WO2018047534A1 - Instrument temperature adjustment device - Google Patents

Abstract

This instrument temperature adjustment device for adjusting the temperature of a target instrument (2) comprises an evaporator (3), a first condenser (41), and a second condenser (42). The evaporator (3) cools the target instrument (2) by the latent heat of vaporization of a working fluid that absorbs heat from the target instrument (2) and evaporates. The first condenser (41) is provided on the upper side, in the gravitational direction, of the evaporator (3), and includes a first heat exchange passage (412) that condenses the working fluid having evaporated in the evaporator (3) by heat exchange with a first medium in the exterior. The second condenser (42) is provided on the upper side, in the gravitational direction, of the evaporator (3), includes a second heat exchange passage (422) that condenses the working fluid having flowed in from the first condenser (41) by heat exchange with a second medium in the exterior, and causes the condensed working fluid to flow out toward the evaporator (3). The second heat exchange passage (422) of the second condenser (42) has a smaller flow path cross-sectional area or equivalent diameter relative to the first heat exchange passage (412) of the first condenser (41).

Description

Equipment temperature controller Cross-reference to related applications

This application is based on Japanese Patent Application No. 2016-176789 filed on September 9, 2016, the description of which is incorporated herein by reference.

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

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

In the device temperature control device described in Patent Literature 1, an evaporator provided on a side surface of a battery as a power storage device and a condenser provided above the evaporator are connected in an annular shape by two pipes, A refrigerant as a working fluid is enclosed in the inside. In this device temperature control device, when the battery generates heat, the liquid-phase refrigerant in the evaporator boils, and the battery is cooled by the latent heat of evaporation at that time. The gas-phase refrigerant generated by the evaporator flows through the gas-phase passage formed by one of the two pipes and flows into the condenser. In the condenser, the gas-phase refrigerant is condensed by heat exchange with a medium outside the condenser. The liquid phase refrigerant generated by the condenser flows by gravity through a liquid phase passage formed by the other pipe of the two pipes, and flows into the evaporator. The battery as the target device is cooled by such natural circulation of the refrigerant.

In addition, in this specification, an apparatus temperature control apparatus includes the whole apparatus which adjusts the temperature of an object apparatus by a thermosiphon system. That is, the device temperature control device includes both a device that only cools the target device, a device that performs only heating, and a device that performs both cooling and heating of the target device.

Japanese Patent Laying-Open No. 2015-041418

The device temperature control apparatus described in Patent Document 1 described above includes only one condenser. For this reason, when the heat generation amount of the battery increases, it is conceivable that the liquid phase refrigerant necessary for cooling the battery is not sufficiently supplied from the condenser to the evaporator. In addition, when the equipment temperature control device is provided with a plurality of condensers, a plurality of condensers are installed so that the refrigerant that has become a liquid phase in one condenser is not reheated in the other condenser. It is preferable to appropriately set the temperature of the environment to be used, the position where the plurality of condensers are arranged, the size of the flow paths of the plurality of condensers, and the like.

Moreover, the apparatus temperature control apparatus described in Patent Document 1 causes the liquid-phase refrigerant in the evaporator to boil due to the heat generated by the battery, and when the gas-phase refrigerant is generated as bubbles in the liquid-phase refrigerant, Some of the bubbles flow into the liquid phase passage and may reverse the flow of the liquid phase refrigerant due to buoyancy. If the bubbles enter the condenser and the generation of the liquid refrigerant in the condenser is hindered, the liquid refrigerant is not smoothly supplied from the condenser to the evaporator via the liquid passage, and the cooling capacity of the battery is reduced. There is concern about the decline.

This disclosure is intended to provide an apparatus temperature control device that can improve the cooling capacity by smoothing the flow of the working fluid.

According to one aspect of the present disclosure, the device temperature control device is a device temperature control device that adjusts the temperature of the target device, and includes an evaporator, a first condenser, and a second condenser. The evaporator cools the target device by latent heat of vaporization of the working fluid that absorbs heat from the target device and evaporates. The first condenser is provided above the evaporator in the direction of gravity, and has a first heat exchange passage that condenses the working fluid evaporated by the evaporator by heat exchange with the first medium outside. The second condenser is provided above the evaporator in the gravitational direction, and has a second heat exchange passage that condenses the working fluid flowing in from the first condenser by heat exchange with the second medium outside. The discharged working fluid flows out toward the evaporator. Here, the second heat exchange passage of the second condenser has a smaller cross-sectional area or equivalent diameter than the first heat exchange passage of the first condenser.

According to this, the second heat exchange passage has higher heat exchange efficiency than the first heat exchange passage, and the amount of liquid-phase working fluid generated is large. Further, the second heat exchange passage has a larger flow resistance than the first heat exchange passage. Therefore, when the liquid-phase working fluid is accumulated from the second heat exchange passage to the first heat exchange passage, the liquid-phase working fluid in the first heat exchange passage is self-weighted and the liquid-phase working fluid in the second heat exchange passage Is pushed to the evaporator side, so that the pressure of the liquid-phase working fluid from the first condenser and the second heat condenser toward the evaporator increases. Therefore, the back flow of the liquid-phase working fluid or the back flow of bubbles is suppressed from the evaporator side, and the working fluid flows smoothly in the forward direction.

Also, if the working fluid condensed in the first heat exchange passage is reheated in the second heat exchange passage and bubbles are generated, the bubbles enter the first heat exchange passage from the second heat exchange passage by buoyancy. It is possible. Also in this case, since the first heat exchange passage has a larger channel cross-sectional area or equivalent diameter than the second heat exchange passage, bubbles that have entered the first heat exchange passage from the second heat exchange passage It is quickly discharged from the passage to the upstream side. Therefore, the liquid-phase working fluid flows smoothly through the first heat exchange passage and the second heat exchange passage. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

In addition, the 2nd heat exchange channel | path which a 2nd condenser has should just have a flow-path cross-sectional area or an equivalent diameter smaller than the 1st heat exchange channel | path which a 1st condenser has at least in one part area | region.

According to another aspect, the first medium outside the first condenser and the second medium outside the second condenser are different media.

According to this, it is possible to set the first medium and the second medium at different temperatures. Therefore, for example, when the calorific value of the target device is large, use the medium having the lower temperature of the first medium and the second medium to increase the amount of liquid-phase working fluid generated, and sufficiently cool the target device. Is possible. On the other hand, when the calorific value of the target device is small, it is possible to cool the target device to an appropriate temperature using a medium having a relatively high temperature of the first medium and the second medium. Therefore, this device temperature control device can adjust the temperature according to the calorific value of the target device.

Moreover, according to another viewpoint, an apparatus temperature control apparatus is provided with an evaporator, a 1st condenser, a 2nd condenser, a 1st medium supply apparatus, and a 2nd medium supply apparatus. The first medium supply device supplies the first medium to the first condenser. The second medium supply device supplies the second medium to the second condenser. Here, the second medium supply device is configured to be able to set the second medium to a temperature lower than that of the first medium.

This prevents the working fluid condensed in the first heat exchange passage from being reheated in the second heat exchange passage. Therefore, since the generation of bubbles is suppressed in the second heat exchange passage, the deterioration of the flow of the liquid-phase working fluid due to the buoyancy of the bubbles is prevented. In addition, it is possible that the bubbles push up the liquid-phase working fluid and the liquid-phase working fluid is prevented from being blown up on the upper surface of the first or second heat exchange passage. It is suppressed. Further, since the generation of bubbles is suppressed in the second heat exchange passage, the liquid phase working fluid is smoothly generated in the first heat exchange passage and the second heat exchange passage, and the first heat exchange passage and the second heat exchange passage Liquid phase refrigerant is smoothly supplied from the heat exchange passage to the evaporator. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

It is a block diagram of the apparatus temperature control apparatus concerning 1st Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 1st Embodiment. It is a block diagram of the apparatus temperature control apparatus concerning 2nd Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 3rd Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 4th Embodiment. It is a block diagram of the apparatus temperature control apparatus concerning 5th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 5th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 6th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 7th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 8th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 9th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 10th Embodiment. It is the elements on larger scale of the apparatus temperature control apparatus concerning 11th Embodiment.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be described with the same reference numerals. In the drawings, when the same configuration is described in a plurality of places, only a part thereof is provided with a reference numeral.

(First embodiment)
A first embodiment will be described with reference to the drawings. The device temperature control device of the present embodiment cools an electrical device such as a power storage device or an electronic circuit mounted on an electric vehicle such as an electric vehicle or a hybrid vehicle, and adjusts the temperature of those target devices. In addition, in each drawing, the arrow which shows up and down shows the gravity direction up and down when the apparatus temperature control apparatus is mounted in a vehicle and the vehicle has stopped on the horizontal surface.

First, a target device whose temperature is adjusted by the device temperature control apparatus 1 of the present embodiment will be described.

As shown in FIG. 1, a target device whose temperature is adjusted by the device temperature adjustment device 1 of the present embodiment is an assembled battery 2 (hereinafter referred to as “battery”). Note that the target device may be a battery pack including the battery 2 and a power converter (not shown).

The battery 2 is used as a power source for vehicles that can be driven by an electric motor for traveling, such as an electric vehicle and a hybrid vehicle. The battery 2 is configured by a stacked body in which a plurality of rectangular parallelepiped battery cells 21 are stacked. The plurality of battery cells 21 constituting the battery 2 are electrically connected in series. The battery cell 21 is comprised by the secondary battery which can be charged / discharged, such as a lithium ion battery or a lead acid battery, for example. The battery cell 21 is not limited to a rectangular parallelepiped shape, and may have another shape such as a cylindrical shape. Moreover, the battery 2 may be comprised including the battery cell 21 electrically connected in parallel.

The battery 2 is connected to a power conversion device and a motor generator (not shown) included in the vehicle. The power conversion device is a device that converts, for example, a direct current supplied from the battery 2 into an alternating current, and discharges the converted alternating current to various electric loads such as a traveling electric motor. The motor generator is a device that reversely converts the traveling energy of the vehicle into electric energy during regenerative braking of the vehicle and supplies the reversely converted electric energy as regenerative power to the battery 2 via an inverter or the like.

The battery 2 may self-heat when power is supplied while the vehicle is running, and the battery 2 may become excessively hot. When the battery 2 becomes excessively high in temperature, deterioration of the battery cell 21 is promoted. Therefore, it is necessary to limit output and input so that self-heating is reduced. Therefore, in order to ensure the output and input of the battery cell 21, a cooling means for maintaining the temperature below a predetermined temperature is required.

Also, the power storage device including the battery 2 is often arranged under the floor of the vehicle or under the trunk room. Therefore, the temperature of the battery 2 gradually rises not only when the vehicle is running but also during parking in the summer, and the battery 2 may become excessively hot. If the battery 2 is left in a high temperature environment, the battery 2 will deteriorate and its life will be greatly reduced. Therefore, it is desirable to keep the temperature of the battery 2 below a predetermined temperature even during parking of the vehicle. It is rare.

Furthermore, since the battery 2 includes a structure in which the battery cells 21 are electrically connected in series, the input / output characteristics of the entire battery are determined according to the battery cell 21 that has undergone the most deterioration among the battery cells 21. . Therefore, if the temperature of each battery cell 21 varies, the degree of progress of the deterioration of each battery cell 21 is biased, and the input / output characteristics of the entire battery are degraded. For this reason, in order for the battery 2 to exhibit desired performance for a long period of time, it is important to equalize the temperature so as to reduce the temperature variation of each battery cell 21.

Generally, as a cooling means for cooling the battery 2, an air-cooling cooling means using a blower, a cooling means using cooling water, or a cooling means using a vapor compression refrigeration cycle is employed.

However, since the air-cooled cooling means using the blower only blows air inside or outside the vehicle to the battery 2, a cooling capacity sufficient to sufficiently cool the battery 2 may not be obtained. In addition, the cooling means using air cooling and cooling water may cause variations in the cooling temperature of the battery cell 21 on the upstream side of the flow of air or cooling water and the cooling temperature of the battery cell 21 on the downstream side.

Moreover, although the cooling means using the cold heat of the refrigeration cycle has a high cooling capacity of the battery 2, it is necessary to drive a compressor or the like that consumes a large amount of power while the vehicle is parked. This leads to an increase in power consumption and noise.

Therefore, the apparatus temperature control device 1 of the present embodiment employs a thermosiphon system in which the temperature of the battery 2 is adjusted by natural circulation of the refrigerant, instead of forcibly circulating the refrigerant as the working fluid by the compressor.

Next, the configuration of the device temperature control device 1 will be described.

As shown in FIG. 1, the device temperature control device 1 includes an evaporator 3, a first condenser 41, a second condenser 42, a gas phase passage 5, a liquid phase passage 6, and the like, and these constituent members are connected to each other. As a result, a loop-type thermosiphon is configured. The apparatus temperature control device 1 is filled with a predetermined amount of refrigerant in a state where the inside thereof is evacuated. Various refrigerants such as R134a, R1234yf, carbon dioxide, or water can be employed as the refrigerant. As indicated by the one-dot chain lines S1 and S2 in FIG. 1, the amount of the refrigerant is the state before the cooling of the battery 2 is started, and the liquid upper surface of the liquid phase refrigerant It is preferable that it is in the middle. In addition, when a refrigerant | coolant circulates in the direction of the arrow of the broken line of FIG. 1, the liquid upper surface of a liquid phase refrigerant will change according to it.

The evaporator 3 is a sealed case, is formed in a flat shape, and is provided at a position facing the lower surface of the battery 2. The evaporator 3 is preferably formed of a material having excellent thermal conductivity such as aluminum or copper. The evaporator 3 only needs to be provided so as to be able to transfer heat to the plurality of battery cells 21, and may be provided at a position facing the side surface or the upper surface of the battery 2, for example. Further, the shape and size of the evaporator 3 can be arbitrarily set according to the space mounted on the vehicle.

The evaporator 3 has a fluid chamber 30 inside. It is preferable that the fluid chamber 30 is filled with a liquid-phase refrigerant before the battery 2 starts cooling. In practice, a liquid phase refrigerant and a gas phase refrigerant may be included. When the battery 2 self-heats due to power storage or discharge, heat is transferred from the battery 2 to the evaporator 3, and the liquid phase refrigerant in the fluid chamber 30 absorbs the heat and evaporates. At that time, evaporation of the liquid-phase refrigerant occurs in the entire fluid chamber 30, and the plurality of battery cells 21 are cooled substantially uniformly by the latent heat of evaporation. Therefore, the evaporator 3 can reduce the temperature variation between the plurality of battery cells 21 to equalize and cool the plurality of battery cells 21.

As described above, the battery 2 cannot obtain a sufficient function at a high temperature, and may be deteriorated or damaged. In the battery 2, the input / output characteristics of the entire battery are determined in accordance with the characteristics of the battery cell 21 that is most deteriorated. Therefore, the evaporator 3 can make the battery 2 exhibit desired performance for a long period of time by equalizing and cooling the plurality of battery cells 21 by cooling using latent heat of evaporation. .

The vapor phase passage 5 and the liquid phase passage 6 are connected to the evaporator 3. A location where the evaporator 3 and the liquid phase passage 6 are connected is referred to as a first opening 31, and a location where the evaporator 3 and the gas phase passage 5 are connected is referred to as a second opening 32. In the evaporator 3, it is preferable that the 1st opening part 31 and the 2nd opening part 32 are separated. Thereby, when the refrigerant circulates through the thermosiphon, a flow of the refrigerant from the first opening 31 toward the second opening 32 is formed in the evaporator 3. In FIG. 1, both the first opening 31 and the second opening 32 are provided on the side surface of the evaporator 3, but the positions of the first opening 31 and the second opening 32 are not limited to the side surfaces. The upper surface or the lower surface may be used.

Both the first condenser 41 and the second condenser 42 are provided above the evaporator 3 in the gravity direction. In the first embodiment, the entire region of the first condenser 41 is disposed above the second condenser 42 in the gravity direction.

The vapor phase passage 5 connects the evaporator 3 and the first condenser 41. The gas phase passage 5 has one end connected to the second opening 32 of the evaporator 3 and the other end connected to the first condenser 41. The gas phase passage 5 can flow the gas phase refrigerant evaporated in the evaporator 3 to the first condenser 41. The gas-phase passage 5 mainly flows through the gas-phase refrigerant, but a gas-liquid two-phase refrigerant or a liquid-phase refrigerant may flow therethrough.

The first condenser 41 has a function of condensing the refrigerant flowing through the internal flow path by heat exchange with a medium (not shown) outside the first condenser 41. In the following description, a medium outside the first condenser 41 is referred to as a first medium. A connection passage 43 connects the first condenser 41 and the second condenser 42. The liquid phase refrigerant condensed in the first condenser 41 passes through the connection passage 43 and flows into the second condenser 42. The second condenser 42 also has a function of condensing the refrigerant flowing in the internal flow path by heat exchange with a medium (not shown) outside the second condenser 42. In the following description, a medium outside the second condenser 42 is referred to as a second medium. In the first to fifth embodiments, the first medium and the second medium may be the same type of media or different types of media.

The liquid phase passage 6 connects the second condenser and the evaporator 3. The liquid phase passage 6 has one end connected to the second condenser 42 and the other end connected to the first opening 31 of the evaporator 3. The liquid phase passage 6 can flow the liquid phase refrigerant condensed by the first condenser 41 and the second condenser 42 to the evaporator 3 by gravity. In addition, although the liquid phase passage 6 mainly flows through the liquid phase refrigerant, a gas-liquid two-phase refrigerant or a gas phase refrigerant may flow therethrough.

Subsequently, the first condenser 41 and the second condenser 42 will be described in detail.

2, the first condenser 41 includes a first upper tank 411, a plurality of first heat exchange tubes 412, a first lower tank 413, and the like. The first condenser 41 is preferably formed of a material having excellent thermal conductivity such as aluminum or copper. The shape and size of the first condenser 41 can be arbitrarily set according to the space mounted on the vehicle.

The first heat exchange tube 412 corresponds to a first heat exchange passage that condenses the gas-phase refrigerant by heat exchange with an external first medium. A plurality of fins 414 are provided outside the first heat exchange tube 412. The multiple first heat exchange tubes 412 extend along the direction of gravity. Thereby, a liquid phase refrigerant flows along the direction of gravity inside the plurality of first heat exchange tubes 412.

The vapor phase refrigerant supplied from the vapor phase passage 5 to the first upper tank 411 flows into the first heat exchange tubes 412 from the first upper tank 411. The gas-phase refrigerant is condensed by heat exchange with the first medium outside the first condenser 41 when flowing through the plurality of first heat exchange tubes 412. The liquid refrigerant generated in the plurality of first heat exchange tubes 412 flows into the first lower tank 413 due to its own weight.

The second condenser 42 also includes a second upper tank 421, a plurality of second heat exchange tubes 422, a second lower tank 423, and the like. The second condenser 42 is also preferably formed of a material having excellent thermal conductivity such as aluminum or copper. The shape and size of the second condenser 42 can be arbitrarily set according to the space mounted on the vehicle.

The second heat exchange tube 422 corresponds to a second heat exchange passage that condenses the gas-phase refrigerant by heat exchange with an external second medium. A plurality of fins 424 are provided outside the second heat exchange tube 422. The multiple second heat exchange tubes 422 extend along the direction of gravity. Thereby, a liquid phase refrigerant flows along the direction of gravity inside the plurality of second heat exchange tubes 422.

A connection passage 43 connects the first lower tank 413 of the first condenser 41 and the second upper tank 421 of the second condenser 42. The liquid refrigerant that has passed through the first condenser 41 passes through the connection passage 43 and flows into the second upper tank 421 of the second condenser 42. A part of the gas-phase refrigerant included in the flow of the liquid-phase refrigerant also flows into the second upper tank 421. The refrigerant supplied from the connection passage 43 to the second upper tank 421 of the second condenser 42 flows from the second upper tank 421 into the plurality of second heat exchange tubes 422. The gas phase refrigerant in the refrigerant is condensed by heat exchange with the second medium outside the second condenser 42 when flowing through the plurality of second heat exchange tubes 422. The liquid refrigerant generated in the plurality of second heat exchange tubes 422 flows into the second lower tank 423 by its own weight.

Here, the flow path cross-sectional area of the first heat exchange tube 412 included in the first condenser 41 is S1, and the flow path cross-sectional area of the second heat exchange tube 422 included in the second condenser 42 is S2. The number of first heat exchange tubes 412 included in the first condenser 41 is N1, and the number of second heat exchange tubes 422 included in the second condenser 42 is N2. The equivalent diameter of the first heat exchange tube 412 included in the first condenser 41 is D1, and the equivalent diameter of the second heat exchange tube 422 included in the second condenser 42 is D2.

At this time, the first condenser 41 and the second condenser 42 have the following relationship.

S1> S2 (Formula 1)
S1 × N1> S2 × N2 (Formula 2)
D1> D2 (Formula 3)
That is, as shown in the above formulas 1 and 3, the second heat exchange tube 422 included in the second condenser 42 has a flow path cross-sectional area or a larger area than the first heat exchange tube 412 included in the first condenser 41. It has a region with a small equivalent diameter.

Further, as shown in Equation 2 above, the total cross-sectional area of the plurality of first heat exchange tubes 412 combined with the cross-sectional area of the plurality of first heat exchange tubes 412 is the same as the cross-sectional area of the plurality of second heat exchange tubes 422. It is larger than the total channel cross-sectional area.

The apparatus temperature control apparatus 1 of 1st Embodiment has the following effect by providing the structure mentioned above.

(1) Since the second heat exchange tube 422 has a smaller channel cross-sectional area or equivalent diameter than the first heat exchange tube 412, as shown in the above formulas 1 and 3, the heat exchange efficiency is high. For this reason, the second heat exchange tube 422 generates more liquid refrigerant than the first heat exchange tube 412.

Further, as shown in Equation 2 above, the total flow path cross-sectional area (S1 × N1) of the flow path cross-sectional areas S1 of the plurality of first heat exchange tubes 412 is the sum of the plurality of second heat exchange tubes 422. It is larger than the total channel cross-sectional area (S2 × N2) including the channel cross-sectional area S2. Therefore, the second heat exchange tube 422 has a larger flow path resistance than the first heat exchange tube 412.

As a result, when the liquid refrigerant accumulates from the second heat exchange tube 422 to the first heat exchange tube 412, the liquid phase medium in the first heat exchange tube 412 is self-weighted to cause the liquid phase medium in the second heat exchange tube 422 to flow. Press to the evaporator 3 side. Therefore, the pressure of the liquid-phase refrigerant toward the evaporator 3 from the first condenser 41 and the second condenser 42 increases. Therefore, the backflow of the liquid phase refrigerant or the backflow of bubbles is suppressed from the evaporator 3 side, and the refrigerant flows smoothly in the forward direction. Therefore, this apparatus temperature control apparatus 1 can improve the cooling capacity of the battery 2.

In addition, if the refrigerant condensed in the first heat exchange tube 412 is reheated in the second heat exchange tube 422 to generate bubbles, the bubbles are buoyant and the bubbles are transferred from the second heat exchange tube 422 to the first heat exchange tube 412. It is possible to intrude into. Also in this case, since the first heat exchange tube 412 has a larger channel cross-sectional area or equivalent diameter than the second heat exchange tube 422, the bubbles that have entered the first heat exchange tube 412 from the second heat exchange tube 422 1 The heat exchange tube 412 is quickly discharged upstream. Therefore, the liquid refrigerant flows smoothly through the first heat exchange tube 412 and the second heat exchange tube 422. Therefore, the device temperature control device 1 can improve the cooling capacity of the battery 2.

(2) The apparatus temperature control apparatus 1 of the first embodiment has a region where the first condenser 41 is located above the second condenser 42 in the gravity direction.

According to this, the liquid phase refrigerant generated in the first condenser 41 flows from the first condenser 41 to the second condenser 42 by its own weight. Therefore, since the liquid phase refrigerant smoothly flows from the first condenser 41 to the evaporator 3 via the second condenser 42, the back flow of the liquid phase refrigerant or the back flow of bubbles from the evaporator 3 side is suppressed. Therefore, the device temperature control device 1 can improve the cooling capacity of the battery 2.

(3) The apparatus temperature control device 1 of the first embodiment includes a plurality of first heat exchange tubes 412 included in the first condenser 41 and a plurality of second heat exchange tubes 422 included in the second condenser 42. , Extending along the direction of gravity.

According to this, the first heat exchange tube 412 and the second heat exchange tube 422 can smoothly flow the liquid-phase refrigerant downward in the gravity direction by its own weight. Therefore, the device temperature control device 1 can improve the cooling capacity of the battery 2.

(Second Embodiment)
A second embodiment will be described. The second embodiment is obtained by changing the arrangement of the first condenser 41 or the second condenser 42 with respect to the first embodiment, and is otherwise the same as the first embodiment, and therefore the first embodiment. Only different parts will be described.

As shown in FIG. 3, in the second embodiment, at least a part of the first condenser 41 is located above the second condenser 42 in the gravity direction. In FIG. 3, a region where the first condenser 41 is located above the second condenser 42 in the gravity direction is indicated by an arrow α.

According to this, the liquid refrigerant generated in the first condenser 41 flows from the first condenser 41 to the second condenser 42 by its own weight. Therefore, since the liquid phase refrigerant smoothly flows in the forward direction from the first condenser 41 to the evaporator 3 via the second condenser 42, the reverse flow of the liquid phase refrigerant or the reverse flow of the bubbles is caused from the evaporator 3 side. It is suppressed. Therefore, the device temperature control device 1 can improve the cooling capacity of the battery 2.

(Third embodiment)
A third embodiment will be described. In the third embodiment, the arrangement of the second condenser 42 is changed with respect to the first embodiment, and the others are the same as those in the first embodiment. Therefore, only the parts different from the first embodiment will be described. To do.

As shown in FIG. 4, in the third embodiment, the plurality of second heat exchange tubes 422 included in the second condenser 42 extend in a direction intersecting the direction of gravity. In addition, the 2nd upper tank 421 and the 2nd lower tank 423 which the 2nd condenser 42 has extended along the gravity direction.

On the other hand, the multiple first heat exchange tubes 412 included in the first condenser 41 extend along the direction of gravity. Thereby, the force by which the liquid refrigerant flows along the direction of gravity inside the plurality of first heat exchange tubes 412 increases.

In the third embodiment, the liquid refrigerant generated in the plurality of first heat exchange tubes 412 of the first condenser 41 has a greater force flowing along the direction of gravity due to its own weight, and is connected from the first lower tank 413. It flows to the second condenser 42 via the passage 43. In the second condenser 42, the liquid phase refrigerant generated in the plurality of second heat exchange tubes 422 flows into the second upper tank 421 or the second lower tank 423, and then passes through the liquid phase passage 6 to the evaporator. 3 flows smoothly. Thereby, the backflow of a liquid phase refrigerant | coolant or the backflow of a bubble is suppressed from the evaporator 3 side. Therefore, in the apparatus temperature adjustment device 1 of the third embodiment, at least one of the plurality of first heat exchange tubes 412 of the first condenser 41 or the plurality of second heat exchange tubes 422 of the second condenser 42 is gravity. By extending along the direction, the cooling capacity of the battery 2 can be improved.

(Fourth embodiment)
A fourth embodiment will be described. In the fourth embodiment, the arrangement of the first condenser 41 is changed with respect to the first embodiment, and the other parts are the same as those in the first embodiment. Therefore, only the parts different from the first embodiment will be described. To do.

As shown in FIG. 5, in the fourth embodiment, the plurality of first heat exchange tubes 412 included in the first condenser 41 extend in a direction crossing the gravity direction. Note that the first upper tank 411 and the first lower tank 413 of the first condenser 41 extend along the direction of gravity.

On the other hand, the plurality of second heat exchange tubes 422 included in the second condenser 42 extend along the direction of gravity. Thereby, the force by which the liquid refrigerant flows along the direction of gravity inside the plurality of second heat exchange tubes 422 increases.

Also in the fourth embodiment, the liquid-phase refrigerant generated by the plurality of first heat exchange tubes 412 included in the first condenser 41 flows from the first upper tank 411 to the first lower tank 413 and then passes through the connection passage 43. Via the second condenser 42. The liquid refrigerant generated in the plurality of second heat exchange tubes 422 included in the second condenser 42 has a larger force flowing along the direction of gravity due to its own weight, and passes through the liquid phase passage 6 from the second condenser 42. And flows smoothly into the evaporator 3. Thereby, the backflow of a liquid phase refrigerant | coolant or the backflow of a bubble is suppressed from the evaporator 3 side. Therefore, in the device temperature control apparatus 1 of the fourth embodiment, at least one of the plurality of first heat exchange tubes 412 of the first condenser 41 or the plurality of second heat exchange tubes 422 of the second condenser 42 is gravity. By extending along the direction, the cooling capacity of the battery 2 can be improved.

(Fifth embodiment)
A fifth embodiment will be described. 5th Embodiment changes the structure of the 1st condenser 41 and the 2nd condenser 42 with respect to 1st Embodiment, Since it is the same as that of 1st Embodiment about others, 1st Embodiment Only different parts will be described.

As shown in FIG. 6, in the fifth embodiment, the first condenser 41 and the second condenser 42 are integrally formed. Specifically, as shown in FIG. 7, the first lower tank 413 of the first condenser 41 and the second upper tank 421 of the second condenser 42 are configured integrally in a continuous manner. A plate-like separator 44 is provided between the first lower tank 413 of the first condenser 41 and the second upper tank 421 of the second condenser 42. A hole 45 is provided in a part of the separator 44. Through this hole 45, the refrigerant flows between the first lower tank 413 of the first condenser 41 and the second upper tank 421 of the second condenser 42.

In the fifth embodiment, the first condenser 41 and the second condenser 42 are integrally configured to reduce the size of the first condenser 41 and to connect the first condenser 41 and the second condenser 42. The passage 43 can be abolished, and the fear of heating or heat radiation by the connection passage 43 can be eliminated.

Further, by integrally configuring the first lower tank 413 and the second upper tank 421, the number of parts can be reduced, the configuration can be simplified, and the manufacturing cost can be reduced.

(Sixth embodiment)
A sixth embodiment will be described. The plurality of embodiments to be described below describe the first medium and the second medium outside the first condenser 41 and the second condenser 42, respectively, with respect to the first to fifth embodiments described above. It is. In addition, in each drawing referred in the several embodiment demonstrated below, illustration of the evaporator 3 and its periphery structure is abbreviate | omitted.

As shown in FIG. 8, the device temperature adjustment device 1 of the sixth embodiment includes a first blower 71 as an example of the first medium supply device 100, and a second blower 72 as an example of the second medium supply device 200. It has. The first blower 71 supplies air as the first medium to the first condenser 41. The second blower 72 also supplies air as the second medium to the second condenser 42.

The first blower 71 supplies vehicle exterior air to the first condenser 41 as a first medium at least in summer. The vehicle exterior air flows outside the first condenser 41 and exchanges heat with the refrigerant flowing through the first condenser 41. On the other hand, the second blower 72 supplies vehicle interior air to the second condenser 42 as the second medium at least in summer. The vehicle interior air flows outside the second condenser 42 and exchanges heat with the refrigerant flowing through the second condenser 42.

Generally, at least when the vehicle travels in summer, the air in the vehicle interior is set at a lower temperature than the air outside the vehicle interior by the air conditioner. For this reason, the air in the passenger compartment as the second medium is at a lower temperature than the air outside the passenger compartment as the first medium. Therefore, the refrigerant condensed by the first condenser 41 can be prevented from being reheated by the second condenser 42. For this reason, since the generation of bubbles in the second condenser 42 is suppressed, the deterioration of the flow of the liquid-phase refrigerant due to the buoyancy of the bubbles is prevented. In addition, it is possible that the bubbles push up the liquid-phase refrigerant and the liquid-phase refrigerant is prevented from being blown up on the liquid upper surface of the first condenser 41 or the second condenser 42, and the bubbles burst there and generate abnormal noise. It is suppressed. Further, since the generation of bubbles in the second condenser 42 is suppressed, the liquid refrigerant is smoothly generated in the first condenser 41 and the second condenser 42, and the first condenser 41 and the second condenser 42 are generated. The liquid refrigerant is smoothly supplied from the two condenser 42 to the evaporator 3. Therefore, the device temperature control device 1 can improve the cooling capacity of the battery 2.

(Seventh embodiment)
A seventh embodiment will be described. As shown in FIG. 9, the device temperature adjustment device 1 of the seventh embodiment includes a first blower 71 and a first cold heat supply device 101 as an example of the first medium supply device 100. Moreover, the apparatus temperature control apparatus 1 is provided with the 2nd air blower 72 and the 2nd cold heat supply device 201 as an example of the 2nd medium supply apparatus 200. As shown in FIG. The 1st cold heat supply device 101 and the 2nd cold heat supply device 201 are comprised by the low pressure side heat exchanger which comprises a refrigerating cycle, or the heat exchanger which comprises the circulating cycle of cooling water, etc., for example.

The first medium supply device 100 generates an air flow by the first blower 71 and causes the air that has passed through the first cold heat supply device 101 to flow to the first condenser 41 as the first medium. Thereby, the refrigerant | coolant which flows through the 1st condenser 41 is cooled. The first medium supply device 100 can adjust the temperature of the air as the first medium by adjusting the temperature of the first cold heat supply device 101.

The second medium supply device 200 generates an air flow by the second blower 72 and causes the air that has passed through the second cold heat supply device 201 to flow to the second condenser 42 as the second medium. Thereby, the refrigerant | coolant which flows through the 2nd condenser 42 is cooled. The second medium supply device 200 can also adjust the temperature of the air as the second medium by adjusting the temperature of the second cold heat supply device 201.

The first medium supply device 100 and the second medium supply device 200 cool the refrigerant flowing through the second condenser 42 by lowering the temperature of the air as the second medium than the temperature of the air as the first medium. Is possible. Therefore, the seventh embodiment can also prevent the refrigerant condensed by the first condenser 41 from being reheated by the second condenser 42. In the seventh embodiment, the first medium and the second medium can be adjusted to desired temperatures.

(Eighth embodiment)
An eighth embodiment will be described. As illustrated in FIG. 10, the device temperature adjustment device 1 according to the eighth embodiment includes a first blower 71 as an example of the first medium supply device 100. The first blower 71 supplies air as the first medium to the first condenser 41. The air flows outside the first condenser 41 and exchanges heat with the refrigerant flowing through the first condenser 41.

Moreover, the apparatus temperature control apparatus 1 is provided with the 2nd cold heat supply device 201 as an example of the 2nd medium supply apparatus 200. FIG. The 2nd cold heat supply device 201 is comprised by the low pressure side heat exchanger which comprises a refrigerating cycle, or the heat exchanger which comprises the circulation cycle through which cooling water flows, for example. When the second cold heat supply device 201 is a low-pressure side heat exchanger constituting the refrigeration cycle, the second cold heat supply device 201 supplies the second condenser 42 with the cold heat of the refrigerant circulating in the refrigeration cycle as the second medium. On the other hand, when the 2nd cold heat supply device 201 is a heat exchanger which comprises the circulation cycle of a cooling water, the 2nd cold heat supply device 201 supplies the cold heat of a cooling water to the 2nd condenser 42 as a 2nd medium. The refrigerant flowing through the second condenser 42 is cooled by heat conduction from the refrigerant or cooling water as the second medium. The second cold heat supply device 201 can adjust the amount of cold heat supplied to the refrigerant flowing through the second condenser 42 by adjusting the output of the refrigeration cycle or the cooling water circulation cycle.

In 8th Embodiment, the 1st medium supply apparatus 100 and the 2nd medium supply apparatus 200 are the refrigerant | coolant or cooling water as a 2nd medium from the cold heat amount supplied to the 1st condenser 41 from the air as a 1st medium. It is possible to increase the amount of cold supplied to the second condenser 42. Thereby, the refrigerant flowing through the second condenser 42 is cooled more than the refrigerant flowing through the first condenser 41. Therefore, also in the eighth embodiment, the refrigerant condensed by the first condenser 41 can be prevented from being reheated by the second condenser 42.

In the eighth embodiment, the first medium and the second medium are different types of media. According to this, it is possible to easily set the first medium and the second medium at different temperatures. Therefore, for example, when the amount of heat generated by the battery 2 is large, such as when the vehicle is traveling at high speed, it is possible to sufficiently cool the battery 2 using a low-temperature refrigerant or cooling water as the second medium. On the other hand, when the heat generation amount of the battery 2 is small, for example, when the vehicle is traveling in the city, the battery 2 is cooled to an appropriate temperature by using air having a relatively higher temperature than the second medium as the first medium. Is possible. Therefore, the device temperature control device 1 can adjust the temperature according to the amount of heat generated by the battery 2.

In the eighth embodiment, the first medium supply device 100 is a blower 71. The second medium supply device 200 is a low-pressure side heat exchanger constituting a refrigeration cycle or a heat exchanger constituting a circulation cycle through which cooling water flows.

According to this, when the heat generation amount of the battery 2 is small, for example, when the vehicle travels in the city, the battery 2 is used compared to driving the refrigeration cycle or the like by using the blower as the first medium supply device 100. It is possible to reduce the power consumption required for cooling.

On the other hand, the second medium supply device 200 can set the temperature of the refrigerant or cooling water of the refrigeration cycle as the second medium to be lower than the temperature of the air as the first medium. For example, when the amount of heat generated by the battery 2 is large, such as when the vehicle is traveling at high speed, the battery 2 can be sufficiently cooled by using a refrigeration cycle or the like as the second medium supply device 200. Therefore, the device temperature adjustment device 1 can reduce the power consumption required for cooling the battery 2 and can adjust the temperature according to the amount of heat generated by the battery 2.

(Ninth embodiment)
A ninth embodiment will be described. As shown in FIG. 11, the device temperature adjustment device 1 of the ninth embodiment includes a cooling water circulation cycle 8 as an example of the first medium supply device 100. Specifically, the cooling water circulation cycle 8 includes a first medium circulation circuit 111 in which a pump 81, a blower 82, an air cooling radiator 83, a heat exchanger 84, and the like are connected in a ring shape by a pipe 85, and the cooling water circulates. It is a thing.

The pump 81 circulates cooling water through the pipe 85. The blower 82 causes an air flow to flow to the air cooling radiator 83. Thereby, the cooling water flowing inside the air-cooling radiator 83 is cooled. The heat exchanger 84 corresponds to the first cold heat supply device 101. The cooling water flowing through the heat exchanger 84 exchanges heat with the refrigerant flowing through the first condenser 41 and cools the refrigerant flowing through the second condenser 42. The cooling water absorbed by the heat exchanger 84 flows to the air cooling radiator 83.

In addition, the device temperature adjustment device 1 includes a refrigeration cycle 9 as an example of the second medium supply device 200. Specifically, the refrigeration cycle 9 includes a compressor 91, a high-pressure side heat exchanger 92, an expansion valve 93, a low-pressure side heat exchanger 94, and the like that are annularly connected by a pipe 95 to circulate the refrigerant. Is configured. The first medium circulation circuit 111 and the second medium circulation circuit 211 described above are separate and independent.

Note that the refrigerant used in the refrigeration cycle 9 may be the same as or different from the refrigerant as the working fluid used in the device temperature control apparatus 1.

The compressor 91 sucks and compresses the refrigerant from the low-pressure side heat exchanger 94 side. The compressor 91 is driven by power transmitted from a traveling engine or an electric motor of the vehicle (not shown).

The high-pressure gas-phase refrigerant discharged from the compressor 91 flows into the high-pressure side heat exchanger 92. When the high-pressure gas-phase refrigerant flowing into the high-pressure side heat exchanger 92 flows through the flow path of the high-pressure side heat exchanger 92, the high-pressure gas-phase refrigerant is cooled and condensed by heat exchange with outside air by a blower (not shown).

The liquid-phase refrigerant condensed in the high-pressure side heat exchanger 92 is depressurized when passing through the expansion valve 93, becomes a mist-like gas-liquid two-phase state, and flows into the low-pressure side heat exchanger 94. The expansion valve 93 is configured by a fixed throttle such as an orifice or a nozzle, or an appropriate variable throttle. The low-pressure side heat exchanger 94 corresponds to the second cold heat supply device 201. The low pressure side heat exchanger 94 cools the refrigerant flowing through the second condenser 42 by the evaporation heat of the refrigerant flowing through the inside. The refrigerant that has passed through the low-pressure side heat exchanger 94 is sucked into the compressor 91 via an accumulator (not shown).

The second medium supply device 200 is configured so that the refrigerant flowing through the second condenser 42 is more than the amount of cold supplied to the refrigerant flowing through the first condenser 41 by adjusting the output of the cooling water circulation cycle 8 or adjusting the output of the refrigeration cycle 9. It is possible to increase the amount of cooling heat supplied to. Thereby, the refrigerant flowing through the second condenser 42 is cooled more than the refrigerant flowing through the first condenser 41. Therefore, also in the ninth embodiment, the refrigerant condensed by the first condenser 41 can be prevented from being reheated by the second condenser 42.

In the ninth embodiment, the cooling water as the first medium and the refrigerant of the refrigeration cycle 9 as the second medium are different media. According to this, it is possible to easily set the temperatures of the first medium and the second medium to different temperatures. Therefore, the device temperature control device 1 can adjust the temperature according to the amount of heat generated by the battery 2.

Furthermore, in the ninth embodiment, the first medium circulation circuit 111 for circulating the cooling water as the first medium and the second medium circulation circuit 211 for circulating the refrigerant as the second medium are separate and independent circuits. According to this, it is possible to prevent the temperature of the first medium and the temperature of the second medium from affecting each other. Therefore, the amount of cold supplied to the refrigerant flowing through the first condenser 41 by the first medium supply device 100 is appropriately adjusted, and the amount of cold supplied to the refrigerant flowing through the second condenser 42 by the second medium supply device 200. Can be adjusted appropriately.

(10th Embodiment)
A tenth embodiment will be described. As shown in FIG. 12, in the tenth embodiment, the first medium supply device 100 and the second medium supply device 200 included in the device temperature adjustment device 1 are configured by the same refrigeration cycle 9. In this refrigeration cycle 9, a first low-pressure side heat exchanger 941 corresponding to the first cold heat supply device 101 and a second low-pressure side heat exchanger 942 corresponding to the second cold heat supply device 201 are connected in parallel. Yes.

Specifically, the refrigeration cycle 9 includes a compressor 91, a high pressure side heat exchanger 92, a first flow rate adjustment valve 961, a first expansion valve 931, a first low pressure side heat exchanger 941, a second flow rate adjustment valve 962, The second expansion valve 932 and the second low-pressure side heat exchanger 942 are connected in a ring shape by a pipe 95 to constitute a circulation circuit in which the refrigerant circulates.

The compressor 91 and the high pressure side heat exchanger 92 are substantially the same as those described in the ninth embodiment.

The liquid-phase refrigerant condensed in the high-pressure side heat exchanger 92 flows separately through the branched pipes 951 and 952 to the first low-pressure side heat exchanger 941 side and the second low-pressure side heat exchanger 942 side. A pipe 951 on the first low pressure side heat exchanger 941 side is provided with a first flow rate adjustment valve 961 for adjusting the flow rate of the refrigerant. The liquid-phase refrigerant that has passed through the first flow rate adjustment valve 961 is reduced in pressure when passing through the first expansion valve 931, becomes a mist-like gas-liquid two-phase state, and flows into the first low-pressure side heat exchanger 941. The first low-pressure side heat exchanger 941 corresponds to the first cold heat supply device 101.

The first low-pressure side heat exchanger 941 is provided so as to be able to exchange heat with the refrigerant flowing through the first condenser 41 of the device temperature control device 1. The low-pressure refrigerant flowing through the flow path of the first low-pressure side heat exchanger 941 absorbs heat from the refrigerant flowing through the first condenser 41 of the device temperature control device 1 and evaporates. The refrigerant flowing through the first condenser 41 of the device temperature control apparatus 1 is cooled and condensed by the latent heat of vaporization of the low-pressure refrigerant flowing through the flow path of the first low-pressure side heat exchanger 941. The refrigerant that has passed through the first low-pressure side heat exchanger 941 is sucked into the compressor 91 via an accumulator (not shown).

Meanwhile, a second flow rate adjusting valve 962 for adjusting the flow rate of the refrigerant is also provided in the pipe 952 on the second low pressure side heat exchanger 942 side. The liquid-phase refrigerant that has passed through the second flow rate adjustment valve 962 is depressurized when passing through the second expansion valve 932, enters a second gas-liquid two-phase state, and flows into the second low-pressure side heat exchanger 942. The second low-pressure side heat exchanger 942 corresponds to the second cold heat supply device 201. The second low-pressure side heat exchanger 942 is provided so as to be able to exchange heat with the refrigerant flowing through the second condenser 42 of the device temperature control device 1. The low-pressure refrigerant flowing through the flow path of the second low-pressure side heat exchanger 942 absorbs heat from the refrigerant flowing through the second condenser 42 of the device temperature control device 1 and evaporates. The refrigerant flowing through the second condenser 42 of the device temperature control apparatus 1 is cooled and condensed by the latent heat of vaporization of the low-pressure refrigerant flowing through the flow path of the second low-pressure side heat exchanger 942. The refrigerant that has passed through the second low-pressure side heat exchanger 942 is also sucked into the compressor 91 via an accumulator (not shown).

In the tenth embodiment, the first flow rate adjustment valve 961 and the second flow rate adjustment valve 962 included in the refrigeration cycle 9 are used to change the amount of cold supplied to the refrigerant flowing through the first condenser 41 and the refrigerant flowing through the second condenser 42. It is possible to adjust the amount of cold supplied. The flow rate adjustment of the first flow rate adjustment valve 961 and the second flow rate adjustment valve 962 is performed by adjusting the on / off time. By adjusting the output of the refrigeration cycle 9 as described above, the amount of cold supplied to the refrigerant flowing through the second condenser 42 can be made larger than the amount of cold supplied to the refrigerant flowing through the first condenser 41. Thereby, the refrigerant flowing through the second condenser 42 is cooled more than the refrigerant flowing through the first condenser 41. Therefore, also in the tenth embodiment, the refrigerant condensed by the first condenser 41 can be prevented from being reheated by the second condenser 42.

In the tenth embodiment, the first and second low-pressure heat exchangers 941 and 942 constituting the refrigeration cycle 9 are used as the first and second cold heat supply devices 101 and 201, respectively. It is possible to increase the refrigerant condensing capacity of both 41 and the second condenser 42. Further, by using the first and second low-pressure heat exchangers 941 and 942 of the refrigeration cycle 9 of the air conditioner mounted on the vehicle as the first and second cold heat supply devices 101 and 201, respectively, the device temperature control is performed. The configuration of the device 1 can be simplified.

(Eleventh embodiment)
An eleventh embodiment will be described. As shown in FIG. 13, the eleventh embodiment is a modification of the eighth embodiment.

The apparatus temperature control apparatus 1 of 11th Embodiment is provided with the 1st air blower 71 as an example of the 1st medium supply apparatus 100. FIG. Moreover, the apparatus temperature control apparatus 1 is equipped with what is called a secondary loop structure by the circulating cycle 8 and the refrigerating cycle 9 of a cooling water as an example of the 2nd medium supply apparatus 200. FIG. The heat exchanger 84 constituting the cooling water circulation cycle 8 corresponds to the second cold heat supply device 201.

The cooling water circulation cycle 8 has a pump 81, a heat exchanger 84, a radiator 83, and the like connected in a ring shape by a pipe 85. The radiator 83 of the cooling water circulation cycle 8 is configured to be able to exchange heat with the low-pressure heat exchanger 94 constituting the refrigeration cycle 9. The compressor 91, the high-pressure side heat exchanger 92, the expansion valve 93, and the low-pressure side heat exchanger 94 constituting the refrigeration cycle 9 are substantially the same as those described in the ninth embodiment.

In the eleventh embodiment, the cooling water flowing through the second cold heat supply device 201 is cooled by the low pressure side heat exchanger 94 constituting the refrigeration cycle 9. The second cold heat supply device 201 can adjust the amount of cold supplied from the second cold heat supply device 201 to the refrigerant flowing through the second condenser 42 by adjusting the output of the refrigeration cycle 9 or the like. The eleventh embodiment can also provide the same operational effects as the eighth embodiment.

(Other embodiments)
The present disclosure is not limited to the above-described embodiment, and can be modified as appropriate. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. Further, in each of the above embodiments, when referring to the shape, positional relationship, etc. of the component, etc., the shape, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to the positional relationship or the like.

For example, in the embodiment described above, the device temperature adjustment device 1 cools the battery 2 of the vehicle. However, in other embodiments, the target device cooled by the device temperature adjustment device 1 may be various types of vehicles. It may be an equipment device.

For example, in the embodiment described above, the device temperature adjustment device 1 is configured to cool the battery 2, but in other embodiments, the device temperature adjustment device 1 may be configured to heat the battery 2. In this case, the evaporator 3 condenses the refrigerant, and the condensers 41 and 42 evaporate the refrigerant.

For example, in the above-described embodiment, the evaporator 3 is configured as a flat case, but in other embodiments, the evaporator 3 may include a heat exchange tube.

For example, in the embodiment described above, the device temperature adjustment device 1 is provided with two condensers. However, in other embodiments, the device temperature adjustment device 1 is provided with three or more condensers. Also good.

For example, in the above-described embodiment, as the first medium supply device 100 or the second medium supply device 200, the cooling water circulation cycle 8, the refrigeration cycle 9, the blowers 71 and 72, and the like are illustrated, but the present invention is not limited thereto. In other embodiments, the first medium supply device 100 or the second medium supply device 200 is applied with various devices such as a thermo module having a Peltier element or a cooling body that generates a refrigeration action magnetically. Also good.

(Summary)
According to the 1st viewpoint shown by one part or all part of the above-mentioned embodiment, an apparatus temperature control apparatus is an apparatus temperature control apparatus which adjusts the temperature of object apparatus, and is an evaporator, a 1st condenser, and 1st. Two condensers are provided. The evaporator cools the target device by latent heat of vaporization of the working fluid that absorbs heat from the target device and evaporates. The first condenser is provided above the evaporator in the direction of gravity, and has a first heat exchange passage that condenses the working fluid evaporated by the evaporator by heat exchange with the first medium outside. The second condenser is provided above the evaporator in the gravitational direction, and has a second heat exchange passage that condenses the working fluid flowing in from the first condenser by heat exchange with the second medium outside. The discharged working fluid flows out toward the evaporator. Here, the second heat exchange passage of the second condenser has a smaller cross-sectional area or equivalent diameter than the first heat exchange passage of the first condenser.

According to the second aspect, the first condenser has a plurality of first heat exchange passages, and the second condenser has a plurality of second heat exchange passages. The total channel cross-sectional area of the plurality of first heat exchange passages combined with the channel cross-sectional area is larger than the total channel cross-sectional area of the plurality of second heat exchange passages combined.

According to this, when the liquid-phase working fluid accumulates from the second heat exchange passage to the first heat exchange passage, the liquid-phase working fluid in the first heat exchange passage is self-weighted and the liquid phase in the second heat exchange passage Since the working fluid is pushed to the evaporator side, the pressure of the flow of the liquid-phase working fluid toward the evaporator from the first condenser and the second condenser increases. Therefore, the backflow of the liquid-phase working fluid or the backflow of bubbles is suppressed from the evaporator side, and the working fluid flows smoothly. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

According to the third aspect, the first condenser has a region located above the second condenser in the direction of gravity.

According to this, the liquid-phase working fluid generated in the first condenser flows from the first condenser to the second condenser due to its own weight. Therefore, since the liquid-phase working fluid smoothly flows in the forward direction from the first condenser to the evaporator via the second condenser, the back-flow of the liquid-phase working fluid or the back-flow of bubbles is generated from the evaporator side. It is suppressed. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

According to the fourth aspect, at least one of the plurality of first heat exchange passages included in the first condenser or the plurality of second heat exchange passages included in the second condenser extends along the direction of gravity. .

According to this, the first heat exchange passage or the second heat exchange passage that extends along the gravity direction can smoothly flow the liquid-phase working fluid downward in the gravity direction by its own weight. is there. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

According to the fifth aspect, the first condenser and the second condenser are integrally formed.

According to this, the size of the first condenser and the second condenser can be reduced. Further, by eliminating the pipe connecting the first condenser and the second condenser, it is possible to eliminate the concern of heating or heat radiation by the pipe.

According to a sixth aspect, the first condenser has a first upper tank, a first heat exchange passage, and a first lower tank. The second condenser has a second upper tank, a second heat exchange passage, and a second lower tank. The first lower tank of the first condenser and the second upper tank of the second condenser are integrally formed.

According to this, since the first lower tank and the second upper tank are integrally formed, the number of parts can be reduced, the structure can be simplified, and the manufacturing cost can be reduced. Moreover, piping etc. which connect a 1st condenser and a 2nd condenser can be abolished.

According to the seventh aspect, the first medium outside the first condenser and the second medium outside the second condenser are different media.

According to this, it is possible to easily set the first medium and the second medium at different temperatures. Therefore, for example, when the calorific value of the target device is large, use the medium having the lower temperature of the first medium and the second medium to increase the amount of liquid-phase working fluid generated, and sufficiently cool the target device. Is possible. On the other hand, when the calorific value of the target device is small, it is possible to cool the target device to an appropriate temperature using a medium having a relatively high temperature of the first medium and the second medium. Therefore, this device temperature control device can adjust the temperature according to the calorific value of the target device.

According to an eighth aspect, the device temperature adjustment device further includes a first medium supply device and a second medium supply device. The first medium supply device supplies the first medium to the first condenser. The second medium supply device supplies the second medium to the second condenser.

According to this, the amount of cold supplied to the working fluid flowing from the first medium through the first condenser by the first medium supply device is adjusted, and the working fluid flowing from the second medium to the second condenser by the second medium supply device. It is possible to adjust the amount of cooling heat supplied to.

According to the ninth aspect, the second medium supply device is configured to be able to set the second medium at a temperature lower than that of the first medium.

According to this, it is possible to prevent the working fluid condensed in the first condenser from being reheated in the second condenser. Therefore, since it is suppressed that a bubble is produced | generated by a 2nd condenser, the deterioration of the flow of the liquid-phase working fluid by the buoyancy of the bubble is prevented. In addition, the bubbles push up the liquid-phase working fluid and the working fluid is prevented from being blown up on the liquid surface of the first or second condenser, and the bubbles are prevented from bursting to generate abnormal noise. . Furthermore, since the generation of bubbles in the second condenser is suppressed, the first condenser and the second condenser smoothly generate the liquid-phase working fluid, and the first condenser and the second condenser. The liquid phase refrigerant is smoothly supplied from the evaporator to the evaporator. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

According to a tenth aspect, the first medium supply device has a first medium circulation circuit through which the first medium circulates. The second medium supply device has a second medium circulation circuit through which the second medium circulates. Here, the first medium circulation circuit and the second medium circulation circuit are separate and independent circuits.

According to this, it is possible to prevent the temperature of the first medium and the temperature of the second medium from affecting each other. Therefore, the amount of cooling heat supplied from the first medium to the working fluid flowing through the first condenser is appropriately adjusted by the first medium supply device, and the second medium supply device is operated to flow from the second medium to the second condenser. It is possible to appropriately adjust the amount of cold supplied to the fluid.

According to the eleventh aspect, the first medium supply device is a blower, and the second medium supply device is a low-pressure side heat exchanger constituting a refrigeration cycle.

According to this, when the calorific value of the target device is small, for example, by using the blower as the first medium supply device, the power consumption required for cooling the target device is reduced compared to driving the refrigeration cycle. It is possible to reduce.

On the other hand, the second medium supply device can set the refrigerant of the refrigeration cycle, which is the second medium, to a temperature lower than that of the air, which is the first medium. For example, when the heat generation amount of the target device is large, the target device can be sufficiently cooled by using the low-pressure side heat exchanger that constitutes the refrigeration cycle that is the second medium supply device. Therefore, this device temperature control apparatus can reduce the power consumption required for cooling the target device and can adjust the temperature according to the heat generation amount of the target device.

According to the twelfth aspect, the device temperature control device for adjusting the temperature of the target device includes an evaporator, a first condenser, and a second condenser. The evaporator cools the target device by latent heat of vaporization of the working fluid that absorbs heat from the target device and evaporates. The first condenser has a first heat exchange passage that condenses the working fluid evaporated in the evaporator by heat exchange with the first medium outside. The second condenser has a second heat exchange passage for condensing the working fluid flowing in from the first condenser by heat exchange with the second medium outside, and the condensed working fluid flows out toward the evaporator. To do. Here, the first medium and the second medium are different types of media.

According to this, it is possible to easily set the first medium and the second medium at different temperatures. Therefore, for example, when the calorific value of the target device is large, it is possible to sufficiently cool the target device using the medium having the lower temperature of the first medium and the second medium. On the other hand, when the calorific value of the target device is small, it is possible to cool the target device to an appropriate temperature using a medium having a relatively high temperature of the first medium and the second medium. Therefore, this device temperature control device can adjust the temperature according to the calorific value of the target device.

According to a thirteenth aspect, the device temperature adjustment device further includes a first medium supply device and a second medium supply device. The first medium supply device supplies the first medium to the first condenser. The second medium supply device supplies the second medium to the second condenser. The second medium supply device is configured such that the second medium can be set to a temperature lower than that of the first medium.

According to this, it is possible to prevent the working fluid condensed in the first condenser from being reheated in the second condenser. Therefore, since it is suppressed that a bubble is produced | generated by a 2nd condenser, the deterioration of the flow of the liquid-phase working fluid by the buoyancy of the bubble is prevented. In addition, the bubbles push up the liquid-phase working fluid and the liquid-phase working fluid is prevented from being blown up on the liquid surface of the first or second condenser. It is suppressed. Furthermore, since the generation of bubbles in the second condenser is suppressed, the first condenser and the second condenser smoothly generate the liquid-phase working fluid, and the first condenser and the second condenser. The liquid phase refrigerant is smoothly supplied from the evaporator to the evaporator. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

According to the fourteenth aspect, the device temperature adjustment device for adjusting the temperature of the target device includes an evaporator, a first condenser, a second condenser, a first medium supply device, and a second medium supply device. The evaporator cools the target device by latent heat of vaporization of the working fluid that absorbs heat from the target device and evaporates. The first condenser has a first heat exchange passage for condensing the working fluid evaporated in the evaporator by heat exchange with the first medium outside. The second condenser has a second heat exchange passage that allows the working fluid flowing in from the first condenser to condense by heat exchange with the second medium outside, and the condensed working fluid flows out toward the evaporator. To do. The first medium supply device supplies the first medium to the first condenser. The second medium supply device supplies the second medium to the second condenser. The second medium supply device is configured such that the second medium can be set to a temperature lower than that of the first medium.

According to this, it is possible to prevent the working fluid condensed in the first heat exchange passage from being reheated in the second heat exchange passage. Therefore, generation of bubbles in the second heat exchange passage is suppressed, so that deterioration of the flow of the liquid-phase working fluid due to the buoyancy of the bubbles is prevented. In addition, it is possible that the bubbles push up the liquid-phase working fluid and the liquid-phase working fluid is prevented from being blown up on the upper surface of the first or second heat exchange passage. It is suppressed. Further, since the generation of bubbles in the second heat exchange passage is suppressed, the liquid phase working fluid is smoothly generated in the first heat exchange passage and the second heat exchange passage, and the first heat exchange passage The liquid phase refrigerant is smoothly supplied to the evaporator from the second heat exchange passage. Therefore, this equipment temperature control apparatus can improve the cooling capacity of the target equipment.

Claims (14)

1. A device temperature control device for adjusting the temperature of the target device (2),
   An evaporator (3) for cooling the target device by latent heat of evaporation of the working fluid that absorbs heat from the target device and evaporates;
   A first condenser (41) having a first heat exchange passage (412) provided above the evaporator in the direction of gravity and condensing the working fluid evaporated by the evaporator by heat exchange with a first medium outside. )When,
   A second heat exchange passage (422) that is provided above the evaporator in the gravitational direction and that condenses the working fluid flowing in from the first condenser by heat exchange with the second medium outside is condensed. A second condenser (42) for flowing a working fluid toward the evaporator,
   The device temperature control device, wherein the second heat exchange passage of the second condenser has a smaller cross-sectional area or equivalent diameter than the first heat exchange passage of the first condenser.
2. The first condenser has a plurality of the first heat exchange passages, and the second condenser has a plurality of the second heat exchange passages,
   The total channel cross-sectional area (S1 × N1) obtained by combining the channel cross-sectional areas (S1) of the plurality of first heat exchange passages is the sum of the channel cross-sectional areas (S2) of the plurality of second heat exchange passages. The apparatus temperature control apparatus according to claim 1, wherein the apparatus temperature control apparatus is larger than a total flow path cross-sectional area (S2 × N2).
3. The apparatus temperature control device according to claim 1 or 2, wherein the first condenser has a region (α) located on the upper side in the gravity direction than the second condenser.
4. The at least one of the plurality of first heat exchange passages included in the first condenser or the plurality of second heat exchange passages included in the second condenser extends along the direction of gravity. 4. The apparatus temperature control apparatus according to any one of 3.
5. The apparatus temperature control device according to any one of claims 1 to 4, wherein the first condenser and the second condenser are integrally formed.
6. The first condenser has a first upper tank (411), the first heat exchange passage, and a first lower tank (413),
   The second condenser includes a second upper tank (421), the second heat exchange passage, and a second lower tank (423),
   The apparatus temperature control device according to any one of claims 1 to 5, wherein the first lower tank of the first condenser and the second upper tank of the second condenser are configured integrally.
7. The apparatus according to claim 1, wherein the first medium outside the first condenser and the second medium outside the second condenser are different kinds of media. Temperature control device.
8. A first medium supply device (100) for supplying the first medium to the first condenser;
   The device temperature control device according to any one of claims 1 to 7, further comprising a second medium supply device (200) for supplying the second medium to the second condenser.
9. The device temperature adjusting device according to claim 8, wherein the second medium supply device is configured to be able to set the second medium to a temperature lower than that of the first medium.
10. The first medium supply device has a first medium circulation circuit (111) through which the first medium circulates,
    The second medium supply device has a second medium circulation circuit (211) through which the second medium circulates,
    The apparatus temperature control device according to claim 8 or 9, wherein the first medium circulation circuit and the second medium circulation circuit are separate and independent circuits.
11. The first medium supply device is a blower (71),
    The device temperature control device according to claim 8 or 9, wherein the second medium supply device is a low-pressure side heat exchanger (94) constituting the refrigeration cycle (9).
12. A device temperature control device for adjusting the temperature of the target device (2),
    An evaporator (3) for cooling the target device by latent heat of evaporation of the working fluid that absorbs heat from the target device and evaporates;
    A first condenser (41) having a first heat exchange passage (412) for condensing the working fluid evaporated in the evaporator by heat exchange with an external first medium;
    It has a second heat exchange passage (422) for condensing the working fluid flowing in from the first condenser by heat exchange with the second medium outside, and the condensed working fluid flows out toward the evaporator. A second condenser (42),
    The apparatus temperature control device, wherein the first medium outside the first condenser and the second medium outside the second condenser are different kinds of media.
13. A first medium supply device (100) for supplying the first medium to the first condenser;
    A second medium supply device (200) for supplying the second medium to the second condenser;
    The apparatus temperature control device according to claim 12, wherein the second medium supply device is configured to be able to set the second medium to a temperature lower than that of the first medium.
14. A device temperature control device for adjusting the temperature of the target device (2),
    An evaporator (3) for cooling the target device by latent heat of evaporation of the working fluid that absorbs heat from the target device and evaporates;
    A first condenser (41) having a first heat exchange passage (412) for condensing the working fluid evaporated in the evaporator by heat exchange with an external first medium;
    It has a second heat exchange passage (422) for condensing the working fluid flowing in from the first condenser by heat exchange with the second medium outside, and the condensed working fluid flows out toward the evaporator. A second condenser (42);
    A first medium supply device (100) for supplying the first medium to the first condenser;
    A second medium supply device (200) for supplying the second medium to the second condenser,
    The apparatus for adjusting an apparatus temperature, wherein the second medium supply device is configured to be able to set the second medium to a temperature lower than that of the first medium.

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