WO2018070182A1

WO2018070182A1 - Appliance temperature regulating apparatus

Info

Publication number: WO2018070182A1
Application number: PCT/JP2017/033313
Authority: WO
Inventors: 功嗣三浦; 康光大見; 義則　毅; 竹内　雅之; 山中　隆; 加藤　吉毅; 慧伍佐藤
Original assignee: 株式会社デンソー
Priority date: 2016-10-11
Filing date: 2017-09-14
Publication date: 2018-04-19
Also published as: JP2019215090A

Abstract

This appliance temperature regulating apparatus capable of cooling an appliance (BP) of which temperature is to be regulated has an annular appliance fluid circuit (2) that is configured to include: an appliance heat exchanger (2a) that cools the appliance of which temperature is to be regulated, by causing heat to be absorbed from the appliance of which temperature is to be regulated and causing a working fluid in a liquid form to be evaporated; a condenser (2c) that condenses the working fluid in a gaseous form evaporated at the appliance heat exchanger; a gas passage part (2b) that guides, to the condenser, the gaseous working fluid evaporated at the appliance heat exchanger; and a liquid passage part (2d) that guides, to the appliance heat exchanger, the working fluid in a liquid form condensed at the condenser. The heat radiation amount of the working fluid is adjusted by a heat radiation amount adjusting part (31, BF) that performs, by supplying a heating medium to the condenser, heat exchange between the heating medium and the working fluid present inside the condenser. This appliance temperature regulating apparatus has a cold storage agent (CS) that is disposed in the appliance fluid circuit and that stores at least one of: cold heat of the working fluid; and cold heat of the heating medium.

Description

Equipment temperature controller

Cross-reference to related applications

This application is based on Japanese Patent Application No. 2016-200286 filed on Oct. 11, 2016, the contents of which are incorporated herein by reference.

This disclosure relates to a device temperature control device capable of adjusting the temperature of a temperature control target device.

Conventionally, a loop-type thermosyphon cooling device is known as a cooling device for cooling a temperature-controlled device. There exists a thing of patent document 1 as this kind of cooling device.

The device temperature control apparatus described in Patent Document 1 includes an annular device fluid circuit configured to include a device heat exchanger, a gas passage portion, a condenser, and a liquid passage portion. In addition, this equipment temperature control apparatus supplies a heat medium (for example, blown air) for exchanging heat with the working medium existing inside the condenser to dissipate the working medium, thereby supplying the working fluid. A heat radiation amount adjusting unit (for example, a blower) that adjusts the heat radiation amount is provided. The equipment heat exchanger is a heat exchanger that absorbs heat from the temperature control target equipment and evaporates the liquid working fluid. The condenser is a heat exchanger that is disposed above the equipment heat exchanger and condenses the gaseous working fluid evaporated in the equipment heat exchanger. The condenser radiates heat and condenses the working medium existing in the condenser by heat exchange with the heat medium supplied from the heat radiation amount adjusting unit. The gas passage portion is a passage member that guides the gaseous working fluid evaporated in the equipment heat exchanger to the condenser. The liquid passage portion is a passage member that guides the liquid working fluid condensed by the condenser to the equipment heat exchanger. That is, this equipment temperature control device is a heat pipe that performs heat transfer by evaporation and condensation of the working fluid by circulating the working fluid in the equipment fluid circuit. This device temperature control device is configured to be a loop thermosyphon in which a flow path through which a gaseous working fluid flows and a flow path through which a liquid working fluid flows are separated. In this device temperature control apparatus, in the device fluid circuit, the working fluid flows in the order of the device heat exchanger, the gas passage portion, the condenser, and the liquid passage portion. Further, in the fluid circuit for equipment, the direction in which the working fluid flows in this order (that is, the order of equipment heat exchanger, gas passage, condenser, and liquid passage) is the forward direction.

JP 2012-9646 A

In a thermosiphon type device temperature control apparatus such as Patent Document 1, the heat radiation capacity of the heat radiation amount adjusting unit may be reduced due to various circumstances, thereby reducing the condenser capacity of the condenser. In particular, in a device temperature control device that is mounted on a vehicle and cools a vehicle-mounted device (for example, an electronic device such as a battery), the heat radiation capacity of the heat radiation amount adjusting unit may be reduced due to various circumstances. Specifically, for example, when a blower installed in the engine room is used as the heat dissipation amount adjustment unit, when the vehicle speed is reduced, the air flow by the blower is also reduced, so that the condenser capacity is also reduced. Condensation is not performed sufficiently. At this time, the condensation capacity of the condenser is reduced, and the flow rate of the working fluid in the forward direction is reduced. As a result, it is difficult to maintain the forward flow, and the cooling capacity of the device temperature control device is significantly reduced. . Also, once it becomes difficult to maintain the forward direction in this way, even if the heat radiation capacity of the heat radiation amount adjustment unit is restored again, until the cooling capacity of the equipment temperature control device recovers to the same level as the original state Time (for example, several tens of seconds) is required. As a result, the overall cooling capacity (that is, the total cooling capacity obtained per predetermined time) in the device temperature control device is significantly reduced. As another example, when a refrigeration cycle of a vehicle air conditioner that provides conditioned air to the passenger compartment is used as a heat dissipation adjustment unit, for example, the upper limit of the rotational speed of the compressor is decreased in response to a decrease in vehicle speed. Even when the upper limit of the rotational speed of the compressor of the refrigeration cycle is reduced by various controls or the like, the condenser capacity of the condenser is lowered, and the cooling capacity is significantly lowered for the same reason as described above.

This disclosure aims to provide a configuration in which the cooling capacity is hardly lowered even in the case where the heat radiation capacity of the heat radiation amount adjusting unit is lowered in the thermosiphon type device temperature control device.

In order to achieve the above object, according to one aspect of the present disclosure, a device temperature control apparatus capable of cooling a temperature control target device has the following configuration. In other words, the equipment temperature control device has a configuration including an annular equipment fluid circuit including an equipment heat exchanger, a gas passage section, a condenser, and a liquid passage section. The equipment heat exchanger cools the temperature control target device by absorbing heat from the temperature control target device and evaporating the liquid working fluid. The gas passage part guides the gaseous working fluid evaporated in the equipment heat exchanger to the condenser. The condenser is disposed above the equipment heat exchanger, and condenses the gaseous working fluid evaporated in the equipment heat exchanger. The liquid passage portion guides the liquid working fluid condensed in the condenser to the equipment heat exchanger. Further, in this device temperature control device, the heat dissipation amount of the working fluid is adjusted by the heat dissipation amount adjusting unit. The heat radiation amount adjusting unit is configured to exchange heat between the heat medium and the working fluid existing in the condenser by supplying the heat medium to the condenser. And this apparatus temperature control apparatus is set as the structure which has a cool storage agent arrange | positioned in the fluid circuit for apparatuses, and accumulate | stores at least one of the cold heat of a working fluid, and the cold heat of the said heat medium.

According to this device temperature control device, even when the heat radiation capacity of the heat radiation amount adjusting unit is lowered, the cold heat accumulated in the cold storage agent is transmitted to the working fluid, so that the working fluid is easily cooled and condensed. And since it becomes easy to condense a working fluid, it becomes easy to maintain the forward flow of the working fluid in the fluid circuit for apparatus, and it becomes easy to maintain the cooling capacity of an apparatus temperature control apparatus by extension. That is, since the cool storage agent is arranged in the fluid circuit for equipment, even when the heat radiation capacity of the heat radiation amount adjusting unit is lowered, the cooling capacity is easily maintained without being lowered.

It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the input-output characteristic of an assembled battery. It is a schematic diagram which shows the inside of the apparatus heat exchanger of the apparatus temperature control apparatus shown in FIG. It is a figure which shows the whole structure of the condenser of the apparatus temperature control apparatus shown in FIG. It is a figure which shows the change of the cooling performance of each apparatus temperature control apparatus with and without having a cool storage agent, when a compressor stops. It is a figure which shows the change of the cooling performance of each apparatus temperature control apparatus with and without having a cool storage agent, when the upper limit of the rotation speed of a compressor falls. It is a figure which shows the change of the cooling performance of each apparatus temperature control apparatus with and without having a cool storage agent, when the cooling capacity of a refrigerating cycle is used preferentially for a 2nd freezing cycle. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 2nd Embodiment. It is a figure which shows the change of the cooling performance of each apparatus temperature control apparatus with and without having a cool storage agent, when a vehicle speed falls. It is a figure which shows the change of the cooling performance of each apparatus temperature control apparatus with and without having a cool storage agent, when a grill shutter act | operates. It is a figure which shows the change of the cooling performance of each apparatus temperature control apparatus with and without having a cool storage agent, when installing an air blower in a vehicle interior. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 3rd Embodiment. It is a perspective view of the cool storage agent CS. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 4th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 5th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 6th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 7th Embodiment. FIG. 18 is a sectional view taken along line XVIII-XVIII in FIG. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 8th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 9th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 10th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 11th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on the other example of 11th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 12th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 13th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 14th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 15th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on 16th Embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on other embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on another other embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on other embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on other embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on other embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on other embodiment. It is a typical whole block diagram of the apparatus temperature control apparatus which concerns on other embodiment.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals for description.

(First embodiment)
An apparatus temperature control device 1 according to a first embodiment of the present disclosure will be described with reference to FIGS. 1 to 7. The device temperature control device 1 is a device capable of cooling the temperature control target device BP. In the present embodiment, an example in which the device temperature adjustment device 1 shown in FIG. 1 is applied as a device for adjusting the battery temperature of the assembled battery BP mounted on a vehicle will be described. As the vehicle on which the device temperature control device 1 is mounted, an electric vehicle, a hybrid vehicle, or the like that can be driven by a traveling electric motor (not shown) that uses the assembled battery BP as a power source is assumed.

As shown in FIG. 1, the assembled battery BP is configured by a stacked body in which a plurality of rectangular parallelepiped battery cells BC are stacked. The plurality of battery cells BC constituting the assembled battery BP are electrically connected in series. Each battery cell BC constituting the assembled battery BP is configured by a chargeable / dischargeable secondary battery (for example, a lithium ion battery or a lead storage battery). The battery cell BC is not limited to a rectangular parallelepiped shape, and may have another shape such as a cylindrical shape. The assembled battery BP may include a battery cell BC electrically connected in parallel.

The assembled battery BP is connected to a power converter (not shown) and a motor generator. This power conversion device is, for example, a device that converts a direct current supplied from the assembled battery BP into an alternating current, and supplies (ie, discharges) the converted alternating current to various electric loads such as a traveling electric motor. is there. The motor generator is a device that reversely converts the traveling energy of the vehicle into electric energy during regeneration of the vehicle, and supplies the reversely converted electric energy as regenerative power to the assembled battery BP via a power conversion device or the like. .

The battery pack BP may become excessively hot due to self-heating when power is supplied while the vehicle is running. When the assembled battery BP becomes excessively high in temperature, as shown in FIG. 2, the deterioration of the battery cell BC is promoted. Therefore, it is necessary to limit the output and input so as to reduce self-heating. For this reason, in order to ensure the output and input of the battery cell BC, a cooling means for maintaining the temperature below a predetermined temperature is required.

In addition, the battery temperature of the assembled battery BP may become excessively high even during parking in the summer. That is, the power storage device including the assembled battery BP is often disposed under the floor of the vehicle or under the trunk room, and the battery temperature of the assembled battery BP gradually increases not only during the traveling of the vehicle but also during parking in summer. The battery pack BP may rise to an excessively high temperature. If the battery pack BP is left in a high temperature environment, the battery life will be significantly reduced due to the progress of deterioration. Therefore, the battery temperature of the battery pack BP should be kept below a predetermined temperature even during parking of the vehicle. Is desired.

Furthermore, if the temperature of each battery cell BC varies in the assembled battery BP, the progress of deterioration of each battery cell BC is biased, and the input / output characteristics of the entire assembled battery BP deteriorate. This is because the assembled battery BP includes a series connection body of the battery cells BC, and among the battery cells BC, the input / output characteristics of the entire assembled battery BP according to the battery characteristics of the battery cell BC that is most deteriorated. Because it is decided. For this reason, in order to make the assembled battery BP exhibit desired performance for a long period of time, it is important to equalize the temperature of the battery cells BC to reduce temperature variation.

Here, as a cooling means for cooling the assembled battery BP, an air-cooling cooling means using a blower and a cooling means using the cold heat of a vapor compression refrigeration cycle are generally used. However, since the air-cooled cooling means using the blower only blows air or the like in the passenger compartment to the assembled battery, a cooling capacity sufficient to sufficiently cool the assembled battery BP may not be obtained. Moreover, although the cooling means using the cold heat of the refrigeration cycle has a high ability to cool the assembled battery BP, it is necessary to drive a compressor or the like that consumes a large amount of power while the vehicle is parked. This is undesirable because it leads to an increase in power consumption and an increase in noise.

Therefore, the apparatus temperature control apparatus 1 of the present embodiment employs a thermosiphon system that adjusts the battery temperature of the assembled battery BP not by forced circulation of the refrigerant by the compressor but by natural circulation of the working fluid.

The device temperature control device 1 is a device that adjusts the battery temperature of the assembled battery BP using the assembled battery BP mounted on the vehicle as a temperature control target device. As shown in FIG. 1, the device temperature control device 1 includes an annular device fluid circuit 2 and a refrigeration cycle 3 through which a working fluid circulates. The fluid circuit for equipment 2 is a heat pipe that performs heat transfer by evaporation and condensation of the working fluid. The device fluid circuit 2 is configured to be a loop thermosyphon in which a flow path through which a gaseous working fluid flows and a flow path through which a liquid working fluid flows are separated. As the working fluid that circulates in the device fluid circuit 2, refrigerants (for example, R134a and R1234yf) used in a vapor compression refrigeration cycle can be employed.

Next, the refrigeration cycle 3 will be described before the details of the device fluid circuit 2 are described. As shown in FIG. 1, the refrigeration cycle 3 includes a compressor 3a, a condenser 3b, an expansion valve 3c, an expansion valve 3d, an evaporator 3e, and a refrigerant side heat exchanger HEC. Specifically, the refrigeration cycle 3 includes a refrigeration cycle (hereinafter referred to as a first refrigeration cycle) 31 including a compressor 3a, a condenser 3b, an expansion valve 3c, and a refrigerant side heat exchanger HEC. is doing. The refrigeration cycle 3 includes a refrigeration cycle (hereinafter referred to as a second refrigeration cycle) 32 including a compressor 3a, a condenser 3b, an expansion valve 3d, and an evaporator 3e. That is, the refrigeration cycle 3 includes a first refrigeration cycle 31 and a second refrigeration cycle 32. The first refrigeration cycle 31 is operated by the compressor 3a to flow a heat medium (that is, a refrigerant) that cools the working fluid existing in the condenser 2c (that is, the condenser 2c of the fluid circuit 2 for equipment) described later. A refrigerant flow path 31a. This heat medium is a refrigerant that cools the working fluid by exchanging heat with the working fluid existing inside the condenser 2c of the fluid circuit 2 for equipment. In the present embodiment, the amount of heat release in the condenser 2c of the fluid circuit 2 for equipment changes as the number of rotations of the compressor 3a in the refrigeration cycle 3 increases or decreases. The second refrigeration cycle 32 is a refrigeration cycle included in a vehicle air conditioner (not shown), and is operated by the compressor 3a to generate cold air provided by the vehicle air conditioner. As this heat medium, various refrigerants conventionally used in vapor compression refrigeration cycles (for example, R134a and R1234yf) can be employed. In the present embodiment, the first refrigeration cycle 31 and the second refrigeration cycle 32 are thus integrally configured as a part of the vehicle air conditioner.

That is, the refrigerant flow path 31a corresponds to a heat medium flow path. The first refrigeration cycle 31 corresponds to a heat release amount adjustment unit that adjusts the heat release amount of the working fluid existing inside the condenser 2c of the device fluid circuit 2 by supplying a heat medium to the condenser 2c. Further, in the present embodiment, the heat radiation amount adjustment unit (that is, the first refrigeration cycle 31) uses the limited total cooling capacity of the refrigeration cycle 3 to generate the cold air generation unit (that is, the first refrigeration cycle 31) that generates the cold air of the vehicle air conditioner. 2) Refrigeration cycle 32) and share with various distributions.

Next, the details of the fluid circuit 2 for equipment will be described. As shown in FIG. 1, the device fluid circuit 2 includes a device heat exchanger 2a, a gas passage portion 2b, a condenser 2c, and a liquid passage portion 2d. Moreover, as shown in FIG. 4, the fluid circuit 2 for equipment is provided with the cool storage agent CS. Details of the cold storage agent CS will be described later. 1, 3, and 4 indicate the direction in which the vertical line extends, that is, the vertical direction.

The device fluid circuit 2 of the present embodiment is configured as a closed annular fluid circuit by connecting the device heat exchanger 2a, the gas passage portion 2b, the condenser 2c, and the liquid passage portion 2d to each other. ing. The device fluid circuit 2 is filled with a predetermined amount of working fluid in a state where the inside thereof is evacuated. In the device fluid circuit 2 of the present embodiment, the working fluid flows in the order of the device heat exchanger 2a, the gas passage portion 2b, the condenser 2c, and the liquid passage portion 2d. Hereinafter, this flow direction of the working fluid in the device fluid circuit 2 is referred to as a forward direction.

The equipment heat exchanger 2a is a heat exchanger that functions as an equipment heat exchanger that absorbs heat from the assembled battery BP and evaporates the liquid working fluid when the assembled battery BP, which is a temperature control target apparatus, is cooled. The equipment heat exchanger 2a is disposed at a position facing the bottom surface side of the assembled battery BP. The equipment heat exchanger 2a has a thin rectangular parallelepiped shape.

The equipment heat exchanger 2a constitutes a heat transfer section in which the heat exchange section 2aa that exchanges heat by contacting the bottom surface of the assembled battery BP moves heat between the assembled battery BP and the equipment heat exchanger 2a. is doing. The heat exchange part 2aa has a size that covers the entire area of the bottom part of the assembled battery BP so that temperature distribution does not occur in each battery cell BC constituting the assembled battery BP. In the device heat exchanger 2a, the heat exchanging portion 2aa is in contact with the bottom surface portion of the assembled battery BP so that heat can be transferred to and from the assembled battery BP. The equipment heat exchanger 2a may have a configuration in which the heat exchanging portion 2aa is separated from the bottom surface portion of the assembled battery BP as long as heat can be transferred between the assembled battery BP.

Here, when the liquid level of the working fluid in the equipment heat exchanger 2a is separated from the heat exchange portion 2aa of the equipment heat exchanger 2a, the heat of the assembled battery BP is liquid in the inside of the equipment heat exchanger 2a. It becomes difficult to be transmitted to the working fluid. That is, when the liquid level of the working fluid in the equipment heat exchanger 2a is separated from the heat exchange portion 2aa of the equipment heat exchanger 2a, evaporation of the liquid working fluid existing in the equipment heat exchanger 2a is suppressed. Will be. For this reason, in the fluid circuit for equipment 2 of the present embodiment, the liquid level of the working fluid is such that the heat of the assembled battery BP is transferred to the liquid working fluid existing inside the equipment heat exchanger 2a. The heat exchanger 2aa of the exchanger 2a is in contact with the heat exchanger 2aa. That is, the device fluid circuit 2 of the present embodiment is configured such that the internal space of the device heat exchanger 2a is filled with a liquid working fluid containing bubbles when the assembled battery BP is cooled. For example, as shown in FIG. 3, when the equipment heat exchanger 2a is formed of a hollow container, the liquid level of the working fluid existing inside the equipment heat exchanger 2a when the assembled battery BP is cooled. The LS is in contact with the heat exchange part 2aa adjacent to the assembled battery BP. In addition, the apparatus heat exchanger 2a is not limited to a hollow container, and may have a configuration in which a plurality of flow paths are formed by a heat exchange tube or the like.

As shown in FIG. 1, the equipment heat exchanger 2a includes a gas outlet 2ab to which the lower end of the gas passage 2b is connected, and a liquid to which the lower end of the liquid passage 2d is connected. It has an inlet 2ac. In the equipment heat exchanger 2a of the present embodiment, the gas outlet portion 2ab and the liquid inlet portion 2ac are provided on the side portions facing each other. Further, in the equipment heat exchanger 2a of the present embodiment, the gas outlet portion 2ab and the liquid inlet portion 2ac are provided at the same height in the vertical direction DRg. The equipment heat exchanger 2a is made of a metal or alloy having excellent thermal conductivity such as aluminum or copper. In addition, although the apparatus heat exchanger 2a can also be comprised with materials other than a metal, it is desirable to comprise at least the heat exchange part 2aa which comprises a heat-transfer part with the material excellent in heat conductivity.

As shown in FIG. 1, the gas passage portion 2b is a passage member that guides the gaseous working fluid evaporated in the equipment heat exchanger 2a to the condenser 2c. The gas passage portion 2b has a lower end connected to the gas outlet 2ab of the equipment heat exchanger 2a and an upper end connected to a gas inlet 2ca (described later) of the condenser 2c. The gas passage portion 2b of the present embodiment is configured by a pipe in which a flow path through which a working fluid flows is formed. The gas passage portion 2b of the present embodiment includes an upper gas passage portion 2b that extends upward from the gas inlet portion 2ca of the condenser 2c. In other words, the gas passage portion 2b of the present embodiment is configured to include a passage portion in which a part of the portion on the condenser 2c side extends toward the gas inlet portion 2ca of the condenser 2c. The upper gas passage portion 2b of the present embodiment extends upward along the vertical direction DRg. In addition, the gas passage part 2b shown in drawing is an example to the last. The gas passage portion 2b can be appropriately changed in consideration of the mounting property on the vehicle.

The condenser 2c is a heat exchanger that condenses the gaseous working fluid evaporated in the equipment heat exchanger 2a. The condenser 2c is an air-cooled heat exchanger that causes heat exchange between the refrigerant flowing through the first refrigeration cycle 31 and the gaseous working fluid to condense the gaseous working fluid. As shown in FIG. 1, the condenser 2c is located above the equipment heat exchanger 2a in the vertical direction DRg so that the liquid working fluid condensed inside moves to the equipment heat exchanger 2a by its own weight. Has been placed. The condenser 2c has a gas inlet 2ca to which an upper end of the gas passage 2b is connected, and a liquid outlet 2cb to which an upper end of the liquid passage 2d is connected. In the condenser 2c of this embodiment, the gas inlet portion 2ca and the liquid outlet portion 2cb are provided at portions facing each other in the vertical direction. Further, the condenser 2c of the present embodiment is provided such that the gas inlet portion 2ca is located above the liquid outlet portion 2cb in the vertical direction DRg. Specifically, in the condenser 2c of the present embodiment, the gas inlet 2ca is provided at the upper end of the condenser 2c, and the liquid outlet 2cb is provided at the lower end of the condenser 2c. The condenser 2c is basically made of a metal or alloy having excellent thermal conductivity such as aluminum or copper. The condenser 2c may be configured to include a material other than metal, but it is preferable to configure at least a portion exchanging heat with air with a material having excellent thermal conductivity.

Specifically, as shown in FIG. 4, the condenser 2 c includes a plurality of flow path portions (hereinafter referred to as working fluid flow path portions) P <b> 1 through which the working fluid flows and a part of the first refrigeration cycle 31. And a plurality of flow path portions (hereinafter referred to as refrigerant flow path portions) P2 through which the refrigerant of the first refrigeration cycle 31 flows. In addition, the condenser 2c according to the present embodiment is provided with a plurality of cool storage agents CS. Each of the plurality of working fluid flow path portions P1, each of the plurality of cool storage agents CS, and each of the plurality of refrigerant flow path portions P2 are formed to extend in the vertical direction (that is, the vertical direction in FIG. 4). . Each of the plurality of working fluid flow path portions P1, each of the plurality of cold storage agents CS, and each of the plurality of refrigerant flow passage portions P2 are from the right in the left-right direction (that is, the horizontal direction) in FIG. It arrange | positions in order of P1, the cool storage agent CS, the refrigerant | coolant flow path part P2, the working fluid flow path part P1, the cool storage agent CS, the refrigerant flow path part P2, .... Each of the plurality of working fluid flow paths P1 communicates with each other so that the working fluid can flow between them. Each of the plurality of refrigerant flow path portions P2 communicates with each other so that the refrigerant can flow therethrough.

The cold storage agent CS is for accumulating at least one of the cold heat of the working fluid and the cold heat of the refrigerant in the first refrigeration cycle 31. The regenerator CS is not particularly limited in the configuration of materials and the like, but various known ones such as paraffin can be adopted. For example, you may use the member which packed this cool storage agent CS in the container comprised with metals, such as aluminum. In the present embodiment, the cold storage agent CS is configured to accumulate both the cold heat of the working fluid and the cold heat of the refrigerant in the first refrigeration cycle 31. That is, each of the plurality of cool storage agents CS is capable of exchanging heat with the working fluid that flows through the nearest adjacent working fluid flow path portion P1 among the plurality, and the refrigerant that flows through the nearest neighboring coolant flow path portion P2 among the plurality of cool storage agents CS. It is arranged to be able to exchange heat. Specifically, each of the plurality of cool storage agents CS is disposed in contact with both the adjacent working fluid channel portion P1 and the adjacent refrigerant channel portion P2.

Thus, in this embodiment, the cool storage agent CS is ahead of the uppermost portion located in the forward direction of the gas passage portion 2b in the forward direction and in front of the gas outlet portion in the fluid circuit 2 for equipment. Has been placed. Note that the front and the front in the forward direction are the upstream side and the downstream side, respectively. In the present embodiment, in particular, the regenerator CS is disposed in the device fluid circuit 2 before the gas inlet 2ca and before the gas outlet 2ab. In the present embodiment, in particular, the regenerator agent CS is disposed between the working fluid and the heat medium passage (that is, the refrigerant passage 31a) without being interposed therebetween. In the present embodiment, in particular, the regenerator CS is provided between the working fluid channel (that is, the working fluid channel portion P1) and the heat medium channel (that is, the refrigerant channel 31a) in the condenser 2c. Has been placed. In this embodiment, the cool storage agent CS is configured integrally with the condenser 2c.

In the present embodiment, the gaseous working fluid flowing from the gas inlet portion 2ca is distributed to each of the plurality of working fluid flow passage portions P1, as indicated by an arrow F1 in FIG. Then, after the working fluid of each of the plurality of working fluid flow paths P1 gathers, it flows out from the liquid outlet 2cb. On the other hand, the refrigerant flowing through the refrigerant flow path portion P2 is distributed to each of the plurality of refrigerant flow path portions P2 after flowing in from the inlet HECA, as indicated by an arrow F2 in FIG. The refrigerant flows in a direction opposite to the direction of the working fluid flowing through the working fluid flow path portion P1. After that, the refrigerant in each of the plurality of refrigerant flow path portions P2 flows out from the outlet HECb after gathering.

In the apparatus temperature control apparatus 1 according to the present embodiment, when the battery temperature of the assembled battery BP rises due to self-heating during traveling of the vehicle in the cooling mode, the heat of the assembled battery BP moves to the apparatus heat exchanger 2a. . In the equipment heat exchanger 2a, a part of the liquid working fluid evaporates by absorbing heat from the assembled battery BP. The assembled battery BP is cooled by the latent heat of vaporization of the working fluid existing inside the equipment heat exchanger 2a, and the temperature thereof decreases. The gaseous working fluid evaporated in the equipment heat exchanger 2a flows out from the gas outlet portion 2ab of the equipment heat exchanger 2a to the gas passage portion 2b, and as shown by an arrow Fcg in FIG. It moves to the condenser 2c via 2b. In the condenser 2c, the gaseous working fluid is condensed by dissipating heat to the refrigerant flowing through the first refrigeration cycle 31. Inside the condenser 2c, the gaseous working fluid is liquefied and the specific gravity of the working fluid increases. Thereby, the working fluid liquefied inside the condenser 2c descends toward the liquid outlet 2cb of the condenser 2c by its own weight. The liquid working fluid condensed in the condenser 2c flows out from the liquid outlet portion 2cb of the condenser 2c to the liquid passage portion 2d, and as shown by an arrow Fcl in FIG. 1, heat exchange for equipment is performed via the liquid passage portion 2d. Move to vessel 2a. In the equipment heat exchanger 2a, a part of the liquid working fluid that flows from the liquid inlet 2ac through the liquid passage 2d evaporates by absorbing heat from the assembled battery BP. In this way, the equipment temperature control device 1 circulates between the equipment heat exchanger 2a and the condenser 2c while the phase of the working fluid changes between a gas state and a liquid state in the cooling mode, and exchanges heat for the equipment. The assembled battery BP is cooled by transporting heat from the vessel 2a to the condenser 2c. The device temperature control device 1 is configured such that the working fluid naturally circulates inside the device fluid circuit 2 without the driving force required for the circulation of the working fluid by a compressor or the like. For this reason, the apparatus temperature control apparatus 1 can implement | achieve the temperature control of the assembled battery BP with sufficient efficiency which suppressed both power consumption and noise compared with the refrigerating cycle etc.

As described above, in the device temperature control device 1 according to the present embodiment, in the device fluid circuit 2, the cooling / heating of the working fluid and the coolant supplied by the heat release amount adjustment unit (that is, the coolant of the first refrigeration cycle 31). It has the cool storage agent CS which accumulates at least one of these.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, even when the thermal radiation capability of the heat radiation amount adjustment part (namely, 1st freezing cycle 31) falls, the cold heat accumulate | stored in the cool storage agent CS is transmitted to a working fluid. Thus, the working fluid is cooled and easily condensed. As a result, the forward flow of the working fluid in the device fluid circuit 2 is easily maintained, and as a result, the cooling capacity of the device temperature control device 1 is easily maintained. That is, in the device temperature control apparatus 1 according to the present embodiment, the heat storage capacity of the heat release amount adjusting unit (that is, the first refrigeration cycle 31) is reduced by the cold storage agent CS being arranged in the device fluid circuit 2. Sometimes, the cooling capacity is easily maintained without being lowered.

Specifically, the effect as shown in FIG. 5 is obtained. FIG. 5 shows the change in the cooling performance of the device temperature control device 1 when the rotational speed of the compressor 3a is changed, comparing the case with the cold storage agent CS and the case without the cold storage agent CS.

That is, as shown in FIG. 5, in the case where the regenerator CS is not provided, when the compressor 3 a is stopped, the heat radiation capacity of the heat radiation amount adjustment unit (that is, the first refrigeration cycle 31) is reduced, thereby reducing the condenser. The condensing capacity of 2c also decreases, and as a result, the cooling performance of the device temperature control device 1 decreases. This is due to the fact that the forward flow becomes difficult to maintain due to a decrease in the flow rate of the forward working fluid due to a decrease in the condensation capacity of the condenser 2c. And even if the heat dissipation capacity of the first refrigeration cycle 31 is recovered later, it takes time (for example, several tens of seconds) until the cooling capacity of the device temperature control device 1 recovers to the same level as the original state. As a result, the overall cooling capacity (that is, the total cooling capacity obtained per predetermined time) in the device temperature control apparatus 1 is significantly reduced. On the other hand, in the case of the present embodiment having the regenerator CS, the refrigerant that flows through the first refrigeration cycle 31 in the condenser 2c before the compressor 3a stops (that is, before 1 in FIG. 5). The cooling performance of the device temperature control device 1 is ensured by radiating heat. At the same time, the cold heat of the first refrigeration cycle 31 is accumulated directly or indirectly in the cold storage material CS. After that, when the compressor 3a is stopped (i.e., 1 in FIG. 5), since the refrigerant does not flow in the first refrigeration cycle 31, heat cannot be dissipated in the condenser 2c. Since the cold heat accumulated in is transmitted to the working fluid, the working fluid is sufficiently condensed, and the cooling capacity of the device temperature control device 1 is maintained. Then, when the compressor 3a starts to drive again later (that is, 2 in FIG. 5), since the forward flow is maintained at 1, the cooling capacity compared to the case where the regenerator material CS is not provided. It takes no time to recover to the same level as the original. In the present embodiment, the above-described operation makes it easy to maintain the cooling performance of the device temperature control device 1 without lowering even when the heat dissipation capability of the condenser 2c is reduced, and the overall cooling capability (that is, the predetermined cooling capability). The total cooling capacity obtained per hour) will increase.

Moreover, according to the apparatus temperature control apparatus 1 of this embodiment which has the cool storage agent CS, even when the upper limit of the rotation speed of the compressor 3a falls not only when the compressor 3a stops completely, FIG. As shown in FIG. 4, basically the same effects as described above can be obtained. FIG. 6 shows the change in the cooling performance of the device temperature control device 1 when the upper limit of the rotational speed of the compressor 3a is lowered, comparing the case with the cool storage agent CS and the case without the cool storage agent CS. In addition, the situation where the upper limit of the rotational speed of the compressor 3a is lowered means, for example, that the upper limit of the rotational speed of the compressor 3a is lowered in order to satisfy a demand for NV (that is, noise and vibration) when the vehicle speed is lowered. This is a case where control is performed. In addition, when the vehicle suddenly accelerates, control is performed to reduce the upper limit of the rotational speed of the compressor 3a in order to ensure the output of the vehicle travel battery. Another example is when control is performed to reduce the upper limit of the rotational speed of the compressor 3a when the remaining battery capacity is low.

Further, as described above, the device temperature adjustment device 1 according to the present embodiment has a configuration in which the heat release amount adjustment unit (that is, the first refrigeration cycle 31) shares the total cooling capacity with the second refrigeration cycle 32. In such a configuration, as shown in FIG. 7, even when the cooling capacity of the refrigeration cycle 3 is used preferentially in the second refrigeration cycle 32 (that is, the refrigeration cycle for the air conditioner), the regenerator CS If it does not have, the heat radiation capacity of the heat radiation amount adjusting unit is reduced. FIG. 7 compares the change in the cooling performance of the device temperature control device 1 when the cooling capacity of the refrigeration cycle 3 is preferentially used for the second refrigeration cycle 32 with and without the cool storage agent CS. While showing. Even at this time, according to the device temperature control apparatus 1 of the present embodiment having the cold storage agent CS, basically the same effect as described above can be obtained. The situation in which the cooling capacity of the refrigeration cycle 3 is preferentially used for the second refrigeration cycle 32 is, for example, a cool-down that is performed when the current cabin temperature is higher than the target cabin temperature. is there. Another example is a case where the set temperature of the air conditioner suddenly decreases due to manual operation by the passenger.

Further, as described above, in the present embodiment, the regenerator CS in the device fluid circuit 2 is ahead of the topmost portion of the gas passage portion 2b in the forward direction and is located at the gas outlet portion 2ab. It is arranged in front of.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, the cool storage agent CS is arrange | positioned ahead of the gas outlet part 2ab ahead of the uppermost part among the gas passage parts 2b in a forward direction. Thereby, since the flow rate of the working fluid in the forward direction does not decrease as in the case where the cool storage agent CS is disposed in the portion before the uppermost portion, the forward flow of the working fluid is more easily maintained. .

It should be noted that a portion of the gas passage portion 2b in the forward direction that is in front of the uppermost portion is a passage in which the working fluid is directed upward from the bottom in the forward direction. For this reason, if the cool storage agent CS is disposed in the front portion, the gaseous working fluid is liquefied by the cold heat accumulated in the cool storage agent CS and falls downward, so that the working fluid in the forward direction Will decrease the flow rate. On the other hand, in the apparatus temperature control apparatus 1 which concerns on this embodiment, the cool storage agent CS is arrange | positioned before the gas outlet part 2ab ahead of the uppermost part among the gas passage parts 2b in a forward direction. Thus, the flow rate of the working fluid in the forward direction is not reduced in this way. For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, there exists an advantage that the forward flow of a working fluid is maintained more easily.

Further, as described above, in the present embodiment, in particular, the regenerator CS is arranged in the device fluid circuit 2 before the gas inlet 2ca and before the gas outlet 2ab.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, the cool storage agent CS is arrange | positioned ahead of the gas inlet part 2ca of the condenser 2c in a forward direction. That is, the cool storage agent CS is disposed downstream of the condenser 2c. Therefore, cold heat can be accumulated in the cold storage agent CS by exchanging heat between the liquid working fluid condensed by the condenser 2c and the cold storage agent CS.

In the present embodiment, in particular, the regenerator CS is disposed in the device fluid circuit 2 before the gas inlet 2ca in the forward direction and before the liquid inlet 2ac.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, the cool storage agent CS is arrange | positioned ahead of the gas inlet part 2ca of the condenser 2c in a forward direction. That is, the cool storage agent CS is disposed downstream of the condenser 2c. Therefore, cold heat can be accumulated in the cold storage agent CS by exchanging heat between the liquid working fluid condensed by the condenser 2c and the cold storage agent CS. Furthermore, the cool storage agent CS is disposed in front of the liquid inlet 2ac of the equipment heat exchanger 2a in the forward direction. That is, the cool storage agent CS is arranged upstream of the equipment heat exchanger 2a. Of the liquid passage portion 2d in the forward direction, the portion from the liquid outlet portion 2cb of the condenser 2c to the liquid inlet portion 2ac of the equipment heat exchanger 2a is a passage in which the working fluid is directed from top to bottom in the forward direction. For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, since the cool storage agent CS is arrange | positioned in the part which reaches this liquid inlet part 2ac, a gaseous working fluid is produced | generated by the cold heat accumulate | stored in the cool storage agent CS. By liquefying and falling down under its own weight, a forward flow of the working fluid is more likely to occur.

In this embodiment, in particular, the regenerator CS is arranged between the working fluid and the heat medium passage (that is, the refrigerant passage 31a). Specifically, in the present embodiment, at least a part of the cool storage agent CS is disposed between the working fluid and the heat medium passage (that is, the refrigerant passage 31a).

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, it becomes easy to transmit the cold heat | fever of the cool storage agent CS to a working fluid, and it becomes easy to maintain the forward flow of a working fluid especially.

In the present embodiment, in particular, the regenerator CS is provided between the working fluid channel (that is, the working fluid channel portion P1) and the heat medium channel (that is, the refrigerant channel 31a) in the condenser 2c. Has been placed. Specifically, in the present embodiment, at least a part of the cool storage agent CS includes a working fluid channel (that is, the working fluid channel portion P1) and a heat medium channel (that is, the refrigerant channel 31a) in the condenser 2c. ) Between them.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, the cool storage agent CS functions as a thermal buffer material. Conventionally, in this type of device temperature control apparatus 1, bumps are generated when the temperature difference between the working fluid and the heat medium flowing through the heat medium flow path (that is, the refrigerant flow path 31a) is severe. The problem was that sound was generated. However, in the apparatus temperature control apparatus 1 which concerns on embodiment, since the cool storage agent CS is arrange | positioned in between, the temperature fall of a working fluid becomes moderate and it becomes difficult to produce bumping.

Further, as described above, in the present embodiment, it is particularly configured integrally with the condenser 2c.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, since the liquid working fluid condensed by the condenser 2c can be immediately heat-exchanged with the cool storage agent CS, cold energy is accumulate | stored in the cool storage agent CS efficiently. And the forward flow of the working fluid is particularly easily maintained.

As described above, in the present embodiment, the temperature control target device is the assembled battery BP having a plurality of battery cells BC.

For this reason, since the apparatus temperature control apparatus 1 which concerns on this embodiment is a thermosiphon-type cooling device, it cools the temperature control object apparatus using the evaporative heat which arises in the case of evaporation of a working fluid, ie, a latent heat. . On the other hand, there is a method of cooling the assembled battery BP by blowing air from a blower. However, in this method, there is a problem that the cooling capacity is low. In this case, since the cooling is performed by the latent heat of the air, the temperature difference between the upstream and downstream of the air becomes large, thereby causing variations in the temperature distribution between the battery cells BC. However, in the device temperature adjustment device 1 according to the present embodiment, the temperature adjustment target device is cooled using latent heat, so that the temperature variation of each battery cell BC can be reduced, and each battery cell BC is cooled evenly. can do. Therefore, the apparatus temperature control apparatus 1 which concerns on this embodiment is especially suitable for cooling of the assembled battery BP where temperature equalization which reduces the temperature variation of each battery cell BC becomes important.

As shown in FIG. 1, the liquid passage portion 2d is a passage member that guides the liquid working fluid condensed in the condenser 2c to the equipment heat exchanger 2a. The liquid passage 2d has a lower end connected to the liquid inlet 2ac of the equipment heat exchanger 2a and an upper end connected to the liquid outlet 2cb of the condenser 2c. The liquid passage portion 2d of the present embodiment is constituted by a pipe in which a flow path through which a working fluid flows is formed. In the liquid passage portion 2d of the present embodiment, the portion on the condenser 2c side is positioned above the portion on the equipment heat exchanger 2a side. Further, the liquid passage portion 2d of the present embodiment is configured such that the part on the equipment heat exchanger 2a side is located at the same level as or the upper part of the lowermost part of the equipment heat exchanger 2a. The liquid passage portion 2d shown in the drawing is merely an example. The liquid passage portion 2d can be appropriately changed in consideration of the mounting property on the vehicle.

As described above, in the device temperature control apparatus 1 according to the present embodiment, in the device fluid circuit 2, the heat medium supplied by the working fluid cooling / radiating amount adjustment unit (that is, the refrigerant of the first refrigeration cycle 31). ) Of a cold storage agent CS that accumulates at least one of the cold heat.

For this reason, in the apparatus temperature control apparatus 1 which concerns on this embodiment, even when the thermal radiation capability of the heat radiation amount adjustment part (namely, 1st freezing cycle 31) falls, the cold heat accumulate | stored in the cool storage agent CS is transmitted to a working fluid. Thus, the working fluid is easily cooled and condensed, and the flow rate of the working fluid in the forward direction is easily maintained. As a result, the forward flow of the working fluid in the device fluid circuit 2 is easily maintained, and as a result, the cooling capacity of the device temperature control device 1 is easily maintained. That is, in the device temperature control apparatus 1 according to the present embodiment, the heat storage capacity of the heat release amount adjusting unit (that is, the first refrigeration cycle 31) is reduced by the cold storage agent CS being arranged in the device fluid circuit 2. Sometimes, the cooling capacity is easily maintained without being lowered.

(Second Embodiment)
A second embodiment of the present disclosure will be described with reference to FIGS. The present embodiment is different from the first embodiment in that the heat dissipation amount adjustment unit is changed to the blower BF, and the other aspects are the same as those of the first embodiment. Therefore, only the parts different from the first embodiment will be described, except for the case where it is specified that it is the same as the first embodiment.

In the first embodiment, the first refrigeration cycle 31 is provided as a heat release amount adjusting unit that adjusts the heat release amount of the working fluid existing in the condenser 2c of the fluid circuit 2 for equipment by supplying a heat medium to the condenser 2c. Thus, the heat exchange is performed between the working fluid and the refrigerant of the refrigeration cycle. On the other hand, in this embodiment, as shown in FIG. 8, the blower BF is provided as the heat release amount adjusting unit, and heat is exchanged between the working fluid and the blown air of the blower BF. That is, the blown air corresponds to a heat medium supplied by the heat dissipation amount adjustment unit.

The blower BF is a device that blows out air in the passenger compartment or outside the passenger compartment toward the equipment heat exchanger 2a. The blower BF includes an electric fan that operates when energized. The blower BF is connected to a control device (not shown), and the blower capacity is controlled based on a control signal from the control device.

That is, in the apparatus temperature control apparatus 1 according to the present embodiment, the working fluid existing in the condenser 2c is cooled by exchanging heat with the air in the vehicle.

The apparatus temperature control apparatus 1 according to the present embodiment also includes the cold storage agent CS that accumulates at least one of the cold heat of the working fluid and the cold heat of the heat medium (that is, the blown air of the blower BF) supplied by the heat dissipation amount adjusting unit. In the present embodiment as well, the cool storage agent CS is configured integrally with the condenser 2c.

For this reason, also in this embodiment, the same effect as the first embodiment can be obtained.

That is, in this embodiment, when the cool storage agent CS is not provided, when the blower capacity of the blower BF is reduced, the heat release capacity of the first refrigeration cycle 31 that is the heat release amount adjustment unit is reduced, thereby condensing the condenser 3b. The capability also decreases, and consequently the cooling performance of the device temperature control device 1 decreases. On the other hand, in the case of the present embodiment having the cool storage agent CS, the working fluid is sufficiently condensed by the cold heat accumulated in the cool storage agent CS being transmitted to the working fluid even if the blowing capacity of the blower BF is reduced. The cooling capacity of the device temperature control device 1 is maintained. The situation where the blowing capacity of the blower BF is lowered is, for example, when the vehicle speed is lowered as shown in FIG. Further, as shown in FIG. 10, it is when the grille shutter is activated due to a request from the vehicle side. Further, as shown in FIG. 11, the blower BF is installed in the vehicle interior. Moreover, since the cool storage agent CS is configured integrally with the condenser 2c, cold heat can be efficiently stored in the cool storage agent CS as in the first embodiment.

Further, similarly to the first embodiment, also in this embodiment, the regenerator CS is gas in the device fluid circuit 2 ahead of the topmost portion of the gas passage portion 2b in the forward direction. It is arranged in front of the exit.

Further, similarly to the first embodiment, also in the present embodiment, the regenerator CS is arranged in the device fluid circuit 2 before the gas inlet portion 2ca and before the gas outlet portion 2ab.

Similarly to the first embodiment, also in this embodiment, the regenerator CS is arranged in the device fluid circuit 2 before the gas inlet 2ca in the forward direction and before the liquid inlet 2ac. ing.

Further, similarly to the first embodiment, in the present embodiment, the flow path is a channel for flowing a heat medium that cools the working fluid by exchanging heat with the working fluid existing in the condenser 2c. The illustrated heat medium flow path is provided. And also in this embodiment, at least one part of the cool storage agent CS is arrange | positioned without a heat medium flow path between working fluid.

Further, similarly to the first embodiment, the present embodiment is also disposed between the working fluid flow path and the heat medium flow path in the condenser 2c.

(Third embodiment)
Next, a third embodiment will be described. The apparatus temperature control apparatus 1 of the present embodiment is different from the apparatus temperature control apparatus 1 of the first and second embodiments in the installation site of the cool storage agent CS, but other configurations are the apparatus temperature control of the first and second embodiments. Same as device 1.

In the present embodiment, the regenerator CS is not provided in the condenser 2c, and as shown in FIGS. 12 and 13, in the gas passage portion 2b, in the forward direction than the uppermost portion of the gas passage portion 2b. Arranged upstream.

More specifically, the cool storage agent CS is in contact with a pipe forming the gas passage part 2b on the downstream side of the gas outlet part 2ab in the forward direction and upstream of the uppermost part of the gas passage part 2b. Is wound in an annular shape.

The cold storage agent CS of this embodiment is for accumulating the cold heat of the working fluid. The material which comprises the cool storage agent CS may be the same as 1st Embodiment, and does not need to be the same. Hereinafter, the operation of the device temperature control apparatus 1 having such a configuration will be described.

[When cold storage agent stores cold]
First, in the cooling mode (that is, when the compressor is operating), the flow of the working fluid when the battery temperature of the assembled battery BP is high due to self-heating during traveling of the vehicle is the first and second implementations. Like the form, it is forward.

And the working fluid in this case is evaporated by absorbing heat from the assembled battery BP in the equipment heat exchanger 2a as in the first and second embodiments, and then the refrigerant side heat of the first refrigeration cycle 31 in the condenser 2c. Heat is condensed to the refrigerant flowing through the exchanger HEC and condensed.

However, in this case, the working fluid of the present embodiment is in the vicinity of the regenerator CS on the upstream side in the forward direction from the uppermost portion of the gas passage portion 2b in the gas phase state while the gas passage portion 2b is moving toward the condenser 2c. Then, it absorbs heat from the regenerator CS. That is, the working fluid passes cold heat to the cool storage agent CS. In other words, the working fluid is allowed to cool to the cool storage agent CS.

In this case, the working fluid can be cooled to the regenerator CS because the refrigerant takes the latent heat of evaporation from the working fluid and cools the working fluid in the condenser 2c when the compressor 3a is operated. This is because the temperature of the working fluid passing through the refrigerant becomes lower than the temperature of the regenerator CS. The state in which the working fluid is condensed in the condenser 2c is a state in which the condenser 2c is operating.

冷 As such operation continues, the regenerator CS continues to accumulate cold energy. However, the cold storage agent CS is different from the first and second embodiments in that cold storage is performed by receiving cold heat from a superheated gas phase working fluid. In addition, when the compressor 3a is not operated and the working fluid cannot radiate heat to the refrigerant in the condenser 2c, that is, when the condenser 2c does not function, the cold storage agent CS cannot store cold.

[When the regenerator CS is allowed to cool and the condenser 2c is operating]
After the cool storage agent CS has sufficiently stored, the gas phase working fluid passing through the gas passage portion 2b toward the condenser 2c becomes higher than the temperature of the cool storage agent CS while the compressor 3a continues to operate. There is a case. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the point that the working fluid cools and evaporates the assembled battery BP in the equipment heat exchanger 2a and flows out from the gas outlet 2ab to the gas passage 2b is the same as in the cold storage of the cool storage agent CS.

The gas phase working fluid that has flowed out radiates heat to the cool storage agent CS in the vicinity of the cool storage agent CS on the upstream side in the forward direction from the uppermost portion of the gas passage portion 2b. That is, the working fluid receives cold heat from the cold storage agent CS. In other words, the cool storage agent CS is cooled to the working fluid. As a result, a part of the gas-phase working fluid is liquefied in the vicinity of the cool storage agent CS, and the specific gravity of the part of the working fluid increases.

Thereby, the part of the working fluid is condensed in the gas passage portion 2b to be in a liquid phase state. The working fluid that has become a liquid phase further falls inside the gas passage portion 2b by its own weight and descends toward the gas outlet portion 2ab. That is, the working fluid in a liquid phase flows backward in the gas passage portion 2b. Further, the liquid-phase working fluid moves into the equipment heat exchanger 2a through the gas outlet 2ab. In the apparatus heat exchanger 2a, a part of the liquid-phase working fluid is evaporated by absorbing heat from the assembled battery BP.

On the other hand, the remaining working fluid that has not been liquefied out of the working fluid that has received cold from the regenerator CS is cooled through the same path as the working fluid of the first and second embodiments. That is, the remaining working fluid that has not been liquefied enters the condenser 2c from the gas inlet 2ca in the gas phase, and dissipates heat to the refrigerant flowing through the refrigerant side heat exchanger HEC of the first refrigeration cycle 31 in the condenser 2c. Condensed. Then, the working fluid condensed in the condenser 2c passes through the liquid passage portion 2d, enters the equipment heat exchanger 2a, and evaporates by absorbing heat from the assembled battery BP.

In this way, while the cool storage agent CS is allowed to cool and the condenser 2c continues to operate, the device temperature control device 1 uses the cool heat accumulated by the cool storage agent CS and the cool heat received from the refrigerant in the refrigeration cycle 3. The assembled battery BP can be cooled.

In this case, the loop flow of the working fluid in the forward direction similar to the first and second embodiments is maintained, but a reverse flow is generated in part. As a result of the backflow, the difference between the height of the working fluid level in the liquid passage portion 2d and the height of the working fluid level in the gas passage portion 2b (that is, the head difference) is the same as in the first and second embodiments. Smaller than that. In addition, the pressure loss when the gas refrigerant passes through the gas passage portion 2b due to the backflow also increases. As a result, the flow rate of the working fluid inside the device fluid circuit 2 is smaller than in the first and second embodiments. This can cause a decrease in the cooling performance of the device temperature control device 1.

In addition to the present embodiment, generally, when the liquid level of the working fluid in the liquid passage portion 2d is higher than the liquid level of the working fluid in the gas passage portion 2b, that is, when there is a positive head difference, the head difference The larger the is, the larger the flow rate of the working fluid.

[When the regenerator CS is allowed to cool and the condenser 2c is inactive]
Next, the case where the compressor 3a stops from the operating state after the cold storage agent CS has sufficiently stored cold will be described. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the point that the working fluid cools and evaporates the assembled battery BP in the equipment heat exchanger 2a and flows out from the gas outlet 2ab to the gas passage 2b is the same as in the cold storage of the cool storage agent CS.

The gas phase working fluid that has flowed out radiates heat to the cool storage agent CS in the vicinity of the cool storage agent CS on the upstream side in the forward direction from the uppermost portion of the gas passage portion 2b. That is, the cool storage agent CS is cooled to the working fluid. As a result, a part of the gas-phase working fluid is liquefied in the vicinity of the cool storage agent CS, and the specific gravity of the part of the working fluid increases.

Thereby, the part of the working fluid is condensed in the gas passage portion 2b to be in a liquid phase state. The working fluid that has become a liquid phase further falls in the gas passage portion 2b due to its own weight and descends toward the gas outlet portion 2ab. That is, the working fluid in a liquid phase flows backward in the gas passage portion 2b. Further, the liquid-phase working fluid moves into the equipment heat exchanger 2a through the gas outlet 2ab. In the apparatus heat exchanger 2a, a part of the liquid-phase working fluid is evaporated by absorbing heat from the assembled battery BP.

On the other hand, the remaining working fluid that has not been liquefied out of the working fluid that has received the cold heat from the cold storage agent CS does not liquefy even when entering the condenser 2c. This is because the compressor 3a is not operating. As a result, the loop flow of the working fluid in the forward direction is not maintained.

Thus, when the cool storage agent CS is allowed to cool and the condenser 2c is not operated, the device temperature control device 1 can cool the assembled battery BP by the cold heat accumulated in the cool storage agent CS, and the loop flow is not maintained.

(Fourth embodiment)
Next, a fourth embodiment will be described. The apparatus temperature control apparatus 1 of the present embodiment is different from the apparatus temperature control apparatus 1 of the first and second embodiments in the installation site of the cool storage agent CS, but other configurations are the apparatus temperature control of the first and second embodiments. Same as device 1.

In the present embodiment, the regenerator CS is not provided in the condenser 2c, and as shown in FIG. 14, in the gas passage portion 2b, on the downstream side in the forward direction from the uppermost portion of the gas passage portion 2b. Have been placed.

More specifically, the cool storage agent CS is in contact with a pipe forming the gas passage part 2b on the downstream side of the uppermost part of the gas passage part 2b in the forward direction and on the upstream side of the gas inlet part 2ca. Is wound in an annular shape. The cool storage agent CS of this embodiment is for accumulating the cold heat of a working fluid. The material which comprises the cool storage agent CS may be the same as 1st Embodiment, and does not need to be the same. Hereinafter, the operation of the device temperature control apparatus 1 having such a configuration will be described.

[When cold storage agent stores cold]
First, in the cooling mode (that is, in a state where the compressor is operating), the operation when the battery temperature of the assembled battery BP is high due to self-heating during traveling of the vehicle is the same as in the third embodiment. However, the working fluid passing through the gas passage portion 2b absorbs heat from the cold storage agent CS in the vicinity of the cold storage agent CS not on the upstream side in the forward direction but on the downstream side of the uppermost portion of the gas passage portion 2b.

The outflowing gaseous working fluid dissipates heat to the cool storage agent CS in the vicinity of the cool storage agent CS on the downstream side in the forward direction from the uppermost portion of the gas passage portion 2b. As a result, a part of the gas-phase working fluid is liquefied in the vicinity of the cool storage agent CS, and the specific gravity of the part of the working fluid increases.

Thereby, the part of the working fluid is condensed in the gas passage portion 2b to be in a liquid phase state. The working fluid that has become a liquid phase further falls inside the gas passage portion 2b by its own weight and descends toward the gas inlet portion 2ca. Further, the liquid-phase working fluid moves into the condenser 2c through the gas inlet 2ca.

On the other hand, the remaining working fluid that has not been liquefied out of the working fluid that has received cold from the regenerator CS is cooled through the same path as the working fluid of the first and second embodiments. That is, the remaining working fluid that has not been liquefied also enters the condenser 2c from the gas inlet 2ca in the gas phase.

The liquid-phase working fluid and the gas-phase working fluid that have entered the condenser 2c radiate heat to the refrigerant flowing through the refrigerant-side heat exchanger HEC of the first refrigeration cycle 31 in the condenser 2c. At this time, the gas-phase working fluid is condensed into a liquid phase. Then, the liquid-phase working fluid passes through the liquid passage portion 2d by its own weight, enters the equipment heat exchanger 2a, and evaporates by absorbing heat from the assembled battery BP.

In this way, while the cool storage agent CS is allowed to cool and the condenser 2c continues to operate, the device temperature control device 1 uses the cool heat accumulated by the cool storage agent CS and the cool heat received from the refrigerant in the refrigeration cycle 3. The assembled battery BP can be cooled. Further, in this case, the loop flow of the working fluid in the forward direction similar to the first and second embodiments is maintained in all the working fluids. Therefore, the condensation performance of the assembled battery BP by the device temperature control device 1 is as good as that of the first and second embodiments.

[When the regenerator CS is allowed to cool and the condenser 2c is inactive]
Next, the case where the compressor 3a is stopped from the operating state after the cold storage agent CS has sufficiently stored cold, or the case where the refrigerant discharge capacity is reduced due to a decrease in the rotation speed of the compressor 3a will be described. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the point that the working fluid cools and evaporates the assembled battery BP in the equipment heat exchanger 2a and flows out from the gas outlet 2ab to the gas passage 2b is the same as in the cold storage of the cool storage agent CS.

Thereby, the part of the working fluid is condensed in the gas passage portion 2b to be in a liquid phase state. The working fluid that has become a liquid phase further falls in the gas passage portion 2b due to its own weight and descends toward the condenser 2c. Further, the liquid-phase working fluid moves into the equipment heat exchanger 2a through the gas outlet 2ab.

The liquid-phase working fluid that has entered the condenser 2c is not cooled by the refrigerant of the first refrigeration cycle 31, and enters the equipment heat exchanger 2a through the liquid passage portion 2d by its own weight, and the assembled battery BP. Evaporates by absorbing heat from

Thus, while the cool storage agent CS is allowed to cool and the condenser 2c is not operating, the device temperature control device 1 can cool the assembled battery BP by the cold heat accumulated in the cool storage agent CS. In this case, the loop flow of the working fluid in the forward direction similar to the first and second embodiments is maintained. Therefore, the condensation performance of the assembled battery BP by the device temperature control device 1 is good.

(Fifth embodiment)
Next, a fifth embodiment will be described. The apparatus temperature control apparatus 1 of the present embodiment is different from the apparatus temperature control apparatus 1 of the first and second embodiments in the installation site of the cool storage agent CS, but other configurations are the apparatus temperature control of the first and second embodiments. Same as device 1.

In the present embodiment, the regenerator CS is not provided in the condenser 2c, but is disposed in the liquid passage portion 2d as shown in FIG. More specifically, the regenerator CS is in contact with the pipe forming the liquid passage part 2d on the downstream side of the liquid outlet part 2cb and the upstream side of the liquid inlet part 2ac in the forward direction with respect to the pipe. It is wound in a ring.

And the working fluid in this case is evaporated by absorbing heat from the assembled battery BP in the equipment heat exchanger 2a as in the first and second embodiments, and then the refrigerant side heat of the first refrigeration cycle 31 in the condenser 2c. It dissipates heat and condenses in the refrigerant flowing through the exchanger HEC, and then returns to the equipment heat exchanger 2a through the liquid passage portion 2d.

However, in this case, the working fluid of the present embodiment absorbs heat from the cool storage agent CS in the vicinity of the cool storage agent CS on the way to the equipment heat exchanger 2a through the liquid passage portion 2d in the liquid phase state. That is, the working fluid is allowed to cool to the cool storage agent CS.

In this case, the working fluid can be allowed to cool to the regenerator CS because the refrigerant takes the latent heat of evaporation from the working fluid and cools the working fluid in the condenser 2c by the operation of the compressor 3a. This is because the temperature of the working fluid passing through the refrigerant becomes lower than the temperature of the regenerator CS. By continuing such an operation, the cold storage agent CS continues to accumulate cold heat.

However, in this case, a part of the liquid-phase working fluid is vaporized by releasing heat to the cold storage agent CS. The vaporized working refrigerant generated by the vaporization rises in the liquid passage portion 2d and moves toward the condenser 2c. That is, the working refrigerant in the gas phase generated by the vaporization flows backward in the liquid passage portion 2d.

In addition, when the compressor 3a is not operating and the working fluid cannot release heat to the refrigerant in the condenser 2c, that is, when the condenser 2c does not function, the cold storage agent CS cannot store cold.

[When the regenerator CS is allowed to cool and the condenser 2c is operating]
After the cold storage agent CS has sufficiently stored cold, the liquid-phase working fluid passing through the liquid passage portion 2d toward the equipment heat exchanger 2a in a state where the compressor 3a continues to operate is more than the temperature of the cold storage agent CS. May become hot. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the working fluid cools and evaporates the assembled battery BP in the equipment heat exchanger 2a, flows out from the gas outlet 2ab to the gas passage 2b, flows into the condenser 2c, condenses, and the liquid passage by its own weight. The point which flows out to the part 2d is the same as that during cold storage of the cold storage agent CS.

The outflowing gas phase working fluid dissipates heat to the cool storage agent CS in the vicinity of the cool storage agent CS in the liquid passage portion 2d. That is, the cool storage agent CS is cooled to the working fluid. As a result, in the vicinity of the cool storage agent CS, the liquid-phase working fluid is further cooled to be in a supercooled state.

The working fluid cooled by the regenerator CS further descends in the liquid passage portion 2d toward the equipment heat exchanger 2a by its own weight. Further, the liquid-phase working fluid moves through the liquid inlet 2ac and into the equipment heat exchanger 2a. In the apparatus heat exchanger 2a, a part of the liquid-phase working fluid is evaporated by absorbing heat from the assembled battery BP.

In this way, while the cool storage agent CS is allowed to cool and the condenser 2c continues to operate, the device temperature control device 1 uses the cool heat accumulated by the cool storage agent CS and the cool heat received from the refrigerant in the refrigeration cycle 3. The assembled battery BP can be cooled. In this case, the loop flow of the working fluid in the forward direction similar to the first and second embodiments is maintained. In addition, the liquid-phase working fluid is cooled by the cool storage agent CS in the liquid passage portion 2d and is brought into a supercooled state. Therefore, the cooling performance of the assembled battery BP by the device temperature control device 1 is improved.

[When the regenerator CS is allowed to cool and the condenser 2c is inactive]
Next, the case where the compressor 3a is stopped from the operating state after the cold storage agent CS has sufficiently stored cold, or the case where the refrigerant discharge capacity is reduced due to a decrease in the rotation speed of the compressor 3a will be described. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the working fluid cools the assembled battery BP in the equipment heat exchanger 2a, evaporates, flows out from the gas outlet portion 2ab to the gas passage portion 2b, and further flows into the condenser 2c from the gas inlet portion 2ca. This is the same as the cold storage of the cold storage agent CS.

The vapor-phase working fluid that has entered the condenser 2c is not cooled by the refrigerant in the first refrigeration cycle 31, and flows out to the liquid passage portion 2d through the liquid outlet portion 2cb. Then, the working fluid in the gas phase radiates heat to the cool storage agent CS in the vicinity of the cool storage agent CS in the liquid passage portion 2d. As a result, a part of the gas-phase working fluid is liquefied in the vicinity of the cool storage agent CS, and the specific gravity of the part of the working fluid increases.

Thereby, the part of the working fluid is condensed in the liquid passage portion 2d to be in a liquid phase state. The working fluid in the liquid phase is further lowered in the liquid passage portion 2d toward the condenser 2c by its own weight. Further, the liquid-phase working fluid moves through the liquid inlet 2ac and into the equipment heat exchanger 2a. In the apparatus heat exchanger 2a, a part of the liquid-phase working fluid is evaporated by absorbing heat from the assembled battery BP.

(Sixth embodiment)
Next, a sixth embodiment will be described. The apparatus temperature control apparatus 1 of the present embodiment is different from the apparatus temperature control apparatus 1 of the first and second embodiments in the installation site of the cool storage agent CS, but other configurations are the apparatus temperature control of the first and second embodiments. Same as device 1.

In the present embodiment, the regenerator CS is not provided in the condenser 2c, and is disposed inside the equipment heat exchanger 2a as shown in FIG. More specifically, the regenerator CS is disposed in the equipment heat exchanger 2a at a position closer to the gas outlet 2ab between the gas outlet 2ab and the liquid inlet 2ac. More specifically, the cool storage agent CS is disposed at the most downstream end in the forward direction in the equipment heat exchanger 2a.

By arranging the cool storage agent CS at such a position, bubbles of the working fluid generated when the cool storage agent CS cools are moved toward the gas passage 2b rather than the liquid passage 2d, that is, in the forward direction. Easy to flow.

Further, the regenerator CS extends from the lower end of the equipment heat exchanger 2a to the heat exchange section 2aa (that is, the upper end of the equipment heat exchanger 2a) in the equipment heat exchanger 2a. As described in the first embodiment, the heat exchange part 2aa constitutes a heat transfer part that moves heat between the assembled battery BP and the equipment heat exchanger 2a.

Thus, since the cool storage agent CS is arranged in the heat exchange part 2aa, it becomes easy to cool the bubbles generated by the evaporation of the working fluid in the equipment heat exchanger 2a by the cool storage agent CS.

However, in this case, the gas-phase working fluid and the liquid-phase working fluid of the present embodiment absorb heat from the cool storage agent CS in the vicinity of the cool storage agent CS in the equipment heat exchanger 2a. That is, the working fluid is allowed to cool to the cool storage agent CS.

In this case, the working fluid can be allowed to cool to the regenerator CS because the refrigerant takes the latent heat of evaporation from the working fluid and cools the working fluid in the condenser 2c when the compressor 3a is operated. This is because the temperature of the working fluid in the vessel 2a is lower than the temperature of the regenerator CS.

冷 As such operation continues, the regenerator CS continues to accumulate cold energy. At this time, the cool storage agent CS receives cold from both the gas-phase working fluid and the liquid-phase working fluid and stores the cold. In addition, when the compressor 3a is not operated and the working fluid cannot radiate heat to the refrigerant in the condenser 2c, that is, when the condenser 2c does not function, the cold storage agent CS cannot store cold.

[When the regenerator CS is allowed to cool and the condenser 2c is operating]
After the cool storage agent CS is sufficiently stored, the working fluid in the equipment heat exchanger 2a may be higher than the temperature of the cool storage agent CS in a state where the compressor 3a continues to operate. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the working fluid cools and evaporates the assembled battery BP in the equipment heat exchanger 2a, flows out from the gas outlet 2ab to the gas passage 2b, flows into the condenser 2c, condenses, and the liquid passage by its own weight. The point which flows out into the part 2d and returns to the heat exchanger 2a for equipment from the liquid passage part 2d is the same as that during cold storage of the cold storage agent CS.

The working fluid in the equipment heat exchanger 2a dissipates heat to the cool storage agent CS in the vicinity of the cool storage agent CS. That is, the cool storage agent CS is cooled to the working fluid. As a result, in the vicinity of the cool storage agent CS, a part of the gas-phase working fluid is liquefied and remains in the equipment heat exchanger 2a. On the other hand, the remaining working fluid that has not been liquefied out of the working fluid that has received cold heat from the cold storage agent CS is cooled through the same path as the working fluid of the first and second embodiments.

In this way, while the cool storage agent CS is allowed to cool and the condenser 2c continues to operate, the device temperature control device 1 uses the cool heat accumulated by the cool storage agent CS and the cool heat received from the refrigerant in the refrigeration cycle 3. The assembled battery BP can be cooled. In this case, since the loop flow of the working fluid in the forward direction similar to that in the first and second embodiments is maintained, the cooling performance of the assembled battery BP by the device temperature adjustment device 1 is good.

[When the regenerator CS is allowed to cool and the condenser 2c is inactive]
Next, the case where the compressor 3a is stopped from the operating state after the cold storage agent CS has sufficiently stored cold, or the case where the refrigerant discharge capacity is reduced due to a decrease in the rotation speed of the compressor 3a will be described. In this case, it is assumed that the battery temperature of the assembled battery BP is still high. In this case, the point that the working fluid cools the assembled battery BP in the equipment heat exchanger 2a is the same as in the cold storage of the cold storage agent CS.

The working fluid heated by the assembled battery BP in the equipment heat exchanger 2a dissipates heat to the cool storage agent CS in the vicinity of the cool storage agent CS. As a result, the working fluid remains in the equipment heat exchanger 2a.

Thus, while the cool storage agent CS is allowed to cool and the condenser 2c is not operating, the device temperature control device 1 can cool the assembled battery BP by the cold heat accumulated in the cool storage agent CS. However, since the compressor 3a is not operated, the working fluid is not cooled by the condenser 2c, and therefore, the loop flow of the working fluid in the forward direction is not maintained.

(Seventh embodiment)
Next, a seventh embodiment will be described. The device temperature control device 1 of the present embodiment is different from the device temperature control device 1 of the first embodiment only in the configuration of the device heat exchanger 2a and the arrangement of the assembled battery BP with respect to the device heat exchanger 2a. Specifically, the equipment heat exchanger 2a of the present embodiment is disposed at a position facing the side surface of the assembled battery BP.

As shown in FIGS. 17 and 18, the equipment heat exchanger 2 a according to the present embodiment includes a tubular upper tank 124, a tubular lower tank 125, and a plurality of tubes communicating the upper tank 124 and the lower tank 125. 126 is comprised. Note that the equipment heat exchanger 2a has a configuration in which the upper tank 124 and the lower tank 125 communicate with each other by a member in which a plurality of flow paths are formed inside a hollow member instead of the plurality of tubes 126. May be.

Each member which comprises the heat exchanger 2a for apparatuses is comprised with metals with high heat conductivity, such as aluminum and copper, for example. In addition, each member which comprises the heat exchanger 2a for apparatuses may be comprised with materials with high heat conductivity other than a metal.

The upper tank 124 is provided in the upper part of the vertical direction DRg in the equipment heat exchanger 2a. The upper tank 124 is provided with a gas outlet 2ab having a function equivalent to that of the first embodiment on one side in the longitudinal direction of the equipment heat exchanger 2a. The lower tank 125 is provided in the lower part of the vertical direction DRg in the equipment heat exchanger 2a. The lower tank 125 is provided with a liquid inlet 2ac having a function equivalent to that of the first embodiment on the other side in the longitudinal direction of the equipment heat exchanger 2a.

The assembled battery BP is installed outside the equipment heat exchanger 2a via a heat conductive sheet 13 having electrical insulation. The device heat exchanger 2a is electrically insulated from the assembled battery BP by the heat conductive sheet 13, and has a small thermal resistance with the assembled battery BP.

The equipment heat exchanger 2a is arranged to face the assembled battery BP in a direction orthogonal to the vertical direction DRg. In the device heat exchanger 2a of the present embodiment, a portion facing the assembled battery BP in the direction orthogonal to the vertical direction DRg constitutes a heat exchange unit 121 that exchanges heat with the assembled battery BP.

The heat exchange unit 121 is a heat transfer unit that moves heat between the assembled battery BP and the device heat exchanger 2a. In this embodiment, the heat exchange part 121 comprises the heat exchange site | part which heat-exchanges with the assembled battery BP in the heat exchanger 2a for apparatuses.

The heat exchanging part 121 has a size that covers almost the entire side surfaces of both the assembled batteries BP so that no temperature distribution is generated in each battery cell BC constituting the assembled battery BP. In addition, the heat exchange part 121 of this embodiment is extended along the perpendicular direction DRg.

The assembled battery BP of the present embodiment is such that the surface opposite to the surface on which the terminal TE is provided faces the heat exchanging parts 121 on both side surfaces of the equipment heat exchanger 2a via the heat conductive sheet 13. is set up. The battery cells BC constituting the assembled battery BP are arranged in a direction intersecting the vertical direction DRg. Operation | movement of the apparatus temperature control apparatus 1 in this embodiment is the same as that of 1st Embodiment.

(Eighth embodiment)
Next, an eighth embodiment will be described. In the apparatus temperature control apparatus 1 of this embodiment, as shown in FIG. 19, with respect to the apparatus temperature control apparatus 1 of 7th Embodiment, the position of the cool storage agent CS is moved to the position equivalent to 3rd Embodiment. has been edited. That is, the cool storage agent CS is disposed on the upstream side in the forward direction of the gas passage portion 2b with respect to the uppermost portion of the gas passage portion 2b. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 3rd Embodiment.

(Ninth embodiment)
Next, a ninth embodiment will be described. In the apparatus temperature control apparatus 1 of this embodiment, as shown in FIG. 20, with respect to the apparatus temperature control apparatus 1 of 7th Embodiment, the position of the cool storage agent CS is moved to the position equivalent to 4th Embodiment. has been edited. That is, the cool storage agent CS is disposed on the downstream side in the forward direction of the gas passage portion 2b with respect to the uppermost portion of the gas passage portion 2b. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 4th Embodiment.

(10th Embodiment)
Next, a tenth embodiment will be described. As shown in FIG. 21, the device temperature adjustment device 1 of the present embodiment moves the position of the regenerator CS to a position equivalent to that of the fifth embodiment with respect to the device temperature adjustment device 1 of the seventh embodiment. has been edited. That is, the cool storage agent CS is disposed in the liquid passage portion 2d. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 5th Embodiment.

(Eleventh embodiment)
Next, an eleventh embodiment will be described. The apparatus temperature adjustment apparatus 1 of the present embodiment is different from the apparatus temperature adjustment apparatus 1 of the seventh embodiment in the installation site of the cool storage agent CS, but the other configuration is the same as the apparatus temperature adjustment apparatus 1 of the seventh embodiment. .

In the present embodiment, the regenerator CS is not provided in the condenser 2c, but is disposed inside the equipment heat exchanger 2a as shown in FIG. 22A. More specifically, the regenerator CS is disposed in the tube 126 of the equipment heat exchanger 2a at a position closer to the liquid inlet 2ac between the gas outlet 2ab and the liquid inlet 2ac. More specifically, the cool storage agent CS is disposed at the most upstream end in the forward direction in the equipment heat exchanger 2a. In addition, the cool storage agent CS may be disposed at a position closer to the gas outlet 2ab of the gas outlet 2ab and the liquid inlet 2ac in the tube 126 of the equipment heat exchanger 2a.

Further, the regenerator CS extends from the lower end to the upper end of the tube 126 in the tube 126. Therefore, the cool storage agent CS contacts the working fluid and exchanges heat both above and below the liquid level of the working fluid in the tube 126. This is to realize both cold storage of the cold storage agent CS accompanying the evaporation of the working fluid and natural cooling of the cold storage agent CS accompanying the condensation of the working fluid.

Actually, as shown in FIG. 22A, the liquid level LS of the working fluid in the tube 126 may or may not be cooled even if the cool storage agent CS is stored cold or the compressor 3a is operating. Is lower than the upper end of the tube 126 and higher than the lower end of the tube 126. Therefore, the cool storage agent CS is above the liquid level of the working fluid in the tube 126 regardless of whether the cool storage agent CS cools or cools and the condenser 2c is not operating. Heat exchange in contact with the working fluid.

If this is the case, when the regenerator CS is allowed to cool, the gas-phase working fluid can be condensed by exchanging heat with the regenerator CS in the equipment heat exchanger 2a. Further, when the cold storage agent CS is stored cold, the liquid-phase working fluid in the equipment heat exchanger 2a can be evaporated by exchanging heat with the cold storage agent CS.

In addition, as the cool storage agent CS, the thermal conductivity may be higher than the working fluid in the gas phase than the working fluid in the liquid phase. If it becomes like this, the part which contact | connects the liquid-phase working fluid among the cool storage agents CS and the part which contact | connects a gaseous-phase working fluid can perform heat exchange mutually rapidly.

Therefore, when the cool storage agent CS is storing cold, not only the portion of the cool storage agent CS that contacts the liquid working fluid but also the portion that contacts the gas working fluid is sufficiently cooled. That is, at the time of cold storage, the cool storage agent CS is not stored only in a part (that is, a part in contact with the liquid-phase working fluid), but the possibility that the entire cool storage agent CS is used for cold storage is increased.

When the cool storage agent CS is allowed to cool, not only the portion of the cool storage agent CS that comes into contact with the gas phase working fluid but also the portion that touches the liquid phase working fluid is sufficiently cooled. That is, at the time of cooling, not only a part of the regenerator CS (that is, a part in contact with the gas-phase working fluid) is allowed to cool, but the possibility that the whole regenerator CS is used for cooling is increased.

In the present embodiment, as shown in FIG. 22B, the regenerator CS may be in contact with the high thermal conductivity member CSx on one side and the other side. The high thermal conductivity member CSx extends from the upper side to the lower side of the liquid level LS of the working fluid both when the condenser 2c is operating and when not operating. That is, the high thermal conductivity member CSx contacts both the liquid-phase working fluid and the gas-phase working fluid both when the condenser 2c is operating and when not operating. The thermal conductivity of the high thermal conductivity member CSx is higher than that of the regenerator CS than the working fluid in the gas phase than the working fluid in the liquid phase.

If it becomes like this, among the cool storage agent CS, the part mainly exchanging heat with the liquid phase working fluid and the part mainly exchanging heat with the gas phase working fluid will pass through the high thermal conductivity member CSx. Heat exchange with each other quickly. As a result, there is a high possibility that the entire cool storage agent CS will be used for cooling, both during cold storage and during cooling.

Here, the portion that mainly exchanges heat with the liquid-phase working fluid may be in contact with the liquid-phase working fluid, or may exchange heat with the liquid-phase working fluid via the high thermal conductivity member CSx. Good. In addition, the portion that mainly exchanges heat with the gas phase working fluid may be in contact with the gas phase working fluid, or may exchange heat with the gas phase working fluid via the high thermal conductivity member CSx. .

(Twelfth embodiment)
Next, a twelfth embodiment will be described. The difference between the device temperature control device 1 of the present embodiment and the device temperature control device 1 of the seventh embodiment is the arrangement of the gas passage portion 2b, the condenser 2c, and the liquid passage portion 2d with respect to the device heat exchanger 2a.

Specifically, as shown in FIG. 23, the entire condenser 2c of the present embodiment is below the upper end of the equipment heat exchanger 2a and above the lower end of the equipment heat exchanger 2a. is there. In addition, the vertical center position of the condenser 2c coincides with the vertical center position of the equipment heat exchanger 2a.

Unlike the seventh embodiment, the gas outlet 2ab is provided on the upper tank 124 on the side close to the condenser 2c in the longitudinal direction of the equipment heat exchanger 2a. Further, the gas passage portion 2b extends in the horizontal direction from the gas outlet portion 2ab toward the condenser 2c without passing through a position higher than the whole of the equipment heat exchanger 2a. Further, the gas passage portion 2b is bent by about 90 ° and extends downward to reach the gas inlet portion 2ca. Further, the liquid passage portion 2d extends downward from the liquid outlet portion 2cb, bends about 90 °, and does not pass through a position lower than the whole of the device heat exchanger 2a in the horizontal direction. To reach the liquid inlet 2ac.

Here, the vertical position of the condenser 2c with respect to the equipment heat exchanger 2a will be further described. The whole condenser 2c is disposed above the lower end of the tube 126, and is disposed above the lower end of the heat exchanging part 121 (that is, a heat exchange part that exchanges heat with the assembled battery BP).

As already described, the circulation of the working fluid in the device fluid circuit 2 is realized by the head difference. That is, the head difference becomes a driving source for circulating the working fluid. Therefore, when the condenser 2c operates and the working fluid circulates in the forward direction (that is, in the clockwise direction in FIG. 23), the liquid passage portion rather than the liquid level of the working fluid in the equipment heat exchanger 2a. The liquid level of the working fluid in 2d is higher.

In addition, when the liquid level of the working fluid becomes the lowest in the equipment heat exchanger 2a, the height of the liquid level is expected to coincide with the lower end of the heat exchanging part 121 that is a heat exchange part. Therefore, if the lower end of the condenser 2c is lower than the lower end of the heat exchange unit 121, at least a part of the inside of the condenser 2c is always filled with the liquid-phase working fluid, and the working fluid does not condense.

From this point of view, it is desirable that the lower end of the condenser 2c is located above the lower end of the heat exchange unit 121 from the viewpoint of using the entire condenser 2c. Further, it is desirable that the lower end of the condenser 2c is located above the lower tank 125.

(13th Embodiment)
Next, a thirteenth embodiment will be described. As shown in FIG. 24, in the device temperature control apparatus 1 of the present embodiment, the cold storage agent CS is upstream in the forward direction of the gas passage portion 2b in the forward direction, as in the eighth embodiment. On the side. The difference between the device temperature control device 1 of the present embodiment and the device temperature control device 1 of the eighth embodiment is the arrangement of the gas passage 2b, the condenser 2c, and the liquid passage 2d with respect to the device heat exchanger 2a.

Specifically, as shown in FIG. 24, the entire condenser 2c of the present embodiment is below the upper end of the equipment heat exchanger 2a and above the lower end of the equipment heat exchanger 2a. is there. In addition, the vertical center position of the condenser 2c coincides with the vertical center position of the equipment heat exchanger 2a.

Unlike the eighth embodiment, the gas outlet 2ab is provided on the upper tank 124 on the side close to the condenser 2c in the longitudinal direction of the equipment heat exchanger 2a. Further, the gas passage portion 2b extends upward from the gas outlet portion 2ab and reaches a position higher than the entire heat exchanger for equipment 2a. Further, the gas passage portion 2b is bent by about 90 °, extends in the horizontal direction and further bent by about 90 ° at a position higher than the whole of the equipment heat exchanger 2a, and extends downward to reach the gas inlet portion 2ca. .

Here, the vertical position of the condenser 2c relative to the equipment heat exchanger 2a is the same as in the twelfth embodiment. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 8th Embodiment.

(14th Embodiment)
Next, a fourteenth embodiment will be described. As shown in FIG. 25, in the device temperature control apparatus 1 of the present embodiment, the cold storage agent CS is downstream in the forward direction from the uppermost part of the gas passage portion 2b in the gas passage portion 2b, as in the ninth embodiment. On the side. The difference between the device temperature control device 1 of the present embodiment and the device temperature control device 1 of the ninth embodiment is the arrangement of the gas passage part 2b, the condenser 2c, and the liquid passage part 2d with respect to the equipment heat exchanger 2a.

Specifically, it is as shown in FIG. That is, the same changes as applied to the seventh embodiment in the twelfth embodiment are applied to the ninth embodiment. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 9th Embodiment.

(Fifteenth embodiment)
Next, a fifteenth embodiment is described. As shown in FIG. 26, in the device temperature control apparatus 1 of the present embodiment, the cool storage agent CS is disposed in the liquid passage portion 2d, as in the tenth embodiment. The difference between the device temperature control device 1 of the present embodiment and the device temperature control device 1 of the tenth embodiment is the arrangement of the gas passage portion 2b, the condenser 2c, and the liquid passage portion 2d with respect to the device heat exchanger 2a.

Specifically, it is as shown in FIG. That is, the same changes as applied to the seventh embodiment in the twelfth embodiment are applied to the tenth embodiment. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 10th Embodiment.

(Sixteenth embodiment)
Next, a sixteenth embodiment will be described. As shown in FIG. 27, in the device temperature control apparatus 1 of the present embodiment, the regenerator CS is disposed in the device heat exchanger 2a, as in the eleventh embodiment. The difference between the device temperature control device 1 of the present embodiment and the device temperature control device 1 of the eleventh embodiment is the arrangement of the gas passage portion 2b, the condenser 2c, and the liquid passage portion 2d with respect to the device heat exchanger 2a.

Specifically, it is as shown in FIG. That is, the same changes as applied to the seventh embodiment in the twelfth embodiment are applied to the eleventh embodiment. Operation | movement of the apparatus temperature control apparatus 1 of this embodiment is the same as that of 10th Embodiment.

(Other embodiments)
The present disclosure is not limited to the above-described embodiment, and can be appropriately changed within the scope described in the claims.

For example, in the first and second embodiments, the cold storage agent CS is configured integrally with the condenser 2c, but is not limited to this configuration.

However, even if the cool storage agent CS is not integrally formed with the condenser 2c, the above-described effects can be obtained as long as the cool storage agent CS is disposed at least in the device fluid circuit 2. That is, if the cool storage agent CS is arranged in the fluid circuit 2 for equipment, the cold heat accumulated in the cool storage agent CS is transmitted to the working fluid, so that the working fluid is easily cooled and condensed, and the cooling capacity is reduced. It becomes easy to be maintained.

Even if the regenerator CS is not integrated with the condenser 2c, the gas outlet portion 2ab is ahead of the uppermost portion of the gas passage portion 2b in the forward direction in the fluid circuit 2 for equipment. If the cool storage agent CS is arranged on the near side, the above effect can be obtained. That is, if the regenerator CS is disposed before the gas outlet portion 2ab before the uppermost portion of the gas passage portion 2b in the forward direction in the fluid circuit 2 for equipment, the working fluid The forward flow is more easily maintained. This is because the flow rate of the working fluid in the forward direction does not decrease unlike the case where the cool storage agent CS is disposed in a portion before the uppermost portion.

Even if the regenerator CS is not integrally formed with the condenser 2c, the regenerator CS is arranged in the device fluid circuit 2 before the gas inlet 2ca and before the gas outlet 2ab. In this case, the above effect can be obtained. That is, if the regenerator CS is disposed before the gas inlet 2ca and before the gas outlet 2ab in the device fluid circuit 2, the liquid working fluid condensed by the condenser 2c is used as the regenerator. By exchanging heat with CS, cold energy can be accumulated in the cold storage agent CS.

Further, even if the regenerator CS is not integrally formed with the condenser 2c, the regenerator CS is arranged in the fluid circuit 2 for equipment ahead of the gas inlet 2ca in the forward direction and before the liquid inlet 2ac. If it is done, the above effect can be obtained. In other words, if the regenerator CS is disposed before the gas inlet 2ca in the forward direction and before the liquid inlet 2ac in the device fluid circuit 2, the forward flow of the working fluid is more likely to occur. Become. This is because the liquid working fluid condensed by the condenser 2c is heat-exchanged with the cold storage agent CS, so that the gaseous working fluid is liquefied and falls down by the cold heat accumulated in the cold storage agent CS.

Moreover, since water has a large heat capacity, water may be used as the regenerator CS of the above embodiment. That is, in the above embodiment, as shown in FIG. 28, the cold heat of the working fluid may be accumulated by the water flowing through the water circulation path 4 through which the water circulates. This water is antifreeze. Reference numeral 4a in FIG. 28 is a pump. Reference numeral 4b denotes a heat exchanger. Reference numeral 4c is a valve. Reference numeral 4d denotes a cooler core. The cooler core is a heat exchanger for cooling the vehicle interior by generating cold air by exchanging heat between the cold water in the water circulation path 4 and the air in the vehicle interior, and is used as an alternative to the evaporator. The cooler core performs cooling by heat exchange between water and air. Reference numeral 4e denotes a heat exchanger. By exchanging heat between the working fluid flowing in the condenser 2c and the water flowing in the heat exchanger 4e, the water is cooled when the water is stored, and the water is warmed when the water is allowed to cool. The heat exchanger 4e and the condenser 2c constitute an integral condenser.

Numeral 5 in FIG. 28 is a refrigeration cycle. Reference numeral 5 a is a compressor, reference numeral 5 b is a condenser, reference numeral 5 c is an expansion valve, and reference numeral 5 e is an evaporator for exchanging heat between the refrigerant flowing through the refrigeration cycle 5 and the water flowing through the water circulation path 4. is there. Water is cooled by heat exchange between the water flowing in the heat exchanger 4b and the refrigerant evaporated in the evaporator 5e. The heat exchanger 4b and the evaporator 5e together constitute a chiller (that is, a water refrigerant heat exchanger).

Thus, when water is used as the regenerator CS, stable cooling is possible with a simple configuration. In the example of FIG. 28, water cooled by the refrigeration cycle 5 (that is, water flowing through the water circulation path 4) is used for heat dissipation as the heat dissipation amount adjusting unit and also used for cooling the cooler core. In addition, you may make it use the water cooled by the refrigerating cycle 5 only for the heat radiation as a heat radiation amount adjustment part.

In the example of FIG. 28, the cooler core 4d and the

condensers

2c and 4e are arranged in parallel, but may be arranged in series. In that case, it is desirable to provide a valve after providing a flow path that bypasses at least one of the cooler core 4d and the

condensers

2c and 4e. In the example of FIG. 28, the cooler core 4d is used as a heat exchanger for cooling the passenger compartment. However, as shown in FIG. 29, in the refrigeration cycle 5, a conventional evaporator 5f for cooling the passenger compartment may be used.

In FIG. 29, two

evaporators

5e and 5f are connected in series. However, as shown in FIG. 30, two

evaporators

5e and 5f may be arranged in parallel. At this time, it is desirable to install the

expansion valves

5c and 5d upstream of each of the two

evaporators

5e and 5f.

In the examples of FIGS. 28, 29, and 30, the heat exchanger 4b is connected to the evaporator 5e in order to exchange heat between the water flowing through the water circulation path 4 and the refrigerant flowing through the refrigeration cycle 5. However, as shown in FIG. 31, the heat exchanger 4b may be a radiator that radiates heat from the water flowing through the water circulation path 4 to the outside air.

Further, as shown in FIG. 32, a radiator 4f and a valve 4g may be added to the water circulation path 4 of FIG. The radiator 4f is disposed in the radiator flow path 4h in the water circulation path 4, and radiates heat from the water flowing in the radiator 4f to the outside air. The valve 4g switches between a state where water discharged from the pump 4a flows into the radiator flow path 4h and a state where water discharged from the pump 4a flows into the radiator bypass flow path 4i. In the latter state, the water discharged from the pump 4a bypasses the radiator 4f and flows into the heat exchanger 4b. These two states realized by the valve 4g are switched according to the temperature of the water and the like. By doing in this way, the refrigerant | coolant of the refrigerating cycle 5 and two outside air can be ensured as a heat dissipation point of water.

Further, as shown in FIG. 33, the heat exchanger 4b, the heat exchanger 44e, the condenser 2c, and the evaporator 5e may be configured as an integral casing as a whole with respect to the water circulation path 4 in FIG. Good. By doing in this way, the heat exchanger for carrying out heat exchange of the three media which distribute | circulate the refrigerating cycle 5, the water circulation path 4, and the fluid circuit 2 for apparatuses can be comprised as one housing | casing. In this housing, the water in the heat exchanger 4b and the refrigerant in the evaporator 5e exchange heat, and the water in the heat exchanger 4e and the working fluid in the condenser 2c exchange heat.

Further, as shown in FIG. 34, a pump 4j, an inverter 4k, a valve 4m, and an inverter flow path 4n may be added to the water circulation path 4 of FIG. The valve 4m is disposed between the outlet of the radiator 4f and the downstream end of the radiator bypass passage 4i. The inverter flow path 4n is a flow path that connects the valve 4m to the valve 4g and the radiator 4f inlet.

The pump 4j is arranged in the inverter flow path 4n, sucks water in the inverter flow path 4n, and discharges it to the inverter 4k side. The inverter 4k is an electric device that converts direct current into alternating current, and generates heat during operation. The inverter 4k is cooled by exchanging heat with water flowing through the inverter flow path 4n.

The valve 4m switches between a state where the inverter flow path 4n is closed and the radiator flow path 4h is opened, and a state where the inverter flow path 4n is opened and the radiator flow path 4h is closed. In the former case, the water is cooled by the radiator 4f. In the latter case, the water is heated by cooling the inverter 4k. Thus, a circuit for cooling the inverter 4k can be integrated into the water circulation path 4.

Note that the modifications shown in FIGS. 28 to 34 with respect to the first embodiment may be applied to the third to sixth embodiments.

In the above embodiment, the water-cooled condenser 2c is connected to the evaporator 5e in order to exchange heat with the refrigeration cycle. However, the water-cooled condenser 2c may be connected to a heat exchanger for exchanging heat with the outside air or air in the passenger compartment. good.

(Summary)
In the 1st viewpoint shown by one part or all part of said each embodiment, in the apparatus temperature control apparatus which can cool a temperature control object apparatus, the heat exchanger for apparatus, a gas passage part, a condenser, and liquid An annular device fluid circuit including a passage portion. The equipment heat exchanger cools the temperature control target device by absorbing heat from the temperature control target device and evaporating the liquid working fluid. The gas passage portion guides the gaseous working fluid evaporated in the equipment heat exchanger to the condenser. The condenser is disposed above the equipment heat exchanger, and condenses the gaseous working fluid evaporated in the equipment heat exchanger. The liquid passage portion guides the liquid working fluid condensed by the condenser to the equipment heat exchanger. And this apparatus temperature control apparatus has a cool storage agent which is arrange | positioned at the fluid circuit for apparatuses and accumulate | stores at least one of the cold heat of a working fluid, and the cold heat of a heat medium.

Further, according to the second aspect, the cold storage agent is configured integrally with the condenser. By doing in this way, it can cool directly from the heat medium of a heat radiation amount adjustment part.

Further, according to the third aspect, the cool storage agent is disposed on the downstream side of the condenser and on the upstream side of the equipment heat exchanger. By doing in this way, it can cool from the working fluid of a liquid phase state. Further, when the cool storage agent is allowed to cool, the cool storage agent can further cool the working fluid in the liquid phase. That is, the working fluid can be brought into a subcooled state.

Moreover, according to the 4th viewpoint, the cool storage agent is arrange | positioned in the gas passage part downstream from the uppermost part of the gas passage part. By doing in this way, a cool storage agent can cool-store and cool-down, maintaining the loop through which a working fluid flows in order of an equipment heat exchanger, a gas passage part, a condenser, and a liquid passage part.

Further, according to the fifth aspect, the cold storage agent is disposed in the equipment heat exchanger. By doing in this way, a cool storage agent can store cold, maintaining the loop through which a working fluid flows in order of an equipment heat exchanger, a gas passage part, a condenser, and a liquid passage part.

Further, according to the sixth aspect, the cold storage agent is disposed in the gas passage portion on the upstream side of the uppermost portion of the gas passage portion. By doing in this way, a cool storage agent can store cold, maintaining the loop through which a working fluid flows in order of an equipment heat exchanger, a gas passage part, a condenser, and a liquid passage part.

Also, in the seventh aspect, in the device temperature control apparatus in the first aspect, the cold storage agent is configured integrally with the condenser.

According to the seventh aspect, since the liquid working fluid condensed by the condenser can be immediately heat-exchanged with the cold storage agent, cold energy can be efficiently accumulated in the cold storage agent, and the order of the working fluid can be increased. The directional flow is particularly easily maintained.

Moreover, in the 8th viewpoint shown by one part or all of said each embodiment, in the apparatus temperature control apparatus in any one viewpoint of 1st thru | or 7, a heat radiation amount adjustment part exists in the inside of a condenser. It is a refrigeration cycle having a heat medium flow path that is a flow path for flowing a heat medium that cools the working fluid by exchanging heat with the working fluid.

In the ninth aspect shown in part or all of the above embodiments, in the device temperature control apparatus according to the eighth aspect, the refrigeration cycle is the first refrigeration cycle, and the first refrigeration cycle is compressed. Actuated by a compressor of an air conditioner with a second refrigeration cycle actuated by the machine.

Moreover, in the 10th viewpoint shown by one part or all of said each embodiment, in the apparatus temperature control apparatus in any one viewpoint of 1st thru | or 7, it is between the working fluid which exists in the inside of a condenser. It is a blower that blows blown air that cools the working fluid by exchanging heat. Moreover, it has the heat medium flow path which is a flow path for flowing the heat medium which cools this working fluid by exchanging heat with the working fluid which exists in the inside of a condenser.

In the eleventh aspect shown in part or all of the above embodiments, in the apparatus temperature control apparatus according to the eighth or tenth aspect, the cold storage agent is interposed between the working fluid and the heat medium flow path. Without being arranged. Specifically, at least a part of the cool storage agent is disposed between the working fluid and the heat medium flow path. According to the ninth aspect, the cold energy of the cool storage agent is easily transmitted to the working fluid, and the forward flow of the working fluid is particularly easily maintained.

Further, in a twelfth aspect shown in a part or all of each of the above embodiments, in the apparatus temperature control apparatus according to the eighth or tenth aspect, the cold storage agent is a flow path of the working fluid in the condenser and a heat medium flow It is arranged between the road. Specifically, at least a part of the cool storage agent is disposed between the working fluid flow path and the heat medium flow path in the condenser.

According to the tenth aspect, the cold energy of the cool storage agent is easily transmitted to the working fluid, and the forward flow of the working fluid is particularly easily maintained.

In a thirteenth aspect shown in part or all of the above embodiments, in the device temperature control apparatus according to any one of the first to seventh aspects, the cold storage agent flows through a water circulation path through which water circulates. It is water.

In the fourteenth aspect shown in part or all of the above embodiments, in the apparatus temperature adjustment device according to any one of the first to thirteenth aspects, the temperature adjustment target apparatus has a plurality of battery cells. It is an assembled battery.

According to the fourteenth aspect, since the temperature adjustment target device is cooled using latent heat, the temperature variation of each battery cell can be reduced, and each battery cell can be cooled uniformly. Therefore, it is particularly suitable for cooling an assembled battery in which temperature equalization for reducing the temperature variation of each battery cell is important.

In another aspect, in the equipment temperature control apparatus according to the first aspect, in the forward direction, the equipment heat exchanger, the gas passage section, the condenser, and the liquid passage section are arranged in this order, and the equipment heat exchange is performed. The vessel has a gas outlet portion to which the lower end portion of the gas passage portion is connected. And the cool storage agent is arrange | positioned ahead of the gas outlet part ahead of the uppermost part located in the uppermost part among the gas passage parts in a forward direction in the fluid circuit for apparatuses.

According to this aspect, the cool storage agent is disposed in front of the uppermost portion of the gas passage portion in the forward direction, and the cool storage agent is disposed in front of the gas outlet portion. Since the flow rate of the working fluid in the forward direction does not decrease as in the case where is disposed, the forward flow of the working fluid is more easily maintained.

In another aspect, in the equipment temperature control apparatus according to the first aspect, in the forward direction, the equipment heat exchanger, the gas passage section, the condenser, and the liquid passage section are arranged in this order, and the equipment heat exchange is performed. The vessel has a gas inlet portion to which an upper end portion of the gas passage portion is connected. And the cool storage agent is arrange | positioned ahead of the gas inlet part in a forward direction, and before the gas outlet part in the fluid circuit for apparatuses.

According to this aspect, the cool storage agent is disposed before the gas inlet of the condenser in the forward direction, that is, the cool storage agent is disposed downstream of the condenser. Therefore, cold heat can be accumulated in the cold storage agent by exchanging heat between the liquid working fluid condensed by the condenser and the cold storage agent.

In another aspect, in the equipment temperature control apparatus according to the first aspect, the equipment heat exchanger, the gas passage section, the condenser, and the liquid passage section are arranged in this order in the forward direction. Further, the equipment heat exchanger has a liquid inlet portion to which the lower end portion of the liquid passage portion is connected, and the condenser has a gas inlet portion to which the upper end portion of the gas passage portion is connected. Have. And the cool storage agent is arrange | positioned in the fluid circuit for apparatuses ahead of the gas inlet part in the forward direction, and before this liquid inlet part.

According to this aspect, the cool storage agent is disposed before the gas inlet of the condenser in the forward direction, that is, the cool storage agent is disposed downstream of the condenser. Therefore, cold heat can be accumulated in the cold storage agent by exchanging heat between the liquid working fluid condensed by the condenser and the cold storage agent. Furthermore, the cool storage agent is disposed in front of the liquid inlet portion of the equipment heat exchanger in the forward direction, that is, the cool storage agent is disposed upstream of the equipment heat exchanger. Of the liquid passage portion in the forward direction, the portion from the liquid outlet portion of the condenser to the liquid inlet portion of the equipment heat exchanger is a passage in which the working fluid is directed from top to bottom in the forward direction. For this reason, by arranging the cool storage agent in the part leading to the liquid inlet, the gaseous working fluid is liquefied by the cold heat accumulated in the cool storage agent and falls down, so that the forward direction of the working fluid is reduced. Flow is more likely to occur.

Claims

A device temperature control device capable of cooling a temperature control target device (BP),
A heat exchanger for equipment (2a) that cools the temperature control target device by absorbing heat from the temperature control target device and evaporating the liquid working fluid;
A condenser (2c) for condensing the gaseous working fluid evaporated in the equipment heat exchanger;
A gas passage portion (2b) for guiding the gaseous working fluid evaporated in the equipment heat exchanger to the condenser;
A liquid passage portion (2d) for guiding the liquid working fluid condensed in the condenser to the device heat exchanger, and an annular device fluid circuit (2) configured to include
The heat dissipation amount of the working fluid is adjusted by a heat dissipation amount adjusting unit (31, BF) that exchanges heat between the heat medium and the working fluid existing inside the condenser by supplying the heat medium to the condenser. ,
A device temperature control device having a cold storage agent (CS) that is disposed in the device fluid circuit and stores at least one of cold heat of the working fluid and cold heat of the heat medium.
The apparatus temperature control device according to claim 1, wherein the cold storage agent is configured integrally with the condenser.
The equipment temperature control device according to claim 1, wherein the cold storage agent is disposed on the downstream side of the condenser and on the upstream side of the equipment heat exchanger.
The apparatus temperature control device according to claim 1, wherein the cold storage agent is disposed in the gas passage portion on the downstream side of the uppermost portion of the gas passage portion.
The equipment temperature control device according to claim 1, wherein the cold storage agent is disposed in the equipment heat exchanger.
The apparatus temperature control device according to claim 1, wherein the cold storage agent is disposed in the gas passage portion on the upstream side of the uppermost portion of the gas passage portion.
The apparatus temperature control device according to claim 1, wherein the cold storage agent is configured integrally with the condenser.
The heat dissipation amount adjustment unit includes a heat medium flow path (31a) that is a flow path for flowing a heat medium that cools the working fluid by exchanging heat with the working fluid existing inside the condenser. It is a refrigerating cycle (31) which has, The apparatus temperature control apparatus as described in any one of Claim 1 thru | or 7.
The refrigeration cycle is a first refrigeration cycle;
The apparatus temperature control device according to claim 8, wherein the first refrigeration cycle is operated by the compressor of an air conditioner including a second refrigeration cycle (32) operated by a compressor (3a).
The heat dissipation amount adjustment unit is a blower (BF) that blows blown air that cools the working fluid by exchanging heat with the working fluid existing inside the condenser.
The heat medium flow path which is a flow path for flowing the heat medium which cools this working fluid by exchanging heat with the said working fluid which exists in the inside of the said condenser. Equipment temperature control device as described in one.
The apparatus temperature control device according to claim 8 or 10, wherein at least a part of the cold storage agent is disposed between the working fluid and the heat medium passage without being interposed.
The apparatus temperature control according to claim 8 or 10, wherein at least a part of the cold storage agent is disposed between the flow path (P1) of the working fluid and the heat medium flow path (P2) in the condenser. apparatus.
The device temperature control device according to any one of claims 1 to 7, wherein the cold storage agent is the water flowing through a water circulation path (4) through which water circulates.
The device temperature control device according to any one of claims 1 to 13, wherein the temperature control target device is a battery pack (BP) having a plurality of battery cells (BC).