one of claims 1 to 9, comprising a cooling water flow path (501) through which the cooling water flows orthogonally to the flow direction of the intake air. The first heat exchange section includes:
The cooling water system for a vehicle according to any one of claims 1 to 10, comprising a cooling water flow path formed such that the cooling water flows and the flow direction of the cooling water is rotated at least once. It has a heat exchange part (31) disposed in an intake passage (110) of an internal combustion engine (11) of a vehicle, and heat exchange is performed between cooling water flowing through the heat exchange part and intake air flowing through the intake passage. A cooling water system for a vehicle,
comprising a cooling water circuit (30) that circulates cooling water to the heat exchange section and the internal combustion engine,
The cooling water circuit is
a first circulation state in which the heat exchanger is arranged in parallel with the internal combustion engine with respect to the flow of cooling water;
and a second circulation state in which the heat exchanger is arranged in series downstream of the internal combustion engine with respect to the flow of cooling water.

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