WO2018047540A1 - Device temperature adjusting apparatus - Google Patents

Abstract

The present invention provides a device temperature adjusting apparatus which is capable of improving cooling performance. This device temperature adjusting apparatus is mounted to a vehicle provided with an air-conditioning unit (41) which cools blown air using a cooling unit (50) provided in an air-conditioning case (44), and blows the air into a cabin. A heat absorption unit (14) causes a working fluid to absorb heat from a device (12) to be subjected to temperature adjustment. A heat release unit (16) causes the working fluid evaporated by the heat absorption unit (14) to release heat. An outward path part (18) connects a heat release unit discharge port (16b) through which the liquid-phase working fluid is discharged from the heat release unit (16), and a heat absorption unit inflow port (14b) through which the liquid-phase working fluid flows into the heat absorption unit (14). A return path part (20) connects a heat absorption unit discharge port (14c) through which the gas-phase working fluid is discharged from the heat absorption unit (14), and a heat release unit inflow port (16a) through which the gas-phase working fluid flows into the heat release unit (16). The heat release unit (16) and/or the outward path part (18) are/is provided with a contact part (161, 181) formed such that heat is exchanged between the working fluid flowing therein, and a condensate generated by the cooling unit (50).

Description

Equipment temperature controller Cross-reference to related applications

This application is based on Japanese Patent Application No. 2016-176785 filed on Sep. 9, 2016, the contents of which are incorporated herein by reference.

This disclosure relates to a device temperature control device that adjusts the temperature of a target device.

In recent years, a technique using a thermosiphon as a device temperature control device for adjusting the temperature of an electrical device such as a power storage device mounted on an electric vehicle such as an electric vehicle or a hybrid vehicle has been studied.

In the device temperature control device described in Patent Document 1, a heat absorption part provided in an upper part of a power storage device for a vehicle and a heat dissipation part provided above the heat absorption part are connected in an annular shape by two circulation paths. The refrigerant as the working fluid is sealed inside. When the power storage device self-heats, the liquid-phase refrigerant in the heat-absorbing part absorbs the heat and boils to flow into the heat-radiating part as a gas-phase refrigerant. The heat dissipation unit condenses the gas-phase refrigerant to generate a liquid-phase refrigerant. The liquid phase refrigerant is supplied to the heat absorption unit. The power storage device is cooled by such natural circulation of the refrigerant.

By the way, generally, since the temperature of the power storage device becomes high in the season when the outside air temperature is high such as summer, it is necessary to further cool the power storage device. Therefore, the device temperature control apparatus described in Patent Document 1 cools the heat dissipating part and condenses the refrigerant flowing inside the heat dissipating part by injecting washer liquid onto the heat dissipating part. If the condensation of the refrigerant by the heat dissipating part is promoted, it is possible to increase the cooling capacity of the device temperature control device.

JP 2016-105365 A

However, the apparatus temperature control device described in Patent Document 1 has a problem in that the number of times the washer liquid is replenished to the tank for storing the washer liquid increases in order to prevent the washer liquid from being depleted. In addition, the configuration for injecting the washer liquid to the heat radiating portion becomes complicated. Further, generally, since the tank for storing the washer liquid is disposed in the engine room, the temperature of the washer liquid becomes higher than the outside air temperature. For this reason, it is difficult to sufficiently cool the heat radiating portion only by spraying the washer liquid onto the heat radiating portion.

Also, in order to increase the cooling capacity of the equipment temperature control device, it is conceivable to increase the size of the heat dissipating part and to increase the area where the heat dissipating part is in contact with the outside air, thereby promoting the condensation of refrigerant by the heat dissipating part. However, when the physique of the heat dissipating part is enlarged, the mountability on the vehicle is deteriorated. Moreover, when cooling a thermal radiation part with external air, a thermal radiation part cannot be cooled below to external temperature. For this reason, it is difficult to increase the cooling capacity of the device temperature controller under conditions where the outside air temperature is high, such as in summer.

This disclosure aims to provide a device temperature control device capable of increasing the cooling capacity.

According to one aspect of the present disclosure, a cooling unit disposed in an air conditioning case is mounted on a vehicle including an air conditioning unit that cools blown air and blows air into a vehicle interior. The device temperature control device that adjusts the temperature of the target device by phase change
A heat absorbing part that evaporates the working fluid by absorbing heat from the target device to the working fluid;
A heat dissipating part that is provided above the heat absorbing part in the direction of gravity and that condenses the working fluid by dissipating the working fluid evaporated in the heat absorbing part;
A forward path portion that forms a forward flow path that connects a heat radiation portion discharge port that discharges the liquid-phase working fluid from the heat radiation portion and a heat absorption portion inlet that the liquid-phase working fluid flows into the heat absorption portion;
A heat return part discharge port for discharging the gas phase working fluid from the heat absorption part, and a return path part that forms a return flow path that connects the heat radiation part inlet port where the gas phase working fluid flows into the heat dissipation part, and
At least one of the heat dissipating part and the forward path part has a contact part configured to exchange heat between the working fluid flowing inside thereof and the condensed water generated in the cooling part.

As described above, it is necessary to further cool the target device in the season when the outside air temperature is high such as summer. On the other hand, in the season when the outside air temperature is high such as summer, the amount of condensed water generated in the cooling unit of the air conditioning unit increases. That is, the inventors focused on the fact that the time when the target device needs to be further cooled and the time when the amount of condensed water generated in the cooling unit of the air conditioning unit increases are common. Here, the temperature of the condensed water is generally lower than the temperature of the working fluid flowing inside at least one of the heat radiating section and the forward path section. Heat exchange between the condensed water and the working fluid that flows inside the contact portion of the device temperature control device facilitates condensation of the working fluid that flows inside the contact portion, and the working fluid is in a liquid phase. The temperature of the is lower. Therefore, it is possible to increase the flow rate of the liquid-phase working fluid supplied from the forward path portion to the heat absorption portion, and to reduce the temperature of the liquid-phase working fluid. Therefore, this device temperature control device can further increase the cooling capacity when it is necessary to further cool the target device.

Also, the condensed water generated in the cooling unit of the air conditioning unit is generated by the electric power used in the vehicle air conditioner. Therefore, by effectively using the condensed water for the device temperature control device, the cooling capacity of the device temperature control device can be efficiently increased without increasing the power consumption of the vehicle.

Also, by using the condensed water generated in the cooling unit of the air conditioning unit, it is possible to increase the amount of liquid-phase working fluid generated without increasing the size of the heat dissipation unit. Furthermore, since a mechanism for spraying a liquid such as a washer liquid is not required with respect to the technique described in Patent Document 1 described above, the configuration of the device temperature control device can be simplified.

It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 1st Embodiment. It is sectional drawing of the II-II line | wire of FIG. It is the schematic diagram which showed schematic structure of the refrigerating cycle which the air conditioner concerning 1st Embodiment has. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 2nd Embodiment. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 3rd Embodiment. It is typical sectional drawing which showed a part of apparatus temperature control apparatus concerning 4th Embodiment, and the schematic structure of an air conditioner. It is typical sectional drawing which showed a part of apparatus temperature control apparatus concerning 5th Embodiment, and schematic structure of an air conditioner. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 6th Embodiment. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 7th Embodiment. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 8th Embodiment. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 9th Embodiment. It is typical sectional drawing which showed a part of apparatus temperature control apparatus concerning 10th Embodiment, and schematic structure of an air conditioner. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 11th Embodiment. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 12th Embodiment. It is typical sectional drawing which showed schematic structure of the apparatus temperature control apparatus and air conditioner concerning 13th Embodiment.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be described with the same reference numerals.

(First embodiment)
The apparatus temperature control device of this embodiment is mounted on an electric vehicle (hereinafter simply referred to as “vehicle”) such as an electric vehicle or a hybrid vehicle. As shown in FIG. 1, the device temperature control device 10 functions as a cooling device that cools a secondary battery 12 (hereinafter referred to as “battery 12”) mounted on a vehicle.

First, the battery 12 as a target device to be cooled by the device temperature control device 10 will be described.

In a vehicle equipped with the device temperature control device 10, electric power stored in a power storage device (in other words, a battery pack) including the battery 12 as a main component is supplied to a vehicle travel motor via an inverter or the like. The battery 12 generates heat when the vehicle is used, such as when the vehicle is running. And if the battery 12 becomes high temperature, it not only can not exhibit a sufficient function, but also causes deterioration and breakage, so a cooling device for maintaining the battery 12 at a certain temperature or less is required.

In addition, in high seasons such as summer, the battery temperature rises not only when the vehicle is running but also when parked. Further, the battery 12 is often arranged under the floor of a vehicle or under a trunk room, and although the amount of heat per unit time given to the battery 12 is small, the battery temperature gradually rises when left for a long time. If the battery 12 is left in a high temperature state, the life of the battery 12 is shortened. Therefore, it is desired to maintain the battery temperature at a low temperature, for example, by cooling the battery 12 while the vehicle is left.

Furthermore, the battery 12 is configured as an assembled battery including a plurality of battery cells 121. However, if the temperature of each battery cell 121 varies, the deterioration of the battery cell 121 is biased, and the performance of the power storage device decreases. End up. This is because the input / output characteristics of the power storage device are determined in accordance with the characteristics of the battery cell 121 that is most deteriorated. Therefore, in order for the battery 12 to exhibit desired performance over a long period of time, it is important to equalize the temperature so as to reduce the temperature variation between the plurality of battery cells 121.

Further, generally, as another cooling device for cooling the battery 12, generally, air blowing by a blower, air cooling using the refrigeration cycle 1, water cooling, or a direct refrigerant cooling system is adopted. However, since the blower only blows air in the passenger compartment, the cooling capacity is low. Moreover, since the battery 12 is cooled by the sensible heat of the air by the blower by the blower, the temperature difference between the upstream and downstream of the air flow becomes large, and the temperature variation among the plurality of battery cells 121 cannot be sufficiently suppressed. In addition, although the refrigeration cycle method has a high cooling capacity, since the battery 12 is cooled by sensible heat of air or water in either air cooling or water cooling, temperature variations between the battery cells 121 cannot be sufficiently suppressed. Furthermore, driving the compressor or cooling fan of the refrigeration cycle 1 while the vehicle is parked is not preferable because it causes an increase in power consumption and noise.

From these backgrounds, the device temperature control apparatus 10 of the present embodiment adopts a thermosiphon system that adjusts the temperature of the battery 12 by natural circulation of the refrigerant, instead of forcibly circulating the refrigerant as the working fluid by the compressor. Yes.

Next, the configuration of the device temperature control device 10 will be described.

The device temperature control apparatus 10 includes a battery cooler 14 as a heat absorption unit, a heat radiation unit 16, an outward piping 18 as an outward path, and a return piping 20 as an inward path. The heat radiating section 16, the forward piping 18, the battery cooler 14, and the return piping 20 are connected in an annular shape to constitute a fluid circulation circuit 26 in which a refrigerant as a working fluid of the device temperature control device 10 circulates. Yes.

That is, the fluid circulation circuit 26 is a heat pipe that performs heat transfer by evaporation and condensation of the refrigerant. The fluid circulation circuit 26 is configured to be a loop thermosiphon (in other words, a thermosiphon circuit) in which a flow path through which a gas-phase refrigerant flows and a flow path through which a liquid-phase refrigerant flows are separated. In FIG. 1, an arrow DR <b> 1 indicates the direction of the vehicle on which the device temperature control device 10 is mounted. That is, the arrow DR1 indicates the vehicle vertical direction DR1. However, the vehicle vertical direction DR1 does not indicate the vertical direction in each configuration of the air conditioning unit 41 of the air conditioner 40.

The fluid circulation circuit 26 is filled with refrigerant. The fluid circulation circuit 26 is filled with the refrigerant. The refrigerant circulates in the fluid circulation circuit 26, and the device temperature adjustment device 10 adjusts the temperature of the battery 12 by the phase change between the liquid phase and the gas phase of the refrigerant. Specifically, the battery 12 is cooled by the phase change of the refrigerant.

The refrigerant filled in the fluid circulation circuit 26 is, for example, a fluorocarbon refrigerant such as HFO-1234yf or HFC-134a.

The battery cooler 14 of the device temperature control device 10 is a heat absorption unit that absorbs heat from the battery 12 to the refrigerant. In other words, the battery cooler 14 cools the battery 12 by transferring heat from the battery 12 to the refrigerant. The battery cooler 14 is made of a metal having high thermal conductivity, for example.

Specifically, a cooler chamber 14 a for storing a liquid phase refrigerant is formed inside the battery cooler 14. The battery cooler 14 absorbs heat from the battery 12 to the refrigerant in the cooler chamber 14a, thereby evaporating the refrigerant in the cooler chamber 14a.

The battery 12 cooled by the battery cooler 14 includes a plurality of battery cells 121 electrically connected in series. The plurality of battery cells 121 are stacked in the battery stacking direction DRb, and the battery stacking direction DRb is in the horizontal direction in a vehicle horizontal state in which the vehicle is horizontally disposed.

Further, in the present embodiment, the battery 12 is disposed under the floor of the vehicle. Therefore, the battery cooler 14 is also arranged under the floor of the vehicle. In addition, although it confirms, FIG. 1 is a schematic diagram and does not show the shape of each component and the specific connection location of the pipes 18 and 20 connected to the battery cooler 14 and the heat radiating part 16 respectively. Absent.

The battery cooler 14 has, for example, a rectangular parallelepiped box shape and is formed to extend in the battery stacking direction DRb. Further, the battery cooler 14 has an upper surface portion 141 on which an upper surface 141a of the battery cooler 14 is formed. That is, an upper inner wall surface 141b that forms the upper side of the cooler chamber 14a is formed on the side of the upper surface portion 141 opposite to the upper surface 141a side.

When the liquid refrigerant accumulated in the cooler chamber 14a does not include bubbles due to refrigerant boiling or the like, the cooler chamber 14a is filled with the liquid refrigerant in the horizontal state of the vehicle. It is said to be a quantity. Therefore, the liquid level of the liquid-phase refrigerant is formed in the forward piping 18 and the return piping 20, and is positioned above the upper inner wall surface 141 b of the battery cooler 14. In FIG. 1, the liquid surface position SF1 of the liquid phase refrigerant in the forward pipe 18 is indicated by a one-dot chain line SF1, and the liquid surface position SF2 of the liquid phase refrigerant in the return pipe 20 is indicated by a one-dot chain line SF2.

The plurality of battery cells 121 are arranged side by side on the upper surface 141a of the battery cooler 14, respectively. Each of the plurality of battery cells 121 is connected to the upper surface portion 141 so as to be able to conduct heat with the upper surface portion 141 of the battery cooler 14. Thereby, the upper surface 141a of the battery cooler 14 functions as a battery cooling surface that cools the battery 12, and the upper surface portion 141 of the battery cooler 14 functions as a cooling surface forming portion that forms the battery cooling surface.

The battery cooler 14 is formed with an endothermic inlet 14b and an endothermic outlet 14c. The heat absorption part inlet 14b connects the forward flow passage 18a formed in the forward piping 18 to the inside of the battery cooler 14 (that is, the cooler chamber 14a). Therefore, when the refrigerant circulates in the fluid circulation circuit 26, the refrigerant in the forward flow passage 18a flows into the cooler chamber 14a through the heat absorption part inlet 14b of the battery cooler 14. The forward flow path 18 a is a refrigerant flow path for flowing the refrigerant from the heat radiating unit 16 to the battery cooler 14. The endothermic inlet 14b of the battery cooler 14 is provided at, for example, one end of the battery cooler 14 in the battery stacking direction DRb.

Further, the heat absorption part discharge port 14 c of the battery cooler 14 communicates the return flow passage 20 a formed inside the return pipe 20 into the battery cooler 14. Therefore, when the refrigerant circulates in the fluid circulation circuit 26, the refrigerant in the cooler chamber 14a flows out to the return flow passage 20a through the heat absorption part discharge port 14c of the battery cooler 14. The return flow path 20 a is a refrigerant flow path for flowing the refrigerant from the battery cooler 14 to the heat radiating unit 16. The heat absorption part discharge port 14c of the battery cooler 14 is provided, for example, at the other end of the battery cooler 14 in the battery stacking direction DRb. Note that the battery cooler 14 has a structure (not shown) that causes the gas-phase refrigerant in the cooler chamber 14a to flow out of the endothermic portion outlet 14c exclusively of the endothermic portion inlet 14b and the endothermic portion outlet 14c.

The heat radiating part 16 of the device temperature control device 10 is for radiating heat from the refrigerant in the heat radiating part 16 to the heat receiving fluid. More specifically, the refrigerant in the gas phase flows into the heat radiating section 16 from the return pipe 20, and the heat radiating section 16 is a condenser that condenses the refrigerant by radiating heat from the refrigerant. In the present embodiment, the heat receiving fluid for exchanging heat with the refrigerant in the heat radiating unit 16 is air. The heat receiving fluid for exchanging heat with the refrigerant in the heat radiating unit 16 is not limited to air.

The heat dissipation part 16 is disposed above the battery cooler 14. A heat radiating portion inlet 16 a is formed in the upper portion of the heat radiating portion 16, and a heat radiating portion discharge port 16 b is formed in the lower portion of the heat radiating portion 16. The heat radiating portion inlet 16 a communicates the return flow passage 20 a formed inside the return piping 20 with the heat radiating portion 16. Accordingly, when the refrigerant circulates in the fluid circulation circuit 26, the refrigerant in the return flow passage 20 a flows into the heat radiating portion 16 through the heat radiating portion inlet 16 a of the heat radiating portion 16.

The heat radiation part discharge port 16 b communicates the forward flow passage 18 a formed inside the forward pipe 18 with the inside of the heat radiation part 16. Therefore, when the refrigerant condenses in the heat radiating section 16, the liquid refrigerant flows from the inside of the heat radiating section 16 to the forward flow passage 18a by gravity. The refrigerant flowing through the forward flow passage 18a flows into the cooler chamber 14a via the heat absorption part inlet 14b of the battery cooler 14.

In the device temperature control apparatus 10 configured as described above, for example, when the battery 12 generates heat and the battery temperature becomes high, for example, when the vehicle is running, heat is transmitted to the upper surface portion 141 of the battery cooler 14 through the lower surface of the battery cell 121, The liquid phase refrigerant in the battery cooler 14 boils due to heat. Each battery cell 121 is cooled by the latent heat of vaporization caused by the boiling of the liquid phase refrigerant. Moreover, the refrigerant | coolant which boiled within the battery cooler 14 becomes gas, and moves upwards. That is, the refrigerant (that is, the gas-phase refrigerant) that has become the gas moves to the heat radiating unit 16 through the return flow passage 20a. Then, the gas-phase refrigerant that has flowed into the heat radiating portion 16 is cooled and liquefied by the heat radiating portion 16, and then flows into the battery cooler 14 again through the outward piping 18.

In short, when the thermosiphon phenomenon is started in the device temperature control device 10, the refrigerant circulates in the fluid circulation circuit 26 as indicated by the arrow ARc. Thus, in the apparatus temperature control apparatus 10, these operation | movements are performed by the natural circulation of the refrigerant | coolant enclosed by the fluid circulation circuit 26, without requiring drive devices, such as a compressor.

Subsequently, the air conditioner 40 provided in the vehicle of the present embodiment will be described. The vehicle according to the present embodiment includes an air conditioner 40 for adjusting the temperature and humidity of air in the passenger compartment, as in a general vehicle. The air conditioner 40 includes an air conditioning unit 41 that cools the air blown by a cooling unit disposed in the air conditioning case 44 and blows the air into the vehicle interior, and a refrigeration cycle that supplies refrigerant to the cooling unit in the air conditioning unit 41. ing. The cooling unit disposed in the air conditioning case 44 of the air conditioning unit 41 is not limited to the evaporator 50, and may be configured by, for example, a Peltier element.

First, the refrigeration cycle of the air conditioner 40 will be described.

As shown in FIG. 3, the refrigeration cycle 1 includes a compressor 2, a condenser 3, an expansion valve 4, an evaporator 50, and the like. These components are connected in an annular shape by a pipe 6 and constitute a refrigerant circulation path.

The compressor 2 sucks and compresses the refrigerant from the evaporator 50 side. The compressor 2 is driven by power transmitted from an engine or electric motor for traveling the vehicle (not shown).

The high-pressure gas-phase refrigerant discharged from the compressor 2 flows into the condenser 3. When the high-pressure gas-phase refrigerant that has flowed into the condenser 3 flows through the refrigerant flow path of the condenser 3, it is cooled and condensed by heat exchange with the outside air.

The liquid-phase refrigerant condensed in the condenser 3 is decompressed when passing through the expansion valve 4, and becomes a mist-like gas-liquid two-phase state. The expansion valve 4 is configured by a fixed throttle such as an orifice or a nozzle, or an appropriate variable throttle.

The low-pressure refrigerant after decompression flows into the evaporator 50. As shown in FIG. 1, the evaporator 50 is disposed in the air conditioning case 44. The low-pressure refrigerant flowing inside the evaporator 50 absorbs heat from the air blown by the blower 48 and evaporates. The evaporator 50 cools the air flowing through the ventilation path 44c in the air conditioning case 44 by the latent heat of vaporization of the low-pressure refrigerant. The temperature of the air is adjusted by the air heater 52 and blown out into the passenger compartment. As shown in FIG. 3, the refrigerant that has passed through the evaporator 50 is sucked into the compressor 2 via an accumulator (not shown).

Subsequently, the air conditioning unit 41 of the air conditioner 40 will be described.

As shown in FIG. 1, the air conditioning unit 41 of the present embodiment is disposed inside the instrument panel at the foremost part of the vehicle interior. The air conditioning unit 41 sucks one or both of the inside air that is the air inside the vehicle interior and the outside air that is the air outside the vehicle interior, and adjusts the sucked air to blow out the air into the vehicle interior. As shown in FIG. 1, the air conditioning unit 41 includes an air conditioning case 44, an inside / outside air switching door 46, a blower or blower 48, the evaporator 50, the air heater 52, the air mix door 54, and a plurality of outlet switching. The doors 56a to 56d are provided. The outlet switching doors 56a to 56d are all butterfly doors, for example.

The air conditioning case 44 forms a housing of the air conditioning unit 41, and air inlets 44a and 44b are formed on one side of the air conditioning case 44, and a plurality of airs that pass toward the vehicle interior pass on the other side. An air outlet is formed. And the ventilation path 44c is formed in the air-conditioning case 44, and the ventilation path 44c flows blowing air from the air inlets 44a and 44b to a blower outlet.

In addition, the air conditioning case 44 has an air suction part 441 in which two air inlets 44 a and 44 b are formed on the upstream side (that is, one side) of the air conditioning case 44. One of the two air introduction ports 44a and 44b is an inside air introduction port 44a that sucks in the inside air, and the other is an outside air introduction port 44b that sucks in outside air. That is, the air conditioning unit 41 sucks in the inside air from the inside air introduction port 44a and sucks the outside air from the outside air introduction port 44b.

The inside / outside air switching door 46 is an opening / closing device that increases or decreases the opening degree of the inside air introduction port 44a and the opening degree of the outside air introduction port 44b. The inside / outside air switching door 46 rotates in the air suction portion 441 and is driven by an actuator such as a servo motor. Specifically, the inside / outside air switching door 46 rotates so as to close the other of the inside air introduction port 44a and the outside air introduction port 44b, and the flow rate ratio between the inside air and the outside air flowing into the air suction portion 441. Adjust. The opening degree of the inside air introduction port 44a is the opening degree of the inside air introduction port 44a, and the opening degree of the outside air introduction port 44b is the opening degree of the outside air introduction port 44b.

For example, the inside / outside air switching door 46 switches the air conditioning unit 41 between an inside air mode in which inside air is exclusively introduced into the air conditioning unit 41 and an outside air mode in which outside air is exclusively introduced into the air conditioning unit 41. In the inside air mode, the inside / outside air switching door 46 opens the inside air introduction port 44a while closing the outside air introduction port 44b. On the other hand, in the outside air mode, the inside / outside air switching door 46 closes the inside air introduction port 44a while opening the outside air introduction port 44b.

Thus, the air conditioning unit 41 has the inside / outside air switching door 46 so that it can be switched between the inside air mode and the outside air mode.

The blower 48 flows the air that has flowed into the air suction portion 441 to the evaporator 50 and blows the air that has passed through the evaporator 50 so as to flow into the vehicle interior. In short, the blower 48 allows air to flow from the air conditioning unit 41 into the vehicle interior. For this purpose, the blower 48 includes an impeller 481 that is a centrifugal fan and a motor (not shown) that rotates the impeller 481.

The impeller 481 of the blower 48 is disposed downstream of the air suction portion 441 and upstream of the evaporator 50 in the air flow in the air conditioning case 44.

The evaporator 50 is disposed in the airflow case 44 on the downstream side of the air flow with respect to the impeller 481 of the blower 48. The evaporator 50 is a heat exchanger for air cooling. The evaporator 50 constitutes a part of the refrigeration cycle 1 described above. The evaporator 50 exchanges heat between the refrigerant circulating in the refrigeration cycle 1 and the blown air sent from the blower 48, evaporates the refrigerant by the heat exchange, and cools the blown air. Note that when the blown air is cooled by the evaporator 50, water vapor contained in the blown air is condensed, and condensed water may be generated on the outer wall of the evaporator 50.

A lower tray 60 for receiving the condensed water generated by the evaporator 50 is provided on the lower side in the gravity direction of the evaporator 50. Packings 51 are provided between the lower surface of the evaporator 50 and the lower tray 60 and between the upper surface of the evaporator 50 and the inner wall of the air conditioning case 44. The packing 51 is made of, for example, sponge-like polyurethane. The lower receiving tray 60 is connected to a discharge pipe 61 for discharging condensed water accumulated in the lower receiving tray 60. Thereby, the condensed water produced | generated by the evaporator 50 passes along the discharge flow path 61a formed inside the discharge pipe 61 from the lower tray 60, and is discharged | emitted outside the vehicle.

The air heater 52 is disposed on the downstream side of the air flow with respect to the evaporator 50 in the air conditioning case 44. The air heater 52 is a heater core that heats the air passing through the air heater 52 by exchanging heat with engine cooling water for engine cooling.

The air heater 52 is disposed in the air conditioning case 44 so as to partially cross the ventilation path 44 c on the downstream side of the air flow from the evaporator 50.

The air mix door 54 is disposed on the upstream side of the air flow with respect to the air heater 52 and on the downstream side of the air flow with respect to the evaporator 50. The air mix door 54 is driven by an actuator such as a servo motor, and changes the blowout temperature of the conditioned air blown from each blowout port toward the vehicle interior. In other words, the air mix door 54 passes through the evaporator 50 and bypasses the air heater 52 according to the rotational position of the air mix door 54, and the air heater after passing through the evaporator 50. The air volume ratio with the warm air passing through 52 is adjusted.

The air conditioning case 44 has a defroster opening 442, a face opening 443, a front seat foot opening 444, and a rear seat foot opening 445. These openings 442, 443, 444, 445 are arranged at the most downstream site in the air flow in the air conditioning case 44.

The defroster duct 442a is connected to the defroster opening 442. In addition, a defroster door 56 a is provided in the defroster opening 442. The defroster door 56 a opens and closes the defroster opening 442. If the defroster opening 442 is opened by the defroster door 56a, air is blown out from the defroster opening 442 to the inner surface of the front window of the vehicle via the defroster duct 442a.

A face duct 443a is connected to the face opening 443. The face opening 443 is provided with a face door 56b. The face door 56 b opens and closes the face opening 443. If the face opening 443 is opened by the face door 56b, air is blown out from the face opening 443 through the face duct 443a toward the head chest of the front seat occupant.

A front seat foot duct 444a is connected to the front seat foot opening 444. The front seat foot opening 444 is provided with a front seat foot door 56c. The front seat foot door 56 c opens and closes the front seat foot opening 444. If the front seat foot opening 444 is opened by the front seat foot door 56c, air is blown out from the front seat foot opening 444 to the feet of the front seat occupant through the front seat foot duct 444a.

The rear seat foot duct 445a is connected to the rear seat foot opening 445. The rear seat foot opening 445 is provided with a rear seat foot door 56d. The rear seat foot door 56d opens and closes the rear seat foot opening 445. If the rear seat foot opening 445 is opened by the rear seat foot door 56d, air is blown out from the rear seat foot opening 445 through the rear seat foot duct 445a toward the feet of the rear seat occupant.

The air outlet mode of the air conditioning unit 41 is switched according to the opening / closing operation of the air outlet switching doors 56a to 56d. For example, the outlet mode may include a face mode, a bi-level mode, a foot mode, a foot defroster mode, a defroster mode, and the like.

Next, the characteristic configurations of the device temperature control device 10 and the air conditioner 40 of the present embodiment and the operation and effects thereof will be described.

As described above, the air conditioner 40 of the present embodiment includes the discharge pipe 61 for discharging the condensed water generated by the evaporator 50 provided in the air conditioning case 44 to the outside of the vehicle. As shown in FIGS. 1 and 2, at least a part of the discharge pipe 61 and at least a part of the outgoing pipe 18 constitute a double pipe structure 70. The double pipe structure 70 of the present embodiment has a configuration in which the forward pipe 18 is disposed inside the discharge pipe 61. A portion constituting the double-pipe structure 70 in the outgoing pipe 18 functions as a contact portion 181 that comes into contact with the condensed water flowing through the discharge flow passage 61 a inside the discharge pipe 61. In the present embodiment, the contact portion 181 provided on the outward route pipe 18 is referred to as an outward route contact portion 181. When the refrigerant flowing in the forward pipe 18 passes through the forward flow path 18 a inside the forward path contact portion 181, the refrigerant exchanges heat with the condensed water flowing through the discharge flow path 61 a inside the discharge pipe 61.

The battery 12 to be cooled by the device temperature control device 10 of the present embodiment needs to be cooled with a large cooling capacity at a time when the outside air temperature is high such as summer. On the other hand, in the season when the outside air temperature is high such as summer, the difference between the outside air temperature and the set temperature in the passenger compartment is large, and the humidity of the outside air is also high. Therefore, the amount of condensed water generated in the evaporator 50 of the refrigeration cycle 1 Will increase. That is, the time when the battery 12 needs to be cooled with a large cooling capacity and the time when the amount of condensed water generated in the evaporator 50 increases are common. In addition, the temperature of the refrigerant flowing through the evaporator 50 of the refrigeration cycle 1 is normally controlled at about 1 ° C. to 3 ° C., and the condensed water generated in the evaporator 50 has the same temperature as the refrigerant flowing through the evaporator 50. It has become. Therefore, in the forward contact portion 181, the refrigerant flowing through the forward flow passage 18 a inside the forward contact portion 181 exchanges heat with the cold condensed water flowing through the discharge flow passage 61 a inside the discharge pipe 61. Therefore, the condensation of the refrigerant flowing through the forward flow passage 18a inside the forward contact portion 181 is further promoted, and the temperature of the liquid phase refrigerant is further reduced. Therefore, it is possible to increase the flow rate of the liquid phase refrigerant supplied from the forward piping 18 to the battery cooler 14 and to lower the temperature of the liquid phase refrigerant. Therefore, the device temperature control apparatus 10 can increase the cooling capacity of the battery 12 by the battery cooler 14 at a time when the outside air temperature is high such as in summer and the battery 12 needs to be cooled with a large cooling capacity.

Further, the condensed water generated by the evaporator 50 of the refrigeration cycle 1 is generated by the electric power used for the air conditioner 40 of the vehicle. In general, the condensed water is discharged out of the vehicle as it is. In contrast, in the present embodiment, by effectively using the condensed water for the device temperature control device 10, the cooling capacity of the device temperature control device 10 can be efficiently increased without increasing the power consumption of the vehicle. .

Furthermore, the apparatus temperature control apparatus 10 of this embodiment uses the condensed water produced | generated with the evaporator 50 of the refrigerating cycle 1, without enlarging the physique of the thermal radiation part 16 of the apparatus temperature control apparatus 10, The flow rate of the liquid phase refrigerant can be increased. Furthermore, since a mechanism for spraying a liquid such as a washer liquid is not required with respect to the technique described in Patent Document 1 described above, the configuration of the device temperature adjustment device 10 can be simplified.

Further, in the present embodiment, the forward contact portion 181 and the discharge pipe 61 constitute a double pipe structure 70. Therefore, it is possible to increase the area where the condensed water is in contact with the outer periphery of the forward path contact portion 181. Therefore, the heat exchange efficiency between the refrigerant flowing through the forward flow passage 18a inside the forward contact portion 181 and the condensed water flowing through the discharge flow passage 61a inside the discharge pipe 61 can be increased.

Furthermore, the forward contact portion 181 is provided inside the double pipe structure 70 and the discharge pipe 61 is provided outside, so that the forward contact portion 181 is not exposed to the outside air. Therefore, the refrigerant flowing through the forward flow passage 18a inside the forward contact portion 181 is not heated by the outside air. Therefore, this equipment temperature control apparatus 10 can suppress that the refrigerant flowing from the heat radiating unit 16 through the outward piping 18 is heated by the outside air.

(Second Embodiment)
A second embodiment will be described. The second embodiment is different from the first embodiment in the configuration of the double-pipe structure 70 constituted by the forward contact portion 181 and the discharge pipe 61, and is otherwise the same as the first embodiment. Therefore, only a different part from 1st Embodiment is demonstrated.

As shown in FIG. 4, also in the second embodiment, the forward contact portion 181 and the discharge pipe 61 constitute a double pipe structure 70. However, the double-pipe structure 70 of the second embodiment has a configuration in which the forward path contact portion 181 is provided outside the discharge pipe 61. Also with this configuration, it is possible to increase the area where the refrigerant flowing in the forward flow passage 18 a inside the forward contact portion 181 contacts the outer periphery of the discharge pipe 61. Therefore, the heat exchange efficiency between the refrigerant flowing through the forward flow passage 18a inside the forward contact portion 181 and the condensed water flowing through the discharge flow passage 61a inside the discharge pipe 61 can be increased. Therefore, the second embodiment can achieve the same operational effects as the first embodiment.

(Third embodiment)
A third embodiment will be described. In the third embodiment, the configurations of the forward contact portion 181 and the discharge pipe 61 are changed with respect to the first and second embodiments described above, and the other parts are the same as the first and second embodiments. Only the differences from the first and second embodiments will be described.

As shown in FIG. 5, in the third embodiment, the forward contact portion 181 and the discharge pipe 61 do not constitute a double pipe structure 70. However, also in the third embodiment, the forward contact portion 181 and the discharge pipe 61 are in contact with each other. Thereby, the refrigerant flowing through the forward flow passage 18 a inside the forward contact portion 181 and the condensed water flowing through the discharge flow passage 61 a inside the discharge pipe 61 exchange heat. In addition, you may comprise the outward path contact part 181 and the discharge pipe 61 so that a surface contact or a line contact may mutually be carried out. Moreover, you may comprise the outward path contact part 181 and the discharge pipe 61 so that it may contact indirectly through a member with high heat conductivity. The third embodiment can achieve the same effects as the first and second embodiments.

(Fourth embodiment)
A fourth embodiment will be described. The fourth embodiment is obtained by changing the configuration of the forward contact portion 181 with respect to the first to third embodiments described above, and is otherwise the same as the first to third embodiments. Only parts different from the third embodiment will be described.

In FIG. 6, the overall configuration of the device temperature control device 10 is omitted, and only the cross section of the forward contact portion 181 is shown. As shown in FIG. 6, in the fourth embodiment, the forward contact portion 181 included in the device temperature adjustment device 10 is provided on the lower tray 60. Condensed water generated by the evaporator 50 of the refrigeration cycle 1 is accumulated in the lower tray 60. Therefore, the condensed water collected in the lower tray 60 comes into contact with the forward contact portion 181 before being discharged from the air conditioning unit 41 via the discharge pipe 61. Thereby, the refrigerant flowing through the forward flow passage 18 a inside the forward contact portion 181 and the condensed water flowing through the discharge flow passage 61 a inside the discharge pipe 61 exchange heat. Therefore, the fourth embodiment can achieve the same operational effects as the first to third embodiments.

Furthermore, in the fourth embodiment, it is possible to eliminate piping for guiding condensed water from the air conditioning unit 41 to the outward contact portion 181. Therefore, the configuration of the fourth embodiment can be simplified compared to the first to third embodiments.

(Fifth embodiment)
A fifth embodiment will be described. In the fifth embodiment, the configurations of the heat radiating section 16 and the outward piping 18 are changed with respect to the first to fourth embodiments described above, and the others are the same as the first to fourth embodiments. Only the parts different from the first to fourth embodiments will be described.

In FIG. 7, the overall configuration of the device temperature control device 10 is omitted, and only the heat radiating unit 16 is shown. As shown in FIG. 7, in the fifth embodiment, the heat radiating unit 16 included in the device temperature control device 10 is provided on the lower tray 60. Condensed water generated by the evaporator 50 of the refrigeration cycle 1 is accumulated in the lower tray 60. Therefore, the condensed water accumulated in the lower tray 60 comes into contact with the heat radiating unit 16 before being discharged from the air conditioning unit 41.

Moreover, the heat radiation part 16 is provided in the downstream side of the air flow in the air conditioning case 44 with respect to the evaporator 50 in the lower tray 60. The condensed water generated in the evaporator 50 flows downstream of the evaporator 50 due to the airflow flowing in the air conditioning case 44. Therefore, the condensed water generated in the evaporator 50 and flowing downstream of the evaporator 50 comes into contact with the heat radiating unit 16.

Both the surface on the lower tray 60 side and the surface on the evaporator 50 side of the heat radiation portion 16 function as a contact portion 161 that contacts the condensed water. In this embodiment, the contact part 161 provided in the surface by the side of the lower saucer 60 and the surface by the side of the evaporator 50 among the heat radiation parts 16 is called the heat radiation contact part 161. The refrigerant flowing inside the heat radiation contact portion 161 exchanges heat with the condensed water generated by the evaporator 50. In addition, the refrigerant flowing inside the heat radiating unit 16 also exchanges heat with the condensed water through the heat radiating contact unit 161. Therefore, the fifth embodiment can achieve the same operational effects as the first to fourth embodiments.

Furthermore, in the fifth embodiment, it is possible to eliminate piping or the like for guiding condensed water from the air conditioning unit 41 to the heat radiation contact portion 161. Therefore, the configuration of the fifth embodiment can be simplified compared to the first to third embodiments.

(Sixth embodiment)
A sixth embodiment will be described. The sixth embodiment is obtained by changing the configurations of the forward contact portion 181 and the discharge pipe 61 with respect to the first to fifth embodiments described above, and is otherwise the same as the first to fifth embodiments. Only differences from the first to fifth embodiments will be described.

As shown in FIG. 8, in the sixth embodiment, the forward contact portion 181 is provided directly below the drain water discharge port 62 formed at the end of the discharge pipe 61 opposite to the lower tray 60. . Therefore, the condensed water W dripping from the drain water discharge port 62 through the discharge pipe 61 comes into contact with the forward contact portion 181. The forward path contact portion 181 is disposed so as to extend in a direction intersecting the direction of gravity so that the condensate W can be easily contacted. In addition, it is preferable that the outward contact part 181 is arrange | positioned in the state near horizontal. As a result, the refrigerant flowing through the forward flow passage 18a inside the forward contact portion 181 and the condensed water W dripped from the drain water discharge port 62 of the discharge pipe 61 and contacting the forward contact portion 181 exchange heat. The sixth embodiment can also provide the same operational effects as the first to fifth embodiments.

Furthermore, in the sixth embodiment, it is possible to eliminate or shorten the piping for guiding the condensed water W from the air conditioning unit 41 to the forward contact portion 181. Accordingly, the sixth embodiment can simplify the configuration compared to the first to third embodiments.

(Seventh embodiment)
A seventh embodiment will be described. The seventh embodiment is a modification of the sixth embodiment described above. As shown in FIG. 9, in the seventh embodiment, a guide plate 63 is provided between the drain water discharge port 62 and the forward path contact portion 181. The guide plate 63 guides the condensed water W generated by the evaporator 50 and dripped from the drain water discharge port 62 to the forward contact portion 181. In addition, it is preferable that the cross section of the guide plate 63 has a U-shape that is convex downward in the direction of gravity. Thereby, even when it is difficult to provide the forward contact portion 181 directly below the position where the condensed water W drops from the drain water discharge port 62, the condensed water W is guided to the forward contact portion 181 by the guide plate 63. The condensed water W can be brought into contact with 181. Therefore, in 7th Embodiment, the apparatus temperature control apparatus 10 can respond | correspond to various vehicle types. Further, in the seventh embodiment, even when the discharge pipe 61 is deformed due to secular change, the condensed water W dripped from the drain water discharge port 62 can be reliably brought into contact with the forward contact portion 181 by the guide plate 63. Also, the seventh embodiment can achieve the same effects as the first to sixth embodiments.

(Eighth embodiment)
An eighth embodiment will be described. In the eighth embodiment, the configurations of the heat radiating section 16 and the discharge pipe 61 are changed with respect to the first to seventh embodiments described above, and the others are the same as those of the first to seventh embodiments. Only portions different from the first to seventh embodiments will be described.

As shown in FIG. 10, in the eighth embodiment, the heat radiating portion 16 is provided directly below the drain water discharge port 62 provided at the end of the discharge pipe 61. Condensed water W dripping from the drain water discharge port 62 through the discharge pipe 61 contacts the heat radiation contact portion 161 of the heat radiation portion 16. In the eighth embodiment, the surface of the heat radiating portion 16 that faces the drain water discharge port 62 is the heat radiating contact portion 161. The heat dissipating contact portion 161 is arranged so as to intersect the direction of gravity so that it can easily come into contact with the condensed water W. When the condensed water W dripped from the drain water discharge port 62 comes into contact with the heat radiation contact portion 161, the condensed water W and the refrigerant flowing inside the heat radiation contact portion 161 exchange heat. Further, the refrigerant flowing inside the heat radiating unit 16 also exchanges heat with the condensed water W through the heat radiating contact portion 161. Therefore, the eighth embodiment can achieve the same operational effects as the first to seventh embodiments.

Furthermore, in the eighth embodiment, it is possible to eliminate or shorten the piping for guiding the condensed water W from the air conditioning unit 41 to the heat radiation contact portion 161. Therefore, the configuration of the eighth embodiment can be simplified compared to the first to third embodiments.

Although not shown, in the eighth embodiment, a guide plate as described in the seventh embodiment may be provided. In that case, the guide plate is provided between the drain water discharge port 62 and the heat radiation contact portion 161, and guides the condensed water W dripping from the drain water discharge port 62 to the heat radiation contact portion 161. Thereby, even when it is difficult to provide the heat radiation contact portion 161 immediately below the position where the condensed water W drops from the drain water discharge port 62, the condensed water W is guided to the heat radiation contact portion 161 by the guide plate, and the heat radiation contact portion 161 is provided. It is possible to bring the condensed water W into contact therewith.

(Ninth embodiment)
A ninth embodiment will be described. The ninth embodiment is different from the first embodiment in that the water retaining member 64 is provided outside the outward contact portion 181 with respect to the first embodiment, and the other parts are the same as the first embodiment. Only will be described.

As shown in FIG. 11, a water retaining member 64 is provided on the outside of the forward contact portion 181. The water retaining member 64 is formed in a cylindrical shape and covers the outer periphery of the forward path contact portion 181. The water retaining member 64 may be provided on at least a part of the forward path contact portion 181. The water retaining member 64 is formed of a material capable of retaining condensed water inside. Examples of the water retaining member 64 include sponge-like polyurethane.

By providing the water retaining member 64 outside the outward path contact portion 181, the water retaining member 64 can always retain the condensed water even if the amount of condensed water generated by the evaporator 50 changes. Therefore, the site | part which provided the water retention member 64 among the outward path contact parts 181 always contacts condensed water. Therefore, the device temperature control device 10 can stably cool the refrigerant flowing in the forward flow passage 18a inside the forward contact portion 181.

By the way, when the outside air temperature is low such as in winter, it is preferable to suppress the cooling of the battery 12 in order to improve the performance of the battery 12. On the other hand, when the outside air temperature is low such as in the winter, the humidity is low, so that almost no condensed water is generated in the evaporator 50 of the refrigeration cycle 1. That is, the time when it is preferable to suppress the cooling of the battery 12 and the time when almost no condensed water is generated in the evaporator 50 of the refrigeration cycle 1 are common. Therefore, by providing the water retaining member 64 outside the outward contact portion 181, when the outside air temperature is low, such as in winter, the water retaining member 64 functions as a heat insulating layer, so that the outward flow passage inside the outward contact portion 181 by the outside air. It can suppress that the refrigerant | coolant which flows through 18a is cooled. Therefore, when the outside air temperature is low such as in winter, the cooling capacity of the device temperature control device 10 can be suppressed.

(10th Embodiment)
A tenth embodiment will be described. The tenth embodiment is different from the fourth embodiment in that the water retaining member 64 is provided outside the outward contact portion 181 with respect to the fourth embodiment, and the other parts are the same as the fourth embodiment. Only will be described.

As shown in FIG. 12, a water retaining member 64 is provided on the outside of the outward contact portion 181. The water retaining member 64 is formed in a cylindrical shape and covers the outer periphery of the forward path contact portion 181. The water retaining member 64 is disposed on the lower tray 60. The water retaining member 64 may cover at least a part of the outer periphery of the forward path contact portion 181.

By providing the water retaining member 64 outside the outward path contact portion 181, the water retaining member 64 can always retain the condensed water even if the amount of condensed water generated by the evaporator 50 changes. Therefore, the site | part which provided the water retention member 64 among the outward path contact parts 181 always contacts condensed water. Furthermore, it is possible to spread the condensed water from the lower tray 60 to the upper part of the forward contact portion 181 by the capillary phenomenon of the condensed water transmitted through the water retaining member 64. Therefore, the device temperature control device 10 can stably cool the refrigerant flowing in the forward flow passage 18a inside the forward contact portion 181.

On the other hand, when the outside air temperature is low such as in winter, it is possible to prevent the coolant flowing through the forward flow passage 18a inside the forward contact portion 181 from being cooled by the outside air by causing the water retaining member 64 to function as a heat insulating layer. Therefore, when the outside air temperature is low such as in winter, the cooling capacity of the device temperature control device 10 can be suppressed.

Note that the packing 51 and the water retaining member 64 provided between the lower surface of the evaporator 50 and the lower tray 60 may be integrally formed. Thereby, the number of parts can be reduced and the manufacturing cost can be reduced.

(Eleventh embodiment)
An eleventh embodiment will be described. In the eleventh embodiment, a switching valve 65 is provided in the middle of the outward piping 18 with respect to the first embodiment, and the other parts are the same as in the first embodiment. Only explained.

As shown in FIG. 13, a switching valve 65 is provided in the middle of the outward piping 18. The switching valve 65 includes a first discharge pipe 611 that connects the lower tray 60 and the switching valve 65, a second discharge pipe 612 that connects the switching valve 65 and the double pipe structure 70, and the switching valve 65 and the outside air. The 3rd discharge pipe 613 which connects is connected. The switching valve 65 switches between a state in which the condensed water flowing from the lower tray 60 through the first discharge pipe 611 flows through the second discharge pipe 612 and a state through which the condensed water flows through the third discharge pipe 613.

When cooling the battery 12, the switching valve 65 causes the condensed water flowing from the lower tray 60 to flow through the first discharge pipe 611 to flow into the second discharge pipe 612. Thereby, the refrigerant flowing through the forward flow passage 18a inside the forward contact portion 181 constituting the double pipe structure 70 and the condensed water flowing inside the second discharge pipe 612 exchange heat.

On the other hand, when the cooling of the battery 12 is suppressed, the switching valve 65 causes the condensed water flowing from the lower tray 60 to flow through the first discharge pipe 611 to flow into the third discharge pipe 613. Thereby, the condensed water flowing through the first discharge pipe 611 is discharged from the third discharge pipe 613 to the outside without flowing into the second discharge pipe 612. That is, the switching valve 65 can stop the condensed water flowing through the first discharge pipe 611 from flowing through the second discharge pipe 612 to the forward contact portion 181. Therefore, in the eleventh embodiment, even when condensed water is generated in the evaporator 50 by the dehumidifying and heating control of the air conditioner 40, the condensed water can be prevented from flowing to the forward contact portion 181.

(Twelfth embodiment)
A twelfth embodiment will be described. The twelfth embodiment is further provided with a configuration for cooling the refrigerant in the middle of the outward piping 18 with respect to the first embodiment, and the other aspects are the same as those of the first embodiment. Only the different parts will be described.

As shown in FIG. 14, in the twelfth embodiment, the refrigeration cycle 1 of the air conditioner 40 includes a first evaporator 50 and a second evaporator 53. The first evaporator 50 and the second evaporator 53 are connected in parallel by the pipe 6. The first evaporator 50 is provided in the air conditioning unit 41 of the air conditioner 40. The second evaporator 53 is provided in the middle of the outward piping 18. As a result, the refrigerant flowing through the second evaporator 53 of the refrigeration cycle 1 and the refrigerant flowing through the forward flow passage 18a inside the forward piping 18 exchange heat. For this reason, the condensation of the refrigerant flowing in the forward flow passage 18a inside the forward piping 18 is further promoted, and the temperature of the liquid phase refrigerant is further reduced. Therefore, it is possible to increase the flow rate of the liquid phase refrigerant supplied from the forward piping 18 to the battery cooler 14 and to lower the temperature of the liquid phase refrigerant. Therefore, the device temperature control device 10 can further increase the cooling capacity of the battery 12 by the battery cooler 14.

In addition, the refrigeration cycle 1 described in the twelfth embodiment may be configured separately from the refrigeration cycle 1 included in the air conditioner 40.

(13th Embodiment)
A thirteenth embodiment will be described. 13th Embodiment changes the structure which cools the refrigerant | coolant which flows through the outward piping 18 with respect to 12th Embodiment, Since others are the same as that of 13th Embodiment, it is a different part from 13th Embodiment. Only will be described.

As shown in FIG. 15, also in the thirteenth embodiment, the refrigeration cycle 1 included in the air conditioner 40 includes a first evaporator 50 and a second evaporator 53. The first evaporator 50 is provided in the air conditioning unit 41 of the air conditioner 40. The second evaporator 53 is connected to the cooling water circulation circuit 80.

The cooling water circulation circuit 80 is configured such that a pump 81, a first heat exchanger 82, and a second heat exchanger 83 are connected in a ring shape by a pipe 84. The first heat exchanger 82 of the cooling water circulation circuit 80 and the second evaporator 53 of the refrigeration cycle 1 are integrally configured. The second heat exchanger 83 of the cooling water circulation circuit 80 is provided in the middle of the forward piping 18.

The cooling water flows through the piping 84 of the cooling water circulation circuit 80 by driving the pump. The cooling water is cooled by exchanging heat with the refrigerant flowing through the second evaporator 53 of the refrigeration cycle 1 when flowing through the first heat exchanger 82. Further, when the cooling water flows through the second heat exchanger 83, the cooling water exchanges heat with the refrigerant flowing through the outward piping 18. For this reason, the condensation of the refrigerant flowing in the forward pipe 18 is further promoted, and the temperature of the liquid-phase refrigerant is further lowered. Therefore, the thirteenth embodiment can achieve the same effects as the twelfth embodiment.

(Other embodiments)
(1) In each of the above-described embodiments, as illustrated in FIG. 1, the target device that the device temperature control device 10 cools is the secondary battery 12, but the target device is not limited. For example, the target device may be an electric device other than the secondary battery 12 such as a motor, an inverter, or a charger, or may be a simple heating element. In addition, the target device is not limited to a vehicle-mounted device, and may be a device such as a base station that requires stationary cooling.

(2) In each of the above-described embodiments, the air heater 52 is a heater core, but it may be an indoor condenser that constitutes a part of the refrigeration cycle 1.

(3) In each of the above-described embodiments, the air conditioning unit 41 is a front air conditioning unit that is disposed, for example, in the foremost part of the vehicle interior, but this is an example. For example, the air conditioning unit 41 in which the heat radiating unit 16 of the device temperature control device 10 is disposed may be a rear air conditioning unit of a dual air conditioner.

(4) In each of the above-described embodiments, the outward piping 18 is provided as an outward portion of the device temperature control device 10, but the outward portion does not need to be configured by a piping member. For example, when a hole formed in the block-like object is provided as the forward flow path 18a, a portion of the block-like object that forms the forward flow path 18a corresponds to the forward path part. The same applies to the return pipe 20.

(5) In each of the above-described embodiments, as shown in FIG. 1, one heat radiating part 16 is provided, but a plurality of heat radiating parts 16 may be provided.

(6) In each of the embodiments described above, the refrigerant filled in the fluid circulation circuit 26 is, for example, a chlorofluorocarbon refrigerant. However, the refrigerant in the fluid circulation circuit 26 is not limited to the chlorofluorocarbon refrigerant. For example, as the refrigerant filled in the fluid circulation circuit 26, other refrigerants such as propane or CO ₂ and other media that change phase may be used.

(7) In each of the above-described embodiments, the device temperature adjustment device 10 adjusts the temperature of the battery 12 by cooling the battery 12, but the device temperature adjustment device 10 includes the battery 12 in addition to such a cooling function. A heating function for heating may be provided.

(8) In each of the above-described embodiments, the arrangement of the components in the air conditioning case 44 of the air conditioning unit 41 is determined according to the specific vehicle on which the air conditioning unit 41 is mounted.

(9) In each of the above-described embodiments, the air conditioning case 44 of the air conditioning unit 41 has the two foot opening portions 444 and 445, but the air conditioning case without one of the two foot opening portions 444 and 445. 44 can also be assumed.

Note that the present disclosure is not limited to the above-described embodiment, and includes various modifications and modifications within an equivalent range. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible.

In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case.

In each of the above embodiments, when referring to the material, shape, positional relationship, etc. of the constituent elements, etc., unless otherwise specified, or in principle limited to a specific material, shape, positional relationship, etc. The material, shape, positional relationship, etc. are not limited.

(Summary)
According to the 1st viewpoint shown by one part or all part of said each embodiment, apparatus temperature control apparatus cools ventilation air in the cooling part arrange | positioned in an air-conditioning case, and air-conditioning unit which ventilates into a vehicle interior It is mounted on a vehicle equipped with This device temperature control device adjusts the temperature of a target device by a phase change between a liquid phase and a gas phase of a working fluid, and includes a heat absorption unit, a heat radiation unit, a forward path unit, and a return path unit. The heat absorption part evaporates the working fluid by absorbing heat from the target device to the working fluid. The heat dissipating part is provided above the heat absorbing part in the gravity direction, and condenses the working fluid by dissipating the working fluid evaporated in the heat absorbing part. The forward path portion forms an outward flow path that connects the heat radiation portion discharge port that discharges the liquid phase working fluid from the heat radiation portion and the heat absorption portion inlet port where the liquid phase working fluid flows into the heat absorption portion. The return path section forms a return flow path that connects the heat absorption section discharge port that discharges the gas phase working fluid from the heat absorption section and the heat radiation section inlet that the gas phase working fluid flows into the heat dissipation section. At least one of the heat dissipating part and the forward path part has a contact part configured to exchange heat between the working fluid flowing inside thereof and the condensed water generated in the cooling part.

According to the 2nd viewpoint, the contact part is provided in the position where the condensed water produced | generated in a cooling part contacts.

According to this, it is possible to eliminate or shorten the piping for guiding the condensed water to the contact portion, and to simplify the configuration of the device temperature control device.

According to the third aspect, the device temperature control device further includes a guide plate that guides the condensed water generated in the cooling unit to the contact unit.

According to this, even when it is difficult to provide the contact portion directly below the position where the condensed water is discharged from the air conditioner, the condensed water is brought into contact with the contact portion by guiding the condensed water to the contact portion by the guide plate. It is possible. Therefore, this apparatus temperature control apparatus can respond to various vehicle types.

In addition, even when the discharge pipe that discharges condensed water from the air conditioner is deformed due to aging, this equipment temperature control device can reliably contact the condensed water with the contact portion by the guide plate.

According to the fourth aspect, the device temperature control device further includes a discharge pipe for discharging the condensed water generated in the cooling unit to the outside of the vehicle. The contact portion comes into contact with the discharge pipe.

According to this, it is possible to reliably exchange heat between the working fluid flowing inside the contact portion and the condensed water by guiding the condensed water to the contact portion by the discharge pipe.

According to the fifth aspect, the contact part and the discharge pipe of the forward path part constitute a double pipe structure in which either one is arranged inside the other.

According to this, the area where the condensed water flowing through the discharge pipe contacts the contact portion can be increased, and the heat exchange efficiency between the working fluid flowing inside the contact portion and the condensed water can be increased.

According to a sixth aspect, the device temperature control device further includes a switching valve that switches between a state in which condensed water flowing through the discharge pipe flows to the contact portion and a state in which it is stopped.

According to this, when the target device is cooled, it is possible to flow the condensed water flowing through the discharge pipe to the contact portion by the switching valve. On the other hand, when it is preferable to suppress the cooling of the target device, the switching valve can stop the condensed water flowing through the discharge pipe from flowing to the contact portion. Therefore, this apparatus temperature control apparatus can prevent the condensed water from flowing to the contact portion even when condensed water is generated by dehumidifying heating control of the air conditioner.

According to a seventh aspect, the air conditioner further includes a tray for receiving condensed water generated in the cooling unit. The contact portion is provided on the lower tray.

According to this, since the condensed water accumulated in the receiving tray comes into contact with the contact portion, it is possible to surely exchange heat between the working fluid flowing inside the contact portion and the condensed water. Further, the configuration can be simplified by eliminating the piping for guiding the condensed water to the contact portion.

According to the 8th viewpoint, the contact part is provided in the site | part downstream of the airflow flow of an air conditioner from the cooling part among the receiving trays.

According to this, since the condensed water generated in the cooling unit flows to the downstream side of the cooling unit due to the airflow of the air conditioner, the condensed water can be brought into contact with the surface of the contact unit.

According to the ninth aspect, the apparatus further includes a water retaining member provided outside the contact portion and capable of retaining condensed water.

According to this, even if the amount of condensed water generated in the cooling unit changes, the water retaining member always retains the condensed water, so the portion of the contact portion where the water retaining member is provided is always in contact with the condensed water. To do. Therefore, this apparatus temperature control apparatus can cool stably the working fluid which flows inside the contact part.

On the other hand, when the outside air temperature is low such as in winter, the water retaining member provided outside the contact portion functions as a heat insulating layer, so that the working fluid flowing inside the contact portion can be prevented from being cooled by the outside air. Therefore, when the outside air temperature is low such as in winter, the cooling capacity of the device temperature control device can be suppressed.

Claims (9)

1. It is mounted on a vehicle including an air conditioning unit (41) that cools blown air by a cooling unit (50) disposed in an air conditioning case (44) and blows the air into the passenger compartment, and a phase between a liquid phase and a gas phase of the working fluid. A device temperature control device for adjusting the temperature of the target device (12) by a change,
   A heat absorbing part (14) for evaporating the working fluid by absorbing heat from the target device to the working fluid;
   A heat dissipating part (16) provided above the heat absorbing part and condensing the working fluid by dissipating the working fluid evaporated in the heat absorbing part;
   A forward flow passage (18a) that connects the heat radiation portion discharge port (16b) for discharging the liquid phase working fluid from the heat radiation portion and the heat absorption portion inlet (14b) for flowing the liquid phase working fluid into the heat absorption portion. A forward path portion (18) to be formed;
   A return flow passage (20a) that connects a heat absorption part discharge port (14c) for discharging the gas phase working fluid from the heat absorption part and a heat radiation part inlet (16a) for flowing the gas phase working fluid into the heat dissipation part. A return path portion (20) to be formed,
   At least one of the heat radiating part and the forward path part has a temperature control unit having contact parts (161, 181) configured to exchange heat between the working fluid flowing inside thereof and the condensed water generated in the cooling part. apparatus.
2. The apparatus temperature adjusting device according to claim 1, wherein the contact portion is provided at a position where the condensed water generated in the cooling portion comes into contact.
3. The apparatus temperature control device according to claim 1 or 2, further comprising a guide plate (63) for guiding the condensed water generated in the cooling unit to the contact unit.
4. Further comprising a discharge pipe (61) for discharging the condensed water generated in the cooling unit to the outside of the vehicle,
   The apparatus temperature control device according to claim 1, wherein the contact portion is in contact with the discharge pipe.
5. The apparatus temperature control device according to claim 4, wherein the contact portion and the discharge pipe included in the forward path section constitute a double pipe structure (70) in which one of them is disposed inside the other.
6. The apparatus temperature control device according to claim 4 or 5, further comprising a switching valve (65) provided in the discharge pipe and configured to switch between a state in which condensed water flowing through the discharge pipe flows to the contact portion and a state in which the condensed water is stopped.
7. The air conditioner further includes a tray (60) that receives the condensed water generated in the cooling unit,
   The apparatus temperature control device according to claim 1, wherein the contact portion is provided in the lower tray.
8. The device temperature adjusting device according to claim 7, wherein the contact portion is provided in a portion of the lower tray that is downstream of the cooling portion with respect to the air flow.
9. The device temperature adjusting device according to any one of claims 1 to 8, further comprising a water retaining member (64) provided outside the contact portion and capable of retaining condensed water.

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