WO2014073150A1

WO2014073150A1 - Cooling device

Info

Publication number: WO2014073150A1
Application number: PCT/JP2013/005862
Authority: WO
Inventors: 木下　宏; 山中　隆; 竹内　雅之
Original assignee: 株式会社デンソー
Priority date: 2012-11-07
Filing date: 2013-10-02
Publication date: 2014-05-15
Also published as: JP6098121B2; JP2014095484A

Abstract

A cooling device equipped with multiple batteries (4) and a refrigeration cycle device (10). The refrigeration cycle device is formed by connecting, in a circular arrangement, a compressor (11), a cooling medium radiator (12), a decompression unit (13), and multiple evaporators (14) provided in correspondence with the multiple batteries. The cooling medium flowing through the multiple evaporators absorbs heat from the multiple batteries, thereby cooling the multiple batteries. The multiple batteries are mounted dispersed in different locations in a vehicle (2). At least one of the multiple batteries is mounted in a location where the environmental temperature when the vehicle is in use differs from that of the other batteries. The multiple evaporators are connected in series such that the cooling medium that has been decompressed by the decompression unit passes through the evaporators sequentially. In the refrigeration cycle device the cooling medium that has been decompressed by the decompression unit and changed to a gas-liquid two-phase state is circulated so as to maintain the cooling medium in the gas-liquid two-phase state until the cooling medium flows out from the evaporator farthest downstream in the refrigerant flow, that is, the evaporator (14C) which is closest to the compressor.

Description

Cooling system

Cross-reference of related applications

This disclosure is based on Japanese Patent Application No. 2012-245532 filed on November 7, 2012, the contents of which are incorporated herein.

The present disclosure relates to a cooling device that cools a plurality of storage batteries mounted on a vehicle.

2. Description of the Related Art Conventionally, a cooling device that cools a storage battery by circulating a refrigerant that circulates in a refrigeration cycle is known in a case of a storage battery in which a single cell is accommodated inside the case (see, for example, Patent Document 1 below). .

Japanese Patent No. 3855382

In recent years, for example, in vehicles such as electric vehicles and hybrid vehicles, a relatively large capacity storage battery is required, but in order to ensure a relatively large boarding space for passengers and a large space for loading luggage, The restrictions on the storage space for storage batteries are increasing. In order to cope with this restriction, it may be necessary to disperse and mount a plurality of relatively small-capacity storage batteries in the vehicle.

However, in such a case, when the vehicle is used, since the environmental temperature such as the ambient temperature at the position where the plurality of storage batteries are mounted is different, it is difficult to cool the plurality of storage batteries well.

This indication is made in view of the above-mentioned point, and provides a cooling device which can cool a plurality of storage batteries satisfactorily, even when environmental temperature in a mounting position of a plurality of storage batteries differs. With the goal.

In order to achieve the above object, a cooling device according to the present disclosure includes a plurality of storage batteries and a refrigeration cycle device. The refrigeration cycle apparatus includes a plurality of evaporators provided corresponding to a plurality of storage batteries that are distributed and mounted at different positions of a vehicle. The plurality of evaporators are connected in series so that the refrigerant depressurized by the depressurization unit sequentially flows. The refrigeration cycle apparatus is in a gas-liquid two-phase state until the refrigerant that has been decompressed by the decompression unit and is in a gas-liquid two-phase state flows out of the most downstream evaporator closest to the compressor in the refrigerant flow among the plurality of evaporators. Circulate refrigerant to maintain.

According to this, the gas-liquid two-phase refrigerant decompressed by the decompression unit flows in any of the plurality of evaporators, and the liquid refrigerant is evaporated by heat absorption from the plurality of storage batteries in all of the plurality of evaporators. Can do. Therefore, it is possible to cool a some storage battery with the refrigerant | coolant of the same temperature. Thus, even if the environmental temperature in the mounting place of a some storage battery differs, a some storage battery can be cooled favorably.

It is a schematic diagram which shows schematic structure of the cooling device in 1st Embodiment. It is a schematic diagram which shows the vehicle mounting position of the cooling device of 1st Embodiment. FIG. 3 is a sectional view taken along line III-III in FIG. 2. FIG. 4 is a sectional view taken along line IV-IV in FIG. 2. FIG. 5 is a sectional view taken along line VV in FIG. 2. It is a schematic diagram which shows schematic structure of the cooling device of the modification of 1st Embodiment. It is a schematic diagram which shows schematic structure of the cooling device of a comparative example. It is a schematic diagram which shows schematic structure of the cooling device of another comparative example. It is a graph which shows an example of the cooling temperature of a some evaporator. It is a schematic diagram which shows schematic structure of the cooling device in 2nd Embodiment. It is a schematic diagram which shows schematic structure of the cooling device of the modification of 2nd Embodiment. It is a schematic diagram which shows schematic structure of the cooling device in 3rd Embodiment. It is a schematic diagram which shows schematic structure of the cooling device in 4th Embodiment. It is a pressure-enthalpy diagram which shows the state of the refrigerant | coolant of the refrigerating cycle of 4th Embodiment. It is a schematic diagram which shows schematic structure of the cooling device in 5th Embodiment. It is a pressure-enthalpy diagram which shows the state of the refrigerant | coolant of the refrigerating cycle of 5th Embodiment. It is a schematic diagram which shows the vehicle mounting position of the cooling device of other embodiment. FIG. 18 is a cross-sectional view taken along line XVIII-XVIII in FIG. FIG. 18 is a sectional view taken along line XIX-XIX in FIG. 17. FIG. 18 is a sectional view taken along line XX-XX in FIG.

Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. In the case where only a part of the configuration is described in each embodiment, the other parts of the configuration are the same as those described previously. In addition to the combination of parts specifically described in each embodiment, the embodiments may be partially combined as long as the combination is not particularly troublesome.

(First embodiment)
A first embodiment to which the present disclosure is applied will be described with reference to FIGS. 1 to 9.

A cooling device 1 shown in FIG. 1 is mounted on a hybrid vehicle having, for example, an internal combustion engine and an electric motor as a driving force source (for example, a drive unit 3 shown in FIG. 2), and includes a plurality of storage batteries 4. A refrigeration cycle apparatus 10 (hereinafter sometimes referred to as a refrigeration cycle) for cooling is provided.

The refrigeration cycle apparatus 10 is configured by connecting a compressor 11, a condenser 12, a decompressor 13, and a plurality of evaporators 14 in a ring shape with a refrigerant pipe 19.

The compressor 11 is, for example, an electric type, and sucks, compresses and discharges the refrigerant. The condenser 12 blows the high-temperature and high-pressure refrigerant discharged from the compressor 11 by, for example, an electric fan 12a. This is a refrigerant radiator that cools and condenses by exchanging heat with the outside air. The refrigerant radiator can be a gas cooler that cools the refrigerant in a supercritical state, for example, when carbon dioxide is used as the refrigerant and the compressor 11 raises the refrigerant to a pressure exceeding the critical pressure.

The condenser 12 of this example is a so-called subcool condenser that has a liquid receiver integrally provided and cools the liquid-phase refrigerant to a supercooled state. When the condenser 12 is a heat exchanger that does not have a supercooling section, the liquid receiver may be provided between the condenser 12 and the decompressor 13.

The decompressor 13 is composed of, for example, an expansion valve, and decompresses the high-pressure refrigerant condensed by the condenser 12. That is, the decompressor 13 is a decompression unit that decompresses the high-pressure refrigerant that has flowed out of the refrigerant radiator. The plurality of evaporators 14 are provided in the low-pressure refrigerant flow path on the downstream side of the decompressor 13.

In this example, three evaporators 14 are provided corresponding to the three storage batteries 4 mounted on the vehicle. The three evaporators 14 are connected in series via a refrigerant pipe 19 so that the low-pressure refrigerant decompressed by the decompressor 14 flows in sequence.

The plurality of storage batteries 4 are, for example, storage batteries each having one or more lithium ion battery cells, and are preferably used in a predetermined temperature range determined by charge / discharge characteristics and the like. That is, the some storage battery 4 is a storage battery with the same management temperature range which should be managed based on a battery characteristic.

The plurality of storage batteries 4 are distributed and mounted on the vehicle for the purpose of securing the cabin of the vehicle and the space of the cargo compartment. Therefore, the plurality of evaporators 14 for cooling the plurality of storage batteries 4 are also distributed at the mounting positions of the plurality of storage batteries 4, and the plurality of evaporators 14 that are distributed are connected by the refrigerant pipe 19. ing.

The storage battery 4 is arranged so as to be able to exchange heat with the refrigerant flowing through the evaporator 14. That is, the storage battery 4 is disposed so as to be thermally connected to the evaporator 14. For example, when the evaporator 14 has a plurality of flat tubes through which the refrigerant flows, the storage battery 4 can be disposed so as to be sandwiched between the flat tubes. Further, for example, in the case where the evaporator 14 is a container body having heat insulation properties and a refrigerant is circulated inside the container body, the storage battery 4 may be disposed inside the container body. .

The plurality of storage batteries 4 and the evaporators 14 are distributed and mounted at different positions on the vehicle 2 as shown in FIG. In the refrigeration cycle 10 illustrated in FIG. 2, among the plurality of evaporators 14, the most upstream evaporator 14 A closest to the decompressor 13 in the refrigerant flow is disposed at the bottom of the cargo compartment at the rear of the vehicle. The most downstream evaporator 14 C closest to the compressor 11 in the refrigerant flow and the evaporator 14 B disposed on the upstream side thereof are disposed below the cabin of the vehicle 2.

As shown in FIGS. 3 and 4, the

evaporators

14B and 14C are disposed outside the passenger compartment below the floor plate portion 5a of the vehicle body 5. FIG. As shown in FIG. 3, the evaporator 14C is disposed adjacent to the exhaust pipe 6 extending from the internal combustion engine of the vehicle below the floor plate portion 5a.

The exhaust pipe 6 shown in FIG. 3 is a part through which the exhaust gas immediately after being exhausted from the internal combustion engine and purified by, for example, a catalyst, circulates, and thus includes a heat insulator 6a disposed so as to surround the exhaust pipe 6. Since exhaust gas of about 400 ° C., for example, flows through the exhaust pipe 6 shown in FIG. 3 when the vehicle is used, the environmental temperature (storage battery for transmitting the ambient temperature and the floor plate portion 5a) at the mounting position of the evaporator 14C and the storage battery 4 to be cooled by this. The temperature at the mounting position is, for example, about 50 ° C.

On the other hand, the exhaust pipe 6 shown in FIG. 4 is a portion through which exhaust gas radiated to the outside flows after being exhausted from the internal combustion engine. Since exhaust gas of about 150 ° C. flows through the exhaust pipe 6 shown in FIG. 4, for example, the environmental temperature at the mounting position of the evaporator 14B and the storage battery 4 cooled by the evaporator 14B is about 40 ° C.

Further, as shown in FIG. 5, the evaporator 14 A is disposed in the passenger compartment above the floor plate portion 5 a of the body 5. Specifically, the evaporator 14A is disposed in the storage battery housing recess 5b formed in the lower part of the cargo compartment of the vehicle, and is covered with a cover plate 5c. The evaporator 14A is disposed adjacent to the exhaust pipe 6 via the floor plate portion 5a in the storage battery housing recess 5b.

However, the exhaust pipe 6 shown in FIG. 5 is a part through which the exhaust gas that has largely radiated heat flows after being exhausted from the internal combustion engine. For example, since exhaust gas of about 40 ° C. flows through the exhaust pipe 6 shown in FIG. 5, the heat of the exhaust gas hardly affects the storage battery housing recess 5b. Therefore, the environmental temperature at the mounting position of the evaporator 14A and the storage battery 4 cooled by the evaporator 14A is about 20 to 40 ° C. due to, for example, the outside air temperature or the influence of solar radiation on the body 5.

As described above, the plurality of storage batteries 4 and the evaporator 14 are different from each other in environmental temperature (atmosphere temperature or temperature of a member to be contacted) at each mounting position. Moreover, the evaporator 14 which cools the some storage battery 4 differs in the mounting height in a vehicle.

For example, when the vehicle is stopped on a horizontal ground and the vehicle is not inclined, the evaporator 14A is mounted at the highest position and the evaporator 14C is mounted at the lowest position among the three evaporators 14. ing. Therefore, in the evaporators 14 connected via the refrigerant pipe 19 and adjacent to each other, the evaporator 14 having a higher environmental temperature at the mounting position is mounted higher than the evaporator 14 having a lower environmental temperature at the mounting position. Is low.

As shown in FIGS. 1 and 2, the pressure reducer 13 flows out of the most downstream evaporator 14C and is sucked into the compressor 11 (specifically, immediately after flowing out of the most downstream evaporator 14C). It has a temperature sensing part 131 that senses the temperature of the refrigerant. The temperature sensing unit 131 transmits pressure information corresponding to the detected refrigerant temperature to the main body of the decompressor 13.

Based on the information from the temperature sensing unit 131, the decompressor 13 is configured so that the refrigerant flowing out from the most downstream evaporator 14C is in a gas-liquid two-phase state (specifically, the two-phase state having a very high degree of dryness). Adjust the opening of the expansion valve.

Next, the operation of the cooling device 1 will be described based on the above configuration. When the compressor 11 is driven, the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 is condensed and liquefied by the condenser 12. The high-pressure liquid refrigerant that has flowed out of the condenser 12 is decompressed to a low-pressure by the decompressor 13 and enters a gas-liquid two-phase state. The low-pressure refrigerant decompressed by the decompressor 13 flows through the plurality of evaporators 14 in the order of the

evaporators

14A, 14B, and 14C, and cools the storage battery 4 in each of the evaporators 14.

Thus, when the refrigerant circulates in the refrigeration cycle 1, the decompressor 13 adjusts the amount of decompression so that the refrigerant flowing out of the most downstream evaporator 14C is in a gas-liquid two-phase state. Therefore, in the three evaporators 14, although the dryness is different from each other, the refrigerant flows in the state where the liquid phase refrigerant exists. Therefore, in all the evaporators 14, a liquid phase refrigerant can be evaporated and the storage battery 4 can be cooled, and it suppresses that the cooling shortage by a dry-out phenomenon arises.

According to the above-described configuration and operation, the plurality of evaporators 14 provided corresponding to the plurality of storage batteries 4 distributed and mounted at different positions of the vehicle are configured so that the refrigerant decompressed by the decompressor 13 sequentially flows. The refrigerant is circulated so as to maintain a gas-liquid two-phase state until the refrigerant decompressed by the decompressor 13 flows out of the most downstream evaporator 14C.

According to this, the gas-liquid two-phase refrigerant decompressed by the decompressor 13 circulates in any of the plurality of evaporators 14, and the liquid refrigerant is absorbed by heat absorption from the plurality of storage batteries 4 in all of the plurality of evaporators 14. Can be evaporated. Therefore, the plurality of storage batteries 4 can be cooled with the refrigerant having the same temperature. Thus, even if it is a case where the environmental temperature in the mounting place of the some storage battery 4 differs, the some storage battery 4 can be cooled favorably.

The plurality of storage batteries 4 are storage batteries having the same management temperature range to be managed based on the battery characteristics. A plurality of storage batteries 4 are mounted in a distributed manner at different positions in the vehicle when the environment temperature is in use. The refrigeration cycle 10 having a plurality of evaporators 14 provided corresponding to the plurality of storage batteries 4 is decompressed by the decompressor 13 and the most downstream of the plurality of evaporators 14 closest to the compressor 11 in the refrigerant flow. The refrigerant is circulated so as to maintain the gas-liquid two-phase state within the management temperature range of the storage battery 4 until it flows out of the evaporator 14C.

Therefore, it is possible to cool the storage battery 4 by evaporating the liquid refrigerant by heat absorption from the plurality of storage batteries 4 in all of the plurality of evaporators 14, and to maintain all of the plurality of storage batteries 4 at substantially the same temperature within the management temperature range. it can.

As a comparative example, a cooling device 901 is illustrated in FIG. The cooling device 901 cools the cooling water by exchanging heat between the refrigerant circulating in the refrigeration cycle 910 and the cooling water circulating in the water circulation circuit 911 by the water circulation pump 912 in the evaporator of the refrigeration cycle 901. . A plurality of storage batteries 4 are provided in parallel in the water circulation circuit 911 and are cooled by cooling water circulating in the water circulation circuit 911.

In such a cooling device 901, when a plurality of storage batteries 4 are distributed and mounted at different positions of the vehicle, the circuit configuration of the water circulation circuit 911 becomes complicated, and the environmental temperature of the storage battery 4 and the handling of the water circulation circuit 911 are increased. There exists a problem that the cooling temperature of the some storage battery 4 may differ depending on a form. On the other hand, according to the cooling device 1 of the present embodiment, the circuit configuration can be relatively simplified, and the cooling temperatures of the plurality of storage batteries 4 can be set to substantially the same temperature.

Further, as another comparative example, a cooling device 902 is illustrated in FIG. The cooling device 902 cools the cooling water by exchanging heat between the refrigerant circulating in the refrigeration cycle 910 and the cooling water circulating in the water circulation circuit 911A by the water circulation pump 912 in the evaporator of the refrigeration cycle 901. . A plurality of storage batteries 4 are provided in series in the water circulation circuit 911 A and are cooled by cooling water circulating in the water circulation circuit 911.

In such a cooling device 902, the circuit configuration of the water circulation circuit 911A can be simplified more than the circuit configuration of the water circulation circuit 911 described above when the plurality of storage batteries 4 are distributed and mounted at different positions of the vehicle. However, there is a problem that the cooling temperatures of the plurality of storage batteries 4 are greatly different. For example, as shown by a broken line in FIG. 9, the cooling water flowing out of the evaporator rises in temperature each time it passes through the storage battery 4 provided in series with the water circulation circuit 911 A, and the downstream side of the storage battery 4 provided on the most upstream side. The cooling temperature greatly deviates from the storage battery 4 provided in the battery.

On the other hand, according to the cooling device 1 of the present embodiment, as shown by the solid line in FIG. 9, there is a slight temperature drop due to the pressure loss of each evaporator 14 and the refrigerant pipe 19 connecting the evaporators 14. However, the temperature of the refrigerant passing through the plurality of evaporators 14 can be made substantially the same.

Further, among the plurality of evaporators 14, the evaporator 14A is mounted at the highest position, and the evaporator 14C is mounted at the lowest position. Therefore, in the evaporators 14 connected via the refrigerant pipe 19 and adjacent to each other, the evaporator 14 having a higher environmental temperature at the mounting position is mounted higher than the evaporator 14 having a lower environmental temperature at the mounting position. Is low.

According to this, for example, when the compressor 11 stops driving and the refrigerant circulation of the refrigeration cycle 10 stops, the storage battery 4 is cooled using the height relationship between the adjacent evaporators 14 via the refrigerant pipe 19. Is possible.

Here, the case of the evaporator 14B and the evaporator 14C will be described as an example. The evaporator 14B is mounted on the vehicle at a position higher than the evaporator 14C. Moreover, the environmental temperature of the evaporator 14B is lower than the environmental temperature of the evaporator 14C.

With such a configuration, in a state where the refrigerant circulation of the refrigeration cycle 10 is stopped, the liquid-phase refrigerant is easily evaporated in the evaporator 14C. The vapor-phase refrigerant generated by evaporation in the evaporator 14C rises toward the evaporator 14B mounted above the evaporator 14C via the refrigerant pipe 19 that connects the evaporator 14B and the evaporator 14C. To do. At that time, the gas-phase refrigerant is cooled in the refrigerant pipe 19 and in the evaporator 14B, and becomes a liquid-phase refrigerant and returns to the evaporator 14C mounted below.

That is, the storage battery 4 can be preferentially cooled by the evaporator 14C having the higher environmental temperature by causing the configuration including the

evaporators

14B and 14C connected by the refrigerant pipe 19 to function as a heat pipe.

Next, a modification of the present embodiment is shown in FIG. In the cooling device shown in FIG. 6, the refrigeration cycle 10 is provided in parallel with the plurality of evaporators 14, and is disposed in an air conditioning duct (not shown), for example, for air conditioning evaporation that cools air blown into the passenger compartment. A container 24 is provided.

A parallel refrigerant pipe 19a is connected to the refrigerant pipe 19 that connects each component of the refrigeration cycle 10 in an annular shape. The upstream end of the parallel refrigerant pipe 19a is connected to the refrigerant pipe 19 through which the refrigerant flowing out of the condenser 12 and flowing into the decompressor 13 flows. The downstream end of the parallel refrigerant pipe 19a is connected to the refrigerant pipe 19 through which the refrigerant flowing out of the most downstream evaporator 14C and sucked into the compressor 11 flows.

The air conditioning evaporator 24 is provided in the parallel refrigerant pipe 19a. The parallel refrigerant pipe 19a is provided with an opening / closing valve 25 for opening / closing a flow path of the refrigerant flowing through the air conditioning evaporator 24 and a decompressor 23 between the upstream end and the site where the air conditioning evaporator 24 is disposed. Has been. The decompressor 23 is a decompression unit having a temperature sensing unit 231 similarly to the decompressor 13, and adjusts the opening of the expansion valve so that the refrigerant flowing out of the air conditioning evaporator 24 is in a predetermined state.

Also, between the parallel refrigerant pipe 19 a upstream end connection portion of the refrigerant pipe 19 and the decompressor 13, an opening / closing valve 15 that opens and closes the refrigerant flow path through the plurality of evaporators 14 is provided.

The cooling device shown in FIG. 6 includes an evaporation temperature sensor 16 that detects the refrigerant evaporation temperature of the evaporator 14, an evaporator temperature sensor 26 that detects the temperature of the air conditioning evaporator 24, and a control device 30 that is a control unit. ing. The control device 30 controls the driving of the compressor 11 and the on-off valve 15 based on temperature information from the evaporation temperature sensor 16 and the evaporator temperature sensor 26 in addition to information from various sensors for air conditioning and an air conditioning condition setting unit. , 25 is controlled.

In this example, the evaporator temperature sensor 26 is an air temperature sensor (so-called post-evaporation temperature sensor) that detects the temperature of the conditioned air immediately after flowing out of the air conditioning evaporator 24, but is not limited thereto. . The evaporator temperature sensor 26 may be, for example, a fin temperature sensor attached to an outer fin of the air conditioning evaporator 24.

The control device 30 calculates a target blowing temperature TAO of the conditioned air into the passenger compartment based on information from various sensors for air conditioning and an air conditioning condition setting unit, and the air conditioning evaporator 24 based on the target blowing temperature TAO. The target air temperature TEO which is the cooling target of the conditioned air by is calculated. Then, the rotational speed NcA of the compressor 11 is set so that the air temperature TE detected by the evaporator temperature sensor 26 matches the target air temperature TEO (so that the air temperature TE is feedback-controlled with respect to the target air temperature TEO). decide.

The control device 30 also sets the target evaporation temperature for battery cooling so that the evaporation temperature Tb detected by the evaporation temperature sensor 16 matches the target evaporation temperature Tbo in the evaporator 14 (the target cooling temperature of the storage battery 4 in the evaporator 14). The rotational speed NcB of the compressor 11 is determined so that the evaporation temperature Tb is feedback-controlled with respect to the temperature Tbo).

Then, the control device 30 drives and controls the compressor 11 so that the compressor 11 is driven at the rotation speed Nc that is the sum of the rotation speed NcA and the rotation speed NcB. The control device 30 controls the opening /

closing valves

15 and 25 according to whether or not the evaporator 14 and the air conditioning evaporator 24 need to be cooled. The control device 30 also determines the rotational speed Nc for the drive control of the compressor 11 according to the necessity of cooling in the evaporator 14 and the air conditioning evaporator 24.

For example, when it is not necessary to cool the conditioned air by the air conditioning evaporator 24 (for example, when the air conditioner switch is off in the air conditioning operation panel) and only the storage battery 4 is cooled, the on-off valve 15 is opened and opened / closed. The valve 25 is closed and the compressor 11 is driven and controlled so as to be driven at the rotational speed NcB (assuming the rotational speed Nc = NcB).

According to this example, the compressor 11 and the condenser 12 can be shared for battery cooling and air conditioning. In addition, since the air conditioning evaporator 24 and the plurality of evaporators 14 for cooling the storage battery 4 are not connected in series, the refrigerant flowing out from the most downstream evaporator 14C is removed even if the air conditioning evaporator 24 is provided. It is easy to make a liquid two-phase refrigerant.

(Second Embodiment)
Next, 2nd Embodiment is described based on FIG. 10 and FIG.

The second embodiment is different from the first embodiment in that the refrigeration cycle apparatus is changed from a receiver cycle to an accumulator cycle. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted. Components having the same reference numerals as those in the drawings according to the first embodiment and other configurations not described in the second embodiment are the same as those in the first embodiment and have the same effects.

As shown in FIG. 10, the refrigeration cycle apparatus used in the cooling apparatus of the present embodiment includes an accumulator 17 in the refrigerant pipe 19 through which the refrigerant flowing out of the most downstream evaporator 14C and sucked by the compressor 11 flows. The accumulator 17 has a function of performing gas-liquid separation of the refrigerant flowing out from the most downstream evaporator 14C and storing excess liquid-phase refrigerant. The gas phase refrigerant separated from the liquid phase refrigerant by the accumulator 17 is sucked into the compressor 11.

In the present embodiment, the condenser 12 does not have a liquid receiver, and the decompressor 13A as the decompression unit opens the expansion valve so that, for example, the refrigerant flowing out of the condenser 12 is in a predetermined supercooled state. Adjust the degree. When it is not necessary to control the supercooling state of the refrigerant flowing out of the condenser 12, the decompressor 13A may be a fixed throttle, for example.

According to the cooling device of the present embodiment, the accumulator 17 is provided in a path through which the refrigerant that flows out of the most downstream evaporator 14C and sucked by the compressor 11 flows, and stores the liquid-phase refrigerant by gas-liquid separation. Yes.

According to this, the refrigerant flowing out from the most downstream evaporator 14C can be easily made into a gas-liquid two-phase refrigerant. Therefore, even if the environmental temperature in the mounting place of the some storage battery 4 differs, the some storage battery 4 can be cooled favorably easily.

Next, a modification of this embodiment is shown in FIG. In the cooling apparatus shown in FIG. 11, the refrigeration cycle 10 includes an air conditioning evaporator 24 provided in parallel with a plurality of evaporators 14. The parallel refrigerant pipe 19a provided with the air conditioning evaporator 24 is provided with a flow rate adjusting valve 27 between the upstream end and the site where the air conditioning evaporator 24 is disposed. The flow rate adjusting valve 27 is a pressure reducing unit formed of, for example, an expansion valve having a fully closed function.

In the refrigerant pipe 19 through which the refrigerant flowing out from the condenser 12 and flowing to the upstream end connection point of the parallel refrigerant pipe 19a flows (specifically, at the refrigerant outlet of the condenser 12), the pressure and temperature of the refrigerant are detected. A pressure temperature sensor 28 is provided.

The cooling apparatus shown in FIG. The control device 30 controls the driving of the compressor 11, the opening / closing operation control of the on-off valve 15, and the flow rate based on the pressure information and temperature information from the pressure temperature sensor 28 in addition to the information from various sensors and the air conditioning condition setting unit. The opening degree of the adjustment valve 27 is controlled.

The control device 30 calculates the rotational speed Nc of the compressor 11 and controls the drive of the compressor 11 as in the modification of the first embodiment described with reference to FIG.

Further, the cooling capacity required for the air conditioning evaporator 24 is much larger than the cooling capacity required for the plurality of evaporators 14 for cooling the storage battery 4. Therefore, the control device 30 controls the degree of supercooling of the refrigerant flowing out of the condenser 12 by adjusting the opening degree of the flow rate adjustment valve 27 based on the pressure information and temperature information from the pressure temperature sensor 28.

Further, the control device 30 controls opening / closing of the opening / closing valve 15 and the flow rate adjusting valve 27 in accordance with the necessity of cooling in the evaporator 14 and the evaporator 24 for air conditioning. The control device 30 also determines the rotational speed Nc for the drive control of the compressor 11 according to the necessity of cooling in the evaporator 14 and the air conditioning evaporator 24.

For example, when it is not necessary to cool the conditioned air by the air-conditioning evaporator 24 and only the storage battery 4 is cooled, the on-off valve 15 is opened, the flow rate adjustment valve 27 is fully closed, and the compressor is driven at the rotational speed NcB. The machine 11 is driven and controlled.

(Third embodiment)
Next, a third embodiment will be described with reference to FIG.

3rd Embodiment differs in the point provided with the structure which can suppress the temperature rising of the storage battery 4 also at the time of the compressor 11 drive stop compared with the above-mentioned 1st Embodiment. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted. Components having the same reference numerals as those in the drawing according to the first embodiment, and other configurations not described in the third embodiment are the same as those in the first embodiment, and have the same effects.

As shown in FIG. 12, the refrigeration cycle apparatus used in the cooling apparatus of the present embodiment includes a refrigerant circulation path 40, a refrigerant tank 41, a refrigerant pump 42, and

check valves

18 and 43.

The refrigerant tank 41 is provided in the refrigerant pipe 19 through which the refrigerant flowing out of the most downstream evaporator 14C and sucked by the compressor 11 flows. The refrigerant tank 41 is a tank for storing a liquid phase refrigerant therein. The accumulator 17 described in the second embodiment can be used as a refrigerant tank.

The refrigerant circulation path 40 is connected to a refrigerant tank 41 (specifically, a portion where the liquid-phase refrigerant in the refrigerant tank 41 can be introduced) at the lower upstream end in the figure, and the decompressor 13 at the upper downstream end in the figure. The refrigerant is connected to a refrigerant pipe 19 through which the refrigerant that has been decompressed and flows into the evaporator 14A flows. A refrigerant pump 42 and a check valve 43 are provided in the refrigerant circulation path 40. The check valve 43 allows the refrigerant flow from the upstream end to the downstream end of the refrigerant circulation path 40 and prohibits the refrigerant flow from the downstream end to the upstream end.

Further, a check valve 18 is provided in the refrigerant pipe 19 through which the refrigerant is decompressed by the decompressor 13 and reaches the downstream end connection portion of the refrigerant circulation path 40. The check valve 18 allows the refrigerant flow from the decompressor 13 toward the downstream end connection portion of the refrigerant circulation path 40 and prohibits the refrigerant flow from the downstream end connection portion of the refrigerant circulation path 40 toward the decompressor 13.

In the cooling device of this embodiment, the control device (not shown) drives the refrigerant pump 42 when the drive of the compressor 11 is stopped, and enters the refrigerant tank 41 as shown by an arrow in FIG. The stored liquid-phase refrigerant is circulated to the refrigerant circulation path 40 and the plurality of evaporators 14. In the plurality of evaporators 14, the liquid phase refrigerant that has absorbed heat from the storage battery 4 evaporates. As the liquid-phase refrigerant evaporates into a gas-phase refrigerant, the pressure in the plurality of evaporators 14 gradually rises and the refrigerant temperature gradually rises, but the inside of the plurality of evaporators 14 has the same temperature. can do.

According to the cooling device of the present embodiment, the refrigerant circulation path 40 that can circulate the refrigerant in a path that includes the plurality of evaporators 14 and does not include the compressor 11, the condenser 12, and the decompressor 13, and the refrigerant circulation path 40 A refrigerant tank 41 that is provided and can store a liquid-phase refrigerant, and a refrigerant pump 42 that is a pump unit that circulates the refrigerant in the refrigerant circulation path 40 are provided.

According to this, when the compressor 11 is stopped, the refrigerant can be circulated in the refrigerant circulation path 40 by driving the refrigerant pump 42. Therefore, even when the compressor 11 is stopped, the liquid refrigerant stored in the refrigerant tank 41 can be circulated through the refrigerant circulation path 40 and the refrigerant can be evaporated by the plurality of evaporators 14. Thus, even when the compressor 11 is stopped, the temperature of the plurality of storage batteries 4 can be gradually increased at a uniform temperature.

In other words, even when the compressor 11 is stopped, the stored liquid-phase refrigerant is circulated to the plurality of evaporators 14, and the cooling temperatures of the plurality of storage batteries 4 are transferred to the plurality of storage batteries 4. The cooling temperature can be gradually increased while being uniform throughout.

Further, by operating the compressor 11 intermittently and driving the refrigerant pump 42 when the compressor 11 is stopped, it is possible to shorten the operation time of the compressor 11 having a relatively large amount of energy consumption.

(Fourth embodiment)
Next, 4th Embodiment is described based on FIG. 13 and FIG.

The fourth embodiment is different from the second embodiment described above in that an internal heat exchanger is provided to improve the cooling capacity. In addition, about the part similar to 1st, 2nd embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted. The components denoted by the same reference numerals as those in the drawings according to the first and second embodiments, and other configurations not described in the fourth embodiment are the same as those in the first and second embodiments, and have the same effects. Is.

As shown in FIG. 13, the refrigeration cycle apparatus used for the cooling apparatus of this embodiment includes an internal heat exchanger 50 and a throttle 51. The restrictor 51 is a decompression unit that further decompresses the refrigerant before being decompressed by the decompressor 13 A and flowing into the plurality of evaporators 14. The decompressor 13A corresponds to the first decompression unit in the present embodiment, and the throttle 51 corresponds to the second decompression unit in the present embodiment.

The internal heat exchanger 50 is a heat exchanger that exchanges heat between the refrigerant that has been decompressed by the decompressor 13A and before being decompressed by the throttle 51, and the refrigerant that has flowed out of the most downstream evaporator 14C and has been sucked into the compressor 11. It is.

When the compressor 11 of the refrigeration cycle apparatus of the present embodiment is driven and the refrigerant circulates in the refrigeration cycle apparatus, the refrigerant state in the cycle is as shown in FIG. By the heat exchange in the internal heat exchanger 50, the dryness of the refrigerant flowing into the uppermost stream evaporator 14A can be reduced, and a refrigerant state in which the ratio of the liquid phase refrigerant is extremely high can be obtained. The broken line shown in FIG. 14 shows the case where the internal heat exchanger 50 and the throttle 51 are not provided.

According to the cooling apparatus of the present embodiment, the refrigeration cycle apparatus has, as the decompression unit, the decompressor 13A and the throttle 51 that further decompresses the refrigerant before being decompressed by the decompressor 13A and flowing into the plurality of evaporators 14. The internal heat exchanger 50 exchanges heat between the refrigerant before being decompressed by the decompressor 13A and before being decompressed by the throttle 51 and the refrigerant before flowing out of the most downstream evaporator 14C and sucked into the compressor 11. It has.

According to this, it is possible to cool the refrigerant whose dryness has been increased by reducing the pressure by the decompressor 13A by heat exchange of the internal heat exchanger 50, and to reduce the dryness. Therefore, the refrigerant flowing into the plurality of evaporators 14 can be a refrigerant rich in liquid phase refrigerant.

Moreover, the pressure loss in the refrigerant | coolant piping 19 which connects the some evaporator 14 and several evaporators 14 is reduced by making the refrigerant | coolant which flows into the several evaporator 14 into a refrigerant | coolant with a large ratio of a liquid phase refrigerant | coolant. The refrigerant evaporating temperature in each evaporator 14 can be approximated and made uniform (the slope of the graph illustrated in FIG. 9 can be made close to 0).

(Fifth embodiment)
Next, 5th Embodiment is described based on FIG. 15 and FIG.

The fifth embodiment is different from the first embodiment described above in that an internal heat exchanger is provided to improve the cooling capacity. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted. The components denoted by the same reference numerals as those in the drawing according to the first embodiment and other configurations not described in the fifth embodiment are the same as those in the first embodiment and have the same effects.

As shown in FIG. 15, the refrigeration cycle apparatus used in the cooling apparatus of this embodiment includes an internal heat exchanger 60. The internal heat exchanger 60 heats to exchange heat between the refrigerant that has flowed out of the condenser 12 and before being depressurized by the pressure reducer 13, and the refrigerant that has flowed out of the most downstream evaporator 14 C and before being sucked into the compressor 11. It is an exchanger.

When the compressor 11 of the refrigeration cycle apparatus of this embodiment is driven and the refrigerant circulates in the refrigeration cycle apparatus, the refrigerant state in the cycle is as shown in FIG. By heat exchange in the internal heat exchanger 60, the dryness of the refrigerant flowing into the uppermost stream evaporator 14A can be reduced, and a refrigerant state in which the ratio of the liquid phase refrigerant is high can be obtained. The broken line shown in FIG. 16 has shown the case where the internal heat exchanger 60 is not provided.

According to the cooling device of the present embodiment, the refrigeration cycle device includes the refrigerant before flowing out of the condenser 12 and being decompressed by the decompressor 13 and the refrigerant before flowing out of the most downstream evaporator 14C and sucked into the compressor 11. And an internal heat exchanger 60 for exchanging heat with each other.

According to this, the refrigerant before being decompressed by the decompressor 13 can be cooled by heat exchange of the internal heat exchanger 60. Thereby, the dryness of the refrigerant | coolant after being pressure-reduced with the pressure reduction device 13 can be raised. Therefore, the refrigerant flowing into the plurality of evaporators 14 can be a refrigerant rich in liquid phase refrigerant.

Moreover, the pressure loss in the refrigerant | coolant piping 19 which connects the some evaporator 14 and several evaporators 14 is reduced by making the refrigerant | coolant which flows into the several evaporator 14 into a refrigerant | coolant with a large ratio of a liquid phase refrigerant | coolant. The refrigerant evaporating temperatures in the respective evaporators 14 can be approximated and made uniform.

(Other embodiments)
The preferred embodiments of the present disclosure have been described above. However, the present disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present disclosure.

In each of the above embodiments, an example in which three evaporators 14 for cooling the storage battery 4 are provided has been described, but the number of evaporators 14 is not limited thereto. The evaporator 14 may be two, or four or more, corresponding to the number of storage batteries 4 distributed and mounted in the vehicle.

Further, in each of the above embodiments, the example in which the storage battery 4 and the evaporator 14 are mounted outside the vehicle cabin under the vehicle cabin or in the storage battery housing recess of the cargo compartment is described, but the present invention is not limited to this. For example, as illustrated in FIG. 17, a plurality of storage batteries 4 and corresponding evaporators 14A to 14F may be distributed and mounted.

For example, as shown in FIG. 18, the evaporator 14 D may be disposed in the vehicle interior (in the cabin in this example) above the floor plate portion 5 a of the body 5. The evaporator 14D is disposed on the upper surface of the tunnel ceiling portion of the floor plate portion 5a where the exhaust pipe 6 is disposed. Due to the influence of the exhaust gas immediately after being exhausted from the internal combustion engine, the upper surface of the tunnel ceiling portion of the floor plate portion 5a is For example, it becomes about 100 ° C. That is, the environmental temperature at the mounting position of the evaporator 14D and the storage battery 4 cooled by the evaporator 14D is about 100 ° C., for example.

Further, for example, as shown in FIG. 19, the evaporator 14 E may be disposed in the passenger compartment (in the cabin in this example) above the floor plate portion 5 a of the body 5. The evaporator 14E is also disposed on the upper surface of the tunnel ceiling portion of the floor plate portion 5a where the exhaust pipe 6 is disposed. Due to the influence of the exhaust gas flowing through the exhaust pipe 6, the upper surface of the tunnel ceiling portion of the floor plate portion 5a is, for example, about 60 ° C. That is, the environmental temperature at the mounting position of the evaporator 14E and the storage battery 4 that it cools is, for example, about 60 ° C.

Further, for example, as shown in FIG. 20, the evaporator 14F may be disposed in the cargo compartment. The environmental temperature at the mounting position of the evaporator 14F and the storage battery 4 cooled by the evaporator 14F is, for example, about 20 to 60 ° C. due to the influence of the outside air temperature and solar radiation.

As described above, even in the case of the cooling device including the storage batteries 4 mounted in a distributed manner at different environmental temperatures and the evaporators 14A to 14F for cooling them, the plurality of storage batteries 4 can be cooled satisfactorily.

In each of the above embodiments, the case where the environmental temperatures of all the storage batteries 4 are different from each other has been described. However, the present invention is not limited to this. It is effective to apply the present disclosure as long as at least one of the storage batteries 4 is mounted at a position where the environmental temperature during use of the vehicle is different from that of the other storage batteries 4.

In each of the above embodiments, all of the evaporators 14A to 14C are arranged such that the mounting position is lower as the evaporator 14 has a higher environmental temperature. However, the present invention is not limited to this. Of the at least one pair of evaporators 14 adjacent to each other in the refrigerant flow, it is only necessary that the evaporator 14 having a higher environmental temperature is disposed so that the mounting position becomes lower.

In each of the above embodiments, the cooling device that cools the plurality of storage batteries 4 mounted on the hybrid vehicle has been described. However, the present invention is not limited to this. For example, the vehicle may be an electric vehicle.

Claims

A plurality of storage batteries (4);
A refrigeration cycle apparatus (10) in which a compressor (11), a refrigerant radiator (12), a decompression unit (13), and a plurality of evaporators (14) provided corresponding to the plurality of storage batteries are annularly connected. ) And
A refrigerant that circulates through the plurality of evaporators absorbs heat from the plurality of storage batteries and cools the plurality of storage batteries,
The plurality of storage batteries are distributed and mounted at different positions of the vehicle (2),
Among the plurality of storage batteries, at least one storage battery is mounted at a position where the environmental temperature during use of the vehicle is different from other storage batteries,
The plurality of evaporators are connected in series so that the refrigerant depressurized by the depressurization unit sequentially flows,
In the refrigeration cycle apparatus, the refrigerant that has been decompressed by the decompression unit and is in a gas-liquid two-phase state flows out from the most downstream evaporator (14C) closest to the compressor in the refrigerant flow among the plurality of evaporators. A cooling device that circulates refrigerant so as to maintain a gas-liquid two-phase state.
The cooling device according to claim 1, further comprising an accumulator (17) provided in a path through which the refrigerant that flows out of the most downstream evaporator and flows into the compressor flows, and stores the liquid-phase refrigerant by gas-liquid separation.
A refrigerant circulation path (40) including the plurality of evaporators and capable of circulating a refrigerant in a path not including the compressor, the refrigerant radiator, and the decompression unit;
A refrigerant tank (41) provided in the refrigerant circulation path and capable of storing liquid phase refrigerant;
The cooling device according to claim 1, further comprising: a pump unit (42) that circulates the refrigerant in the refrigerant circulation path.
The decompression unit includes a first decompression unit (13A), and a second decompression unit (51) that further decompresses the refrigerant before being decompressed by the first decompression unit and flowing into the plurality of evaporators,
An internal heat exchanger that exchanges heat between the refrigerant that has been decompressed by the first decompression unit and before being decompressed by the second decompression unit, and the refrigerant that has flowed out of the most downstream evaporator and before being sucked into the compressor. The cooling device according to any one of claims 1 to 3, comprising (50).
An internal heat exchanger (60) for exchanging heat between the refrigerant that has flowed out of the refrigerant radiator and before being decompressed by the decompression unit, and the refrigerant that has flowed out of the most downstream evaporator and has not been sucked into the compressor. The cooling device according to any one of claims 1 to 3, further comprising:
The cooling device according to any one of claims 1 to 5, further comprising an air conditioning evaporator (24) that is provided in parallel to the plurality of evaporators and that cools the air blown into the passenger compartment.