JP2019196841A - Device temperature regulation system - Google Patents

Abstract

To provide a device temperature regulation system which inhibits development of corrosion.SOLUTION: A device temperature regulation system 1 includes: a working fluid circuit 10 forming a thermosiphon type heat pipe; and a refrigerant circuit 22 forming a refrigeration cycle. The working fluid circuit 10 has: a heat exchanger 12 in which the working fluid is evaporated by heat absorption from a device; and a condenser 15 in which the working fluid is cooled to be condensed by heat exchange with the refrigerant of the refrigerant circuit 22. The working fluid of the working fluid circuit 10 is the same kind of heat medium as the refrigerant of the refrigerant circuit 20. Thus, a minor leak of the working fluid or the refrigerant occurs in a condensed part to inhibit acid from occurring when the working fluid mixes with the refrigerant. Therefore, development of corrosion can be inhibited.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a device temperature control system for adjusting the temperature of a device.

  Patent Document 1 discloses a temperature control system that adjusts the temperature of a battery mounted on a vehicle. This temperature control system includes a working fluid circuit that constitutes a loop-type thermosiphon heat pipe and a refrigerant circuit that constitutes a refrigeration cycle. The condensing part of the working fluid circuit has a working fluid channel through which the working fluid in the working fluid circuit flows and a refrigerant channel through which the refrigerant in the refrigerant circuit flows. The condensing unit heat-exchanges the working fluid flowing through the working fluid flow path and the refrigerant flowing through the refrigerant flow path to cool and condense the working fluid.

JP2015-41418A

  When the condensing part is configured to exchange heat between the working fluid in the working fluid circuit and the refrigerant in the refrigerant circuit as in the above prior art, micro holes are generated in the member that separates the working fluid flow and the refrigerant flow due to corrosion. There are things to do. At this time, a slight leakage of the working fluid from the working fluid channel to the refrigerant channel occurs. Alternatively, a slight leakage of the refrigerant from the refrigerant channel to the working fluid channel occurs. Due to this minute leakage, the working fluid and the refrigerant are mixed.

  Small leaks are also called slow leaks. Slight leakage is a phenomenon that takes days or months from when the working fluid or refrigerant starts to leak until the equipment temperature control system stops functioning. Detection of minute leaks is difficult. In the early stage of microleakage, there is no shortage of working fluid and refrigerant, and it is not possible to detect abnormalities in the equipment temperature control system.

  And when a working fluid and a refrigerant | coolant are different heat media, the production | generation of an acid may occur depending on the combination of a different heat medium. When acid is generated, the progress of corrosion is accelerated. Thereby, the minute hole becomes a large hole. In addition, a portion other than the minute holes in the condensing portion is corroded at a stretch, and a large hole is formed. For this reason, it falls into an abrupt leak state, and the function of the device temperature control system stops. As described above, the present inventor has found a problem that a device that can continue to use the device temperature control system cannot continue to be used if it is in a minute leak state.

  This problem occurs not only when the condensing part of the working fluid circuit is configured to exchange heat between the working fluid and the refrigerant of the refrigerant circuit. The same problem occurs when the condensing unit exchanges heat between the working fluid and the coolant in the coolant circuit. In this case, the coolant circuit has a cooler that cools the coolant by heat exchange with the coolant in the coolant circuit. The same problem occurs when a slight leakage of the working fluid occurs in the condensing part and a slight leakage of the refrigerant occurs in the cooling part.

  Moreover, this problem occurs not only when the working fluid circuit is a loop type. The same problem occurs even when the working fluid circuit is not a loop type.

  An object of this invention is to provide the apparatus temperature control system which can suppress advancing of corrosion in view of the said point.

In order to achieve the above object, an apparatus temperature control system according to the first aspect of the present invention provides:
A working fluid circuit (10) that constitutes a thermosiphon heat pipe and in which the working fluid circulates;
Comprising a refrigeration cycle and a refrigerant circuit (22) through which the refrigerant circulates,
The working fluid circuit
An evaporation section (12) in which the working fluid evaporates due to heat absorption from the device (BP);
A condenser (15) in which the working fluid evaporated in the evaporator is cooled and condensed by heat exchange with the refrigerant in the refrigerant circuit;
The working fluid in the working fluid circuit is the same type of heat medium as the refrigerant in the refrigerant circuit.

  According to this, the same kind of heat medium as the refrigerant of the refrigerant circuit is used as the working fluid of the working fluid circuit. Thereby, a slight leakage of the working fluid or the refrigerant occurs in the condensing part, and the generation of acid when the working fluid and the refrigerant are mixed can be suppressed. For this reason, the progress of corrosion can be suppressed.

Moreover, the device temperature control system of the invention according to claim 2
A working fluid circuit (10) that constitutes a thermosiphon heat pipe and in which the working fluid circulates;
A coolant circuit (62) through which the coolant circulates;
Comprising a refrigeration cycle and a refrigerant circuit (22) through which the refrigerant circulates,
The working fluid circuit
An evaporation section (12) in which the working fluid evaporates due to heat absorption from the device (BP);
A condenser (61) in which the working fluid evaporated in the evaporator is cooled and condensed by heat exchange with the coolant in the coolant circuit;
The coolant circuit has a cooling part (70) in which the coolant is cooled by heat exchange with the coolant in the coolant circuit,
The working fluid in the working fluid circuit is the same type of heat medium as the refrigerant in the refrigerant circuit.

  According to this, the same kind of heat medium as the refrigerant of the refrigerant circuit is used as the working fluid of the working fluid circuit. As a result, a slight leakage of the working fluid occurs in the condensing part, and a slight leakage of the refrigerant occurs in the cooling part, so that generation of acid when the working fluid and the refrigerant are mixed can be suppressed. For this reason, the progress of corrosion can be suppressed.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a schematic diagram which shows the structure of the apparatus temperature control system 1 in 1st Embodiment. It is a typical perspective view of the 2nd condenser in FIG. It is typical sectional drawing of the 2nd condenser in FIG. It is sectional drawing of the fluid circuit for apparatuses in FIG. It is a schematic diagram which shows the structure of the apparatus temperature control system 1 in 2nd Embodiment. It is a typical perspective view of the condenser of the fluid circuit for apparatus in FIG. It is typical sectional drawing of the condenser of the fluid circuit for apparatuses in FIG. It is a typical perspective view of the cooler of the cooling water circuit in FIG. It is typical sectional drawing of the cooler of the cooling water circuit in FIG. It is sectional drawing of the gas-liquid separator in FIG.

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

(First embodiment)
The apparatus temperature control system 1 of this embodiment shown in FIG. 1 adjusts the battery temperature of the assembled battery BP as a temperature adjustment object apparatus by cooling the assembled battery BP mounted in the vehicle. As a vehicle on which the device temperature control system 1 is mounted, an electric vehicle and a hybrid vehicle that can be driven by a driving electric motor (not shown) that uses an assembled battery BP as a power source are assumed.

  The device temperature control system 1 includes a device fluid circuit 10 through which a working fluid circulates. The device fluid circuit 10 is a heat pipe that performs heat transfer by evaporation and condensation of the working fluid, and is configured to be a thermosiphon type in which the working fluid naturally circulates by gravity. Furthermore, the fluid circuit for equipment 10 is configured to be a loop type 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. That is, the fluid circuit for equipment 10 constitutes a loop-type thermosiphon heat pipe.

  The assembled battery BP is formed of 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 and a motor generator (not shown). The power conversion device is a device that converts, for example, a direct current supplied from an assembled battery into an alternating current, and supplies (that is, 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 regeneration of the vehicle and supplies the reversely converted electric energy as regenerative power to the assembled battery BP via an inverter or the like.

  The assembled battery 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, not only the input / output characteristics of the assembled battery BP are deteriorated, but also the deterioration of the battery cell BC is promoted. Therefore, a cooling means for maintaining the temperature below a predetermined temperature is required. Become.

  In addition, 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 when the vehicle is running but also during parking in summer. As a result, the battery temperature may become excessively high. 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.

  Further, the assembled battery BP is composed of a plurality of battery cells BC. However, if the temperature of each battery cell BC varies, the degree of progress of deterioration of each battery cell is biased, and the entire assembled battery is inserted. The output characteristics will deteriorate. This is because the assembled battery BP includes battery cells connected in series, so that the input / output characteristics of the entire assembled battery are determined according to the battery characteristics of the battery cell BC that has been most deteriorated among the battery cells BC. Because. 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.

  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, it may not be possible to obtain a cooling capacity sufficient to sufficiently cool the assembled battery BP.

  Moreover, although the cooling means using the cold heat of the refrigeration cycle has a high cooling capacity of 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.

  In view of this, the apparatus temperature control system 1 of the present embodiment employs a thermosiphon system in which the battery temperature of the assembled battery BP is adjusted not by forced circulation of the refrigerant by the compressor but by natural circulation of the working fluid.

  The equipment fluid circuit 10 is formed by connecting the equipment heat exchanger 12, the first condenser 14, the second condenser 15, the gas passage section 16, and the liquid passage section 18 to each other. The device fluid circuit 10 is a closed annular fluid circuit. A predetermined amount of working fluid is sealed inside the device fluid circuit 10. As the working fluid, the same type of heat medium as the refrigerant of the refrigerant circuit 22 described later is used. For example, when R134a is used as the refrigerant of the refrigerant circuit 22, R134a is used as the working fluid.

  The equipment heat exchanger 12 is a heat exchanger that functions as an evaporation section that absorbs heat from the assembled battery BP and evaporates the liquid working fluid when the assembled battery BP is cooled. The equipment heat exchanger 12 has a thin, rectangular parallelepiped shape. The equipment heat exchanger 12 is disposed at a position facing the bottom surface side of the assembled battery BP. That is, the assembled battery BP is arranged on the upper surface of the equipment heat exchanger 12.

  The equipment heat exchanger 12 is disposed below the first condenser 14 and the second condenser 15. As a result, the liquid working fluid accumulates in the lower portion of the equipment fluid circuit 10 including the equipment heat exchanger 12 by gravity.

  The first condenser 14 and the second condenser 15 are heat exchangers that condense the gaseous working fluid evaporated in the equipment heat exchanger 12. In this embodiment, the 1st condenser 14 and the 2nd condenser 15 comprise the apparatus condensation part 13 which condenses a working fluid. One of the first condenser 14 and the second condenser 15 condenses the working fluid. A second condenser 15 is connected to the downstream side of the first condenser 14 via a communication path portion 17. The communication path part 17 is comprised by piping in which the flow path through which a working fluid distribute | circulates was formed.

  The first condenser 14 is an air-cooled condenser that cools the working fluid by heat exchange between air and the working fluid. The apparatus temperature control system 1 has a blower 20 that sends air to the first condenser 14.

  The second condenser 15 is a condenser that cools the working fluid by heat exchange with the refrigerant of the air-conditioning refrigeration cycle device 21 mounted on the vehicle. The refrigeration cycle apparatus 21 constitutes a part of the vehicle air conditioner. In other words, the device temperature control system 1 of the present embodiment includes the refrigeration cycle device 21 shared with the vehicle air conditioner. The refrigeration cycle apparatus 21 includes a refrigerant circuit 22 through which refrigerant flows. As the refrigerant, a refrigerant used in a general refrigeration cycle apparatus can be used. Examples of the refrigerant include R134a and R1234yf.

  The second condenser 15 includes a working fluid side heat exchanging portion 15a through which the working fluid of the device fluid circuit 10 flows, and a refrigerant side heat exchanging portion 15b through which the refrigerant of the refrigerant circuit 22 flows. The working fluid side heat exchanging portion 15a and the refrigerant side heat exchanging portion 15b are thermally connected so that heat exchange between the working fluid and the refrigerant is possible.

  As shown in FIG. 2, the second condenser 15 includes a first inlet portion 151 a into which the working fluid of the device fluid circuit 10 flows and a first outlet portion 151 b from which the working fluid of the device fluid circuit 10 flows out. Have. The second condenser 15 has a second inlet portion 151c into which the refrigerant of the refrigerant circuit 22 flows, and a second outlet portion 151d from which the refrigerant of the refrigerant circuit 22 flows out. The first inlet portion 151 a and the second outlet portion 151 d are provided in the upper part of the second condenser 15. The first outlet part 151 b and the second inlet part 151 c are provided in the lower part of the second condenser 15.

  As shown in FIG. 3, the second condenser 15 includes a heat exchange core unit 152. The second condenser 15 includes a working fluid distribution unit 153 a and a refrigerant assembly unit 153 d on the upper side of the heat exchange core unit 152. The second condenser 15 includes a working fluid collecting portion 153b and a refrigerant distribution portion 153c below the heat exchange core portion 152.

  The heat exchange core part 152 includes a plurality of working fluid channels 152a and a plurality of refrigerant channels 152b. The working fluid channel 152a and the refrigerant channel 152b are alternately arranged. The second condenser 15 is a stacked heat exchanger. The heat exchange core portion 152 includes a metal plate 152c as a member that separates the adjacent working fluid flow paths 152a and refrigerant flow paths 152b. The metal plate 152c is a member that transfers heat. For this reason, in order to improve heat exchange efficiency, the metal plate 152c is made of a metal material having high thermal conductivity. Furthermore, in order to increase the heat exchange efficiency, the metal plate 152c is made thinner than the wall of a pipe (not shown) connected to the second condenser 15. The plurality of working fluid flow paths 152a constitute the working fluid side heat exchange section 15a. The plurality of refrigerant flow paths 152b constitute the refrigerant side heat exchange section 15b. The second condenser 15 may be a heat exchanger other than the stacked type.

  The working fluid flowing in from the first inlet portion 151a is distributed from the working fluid distributor 153a to the plurality of working fluid channels 152a of the heat exchange core portion 152. The distributed working fluid flows through the plurality of working fluid flow paths 152a from top to bottom. The distributed working fluid is collected at the working fluid collecting portion 153b and flows out from the first outlet portion 151b.

  On the other hand, the refrigerant flowing from the second inlet portion 151c is distributed from the refrigerant distribution portion 153c to the plurality of refrigerant flow paths 152b of the heat exchange core portion 152. The distributed refrigerant flows from the bottom to the top through the plurality of refrigerant flow paths 152b. The distributed refrigerant gathers at the refrigerant gathering portion 153d and flows out from the second outlet portion 151d. When the working fluid and the refrigerant flow through the heat exchange core part 152, the working fluid and the refrigerant exchange heat through the metal plate 152c. Thereby, the working fluid is cooled and condensed. The refrigerant is heated and evaporates.

  As shown in FIG. 1, the refrigerant circuit 22 constitutes a vapor compression refrigeration cycle. Specifically, the refrigerant circuit 22 is formed by connecting a compressor 24, an air conditioning condenser 26, a first expansion valve 28, an air conditioning evaporator 30 and the like by piping. The refrigeration cycle apparatus 21 includes a blower 27 that sends air to the air conditioning condenser 26 and a blower 31 that forms an air flow toward the vehicle interior space.

  The compressor 24 compresses and discharges the refrigerant. The air conditioning condenser 26 is a heat radiator that condenses the refrigerant flowing out of the compressor 24 by heat exchange with heat. The first expansion valve 28 depressurizes the refrigerant flowing out of the air conditioning condenser 26. The air conditioning evaporator 30 evaporates the refrigerant flowing out of the first expansion valve 28 by heat exchange with the air traveling toward the vehicle interior space, and cools the air traveling toward the vehicle interior space.

  Furthermore, the refrigerant circuit 22 includes a second expansion valve 32 and a refrigerant side heat exchange unit 15b connected in parallel with the refrigerant flow with respect to the first expansion valve 28 and the air conditioning evaporator 30. The second expansion valve 32 decompresses the refrigerant flowing out of the air conditioning condenser 26. The refrigerant side heat exchange unit 15b is an evaporation unit that evaporates the refrigerant by heat exchange with the working fluid flowing through the working fluid side heat exchange unit 15a.

  Furthermore, the refrigerant circuit 22 has an open / close valve 34 that opens and closes a refrigerant flow path through which the refrigerant flows toward the refrigerant-side heat exchange unit 15b. By closing the on-off valve 34, a first refrigerant circuit is formed in which the refrigerant flows in the order of the compressor 24, the air conditioning condenser 26, the first expansion valve 28, and the air conditioning evaporator 30. By opening the on-off valve 34, in addition to the first refrigerant circuit, a second refrigerant circuit is formed in which the refrigerant flows in the order of the compressor 24, the air conditioning condenser 26, the second expansion valve 32, and the refrigerant side heat exchange unit 15b. The

  When the outside air temperature is lower than the predetermined temperature or when the battery temperature is lower than the predetermined temperature, the blower 20 is activated. The refrigeration cycle apparatus 21 is in a stopped state. Thereby, the working fluid is cooled and condensed in the first condenser 14 by heat exchange with the blown air.

  When the outside air temperature is higher than the predetermined temperature and the battery temperature is higher than the predetermined temperature, the on-off valve 34 is opened. At this time, at least the compressor 24 and the blower 27 are operated. Thereby, the working fluid is cooled and condensed by heat exchange with the refrigerant flowing through the refrigerant side heat exchange unit 15b in the working fluid side heat exchange unit 15a of the second condenser 15.

  The gas passage portion 16 guides the gaseous working fluid evaporated in the equipment heat exchanger 12 to the equipment condensation section 13. In other words, the gas passage portion 16 is a first flow path through which the working fluid flows from the equipment heat exchanger 12 as the evaporation section toward the equipment condensation section 13 as the condensation section. The gas passage portion 16 has a lower end connected to the equipment heat exchanger 12 and an upper end connected to the first condenser 14. The gas passage part 16 of this embodiment is comprised by piping in which the flow path through which a working fluid distribute | circulates was formed.

  The liquid passage part 18 guides the liquid working fluid condensed in the equipment condensing part 13 to the equipment heat exchanger 12. That is, the liquid passage portion 18 is a second flow path through which the working fluid flows from the device condensing unit 13 as the condensing unit toward the device heat exchanger 12 as the evaporation unit. The liquid passage portion 18 has a lower end connected to the equipment heat exchanger 12 and an upper end connected to the second condenser 15. The liquid passage portion 18 of the present embodiment is configured by a pipe in which a flow path through which a working fluid flows is formed.

  Subsequently, a basic operation of the device temperature control system 1 of the present embodiment will be described with reference to FIG. Note that an arrow DRg shown in FIG. 4 indicates the direction in which the vertical line extends, that is, the vertical direction.

  In the device temperature control system 1, when the battery temperature Tb of the assembled battery BP rises due to self-heating during traveling of the vehicle, the heat of the assembled battery BP moves to the device heat exchanger 12. In the equipment heat exchanger 12, a part of the liquid working fluid WF 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 WF existing inside the equipment heat exchanger BP, and the temperature thereof decreases.

  The gaseous working fluid WF evaporated in the equipment heat exchanger 12 flows out from the equipment heat exchanger 12 to the gas passage section 16, and passes through the gas passage section 16 as indicated by an arrow F11 in the figure. It moves to the condensing part 13 for apparatuses.

  In the equipment condensing unit 13, the gaseous working fluid WF is condensed by the heat radiation of the gaseous working fluid WF in the first condenser 14 or the second condenser 15. The condensed liquid working fluid WF descends due to gravity. As a result, the liquid working fluid WF condensed in the device condensing unit 13 flows out from the device condensing unit 13 to the liquid passage unit 18, and the device passes through the liquid passage unit 18 as indicated by an arrow F <b> 12 in the drawing. It moves to the heat exchanger 12 for work. In the equipment heat exchanger 12, a part of the flowing liquid working fluid WF is evaporated by absorbing heat from the assembled battery BP.

  As described above, the equipment temperature control system 1 circulates between the equipment heat exchanger 12 and the equipment condensing unit 13 while the working fluid WF changes between a gas state and a liquid state, and the equipment heat exchanger. The assembled battery BP is cooled by transporting heat from 12 to the apparatus condensing unit 13. In addition, the device temperature control system 1 is configured such that the working fluid WF naturally circulates inside the device fluid circuit 10 without the driving force required to circulate the working fluid by a compressor or the like.

  By the way, in the 2nd condenser 15, as shown in FIG. 3, the minute hole H1 may generate | occur | produce in the metal plate 152c of the heat exchange core part 152 by corrosion. At this time, if the internal pressure of the device fluid circuit 10 is higher than the internal pressure of the refrigerant circuit 22, a slight leakage of the working fluid from the working fluid flow path 152a to the refrigerant flow path 152b occurs. On the other hand, when the internal pressure of the device fluid circuit 10 is lower than the internal pressure of the refrigerant circuit 22, a slight leakage of the refrigerant from the refrigerant channel 152b to the working fluid channel 152a occurs. Due to this slight leakage, the working fluid and the refrigerant are mixed.

  Unlike the present embodiment, when the working fluid of the device fluid circuit 10 and the refrigerant of the refrigerant circuit 22 are different types of heat media, the generation of acid may occur depending on the combination of different types of heat media. . When acid is generated, the progress of corrosion is accelerated. For this reason, the minute hole H1 becomes a large hole. Further, a portion of the metal plate 152c different from the portion where the minute hole H1 is formed is corroded at a stretch to form a large hole. Moreover, parts other than the 2nd condenser 15 of the fluid circuit 10 for apparatuses, and parts other than the refrigerant | coolant side heat exchange part 15b of the refrigerant circuit 22 corrode at a stretch, and a big hole is formed. As a result, the working fluid or the refrigerant leaks rapidly. As a result, the function of the device temperature control system 1 is stopped.

  On the other hand, in the present embodiment, the same type of heat medium as the refrigerant of the refrigerant circuit 22 is used as the working fluid of the device fluid circuit 10. Thereby, the production | generation of the acid by mixing with a working fluid and a refrigerant | coolant can be suppressed. For this reason, the progress of corrosion can be suppressed. Therefore, according to the present embodiment, it is possible to lengthen the period from when a slight leakage of the working fluid or refrigerant due to corrosion occurs to when the function of the device temperature control system 1 is stopped.

(Second Embodiment)
As shown in FIG. 5, the present embodiment is different from the first embodiment in the apparatus condensing unit 13. The other structure of the apparatus temperature control system 1 is the same as 1st Embodiment.

  The apparatus temperature control system 1 includes a water-cooled condenser 61 as the apparatus condensing unit 13 and a cooling water circuit 62 through which cooling water circulates. The cooling water is a cooling liquid containing water. The cooling liquid is a liquid heat medium for transporting heat. As the cooling water, for example, an antifreeze or water is used. The condenser 61 is a heat exchanger that condenses the working fluid of the device fluid circuit 10 by heat exchange with the cooling water of the cooling water circuit 62. The condenser 61 has a working fluid side heat exchanging portion 61a through which the working fluid of the device fluid circuit 10 flows, and a cooling water side heat exchanging portion 61b through which the cooling water of the cooling water circuit 62 flows. The working fluid side heat exchange unit 61a and the cooling water side heat exchange unit 61b are thermally connected so that heat exchange between the working fluid and the cooling water is possible.

  As shown in FIG. 6, the condenser 61 includes a first inlet 611 a into which the working fluid of the device fluid circuit 10 flows and a first outlet 611 b from which the working fluid of the device fluid circuit 10 flows out. The condenser 61 includes a second inlet portion 611c into which the cooling water from the cooling water circuit 62 flows and a second outlet portion 611d from which the cooling water from the cooling water circuit 62 flows out. The first inlet portion 611a and the second outlet portion 611d are provided in the upper part of the condenser 61. The first outlet portion 611 b and the second inlet portion 611 c are provided in the lower part of the condenser 61.

  As shown in FIG. 7, the condenser 61 includes a heat exchange core unit 612. The condenser 61 includes a working fluid distribution unit 613a and a cooling water collecting unit 613d on the upper side of the heat exchange core unit 612. The condenser 61 includes a working fluid collecting portion 613b and a cooling water distributing portion 613c below the heat exchange core portion 612.

  In the heat exchange core portion 612, a plurality of working fluid channels 612a and a plurality of cooling water channels 612b are formed. The working fluid channel 612a and the cooling water channel 612b are alternately arranged. The condenser 61 is a stacked heat exchanger. The heat exchange core portion 612 includes a metal plate 612c as a member that separates the adjacent working fluid flow paths 612a and cooling water flow paths 612b. The metal plate 612c corresponds to the metal plate 152c of the first embodiment. The plurality of working fluid flow paths 612a constitute the working fluid side heat exchanging portion 61a. The plurality of cooling water flow paths 612b constitutes the cooling water side heat exchange section 61b. The condenser 61 may be a heat exchanger other than the stacked type.

  The working fluid flowing in from the first inlet 611a is distributed from the working fluid distributor 613a to the plurality of working fluid channels 612a of the heat exchange core 612. The distributed working fluid flows through the plurality of working fluid flow paths 612a from top to bottom. The distributed working fluid gathers at the working fluid gathering part 613b and flows out from the first outlet part 611b.

  On the other hand, the cooling water flowing in from the second inlet portion 611c is distributed from the cooling water distribution portion 613c to the plurality of cooling water flow paths 612b of the heat exchange core portion 612. The distributed cooling water flows through the plurality of cooling water flow paths 612b from the bottom to the top. The distributed cooling water gathers at the cooling water gathering part 613d and flows out from the second outlet part 611d. When the working fluid and the cooling water flow through the heat exchange core portion 612, the working fluid and the cooling water exchange heat through the metal plate 612c. Thereby, the working fluid is cooled and condensed. Cooling water receives heat.

  As shown in FIG. 5, the cooling water circuit 62 is basically formed by connecting a water pump 63, a radiator 64, and a cooling water side heat exchanging portion 61b. The device temperature control system 1 has a blower 65.

  The water pump 63 discharges the sucked cooling water to form a cooling water flow. The radiator 64 is a heat exchanger that radiates cooling water by heat exchange with the air blown by the blower 65, that is, outside air. The cooling water side heat exchanging part 61b receives heat from the working fluid to the cooling water by exchanging heat with the working fluid flowing through the working fluid side heat exchanging part 61a.

  The cooling water circuit 62 further includes a bypass channel 66 and a switching valve 67. The bypass flow channel 66 is a flow channel in which cooling water flows around the radiator 64. The switching valve 67 switches between a cooling water flow that flows through the radiator 64 and a cooling water flow that flows through the bypass passage 66. One end side of the bypass flow channel 66 is connected to a branch portion 68 located on the downstream side of the water pump 63 and the upstream side of the radiator 64. A switching valve 67 is installed in the branch portion 68. The other end side of the bypass flow channel 66 is connected to a merging portion 69 located on the downstream side of the radiator 64.

  The cooling water circuit 62 has a cooler 70. The cooler 70 is connected between the confluence | merging part 69 and the cooling water side heat exchange part 61b. The cooler 70 is a heat exchanger that cools the cooling water by heat exchange with the refrigerant of the refrigeration cycle apparatus 21.

  The cooler 70 includes a cooling water side heat exchanging portion 70a through which cooling water flows and a refrigerant side heat exchanging portion 70b through which the refrigerant of the refrigerant circuit 22 flows. The cooling water side heat exchange unit 70a and the refrigerant side heat exchange unit 70b are thermally connected so that heat exchange between the cooling water and the refrigerant is possible.

  As shown in FIG. 8, the cooler 70 includes a first inlet portion 701 a into which cooling water from the cooling water circuit 62 flows and a first outlet portion 701 b from which cooling water from the cooling water circuit 62 flows out. The cooler 70 includes a second inlet portion 701c into which the refrigerant of the refrigerant circuit 22 flows and a second outlet portion 701d from which the refrigerant of the refrigerant circuit 22 flows out. The first inlet portion 701a and the second outlet portion 701d are provided in the upper part of the cooler 70. The first outlet portion 701 b and the second inlet portion 701 c are provided in the lower part of the cooler 70.

  As shown in FIG. 9, the cooler 70 includes a heat exchange core portion 702. The cooler 70 includes a cooling water distribution unit 703a and a refrigerant assembly unit 703d on the upper side of the heat exchange core unit 702. The cooler 70 includes a cooling water collecting portion 703b and a refrigerant distribution portion 703c below the heat exchange core portion 702.

  In the heat exchange core part 702, a plurality of cooling water channels 702a and a plurality of refrigerant channels 702b are formed. The cooling water channel 702a and the coolant channel 702b are alternately arranged. The cooler 70 is a stacked heat exchanger. The heat exchange core part 702 includes a metal plate 702c as a member that separates the adjacent cooling water channel 702a and refrigerant channel 702b. The metal plate 702c corresponds to the metal plate 152c of the first embodiment. The plurality of cooling water flow paths 702a constitute the cooling water side heat exchange unit 70a. The plurality of refrigerant flow paths 702b constitute the refrigerant side heat exchange unit 70b. The cooler 70 may be a heat exchanger other than the stacked type.

  The cooling water flowing from the first inlet 701a is distributed from the cooling water distributor 703a to the plurality of cooling water channels 702a of the heat exchange core 702. The distributed cooling water flows through the plurality of cooling water flow paths 702a from the top to the bottom. The distributed cooling water is collected at the cooling water collecting portion 703b and flows out from the first outlet portion 701b.

  On the other hand, the refrigerant flowing in from the second inlet portion 701c is distributed from the refrigerant distribution portion 703c to the plurality of refrigerant flow paths 702b of the heat exchange core portion 702. The distributed refrigerant flows from the bottom to the top through the plurality of refrigerant flow paths 702b. The distributed refrigerant gathers at the refrigerant gathering portion 703d and flows out from the second outlet portion 701d. When the cooling water and the refrigerant flow through the heat exchange core part 702, the cooling water and the refrigerant exchange heat through the metal plate 702c. Thereby, the cooling water dissipates heat. The refrigerant is heated and evaporates.

  As shown in FIG. 5, the refrigerant circuit 22 includes a second expansion valve 32 and a refrigerant side heat exchange unit 70 b connected in parallel with the refrigerant flow with respect to the first expansion valve 28 and the air conditioning evaporator 30. ing. The refrigerant side heat exchange unit 70b corresponds to the refrigerant side heat exchange unit 15b of the first embodiment. The refrigerant side heat exchange unit 70b is an evaporation unit that evaporates the refrigerant by exchanging heat with cooling water. Other configurations of the refrigeration cycle apparatus 21 are the same as those in the first embodiment.

  Also in the present embodiment, the on-off valve 34 of the refrigerant circuit 22 is opened, so that in addition to the first refrigerant circuit, the refrigerant in the order of the compressor 24, the condenser 26 for air conditioning, the second expansion valve 32, and the refrigerant side heat exchange unit 70b. A second refrigerant circuit is formed.

  When the outside air temperature is lower than the predetermined temperature or when the battery temperature is lower than the predetermined temperature, the cooling water radiation mode is set to the outside air radiation mode in which heat is radiated from the cooling water to the outside air. That is, the switching valve 67 is in a state in which the cooling water flows through the radiator 64. The water pump 63 and the blower 65 are activated. The refrigeration cycle apparatus 21 is in a stopped state. Alternatively, the refrigeration cycle apparatus 21 is in a state where the refrigerant does not flow through the second refrigerant circuit and the refrigerant flows through the first refrigerant circuit. Thereby, in the cooling water circuit 62, the cooling water circulates between the condenser 61 and the radiator 64 as shown by arrows F21a, 21b, and 21c in FIG. Then, in the condenser 61, the working fluid is cooled and condensed by heat exchange with the cooling water. The radiator 64 dissipates heat by heat exchange with the outside air.

  When the outside air temperature is higher than the predetermined temperature and the battery temperature is higher than the predetermined temperature, the heat dissipation mode of the cooling water is set to the refrigerant heat dissipation mode for dissipating heat from the cooling water to the refrigerant of the refrigeration cycle apparatus 21. That is, the switching valve 67 is in a state in which the cooling water flows through the bypass channel 66. The water pump 63 is activated. Thereby, in the cooling water circuit 62, the cooling water circulates between the condenser 61 and the cooler 70 as shown by arrows F22a, 22b, and 22c in FIG. Furthermore, the on-off valve 34 of the refrigeration cycle apparatus 21 is opened. The compressor 24 and the blower 27 of the refrigeration cycle apparatus 21 are operated. As a result, the refrigerant flows through the second refrigerant circuit. As a result, in the cooler 70, the cooling water radiates heat by heat exchange with the refrigerant. That is, the cooling water is cooled. In the condenser 61, the working fluid is cooled and condensed by heat exchange with the cooling water cooled by the cooler 70.

  Thus, in this embodiment, the condensing part of the apparatus fluid circuit 10 and the evaporation part of the refrigerant circuit 22 are thermally connected via the cooling water circuit 62.

  As shown in FIG. 5, the cooling water circuit 62 includes a gas-liquid separator 60 that separates cooling water and gas. The gas-liquid separator 60 is disposed on the upstream side of the water pump 63.

  As shown in FIG. 10, the gas-liquid separator 60 includes a main body 602 that forms a gas-liquid separation chamber 601 and a relief valve 603 therein.

  In the lower part of the main body 602, an inlet 604 into which cooling water flows and an outlet 605 from which cooling water flows out are provided. A baffle plate 606 is disposed between the inlet 604 and the outlet 605 at the lower part of the gas-liquid separation chamber 601. For this reason, in the gas-liquid separation chamber 601, the cooling water that has flowed from the inlet portion 604 flows toward the outlet portion 605, bypassing the baffle plate 606. At this time, the gas contained in the cooling water is separated from the cooling water. The separated gas accumulates in the upper part of the gas-liquid separation chamber 601.

  The relief valve 603 is provided in the upper part of the main body 602. The relief valve 603 releases gas from the gas-liquid separation chamber 601 to the outside of the gas-liquid separation chamber 601 when the pressure in the gas-liquid separation chamber 601 exceeds a predetermined pressure. The relief valve 603 sucks air into the gas-liquid separation chamber 601 from the outside of the gas-liquid separation chamber 601 when the pressure in the gas-liquid separation chamber 601 becomes lower than a predetermined pressure. Thereby, the inside of the cooling water circuit 62 is maintained at a constant pressure.

  The basic operation of the device temperature control system 1 is the same as that in the first embodiment.

  By the way, in the condenser 61, as shown in FIG. 7, the micro hole H2 may generate | occur | produce in the metal plate 612c of the heat exchange core part 612 by corrosion. At this time, in the normal use temperature range of the device fluid circuit 10, the pressure of the working fluid sealed in the device fluid circuit 10 is higher than the pressure of the coolant in the coolant circuit 62. For this reason, a slight leakage of the working fluid from the working fluid channel 612a to the cooling water channel 612b occurs. Since the pressure of the working fluid in the device fluid circuit 10 is higher than the pressure of the coolant in the coolant circuit 62, the coolant does not enter the device fluid circuit 10.

  Also in the cooler 70, as shown in FIG. 9, a minute hole H3 may be generated in the metal plate 702c of the heat exchange core part 702 due to corrosion. At this time, the pressure of the refrigerant sealed in the refrigerant circuit 22 is higher than the pressure of the cooling water in the cooling water circuit 62. For this reason, a slight leakage of the refrigerant from the refrigerant flow path 702b to the cooling water flow path 702a occurs. In addition, since the pressure of the refrigerant in the refrigerant circuit 22 is higher than the pressure of the cooling water in the cooling water circuit 62, the cooling water does not enter the refrigerant circuit 22.

  Thus, when a slight leak occurs in both the condenser 61 and the cooler 70, the working fluid and the refrigerant are mixed inside the cooling water circuit 62. For this reason, unlike the present embodiment, when the working fluid of the device fluid circuit 10 and the refrigerant of the refrigerant circuit 22 are different types of heat media, acid generation may occur depending on the combination of different types of heat media. is there. When acid is generated, the progress of corrosion is accelerated. For this reason, when the minute hole H2 of the condenser 61 becomes large, the condenser 61 falls into an abrupt leak state. In addition, since the minute hole H3 of the cooler 70 becomes large, the cooler 70 falls into an abrupt leak state. Further, in the condenser 61 and the cooler 70, a portion other than the portion where the minute holes H2 and H3 are formed in the metal plates 612c and 702c is corroded at a stroke and a large hole is formed, so that a sudden leakage occurs. Fall into a state. As a result, the function of the device temperature control system 1 is stopped.

  On the other hand, in the present embodiment, the same type of heat medium as the refrigerant of the refrigerant circuit 22 is used as the working fluid of the device fluid circuit 10. Thereby, there exists an effect similar to 1st Embodiment.

  In the present embodiment, the cooling water circuit 62 includes a gas-liquid separator 60. Therefore, when a slight leak occurs in at least one of the condenser 61 and the cooler 70, the gaseous working fluid that has entered the cooling water circuit 62, that is, the refrigerant gas, is captured by the gas-liquid separator 60. Can do. For this reason, it is possible to prevent the refrigerant gas from actively circulating through the coolant circuit 62. For this reason, the refrigerant gas actively circulates in the cooling water circuit 62, so that an acid is generated by the reaction of the refrigerant with the cooling water additive and the material in the cooling water circuit, and the cooling water circuit 62 is corroded. Can be suppressed.

  Further, in the present embodiment, when a large amount of refrigerant gas is accumulated in the gas-liquid separator 60, the refrigerant gas can be released from the relief valve 603 to the outside of the gas-liquid separator 60 with the pressure of the refrigerant gas. it can. Thereby, rupture of the cooling water circuit 62 and leakage of the cooling water can be prevented. In this way, the refrigerant gas that has entered the cooling water circuit 62 is separated from the cooling water by the gas-liquid separator 60 and discharged to the outside. For this reason, refrigerant gas does not mix with cooling water positively.

  In this embodiment, the cooling water, that is, the cooling liquid containing water is used, but a cooling liquid not containing water may be used.

(Other embodiments)
(1) In the first embodiment, in the refrigeration cycle apparatus 21, the refrigerant side heat exchange unit 15 b of the second condenser 15 is connected in parallel to the air conditioning evaporator 30, but is not limited thereto. The refrigerant side heat exchanger 15b of the second condenser 15 may be connected in series to the downstream side of the refrigerant flow of the air conditioning evaporator 30.

  Similarly, in 2nd Embodiment, although the refrigerant | coolant side heat exchange part 70b of the cooler 70 was connected in parallel with respect to the air conditioning evaporator 30 in the refrigerating-cycle apparatus 21, it is not limited to this. The refrigerant side heat exchange part 70b of the cooler 70 may be connected in series to the downstream side of the refrigerant flow of the air conditioning evaporator 30.

  (2) In the first and second embodiments, the refrigeration cycle apparatus 21 is provided for the equipment temperature control system 1 and the vehicle air conditioner, but is not limited thereto. The refrigeration cycle apparatus 21 may be dedicated to the equipment temperature control system 1.

  (3) In each of the above embodiments, the equipment heat exchanger 12 has only a cooling function for cooling the assembled battery BP. However, the equipment heat exchanger 12 performs heating for heating the battery in addition to the cooling function. It may have a function. That is, the apparatus temperature control system 1 may adjust the battery temperature of the assembled battery BP by cooling or heating the assembled battery BP.

  (4) In each said embodiment, although the cooling target object of the apparatus temperature control system 1 was a battery, it is not limited to this. The cooling object may be an electronic device mounted on a vehicle other than the battery. Further, the object to be cooled is not limited to the electronic device installed in the vehicle. The cooling object may be an electronic device installed in a place other than the vehicle.

  (5) In each of the above embodiments, the device fluid circuit 10 is configured to be a loop type in which the flow path through which the gaseous working fluid flows and the flow path through which the liquid working fluid flows are separated. It does not have to be a loop type.

  (6) The present invention is not limited to the above-described embodiment, and can be appropriately changed within the scope described in the claims, and includes various modifications and modifications within the equivalent range. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. In each of the above embodiments, when referring to the material, shape, positional relationship, etc. of the constituent elements, etc., unless otherwise specified, or in principle limited to a specific material, shape, positional relationship, etc. The material, shape, positional relationship, etc. are not limited.

(Summary)
According to the first aspect shown in part or all of the above embodiments, the device temperature control system includes a working fluid circuit that forms a thermosiphon heat pipe, and a refrigerant circuit that forms a refrigeration cycle. Prepare. The working fluid circuit includes an evaporation unit in which the working fluid evaporates due to heat absorption from the device, and a condensing unit in which the working fluid evaporated in the evaporation unit is cooled and condensed by heat exchange with the refrigerant in the refrigerant circuit. The working fluid in the working fluid circuit is the same type of heat medium as the refrigerant in the refrigerant circuit.

  According to the second aspect, the device temperature control system includes a working fluid circuit that constitutes a thermosiphon heat pipe, a coolant circuit that circulates coolant, and a refrigerant circuit that constitutes a refrigeration cycle. . The working fluid circuit has an evaporating part where the working fluid evaporates due to heat absorption from the device, and a condensing part where the working fluid evaporated in the evaporating part is cooled and condensed by heat exchange with the coolant in the coolant circuit. . The coolant circuit has a cooling unit in which the coolant is cooled by heat exchange with the coolant in the coolant circuit. The working fluid in the working fluid circuit is the same type of heat medium as the refrigerant in the refrigerant circuit.

  According to the third aspect, in the second aspect, the coolant circuit includes a gas-liquid separator. According to this, the gaseous heat medium that has entered the coolant circuit from the working fluid circuit or the refrigerant circuit can be captured by the gas-liquid separator. For this reason, it can suppress that the gaseous heat medium of a working fluid circuit or a refrigerant circuit circulates through a cooling fluid circuit. The occurrence of corrosion due to the gaseous heat medium circulating in the coolant circuit can be suppressed.

DESCRIPTION OF SYMBOLS 1 Apparatus temperature control system 10 Fluid circuit for apparatus 12 Heat exchanger for apparatus 15 2nd condenser 22 Refrigerant circuit 61 Water-cooled condenser 62 Cooling water circuit 70 Cooler

Claims (3)

A device temperature control system for adjusting the temperature of the device,
A working fluid circuit (10) that constitutes a thermosiphon heat pipe and in which the working fluid circulates;
Comprising a refrigeration cycle and a refrigerant circuit (22) through which the refrigerant circulates,
The working fluid circuit includes:
An evaporation section (12) in which the working fluid evaporates due to heat absorption from the device (BP);
A condenser (15) that cools and condenses the working fluid evaporated in the evaporator by heat exchange with the refrigerant in the refrigerant circuit;
The equipment temperature control system, wherein the working fluid in the working fluid circuit is the same type of heat medium as the refrigerant in the refrigerant circuit. A device temperature control system for adjusting the temperature of the device,
A working fluid circuit (10) that constitutes a thermosiphon heat pipe and in which the working fluid circulates;
A coolant circuit (62) through which the coolant circulates;
Comprising a refrigeration cycle and a refrigerant circuit (22) through which the refrigerant circulates,
The working fluid circuit includes:
An evaporation section (12) in which the working fluid evaporates due to heat absorption from the device (BP);
A condenser (61) that cools and condenses the working fluid evaporated in the evaporator by heat exchange with the coolant in the coolant circuit;
The coolant circuit has a cooling unit (70) in which the coolant is cooled by heat exchange with the refrigerant in the coolant circuit,
The equipment temperature control system, wherein the working fluid in the working fluid circuit is the same type of heat medium as the refrigerant in the refrigerant circuit.   The said coolant circuit is an apparatus temperature control system of Claim 2 provided with a gas-liquid separator (60).

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