WO2017086045A1 - Thermal management system - Google Patents

Abstract

A thermal management system (10) is provided with: a first flow channel (510), a part of which is heated by a condenser (110); a second flow channel (520), a part of which is cooled by an evaporator (120); a third flow channel (530), in which a heat medium to be supplied to a radiator (300) flows; a first valve device (410), to which one end of the first flow channel, one end of the second flow channel, and one end of the third flow channel are connected, and which switches a path in which the heat medium flows; and a second valve device (420), to which the other end of the first flow channel, the other end of the second flow channel, and the other end of the third flow channel are connected, and which switches a path in which the heat medium flows.

Description

Thermal management system Cross-reference of related applications

This application is based on Japanese Patent Application No. 2015-226554 filed on November 19, 2015, and claims the benefit of its priority. Which is incorporated herein by reference.

This disclosure relates to a thermal management system mounted on a vehicle.

By circulating the high-temperature heat medium heated by the condenser of the refrigeration cycle and the low-temperature heat medium cooled by the evaporator of the refrigeration cycle in the vehicle, the air conditioning of the vehicle, the cooling of various in-vehicle devices, etc. Thermal management systems that perform are known.

For example, in the heat management system described in Patent Document 1 below, a low-temperature heat medium is supplied to the cooler core of the air conditioner. When cooling by the air conditioner is performed, air cooled by heat exchange with the heat medium is blown into the passenger compartment. A high-temperature heat medium is supplied to the heater core of the air conditioner. When the heating operation by the air conditioner is performed, air heated by heat exchange with the heat medium is blown out into the passenger compartment. Furthermore, the air conditioner of the thermal management system can also perform an operation of simultaneously dehumidifying the air by the cooler core and heating the air by the heater core, that is, a dehumidifying heating operation.

In the above thermal management system, air conditioning of the vehicle interior is performed by an air conditioner, and cooling of in-vehicle devices such as an inverter and a motor generator is also performed. Each vehicle-mounted device is provided with a cooler in which a heat medium flow path is formed. A part of the heat medium circulating in the vehicle is also supplied to the cooler, thereby cooling the in-vehicle device.

JP 2013-230805 A

When the dehumidifying and heating operation is being performed, it is necessary to match the temperature of the air blown into the vehicle interior to the target temperature while appropriately exhibiting the dehumidifying performance of the cooler core and the heating performance of the heater core. According to a study by the inventors, the control of adjusting the surface temperature of the heater core by changing the rotation speed of the compressor included in the refrigeration cycle and making the temperature of the blown air coincide with the target temperature is performed by dehumidification. Knowledge that it is desirable for heating operation has been obtained.

At this time, if the surface temperature of the cooler core also changes with the change in the rotation speed of the compressor, the dehumidifying performance may be lowered. For this reason, it is necessary to adjust the heat absorption amount in the radiator so that the surface temperature of the cooler core is maintained at an appropriate temperature. The endothermic amount can be adjusted by changing the flow rate of the heat medium supplied to the radiator.

By the way, the heat management system described in Patent Document 1 is configured such that the flow rate of the heat medium supplied to the cooler core and the flow rate of the heat medium supplied to the radiator are adjusted by a single pump. ing.

For this reason, if the flow rate of the heat medium supplied to the radiator is changed so as to obtain an appropriate heat absorption amount, the flow rate of the heat medium supplied to the cooler core also changes simultaneously. As a result, the surface temperature of the cooler core changes, and the “appropriate heat absorption amount” at that time also changes, so that it becomes necessary to further change the flow rate of the heat medium supplied to the radiator. As a result, the surface temperature of the cooler core may become unstable.

Thus, in the conventional heat management system, the flow rate of the heat medium supplied to the radiator and the flow rate of the heat medium supplied to the air conditioner cannot be individually adjusted, and the performance of the air conditioner, particularly There was a problem that it was difficult to stably exhibit the performance during dehumidifying heating.

In order to solve such a problem, it is considered to connect a flow path for supplying a heat medium to a radiator and a flow path for supplying a heat medium to a cooler core in parallel rather than in series. available. Specifically, after a part of the heat medium supplied to the cooler core is also supplied to the radiator, a flow rate adjusting valve may be arranged in the middle of the flow path for supplying the heat medium to the radiator. Conceivable.

However, in that case, the pressure loss in the flow path for supplying the heat medium to the radiator becomes too large. For this reason, it is necessary to pump the heat medium by a large pump in order to fully exhibit the heat absorption performance of the radiator during high loads such as summer and winter. However, when a large pump is used, there is a problem that the cost of not only the pump but the entire system increases, such as the need to increase the pressure resistance of the hose that forms the flow path of the heat medium. .

The present disclosure has been made in view of the above problems found by the inventor, and the purpose thereof is the flow rate of the heat medium supplied to the radiator and the flow rate of the heat medium supplied to the air conditioner. Is to provide a heat management system that can suppress the increase in size of a pump that pumps a heat medium.

In order to solve the above problems, a thermal management system according to one aspect of the present disclosure is a thermal management system mounted on a vehicle, and includes a refrigeration cycle having a condenser and an evaporator, and a flow path through which a heat medium flows. A part of which is heated by a condenser, a first pump that is provided in the first channel and that pumps the heat medium, and a flow path through which the heat medium flows. A second flow path whose part is cooled by the evaporator, a second pump provided in the second flow path for pumping the heat medium, and air supplied to the passenger compartment through the first flow path Supplied to the radiator, an air conditioner that heats or cools by heat exchange with the heat medium that flows through the second flow path, a radiator that heat-exchanges the heat medium that flows through the air conditioner, and the outside air, and the radiator A third flow path that is a flow path through which the heat medium flows, and a third flow path, A first pump that switches a path through which a heat medium flows, wherein a third pump that pumps the body, one end of the first flow path, one end of the second flow path, and one end of the third flow path are connected to each other. A second valve device that is connected to the other end of the first flow path, the other end of the second flow path, and the other end of the third flow path, and switches a path through which the heat medium flows; And a control device that controls the overall operation of the thermal management system.

In such a heat management system, the third flow path is connected to a position parallel to the first flow path and the second flow path. The flow rate of the heat medium supplied to the air conditioner is adjusted by the rotational speed of the first pump or the second pump. On the other hand, the flow rate of the heat medium supplied to the radiator is adjusted by a third pump provided separately from the first pump and the second pump.

Therefore, it is possible to individually adjust the flow rate of the heat medium supplied to the radiator and the flow rate of the heat medium supplied to the air conditioner. As a result, it is possible to perform the control for ensuring the heat absorption amount and the heat radiation amount in the radiator and the control for making the temperature of the air blown out from the air conditioner coincide with the target temperature and stabilize them independently of each other. Become.

In the heat management system, the heat medium is pumped to the radiator by a third pump that is provided separately from the pump that pumps the heat medium toward the air conditioner. Thus, since the heat medium is circulated by a plurality of pumps instead of a single pump, the load required for each pump is reduced. For this reason, it is not necessary to enlarge the pump.

According to the present disclosure, it is possible to individually adjust the flow rate of the heat medium supplied to the radiator and the flow rate of the heat medium supplied to the air conditioner, and the size of the pump that pumps the heat medium is increased. A thermal management system capable of suppressing the above is provided.

FIG. 1 is a diagram illustrating an overall configuration of a thermal management system according to the first embodiment. FIG. 2 is a diagram illustrating the flow of the heat medium during heating or dehumidifying heating. FIG. 3 is a diagram illustrating the flow of the heat medium during cooling. FIG. 4 is a flowchart showing a flow of processing executed by the control device. FIG. 5 is a flowchart showing the flow of processing executed by the control device. FIG. 6 is a flowchart showing a flow of processing executed by the control device. FIG. 7 is a diagram illustrating an overall configuration of a thermal management system according to the second embodiment. FIG. 8 is a diagram illustrating the flow of the heat medium during heating or dehumidifying heating. FIG. 9 is a diagram illustrating the flow of the heat medium during cooling. FIG. 10 is a diagram illustrating an overall configuration of a thermal management system according to the third embodiment. FIG. 11 is a diagram illustrating the flow of the heat medium during heating or dehumidifying heating. FIG. 12 is a diagram illustrating the flow of the heat medium during cooling.

Hereinafter, the present embodiment will be described with reference to the accompanying drawings. In order to facilitate the understanding of the description, the same constituent elements in the drawings will be denoted by the same reference numerals as much as possible, and redundant description will be omitted.

The configuration of the thermal management system 10 according to the first embodiment will be described with reference to FIG. The thermal management system 10 is mounted on a vehicle (not shown), and is configured as a system for performing air conditioning in the vehicle interior, cooling various in-vehicle devices provided in the vehicle, and the like. In the present embodiment, the vehicle is an electric vehicle. That is, it is a vehicle that does not have an internal combustion engine and travels by the driving force of the rotating electrical machine.

The thermal management system 10 includes a refrigeration cycle 100, an air conditioner 200, a radiator 300, an inverter cooler E1, a battery cooler E2, a first valve device 410, a second valve device 420, and a control device 20. It is equipped with.

The refrigeration cycle 100 is a device for heating and cooling a heat medium circulating in the heat management system 10. In the present embodiment, an antifreeze liquid mainly composed of ethylene glycol is used as the heat medium. The refrigeration cycle 100 includes a circulation channel 101, a compressor 130, an expansion valve 140, a condenser 110, and an evaporator 120.

The circulation channel 101 is a channel through which the refrigerant of the refrigeration cycle 100 circulates. For example, carbon dioxide is used as the refrigerant.

The compressor 130 is a device for pumping the refrigerant and circulating it in the circulation channel 101, and is provided in the middle of the circulation channel 101. The rotation speed of the compressor 130 is controlled by the control device 20 described later. That is, the flow rate of the refrigerant circulating in the circulation channel 101 is controlled by the control device 20.

The expansion valve 140 is an orifice provided in the middle of the circulation channel 101. The flow passage cross-sectional area of the circulation flow passage 101 is locally reduced in the expansion valve 140. For this reason, when the compressor 130 operates and the refrigerant circulates, the refrigerant pressure is higher in the downstream portion of the circulation flow path 101 than the compressor 130, and the compressor 130 in the circulation flow path 101. In the upstream side portion, the pressure of the refrigerant is low.

The condenser 110 is provided in the circulation channel 101 at a position downstream of the compressor 130 and upstream of the expansion valve 140. When the compressor 130 operates and the refrigerant circulates through the circulation channel 101, the refrigerant changes from the gas phase to the liquid phase inside the condenser 110, and increases its temperature. For this reason, the condenser 110 becomes high temperature.

A part of piping constituting a first flow path 510 described later is attached to the outside of the condenser 110. For this reason, when the condenser 110 is at a high temperature as described above, a part of the first flow path 510 is heated by the condenser 110, and the heat medium flowing inside the first flow path 510 is also heated. As the rotation speed of the compressor 130 increases, that is, as the flow rate of the refrigerant circulating in the circulation flow path 101 increases, the amount of heat given from the condenser 110 to the first flow path 510 also increases.

The evaporator 120 is provided in a position that is upstream of the compressor 130 and downstream of the expansion valve 140 in the circulation channel 101. When the compressor 130 operates and the refrigerant circulates in the circulation channel 101, the refrigerant changes from the liquid phase to the gas phase inside the evaporator 120, and the temperature is lowered. For this reason, the evaporator 120 becomes low temperature.

A part of piping constituting a second flow path 520 described later is attached to the outside of the evaporator 120. For this reason, when the evaporator 120 is at a low temperature as described above, a part of the second flow path 520 is cooled by the evaporator 120 and the heat medium flowing inside the second flow path 520 is also cooled. As the number of rotations of the compressor 130 increases, that is, as the flow rate of the refrigerant circulating in the circulation channel 101 increases, the amount of heat taken away from the second channel 520 by the evaporator 120 also increases.

The air conditioner 200 is an apparatus for performing air conditioning of the passenger compartment by heating or cooling the air and then blowing the air into the passenger compartment. The air conditioner 200 includes a casing 201, a blower 202, a heater core 210, and a cooler core 220.

The casing 201 is a container in which a flow path through which air passes is formed. A temperature sensor 203 is provided on the air outlet side (the right side in FIG. 1) of the casing 201. The temperature sensor 203 is a sensor for measuring the temperature of air blown from the air conditioner 200 into the vehicle interior. The temperature measured by the temperature sensor 203 is transmitted to the control device 20.

The casing 201 is provided with an air mix door (not shown). By the operation of the air mix door, a cooling state in which the air that has passed through the cooler core 220 is blown out without passing through the heater core 210, and a heating state in which the air that has passed through the cooler core 220 is also blown out after passing through the heater core 210, Is switched. In addition, since the structure and operation | movement of such an air mix door are well-known, the specific description is abbreviate | omitted.

The blower 202 is a device for creating a flow of air blown into the passenger compartment, and is provided on the air inlet side (the left side in FIG. 1) of the casing 201. The operation of the blower 202 is controlled by the control device 20. When the blower 202 is operated, the air sent out from the blower 202 flows through the inside of the casing 201 and then blown into the vehicle interior.

The heater core 210 is a heat exchanger for heating the air flowing in the casing 201. The heater core 210 is disposed in the casing 201 at a position near the outlet.

The heater core 210 is supplied with a high-temperature heat medium flowing through the first flow path 510, that is, a high-temperature heat medium heated by the condenser 110. In the heater core 210, heat exchange between the high-temperature heat medium and the air flowing in the casing 201 is performed, whereby the air is heated. As already described, the amount of heat given from the condenser 110 to the first flow path 510 increases as the rotational speed of the compressor 130 increases. Along with this, the temperature of the heat medium passing through the heater core 210 rises, and the temperature of the air blown out from the air conditioner 200 also rises.

The cooler core 220 is a heat exchanger for cooling the air flowing in the casing 201. Further, when the air passes through the cooler core 220, moisture contained in the air is condensed. For this reason, the cooler core 220 can also be said to dehumidify the air flowing in the casing 201. The cooler core 220 is disposed in the casing 201 at a position upstream of the heater core 210 in the air flow direction (the direction indicated by the arrow AR1 in FIG. 1).

The cooler core 220 is supplied with a low-temperature heat medium flowing through the second flow path 520, that is, a low-temperature heat medium cooled by the evaporator 120. In the cooler core 220, heat exchange between the low-temperature heat medium and the air flowing in the casing 201 is performed, thereby cooling the air. As already described, the amount of heat taken away from the second flow path 520 by the evaporator 120 increases as the rotational speed of the compressor 130 increases. Along with this, the temperature of the heat medium passing through the cooler core 220 decreases, and the temperature of the air reaching the heater core 210 also decreases.

The cooler core 220 is provided with a temperature sensor 221 for measuring the surface temperature. The surface temperature of the cooler core 220 measured by the temperature sensor 221 is transmitted to the control device 20.

The radiator 300 is a heat exchanger for exchanging heat between the heat medium circulating in the heat management system 10 and the outside air. As will be described later, by the operation of the first valve device 410 and the second valve device 420, a heat dissipation state in which a high-temperature heat medium is supplied to the radiator 300, and a heat absorption state in which a low-temperature heat medium is supplied to the radiator 300, Are switched.

In the heat dissipation state, the heat of the heat medium that has become high temperature through the condenser 110 and the heater core 210 is released to the outside air. For this reason, the temperature of the heat medium decreases when passing through the radiator 300. When the vehicle interior is cooled by the air conditioner 200, a heat dissipation state is established.

In the endothermic state, heat from the outside air is taken into the heat medium that has passed through the evaporator 120 and the cooler core 220 and has become low temperature. For this reason, the heat medium increases its temperature when passing through the radiator 300. When the vehicle interior is heated by the air conditioner 200, an endothermic state is established.

The radiator 300 is provided with an electric fan 301. The electric fan 301 is a device for adjusting the flow rate of outside air passing through the radiator 300. The rotational speed of the electric fan 301 is controlled by the control device 20.

The inverter cooler E1 is a heat exchanger for adjusting the temperature of an inverter (not shown) mounted on the vehicle, and is attached to the inverter. The inverter is a power converter that converts DC power supplied from a storage battery (not shown) mounted on the vehicle into AC power and supplies the AC power to the rotating electrical machine.

The inverter cooler E1 is supplied with a high-temperature heat medium flowing through the first flow path 510 or a low-temperature heat medium flowing through the second flow path 520. The inverter cooler E1 performs heat exchange between the heat medium and the inverter. When the high-temperature heat medium is supplied to the inverter cooler E1, the inverter is warmed up. When the low-temperature heat medium is supplied to the inverter cooler E1, the inverter is cooled. Which heat medium is supplied to the inverter cooler E1 is switched by the operation of the first valve device 410 and the like to be described later.

The battery cooler E2 is a heat exchanger for adjusting the temperature of the storage battery mounted on the vehicle, and is attached to the storage battery. The storage battery is for storing electric power necessary for traveling of the vehicle.

Like the inverter cooler E1, the battery cooler E2 is also supplied with a high-temperature heat medium that has flowed through the first flow path 510 or a low-temperature heat medium that has flowed through the second flow path 520. Heat exchange between the heat medium and the storage battery is performed by the battery cooler E2. When the high-temperature heat medium is supplied to the battery cooler E2, the storage battery is warmed up. When the low-temperature heat medium is supplied to the battery cooler E2, the storage battery is cooled. Which heat medium is supplied to the battery cooler E2 is switched by the operation of the first valve device 410 and the like.

Prior to the description of the first valve device 410 and the second valve device 420, the flow path through which the heat medium circulates in the heat management system 10 will be described. The heat management system 10 includes a first flow path 510, a second flow path 520, a third flow path 530, a heater core flow path 550, and a cooler core flow path 540 as flow paths through which the heat medium flows. An inverter flow path 560 and a storage battery flow path 570 are provided. These are all configured by piping arranged inside the vehicle. The piping is partially formed of metal and partially formed of resin.

The first flow path 510 is a flow path for heating the heat medium flowing inside by the condenser 110. As already described, a part of the piping constituting the first flow path 510 is attached to the outside of the condenser 110. A first pump P <b> 1 is provided in a position on the upstream side of the condenser 110 in the first flow path 510. The first pump P1 is a pump for pumping the heat medium so that the heat medium flows through the first flow path 510. The number of rotations of the first pump P1 is controlled by the control device 20. That is, the flow rate of the heat medium flowing through the first flow path 510 and passing through the condenser 110 is controlled by the control device 20.

The second flow path 520 is a flow path for cooling the heat medium flowing inside by the evaporator 120. As already described, a part of the piping constituting the second flow path 520 is attached to the outside of the evaporator 120. A second pump P <b> 2 is provided in a position on the upstream side of the evaporator 120 in the second flow path 520. The second pump P <b> 2 is a pump for pumping the heat medium so that the heat medium flows through the second flow path 520. The rotation speed of the second pump P2 is controlled by the control device 20. That is, the flow rate of the heat medium that flows through the second flow path 520 and passes through the evaporator 120 is controlled by the control device 20.

The third channel 530 is a channel through which the heat medium supplied to the radiator 300 flows. In the present embodiment, the radiator 300 is provided in the middle of the third flow path 530. A third pump P3 is provided in a position on the upstream side of the radiator 300 in the third flow path 530. That is, in the third flow path 530, the radiator 300 and the third pump P3 are arranged in series. The third pump P3 is a pump for pumping the heat medium so that the heat medium flows through the third flow path 530. The rotation speed of the third pump P3 is controlled by the control device 20. That is, the flow rate of the heat medium flowing through the third flow path 530 and passing through the radiator 300 is controlled by the control device 20.

The heater core channel 550 is a channel through which the heat medium supplied to the heater core 210 flows. The heater core 210 is provided in the middle of the heater core flow path 550. The heat medium flows through the first flow path 510 described above, and then flows through the heater core flow path 550 via the first valve device 410. For this reason, the flow rate of the heat medium flowing through the heater core flow path 550 is adjusted by the first pump P <b> 1 provided in the first flow path 510.

The cooler core channel 540 is a channel through which the heat medium supplied to the cooler core 220 flows. The cooler core 220 is provided in the middle of the cooler core flow path 540. The heat medium flows through the cooler core flow path 540 via the first valve device 410 after flowing through the second flow path 520 described above. For this reason, the flow rate of the heat medium flowing through the cooler core channel 540 is adjusted by the second pump P <b> 2 provided in the second channel 520.

The inverter channel 560 is a channel through which the heat medium supplied to the inverter cooler E1 flows. The inverter cooler E1 is provided in the middle of the inverter flow path 560. The flow rate of the heat medium flowing through the inverter flow path 560 is adjusted by the opening degree of the first valve device 410 or the opening degree of the second valve device 420.

The storage battery channel 570 is a channel through which the heat medium supplied to the battery cooler E2 flows. The battery cooler E2 is provided in the middle of the storage battery flow path 570. The flow rate of the heat medium flowing through the storage battery flow path 570 is adjusted by the opening degree of the first valve device 410 or the opening degree of the second valve device 420.

The first valve device 410 is an electrically coupled multi-way valve. The first valve device 410 is formed with openings 411 and 412 that are inlets of the heat medium, and openings 413, 414, 415, 416, and 417 that are outlets of the heat medium. A downstream end portion of the first flow path 510 is connected to the opening 411. The downstream end of the second flow path 520 is connected to the opening 412. The opening 413 is connected to the upstream end of the third flow path 530. The upstream end of the cooler core channel 540 is connected to the opening 414. The upstream end of the heater core flow path 550 is connected to the opening 415. The upstream end of the inverter flow path 560 is connected to the opening 416. The upstream end of the storage battery flow path 570 is connected to the opening 417.

After flowing through the first flow path 510, at least a part of the high-temperature heat medium flowing into the first valve device 410 from the opening 411 is discharged from the opening 415 and supplied to the heater core 210. The first valve device 410 can also supply a part of the high-temperature heat medium to the radiator 300 from the opening 413 by switching the flow path formed inside. Also, a part of the high-temperature heat medium can be supplied to the inverter cooler E1 from the opening 416 or supplied to the battery cooler E2 from the opening 417.

After flowing through the second flow path 520, at least a part of the low-temperature heat medium flowing into the first valve device 410 from the opening 412 is discharged from the opening 414 and supplied to the cooler core 220. The first valve device 410 can also supply a part of the low-temperature heat medium to the radiator 300 from the opening 413 by switching the flow path formed inside. Further, a part of the low-temperature heat medium can be supplied from the opening 416 to the inverter cooler E1, or can be supplied from the opening 417 to the battery cooler E2.

As described above, a flow path through which a high-temperature heat medium flows and a flow path through which a low-temperature heat medium flows are formed inside the first valve device 410. However, each flow path is separated. For this reason, the high temperature heat medium and the low temperature heat medium do not merge in the first valve device 410.

In addition, as a specific configuration of the first valve device 410, a known configuration such as a configuration of a switching valve described in JP2013-230805A can be employed. Further, the first valve device 410 that functions as described above may be configured by combining a plurality of electric two-way valves, three-way valves, four-way valves, and the like.

The second valve device 420 is an electrically coupled multi-way valve similar to the first valve device 410. The second valve device 420 is formed with openings 421 and 422 that are outlets of the heat medium, and openings 423, 424, 425, 426, and 427 that are inlets of the heat medium. An upstream end of the first flow path 510 is connected to the opening 421. An upstream end of the second flow path 520 is connected to the opening 422. The downstream end of the third flow path 530 is connected to the opening 423. The downstream end of the cooler core channel 540 is connected to the opening 424. The downstream end of the heater core flow path 550 is connected to the opening 425. The downstream end of the inverter flow path 560 is connected to the opening 426. The downstream end of the storage battery flow path 570 is connected to the opening 427.

After flowing through the heater core flow path 550, at least a part of the high-temperature heat medium flowing into the second valve device 420 from the opening 425 is discharged from the opening 421 and flows through the first flow path 510. Further, when a high-temperature heat medium is supplied to the radiator 300, the second valve device 420 receives the heat medium from the opening 423 by switching the flow path formed inside. The heat medium merges with the heat medium flowing through the first flow path 510 and the heater core flow path 550.

Also, the second valve device 420 can receive the high-temperature heat medium flowing through the inverter cooler E1 from the opening 426 and can receive the high-temperature heat medium flowing through the battery cooler E2 from the opening 427. In this case, the heat medium joins the heat medium flowing through the first flow path 510 and the heater core flow path 550.

After flowing through the cooler core flow path 540, at least a part of the low-temperature heat medium flowing into the second valve device 420 from the opening 424 is discharged from the opening 422 and flows through the second flow path 520. When the low-temperature heat medium is supplied to the radiator 300, the second valve device 420 receives the heat medium from the opening 423 by switching the flow path formed inside. The heat medium joins the heat medium flowing through the second flow path 520 and the cooler core flow path 540.

Also, the second valve device 420 can receive the low-temperature heat medium that has flowed through the inverter cooler E1 from the opening 426, and can receive the low-temperature heat medium that has flowed through the battery cooler E2 from the opening 427. In this case, the heat medium joins the heat medium flowing through the second flow path 520 and the cooler core flow path 540.

As described above, the flow path through which the high-temperature heat medium flows and the flow path through which the low-temperature heat medium flow are formed inside the second valve device 420. However, each flow path is separated. For this reason, the high temperature heat medium and the low temperature heat medium do not merge inside the second valve device 420.

In addition, as a specific configuration of the second valve device 420 as described above, a known configuration such as a configuration of a switching valve described in Japanese Patent Application Laid-Open No. 2013-230805 can be employed. Further, the first valve device 410 that functions as described above may be configured by combining a plurality of electric two-way valves, three-way valves, four-way valves, and the like.

The control device 20 is a computer system that includes a CPU, ROM, RAM, and the like, and is configured as a device that controls the overall operation of the thermal management system 10. The control device 20 controls the operation of the various components described so far. For example, the control device 20 individually adjusts the rotation speed of the first pump P1, the rotation speed of the second pump P2, and the rotation speed of the third pump P3. That is, the flow rate of the heat medium passing through each is individually adjusted. Moreover, the flow path of the heat medium in the heat management system 10 is switched by switching the states of the first valve device 410 and the second valve device 420.

A path through which the heat medium flows in the entire heat management system 10 will be described. FIG. 2 shows the flow of the heat medium when the vehicle interior is heated by the air conditioner 200. In FIG. 2, a path through which a high-temperature heat medium heated by the condenser 110 flows is indicated by a solid line. A path through which a low-temperature heat medium cooled by the evaporator 120 flows is indicated by a one-dot chain line.

As indicated by the solid line, the high-temperature heat medium discharged from the condenser 110 sequentially flows through the first valve device 410, the heater core 210, the second valve device 420, and the first pump P1, and then returns to the condenser 110 again. It is.

In addition, in a period in which heating is performed, that is, in winter, in-vehicle equipment such as an inverter becomes low temperature, and warm-up is often required at start-up. For this reason, when warming up of an inverter etc. is required, a high temperature heat medium is supplied also to the inverter cooler E1 and the battery cooler E2. That is, the first valve device 410 and the second valve device 420 are configured such that a part of the high-temperature heat medium flowing into the first valve device 410 from the opening 411 flows through the inverter flow channel 560 and the storage battery flow channel 570. The state is switched.

In FIG. 2, the path through which the heat medium flows is indicated by a dotted line. Even when the heat medium flows through the inverter flow path 560 and the storage battery flow path 570, the flow of the heat medium indicated by the solid line and the alternate long and short dash line is maintained.

Note that the flow rate of the heat medium in the inverter flow path 560 controls the operation of at least one of the first valve device 410 and the second valve device 420, and the opening (416 or 426) connected to the inverter flow path 560. It is adjusted by changing the opening.

Similarly, the flow rate of the heat medium in the storage battery channel 570 controls the operation of at least one of the first valve device 410 or the second valve device 420, and the opening (417 or 427) connected to the storage battery channel 570. It is adjusted by changing the opening degree.

As indicated by the alternate long and short dash line, the low-temperature heat medium discharged from the evaporator 120 flows in order through the first valve device 410, the cooler core 220, the second valve device 420, and the second pump P2, and then returns to the evaporator 120 again. Returned.

Further, a part of the low-temperature heat medium that has flowed into the first valve device 410 is discharged from the opening 413, and then flows into the second valve device 420 from the opening 423 through the third pump P3 and the radiator 300 in order. The heat medium joins the heat medium flowing through the second flow path 520 and the cooler core flow path 540.

Thus, when heating by the air conditioner 200 is performed, a low-temperature heat medium is supplied to the radiator 300. In the radiator 300, heat exchange between the low-temperature heat medium and the outside air is performed, and the heat of the outside air is taken into the low-temperature heat medium. That is, in the radiator 300, heat necessary for heating is taken from outside air.

The state in which at least a part of the low-temperature heat medium that has flowed through the second flow path is supplied to the radiator 300, that is, the state in which the heat medium circulates in the path shown in FIG. 2 corresponds to the “heat absorption state” described above. To do.

When heating is performed, in the air conditioner 200, after the air is once cooled by heat exchange with the cooler core 220, the air is heated by heat exchange with the heater core 210. The air that has finally reached a high temperature is blown out from the air conditioner 200 into the passenger compartment.

At this time, by maintaining the temperature of the cooler core 220 at a temperature suitable for dehumidification, efficient dehumidification of air and heating of air can be performed simultaneously. Although air conditioning performed in this way is a kind of heating, in order to distinguish it from heating in which dehumidification is performed in an eventual manner, hereinafter, it is also referred to as “dehumidification heating”. The path through which the heat medium flows when dehumidifying heating is performed is the same as that shown in FIG. Control executed during dehumidifying heating will be described later.

FIG. 3 shows the flow of the heat medium when the vehicle interior is cooled by the air conditioner 200. Also in FIG. 3, a path through which a high-temperature heat medium heated by the condenser 110 flows is indicated by a solid line. A path through which a low-temperature heat medium cooled by the evaporator 120 flows is indicated by a one-dot chain line.

As indicated by the solid line, the high-temperature heat medium discharged from the condenser 110 sequentially flows through the first valve device 410, the heater core 210, the second valve device 420, and the first pump P1, and then returns to the condenser 110 again. It is.

Further, a part of the high-temperature heat medium that has flowed into the first valve device 410 is discharged from the opening 413, and then flows through the third pump P3 and the radiator 300 in order to flow into the second valve device 420 from the opening 423. The heat medium merges with the heat medium flowing through the first flow path 510 and the heater core flow path 550.

As indicated by the alternate long and short dash line, the low-temperature heat medium discharged from the evaporator 120 flows in order through the first valve device 410, the cooler core 220, the second valve device 420, and the second pump P2, and then returns to the evaporator 120 again. Returned.

In the period when cooling is performed, that is, in summer, the temperature of the in-vehicle devices such as the inverter is likely to rise, which may hinder the operation of the in-vehicle devices. For this reason, when the temperature of an inverter etc. becomes high, a low temperature heat medium is supplied also to the inverter cooler E1 and the battery cooler E2. That is, the first valve device 410 and the second valve device 420 are configured so that a part of the low-temperature heat medium flowing into the first valve device 410 from the opening 412 flows through the inverter flow channel 560 and the storage battery flow channel 570. The state is switched.

In FIG. 3, the path through which the heat medium flows is indicated by a dotted line. Even when the heat medium flows through the inverter flow path 560 and the storage battery flow path 570, the flow of the heat medium indicated by the solid line and the alternate long and short dash line is maintained.

As described above, when cooling by the air conditioner 200 is performed, a high-temperature heat medium is supplied to the radiator 300. In the radiator 300, heat exchange between the high-temperature heat medium and the outside air is performed, and the heat of the heat medium is released to the outside air. That is, in the radiator 300, the vehicle interior is cooled by releasing heat to the outside air.

The state in which at least a part of the high-temperature heat medium that has flowed through the first flow path is supplied to the radiator 300, that is, the state in which the heat medium circulates in the path shown in FIG. 3 corresponds to the “heat dissipation state” described above. To do.

When cooling is performed, the air conditioner 200 once cools the air by heat exchange with the cooler core 220. The air is guided through the air mix door, and is blown into the passenger compartment without passing through the heater core 210.

FIG. 4 shows a flow of processing executed by the control device 20 in order to switch between the heat absorption state and the heat dissipation state described so far. A series of processes shown in FIG. 4 is repeatedly executed every time a predetermined period elapses in a period in which air conditioning is performed by the air conditioner 200.

In the first step S01, it is determined whether or not the air conditioning performed by the air conditioner 200 is cooling. For example, when a switch or the like provided on the front panel of the vehicle is operated and “cooling” is selected, it is determined that cooling is performed. If it is determined that cooling is performed, the process proceeds to step S02.

In step S02, each of the first valve device 410 and the second valve device 420 is operated to switch to the heat dissipation state shown in FIG. As a result, a high-temperature heat medium flows through the radiator 300, and heat is radiated from the radiator 300.

In step S01, when it is not determined that cooling is performed, that is, when it is determined that heating is performed, the process proceeds to step S03. In step S03, each of the first valve device 410 and the second valve device 420 is operated to switch to the heat absorption state shown in FIG. As a result, a low-temperature heating medium flows through the radiator 300, and heat is absorbed from outside air in the radiator 300.

Referring to FIG. 5, the flow of processing executed by the control device 20 when dehumidification heating is performed by the air conditioner 200 will be described. A series of processes shown in FIG. 5 are repeatedly executed every time a predetermined period elapses in a period in which dehumidifying heating is performed.

In the first step S11, is the temperature measured by the temperature sensor 203, that is, the temperature of the air blown out from the air conditioner 200 into the vehicle interior (hereinafter also referred to as “blowing temperature”) below a predetermined target value? It is determined whether or not. The target value is an air conditioning target temperature set by a vehicle driver by operating a switch or the like provided on the front panel of the vehicle. Instead of such an aspect, the target value for keeping the vehicle interior comfortable may be an aspect that is automatically set by calculation performed by the control device 20.

In step S11, if the blowing temperature is lower than the target value, the process proceeds to step S12. In step S12, the rotation speed of the compressor 130 provided in the refrigeration cycle 100 is increased. As a result, the amount of heat generated in the condenser 110 increases, so that the temperature of the heat medium that reaches the heater core 210 through the first flow path 510 and the heater core flow path 550 increases. As a result, the blowing temperature also rises and approaches the target value.

In step S11, when the blowing temperature is equal to or higher than the target value, the process proceeds to step S13. In step S13, it is determined whether or not the blowing temperature exceeds a target value. If the blowout temperature does not exceed the target value, it means that the blowout temperature matches the target value, and the series of processing shown in FIG. 5 is terminated.

If the blowing temperature exceeds the target value, the process proceeds to step S14. In step S14, the rotation speed of the compressor 130 provided in the refrigeration cycle 100 is decreased. As a result, the amount of heat generated in the condenser 110 decreases, so that the temperature of the heat medium that reaches the heater core 210 through the first flow path 510 and the heater core flow path 550 decreases. As a result, the blowout temperature also decreases and approaches the target value.

As described above, at the time of dehumidifying heating, by adjusting the rotation speed of the compressor 130, the control for making the blowing temperature coincide with the target value is performed.

In addition, when the rotation speed of the compressor 130 is changed, not only the heat generation amount in the condenser 110 is changed as described above, but also the heat absorption amount in the evaporator 120 is changed. As a result, there is a concern that the surface temperature of the cooler core 220 changes and the dehumidifying performance cannot be exhibited.

Therefore, in the present embodiment, control is performed to keep the surface temperature of the cooler core 220 constant by adjusting the rotational speed of the third pump P3 as well. As a result, control is performed so that the temperature of the air blown out from the air conditioner 200 (the blown air temperature) matches the target value. A flow of processing executed by the control device 20 for the control will be described with reference to FIG. A series of processing shown in FIG. 6 is repeatedly executed every time a predetermined period elapses in parallel with the processing shown in FIG.

In the first step S21, it is determined whether or not the temperature measured by the temperature sensor 221, that is, the surface temperature of the cooler core 220 is below a predetermined target value. The target value is set in advance as a temperature at which the dehumidifying performance is appropriately exhibited in the cooler core 220. For example, when the surface temperature of the cooler core 220 is too low, the condensed water adhering to the surface of the cooler core 220 is frozen to form frost (so-called “frost”), and the flow of air passing through the casing 201 is obstructed. There is a possibility that. On the other hand, when the surface temperature of the cooler core 220 is too high, the condensed water adhering to the surface of the cooler core 220 evaporates, so that high-humidity air may be blown out into the vehicle interior. In order to prevent the above phenomenon, the target value for the surface temperature of the cooler core 220 is desirably set to about 0 ° C. to 10 ° C., for example.

In step S21, if the surface temperature of the cooler core 220 is lower than the target value, the process proceeds to step S22. In step S22, the rotation speed of the third pump P3 provided in the third flow path 530 is increased. As a result, the flow rate of the low-temperature heat medium passing through the radiator 300 increases, so that the amount of heat taken into the heat medium from the outside air in the radiator 300 increases. As a result, the surface temperature of the cooler core 220 rises and approaches the target value.

In step S21, when the surface temperature of the cooler core 220 is equal to or higher than the target value, the process proceeds to step S23. In step S23, it is determined whether or not the surface temperature of the cooler core 220 exceeds a target value. If the surface temperature of the cooler core 220 does not exceed the target value, it means that the surface temperature of the cooler core 220 matches the target value, and the series of processes shown in FIG.

If the surface temperature of the cooler core 220 exceeds the target value, the process proceeds to step S24. In step S24, the rotational speed of the third pump P3 is decreased. As a result, the flow rate of the low-temperature heat medium passing through the radiator 300 is reduced, so that the amount of heat taken into the heat medium from the outside air in the radiator 300 is reduced. As a result, the surface temperature of the cooler core 220 decreases and approaches the target value.

Thus, when the dehumidifying heating is performed, the surface temperature of the cooler core 220 is adjusted by the rotation speed of the third pump P3 while adjusting the blowing temperature by the rotation speed of the compressor 130. Thereby, the dehumidification performance and heating performance of the air conditioner 200 can be exhibited stably.

If the cooler core 220 and the radiator 300 are arranged in series in the flow path through which the low-temperature heat medium flows, the flow rate of the heat medium flowing through the cooler core 220 and the flow rate of the heat medium flowing through the radiator 300 are always the same. Will be. Therefore, when the flow rate of the heat medium flowing through the radiator 300 is adjusted in order to make the endothermic amount in the radiator 300 appropriate, the flow rate of the heat medium passing through the cooler core 220 changes accordingly.

In the cooler core 220, the phase change of the heat medium does not occur, so the sensible heat change occurs instead of the latent heat change. For this reason, when the flow rate of the heat medium passing through the cooler core 220 changes as described above, the temperature distribution on the surface of the cooler core 220 greatly changes accordingly. As a result, it is necessary to further change the flow rate of the heat medium flowing through the radiator 300 in order to make the surface temperature of the cooler core 220 coincide with the target value.

In other words, when the cooler core 220 and the radiator 300 are arranged in series with each other, the flow rate of the heat medium flowing through each cannot be individually adjusted. Since the optimum flow rate of the heat medium in the cooler core 220 and the optimum flow rate of the heat medium in the radiator 300 are different from each other, there is a problem that the surface temperature of the cooler core 220 becomes unstable in the above configuration. Become.

In contrast, in this embodiment, the cooler core 220 and the radiator 300 are connected in parallel to each other. Specifically, as shown in FIG. 1, a cooler core flow path 540 in which the cooler core 220 is provided in the middle, and a third flow path 530 in which the radiator 300 is provided in the middle include the first valve device 410 and The second valve device 420 is connected in parallel with the second valve device 420 interposed therebetween.

For this reason, as shown in FIG. 2, a part of the low-temperature heat medium circulating in the second flow path 520 and the cooler core flow path 540 is supplied to the radiator 300 through the third flow path 530. In such a configuration, it is not necessary to make the flow rate of the heat medium flowing through the cooler core 220 and the flow rate of the heat medium flowing through the radiator 300 coincide with each other, so that both can be adjusted individually.

In this embodiment, since it is not necessary to frequently change the flow rate of the heat medium flowing through the cooler core 220, fluctuations in the temperature distribution on the surface of the cooler core 220 are suppressed. In addition, since the flow rate of the heat medium flowing through the radiator 300 can be adjusted without affecting the flow rate of the heat medium flowing through the cooler core 220, the heat absorption performance of the radiator 300 can be sufficiently ensured. Furthermore, since the flow rate of the heat medium flowing through the inverter cooler E1 and the like can be adjusted without affecting the flow rate of the heat medium flowing through the cooler core 220, the cooling performance of the in-vehicle device can be sufficiently ensured.

By the way, in order to individually adjust the above two flow rates, it seems that the third pump P3 may be replaced with a flow rate adjusting valve in the configuration of FIG. In such a configuration, the flow rate of the heat medium flowing through the cooler core 220 can be adjusted by adjusting the rotational speed of the second pump P2. Moreover, the flow rate of the heat medium flowing through the radiator 300 can be adjusted by adjusting the opening degree of the flow rate adjusting valve.

However, in such a configuration, since the low-temperature heat medium is circulated only by the single second pump P2, the flow rate of the heat medium supplied to the radiator 300 is reduced. As a result, the heat absorption performance and the like of the radiator 300 are not sufficiently exhibited during high loads such as summer and winter. In order to sufficiently secure the flow rate of the heat medium flowing through the radiator 300, it is necessary to use a large capacity pump as the second pump P2.

However, the flow path (the first flow path 510 and the like) through which the heat medium flows is complicated, and the path is also relatively long due to routing in the vehicle. A plurality of first valve devices 410, inverter coolers E1, and the like are provided in the middle of the flow path. As a result, the pressure loss in the flow path through which the heat medium flows is relatively large.

Therefore, when a large-capacity pump is used as the second pump P2, the pressure of the heat medium becomes very high on the discharge side of the second pump P2. For this reason, a high breakdown voltage is required. On the other hand, on the suction side of the second pump P2, the pressure of the heat medium becomes very low. For this reason, for example, a part of resin piping which comprises the 2nd flow path 520 may be crushed by a negative pressure. Since some measures need to be taken on both the discharge side and the suction side, the overall cost of the heat management system 10 increases.

Furthermore, when a large-capacity pump is used as the second pump P2, there arises a problem that the operation efficiency is remarkably lowered when the flow rate of the heat medium is small. For example, when the load on the air conditioner 200 is small, such as in spring or autumn, electric power is wasted in the large-capacity second pump P2.

Such problems are not limited to heating or dehumidifying heating, but also occur during cooling. That is, when the third pump P3 is replaced with a flow rate adjustment valve, it is necessary to enlarge the first pump P1 particularly during cooling.

Therefore, in the present embodiment, the third pump P3 is provided in the middle of the third flow path 530, which is a flow path through which the heat medium supplied to the radiator 300 passes. That is, the third pump P3 is provided as a dedicated pump for supplying the heat medium to the radiator 300. In such a configuration, since the heat medium is circulated by the two pumps, it is not necessary to use a large pump as described above. In addition, in the flow path through which the heat medium passes, there is no possibility that the pressure is locally excessively high or low, and measures such as a high breakdown voltage are not required.

When an antifreeze liquid mainly composed of ethylene glycol is used as the heat medium as in the present embodiment, the viscosity of the heat medium increases at low temperatures, and the flow rate of the heat medium circulating in the third flow path 530 and the like. Tends to decrease. For this reason, this embodiment which circulates a low-temperature heat medium with two pumps exhibits a big effect especially in winter.

During heating or dehumidifying heating, it is necessary to increase the amount of heat absorbed by the radiator 300. For this reason, it is necessary to increase the flow rate of the low-temperature heat medium among the heat medium circulating in the heat management system 10. As shown in FIG. 2, at the time of heating or dehumidifying heating, a low-temperature heat medium is pumped and circulated by two pumps, the second pump P2 and the third pump P3.

Also, it is necessary to increase the heat radiation amount in the radiator 300 during cooling. For this reason, it is necessary to increase the flow rate of the high-temperature heat medium among the heat medium circulating in the heat management system 10. As shown in FIG. 3, during cooling, a high-temperature heat medium is pumped and circulated by two pumps, the first pump P1 and the third pump P3.

As described above, in the present embodiment, either the low-temperature heat medium or the high-temperature heat medium, which requires a larger flow rate, is configured to be supplementarily pumped by the third pump P3.

It should be noted that the flow rate of the heat medium pumped by the third pump P3 is smaller than the flow rate of the heat medium pumped by the second pump P2 during heating or dehumidifying heating. In other words, the rotation speed of the third pump P3 is controlled by the control device 20 so as to achieve such a flow rate.

Similarly, during cooling in a heat dissipation state, the flow rate of the heat medium pumped by the third pump P3 is smaller than the flow rate of the heat medium pumped by the first pump P1. In other words, the rotation speed of the third pump P3 is controlled by the control device 20 so as to achieve such a flow rate.

In any case, if the flow rate of the heat medium pumped by the third pump P3 becomes too large, the balance of the pressure and flow rate in the entire heat management system 10 is lost. The 3rd pump P3 is a pump used to the last to the last. For this reason, it is desirable to make the flow rate of the heat medium pumped by the third pump P3 smaller than the flow rate of the heat medium pumped by the main pump (that is, the first pump P1 or the second pump P2).

It should be noted that the distance between the first pump P1 and the third pump P3 along the flow path of the heat medium and the distance between the second pump P2 and the third pump P3 along the flow path of the heat medium are as much as possible. It is desirable to arrange the third pump P3 at a position where it becomes longer. Since the pressure of the heat medium in the flow path is dispersed, the above effect by using the third pump P3 as an auxiliary is more exhibited.

A thermal management system 10A according to the second embodiment will be described with reference to FIG. In the present embodiment, the heater core 210 of the air conditioner 200 is arranged in the middle of the first flow path 510, and there is no flow path corresponding to the heater core flow path 550 in the first embodiment. Further, the cooler core 220 of the air conditioner 200 is disposed in the middle of the second flow path 520, and there is no flow path corresponding to the cooler core flow path 540 in the first embodiment. Furthermore, in this embodiment, a common flow path 580 that connects the first valve device 410A and the second valve device 420A is provided. In the present embodiment, the configurations of the first valve device 410A and the second valve device 420A are also different from the first embodiment.

The thermal management system 10A according to the present embodiment is different from the thermal management system 10 in the above points, but is otherwise the same as the thermal management system 10 according to the first embodiment. Below, only a different part from 1st Embodiment is demonstrated.

The first valve device 410A is an electric coupled multi-way valve having the same configuration as the first valve device 410. In the first valve device 410A, openings 413A and 418A that are inlets of the heat medium and openings 411A, 412A, 416A, and 417A that are outlets of the heat medium are formed. The downstream end of the third flow path 530 is connected to the opening 413A. The downstream end of the common flow path 580 is connected to the opening 418A. The upstream end of the first flow path 510 is connected to the opening 411A. The upstream end of the second flow path 520 is connected to the opening 412A. The upstream end of the inverter flow path 560 is connected to the opening 416A. The upstream end of the storage battery flow path 570 is connected to the opening 417A.

Also in the present embodiment, a flow path through which a high-temperature heat medium flows and a flow path through which a low-temperature heat medium flow are formed inside the first valve device 410A. However, each flow path is separated. For this reason, the high temperature heat medium and the low temperature heat medium do not merge in the first valve device 410A.

The second valve device 420A is an electrically coupled multi-way valve having the same configuration as the second valve device 420. In the second valve device 420A, openings 423A and 428A that are outlets of the heat medium and openings 421A, 422A, 426A, and 427A that are inlets of the heat medium are formed. The upstream end of the third flow path 530 is connected to the opening 423A. The upstream end of the common flow path 580 is connected to the opening 428A. The downstream end of the first flow path 510 is connected to the opening 421A. The downstream end of the second flow path 520 is connected to the opening 422A. The downstream end of the inverter flow path 560 is connected to the opening 426A. The downstream end of the storage battery channel 570 is connected to the opening 427A.

Also in the present embodiment, a flow path through which a high-temperature heat medium flows and a flow path through which a low-temperature heat medium flow are formed inside the second valve device 420A. However, each flow path is separated. For this reason, the high temperature heat medium and the low temperature heat medium do not merge in the second valve device 420A.

The path through which the heat medium flows in the entire heat management system 10A will be described. FIG. 8 shows the flow of the heat medium when the vehicle interior is heated or dehumidified by the air conditioner 200. In FIG. 8, a path through which a high-temperature heat medium heated by the condenser 110 flows is indicated by a solid line. A path through which a low-temperature heat medium cooled by the evaporator 120 flows is indicated by a one-dot chain line.

As indicated by the solid line, the high-temperature heat medium discharged from the condenser 110 sequentially flows through the heater core 210, the second valve device 420A, the common flow path 580, the first valve device 410A, and the first pump P1, and again. Returned to the condenser 110. When in-vehicle equipment such as an inverter needs to be warmed, a high-temperature heat medium is also supplied to the inverter cooler E1 and the battery cooler E2. That is, the first valve device 410A and the second valve device 420A of the first valve device 410A and the second valve device 420A so that a part of the high-temperature heat medium flowing into the first valve device 410A from the opening 418A flows through the inverter flow channel 560 and the storage battery flow channel 570. The state is switched. In FIG. 8, the path through which the heat medium flows is indicated by a dotted line. Even when the heat medium flows through the inverter flow path 560 and the storage battery flow path 570, the flow of the heat medium indicated by the solid line and the alternate long and short dash line is maintained.

As indicated by the alternate long and short dash line, the low-temperature heat medium discharged from the evaporator 120 passes through the cooler core 220, the second valve device 420A, the third pump P3, the radiator 300, the first valve device 410A, and the second pump P2. It flows back to the evaporator 120 again.

FIG. 9 shows the flow of the heat medium when the vehicle interior is cooled by the air conditioner 200. Also in FIG. 9, the path through which the high-temperature heat medium heated by the condenser 110 flows is indicated by a solid line. A path through which a low-temperature heat medium cooled by the evaporator 120 flows is indicated by a one-dot chain line.

As indicated by the solid line, the high-temperature heat medium discharged from the condenser 110 sequentially flows through the heater core 210, the second valve device 420A, the third pump P3, the radiator 300, the first valve device 410A, and the first pump P1. Then, it is returned to the condenser 110 again.

As indicated by the alternate long and short dash line, the low-temperature heat medium discharged from the evaporator 120 flows in order through the cooler core 220, the second valve device 420A, the common flow path 580, the first valve device 410A, and the second pump P2. It is returned to the evaporator 120 again. When it is necessary to cool an in-vehicle device such as an inverter, a low-temperature heat medium is also supplied to the inverter cooler E1 and the battery cooler E2. That is, the first valve device 410A and the second valve device 420A of the first valve device 410A and the second valve device 420A so that a part of the low-temperature heat medium flowing into the first valve device 410A from the opening 418A flows through the inverter flow channel 560 and the storage battery flow channel 570. The state is switched. In FIG. 9, a path through which the heat medium flows is indicated by a dotted line. Even when the heat medium flows through the inverter flow path 560 and the storage battery flow path 570, the flow of the heat medium indicated by the solid line and the alternate long and short dash line is maintained.

As described above, also in the present embodiment, a low-temperature heat medium flows through the third flow path 530 and the radiator 300 during heating or dehumidifying heating. Further, a high-temperature heat medium flows through the third flow path 530 and the radiator 300 during cooling. In any case, the heat medium supplied to the radiator 300 is pumped by the third pump P3. Thereby, there exists an effect similar to the case of 1st Embodiment.

Furthermore, in the present embodiment, the heater core 210 and the condenser 110 are arranged in series in the first flow path 510. For this reason, all of the high-temperature heat medium heated by the condenser 110 is supplied to the heater core 210 without branching on the way. Thereby, the air heating performance by the heater core 210 is improved.

Similarly, in this embodiment, the cooler core 220 and the evaporator 120 are arranged in series in the second flow path 520. For this reason, all of the low-temperature heat medium cooled by the evaporator 120 is supplied to the cooler core 220 without branching on the way. Thereby, the air cooling performance by the cooler core 220 is improved.

Note that, in both the first embodiment and the second embodiment, the third pump P3 is disposed at a position upstream of the radiator 300. However, the position where the third pump P3 is disposed may be a position different from these. The third pump P3 may be arranged at any position as long as it is in the middle of the third flow path 530.

A thermal management system 10B according to the third embodiment will be described with reference to FIG. In the present embodiment, the radiator 300 is not disposed in the third flow path 530, and only the third pump P3 is disposed. The radiator 300 is disposed in the middle of a radiator flow path 531 provided separately from the third flow path 530. Furthermore, in the present embodiment, the configurations of the first valve device 410B and the second valve device 420B are also different from the first embodiment.

The thermal management system 10B according to the present embodiment is different from the thermal management system 10 in the above points, but is otherwise the same as the thermal management system 10 according to the first embodiment. Below, only a different part from 1st Embodiment is demonstrated.

The first valve device 410B is an electrically coupled multi-way valve having the same configuration as the first valve device 410. The first valve device 410B is formed with an opening 419 to which the upstream end of the radiator flow path 531 is connected. The downstream end of the third flow path 530 is connected to the opening 413 of the first valve device 410B.

Also in the present embodiment, a flow path through which a high-temperature heat medium flows and a flow path through which a low-temperature heat medium flows are formed in the first valve device 410B. However, each flow path is separated. For this reason, a high temperature heat medium and a low temperature heat medium do not merge in the 1st valve apparatus 410B.

The second valve device 420B is an electrically coupled multi-way valve having the same configuration as the second valve device 420. The second valve device 420B is formed with an opening 429 to which the downstream end of the radiator flow path 531 is connected. The upstream end of the third flow path 530 is connected to the opening 423 of the second valve device 420B.

Also in the present embodiment, a flow path through which a high-temperature heat medium flows and a flow path through which a low-temperature heat medium flows are formed inside the second valve device 420B. However, each flow path is separated. For this reason, a high temperature heat medium and a low temperature heat medium do not merge in the 2nd valve apparatus 420B.

The path through which the heat medium flows in the entire heat management system 10B will be described. FIG. 11 shows the flow of the heat medium when the vehicle interior is heated or dehumidified by the air conditioner 200. In FIG. 11, a path through which a high-temperature heat medium heated by the condenser 110 flows is indicated by a solid line. A path through which a low-temperature heat medium cooled by the evaporator 120 flows is indicated by a one-dot chain line.

The path through which the high-temperature heat medium discharged from the condenser 110 flows is the same as that in the first embodiment shown in FIG. 2 as indicated by the solid line and the dotted line.

A path through which a low-temperature heat medium flows will be described. As indicated by the one-dot chain line in FIG. 11, the low-temperature heat medium discharged from the evaporator 120 flows in order through the first valve device 410B, the cooler core 220, the second valve device 420B, and the second pump P2, and evaporates again. Returned to vessel 120.

Further, a part of the low-temperature heat medium flowing into the first valve device 410B is discharged from the opening 419, flows through the radiator flow path 531 and the radiator 300, and then flows into the second valve device 420B from the opening 429. The heat medium joins the heat medium flowing through the second flow path 520 and the cooler core flow path 540.

Furthermore, a part of the low-temperature heat medium flowing inside the second valve device 420B is discharged from the opening 423, flows through the third flow path 530 and the third pump P3, and then flows into the first valve device 410B. The heat medium joins the heat medium flowing through the second flow path 520 and the cooler core flow path 540.

FIG. 12 shows the flow of the heat medium when the vehicle interior is cooled by the air conditioner 200. Also in FIG. 12, a path through which a high-temperature heat medium heated by the condenser 110 flows is indicated by a solid line. A path through which a low-temperature heat medium cooled by the evaporator 120 flows is indicated by a one-dot chain line.

As indicated by the solid line, the high-temperature heat medium discharged from the condenser 110 sequentially flows through the first valve device 410B, the heater core 210, the second valve device 420B, and the first pump P1, and returns to the condenser 110 again. It is.

Further, part of the high-temperature heat medium that has flowed into the first valve device 410B is discharged from the opening 419, flows through the radiator flow path 531 and the radiator 300, and then flows into the second valve device 420B from the opening 429. The heat medium merges with the heat medium flowing through the first flow path 510 and the heater core flow path 550.

Furthermore, a part of the high-temperature heat medium flowing inside the second valve device 420B is discharged from the opening 423, flows through the third flow path 530 and the third pump P3, and then flows into the first valve device 410B. The heat medium merges with the heat medium flowing through the first flow path 510 and the heater core flow path 550.

The path through which the low-temperature heat medium discharged from the evaporator 120 flows is the same as that in the first embodiment shown in FIG. 3 as indicated by the alternate long and short dash line.

As described above, in the present embodiment, the radiator 300 and the third pump P3 are not disposed in the same flow path, but are disposed in the radiator flow path 531 and the third flow path 530, respectively. When the heat medium is pumped through the third flow path 530 by the third pump P3, the heat medium flows through the radiator flow path 531 and is supplied to the radiator 300. That is, the third flow path 530 in the present insulator form is also a flow path through which the heat medium supplied to the radiator 300 flows. Even with such a configuration, the same effects as those of the first embodiment can be obtained.

In the above description, an example in which an inverter and a storage battery in a vehicle-mounted device are heated or cooled by a heat medium has been described. The vehicle-mounted device heated or cooled by the heat medium may be a device other than the inverter or the storage battery. Examples of such in-vehicle devices include a motor generator, a transaxle, an oil cooler, an intercooler, an EGR cooler, an exhaust heat recovery machine, a fuel supply pipe, an intake path, an exhaust gas purification catalyst, and a throttle cooler. Also, the number of in-vehicle devices heated or cooled by the heat medium may be one of these, or three or more. In this case, a heat exchanger for equipment (in this embodiment, inverter cooler E1 and battery cooler E2) for heating or cooling the in-vehicle equipment, and piping for supplying a heat medium to the heat exchanger for equipment. (In this embodiment, the number of sets with the inverter flow path 560 and the storage battery flow path 570) is as many as the number of in-vehicle devices.

The equipment heat exchanger may be arranged in the middle of the first flow path 510 or in the middle of the second flow path 520. The heat exchanger for equipment should just be arrange | positioned in an appropriate place in consideration of the optimal temperature for vehicle equipment.

The heat absorption amount in the radiator 300 may be adjusted only by the rotation speed of the third pump P3, but may be adjusted by both the rotation speed of the third pump P3 and the rotation speed of the electric fan 301. Further, it may be adjusted by combining with the operation of a radiator shutter (not shown).

The embodiment has been described above with reference to specific examples. However, the present disclosure is not limited to these specific examples. Those in which those skilled in the art appropriately modify the design of these specific examples are also included in the scope of the present disclosure as long as they have the features of the present disclosure. Each element included in each of the specific examples described above and their arrangement, conditions, shape, and the like are not limited to those illustrated, and can be changed as appropriate. Each element included in each of the specific examples described above can be appropriately combined as long as no technical contradiction occurs.

Claims (15)

1. A thermal management system (10, 10A, 10B) mounted on a vehicle,
   A refrigeration cycle (100) having a condenser (110) and an evaporator (120);
   A first flow path (510, 510A, 510B) in which a heat medium flows, a part of which is heated by the condenser;
   A first pump (P1) provided in the first flow path and pumping the heat medium;
   A flow path through which the heat medium flows, a second flow path (520, 520A, 520B), part of which is cooled by the evaporator;
   A second pump (P2) provided in the second flow path to pump the heat medium;
   An air conditioner (200) for heating or cooling the air supplied to the passenger compartment by heat exchange with the heat medium passing through the first flow path and heat exchange with the heat medium flowing through the second flow path; ,
   A radiator (300) for exchanging heat between the heat medium flowing through the air conditioner and the outside air;
   A third flow path (530) that is a flow path through which the heat medium supplied to the radiator flows;
   A third pump (P3) provided in the third flow path and pumping the heat medium;
   One end of the first flow path, one end of the second flow path, and one end of the third flow path are connected to each other, and a first valve device (410, 410A, 410B)
   The other end of the first flow path, the other end of the second flow path, and the other end of the third flow path are connected to each other, and a second valve device (420) that switches a path through which the heat medium flows. , 420A, 420B),
   And a control device (20) for controlling the overall operation of the thermal management system.
2. The control device includes:
   The thermal management system according to claim 1, wherein the flow rate of the heat medium passing through each of the first pump, the second pump, and the third pump is individually adjusted by controlling the operations of the first pump, the second pump, and the third pump.
3. The air conditioner
   A heater core (210) for heating air by heat exchange with the heat medium flowing through the first flow path;
   A cooler core (220) for cooling air by heat exchange with the heat medium flowing through the second flow path,
   The thermal management system according to claim 2, wherein the cooler core is disposed on the upstream side in the air flow direction, and the heater core is disposed on the downstream side.
4. The control device includes:
   By controlling the respective operations of the first valve device and the second valve device,
   A heat dissipation state in which a part of the heat medium flowing through the first flow path flows through the third flow path;
   The thermal management system according to claim 3, wherein a part of the heat medium that has flowed through the second flow path is switched between an endothermic state in which the heat medium flows through the third flow path.
5. The control device includes:
   When the vehicle interior is cooled by the air conditioner, the heat dissipation state is established.
   The heat management system according to claim 4, wherein the operation of the first valve device and the second valve device is controlled so that the heat absorption state is achieved when the vehicle interior is heated by the air conditioner.
6. At the time of dehumidification heating in which dehumidification of air in the cooler core and heating of air in the heater core are performed simultaneously,
   The control device includes:
   The heat management system according to claim 5, wherein the heat absorption amount in the radiator is adjusted by controlling the operation of the third pump, and thereby, the control is performed so that the air temperature of the air conditioner matches the target temperature.
7. In the heat dissipation state, the control device
   The heat management system according to claim 4, wherein the operation of the third pump is controlled so that a flow rate of the heat medium passing through the third pump is smaller than a flow rate of the heat medium passing through the first pump.
8. In the endothermic state, the control device
   5. The heat management system according to claim 4, wherein the operation of the third pump is controlled such that a flow rate of the heat medium passing through the third pump is smaller than a flow rate of the heat medium passing through the second pump.
9. The thermal management system according to claim 3, wherein the heater core and the condenser are arranged in series in the first flow path.
10. The thermal management system according to claim 3, wherein the cooler core and the evaporator are arranged in series in the second flow path.
11. The vehicle-mounted device mounted on the vehicle further includes a device heat exchanger (E1, E2) for heating or cooling by heat exchange with the heat medium that has flowed through the first channel or the second channel, The thermal management system according to claim 1.
12. The control device includes:
    The heat management system according to claim 11, wherein a flow rate of a heat medium supplied to the equipment heat exchanger is adjusted by controlling an operation of at least one of the first valve device and the second valve device. .
13. The fourth flow path (560, 570), which is the flow path through which the heat medium supplied to the device heat exchanger flows, is separate from the first flow path, the second flow path, and the third flow path. It is provided as a flow path of
    The thermal management system according to claim 12, wherein one end of the fourth flow path is connected to the first valve device, and the other end of the fourth flow path is connected to the second valve device.
14. The heat management system according to claim 13, wherein a plurality of sets of the equipment heat exchanger and the fourth flow path are provided.
15. The heat management system according to claim 1, wherein the radiator and the third pump are arranged in series in the third flow path.

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