WO2019208726A1 - Dispositif de refroidissement - Google Patents

Dispositif de refroidissement Download PDF

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Publication number
WO2019208726A1
WO2019208726A1 PCT/JP2019/017773 JP2019017773W WO2019208726A1 WO 2019208726 A1 WO2019208726 A1 WO 2019208726A1 JP 2019017773 W JP2019017773 W JP 2019017773W WO 2019208726 A1 WO2019208726 A1 WO 2019208726A1
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WIPO (PCT)
Prior art keywords
refrigerant
liquid
gas
phase refrigerant
pipe
Prior art date
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PCT/JP2019/017773
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English (en)
Japanese (ja)
Inventor
功嗣 三浦
康光 大見
義則　毅
竹内　雅之
Original Assignee
株式会社デンソー
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Publication of WO2019208726A1 publication Critical patent/WO2019208726A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/02—Arrangement in connection with cooling of propulsion units with liquid cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/06—Control arrangements therefor
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/61—Types of temperature control
    • H01M10/613—Cooling or keeping cold
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries

Definitions

  • the present disclosure relates to a cooling device.
  • an evaporator for cooling a battery and a condenser provided on the upper side of the evaporator are annularly connected by two pipes, and a thermosiphon circuit in which a refrigerant is enclosed.
  • One of the two pipes forms a liquid phase refrigerant passage through which the liquid phase refrigerant flows from the condenser to the evaporator.
  • the other pipe other than the one of the two pipes forms a gas phase refrigerant passage through which the gas phase refrigerant flows from the evaporator to the condenser.
  • the liquid phase refrigerant in the evaporator absorbs heat from the battery and boils, and the battery is cooled by the latent heat of evaporation at that time.
  • the gas-phase refrigerant generated in the evaporator flows into the condenser through the gas-phase refrigerant passage.
  • the gas-phase refrigerant is cooled by the condenser and condensed.
  • the liquid phase refrigerant generated by the condenser flows into the evaporator through the liquid phase refrigerant passage by gravity. In this way, the refrigerant is circulated without power between the evaporator and the condenser to cool the battery.
  • the cross-sectional area of the gas-phase refrigerant flow path through which the gas-phase refrigerant flows is reduced in the gas-phase refrigerant passage. Therefore, the pressure loss generated when the gas-phase refrigerant flows from the evaporator to the condenser through the gas-phase refrigerant passage increases.
  • the head difference is a difference between the refrigerant liquid level in the evaporator and the refrigerant liquid level in the liquid phase refrigerant passage (or condenser).
  • This disclosure is intended to provide a cooling device with a small head difference.
  • a cooling device that circulates a refrigerant and cools an object to be cooled by a phase change between a liquid phase and a gas phase of the refrigerant, At least one evaporation unit for boiling the liquid phase refrigerant by transferring heat from the object to be cooled to the liquid phase refrigerant; A condensing part for condensing the gas-phase refrigerant by releasing heat from the gas-phase refrigerant; A liquid refrigerant pipe for circulating a liquid phase refrigerant from the condensing unit to at least one evaporation unit; A gas refrigerant pipe for circulating a gas-phase refrigerant from at least one evaporation section to the condensation section; A first connection part connected to the gas refrigerant pipe or at least one or more evaporation parts, and a liquid refrigerant pipe or at least one evaporation part connected to the first connection part and located below the gravity direction; A communication pipe having a second connection portion
  • FIG. 6 is a graph for assisting in explaining a decrease in head difference in the first embodiment. It is a figure which shows the whole structure of the cooling device in 2nd Embodiment. It is a figure which shows the whole structure of the cooling device in 3rd Embodiment. It is a figure which shows the whole structure of the cooling device in 4th Embodiment.
  • FIG. 39 is a view on arrow X in FIG. 38. It is sectional drawing which shows the structure of the liquid refrigerant capture part in 25th Embodiment. It is a Y arrow line view in FIG. It is a figure which shows the arrangement
  • the cooling device 10 of this embodiment shown in FIG. 1 is mounted on an electric vehicle such as an electric vehicle or a hybrid vehicle. And in this embodiment, the cooling device 10 cools the secondary battery 12 mounted in the electric vehicle. In other words, the object to be cooled that is cooled by the cooling device 10 is the secondary battery 12.
  • a power storage device in other words, a battery pack
  • the secondary battery 12 self-heats when power is output to the motor via the inverter.
  • a cooling device for maintaining the secondary battery 12 at a predetermined temperature or less is required.
  • the battery temperature rises not only when the vehicle is running but also during parking in summer.
  • the power storage device is often arranged under the floor of a vehicle, under a trunk room, and the like, and although the amount of heat per unit time given to the secondary battery 12 is small, the battery temperature gradually rises when left for a long time. If the secondary battery 12 is left in a high temperature state, the life of the secondary battery 12 is significantly reduced. Therefore, it is desired to maintain the battery temperature at a low temperature, for example, by cooling the secondary battery 12 while the vehicle is left.
  • the secondary battery 12 is configured as an assembled battery including a plurality of battery cells 121.
  • the temperature of each battery cell 121 varies, the deterioration of the battery cell 121 is biased, and the performance of the power storage device is reduced. It will decline. This is because the input / output characteristics of the power storage device are determined in accordance with the characteristics of the battery cell 121 that is most deteriorated. For this reason, in order for the power storage device to exhibit desired performance over a long period of time, temperature equalization that reduces temperature variations among the plurality of battery cells 121 is important.
  • blowing by a blower air cooling using a refrigeration cycle, water cooling, or a direct refrigerant cooling method has been generally used. Since only air is blown, the cooling capacity of the blower is low.
  • the secondary battery 12 is cooled by the sensible heat of the air by the blower, the temperature difference between the upstream and downstream of the air flow becomes large, and the temperature variation between the battery cells 121 cannot be sufficiently suppressed.
  • the cooling capacity is high in the refrigeration cycle method, since the heat exchanging portion with the battery cell 121 is sensible heat cooling by either air cooling or water cooling, similarly, the temperature variation between the battery cells 121 cannot be sufficiently suppressed.
  • the cooling device 10 of the present embodiment employs a thermosiphon system that cools the secondary battery 12 by natural circulation of refrigerant without using a compressor.
  • the cooling device 10 includes an evaporator 14, a condenser 16, a liquid refrigerant pipe 18, a gas refrigerant pipe 20, a liquid refrigerant capture unit 22, and a communication pipe 24.
  • the condenser 16, the liquid refrigerant pipe 18, the evaporator 14, and the gas refrigerant pipe 20 are connected in an annular shape to constitute a thermosiphon circuit 26 in which refrigerant as the refrigerant of the cooling device 10 circulates.
  • thermosiphon circuit 26 constitutes a thermosiphon that performs heat transfer by evaporation and condensation of the refrigerant.
  • the thermosiphon circuit 26 is configured to be a loop-type thermosiphon (in other words, a refrigerant circulation circuit) in which the flow path through which the gas-phase refrigerant flows and the flow path through which the liquid-phase refrigerant flow are separated. .
  • the vertical direction DR1 in FIG. 1 indicates the direction of gravity when the vehicle is mounted with the cooling device 10 in a state where the vehicle traveling direction and the vehicle width direction are parallel to the horizontal direction.
  • the upper side in the vertical direction DR1 indicates the upper side in the vertical direction of the vehicle, and the lower side in the vertical direction DR1 indicates the lower side in the vertical direction of the vehicle.
  • thermosiphon circuit 26 is filled with refrigerant.
  • the thermosiphon circuit 26 is filled with the refrigerant.
  • the refrigerant naturally circulates in the thermosiphon circuit 26 by evaporation and condensation, and the cooling device 10 adjusts the temperature of the secondary battery 12 by the phase change between the liquid phase and the gas phase of the refrigerant. Specifically, the secondary battery 12 is cooled by the phase change of the refrigerant.
  • the refrigerant filled in the thermosiphon circuit 26 is, for example, a fluorocarbon refrigerant such as HFO-1234yf or HFC-134a. Or you may use various working fluids other than Freon-type refrigerant
  • the evaporator 14 is a heat exchanger that cools the secondary battery 12 by exchanging heat between the secondary battery 12 and the refrigerant and transferring heat from the secondary battery 12 to the refrigerant.
  • the evaporator 14 is made of, for example, a metal having high thermal conductivity.
  • the evaporator 14 is an evaporation unit including tanks 14d and 14e and a heat exchange core 14f.
  • the tank 14d supplies the liquid phase refrigerant flowing in from the liquid refrigerant pipe 18 to the heat exchange core 14f.
  • the heat exchange core 14f cools the secondary battery 12 with the liquid phase refrigerant by heat exchange between the secondary battery 12 and the liquid phase refrigerant.
  • the tank 14 e guides the refrigerant from the heat exchange core 14 f to the gas refrigerant pipe 20.
  • the secondary battery 12 in FIG. 2 includes a plurality of battery cells 121.
  • the plurality of battery cells 121 are arranged side by side on the side surfaces 141a and 141b of the evaporator 14, respectively.
  • Each of the plurality of battery cells 121 is connected to the side surfaces 141a and 141b so as to be able to conduct heat between the side surfaces 141a and 141b of the heat exchange core 14f of the evaporator 14.
  • the side surfaces 141a and 141b of the evaporator 14 function as a battery cooling surface for cooling the secondary battery 12 as a vehicle-mounted battery.
  • An inlet 14b is formed in the tank 14d of the evaporator 14.
  • the inlet 14 b communicates the liquid refrigerant flow passage formed in the liquid refrigerant pipe 18 into the tank 14 d of the evaporator 14. Therefore, when the refrigerant circulates through the thermosiphon circuit 26, the refrigerant in the liquid refrigerant flow passage flows into the tank 14d of the evaporator 14 through the inlet 14b.
  • the liquid refrigerant flow passage is a refrigerant flow path for allowing the refrigerant to flow from the condenser 16 as the condensing unit to the evaporator 14.
  • the inlet 14b of the evaporator 14 is provided, for example, at one end of the evaporator 14 in the battery stacking direction DR2.
  • an outlet 14c is formed in the tank 14e of the evaporator 14.
  • the outlet 14 c of the evaporator 14 connects the gas refrigerant flow passage formed in the gas refrigerant pipe 20 into the evaporator 14. Therefore, when the refrigerant circulates through the thermosiphon circuit 26, the refrigerant in the evaporator 14 goes out from the tank 14e to the gas refrigerant flow passage through the outlet 14c.
  • the gas refrigerant flow passage is a refrigerant flow path for flowing the refrigerant from the evaporator 14 to the condenser 16.
  • the outlet 14c of the evaporator 14 is provided at the other end of the evaporator 14 in the battery stacking direction DR2.
  • the evaporator 14 has a structure (not shown) that allows the gas-phase refrigerant to exit exclusively from the outlet 14c of the inlet 14b and the outlet 14c.
  • the condenser 16 is a heat exchanger that exchanges heat between the refrigerant in the condenser 16 and the heat receiving fluid to dissipate heat from the refrigerant to the heat receiving fluid. Specifically, the gas phase refrigerant flows into the condenser 16 through the inlet 16a from the gas refrigerant pipe 20, and the condenser 16 condenses the refrigerant by dissipating heat from the refrigerant to the heat receiving fluid.
  • the heat-receiving fluid that exchanges heat with the refrigerant in the condenser 16 is, for example, air (that is, air outside the passenger compartment) or water.
  • the condenser 16 is disposed above the evaporator 14 in the vertical direction.
  • a liquid refrigerant pipe 18 is connected to the lower outlet 16b of the condenser 16 in the vertical direction, and a gas refrigerant pipe 20 is connected to the upper inlet 16a of the condenser 16 in the vertical direction DR1.
  • the lower side in the vertical direction DR1 means the lower side in the gravity direction.
  • liquid refrigerant pipe 18 is connected to the condenser 16 below the gas refrigerant pipe 20 in the vertical direction DR1.
  • liquid phase refrigerant condensed in the condenser 16 flows from the condenser 16 to the liquid refrigerant flow path by gravity.
  • the liquid refrigerant capturing unit 22 is provided in the gas refrigerant pipe 20 between the outlet 14 c of the evaporator 14 and the inlet 16 a of the condenser 16.
  • a pipe located on the evaporator 14 side with respect to the liquid refrigerant capture unit 22 in the gas refrigerant pipe 20 is referred to as a lower gas pipe 20a, and a condenser 16 side with respect to the liquid refrigerant capture unit 22 in the gas refrigerant pipe 20 is used.
  • the pipe located in the upper gas pipe 20b is a pipe located on the evaporator 14 side with respect to the liquid refrigerant capture unit 22 in the gas refrigerant pipe 20.
  • the liquid refrigerant capture unit 22 includes an inlet 22a that communicates with the lower gas pipe 20a, a gas refrigerant outlet 22b that communicates with the upper gas pipe 20b, and a liquid refrigerant outlet 22c that communicates with the inlet of the communication pipe 24.
  • the outlet of the communication pipe 24 is in communication with the lowermost side in the vertical direction DR1 in the liquid refrigerant pipe 18.
  • the liquid refrigerant capturing unit 22 separates the liquid phase refrigerant and the gas phase refrigerant flowing from the outlet 14c of the evaporator 14 from the upper gas pipe 20b to capture the liquid phase refrigerant, and guides the liquid phase refrigerant to the communication pipe 24.
  • the gas-phase refrigerant is guided to the upper gas pipe 20b. That is, the liquid refrigerant capturing unit 22 captures the liquid phase refrigerant before the liquid phase refrigerant that has risen from the outlet 14 c of the evaporator 14 reaches the condenser 16.
  • the liquid refrigerant capture unit 22 constitutes a tank having a larger refrigerant flow cross-sectional area than the lower gas pipe 20a. For this reason, the liquid refrigerant capturing unit 22 plays a role of separating the liquid-phase refrigerant and the gas-phase refrigerant by reducing the flow rate of the refrigerant rather than the flow rate of the refrigerant in the lower gas pipe 20a.
  • the gas refrigerant outlet 22b is located on the upper side in the vertical direction DR1 in the liquid refrigerant capturing part 22.
  • the liquid refrigerant outlet 22c is located on the lower side in the vertical direction DR1 in the liquid refrigerant capturing portion 22.
  • the inlet 22a is located between the gas refrigerant outlet 22b and the liquid refrigerant outlet 22c in the vertical direction DR1 in the liquid refrigerant trapping portion 22.
  • connection part 24 a as the first connection part connected to the liquid refrigerant capturing part 22 in the communication pipe 24 is vertically above the connection part 24 b connected to the liquid refrigerant pipe 18 in the communication pipe 24. It is located above the direction DR1.
  • the liquid refrigerant capturing unit 22 constitutes a part of the gas refrigerant pipe 20.
  • the connection part 24 a connected to the liquid refrigerant capturing part 22 in the communication pipe 24 constitutes a connection part connected to the gas refrigerant pipe 20 in the communication pipe 24.
  • connection portion 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is positioned above the vertical direction DR1 with respect to the connection section 24b connected to the liquid refrigerant pipe 18 in the communication pipe 24.
  • thermosiphon circuit 26 is filled with a refrigerant so that the liquid level is located in or on the heat exchange core 14f of the evaporator 14.
  • the liquid phase refrigerant liquid level Ha in the liquid refrigerant pipe 18 is positioned above the liquid phase refrigerant liquid level Hb in the evaporator 14 in the vertical direction DR1.
  • the liquid phase refrigerant liquid level Hb in the evaporator 14 here, the liquid phase refrigerant gasifies and blows up inside the evaporator 14, and the liquid level cannot actually be observed.
  • the liquid level Hb of the liquid phase refrigerant indicates a theoretical equivalent liquid level defined by the pressure balance.
  • the volume of the liquid phase refrigerant containing bubbles becomes larger than the volume of the liquid phase refrigerant not containing bubbles when the heat exchange is stopped. Therefore, the liquid level of the apparent liquid phase refrigerant is raised from the liquid level at the time of stoppage in the evaporator 14.
  • the liquid level at the time of stop means the liquid level of the liquid phase refrigerant in a state where heat exchange is stopped in the evaporator 14. Further, when the gas-phase refrigerant rises, part of the pushed up liquid-phase refrigerant flows into the tank 14e and then flows into the gas refrigerant pipe 20.
  • the liquid refrigerant including the gas refrigerant and bubbles rises as a gas-liquid mixed flow.
  • the gas-liquid mixed flow flows into the liquid refrigerant capturing unit 22 through the lower gas pipe 20a and the inlet 22a.
  • the flow velocity of the gas-liquid mixed flow in the liquid refrigerant capturing unit 22 is reduced as compared with the case where the gas-liquid mixed flow flows in the lower gas pipe 20a. To do. For this reason, in the liquid refrigerant capturing unit 22, the liquid-phase refrigerant and the gas-phase refrigerant are separated from the gas-liquid mixed flow.
  • the gas-phase refrigerant rises and moves to the condenser 16 through the gas refrigerant outlet 22b and the upper gas pipe 20b.
  • the gas-phase refrigerant is indicated as “gas”.
  • the gas phase refrigerant radiates heat to the heat receiving fluid, so that the gas phase refrigerant is condensed.
  • the condensed liquid phase refrigerant flows into the liquid refrigerant flow passage of the liquid refrigerant pipe 18 due to gravity.
  • the liquid phase refrigerant falls due to gravity and flows from the liquid refrigerant outlet 22c to the liquid refrigerant flow passage of the liquid refrigerant pipe 18 through the communication flow path of the communication pipe 24.
  • the liquid phase refrigerant is indicated as “liquid”.
  • liquid phase refrigerant from the condenser 16 and the liquid phase refrigerant flowing from the liquid refrigerant capturing portion 22 through the communication flow path of the communication pipe 24 merge in the liquid refrigerant flow path of the liquid refrigerant pipe 18 and flow to the evaporator 14.
  • these operations are performed by natural circulation of the refrigerant sealed in the thermosiphon circuit 26 without the need for a driving device such as a compressor.
  • Natural circulation is that the refrigerant circulates in the thermosiphon circuit 26 due to boiling and condensation caused by the temperature difference between the condenser 16 and the evaporator 14.
  • the liquid-phase refrigerant is captured by the liquid-refrigerant capturing unit 22 among the gas-phase refrigerant and the liquid-phase refrigerant that have risen from the evaporator 14. Then, the captured liquid phase refrigerant is returned to the evaporator 14 through the communication flow path of the communication pipe 24 and the liquid refrigerant flow path of the liquid refrigerant pipe 18.
  • the cooling device 10 is a cooling device that circulates the refrigerant and cools the secondary battery 12 by a phase change between the liquid phase and the gas phase of the refrigerant.
  • the cooling device 10 includes an evaporator 14 for boiling the liquid phase refrigerant by transferring heat from the secondary battery 12 to the liquid phase refrigerant, and a condenser 16 for condensing the gas phase refrigerant by releasing heat from the gas phase refrigerant.
  • the cooling device 10 includes a liquid refrigerant pipe 18 through which liquid phase refrigerant flows from the condenser 16 to the evaporator 14, and a gas refrigerant pipe 20 through which gas phase refrigerant flows from the evaporator 14 to the condenser 16.
  • a liquid refrigerant capturing unit 22 that captures the liquid phase refrigerant before reaching the vessel 16 and a communication pipe 24 are provided.
  • connection part 24a connected to the liquid refrigerant capturing part 22 in the communication pipe 24 is positioned above the vertical direction DR1 with respect to the connection part 24b as the second connection part connected to the liquid refrigerant pipe 18 in the communication pipe 24. To do.
  • the liquid refrigerant is captured by the liquid refrigerant capturing unit 22 before the liquid refrigerant raised from the evaporator 14 by the bubbles reaches the condenser 16.
  • the communication pipe 24 can move the liquid-phase refrigerant captured by the liquid refrigerant capturing unit 22 from the connection unit 24a side to the connection unit 24b side.
  • the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 can be returned to the evaporator 14.
  • thermosiphon circuit 26 in order to circulate the refrigerant, the liquid level refrigerant liquid level Ha in the liquid refrigerant pipe 18 is positioned above the liquid phase refrigerant liquid level Hb in the evaporator 14 in the vertical direction DR1. is required.
  • the head difference ( Ha ⁇ Hb), which is the difference between the liquid level refrigerant level Ha in the liquid refrigerant pipe 18 and the liquid level refrigerant level Hb in the evaporator 14, causes the refrigerant to circulate through the thermosiphon circuit 26. It depends on the pressure loss that occurs when
  • liquid level refrigerant liquid level Hb in the evaporator 14 the liquid phase refrigerant gasifies and blows up in the evaporator 14, and the liquid level cannot actually be observed.
  • the liquid level Hb of the liquid phase refrigerant indicates a theoretical equivalent liquid level defined by the pressure balance.
  • the cross-sectional area of the gas-phase refrigerant channel refers to the cross-sectional area of the refrigerant channel through which the gas-phase refrigerant flows in the gas refrigerant pipe 20.
  • C In the gas refrigerant pipe 20, the liquid-phase refrigerant descends along the inner surface thereof, and the gas-phase refrigerant rises radially inward of the liquid-phase refrigerant. Be inhibited. For this reason, the pressure loss generated when the gas-phase refrigerant flows through the gas refrigerant pipe 20 increases.
  • the liquid refrigerant raised by the bubbles from the evaporator 14 is captured by the liquid refrigerant capturing unit 22 before reaching the condenser 16 by the communication pipe 24,
  • the captured liquid phase refrigerant can be returned to the evaporator 14 through the communication pipe 24. For this reason, only the gas phase refrigerant out of the liquid phase refrigerant and the gas phase refrigerant flows through the upper gas pipe 20b.
  • the head difference can be reduced. For this reason, the height of the condenser 16 with respect to the evaporator 14 can be lowered
  • the head difference can be reduced. Accordingly, even when a large amount of heat is transferred from the secondary battery 12 to the evaporator 14 and a large amount of liquid phase refrigerant is generated in the condenser 16, the liquid level refrigerant liquid level Ha in the liquid refrigerant pipe 18 is reduced in the condenser 16. Can be suppressed. Therefore, it can suppress that condensation performance falls because a part of condenser 16 is satisfy
  • the liquid surface Ha of the liquid phase refrigerant can be kept in the condenser 16 or less, that is, in the liquid refrigerant pipe 18. For this reason, the cooling performance in the cooling device 10 can be improved.
  • the performance of condensing the gas phase refrigerant in the condenser 16 is deteriorated.
  • the liquid refrigerant flowing through the lower gas pipe 20 a is captured by the liquid refrigerant capturing unit 22, the liquid refrigerant is suppressed from flowing into the condenser 16. For this reason, it can suppress that the performance which condenses a gaseous-phase refrigerant
  • the liquid-phase refrigerant that has risen due to the bubbles from the evaporator 14 is captured by the liquid-refrigerant capturing unit 22 and returned to the evaporator 14, so that the amount of liquid-phase refrigerant in the evaporator 14 is ensured. be able to. For this reason, the cooling capacity of the secondary battery 12 can be ensured in the evaporator 14.
  • the gas refrigerant outlet 22b is opened to the upper side in the vertical direction DR1 in the liquid refrigerant capturing part 22. For this reason, a gaseous-phase refrigerant
  • coolant can be favorably flowed from the liquid refrigerant capture part 22 to the upper side gas piping 20b.
  • the liquid refrigerant outlet 22c is opened to the lower side in the vertical direction DR1 in the liquid refrigerant capturing portion 22. For this reason, the liquid-phase refrigerant can be favorably flowed from the liquid refrigerant capturing unit 22 to the communication pipe 24.
  • the comparative cooling device 10 ⁇ / b> A is a cooling device that does not include the liquid refrigerant capturing unit 22 and the communication pipe 24.
  • the vertical axis is the head difference
  • the horizontal axis is the cooling capacity [KW]
  • Ga is a graph showing the head difference of the cooling device 10 of the present embodiment
  • Gb is the head difference of the cooling device 10 ⁇ / b> A in comparison. It is a graph to show.
  • the head difference of the cooling device 10 of the present embodiment is smaller than the head difference of the cooling device 10A in comparison.
  • the difference between the head difference of the cooling device 10 ⁇ / b> A and the head difference of the cooling device 10 according to the present embodiment increases as the cooling capacity increases. That is, it can be seen that the head difference of the cooling device 10 of the present embodiment can be significantly reduced as the cooling capacity increases, based on the head difference of the cooling device 10 ⁇ / b> A in comparison.
  • the present embodiment and the first embodiment are mainly different in the presence / absence of the communication pipe 24 and the configuration of the liquid refrigerant capturing unit 22.
  • the configuration of the liquid refrigerant capturing unit 22 will be described.
  • the liquid refrigerant capture unit 22 of the present embodiment protrudes radially inward from the inner surface of the gas refrigerant pipe 20 to block the liquid phase refrigerant.
  • the liquid refrigerant capturing part 22 is a weir part that is formed in an annular shape and constitutes a gas phase refrigerant flow path 22f that circulates the gas phase refrigerant radially inward.
  • bubbles are generated from the inside of the liquid-phase refrigerant and flow to the rear stream while growing (that is, in the case of the present embodiment, toward the Tian district improvement side). Then, after the bubbles grow to a certain size, they move from the inside of the evaporator 14 into the gas refrigerant flow passage of the gas refrigerant pipe 20 through the outlet 14c as a gas phase refrigerant.
  • the liquid-phase refrigerant is pushed up when the gas-phase refrigerant rises in the heat exchange core 14f of the evaporator 14, and part of the refrigerant flows into the gas refrigerant flow passage of the gas refrigerant pipe 20.
  • the liquid-phase refrigerant containing the liquid rises as a gas-liquid mixed flow.
  • the liquid-phase refrigerant in the gas-liquid mixed flow is captured by the liquid refrigerant capturing unit 22, and the gas-phase refrigerant in the gas-liquid mixed flow moves to the condenser 16 through the gas-phase refrigerant flow path 22f and the upper gas pipe 20b. .
  • the gas phase refrigerant radiates heat to the heat receiving fluid, so that the gas phase refrigerant is condensed.
  • the condensed liquid phase refrigerant flows into the liquid refrigerant flow passage of the liquid refrigerant pipe 18 due to gravity. Thereafter, the liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • these operations are performed by natural circulation of the refrigerant sealed in the thermosiphon circuit 26 without the need for a driving device such as a compressor.
  • the cooling device 10 includes the evaporator 14 for boiling the liquid phase refrigerant by transferring the heat from the secondary battery 12 to the liquid phase refrigerant, and the air by releasing the heat from the gas phase refrigerant. And a condenser 16 for condensing the phase refrigerant.
  • the cooling device 10 includes a liquid refrigerant pipe 18 through which liquid phase refrigerant flows from the condenser 16 to the evaporator 14, and a gas refrigerant pipe 20 through which gas phase refrigerant flows from the evaporator 14 to the condenser 16.
  • the cooling device 10 condenses the moved liquid phase refrigerant.
  • a liquid refrigerant capturing unit 22 that captures the liquid phase refrigerant before reaching the vessel 16 is provided.
  • the cooling device 10 of the present embodiment is not provided with the communication pipe 24.
  • the liquid refrigerant rising from the evaporator 14 by the bubbles is captured by the liquid refrigerant capturing unit 22 through the communication pipe 24.
  • the gas phase refrigerant out of the liquid phase refrigerant and the gas phase refrigerant flows through the upper gas pipe 20b.
  • the loss of energy required to circulate the refrigerant is reduced.
  • the pressure loss generated when the gas-phase refrigerant flows through the gas refrigerant pipe 20 is reduced. As described above, the head difference can be reduced.
  • the liquid refrigerant flowing through the lower gas pipe 20a is captured by the liquid refrigerant capturing unit 22, the liquid refrigerant is suppressed from flowing into the condenser 16. For this reason, it can suppress that the performance which condenses a gaseous-phase refrigerant
  • the cooling device 10 of the present embodiment has a configuration in which the liquid refrigerant capturing unit 22 is omitted from the cooling device 10 of the first embodiment.
  • FIG. 7 the same reference numerals as those in FIG.
  • connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is positioned above the vertical direction DR1 with respect to the connection part 24b connected to the liquid refrigerant pipe 18 in the communication pipe 24. become.
  • the connecting part 24a is located above the evaporator 14 in the up and down direction DR1.
  • the connection part 24b is located below the condenser 16 in the vertical direction DR1.
  • bubbles are generated from the inside of the liquid-phase refrigerant and flow to the rear stream while growing (that is, in the case of the present embodiment, toward the Tian district improvement side). Then, after the bubbles grow to a certain size, they move from the inside of the evaporator 14 into the gas refrigerant flow passage of the gas refrigerant pipe 20 through the outlet 14c as a gas phase refrigerant.
  • the liquid-phase refrigerant is pushed up when the gas-phase refrigerant rises in the heat exchange core 14f of the evaporator 14, and part of the refrigerant flows into the gas refrigerant flow passage of the gas refrigerant pipe 20.
  • the liquid-phase refrigerant containing the liquid rises as a gas-liquid mixed flow.
  • the liquid-phase refrigerant in the gas-liquid mixed flow flowing in the lower gas pipe 20a flows through the communication flow path of the communication pipe 24 to the liquid refrigerant flow path of the liquid refrigerant pipe 18 due to gravity.
  • the gas-phase refrigerant in the gas-liquid mixed flow flowing in the lower gas pipe 20a moves to the condenser 16 through the upper gas pipe 20b.
  • the gas phase refrigerant radiates heat to the heat receiving fluid, so that the gas phase refrigerant is condensed.
  • the condensed liquid phase refrigerant flows into the liquid refrigerant flow passage of the liquid refrigerant pipe 18 due to gravity.
  • liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • these operations are performed by natural circulation of the refrigerant sealed in the thermosiphon circuit 26 without the need for a driving device such as a compressor.
  • the cooling device 10 includes the evaporator 14 for boiling the liquid phase refrigerant by transferring the heat from the secondary battery 12 to the liquid phase refrigerant, and the air by releasing the heat from the gas phase refrigerant. And a condenser 16 for condensing the phase refrigerant.
  • the cooling device 10 includes a liquid refrigerant pipe 18 through which liquid phase refrigerant flows from the condenser 16 to the evaporator 14, and a gas refrigerant pipe 20 through which gas phase refrigerant flows from the evaporator 14 to the condenser 16.
  • the cooling device 10 condenses the moved liquid phase refrigerant. Before reaching the vessel 16, the liquid phase refrigerant is returned to the liquid refrigerant flow path of the liquid refrigerant pipe 18.
  • the cooling device 10 of the present embodiment is not provided with the liquid refrigerant capturing unit 22.
  • the liquid-phase refrigerant that has risen from the evaporator 14 by the bubbles through the communication pipe 24 is returned to the liquid refrigerant flow path of the liquid refrigerant pipe 18.
  • the gas phase refrigerant out of the liquid phase refrigerant and the gas phase refrigerant flows through the upper gas pipe 20b.
  • the loss of energy required to circulate the refrigerant is reduced.
  • the pressure loss generated when the gas-phase refrigerant flows through the gas refrigerant pipe 20 is reduced. As described above, the head difference can be reduced.
  • the liquid phase refrigerant flowing through the lower gas pipe 20a is returned to the liquid refrigerant flow path of the liquid refrigerant pipe 18 through the communication pipe 24, so that the liquid phase refrigerant is prevented from flowing into the condenser 16. .
  • it can suppress that the performance which condenses a gaseous-phase refrigerant
  • connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is arranged below the condenser 16 in the vertical direction DR1 has been described.
  • the fourth embodiment referring to FIG. 8 for an example in which the connection portion 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is arranged above the condenser 16 in the vertical direction DR1. I will explain.
  • the present embodiment and the third embodiment are the same except for the position of the connecting portion 24a connected to the gas refrigerant pipe 20 in the communication pipe 24.
  • the same reference numerals as those in FIG. 8 are the same reference numerals as those in FIG.
  • connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 of the present embodiment is disposed above the evaporator 14 in the vertical direction DR1. That is, the connection part 24 a of the communication pipe 24 is connected to the highest part of the gas refrigerant pipe 20.
  • the connection portion 24 b of the communication pipe 24 is connected to the lowest part of the liquid refrigerant pipe 18.
  • the cooling device 10 includes the evaporator 14, the condenser 16, the liquid refrigerant pipe 18, the gas refrigerant pipe 20, and the communication pipe 24 as in the third embodiment.
  • the connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is located above the connection part 24b connected to the liquid refrigerant pipe 18 in the communication pipe 24 in the vertical direction DR1. For this reason, the head difference can be reduced as in the third embodiment.
  • connection part 24a connected to the gas refrigerant piping 20 among the communication piping 24 demonstrated the example arrange
  • connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is arranged at almost the same height as the tank 14e of the evaporator 14 (that is, at the same position in the gravity direction GR1). An example will be described with reference to FIG.
  • the present embodiment and the third embodiment are the same except for the position of the connecting portion 24a connected to the gas refrigerant pipe 20 in the communication pipe 24. 9, the same reference numerals as those in FIG. 1 denote the same components, and the description thereof is omitted.
  • connection pipe 24 is connected to the liquid refrigerant pipe 18 in the communication pipe 24 and is located above the vertical direction DR1. For this reason, the cooling device 10 of the present embodiment can reduce the head difference as in the third embodiment.
  • connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is disposed at substantially the same height as the tank 14e of the evaporator 14 has been described.
  • connection portion 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is arranged at the height between the lowermost part and the uppermost part of the condenser 16 will be described with reference to FIG. explain.
  • the present embodiment and the fifth embodiment are the same except for the position of the connecting portion 24a connected to the gas refrigerant pipe 20 in the communication pipe 24. 10, the same reference numerals as those in FIG. 1 denote the same components, and the description thereof is omitted.
  • the connecting portion 24 a of the communication pipe 24 is connected to a lower part than the highest part of the gas refrigerant pipe 20.
  • the connection part 24 b of the communication pipe 24 is connected to a part higher than the lowest part of the liquid refrigerant pipe 18.
  • the cooling device 10 of the present embodiment can reduce the head difference as in the fifth embodiment.
  • the present embodiment and the first embodiment are the same except for the arrangement of the communication pipe 24. 10, the same reference numerals as those in FIG. 1 denote the same components, and the description thereof is omitted.
  • the upper end of the communication pipe 24 is connected to the tank 14d, and the lower end of the communication pipe 24 is connected to the tank 14e.
  • the connection part 24a connected to the tank 14d in the communication pipe 24 is located above the connection part 24b connected to the tank 14e in the communication pipe 24 in the gravity direction.
  • bubbles are generated from the inside of the liquid-phase refrigerant and flow to the rear stream while growing (that is, in the case of the present embodiment, toward the Tian district improvement side).
  • the bubbles grow to a certain size and then flow into the tank 14d from the heat exchange core 14f as a gas phase refrigerant.
  • the liquid-phase refrigerant is pushed up when the gas-phase refrigerant rises in the heat exchange core 14f of the evaporator 14, the gas-liquid mixed flow of the gas-phase refrigerant and the liquid-phase refrigerant containing bubbles from the heat exchange core 14f. Ascend to tank 14d.
  • the liquid refrigerant flows from the tank 14e to the tank 14d through the communication channel of the communication pipe 24.
  • the gas phase refrigerant moves from the inside of the tank 14 e of the evaporator 14 to the condenser 16 through the outlet 14 c and the gas refrigerant flow passage of the gas refrigerant pipe 20.
  • the gas phase refrigerant radiates heat to the heat receiving fluid, so that the gas phase refrigerant is condensed.
  • the condensed liquid phase refrigerant flows into the liquid refrigerant flow passage of the liquid refrigerant pipe 18 due to gravity. Thereafter, the liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • the liquid phase refrigerant flowing from the tank 14e through the communication flow path of the communication pipe 24 and the liquid phase refrigerant flowing from the liquid refrigerant flow path of the liquid refrigerant pipe 18 flow to the tank 14d. .
  • the cooling device 10 of the present embodiment described above is configured in the same manner as the above-described sixth embodiment, except that the arrangement of the communication pipes 24 is different. For this reason, the head difference can be reduced as in the sixth embodiment.
  • the uppermost part of the evaporator 14 and the uppermost part of the condenser 16 are arranged at the same height.
  • the lowermost part of the evaporator 14 and the lowermost part of the condenser 16 are arranged at the same height.
  • the outlet 14c of the evaporator 14 and the inlet 16a of the condenser 16 are arranged at the same height.
  • the inlet 14b of the evaporator 14 and the outlet 16b of the condenser 16 are arranged at the same height.
  • the gas refrigerant pipe 20 is arranged so as to extend straight between the outlet 14 c of the evaporator 14 and the inlet 16 a of the condenser 16.
  • a liquid refrigerant pipe 18 is disposed between the inlet 14b of the evaporator 14 and the outlet 16b of the condenser 16 so as to extend straight.
  • the communication pipe 24 is disposed between the gas refrigerant pipe 20 and the liquid refrigerant pipe 18 as in the first embodiment.
  • the connection part 24a connected to the gas refrigerant pipe 20 in the communication pipe 24 is located above the connection part 24b connected to the liquid refrigerant pipe 18 in the communication pipe 24 in the vertical direction DR1.
  • the head difference is set based on the pressure loss of the thermosiphon circuit 26 as in the first embodiment, the evaporator 14 and the condenser 16 may be connected.
  • the refrigerant circulates. Therefore, according to the present embodiment described above, the head difference can be reduced as in the first embodiment.
  • connection portion 24 a in which the evaporator 14 and the condenser 16 are arranged at the same height and connected to the gas refrigerant pipe 20 in the communication pipe 24 is included in the communication pipe 24. It is located on the upper side in the vertical direction DR1 with respect to the connecting portion 24b connected to the liquid refrigerant pipe 18.
  • the refrigerant circulates between the evaporator 14 and the condenser 16 as in the eighth embodiment. Therefore, the head difference can be reduced as in the eighth embodiment.
  • the present embodiment and the first embodiment are mainly the same except for the presence or absence of the flow rate adjustment valve 30. 10, the same reference numerals as those in FIG. 1 denote the same components, and the description thereof is omitted.
  • the flow rate adjusting valve 30 is disposed between the connection portions 24a and 24b in the communication pipe 24.
  • the flow rate adjustment valve 30 is an adjustment unit that adjusts the flow of the liquid-phase refrigerant amount flowing through the communication pipe 24.
  • the flow rate adjusting valve 30 is a motor-operated valve configured to be able to adjust the cross-sectional area of the communication flow path between the connecting portions 24a and 24b in a plurality of stages.
  • the cross-sectional area of the communication channel between the connecting portions 24a and 24b is simply referred to as a communication channel cross-sectional area.
  • the flow rate adjusting valve 30 is controlled by the electronic control unit 40 of FIG.
  • the electronic control unit 40 performs a valve control process to prevent the liquid phase refrigerant from blowing up from the liquid refrigerant pipe 18 to the liquid refrigerant capturing unit 22 through the communication pipe 24.
  • the height of the liquid level Ha of the liquid refrigerant pipe 18 increases as the calorific value of the secondary battery 12 increases. For this reason, the height of the liquid surface Ha of the liquid refrigerant pipe 18 and the cooling amount of the secondary battery 12 have a one-to-one relationship.
  • the electronic control unit 40 calculates the cooling amount of the secondary battery 12 based on the heat generation amount of the secondary battery 12 calculated by the battery heat generation amount estimation unit 41, and this calculation.
  • the head which is the height of the liquid level Ha of the liquid refrigerant pipe 18 is obtained based on the amount of cooling to be performed.
  • the electronic control unit 40 controls the flow rate adjusting valve 30 according to the required head when executing the valve control process.
  • the battery heat generation amount estimation unit 41 includes a current sensor that measures a charging current value charged in the secondary battery 12 or a discharging current value discharged from the secondary battery 12.
  • the battery heat generation amount estimation unit 41 calculates the heat generation amount of the secondary battery 12 based on the charging current value measured by the current sensor and the internal resistance of the secondary battery 12.
  • the battery heat generation amount estimation unit 41 calculates the heat generation amount of the secondary battery 12 based on the discharge current value measured by the current sensor and the internal resistance of the secondary battery 12.
  • the electronic control unit 40 assumes that the heat generation amount of the secondary battery 12 is the same as the cooling amount of the secondary battery 12, and cools the secondary battery 12 based on the calculated value of the battery heat generation amount estimation unit 41. Calculate the amount.
  • the cooling amount calculated from the difference between the temperature of the secondary battery 12 and the refrigerant saturation temperature, the required cooling capacity of the secondary battery 12, Use the cooling amount of the condenser. In addition, it may be calculated using the refrigerant flow rate, the pressure loss of the refrigerant, the amount of power consumption in the battery, and the like.
  • the electronic control unit 40 executes valve control processing according to the flowchart of FIG.
  • the electronic control unit 40 repeatedly executes the valve control process when heat is exchanged between the secondary battery 12 and the evaporator 14.
  • the flow rate of the refrigerant circulating through the thermosiphon circuit 26 increases, so that the refrigerant circulation pressure loss increases. For this reason, the head of the liquid refrigerant pipe 18 (that is, the height of the liquid surface Ha of the liquid refrigerant pipe 18) rises.
  • liquid-phase refrigerant is likely to blow up from the liquid refrigerant pipe 18 to the liquid refrigerant capturing portion 22 through the communication pipe 24.
  • the electronic control device 40 of the present embodiment calculates the heat generation amount (that is, the cooling amount) of the secondary battery 12 at regular intervals based on the calculation result of the battery heat generation amount estimation unit 41, and the heat generation amount The head is calculated for each calculation.
  • the electronic control unit 40 calculates a head for every predetermined period based on the calculation result of the battery heat generation amount estimation unit 41, and determines whether or not the head calculated this time is higher than the head calculated last time (step). S100).
  • step S100 when it is determined YES in step S100 that the head calculated this time has risen from the previously calculated head, the flow rate control valve 30 is controlled as the flow rate control unit to reduce the communication flow path cross-sectional area (step S110). ).
  • the liquid-phase refrigerant can be stored in the upper communication pipe 24c. For this reason, it is possible to prevent the liquid surface Ha of the liquid refrigerant pipe 18 from becoming excessively high.
  • step S100 determines whether the currently calculated head has not risen from the previously calculated head. If it is determined in step S100 that the currently calculated head has not risen from the previously calculated head, the determination is NO (step S120). ).
  • step S120 when it is determined YES in step S120 that the head calculated this time is lower than the previously calculated head, the flow rate control valve 30 is controlled as the flow rate control unit to increase the communication flow path cross-sectional area (step S130). ).
  • the flow rate adjustment valve 30 is connected to the liquid phase refrigerant in the liquid refrigerant trap 22 or the above-described upper side.
  • the liquid refrigerant stored in the communication pipe 24c is allowed to flow to the lower communication pipe 24d.
  • liquid phase refrigerant in the liquid refrigerant trapping section 22 and the liquid phase refrigerant stored in the above-described upper communication pipe 24c are caused by gravity through the flow rate adjusting valve 30, the lower communication pipe 24d, and the liquid refrigerant pipe 18 to the evaporator 14. Can be returned to.
  • step S120 if the head calculated this time is the same as the head calculated last time, NO is determined and the process returns to step S100.
  • the electronic control unit 40 calculates the head for every predetermined period in the calculation result of the battery heat generation amount estimation unit 41, and when the calculated head is higher than the previously calculated head, the flow rate adjustment valve 30 is controlled to reduce the cross-sectional area of the communication channel. On the other hand, when the head calculated this time is lower than the head calculated last time, the flow rate adjusting valve 30 is controlled to increase the communication flow path cross-sectional area.
  • the communication channel cross-sectional area is adjusted according to the displacement of the head, and the liquid refrigerant capture unit 22 is prevented from being blown from the liquid refrigerant pipe 18 to the liquid refrigerant capture unit 22 through the communication pipe 24.
  • the liquid phase refrigerant is allowed to flow to the liquid refrigerant pipe 18 through the communication pipe 24.
  • the communication pipe 24 of the present embodiment causes the liquid refrigerant flowing in the lower gas pipe 20a to flow through the liquid refrigerant flow passage of the liquid refrigerant pipe 18 by gravity.
  • the flow rate adjustment valve 30 is controlled by the electronic control unit 40 to adjust the communication flow path cross-sectional area, as in the tenth embodiment.
  • This embodiment is different from the tenth embodiment only in that an on-off valve 30A instead of the flow rate adjustment valve 30 is provided, and other configurations are common.
  • the same reference numerals as those in FIG. 14 denote the same components, and the description thereof is omitted.
  • the on-off valve 30 ⁇ / b> A is an adjustment unit that adjusts the flow of the liquid-phase refrigerant flowing through the communication pipe 24.
  • the on-off valve 30 ⁇ / b> A is controlled by the electronic control unit 40 and set to one of an open state and a closed state of the communication pipe 24.
  • the electronic control device 40 of the present embodiment uses the on-off valve 30A to perform valve control processing to prevent the liquid-phase refrigerant from blowing up from the liquid refrigerant pipe 18 to the liquid refrigerant trap 22 through the communication pipe 24.
  • the electronic control unit 40 cools the secondary battery 12 based on the heat generation amount of the secondary battery 12 calculated by the battery heat generation amount estimation unit 41 as in the tenth embodiment. Calculate the amount.
  • the electronic control unit 40 calculates the head of the liquid refrigerant pipe 18 based on the calculated cooling amount, and controls the on-off valve 30A according to the calculated head.
  • the electronic control unit 40 assumes that the heat generation amount of the secondary battery 12 is the same as the cooling amount of the secondary battery 12, and cools the secondary battery 12 based on the calculated value of the battery heat generation amount estimation unit 41. Calculate the amount.
  • the cooling amount of the secondary battery 12 is the cooling amount calculated from the difference between the temperature of the secondary battery 12 and the refrigerant saturation temperature, the required cooling capacity of the secondary battery 12, and the current value charged and discharged from the secondary battery.
  • the heat generation amount of the battery calculated by the internal resistance of the secondary battery and the cooling amount of the condenser are used.
  • the calculation may be performed using the refrigerant flow rate, the refrigerant pressure loss, the power consumption in the battery, and the like.
  • the electronic control unit 40 executes valve control processing according to the flowchart of FIG.
  • the electronic control unit 40 repeatedly executes the valve control process when heat is exchanged between the secondary battery 12 and the evaporator 14.
  • the electronic control unit 40 calculates the heat generation amount of the secondary battery 12 at regular intervals by the battery heat generation amount estimation unit 41, calculates the cooling amount based on the heat generation amount for each calculation, and the head based on the cooling amount Is calculated and it is determined whether or not the head is equal to or greater than a threshold value (step S100A).
  • the electronic control unit 40 calculates for each fixed period of the head based on the calculated value of the battery heat generation amount estimation unit 41, and determines whether the head is equal to or greater than a threshold value for each calculation. .
  • step S100A when the head is at the same height as the threshold or when the head is higher than the threshold, YES is determined in step S100A as the head is equal to or greater than the threshold. Accordingly, the flow control unit controls the on-off valve 30A to close the communication flow path of the communication pipe 24 (step S140). For this reason, it is possible to prevent the liquid-phase refrigerant from blowing up from the liquid refrigerant pipe 18 to the liquid refrigerant capturing portion 22 through the communication pipe 24.
  • step S100A when the head is lower than the threshold value in step S100A, it is determined that the head is less than the threshold value, and NO is determined.
  • the flow control unit controls the on-off valve 30A to open the communication flow path of the communication pipe 24 (Step S141). For this reason, the liquid refrigerant is allowed to flow from the liquid refrigerant capturing unit 22 to the liquid refrigerant pipe 18 through the communication pipe 24 due to gravity.
  • the electronic control device 40 calculates the heads at regular intervals based on the cooling amount of the secondary battery 12, and determines whether or not the calculated head is higher than the threshold value. 30 is switched between an open state and a closed state.
  • the liquid refrigerant pipe 18 from the liquid refrigerant catching section 22 through the communication pipe 24 is prevented while the liquid refrigerant is prevented from blowing up from the liquid refrigerant pipe 18 to the liquid refrigerant capturing section 22 through the communication pipe 24 according to the displacement of the head.
  • the liquid-phase refrigerant is allowed to flow through.
  • the communication pipe 24 of the present embodiment allows the liquid refrigerant flowing in the lower gas pipe 20a to flow through the liquid refrigerant flow passage of the liquid refrigerant pipe 18 by gravity.
  • the on-off valve 30A is controlled by the electronic control unit 40 to open and close the communication flow path of the communication pipe 24, as in the tenth embodiment.
  • FIG. 20 the same reference numerals as those in FIG.
  • the pipe located on the heaven region improving side from the check valve 30B in the communication pipe 24 will be referred to as the upper communication pipe 24c, and the communication pipe 24 below the check valve 30B in the top and bottom direction.
  • the located pipe is referred to as a lower communication pipe 24d.
  • the check valve 30 ⁇ / b> B is an adjustment unit that adjusts the flow of the liquid-phase refrigerant flowing through the communication pipe 24.
  • the check valve 30B of the present embodiment allows the liquid-phase refrigerant to flow from the upper communication pipe 24c to the lower communication pipe 24d, and stops the liquid-phase refrigerant from flowing from the lower communication pipe 24d to the upper communication pipe 24c. To do. That is, the check valve 30B stops the liquid refrigerant from flowing backward from the lower communication pipe 24d to the upper communication pipe 24c.
  • liquid phase refrigerant flows from the liquid refrigerant capture unit 22 through the communication pipe 24 to the liquid refrigerant pipe 18 while preventing the liquid phase refrigerant from blowing up from the liquid refrigerant pipe 18 through the communication pipe 24 to the liquid refrigerant capture unit 22. Is acceptable.
  • bubbles are generated from the inside of the liquid-phase refrigerant and flow to the rear stream while growing (that is, in the case of the present embodiment, toward the Tian district improvement side).
  • the bubbles grow to a certain size and then flow from the inside of the evaporator 14 to the outlet 14c as a gas phase refrigerant.
  • the gas-phase refrigerant rises in the heat exchange core 14f of the evaporator 14
  • the liquid-phase refrigerant is pushed up and flows into the outlet 14c.
  • the gas refrigerant pipe 20 moves into the gas refrigerant flow passage.
  • the liquid refrigerant including the gas refrigerant and the bubbles rises as a gas-liquid mixed flow.
  • the liquid phase refrigerant in the gas-liquid mixed flow is captured by the liquid refrigerant capturing unit 22, and the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 flows into the upper communication pipe 24c.
  • gas-phase refrigerant in the gas-liquid mixed flow moves to the condenser 16 through the gas-phase refrigerant flow path 22f and the upper gas pipe 20b.
  • the gas phase refrigerant radiates heat to the heat receiving fluid, so that the gas phase refrigerant is condensed.
  • the condensed liquid phase refrigerant flows into the liquid refrigerant flow passage of the liquid refrigerant pipe 18 due to gravity. Thereafter, the liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • the amount of the liquid phase refrigerant generated in the condenser 16 increases, so that the amount of the liquid phase refrigerant that accumulates in the liquid refrigerant flow passage of the liquid refrigerant pipe 18 increases. For this reason, it flows from the liquid refrigerant flow passage of the liquid refrigerant pipe 18 to the lower communication pipe 24d.
  • the check valve 30B can stop the refrigerant from flowing from the lower communication pipe 24d to the upper communication pipe 24c.
  • the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 can be stored in the upper communication pipe 24c.
  • the check valve 30B allows the refrigerant to flow from the upper communication pipe 24c to the lower communication pipe 24d.
  • liquid-phase refrigerant captured by the liquid refrigerant capturing unit 22 can be returned to the evaporator 14 through the communication pipe 24 and the liquid refrigerant pipe 18.
  • the present embodiment and the twelfth embodiment are the same except for the presence or absence of the liquid reservoir 50.
  • the liquid storage part 50 of this embodiment is disposed between the connection part 24a and the on-off valve 30A in the communication pipe 24. That is, the liquid storage part 50 is disposed on the connection part 24 a side with respect to the on-off valve 30 ⁇ / b> A in the communication pipe 24.
  • the liquid storage unit 50 temporarily stores the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 in a state where the on-off valve 30A closes the communication flow path of the communication pipe 24. For this reason, in a state where the on-off valve 30A opens the communication channel of the communication pipe 24, the liquid phase refrigerant in the liquid storage unit 50 can flow to the liquid refrigerant pipe 18 through the on-off valve 30A.
  • bubbles are generated from the inside of the liquid-phase refrigerant and flow to the rear stream while growing (that is, in the case of the present embodiment, toward the Tian district improvement side).
  • the bubbles grow to a certain size and then flow from the inside of the evaporator 14 to the outlet 14c as a gas phase refrigerant.
  • the gas-phase refrigerant rises in the heat exchange core 14f of the evaporator 14
  • the liquid-phase refrigerant is pushed up and flows into the outlet 14c.
  • the gas refrigerant pipe 20 moves into the gas refrigerant flow passage.
  • the liquid refrigerant including the gas refrigerant and the bubbles rises as a gas-liquid mixed flow.
  • the liquid phase refrigerant in the gas-liquid mixed flow is captured by the liquid refrigerant capturing unit 22, and the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 flows into the upper communication pipe 24c.
  • gas-phase refrigerant in the gas-liquid mixed flow moves to the condenser 16 through the gas-phase refrigerant flow path 22f and the upper gas pipe 20b.
  • the gas phase refrigerant radiates heat to the heat receiving fluid, so that the gas phase refrigerant is condensed.
  • the condensed liquid phase refrigerant flows into the liquid refrigerant flow passage of the liquid refrigerant pipe 18 due to gravity. Thereafter, the liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • the amount of the liquid phase refrigerant generated in the condenser 16 increases, so that the amount of the liquid phase refrigerant that accumulates in the liquid refrigerant flow passage of the liquid refrigerant pipe 18 increases. For this reason, it flows from the liquid refrigerant flow passage of the liquid refrigerant pipe 18 to the lower communication pipe 24d.
  • the refrigerant pressure in the lower communication pipe 24d becomes larger than the refrigerant pressure in the upper communication pipe 24c.
  • the on-off valve 30A stops the refrigerant from flowing from the lower communication pipe 24d to the upper communication pipe 24c.
  • the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 flows to the liquid storage unit 50 through the upper communication pipe 24c, the liquid phase refrigerant in the liquid storage unit 50 is transferred to the lower communication pipe 24d by the on-off valve 30A. Stop flowing.
  • the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 can be stored in the liquid storage unit 50. Therefore, it can be converged that the liquid level Ha of the liquid phase refrigerant in the liquid refrigerant pipe 18 rises.
  • liquid storage unit 50 can be provided to store more liquid phase refrigerant than in the twelfth embodiment, the effect of converging the rise of the liquid level Ha is great.
  • the refrigerant pressure in the upper communication pipe 24c becomes larger than the refrigerant pressure in the lower communication pipe 24d.
  • the on-off valve 30A allows the refrigerant to flow from the upper communication pipe 24c to the lower communication pipe 24d.
  • the liquid phase refrigerant in the liquid storage unit 50 flows to the evaporator 14 through the on-off valve 30A, the lower communication pipe 24d, and the liquid refrigerant pipe 18.
  • the on-off valve 30 ⁇ / b> A stops the liquid refrigerant captured by the liquid refrigerant capturing unit 22 from flowing into the liquid refrigerant piping 18 through the communication pipe 24, the liquid phase refrigerant is temporarily captured by the liquid refrigerant capturing unit 22. It can be stored in the liquid storage unit 50. For this reason, it is possible to prevent the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 from flowing into the upper gas pipe 20b.
  • the present embodiment is different from the fifteenth embodiment except that the check valve 30B instead of the on-off valve 30A is provided and the liquid refrigerant capturing unit 22 is omitted, but the other configurations are common.
  • the check valve 30B of the present embodiment allows liquid-phase refrigerant to flow from the upper communication pipe 24c to the lower communication pipe 24d, and from the lower communication pipe 24d to the upper communication pipe 24c.
  • the liquid phase refrigerant stops flowing.
  • the check valve 30 ⁇ / b> B is arranged on the connection part 24 b side with respect to the liquid storage part 50 in the communication pipe 24.
  • the liquid phase refrigerant in the gas-liquid mixed flow flowing in the lower gas pipe 20a is connected to the communication pipe 24 by gravity, as in the third embodiment. Flows into the communication channel. Of the gas-liquid mixed flow flowing in the lower gas pipe 20a, the gas-phase refrigerant moves to the condenser 16 through the upper gas pipe 20b.
  • the liquid storage part 50 of this embodiment is disposed between the connection part 24a and the on-off valve 30A in the communication pipe 24.
  • the liquid storage unit 50 temporarily stores the liquid-phase refrigerant captured by the liquid refrigerant capturing unit 22 as in the fifteenth embodiment.
  • the heating unit 60 is controlled by the electronic control unit 40 to heat the liquid phase refrigerant in the liquid storage unit 50.
  • the heating unit 60 of the present embodiment is composed of an electric heater or the like.
  • the heating unit 60 of the present embodiment is not limited to an electric heater, and electronic components such as a relay and a DC / DC converter, and waste heat from an electric circuit may be used.
  • the electronic control device 40 of the present embodiment heats the liquid-phase refrigerant in the liquid storage unit 50 when the amount of the liquid-phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient.
  • coolant is performed.
  • the electronic control unit 40 controls the heating unit 60 based on the detection value of the temperature sensor 41a and the detection value of the temperature sensor 41b as the refrigerant heating process is executed.
  • the temperature sensor 41a detects the refrigerant temperature in the upper part 14A of the evaporator 14.
  • the upper part 14A of the evaporator 14 is constituted by the heaven region improvement side region and the tank 14e in the heat exchange core 14f.
  • the temperature sensor 41a detects the refrigerant temperature downstream of the heat exchange core 14f of the evaporator 14 or the refrigerant temperature in the heaven region improvement side region of the heat exchange core 14f.
  • the temperature sensor 41b detects the refrigerant temperature in the lower part 14B of the evaporator 14.
  • the lower part 14B of the evaporator 14 is configured by a top-bottom direction lower region of the heat exchange core 14f and a tank 14d.
  • the temperature sensor 41b detects the refrigerant temperature on the upstream side of the refrigerant flow with respect to the heat exchange core 14f of the evaporator 14, or the refrigerant temperature in the lower area in the top and bottom direction of the heat exchange core 14f.
  • the electronic control unit 40 performs the refrigerant heating process according to the flowchart of FIG.
  • the electronic control device 40 repeatedly performs the refrigerant heating process when heat is exchanged between the secondary battery 12 and the evaporator 14.
  • the amount of the liquid phase refrigerant generated in the condenser 16 increases, so that the amount of the liquid phase refrigerant that accumulates in the liquid refrigerant flow passage of the liquid refrigerant pipe 18 increases. For this reason, it flows from the liquid refrigerant flow passage of the liquid refrigerant pipe 18 to the lower communication pipe 24d.
  • the check valve 30B stops the refrigerant from flowing from the lower communication pipe 24d to the upper communication pipe 24c. For this reason, the check valve 30B stops the liquid refrigerant from flowing from the upper communication pipe 24c to the lower communication pipe 24d. Accordingly, the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 is stored in the liquid storage unit 50.
  • the electronic control unit 40 of the present embodiment determines that the amount of liquid-phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient by executing the refrigerant heating process, the storage is performed.
  • the liquid phase refrigerant in the liquid part 50 is changed into a gas phase refrigerant and recirculated.
  • step S200 the electronic control unit 40 determines whether or not the amount of liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient. That is, it is determined whether or not it is necessary to recycle the liquid phase refrigerant in the liquid storage unit 50 by changing the phase of the liquid phase refrigerant to a gas phase refrigerant.
  • the electronic control unit 40 determines whether or not a difference obtained by subtracting the detected temperature of the temperature sensor 41b from the detected temperature of the temperature sensor 41a is equal to or greater than a threshold value.
  • the temperature sensor 41a detects the refrigerant temperature downstream of the refrigerant flow in the evaporator 14.
  • the temperature sensor 41 b detects the refrigerant temperature on the upstream side of the refrigerant flow in the evaporator 14. For this reason, the difference indicates a difference between the refrigerant temperature downstream of the refrigerant flow in the evaporator 14 and the refrigerant temperature upstream of the refrigerant flow in the evaporator 14.
  • step S200 when the difference is equal to or larger than the threshold value, it is determined that the amount of liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient. That is, it is determined as YES in step S200 because it is necessary to change the liquid phase refrigerant in the liquid storage unit 50 to a gas phase refrigerant and to recirculate it.
  • step S210 the heating unit 60 is turned on.
  • the heating unit 60 generates heat, and the generated heat is transmitted to the liquid phase refrigerant in the liquid storage unit 50.
  • the liquid phase refrigerant in the liquid storage unit 50 changes into a gas phase refrigerant, and the phase changed gas phase refrigerant flows to the upper gas pipe 20b through the upper communication pipe 24c and the liquid refrigerant trapping part 22.
  • the gas-phase refrigerant flowing through the upper gas pipe 20b is cooled by the condenser 16 to become a liquid-phase refrigerant.
  • the liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • the liquid phase refrigerant in the liquid storage unit 50 changes the phase to the gas phase refrigerant and the thermostat.
  • the siphon circuit 26 can be recirculated.
  • the cooling device 10 of this embodiment includes a flow rate adjusting valve 30 instead of the on-off valve 30A in the cooling device 10 of FIG.
  • the electronic control device 40 causes the liquid phase refrigerant in the liquid storage unit 50 to flow when the amount of the liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient.
  • a refrigerant recirculation process for controlling and recirculating the regulating valve 30 is executed.
  • the liquid storage part 50 is arranged on the connection part 24 a side with respect to the flow rate adjustment valve 30 in the communication pipe 24.
  • the electronic control unit 40 controls the flow rate adjusting valve 30 based on the detected value of the temperature sensor 41a and the detected value of the temperature sensor 41b in accordance with the execution of the refrigerant recirculation process (see FIG. 28).
  • the temperature sensor 41a detects the refrigerant temperature in the upper part of the evaporator 14.
  • the upper part of the evaporator 14 is constituted by a heaven region improvement side region and a tank 14e in the heat exchange core 14f.
  • the temperature sensor 41a detects the refrigerant temperature downstream of the heat exchange core 14f of the evaporator 14 or the refrigerant temperature in the heaven region improvement side region of the heat exchange core 14f.
  • the temperature sensor 41b detects the refrigerant temperature in the lower part of the evaporator 14.
  • the lower part 14B of the evaporator 14 is configured by a top-bottom direction lower region and a tank 14d of the heat exchange core 14f.
  • the temperature sensor 41b detects the refrigerant temperature on the upstream side of the refrigerant flow with respect to the heat exchange core 14f of the evaporator 14, or the refrigerant temperature in the lower area in the top and bottom direction of the heat exchange core 14f.
  • the electronic control unit 40 executes the refrigerant recirculation process according to the flowchart of FIG.
  • the electronic control unit 40 repeatedly executes the refrigerant recirculation process when heat is exchanged between the secondary battery 12 and the evaporator 14.
  • the amount of the liquid phase refrigerant generated in the condenser 16 increases, so that the amount of the liquid phase refrigerant that accumulates in the liquid refrigerant flow passage of the liquid refrigerant pipe 18 increases. For this reason, it flows from the liquid refrigerant flow passage of the liquid refrigerant pipe 18 to the lower communication pipe 24d.
  • the flow rate adjusting valve 30 stops the refrigerant from flowing from the lower communication pipe 24d to the upper communication pipe 24c. For this reason, the flow regulating valve 30 stops the liquid phase refrigerant from flowing from the upper communication pipe 24c to the lower communication pipe 24d. For this reason, the liquid phase refrigerant captured by the liquid refrigerant capturing unit 22 is stored in the liquid storage unit 50.
  • the electronic control unit 40 determines that the amount of liquid refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient by executing the refrigerant recirculation process,
  • the liquid phase refrigerant in the liquid storage unit 50 is phase-changed to a gas phase refrigerant and recirculated.
  • step S200 the electronic control unit 40 determines whether or not it is necessary to change the phase of the liquid phase refrigerant in the liquid storage unit 50 to a gas phase refrigerant and to recirculate it.
  • the electronic control unit 40 determines whether or not a difference obtained by subtracting the detected temperature of the temperature sensor 41b from the detected temperature of the temperature sensor 41a is equal to or greater than a threshold value.
  • the temperature sensor 41a detects the refrigerant temperature downstream of the refrigerant flow in the evaporator 14.
  • the temperature sensor 41 b detects the refrigerant temperature on the upstream side of the refrigerant flow in the evaporator 14. For this reason, the difference indicates a difference between the refrigerant temperature downstream of the refrigerant flow in the evaporator 14 and the refrigerant temperature upstream of the refrigerant flow in the evaporator 14.
  • step S200 when the difference is equal to or larger than the threshold value, it is determined that the amount of liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient. That is, it is determined as YES in step S200 because it is necessary to change the liquid phase refrigerant in the liquid storage unit 50 to a gas phase refrigerant and to recirculate it.
  • step S211 the flow rate control valve 30 is controlled as the flow rate control unit to increase the communication flow path cross-sectional area. For this reason, the liquid phase refrigerant in the liquid storage unit 50 flows to the evaporator 14 through the flow rate adjustment valve 30, the lower communication pipe 24 d, and the liquid refrigerant pipe 18.
  • the refrigerant can be recirculated to the thermosiphon circuit 26 by returning the liquid-phase refrigerant in the liquid storage unit 50 to the evaporator 14 through the flow rate adjustment valve 30.
  • step S200 When the difference is less than the threshold, it is determined that the refrigerant necessary for cooling the secondary battery 12 by the evaporator 14 is sufficient. That is, it is determined as NO in step S200 on the assumption that it is unnecessary to recycle the liquid-phase refrigerant in the liquid storage unit 50 into a gas-phase refrigerant. In this case, step S211 (that is, the flow path cross-sectional area increasing process) is skipped, and the process returns to step S200.
  • the electronic control device 40 causes the liquid phase refrigerant in the liquid storage unit 50 to flow when the amount of the liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient.
  • a refrigerant recirculation process for controlling and recirculating the regulating valve 30 is executed.
  • the electronic control unit 40 controls the flow rate adjusting valve 30 based on the detected value of the temperature sensor 41a and the detected value of the pressure sensor 41c as the refrigerant recirculation process is executed (see FIG. 30).
  • the pressure sensor 41 c detects the refrigerant pressure in the evaporator 14.
  • the upper part 14A of the evaporator 14 is constituted by the heaven region improvement side region and the tank 14e in the heat exchange core 14f.
  • the electronic control unit 40 performs the refrigerant heating process according to the flowchart of FIG.
  • the electronic control device 40 repeatedly performs the refrigerant heating process when heat is exchanged between the secondary battery 12 and the evaporator 14.
  • step S200A the electronic control unit 40 according to the present embodiment determines whether or not the amount of liquid-phase refrigerant that is required when the secondary battery 12 is cooled in the evaporator 14 is insufficient as an insufficient determination unit. That is, it is determined whether or not it is necessary to recycle the liquid phase refrigerant in the liquid storage unit 50 by changing the phase of the liquid phase refrigerant to a gas phase refrigerant.
  • the refrigerant pressure in the evaporator 14 and the saturation temperature of the refrigerant in the evaporator 14 have a one-to-one relationship.
  • saturation temperature information indicating the relationship between the refrigerant pressure in the evaporator 14 and the saturation temperature of the refrigerant in the evaporator 14 is stored in advance.
  • a memory is a non-transitional physical storage medium.
  • the electronic control unit 40 calculates the saturation temperature of the refrigerant in the evaporator 14 based on the saturation temperature information and the pressure detected by the pressure sensor 41c.
  • the electronic control unit 40 subtracts the saturation temperature of the refrigerant from the temperature detected by the temperature sensor 41a to obtain the degree of superheat of the upper portion 14A of the evaporator 14, and determines whether this degree of superheat is equal to or greater than a threshold value.
  • the temperature sensor 41a detects the refrigerant temperature in the upper part (that is, the refrigerant flow downstream side) of the evaporator 14.
  • the degree of superheat is equal to or greater than the threshold, it is determined that the amount of liquid refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient.
  • step S200A it is determined as YES in step S200A on the assumption that it is necessary to change the liquid phase refrigerant in the liquid storage unit 50 to a gas phase refrigerant and to recirculate it.
  • step S211 the flow regulating valve 30 is controlled to increase the communication flow path cross-sectional area. For this reason, the liquid phase refrigerant in the liquid storage unit 50 flows to the evaporator 14 through the flow rate adjustment valve 30, the lower communication pipe 24 d, and the liquid refrigerant pipe 18.
  • the refrigerant can be recirculated to the thermosiphon circuit 26 by returning the liquid-phase refrigerant in the liquid storage unit 50 to the evaporator 14 through the flow rate adjustment valve 30.
  • step S200 When the difference is less than the threshold, it is determined that the refrigerant necessary for cooling the secondary battery 12 by the evaporator 14 is sufficient. That is, it is determined as NO in step S200 on the assumption that it is unnecessary to recycle the liquid-phase refrigerant in the liquid storage unit 50 into a gas-phase refrigerant. In this case, step S211 (that is, the flow path cross-sectional area increasing process) is skipped, and the process returns to step S200.
  • the heating unit 60 is controlled according to the temperature difference between the temperature sensors 21a and 21b to recirculate the liquid refrigerant in the liquid storage unit 50 has been described. However, instead of this, the heating unit 60 is controlled according to the degree of superheat of the upper portion 14A of the evaporator 14 to recirculate the liquid refrigerant in the liquid storage unit 50, see FIG. To explain.
  • the cooling device 10 of this embodiment has a configuration in which a heating unit 60 is added to the cooling device 10 of FIG.
  • the electronic control device 40 causes the liquid phase refrigerant in the liquid storage unit 50 to flow when the amount of the liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient.
  • a refrigerant recirculation process for controlling and recirculating the regulating valve 30 is executed.
  • the electronic control unit 40 controls the flow rate adjusting valve 30 based on the detected value of the temperature sensor 41a and the detected value of the pressure sensor 41c as the refrigerant recirculation process is executed (see FIG. 33).
  • the pressure sensor 41 c detects the refrigerant pressure in the evaporator 14.
  • the temperature sensor 41 a detects the refrigerant temperature of the upper part 14 ⁇ / b> A in the evaporator 14.
  • the upper part 14A of the evaporator 14 is constituted by the heaven region improvement side region and the tank 14e in the heat exchange core 14f.
  • the temperature sensor 41a detects the refrigerant temperature downstream of the heat exchange core 14f of the evaporator 14 or the refrigerant temperature in the heaven region improvement side region of the heat exchange core 14f.
  • the electronic control unit 40 performs the refrigerant heating process according to the flowchart of FIG.
  • the electronic control device 40 repeatedly performs the refrigerant heating process when heat is exchanged between the secondary battery 12 and the evaporator 14.
  • step S200A the electronic control unit 40 of the present embodiment determines whether or not it is necessary to recycle the liquid phase refrigerant in the liquid storage unit 50 by changing the phase of the liquid phase refrigerant to a gas phase refrigerant.
  • the electronic control unit 40 calculates the saturation temperature of the refrigerant in the evaporator 14 based on the pressure detected by the pressure sensor 41c.
  • the detected pressure of the pressure sensor 41c and the saturation temperature of the refrigerant in the evaporator 14 are in a relationship specified on a one-to-one basis.
  • the electronic control unit 40 subtracts the saturation temperature of the refrigerant from the temperature detected by the temperature sensor 41a to obtain the degree of superheat of the upper portion 14A of the evaporator 14, and determines whether this degree of superheat is equal to or greater than a threshold value.
  • step S200A when the degree of superheat is equal to or greater than the threshold, it is determined that the amount of liquid refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient. That is, it is determined as YES in step S200A on the assumption that it is necessary to change the phase of the liquid phase refrigerant in the liquid storage unit 50 to a gas phase refrigerant and recirculate it.
  • step S210 the heating unit 60 is turned on as the heating control unit.
  • the heating unit 60 generates heat, and the generated heat is transmitted to the liquid phase refrigerant in the liquid storage unit 50.
  • the liquid phase refrigerant in the liquid storage unit 50 changes into a gas phase refrigerant, and the phase changed gas phase refrigerant flows to the upper gas pipe 20b through the upper communication pipe 24c and the liquid refrigerant trapping part 22.
  • the gas-phase refrigerant flowing through the upper gas pipe 20b is cooled by the condenser 16 to become a liquid-phase refrigerant.
  • the liquid phase refrigerant flows into the evaporator 14 through the liquid refrigerant flow passage of the liquid refrigerant pipe 18.
  • the liquid phase refrigerant in the liquid storage unit 50 changes the phase to the gas phase refrigerant and the thermostat.
  • the siphon circuit 26 can be recirculated.
  • a refrigerant outlet is provided on one side of the evaporator 14 in the horizontal direction DR3 (for example, the left side in the figure).
  • a refrigerant inlet is provided on the other side of the evaporator 14 in the horizontal direction DR3 (for example, on the right side in the figure).
  • the horizontal direction DR3 indicates a direction orthogonal to the vertical direction DR1 in a state where the cooling device 10 is mounted on the vehicle in a state where the vehicle traveling direction and the vehicle width direction are parallel to the horizontal direction.
  • the secondary battery 12 is disposed on the upper surface of the cooling device 10.
  • the plurality of battery cells 121 are arranged in the horizontal direction DR3 on the upper surface of the cooling device 10. Thereby, the upper surface of the evaporator 14 functions as a battery cooling surface for cooling the secondary battery 12.
  • the refrigerant temperature on the other side 14C (that is, the outlet side) in the horizontal direction DR3 of the evaporator 14 is detected by the temperature sensor 41a.
  • the temperature sensor 41 a detects the refrigerant temperature on the downstream side of the refrigerant flow in the evaporator 14.
  • the refrigerant temperature on one side (that is, the inlet side) 14B of the horizontal direction DR3 in the evaporator 14 is detected by the temperature sensor 41b.
  • the temperature sensor 41 b detects the refrigerant temperature on the upstream side of the refrigerant flow in the evaporator 14.
  • the evaporator 14 of the present embodiment is configured such that the refrigerant flows from the right side to the left side in FIG.
  • the electronic control unit 40 determines whether or not a difference obtained by subtracting the detected temperature of the temperature sensor 41b from the detected temperature of the temperature sensor 41a is equal to or greater than a threshold value. That is, it is determined whether or not it is necessary to recycle the liquid phase refrigerant in the liquid storage unit 50 by changing the phase of the liquid phase refrigerant to a gas phase refrigerant. As a result, it is determined whether or not the amount of liquid phase refrigerant necessary for cooling the secondary battery 12 in the evaporator 14 is insufficient.
  • the heating unit 60 of the present embodiment is disposed not on the liquid storage unit 50 but on the outer wall of the communication pipe 24.
  • the present embodiment and the seventeenth embodiment are the same except for the arrangement of the heating unit 60, and the other configurations are the same, so the description of the other configurations is omitted.
  • the present embodiment and the seventeenth embodiment are the same except for the presence or absence of the liquid refrigerant capturing unit 22, and the other configurations are the same, so the description of the other configurations is omitted.
  • the cooling device 10 is provided with a plurality of evaporators 14 as shown in FIGS.
  • An electrical insulating sheet 122 is disposed between the side surfaces 141 a and 141 b of the plurality of evaporators 14 and the secondary battery 12.
  • the electrical insulating sheet 122 is a sheet member having electrical insulation and good thermal conductivity.
  • a gas refrigerant branch pipe 20c is connected to each of the tanks 14e as gas flow path portions of the plurality of evaporators 14 of the present embodiment. As will be described later, the plurality of gas refrigerant branch pipes 20c are connected to a gas refrigerant main pipe 20A that collects the gas refrigerants flowing through them.
  • evaporators 14a and 14y are used as the plurality of evaporators 14.
  • Each of the evaporators 14a and 14y is a plurality of evaporators arranged at intervals in a predetermined direction (that is, the left-right direction in FIG. 38).
  • the left evaporator 14a is connected to the gas refrigerant main pipe 20A through the gas refrigerant branch pipe 20c and the gas refrigerant main pipe 20B.
  • the right evaporator 14y in FIG. 38 is connected to the gas refrigerant main pipe 20A through the gas refrigerant branch pipe 20c.
  • the two gas refrigerant branch pipes 20c, the gas refrigerant main pipe 20B, and the gas refrigerant main pipe 20A constitute the gas refrigerant pipe 20.
  • the gas refrigerant from the evaporator 14a flows to the gas refrigerant main pipe 20A through the gas refrigerant branch pipe 20c and the gas refrigerant main pipe 20B.
  • the gas refrigerant from the evaporator 14y flows into the gas refrigerant main pipe 20A through the gas refrigerant branch pipe 20c.
  • the gas refrigerant main pipe 20A is supplied to the inlet 6a of the condenser 16 with the gas refrigerant flowing from the evaporator 14a through the gas refrigerant branch pipe 20c and the gas refrigerant main pipe 20B and the gas refrigerant flowing through the gas refrigerant branch pipe 20c from the evaporator 14y.
  • a refrigerant flow path is formed.
  • the gas refrigerant main pipes 20A and 20B are arranged in the predetermined direction.
  • the main gas refrigerant pipes 20A and 20B are formed to extend in the predetermined direction.
  • the two gas refrigerant branch pipes 20c connected to the evaporators 14a and 14y are formed to extend in a direction intersecting the predetermined direction (for example, a direction orthogonal).
  • the two gas refrigerant branch pipes 20c are arranged in parallel.
  • a liquid refrigerant branch pipe 18a is connected to the tanks 14d of the plurality of evaporators 14, respectively.
  • the liquid refrigerant main pipe 18A is connected to the plurality of liquid refrigerant branch pipes 18a.
  • the liquid refrigerant branch pipe 18a constitutes the liquid refrigerant pipe 18 in the liquid refrigerant main pipe 18A.
  • the plurality of liquid refrigerant branch pipes 18a guide liquid phase refrigerant and the like flowing from the liquid refrigerant main pipe 18A to the tanks 14d of the plurality of evaporators 14, respectively.
  • the liquid refrigerant main pipe 18A constitutes a refrigerant flow path that guides the gas-phase refrigerant from the outlet 16b of the condenser 16 to the plurality of gas refrigerant branch pipes 20c.
  • a dam portion is provided as a liquid refrigerant capturing portion 22 inside the plurality of gas refrigerant branch pipes 20c as shown in FIG.
  • the liquid refrigerant capturing part 22 is formed so as to protrude upward from the lower part in the gas refrigerant branch pipe 20c. Inside the gas refrigerant branch pipe 20c, a gas-phase refrigerant flow path 22f through which the gas-phase refrigerant flows is formed above the liquid refrigerant capturing portion 22 as indicated by an arrow Ra in FIG.
  • liquid refrigerant capturing unit 22 is arranged on the upstream side in the refrigerant flow direction with respect to the gas refrigerant main pipe 20A where the gas refrigerant flowing from the plurality of evaporators 14 joins.
  • the amount of refrigerant flowing through one gas refrigerant branch pipe 20c among the plurality of gas refrigerant branch pipes 20c is smaller than the amount of refrigerant flowing through the gas refrigerant main pipe 20A.
  • the pressure loss of the refrigerant is generally proportional to the first power of the refrigerant flow velocity or more, the pressure loss of the refrigerant flow generated by the liquid refrigerant capturing unit 22 in the present embodiment causes the liquid refrigerant capturing unit 22 to be gas refrigerant main. It is smaller than the pressure loss of the refrigerant flow that occurs when it is arranged in the pipe 20A. Therefore, the refrigerant can be circulated well in the thermosiphon circuit 26.
  • a gas-phase refrigerant flow path 22f is formed on the center side in the radial direction of the liquid refrigerant capture unit 22.
  • the liquid refrigerant capturing unit 22 of the present embodiment is configured as a part of the gas refrigerant branch pipe 20c.
  • the liquid refrigerant capturing unit 22 constitutes a throttle unit having a smaller sectional area of the refrigerant channel than the upstream side 120 in the refrigerant flow direction in the gas refrigerant branch pipe 20c.
  • the cross-sectional area of the refrigerant flow path is smaller than that of the gas refrigerant branch pipe 20c on the downstream side 123 in the refrigerant flow direction.
  • the liquid-phase refrigerant can be dammed up in the refrigerant flow direction upstream side 120 with respect to the liquid refrigerant capturing portion 22 in the gas refrigerant branch pipe 20c.
  • the liquid refrigerant capturing unit 22 constitutes a refrigerant flow path through which the gas-phase refrigerant flows as indicated by an arrow Ra.
  • the liquid refrigerant capture unit 22 has a smaller cross-sectional area of the refrigerant flow path than the refrigerant flow direction upstream side 120 of the gas refrigerant branch pipe 20c and the refrigerant flow path disconnection of the refrigerant flow direction downstream side 123. The area is getting smaller.
  • the outer diameter dimension of the liquid refrigerant capturing section 22 is smaller than the outer diameter dimension of the upstream side 120 in the refrigerant flow direction of the gas refrigerant branch pipe 20c and smaller than the outer diameter dimension of the downstream side 123 in the refrigerant flow direction.
  • liquid refrigerant capturing unit 22 is softer than the refrigerant flow direction upstream side 120 and the refrigerant flow direction downstream side 123 of the gas refrigerant branch pipe 20c and is easily deformed.
  • connection part 141e a connection part connected to the gas refrigerant branch pipe 20c in the tank 14e of the evaporator 14a
  • a connection part connected to the gas refrigerant branch pipe 20c in the tank 14e of the evaporator 14y Is the connecting portion 142e.
  • a connection part connected to the gas refrigerant branch pipe 20c in the gas refrigerant main pipe 20B is a connection part 201e
  • a connection part connected to the gas refrigerant branch pipe 20c in the gas refrigerant main pipe 20A is a connection part 202e.
  • the distance between the evaporators 14a and 14y (that is, the length between the connecting portions 141e and 142e) is the distance L1
  • the distance between the two gas branch pipes 20c (that is, the length between 201e and 202e) is the distance L2.
  • the liquid refrigerant capturing unit 22 is configured to bend the direction of the refrigerant flow flowing from the evaporator 14 toward the condenser 16 upward in the vertical direction DR1 as indicated by an arrow Ra.
  • the liquid refrigerant capturing unit 22 may have any shape as shown in FIGS. 48, 49, and 50 as long as the direction of the gas-phase refrigerant flow is bent upward in the vertical direction DR1.
  • the liquid-phase refrigerant in the gas-liquid mixed flow from the tank 14e of the evaporator 14 is blocked by the liquid refrigerant capturing unit 22, and the gas-phase refrigerant in the gas-liquid mixed flow is converted into the liquid refrigerant. It can be led to the condenser 16 through the main pipe 18A.
  • the heat exchange core 14f is configured by a plurality of tubes 141.
  • the plurality of tubes 141 are arranged in a predetermined direction.
  • Each of the plurality of tubes 141 constitutes a refrigerant passage through which the liquid-phase refrigerant from the tank 14d flows to the tank 14e.
  • the plurality of tubes 141 cool the secondary battery 12 by heat exchange between the refrigerant and the secondary battery 12.
  • a plurality of liquid refrigerant capturing portions 22 are arranged one by one between two adjacent tubes 141 among the plurality of tubes 141.
  • the plurality of liquid refrigerant capturing portions 22 project upward from the floor portion of the tank 14e to constitute a dam portion that dams the liquid refrigerant.
  • the plurality of liquid refrigerant traps 22 are arranged in the refrigerant flow direction in the tank 14e. Note that an arrow Rb in FIG. 51 indicates the refrigerant flow direction in the tank 14d.
  • the gas-phase refrigerant flowing from the inlet 22a can be guided from the outlet 22b to the inlet 16a of the condenser 16 while storing the liquid-phase refrigerant flowing from the inlet 22a in the liquid refrigerant capturing unit 22.
  • the liquid refrigerant capture unit 22 of the present embodiment includes a centrifugal gas-liquid separator including a main body 200 formed in a cylindrical shape, a gas phase refrigerant outlet cylinder 210, a liquid phase refrigerant outlet cylinder 220, and an inlet cylinder 230. It is.
  • the gas-phase refrigerant outlet cylinder 210 is formed so that its axis coincides with the axis of the main body 200.
  • the radial dimension of the gas-phase refrigerant outlet cylinder part 210 is smaller than the radial dimension of the main body part 200.
  • the upper opening of the vapor phase refrigerant outlet cylinder 210 constitutes a gas refrigerant outlet 22b.
  • the gas refrigerant outlet 22 b is located on the upper side with respect to the main body portion 200.
  • the lower opening of the gas-phase refrigerant outlet cylinder 210 constitutes the gas-phase refrigerant inlet 211.
  • the gas-phase refrigerant inlet 211 is disposed inside the main body 200.
  • the inlet cylinder part 230 is formed so as to protrude from the side wall of the main body part 200.
  • An opening on one side in the axial direction of the inlet cylinder 230 forms an inlet 22a.
  • the opening on the other side in the axial direction of the inlet cylinder 230 is communicated with the main body 200.
  • the liquid phase refrigerant outlet cylinder 220 is formed so that its axis coincides with the axis of the main body 200.
  • the radial dimension of the liquid phase refrigerant outlet cylinder 220 is smaller than the radial dimension of the main body 200.
  • the axial upper opening of the liquid phase refrigerant outlet cylinder 220 communicates with the main body 200.
  • the lower opening in the axial direction of the liquid-phase refrigerant outlet cylinder 220 forms a liquid refrigerant outlet 22c.
  • the gas-liquid mixed flow from the evaporator 14 flows into the main body 200 through the inlet 22a and the inlet cylinder 230.
  • the gas-liquid mixed flow in the main body 200 is reduced by gravity while rotating around the liquid-phase refrigerant outlet cylinder 220 around the axis.
  • centrifugal force acts on the gas-liquid mixed flow, and the liquid phase refrigerant and the gas phase refrigerant are separated.
  • the gas phase refrigerant flows from the gas phase refrigerant inlet 211 to the liquid phase refrigerant outlet cylinder 220. For this reason, it flows to the inlet 16a of the condenser 16 through the gas refrigerant outlet 22b.
  • the liquid refrigerant flows into the communication pipe 24 through the liquid refrigerant outlet cylinder 220 and the liquid refrigerant outlet 22c.
  • the liquid refrigerant capturing unit 22 serves as a gas-liquid separator, and causes the gas-liquid mixed flow from the evaporator 14 to flow in a vortex shape so that the liquid-phase refrigerant and the gas-phase refrigerant are separated by centrifugal force. Can be separated.
  • the secondary battery 12 in which the electrodes 121a and 121b of the plurality of battery cells 121 are arranged on the upper side may be used.
  • the plurality of battery cells 121 are arranged on the upper surface of the evaporator 14.
  • An inlet 14b and an outlet 14c of the evaporator 14 are arranged on one side in the horizontal direction.
  • a battery other than the secondary battery 12 may be the object to be cooled.
  • the cooling device according to the present disclosure is applied to an automobile has been described. Instead, the cooling device according to the present disclosure can be used to move trains, airplanes, ships, etc. It may be applied to the body.
  • the cooling device of the present disclosure may be applied to an installation type device.
  • the cooling device of the present disclosure may be applied to an installation type device.
  • the secondary battery 12 when the secondary battery 12 is cooled in the evaporator 14 by determining whether or not the degree of superheat of the refrigerant in the lower gas pipe 20a in the gas refrigerant pipe 20 is larger than the threshold value. It may be determined whether or not the amount of the liquid-phase refrigerant required is insufficient.
  • the liquid refrigerant capturing unit 22 In the twenty-fourth and twenty-fifth embodiments, the example in which the liquid refrigerant capturing unit 22 is configured in each of the plurality of gas refrigerant branch pipes 20c has been described. However, instead of this, the liquid refrigerant capturing unit 22 may be configured in at least one or more gas refrigerant branch pipes 20c among the plurality of gas refrigerant branch pipes 20c.
  • the liquid refrigerant capturing unit 22 may be configured in at least one or more gas refrigerant branch pipes 20c among the plurality of gas refrigerant branch pipes 20c.
  • the example in which the liquid refrigerant capture unit 22 is configured in the gas refrigerant branch pipe 20c has been described. Instead, the liquid refrigerant capture unit 22 is replaced with a plurality of evaporators 14. You may comprise in the gas refrigerant main piping 20A after the refrigerant
  • the cooling device 10 is configured by using the liquid storage unit 50 and the on-off valve 30A has been described, but instead of this, the liquid storage unit 50 and the on-off valve 30A out of liquid storage
  • the cooling device 10 may be configured using only the unit 50. That is, the cooling device 10 may be configured using the liquid storage unit 50 without using the on-off valve 30A.
  • the cooling device 10 is configured using the check valve 30B and the liquid storage unit 50 has been described.
  • the cooling device 10 may be configured using only the liquid storage unit 50. That is, the cooling device 10 may be configured using the liquid storage unit 50 without using the check valve 30B.
  • cooling device 10 is configured by using the flow rate adjustment valve 30 and the liquid storage unit 50
  • the flow rate adjustment valve 30 and the liquid storage unit 50 may be configured using only the liquid storage unit 50. That is, the cooling device 10 may be configured using the liquid storage unit 50 without using the flow rate adjusting valve 30.
  • the liquid refrigerant capturing unit 22 is installed between the tubes 141, but it may not be installed between all the tubes 141. For example, every other liquid coolant capturing unit 22 may be installed on the tube 141.
  • 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.
  • the refrigerant circulates and is cooled by the phase change between the liquid phase and the gas phase of the refrigerant.
  • a cooling device for cooling an object is not limited to the first aspect described in part or all of the first to thirtieth embodiments and other embodiments.
  • the cooling device includes at least one or more evaporation units for boiling the liquid phase refrigerant by transferring heat from the object to be cooled to the liquid phase refrigerant, and a condensing unit for condensing the gas phase refrigerant by releasing the heat from the gas phase refrigerant.
  • the cooling device includes a liquid refrigerant pipe that circulates the liquid phase refrigerant from the condensing part to at least one evaporation part, and a gas refrigerant pipe that circulates the gas-phase refrigerant from the at least one evaporation part to the condensing part.
  • the cooling device is connected to the gas refrigerant pipe or at least one or more evaporators, and connected to the liquid refrigerant pipe or at least one or more evaporators, and is in the direction of gravity with respect to the first connector. And a communication pipe having a second connection portion located on the lower side.
  • the moved liquid-phase refrigerant reaches the condensing unit.
  • the liquid phase refrigerant is moved from the first connection portion to the second connection portion through the communication pipe.
  • an adjustment unit for adjusting the flow of the liquid-phase refrigerant flowing through the communication pipe is provided.
  • the adjustment unit adjusts the refrigerant flow rate of the liquid-phase refrigerant flowing through the communication pipe by adjusting the cross-sectional area of the refrigerant flow path formed between the first connection unit and the second connection unit. It is a valve.
  • the adjustment unit suppresses the liquid refrigerant from flowing backward through the communication pipe from the second connection unit side to the first connection unit side, and from the first connection unit side to the second connection unit side.
  • the check valve allows the liquid phase refrigerant to flow through the communication pipe.
  • the cooling device circulates the refrigerant and cools the object to be cooled by the phase change between the liquid phase and the gas phase of the refrigerant.
  • the cooling device includes at least one or more evaporation units that boil the liquid-phase refrigerant by transferring heat from the object to be cooled to the liquid-phase refrigerant, and a condensation that condenses the gas-phase refrigerant by releasing heat from the gas-phase refrigerant.
  • the soot cooling device includes a liquid refrigerant pipe that circulates the liquid phase refrigerant from the condensing part to at least one evaporation part, and a gas refrigerant pipe that circulates the gas-phase refrigerant from the at least one evaporation part to the condensing part.
  • a liquid refrigerant pipe that circulates the liquid phase refrigerant from the condensing part to at least one evaporation part
  • a gas refrigerant pipe that circulates the gas-phase refrigerant from the at least one evaporation part to the condensing part.
  • the first connection part connected to the liquid refrigerant capturing part, the liquid refrigerant pipe or at least one evaporation part is connected, and the first connection part is below the gravitational direction.
  • the communication piping which has the 2nd connection part located is provided.
  • the communication pipe returns the liquid-phase refrigerant captured by the liquid refrigerant capturing unit to at least one evaporation unit or liquid refrigerant pipe.
  • an adjustment unit for adjusting the flow of the liquid-phase refrigerant flowing through the communication pipe is provided.
  • the adjusting unit adjusts the cross-sectional area of the refrigerant flow path formed between at least one evaporation unit or the liquid refrigerant pipe and the liquid refrigerant capturing unit, and flows through the communication pipe.
  • This is a valve for adjusting the refrigerant flow rate of the phase refrigerant.
  • the valve is controlled so that the cross-sectional area of the refrigerant flow path becomes smaller as the liquid level of the liquid refrigerant in the liquid refrigerant pipe becomes higher, and the cross-sectional area of the refrigerant flow path becomes smaller as the liquid level becomes lower.
  • a flow rate control unit that controls the valve so as to be large is provided.
  • a cooling device is provided with the determination part which determines whether the liquid level of the liquid phase refrigerant
  • the cooling device sets the valve so that the cross-sectional area of the refrigerant flow path is smaller than when the determination unit determines that the liquid level is lower than the threshold value.
  • a flow control unit for controlling.
  • the cooling device includes a shortage determination unit that determines whether or not the amount of liquid phase refrigerant necessary for cooling the object to be cooled is insufficient in the evaporation unit.
  • a shortage determination unit determines whether or not the amount of liquid phase refrigerant necessary for cooling the object to be cooled is insufficient in the evaporation unit.
  • the cross-sectional area of the refrigerant flow path is larger than when the shortage determination unit determines that the refrigerant amount in the evaporation unit is not insufficient.
  • a flow control unit for controlling the valve to increase the flow rate.
  • a heating unit that is provided on the first connection unit side with respect to the adjustment unit and that heats the liquid-phase refrigerant in the communication pipe to change the phase to a gas-phase refrigerant.
  • the cooling device includes a shortage determination unit that determines whether or not the amount of liquid phase refrigerant necessary for cooling the object to be cooled is insufficient in the evaporation unit.
  • the cooling device includes a heating control unit that controls the heating unit to heat the liquid-phase refrigerant in the communication pipe when the shortage determination unit determines that the refrigerant amount in the evaporation unit is insufficient.
  • At least one of the evaporation sections includes a heat exchange core that exchanges heat between the liquid phase refrigerant from the liquid refrigerant pipe and the object to be cooled, and a gas phase refrigerant generated in the heat exchange core. And a gas flow path section for guiding the gas to the gas refrigerant pipe.
  • the shortage determination unit determines whether or not the degree of superheat of the refrigerant in the gas flow path unit or the refrigerant in the gas refrigerant pipe is equal to or greater than a threshold value.
  • the shortage determination unit determines whether or not the difference between the refrigerant temperature upstream of the refrigerant flow and the refrigerant temperature downstream of the refrigerant flow is equal to or greater than a threshold in at least one evaporation unit. .
  • the communication pipe includes a liquid storage part for temporarily storing a liquid phase refrigerant.
  • the liquid storage part is disposed on the first connection part side with respect to the adjustment part.
  • the liquid refrigerant capturing section is a dam section that dams up the liquid phase refrigerant in order to capture the liquid phase refrigerant.
  • the gas refrigerant pipe includes a bending portion that bends the direction of the flow of the gas-phase refrigerant flowing to the condensing portion upward in the gravity direction, and the bending portion constitutes a liquid refrigerant capturing portion.
  • the liquid refrigerant trapping section constitutes a gas-liquid separator that separates the liquid phase refrigerant and the gas phase refrigerant by decelerating the flow rates of the liquid phase refrigerant and the gas phase refrigerant.
  • the liquid refrigerant capturing unit constitutes a centrifugal gas-liquid separator that separates the liquid phase refrigerant and the gas phase refrigerant by centrifugal force.
  • the adjustment unit suppresses the liquid refrigerant from flowing backward through the communication pipe from the second connection unit side to the first connection unit side, and from the first connection unit side to the second connection unit side.
  • the check valve allows the liquid phase refrigerant to flow through the communication pipe.
  • At least one or more evaporation units are a plurality of evaporation units.
  • the gas refrigerant pipe includes a plurality of branch pipes that circulate the gas-phase refrigerant from the plurality of evaporation sections to the condensation section, and a gas refrigerant book that joins the gas-phase refrigerant from the plurality of branch pipes and distributes the gas-phase refrigerant to the condensation section.
  • the liquid refrigerant capturing unit is disposed in at least one branch pipe among the plurality of branch pipes.
  • the cooling device circulates the refrigerant and cools the object to be cooled by the phase change between the liquid phase and the gas phase of the refrigerant.
  • the cooling device is configured to generate heat by transferring heat from the object to be cooled to liquid-phase refrigerant and generating vapor-phase refrigerant; and by releasing heat from the gas-phase refrigerant, vapor-phase refrigerant is condensed to generate liquid-phase refrigerant.
  • a condensing part is configured to generate heat by transferring heat from the object to be cooled to liquid-phase refrigerant and generating vapor-phase refrigerant; and by releasing heat from the gas-phase refrigerant, vapor-phase refrigerant is condensed to generate liquid-phase refrigerant.
  • the cooling device is necessary for cooling the object to be cooled in the evaporation section, the gas refrigerant pipe for flowing the gas-phase refrigerant from the evaporation section to the condensation section, the liquid refrigerant pipe for flowing the liquid phase refrigerant from the condensation section to the evaporation section, A shortage determining unit that determines whether or not the amount of the liquid phase refrigerant is insufficient.
  • the evaporation unit has a heat exchange core that moves heat from the object to be cooled to the liquid refrigerant from the liquid refrigerant pipe, A gas flow path section for guiding the gas-phase refrigerant generated in the heat exchange core to the gas refrigerant pipe.
  • the shortage determination unit determines whether or not the refrigerant amount of the liquid phase refrigerant is insufficient by determining whether or not the degree of superheat of the refrigerant in the gas flow path unit or the refrigerant in the gas refrigerant pipe is equal to or greater than a threshold value. To do.
  • the cooling device circulates the refrigerant and cools the object to be cooled by the phase change between the liquid phase and the gas phase of the refrigerant.
  • the cooling device is configured to generate heat by transferring heat from the object to be cooled to liquid-phase refrigerant and generating vapor-phase refrigerant; and by releasing heat from the gas-phase refrigerant, vapor-phase refrigerant is condensed to generate liquid-phase refrigerant.
  • a condensing part is configured to generate heat by transferring heat from the object to be cooled to liquid-phase refrigerant and generating vapor-phase refrigerant; and by releasing heat from the gas-phase refrigerant, vapor-phase refrigerant is condensed to generate liquid-phase refrigerant.
  • the cooling device includes a gas refrigerant pipe through which the gas phase refrigerant flows from the evaporation section to the condensation section, and a liquid refrigerant pipe through which the liquid phase refrigerant flows from the condensation section to the evaporation section.
  • the cooling device includes an insufficiency determining unit that determines whether or not the difference between the refrigerant temperature upstream of the refrigerant flow and the refrigerant temperature downstream of the refrigerant flow is greater than or equal to a threshold value in the evaporation unit. Thereby, it is determined whether or not the amount of the liquid phase refrigerant necessary for cooling the object to be cooled in the evaporation unit is insufficient.
  • the object to be cooled is a vehicle-mounted battery.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Manufacturing & Machinery (AREA)
  • Electrochemistry (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Secondary Cells (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

L'invention concerne un dispositif de refroidissement comprenant : au moins une unité d'évaporation (14) qui amène un fluide frigorigène en phase liquide à bouillir en amenant de la chaleur à se déplacer d'un objet à refroidir vers le fluide frigorigène en phase liquide ; une unité de condensation (16) qui condense un fluide frigorigène en phase gazeuse ; un tuyau de fluide frigorigène liquide (18) destiné à la circulation du fluide frigorigène en phase liquide de l'unité de condensation vers ladite ou lesdites unités d'évaporation ; un tuyau de fluide frigorigène gazeux (20) destiné à la circulation du fluide frigorigène en phase gazeuse de ladite ou desdites unités d'évaporation vers l'unité de condensation ; et un tuyau de communication (24) qui comprend une première unité de raccordement (24a) raccordée au tuyau de fluide frigorigène gazeux ou à ladite ou auxdites unités d'évaporation, et une seconde unité de raccordement (24b) qui est raccordée au tuyau de fluide frigorigène liquide ou à ladite ou auxdites unités d'évaporation et est positionnée sur le côté inférieur par rapport à la première unité de raccordement dans la direction de la force gravitationnelle. Lorsque, à mesure que le fluide frigorigène en phase liquide bout, des bulles d'air générées à partir du fluide frigorigène en phase liquide dans ladite ou lesdites unités d'évaporation amènent le fluide frigorigène en phase liquide à se déplacer vers le côté unité de condensation, le fluide frigorigène en phase liquide est amené à se déplacer de la première unité de raccordement vers la seconde unité de raccordement à travers le tuyau de communication avant que le fluide frigorigène en phase liquide qui s'est déplacé atteigne l'unité de condensation.
PCT/JP2019/017773 2018-04-27 2019-04-25 Dispositif de refroidissement WO2019208726A1 (fr)

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JP2018087287A JP7035774B2 (ja) 2018-04-27 2018-04-27 冷却装置
JP2018-087287 2018-04-27

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CN113097594A (zh) * 2021-03-31 2021-07-09 宁波诺丁汉大学 基于可动翅片和相变材料的锂离子电池热管理系统及方法
CN114701636A (zh) * 2022-03-11 2022-07-05 中国船舶重工集团公司第七一九研究所 一种基于分离式热管的船舶自流冷却系统

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JPS6215661Y2 (fr) * 1982-10-07 1987-04-21
JPH03213998A (ja) * 1990-01-18 1991-09-19 Matsushita Electric Ind Co Ltd 熱搬送装置
JPH0631704B2 (ja) * 1986-07-02 1994-04-27 株式会社日立製作所 ヒ−トパイプ
JP2902068B2 (ja) * 1990-07-18 1999-06-07 三機工業株式会社 空調用受液装置
JP2005055079A (ja) * 2003-08-05 2005-03-03 Hachiyo Engneering Kk サーモサイフォンサイクルシステム
JP2005188813A (ja) * 2003-12-25 2005-07-14 Fuji Electric Holdings Co Ltd サーモサイフォン式冷却装置
JP2009168273A (ja) * 2008-01-11 2009-07-30 Fujitsu Ltd ループ型ヒートパイプおよび電子機器
JP2012241976A (ja) * 2011-05-19 2012-12-10 Fujikura Ltd ループ型ヒートパイプ
WO2017051525A1 (fr) * 2015-09-24 2017-03-30 日本電気株式会社 Dispositif de refroidissement, et procédé de commande de débit de frigorigène
WO2018070116A1 (fr) * 2016-10-12 2018-04-19 株式会社デンソー Dispositif de refroidissement

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FR2668673B1 (fr) 1990-10-25 1996-08-23 Inst Textile De France Applicateur resonnant haute-frequence ou micro-onde pour traitement thermique de materiau plan en defilement continu.
JP6215661B2 (ja) 2013-11-13 2017-10-18 出光ユニテック株式会社 容器本体および容器

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JPS6215661Y2 (fr) * 1982-10-07 1987-04-21
JPH0631704B2 (ja) * 1986-07-02 1994-04-27 株式会社日立製作所 ヒ−トパイプ
JPH03213998A (ja) * 1990-01-18 1991-09-19 Matsushita Electric Ind Co Ltd 熱搬送装置
JP2902068B2 (ja) * 1990-07-18 1999-06-07 三機工業株式会社 空調用受液装置
JP2005055079A (ja) * 2003-08-05 2005-03-03 Hachiyo Engneering Kk サーモサイフォンサイクルシステム
JP2005188813A (ja) * 2003-12-25 2005-07-14 Fuji Electric Holdings Co Ltd サーモサイフォン式冷却装置
JP2009168273A (ja) * 2008-01-11 2009-07-30 Fujitsu Ltd ループ型ヒートパイプおよび電子機器
JP2012241976A (ja) * 2011-05-19 2012-12-10 Fujikura Ltd ループ型ヒートパイプ
WO2017051525A1 (fr) * 2015-09-24 2017-03-30 日本電気株式会社 Dispositif de refroidissement, et procédé de commande de débit de frigorigène
WO2018070116A1 (fr) * 2016-10-12 2018-04-19 株式会社デンソー Dispositif de refroidissement

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113097594A (zh) * 2021-03-31 2021-07-09 宁波诺丁汉大学 基于可动翅片和相变材料的锂离子电池热管理系统及方法
CN114701636A (zh) * 2022-03-11 2022-07-05 中国船舶重工集团公司第七一九研究所 一种基于分离式热管的船舶自流冷却系统

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