JP2021038678A - Fluid circuit system for vehicle - Google Patents

Abstract

To provide a fluid circuit system for a vehicle which has a plurality of heat exchangers corresponding to a plurality of different fluid circuits, respectively, arranged in an intake passage for enabling early temperature rise of intake air even when the temperatures of fluid flowing in the heat exchangers are different.SOLUTION: In a fluid circuit system 60 for a vehicle 10, a heat exchange part where low temperature side cooling water flows is a low temperature side heat exchange part 31 and a heat exchange part where high temperature side cooling water having a higher temperature than the low temperature side cooling water flows is a high temperature side heat exchange part 41. In this case, the low temperature side heat exchange part 31 is arranged on the upstream side of the high temperature side heat exchange part 41 in an intake passage 110 in the flowing direction of intake air.SELECTED DRAWING: Figure 1

Description

The present disclosure relates to a fluid circuit system for vehicles.

Conventionally, there are vehicle fluid circuit systems described in Patent Documents 1 and 2 below. The fluid circuit system described in Patent Documents 1 and 2 includes a high temperature side heat exchanger and a low temperature side heat exchanger arranged in an intake passage of a vehicle. Cooling water for an internal combustion engine is flowing through the heat exchanger on the high temperature side. 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 side heat exchanger is arranged on the downstream side of the high temperature side heat exchanger in the flow direction of the intake air. In the fluid circuit system described in Patent Documents 1 and 2, the high-temperature supercharged intake air supercharged through the supercharger flows in the order of the high-temperature side heat exchanger and the low-temperature side heat exchanger. When the supercharged intake air flows through the high temperature side heat exchanger, heat is exchanged between the high temperature cooling water flowing through the high temperature side heat exchanger and the supercharged intake air, so that the rough heat of the supercharged intake air is removed. To. Further, when the supercharged intake air from which the rough heat has been removed flows through the low temperature side heat exchanger, heat exchange is performed between the low temperature cooling water flowing through the low temperature side heat exchanger and the supercharged intake air, so that the heat is excessive. The air supply and intake are cooled.

UK Patent Application Publication No. 2057564 German Patent Application Publication No. 4114704

In recent years, as a measure against stricter regulations on exhaust gas and fuel consumption, the expansion of the introduction of the EGR (Exhaust Gas Recirculation) system into vehicles has been studied. In a vehicle equipped with an EGR system, there is a concern that condensed water containing a component of EGR gas may be generated due to condensation of intake air containing EGR gas in an extremely low temperature environment. Since such condensed water causes corrosion of the intake pipe, there is an increasing need to suppress the generation of condensed water. In this regard, if the fluid circuit system described in Patent Documents 1 and 2 is used, the intake air containing the EGR gas can be heated in the high temperature side heat exchanger, so that the generation of condensed water can be suppressed. It becomes.

However, in the fluid circuit system described in Patent Documents 1 and 2 above, since the low temperature side heat exchanger is arranged on the downstream side of the high temperature side heat exchanger, the intake air heated in the high temperature side heat exchanger is generated. It will be cooled in the low temperature side heat exchanger. Therefore, there is a problem that it is difficult to raise the temperature of the intake air at an early stage.

It should be noted that such a problem is not limited to the vehicle in which the EGR system is introduced, but is a problem common to various vehicles that need to raise the temperature of the intake air at an early stage.
The present disclosure has been made in view of these circumstances, the purpose of which is to have a plurality of heat exchangers corresponding to each of a plurality of different fluid circuits arranged in an intake passage and flow inside each heat exchanger. It is an object of the present invention to provide a fluid circuit system for a vehicle capable of raising the temperature of intake air at an early stage even when the temperature of the fluid is different.

In a vehicle fluid circuit system that solves the above problems, a plurality of heat exchange units (31, 41) corresponding to each of a plurality of different fluid circuits (30, 40) are connected to an intake passage (110) leading to an internal combustion engine (11). ), And the temperature of the fluid flowing inside each heat exchange unit is different. Among the plurality of heat exchange units, the heat exchange unit through which a predetermined fluid flows is heat exchanged on the low temperature side. When the heat exchange section in which a fluid having a temperature higher than a predetermined fluid flows is the high temperature side heat exchange section (41), the low temperature side heat exchange section has a high temperature in the intake passage in the intake flow direction. It is located on the upstream side of the side heat exchange section.

According to this configuration, the intake air heated through the high temperature side heat exchange unit does not exchange heat with the low temperature side heat exchange unit, so that the temperature of the intake air can be increased at an early stage.
The reference numerals in parentheses described in the above means and claims are examples showing the correspondence with the specific means described in the embodiments described later.

According to the present disclosure, even when a plurality of heat exchangers corresponding to each of a plurality of different fluid circuits are arranged in the intake passage and the temperature of the fluid flowing inside each heat exchanger is different, the intake air is introduced. It is possible to provide a fluid circuit system for a vehicle capable of early temperature rise.

FIG. 1 is a block diagram showing a schematic configuration of the fluid circuit system of the first embodiment. FIG. 2 is a plan view showing a plan structure of a plate member of the two-temperature heat exchange module of the first embodiment. FIG. 3 is a perspective view showing a perspective cross-sectional structure of the two-temperature heat exchange module of the first embodiment. FIG. 4 is a block diagram showing an operation example of the fluid circuit system of the first embodiment. FIG. 5 shows the temperature Twh of the high-temperature side cooling water in the two-temperature heat exchange module in the fluid circuit system of the reference example, the temperature Twc of the low-temperature side cooling water, and the temperature Ta of the intake air passing through the two-temperature heat exchange module. It is a graph which shows each transition. FIG. 6 shows the temperature Twh of the high temperature side cooling water in the two temperature heat exchange module in the fluid circuit system of the first embodiment, the temperature Tww of the low temperature side cooling water, and the temperature of the intake air passing through the two temperature heat exchange module. It is a graph which shows each transition of Ta. FIG. 7 is a plan view showing a plan structure of a plate member in the two-temperature heat exchange module of the first modification of the first embodiment. FIG. 8 is a block diagram showing a schematic configuration of a fluid circuit system according to a second modification of the first embodiment. FIG. 9 is a block diagram showing a schematic configuration of a fluid circuit system according to a third modification of the first embodiment. FIG. 10 is a block diagram showing a schematic configuration of the fluid circuit system of the second embodiment. FIG. 11 is a block diagram showing a schematic configuration of the fluid circuit system of the third embodiment. FIG. 12 is a block diagram showing a schematic configuration of the fluid circuit system of the third embodiment. FIG. 13 is a block diagram showing a schematic configuration of the fluid circuit system of the fourth embodiment. FIG. 14 is a cross-sectional view showing a schematic configuration of a two-temperature heat exchange module of another embodiment.

Hereinafter, embodiments of the fluid circuit system of the vehicle will be described with reference to the drawings. In order to facilitate understanding of the description, the same components are designated by the same reference numerals as much as possible in each drawing, and duplicate description is omitted.
<First Embodiment>
First, the fluid circuit system of the vehicle of the first embodiment will be described. As shown in FIG. 1, the vehicle 10 of the present embodiment includes an internal combustion engine 11 and a supercharger 20. The supercharger 20 includes a compressor wheel 21 and a turbine wheel 22 connected to each other. The compressor wheel 21 is arranged in the intake passage 110 of the 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 turbine wheel 22 rotates when the exhaust gas discharged from the internal combustion engine 11 to the exhaust passage 111 passes through the turbine wheel 22. As the compressor wheel 21 rotates with the rotation of the turbine wheel 22, the air flowing through the intake passage 110 is compressed. By supplying the air compressed by the compressor wheel 21, that is, the so-called supercharged intake air, to the internal combustion engine 11, it is possible to increase the output of the internal combustion engine 11. The direction indicated by the arrow A in FIG. 1 indicates the flow direction of the intake air in the intake passage 110.

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 integrally having a low-temperature side heat exchange unit 31 and a high-temperature side heat exchange unit 41. The low temperature side heat exchange unit 31 and the high temperature side heat exchange unit 41 are arranged in the intake passage 110 leading to the internal combustion engine 11. The low temperature side heat exchange unit 31 is arranged on the upstream side of the high temperature side heat exchange unit 41 in the intake flow direction A. Cooling water circulating in the low temperature side cooling circuit 30 flows into the low temperature side heat exchange unit 31. Cooling water circulating in the high-temperature side cooling circuit 40 flows into the high-temperature side heat exchange unit 41. In the present embodiment, the low temperature side cooling circuit 30 corresponds to the low temperature side fluid circuit, and the high temperature side cooling circuit 40 corresponds to the high temperature side fluid circuit. The fluid circuit system 60 is composed of a low temperature side cooling circuit 30 and a high temperature side cooling circuit 40.

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

The low temperature side flow path 501 is formed so as to connect two straight flow paths 501a and 501b extending in a direction orthogonal to the intake flow direction A and one end of each of the straight flow paths 501a and 501b. It has a folded-back portion 501c, and is formed in a U shape as a whole. Therefore, the low temperature side flow path 501 is formed so as to turn in the flow direction of the cooling water flowing inside the flow path 501 at least once. An inflow port 501d is formed at an end of the straight flow path 501a opposite to the end connected to the folded-back portion 501c. An outlet 501e is formed at the end of the straight flow path 501b opposite to the end connected to the folded-back portion 501c. Inner fins 501f for increasing the heat transfer area with respect to the cooling water are arranged in the linear flow paths 501a and 501b.

The high temperature side flow path 502 is arranged on the downstream side of the low temperature side flow path 501 in the intake flow direction A. Similar to the low temperature side flow path 501, the high temperature side flow path 502 also has two linear flow paths 502a and 502b extending in a direction orthogonal to the intake flow direction A and their respective linear flow paths 502a and 502b. It has a folded-back portion 502c formed so as to connect one end portion, and is formed in a U shape as a whole. Therefore, the high temperature side flow path 502 is formed so as to rotate the flow direction of the cooling water flowing inside the flow path 502 at least once. An inflow port 502d is formed at an end of the linear flow path 502a opposite to the end connected to the folded-back portion 502c. An outlet 502e is formed at an end of the straight flow path 502b opposite to the end connected to the folded-back portion 502c. The flow path width of the high temperature side flow path 502 is narrower than the flow path width of the low temperature side flow path 501. Inner fins 502f for increasing the heat transfer area with respect to the cooling water are arranged in the linear flow paths 502a and 502b.

A plurality of slots 503 are formed in the portion of the plate member 500 between the low temperature side flow path 501 and the high temperature side flow path 502. These slots 503 suppress heat transfer between the cooling water flowing through the low temperature side flow path 501 and the cooling water flowing through the high temperature side flow path 502.

As shown in FIG. 3, the two-temperature heat exchange module 50 is configured by stacking and arranging a plurality of plate members 500 shown in FIG. A gap through which the supercharged intake air flowing through the intake air passage 110 flows is formed between the adjacent plate members 500, 500. Outer fins 504 for increasing the heat transfer area with respect to the supercharged intake air are arranged in this gap. The outer fin 504 includes a low temperature side outer fin 504a provided at a position corresponding to the low temperature side flow path 501 and a high temperature side outer fin 504b provided at a position corresponding to the high temperature side flow path 502. The low temperature side outer fin 504a and the high temperature side outer fin 504b are formed by fins of the same object. A gap is formed between the low temperature side outer fin 504a and the high temperature side outer fin 504b for suppressing heat transfer between them. In the present embodiment, the low temperature side outer fin 504a corresponds to the low temperature side fin, and the high temperature side outer fin 504b corresponds to the high temperature side fin.

In this two-temperature heat exchange module 50, the cooling water circulating in the low temperature side cooling circuit 30 flows into the low temperature side flow path 501 from the inflow port 501d, and then is discharged from the outflow port 501e. When the cooling water flows through the low temperature side flow path 501, heat exchange is performed between the supercharged intake air flowing through the gap between the adjacent plate members 500 and 500 and the cooling water. As described above, in the two-temperature heat exchange module 50, the portion provided with the low temperature side flow path 501 is the low temperature side where heat is exchanged between the cooling water circulating in the low temperature side cooling circuit 30 and the supercharged intake air. It constitutes a heat exchange unit 31. Further, after the cooling water circulating in the high temperature side cooling circuit 40 flows into the high temperature side flow path 502 from the inflow port 502d, it is discharged from the outflow port 502e. When the cooling water flows through the high temperature side flow path 502, heat exchange is performed between the supercharged intake air flowing through the gap between the adjacent plate members 500 and 500 and the cooling water. As described above, in the two-temperature heat exchange module 50, the portion provided with the high-temperature side flow path 502 is the high-temperature side that exchanges heat between the cooling water circulating in the high-temperature side cooling circuit 40 and the supercharged intake air. It constitutes a heat exchange unit 41.

In the two-temperature heat exchange module 50, the temperature of the cooling water flowing through the low-temperature side heat exchange unit 31 is lower than the temperature of the cooling water flowing through the high-temperature side heat exchange unit 41. Therefore, the temperatures of the cooling water flowing inside the heat exchange units 31 and 41 are different.
Next, the low temperature side cooling circuit 30 and the high temperature side cooling circuit 40 shown in FIG. 1 will be specifically described.

The low temperature side cooling circuit 30 has a low temperature side radiator 32 and a low temperature side pump 33 in addition to the low temperature side heat exchange unit 31. The low temperature side heat exchange unit 31, the low temperature side radiator 32, and the low temperature side pump 33 are connected in this order by the low temperature side annular flow path 34 in an annular shape. Cooling water made of water, a refrigerant, or the like circulates in the low temperature side annular flow path 34. It is possible to use LLC or the like as the refrigerant.

Cooling water that circulates in the low temperature side annular flow path 34 flows inside the low temperature side radiator 32. The air blown by the fan 61 is flowing outside the low temperature radiator 32. In the low temperature side radiator 32, the cooling water is cooled by heat exchange between the cooling water flowing inside the radiator 32 and the air flowing outside the radiator 32. The low-temperature cooling water cooled by the low-temperature side radiator 32 flows toward the low-temperature side pump 33 through the low-temperature side annular flow path 34.

The low temperature side pump 33 sucks in the low temperature cooling water discharged from the low temperature side radiator 32 and discharges it to the low temperature side heat exchange unit 31. The cooling water circulates in the low temperature side annular flow path 34 due to the discharge pressure applied to the cooling water by the low temperature side pump 33.
The low-temperature cooling water discharged from the low-temperature side pump 33 flows inside the low-temperature side heat exchange unit 31. The supercharged intake air in the intake passage 110 flows outside the low temperature side heat exchange unit 31. In the low temperature side heat exchange unit 31, the supercharged intake air is cooled by heat exchange between the low temperature cooling water flowing inside the low temperature cooling water and the supercharged intake air flowing outside the low temperature cooling water. By cooling the supercharged intake air, the filling efficiency of the supercharged intake air can be increased, so that the output of the internal combustion engine 11 can be improved. The cooling water whose temperature has risen due to heat exchange with the supercharged intake air in the low temperature side heat exchange unit 31 flows toward the low temperature side radiator 32 through the low temperature side annular flow path 34, and is cooled again by the low temperature side radiator 32. To.

The high temperature side cooling circuit 40 includes a high temperature side radiator 42, a high temperature side pump 43, and a switching unit 44 in addition to the high temperature side heat exchange unit 41. The high temperature side radiator 42, the high temperature side pump 43, the internal combustion engine 11, and the switching unit 44 are connected in this order by the high temperature side annular flow path 45 in an annular shape. Cooling water made of water, a refrigerant, or the like circulates in the high-temperature side annular flow path 45. It is possible to use LLC or the like as the refrigerant.

Cooling water that circulates in the high temperature side annular flow path 45 flows inside the high temperature side radiator 42. The air blown by the fan 61 is flowing outside the high temperature side radiator 42. In the high temperature side radiator 42, the cooling water is cooled by heat exchange between the cooling water flowing inside the radiator 42 and the air flowing outside the radiator 42. The cooling water cooled in the high temperature side radiator 42 flows toward the high temperature side pump 43 through the high temperature side annular flow path 45.

The high temperature side pump 43 sucks in the low temperature cooling water discharged from the high temperature side radiator 42 and discharges it to the internal combustion engine 11. The cooling water circulates in the high temperature side annular flow path 45 due to the discharge pressure applied to the cooling water by the high temperature side pump 43. When the cooling water passes through the internal combustion engine 11, the cooling water absorbs the heat of the internal combustion engine 11 to cool the internal combustion engine 11. The cooling water whose temperature has risen in the internal combustion engine 11 flows into the high-temperature side radiator 42 through the switching unit 44, so that the cooling water is cooled again in the high-temperature side radiator 42.

The switching portion 44 is arranged between the internal combustion engine 11 and the high temperature side radiator 42 in the high temperature side annular flow path 45. A first bypass flow path 46 and a second bypass flow path 47 are connected to the switching unit 44. The first bypass flow path 46 extends from the switching portion 44 and is connected to a portion of the high temperature side annular flow path 45 between the high temperature side radiator 42 and the high temperature side pump 43. The second bypass flow path 47 extends from the switching portion 44 and is connected to a portion of the high temperature side annular flow path 45 between the high temperature side radiator 42 and the high temperature side pump 43. The switching unit 44 can selectively switch whether the cooling water discharged from the internal combustion engine 11 flows to the high temperature side radiator 42, the first bypass flow path 46, or the second bypass flow path 47. .. The switching unit 44 includes a valve, a thermostat, or the like. In the present embodiment, the switching unit 44 corresponds to the high temperature side switching unit.

The fluid circuit system 60 further includes a control device 62 that controls a low temperature side pump 33, a high temperature side pump 43, and a switching unit 44, and a temperature sensor 63 that detects the temperature of the cooling water that has passed through the internal combustion engine 11. .. The control device 62 is mainly composed of a microcomputer having a CPU, a memory, and the like, and by executing a program stored in the memory, the flow of cooling water in the low temperature side cooling circuit 30 and the high temperature side cooling circuit 40. To control. In the present embodiment, the control device 62 corresponds to the low temperature side control unit and the high temperature side control unit.

Next, the control procedure executed by the control device 62 will be specifically described. In the following, the cooling water circulating in the low temperature side cooling circuit 30 will be referred to as "low temperature side cooling water", and the cooling water circulating in the high temperature side cooling circuit 40 will be referred to as "high temperature side cooling water". In the present embodiment, the low temperature side cooling water corresponds to the low temperature side fluid, and the high temperature side cooling water corresponds to the high temperature side fluid.

The control device 62 drives the low temperature side pump 33 in the intake air cooling mode for cooling the supercharged intake air. As a result, as shown by the solid arrow in FIG. 1, the cooling water cooled by the low temperature side radiator 32 flows into the low temperature side heat exchange unit 31, so that the supercharging intake air is cooled in the low temperature side heat exchange unit 31. To. Further, the control device 62 controls the switching unit 44 according to the temperature of the high temperature side cooling water detected by the temperature sensor 63 in the intake air cooling mode. Specifically, in the control device 62, when the temperature of the high-temperature side cooling water detected by the temperature sensor 63 is equal to or higher than a predetermined temperature, the high-temperature side cooling water discharged from the internal combustion engine 11 is the high-temperature side annular flow path. The switching unit 44 is controlled so as to flow toward the high temperature side radiator 42 through 45. As a result, as shown by the solid arrow in FIG. 1, the high-temperature side cooling water cooled by the high-temperature side radiator 42 flows through the internal combustion engine 11, so that the internal combustion engine 11 can be cooled. On the other hand, in the control device 62, when the temperature of the high temperature side cooling water detected by the temperature sensor 63 is lower than the predetermined temperature, the high temperature side cooling water discharged from the internal combustion engine 11 flows through the second bypass flow path 47. The switching unit 44 is controlled so as to. As a result, as shown by the broken line arrow in FIG. 1, the high temperature side cooling water circulates in the internal combustion engine 11 without being cooled by the high temperature side radiator 42, so that the internal combustion engine 11 is warmed up at an early stage. Is possible.

In the intake air cooling mode, the high temperature side cooling water does not flow through the first bypass flow path 46, so that the temperature of the high temperature side cooling water inside the high temperature side heat exchange unit 41 is substantially equal to the outside air temperature. Therefore, when the supercharged intake air cooled in the low temperature side heat exchange unit 31 passes through the high temperature side heat exchange unit 41, heat is generated between the high temperature side cooling water inside the high temperature side heat exchange unit 41 and the supercharged intake air. Although the replacement is done, the temperature of the supercharged intake air does not rise above the outside temperature. The output of the internal combustion engine 11 can be improved by supplying the supercharged intake air cooled by the low temperature side heat exchange unit 31 to the internal combustion engine 11.

By the way, since the temperature of the high temperature side cooling water flowing through the high temperature side heat exchange unit 41 is high, the high temperature side heat exchange unit 41 is arranged on the upstream side of the low temperature side heat exchange unit 31 as in the conventional fluid circuit system. If so, the temperature of the high temperature side cooling water may rise excessively, and the high temperature side cooling water may evaporate. When the high-temperature side cooling water evaporates, there is a concern that the plate member 500 may be thermally distorted or the plate member 500 may be corroded due to the adhesion of the rust preventive agent contained in the cooling water. In this respect, the fluid circuit system 60 of the present embodiment has a configuration in which the supercharged intake air flows in the order of the low temperature side heat exchange unit 31 and the high temperature side heat exchange unit 41. In such a configuration, the supercharged intake air is once cooled in the low temperature side heat exchange unit 31 and then flows into the high temperature side heat exchange unit 41. Therefore, it is possible to lower the temperature of the supercharged intake air flowing into the high temperature side heat exchange unit 41. As a result, it is possible to prevent the high-temperature side cooling water inside the high-temperature side heat exchange unit 41 from reaching the boiling point, so that thermal strain and corrosion of the plate member 500 can be suppressed.

According to the experiments of the inventors, the high temperature side heat exchange unit 41 is located on the low temperature side with respect to the intake flow direction A as compared with the configuration in which the low temperature side heat exchange unit 31 is arranged on the upstream side of the low temperature side heat exchange unit 31. The configuration of the present embodiment in which the heat exchange unit 31 is located upstream of the high temperature side heat exchange unit 41 lowers the temperature of the high temperature side cooling water flowing through the high temperature side heat exchange unit 41 by about 10 degrees. It has been confirmed that it can be done. In the following, a configuration in which the high temperature side heat exchange unit 41 is arranged on the upstream side of the low temperature side heat exchange unit 31 with respect to the intake flow direction A will be referred to as a “conventional configuration”.

On the other hand, the control device 62 stops the low temperature side pump 33 in the intake air warming mode for warming the supercharged intake air. Further, the control device 62 controls the switching unit 44 so that the high-temperature side cooling water discharged from the internal combustion engine 11 flows through the first bypass flow path 46 in the intake warm-up mode. As a result, as shown in FIG. 4, the high temperature side cooling water circulates between the internal combustion engine 11 and the high temperature side heat exchange unit 41. Therefore, the high-temperature side cooling water whose temperature has risen by absorbing the heat of the internal combustion engine 11 flows through the high-temperature side heat exchange section 41.

In the intake warm-up mode, the low-temperature side cooling water does not circulate in the low-temperature side cooling circuit 30, so that the temperature of the low-temperature side cooling water inside the low-temperature side heat exchange unit 31 is substantially equal to the outside air temperature. Therefore, when the supercharged intake air passes through the low temperature side heat exchange unit 31, heat exchange is performed between the low temperature side cooling water inside the low temperature side heat exchange unit 31 and the supercharged intake air, but the supercharged intake air The temperature never rises above the outside temperature. Then, when the supercharged intake air that has passed through the low temperature side heat exchange unit 31 passes through the high temperature side heat exchange unit 41, heat is exchanged between the high temperature side cooling water inside the high temperature side heat exchange unit 41 and the supercharged intake air. By performing this, the supercharged intake air can be raised in temperature.

Specifically, with respect to the conventional configuration and the configuration of the present embodiment, the temperature Twh of the high-temperature side cooling water in the two-temperature heat exchange module 50, the temperature Twc of the low-temperature side cooling water, and the two-temperature heat exchange module 50 As a result of experimentally measuring the temperature Ta of the intake air passing through the above, graphs as shown in FIGS. 5 and 6 were obtained. In the graphs shown in FIGS. 5 and 6, the initial temperature of each of the intake air temperature Ta and the low temperature side cooling water temperature Twc is a predetermined temperature T10, and the initial temperature of the high temperature side cooling water temperature Twh is predetermined. It shows the experimental result when the temperature is T20.

In the conventional configuration, the temperature Twh of the high-temperature side cooling water in the two-temperature heat exchange module 50, the temperature Twc of the low-temperature side cooling water, and the temperature Ta of the intake air passing through the two-temperature heat exchange module 50 are shown in FIG. It changes so that it can be done. As shown in FIG. 5, in the conventional configuration, the time when the intake air temperature Ta reaches the temperature threshold value Tth is the time t11 when the predetermined time T1 elapses from the test start time t10.

On the other hand, in the configuration of the present embodiment, the temperature Twh of the high temperature side cooling water in the two temperature heat exchange module 50, the temperature Twc of the low temperature side cooling water, and the temperature Ta of the intake air passing through the two temperature heat exchange module 50 are set. The transition is as shown in FIG. As shown in FIG. 6, in the configuration of the present embodiment, the time when the intake air temperature Ta reaches the temperature threshold value Tth is the time t12 when the predetermined time T2 has elapsed from the test start time t10. Therefore, as compared with the conventional configuration, in the configuration of the present embodiment, the temperature Ta of the supercharged intake air reaches the temperature threshold value Tth earlier. That is, the configuration of the present embodiment makes it possible to raise the temperature of the supercharged intake air earlier.

According to the vehicle fluid circuit system 60 of the present embodiment described above, the actions and effects shown in the following (1) to (5) can be obtained.
(1) In the intake passage 110, the low temperature side heat exchange unit 31 is arranged on the upstream side of the high temperature side heat exchange unit 41 in the intake flow direction A. According to such a configuration, since the intake air heated through the high temperature side heat exchange unit 41 does not exchange heat with the low temperature side heat exchange unit 31, it is possible to raise the temperature of the intake air at an early stage.

(2) The low temperature side heat exchange unit 31 and the high temperature side heat exchange unit 41 are arranged between the supercharger 20 and the internal combustion engine 11 in the intake passage 110. According to such a configuration, the high-temperature side cooling water flowing through the high-temperature side heat exchange unit 41 is less likely to evaporate, so that thermal strain and corrosion of the plate member 500 can be suppressed.

(3) In the intake warm-up mode, the switching unit 44 causes the high-temperature side cooling water to flow through the internal combustion engine 11 and the high-temperature side heat exchange unit 41 and flows through the high-temperature side radiator 42, as shown by the solid arrows in FIG. Do not run cooling water on the high temperature side. Further, in the intake cooling mode, as shown by the solid line and the broken line arrow in FIG. 1, the switching unit 44 causes the high temperature side cooling water to flow through the high temperature side radiator 42 and the internal combustion engine 11, and the high temperature side heat exchange unit 41. Do not let the cooling water on the high temperature side flow into the engine. In the present embodiment, the intake air warm-up mode corresponds to the first flow state, and the intake air cooling mode corresponds to the second flow state. According to such a configuration, in the intake air warm-up mode, the high-temperature side cooling water flows between the internal combustion engine 11 and the high-temperature side heat exchange unit 41, so that the warm air of the internal combustion engine 11 and the temperature rise of the supercharged intake air can be increased. It becomes possible to do it effectively. Further, in the intake air cooling mode, the high temperature side cooling water flows between the high temperature side radiator 42 and the internal combustion engine 11, so that the internal combustion engine 11 can be effectively cooled.

(4) The control device 62 stops the low temperature side pump 33 during the operation of the internal combustion engine 11 in the intake warm-up mode. As a result, the heat of the supercharged intake air is less likely to be absorbed by the low temperature side heat exchange unit 31, so that the temperature of the supercharged intake air can be raised more accurately.
(5) At least one slot 503 is formed between the low temperature side heat exchange section 31 and the high temperature side heat exchange section 41 in the plate member 500. Further, a gap is formed between the low temperature side outer fin 504a and the high temperature side outer fin 504b. According to these configurations, heat transfer between the low temperature side heat exchange unit 31 and the high temperature side heat exchange unit 41 can be suppressed.

(First modification)
Next, a first modification of the fluid circuit system 60 of the first embodiment will be described.
As shown in FIG. 7, the two-temperature heat exchange module 50 of this modified example is composed of a plate member 500 on which a linear high-temperature side flow path 502 is formed. As described above, the configuration of the two-temperature heat exchange module 50 can be changed as appropriate.

(Second modification)
Next, a second modification of the fluid circuit system 60 of the first embodiment will be described.
As shown in FIG. 8, the fluid circuit system 60 of this modification has a reserve tank 64 common to the low temperature side cooling circuit 30 and the high temperature side cooling circuit 40. In this way, the configuration of the fluid circuit system 60 can be changed as appropriate.

(Third modification example)
Next, a third modification of the fluid circuit system 60 of the first embodiment will be described.
The vehicle 10 of this modification is a so-called fuel cell vehicle that travels by driving an electric motor based on the electric power generated by the fuel cell. A fluid circuit system 60 as shown in FIG. 9, for example, can be mounted on such a vehicle 10. As shown in FIG. 9, a compressor 12 and a two-temperature heat exchange module 50 are arranged in an intake passage 110 for supplying air to the fuel cell 13. The compressor 12 compresses the air supplied to the fuel cell 13.

Further, in the low temperature side cooling circuit 30, an inverter cooler 35 is provided between the low temperature side pump 33 and the low temperature side heat exchange unit 31. The fuel cell vehicle 10 is provided with an inverter device that converts the DC power stored in the battery into AC power and supplies it to the electric motor. The inverter cooler 35 cools the inverter device by heat exchange between the cooling water on the low temperature side and the inverter device.

As described above, the configuration of the fluid circuit system 60 of the first embodiment can be applied to the fuel cell vehicle 10.
<Second Embodiment>
Next, the fluid circuit system 60 of the vehicle 10 of the second embodiment will be described. Hereinafter, the differences from the fluid circuit system 60 of the first embodiment will be mainly described.

As shown in FIG. 10, the vehicle 10 of this embodiment is further provided with an EGR system 70. The EGR system 70 includes an EGR passage 71 and an EGR cooler 72.
The EGR passage 71 is provided so as to connect a portion of the intake passage 110 on the upstream side of the compressor wheel 21 and a portion of the exhaust passage 111 on the downstream side of the turbine wheel 22. Therefore, the low temperature side heat exchange unit 31 and the high temperature side heat exchange unit 41 are arranged between the connection portion of the intake passage 110 with the EGR passage 71 and the internal combustion engine 11.

The EGR cooler 72 is provided in the middle of the EGR passage 71. A third bypass flow path 48 is connected to the EGR cooler 72. The third bypass flow path 48 extends from the switching portion 44 and is connected to a portion of the high temperature side annular flow path 45 located between the high temperature side radiator 42 and the high temperature side pump 43. The EGR cooler 72 is provided in the middle of the third bypass flow path 48.

The EGR system 70 is a system for reducing nitrogen oxides and improving fuel efficiency by returning a part of the exhaust gas flowing through the exhaust passage 111 as EGR gas to the intake passage 110 through the EGR passage 71. When the EGR gas passes through the EGR cooler 72, it is cooled by exchanging heat with the cooling water on the high temperature side.

According to the fluid circuit system 60 of the vehicle 10 of the present embodiment described above, the actions and effects shown in (6) below can be further obtained.
(6) When EGR gas is introduced into the intake passage 110 in an extremely low temperature environment, there is a concern that the intake pipes and the like constituting the intake passage 110 may be corroded due to the generation of condensed water containing the components of the EGR gas. In order to avoid this, in the EGR system 70, the EGR gas is introduced into the intake passage 110 on condition that the temperature of the intake air becomes equal to or higher than the temperature threshold value Tth shown in FIGS. 5 and 6, for example. .. In this respect, in the fluid circuit system 60 of the present embodiment, as shown in FIGS. 5 and 6, the temperature Ta of the supercharged intake air reaches the temperature threshold value Tth earlier than the conventional configuration. Therefore, according to the fluid circuit system 60 of the present embodiment, the EGR system 70 can be driven earlier, and corrosion of the intake pipe and the like due to the generation of condensed water can be suppressed.

<Third Embodiment>
Next, the fluid circuit system 60 of the vehicle 10 of the third embodiment will be described. Hereinafter, the differences from the fluid circuit system 60 of the first embodiment will be mainly described.
As shown in FIG. 11, the fluid circuit system 60 of the present embodiment is provided with switching units 80 and 81. The switching unit 80 is provided in a portion on the upstream side of the high temperature side heat exchange unit 41 in the annular flow path 45 of the high temperature side cooling circuit 40. The switching unit 80 is communicated with the portion on the upstream side of the low temperature side heat exchange unit 31 in the annular flow path 34 of the low temperature side cooling circuit 30 through the communication flow path 82. The switching unit 80 has a state in which the high-temperature side cooling water flowing through the high-temperature side cooling circuit 40 flows through the high-temperature side heat exchange unit 41 as shown by the solid arrow in FIG. 11, and as shown by the solid line arrow in FIG. It is possible to switch between a state in which the cooling water flowing through the low temperature side cooling circuit 30 flows through the high temperature side heat exchange unit 41. The switching unit 80 corresponds to a communication flow path switching unit that switches between opening and closing of the communication flow path 82.

The switching portion 81 is provided in a portion on the downstream flow side of the high temperature side heat exchange portion 41 in the annular flow path 45 of the high temperature side cooling circuit 40. The switching portion 81 is communicated with a portion on the downstream side of the low temperature side heat exchange portion 31 in the annular flow path 34 of the low temperature side cooling circuit 30 through the communication flow path 83. The switching unit 81 is in a state where the cooling water that has passed through the high temperature side heat exchange unit 41 flows through the high temperature side cooling circuit 40 as shown by the solid line arrow in FIG. 11, and the high temperature as shown by the solid line arrow in FIG. It is possible to switch to a state in which the cooling water that has passed through the side heat exchange unit 41 flows through the low temperature side cooling circuit 30. The switching unit 81 corresponds to a communication flow path switching unit that switches between opening and closing of the communication flow path 83.

The switching units 80 and 81 are controlled by the control device 62. Specifically, the control device 62 controls the switching units 80 and 81 so that the flow path indicated by the solid arrow in FIG. 11 is formed in the intake warm-up mode. Further, the control device 62 controls the switching units 80 and 81 so that the flow path indicated by the solid arrow in FIG. 12 is formed in the intake air cooling mode. That is, the switching units 80 and 81 open the communication flow paths 82 and 83 in the intake air cooling mode.

According to the fluid circuit system 60 of the vehicle 10 of the present embodiment described above, the actions and effects shown in (7) below can be further obtained.
(7) Since the flow path as shown by the solid arrow in FIG. 12 is formed in the intake air cooling mode, the low temperature side cooling water circulating in the low temperature side cooling circuit 30 flows into the high temperature side heat exchange unit 41. The high temperature side heat exchange unit 41 substantially has the function of the low temperature side heat exchange unit 31. As a result, the supercharged intake air cooled by the low temperature side heat exchange unit 31 is supplied to the internal combustion engine 11 without being heated by the high temperature side heat exchange unit 41, so that the supercharged intake air is cooled. Performance can be improved.

<Fourth Embodiment>
Next, the fluid circuit system 60 of the vehicle 10 of the fourth embodiment will be described. Hereinafter, the differences from the fluid circuit system 60 of the first embodiment will be mainly described.
As shown in FIG. 13, in the fluid circuit system 60 of the present embodiment, heat exchange between the low temperature side cooling water circulating in the low temperature side cooling circuit 30 and the high temperature side cooling water circulating in the high temperature side cooling circuit 40. The heat exchanger 90 is further provided. The low temperature side bypass flow path 91 and the high temperature side bypass flow path 92 are connected to the heat exchanger 90.

One end of the low temperature side bypass flow path 91 is connected to the switching portion 93. The switching unit 93 is provided between the low temperature side pump 33 and the low temperature side heat exchange unit 31 in the low temperature side annular flow path 34. The other end of the low temperature side bypass flow path 91 is provided between the switching portion 93 and the low temperature side heat exchange portion 31 in the low temperature side annular flow path 34. The switching unit 93 is in a state where the low temperature side cooling water discharged from the low temperature side pump 33 directly flows to the low temperature side heat exchange unit 31, and the low temperature side cooling water discharged from the low temperature side pump 33 is sent to the low temperature side bypass flow path 91. It is possible to switch between the flowing state and the flowing state.

One end of the high temperature side bypass flow path 92 is connected to the switching portion 94. The switching unit 94 is provided between the switching unit 44 in the first bypass flow path 46 and the high temperature side heat exchange unit 41. The other end of the high temperature side bypass flow path 92 is provided between the switching portion 94 and the high temperature side heat exchange portion 41 in the first bypass flow path 46. The switching unit 94 has a state in which the high-temperature side cooling water flowing from the switching unit 44 into the first bypass flow path 46 directly flows to the high-temperature side heat exchange unit 41 and a high-temperature side in which the switching unit 44 flows into the first bypass flow path 46. It is possible to switch between a state in which the cooling water flows through the high temperature side bypass flow path 92.

The switching units 93 and 94 are controlled by the control device 62. Specifically, the control device 62 controls the switching unit 94 so that the high-temperature side cooling water flows through the high-temperature side bypass flow path 92 in the intake air cooling mode. As a result, in the heat exchanger 90, heat exchange is performed between the high temperature side cooling water flowing through the high temperature side bypass flow path 92 and the low temperature side cooling water flowing through the low temperature side bypass flow path 91, thereby cooling the low temperature side. The high temperature side cooling water that has released heat to the water can be supplied to the high temperature side heat exchange unit 41. As a result, it is possible to prevent the temperature of the supercharged intake air from rising when the supercharged intake air cooled in the low temperature side heat exchange unit 31 passes through the high temperature side heat exchange unit 41. Therefore, the cooling performance of the supercharged intake air can be improved.

On the other hand, the control device 62 controls the switching unit 93 so that the low temperature side cooling water flows through the low temperature side bypass flow path 91 in the intake warm-up mode. As a result, in the heat exchanger 90, heat exchange is performed between the high temperature side cooling water flowing through the high temperature side bypass flow path 92 and the low temperature side cooling water flowing through the low temperature side bypass flow path 91, thereby cooling the high temperature side. The low temperature side cooling water that has absorbed heat from the water can be supplied to the low temperature side heat exchange unit 31. As a result, when the supercharged intake air passes through the low temperature side heat exchange unit 31, the supercharged intake air can be warmed up, so that the warming performance of the supercharged intake air can be improved.

According to the fluid circuit system 60 of the vehicle 10 of the present embodiment described above, the actions and effects shown in (8) below can be further obtained.
(8) In the fluid circuit system 60 of the present embodiment, the cooling performance of the supercharged intake air in the intake air cooling mode can be improved, and the warming performance of the supercharged intake air in the intake air warming mode can be improved.

<Other Embodiments>
In addition, each embodiment can also be implemented in the following embodiments.
The two-temperature heat exchange module 50 may further include a path changing member for switching whether or not the supercharged intake air is passed through the high temperature side heat exchange unit 41. As such a route changing member, for example, a door member 100 or the like as shown in FIG. 14 can be used. The two-temperature heat exchange module 50 shown in FIG. 14 has passed through an intake passage 101 for flowing supercharged intake air that has passed through the low temperature side heat exchange unit 31 to the high temperature side heat exchange unit 41 and a low temperature side heat exchange unit 31. An intake passage 102 is formed so that the supercharged intake air does not flow to the high temperature side heat exchange unit 41. By selectively enabling the intake passage 101 and the intake passage 102, the door member 100 switches whether or not to allow the supercharged intake air to pass through the high temperature side heat exchange unit 41. According to such a configuration, the cooling performance of the supercharged intake air can be improved by preventing the supercharged intake air from flowing to the high temperature side heat exchange unit 41 in the intake air cooling mode.

The two-temperature heat exchange module 50 includes a first plate member that constitutes the low-temperature side heat exchange unit 31 and a second plate member that is separate from the first plate member and constitutes the high-temperature side heat exchange unit 41. It may have a laminated structure of a first plate member and a second plate member.
The low temperature side outer fin 504a and the high temperature side outer fin 504b of the two-temperature heat exchange module 50 may be made of separate bodies.

-The control device 62 may stop the high temperature side pump 43 in the cooling mode.
-The internal combustion engine 11 is not limited to that mounted on an engine vehicle, but may be mounted on a hybrid vehicle or an electric vehicle. Some electric vehicles include a generator for charging the battery with electric power and an internal combustion engine for driving the generator. As the internal combustion engine of this electric vehicle, the internal combustion engine 11 of each embodiment can be used.

The control device 62 and methods thereof described in the present disclosure are provided by configuring a processor and memory programmed to perform one or more functions embodied by a computer program. It may be realized by a plurality of dedicated computers. The control device 62 and its control method described in the present disclosure may be realized by a dedicated computer provided by configuring a processor including one or more dedicated hardware logic circuits. The control device 62 and its control method according to the present disclosure are composed of 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 be realized by one or more dedicated computers. The computer program may be stored on a computer-readable non-transitional tangible recording medium as an instruction executed by the computer. The dedicated hardware logic circuit and the hardware logic circuit may be realized by a digital circuit including a plurality of logic circuits or an analog circuit.

-The present disclosure is not limited to the above specific examples. Specific examples described above with appropriate design changes 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 above-mentioned specific examples, and their arrangement, conditions, shape, and the like are not limited to those illustrated, and can be changed as appropriate. The combinations of the elements included in each of the above-mentioned specific examples can be appropriately changed as long as no technical contradiction occurs.

10: Vehicle 11: Internal combustion engine 20: Supercharger 30: Low temperature side cooling circuit (fluid circuit)
31: Low temperature side heat exchange unit 33: Low temperature side pump 40: High temperature side cooling circuit (fluid circuit)
41: High temperature side heat exchange unit 42: High temperature side radiator 43: High temperature side pump 44: Switching unit (high temperature side switching unit)
50: 2 temperature heat exchange module (composite heat exchanger)
60: Fluid circuit system 62: Control device (low temperature side control unit, high temperature side control unit)
71: EGR passage 80, 81: Switching part (communication flow path switching part)
82, 83: Communication flow path 110: Intake passage 500: Plate member 503: Slot 504a: Low temperature side outer fin (low temperature side fin)
504b: High temperature side outer fin (high temperature side fin)

Claims (16)

A plurality of heat exchange units (31, 41) corresponding to each of the plurality of different fluid circuits (30, 40) are arranged in the intake passage (110) leading to the internal combustion engine (11), and each heat exchange unit A vehicle fluid circuit system in which the temperature of the fluid flowing inside is different.
Of the plurality of heat exchange units, the heat exchange unit through which a predetermined fluid flows is the low temperature side heat exchange unit (31), and the heat exchange unit in which a fluid higher than the predetermined fluid flows is the high temperature side heat exchange unit (41). When
A vehicle fluid circuit system in which the low temperature side heat exchange section is arranged on the upstream side of the high temperature side heat exchange section in the intake passage in the direction of intake air flow. The intake passage is provided with a supercharger (20) that sends supercharged intake air to the internal combustion engine.
The vehicle fluid circuit system according to claim 1, wherein the low temperature side heat exchange unit and the high temperature side heat exchange unit are arranged between the supercharger and the internal combustion engine in the intake passage. An EGR passage (71) for introducing EGR gas is connected to the intake passage.
The vehicle fluid according to claim 1 or 2, wherein the low temperature side heat exchange unit and the high temperature side heat exchange unit are arranged between the connection portion of the intake passage with the EGR passage and the internal combustion engine. Circuit system. When the fluid circuit composed of the high temperature side heat exchange section is the high temperature side fluid circuit and the fluid flowing through the high temperature side fluid is the high temperature side fluid,
The high-temperature side fluid circuit is provided with a high-temperature side switching unit (44) capable of selectively switching between a state in which the high-temperature side fluid flows and a state in which the high-temperature side fluid does not flow in the high-temperature side heat exchange unit. The vehicle fluid circuit system according to any one of 3 to 3. In the high temperature side fluid circuit, the high temperature side heat exchange unit, the internal combustion engine, and a radiator (42) are arranged.
The high temperature side switching unit
A first distribution state in which the high temperature side fluid flows through the internal combustion engine and the high temperature side heat exchange unit, and the high temperature side fluid does not flow through the radiator.
The vehicle fluid circuit according to claim 4, wherein the fluid circuit of the vehicle is selectively switched between a second distribution state in which the high temperature side fluid flows through the radiator and the internal combustion engine and the high temperature side fluid does not flow through the high temperature side heat exchange section. system. When the fluid circuit composed of the low temperature side heat exchange section is referred to as the low temperature side fluid circuit (30),
The low temperature side fluid circuit is provided with a low temperature side pump (33) that circulates the fluid in the circuit.
A low temperature side control unit (62) for controlling the low temperature side pump is further provided.
The vehicle fluid circuit system according to any one of claims 1 to 5, wherein the low temperature side control unit stops the low temperature side pump when the internal combustion engine is operating. When the fluid circuit composed of the high temperature side heat exchange section is referred to as the high temperature side fluid circuit (40),
The high temperature side fluid circuit is provided with a high temperature side pump (43) that circulates the fluid in the circuit.
A high temperature side control unit (62) for controlling the high temperature side pump is further provided.
The vehicle fluid circuit system according to any one of claims 1 to 6, wherein the high temperature side control unit stops the high temperature side pump when the internal combustion engine is operating. The fluid circuit composed of the low temperature side heat exchange section is a low temperature side fluid circuit (30), the fluid flowing through the low temperature side fluid circuit is a low temperature side fluid, and the fluid circuit composed of the high temperature side heat exchange section is a high temperature. When using the side fluid circuit (40)
A communication flow path (82, 83) that connects the low temperature side fluid circuit and the high temperature side fluid circuit so that the low temperature side fluid flows through the high temperature side fluid circuit.
A communication flow path switching unit (80, 81) for switching between opening and closing of the communication flow path is provided.
The vehicle fluid circuit system according to any one of claims 1 to 7, wherein the communication flow path switching unit opens the communication flow path when cooling the intake air flowing through the intake passage. The vehicle fluid circuit system according to any one of claims 1 to 8, further comprising a composite heat exchanger (50) having the low temperature side heat exchange unit and the high temperature side heat exchange unit integrally. The vehicle fluid circuit system according to claim 9, wherein in the high temperature side heat exchange unit, the flow direction of the fluid flowing inside the heat exchange unit is orthogonal to the flow direction of the intake air. The fluid circuit system according to claim 9, wherein the high temperature side heat exchange unit is formed so that the flow direction of the fluid flowing inside the high temperature side heat exchange unit is turned at least once. The composite heat exchanger is
The first plate member constituting the low temperature side heat exchange portion and
It has a second plate member that is separate from the first plate member and constitutes the high temperature side heat exchange portion.
The fluid circuit system according to any one of claims 9 to 11, which comprises a laminated structure of the first plate member and the second plate member. The composite heat exchanger is
It has a plate member (500) in which the low temperature side heat exchange portion and the high temperature side heat exchange portion are integrally formed.
The vehicle fluid circuit system according to any one of claims 9 to 11, which comprises a laminated structure of the plate members. The vehicle fluid circuit system according to claim 13, wherein at least one slot (503) is formed in a portion of the plate member between the low temperature side heat exchange portion and the high temperature side heat exchange portion. The composite heat exchanger has a low temperature side fin corresponding to the low temperature side heat exchange section and a high temperature side fin corresponding to the high temperature side heat exchange section.
The vehicle fluid circuit system according to any one of claims 9 to 14, wherein the low temperature side fin and the high temperature side fin are separate bodies. The composite heat exchanger has a low temperature side fin (504a) corresponding to the low temperature side heat exchange section and a high temperature side fin (504b) corresponding to the high temperature side heat exchange section.
The vehicle fluid circuit system according to any one of claims 9 to 14, wherein a gap is formed between the low temperature side fin and the high temperature side fin.

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