JP6669266B2 - Equipment temperature controller - Google Patents

Description

Cross-reference to related application

  This application is based on Japanese Patent Application No. 2006-176792 filed on September 9, 2016, the disclosure of which is incorporated herein by reference.

  The present disclosure relates to a device temperature control device that controls the temperature of a device.

  Patent Literature 1 discloses a device temperature controller that adjusts the temperature of a battery mounted on a vehicle as a target device. This device temperature control device includes a working fluid circuit that forms a loop-type thermosiphon heat pipe.

JP, 2015-41418, A

  In the above-described device temperature controller, a liquid working fluid evaporates due to heat absorption from the device inside the evaporating section of the working fluid circuit. At this time, it has been found by the present inventors that if the temperature difference between the device and the liquid working fluid is larger than a predetermined temperature difference, the liquid working fluid will violently boil inside the evaporator. When intense boiling occurs, the liquid level of the working fluid rises and falls violently, and at the same time, abnormal sounds such as bubble bursting noise and flowing noise are generated.

  The case where the temperature difference between the device and the liquid working fluid is larger than the predetermined temperature difference includes immediately after the start of the operation of the cooling device when the working fluid is cooled by the cooling device in the condensing section of the working fluid circuit. In addition, when the working fluid is cooled by the outside air of the working fluid circuit, that is, outside air, in the condensing portion of the working fluid circuit, the temperature of the outside air is low as in winter. Thus, when the temperature of the working fluid cooled in the condensing section is too low, intense boiling occurs in the evaporating section.

  In addition, as a method of preventing generation of abnormal noise due to intense boiling, a gas-liquid separation unit is installed in the working fluid circuit, or the piping diameter of the working fluid circuit is increased, so that gas-liquid separation is easy, and the flow is improved. A calming method is conceivable. However, when the space for mounting the device temperature control device is limited, such as when the device temperature control device is mounted on a vehicle, installation of the gas-liquid separation unit or enlargement of the pipe diameter cannot be adopted.

  Further, such a problem also occurs in an apparatus temperature control device including a working fluid circuit that forms a thermosiphon heat pipe that is not a loop type.

  In view of the above, it is an object of the present disclosure to provide a device temperature controller that can suppress intense boiling generated in an evaporating section.

To achieve the above object, according to one aspect of the present disclosure,
The equipment temperature controller is
A working fluid circuit that constitutes a thermosiphon type heat pipe and circulates a working fluid,
A temperature adjusting unit for adjusting the temperature of the working fluid in the working fluid circuit;
A control device for controlling the operation of the temperature adjustment unit,
The working fluid circuit is
An evaporating section where the working fluid evaporates due to heat absorption from the device;
A condenser that cools and condenses the working fluid evaporated in the evaporator,
When the temperature difference between the device and the liquid working fluid is larger than a predetermined temperature difference, the control device controls the temperature adjustment unit to suppress a decrease in the temperature of the working fluid in the working fluid circuit ,
The device temperature controller includes a cooling device that cools the working fluid in the condensing section,
The temperature adjustment unit is a variable thermal resistor that is provided between the condensation unit and the cooling device and that can change the thermal resistance between the condensation unit and the cooling device,
The control device increases the thermal resistance of the variable thermal resistor when the cooling device is operating and the temperature difference is larger than a predetermined temperature difference.

  According to this, when the temperature difference between the device and the liquid working fluid, which is a condition under which intense boiling occurs, is larger than the predetermined temperature difference, compared with the case where the temperature drop of the working fluid is not suppressed, The expansion of the temperature difference from the working fluid can be suppressed. For this reason, intense boiling generated in the evaporating section can be suppressed.

It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 1st Embodiment. It is sectional drawing of the fluid circuit for apparatuses in FIG. It is a block diagram of the electric control part of the apparatus temperature controller in 1st Embodiment. 5 is a flowchart of control executed by the control device according to the first embodiment. FIG. 3 is a diagram showing conditions under which intense boiling occurs. FIG. 2 is a cross-sectional view of the device fluid circuit in FIG. 1 when intense boiling occurs. It is a flowchart of the control which the control apparatus in 2nd Embodiment performs. It is a saturation temperature curve of R134a refrigerant. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 3rd Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 3rd Embodiment. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 4th Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 4th Embodiment. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 5th Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 5th Embodiment. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 6th Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 6th Embodiment. It is a flow chart of control which a control device in a 6th embodiment performs. It is a flow chart of control which a control device in a 7th embodiment performs. It is a block diagram of the electric control part of the apparatus temperature controller in 8th Embodiment. It is a flow chart of control which a control device in an 8th embodiment performs. It is a block diagram of the electric control part of the apparatus temperature controller in 9th Embodiment. It is a flow chart of control which a control device in a 9th embodiment performs. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 10th Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 10th Embodiment. It is a flow chart of control which a control device in a 10th embodiment performs. It is a flow chart of control which a control device in an 11th embodiment performs. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 12th Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 12th Embodiment. It is a schematic diagram which shows the whole structure of the apparatus temperature control apparatus in 13th Embodiment. It is a block diagram of the electric control part of the apparatus temperature controller in 13th Embodiment.

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

(1st Embodiment)
The device temperature control apparatus 1 of the present embodiment shown in FIG. 1 adjusts the battery temperature of the battery pack BP as a temperature control target device by cooling the battery pack BP mounted on the vehicle. It is assumed that the vehicle equipped with the device temperature control device 1 is an electric vehicle or a hybrid vehicle that can be driven by a driving electric motor (not shown) using the battery pack BP as a power source.

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

  The battery pack BP is connected to a power converter and a motor generator (not shown). The power conversion device is, for example, a device that converts a DC current supplied from a battery pack into an AC current, and supplies (ie, discharges) the converted AC current to various electric loads such as a traveling electric motor. Further, the motor generator is a device that, when the vehicle is regenerated, reversely converts the traveling energy of the vehicle into electric energy and supplies the converted electric energy to the assembled battery BP via an inverter or the like as regenerated electric power.

  When the battery pack BP supplies power while the vehicle is running, the battery pack BP generates heat, and the battery pack BP may become excessively hot. If the temperature of the battery pack BP becomes excessively high, the deterioration of the battery cells BC is promoted. Therefore, it is necessary to limit the output and the input so as to reduce self-heating. Therefore, in order to secure the output and the input of the battery cell BC, a cooling means for maintaining the temperature below a predetermined temperature is required.

  In addition, the power storage device including the battery pack BP is often disposed under the floor of the vehicle or under the trunk room, so that the battery temperature of the battery pack BP gradually increases not only during the running of the vehicle but also during parking in summer or the like. The battery temperature may rise to an excessively high temperature. If the battery pack BP is left in a high-temperature environment, the battery life is greatly reduced due to the progress of deterioration. Therefore, the battery temperature of the battery pack BP must be maintained at a predetermined temperature or less even during parking of a vehicle. Is desired.

  Further, the battery pack BP is composed of a plurality of battery cells BC. However, if the temperature of each battery cell BC varies, the degree of progress of the deterioration of each battery cell is biased, and the input of the entire battery pack is performed. Output characteristics are degraded. This is because the assembled battery BP includes a series connection of battery cells, and the input / output characteristics of the entire assembled battery are determined according to the battery characteristics of the battery cell BC that has deteriorated the most among the battery cells BC. Because. For this reason, in order for the assembled battery BP to exhibit desired performance for a long period of time, it is important to equalize the temperature to reduce the temperature variation of each battery cell BC.

  As a cooling unit for cooling the battery pack BP, an air-cooling type cooling unit using a blower and a cooling unit using cold heat of a vapor compression refrigeration cycle are generally used.

  However, the air-cooling type cooling means using a blower merely blows air or the like in the vehicle compartment to the battery pack, and thus may not be able to obtain sufficient cooling capacity to sufficiently cool the battery pack BP.

  Further, the cooling means using the cold heat of the refrigeration cycle needs to drive a compressor or the like that consumes a large amount of power while the vehicle is parked, although the cooling capacity of the battery pack BP is high. This is not preferable because it leads to an increase in power consumption and an increase in noise.

  Therefore, the device temperature controller 1 of the present embodiment employs a thermosiphon system in which the battery temperature of the battery pack BP is adjusted by the natural circulation of the working fluid instead of the forced circulation of the refrigerant by the compressor.

  The device temperature controller 1 includes a device fluid circuit 10. The device fluid circuit 10 is a working fluid circuit in which a working fluid circulates. As the working fluid circulating in the device fluid circuit 10, a refrigerant (for example, R134a, R1234yf) used in a vapor compression refrigeration cycle is used.

  The device fluid circuit 10 is a heat pipe that performs heat transfer by evaporation and condensation of the working fluid, and is configured to be a thermosiphon type in which the working fluid naturally circulates by gravity. Further, the device fluid circuit 10 is configured to be a loop type in which a flow path through which a gaseous working fluid flows and a flow path through which a liquid working fluid flows are separated. That is, the device fluid circuit 10 constitutes a loop-type thermosiphon heat pipe.

  As shown in FIG. 1, the equipment fluid circuit 10 is formed by connecting the equipment heat exchanger 12, the equipment condenser 14, the gas passage 16 and the liquid passage 18 to each other. The device fluid circuit 10 is a closed annular fluid circuit. A predetermined amount of working fluid is sealed inside the device fluid circuit 10.

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

  The equipment heat exchanger 12 is arranged below the equipment condenser 14. As a result, the liquid working fluid accumulates in the lower part of the equipment fluid circuit 10 including the equipment heat exchanger 12 due to gravity.

  The equipment condenser 14 is a heat exchanger that functions as a condenser that condenses the gaseous working fluid evaporated in the equipment heat exchanger 12. The equipment condenser 14 cools the working fluid by heat exchange with the refrigerant of the refrigeration cycle device 21 for air conditioning mounted on the vehicle. Therefore, in the present embodiment, the refrigeration cycle device 21 constitutes a cooling device that cools the working fluid. Further, the refrigeration cycle device 21 forms a part of a vehicle air conditioner. The refrigeration cycle device 21 includes a refrigerant circuit 22 through which refrigerant circulates and flows.

  The equipment condenser 14 has a working fluid side heat exchange part 14a through which the working fluid of the equipment fluid circuit 10 flows, and a refrigerant side heat exchange part 14b through which the refrigerant of the refrigerant circuit 22 flows. The working fluid side heat exchange part 14a and the refrigerant side heat exchange part 14b are thermally connected so that heat exchange between the working fluid and the refrigerant is possible. The working fluid inside the working fluid-side heat exchange section 14a is cooled and condensed. Therefore, the working fluid side heat exchange part 14a constitutes a condensing part in which the working fluid condenses.

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

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

  Further, the refrigerant circuit 22 has a second expansion valve 32 and a refrigerant-side heat exchange section 14b connected in parallel with the first expansion valve 28 and the air-conditioning evaporator 30 by a refrigerant flow. The second expansion valve 32 reduces the pressure of the refrigerant flowing out of the air conditioning condenser 26. The refrigerant-side heat exchange unit 14b is an evaporation unit that evaporates the refrigerant by heat exchange with the working fluid flowing through the working fluid-side heat exchange unit 14a.

  Further, the refrigerant circuit 22 has an adjustment valve 34 for adjusting the flow rate of the refrigerant in the refrigerant flow path through which the refrigerant flows toward the refrigerant-side heat exchange section 14b. The regulating valve 34 has a valve closing function. By closing the adjustment valve 34, a first refrigerant circuit through which the refrigerant flows in the order of the compressor 24, the air conditioning condenser 26, the first expansion valve 28, and the air conditioning evaporator 30 is formed. By opening the regulating valve 34, in addition to the first refrigerant circuit, a second refrigerant circuit in which the refrigerant flows in the order of the compressor 24, the air conditioning condenser 26, the second expansion valve 32, and the refrigerant-side heat exchange unit 14b is formed. You.

  The gas passage 16 guides the gaseous working fluid evaporated in the equipment heat exchanger 12 to the equipment condenser 14. That is, the gas passage section 16 is a first flow path through which the working fluid flows from the equipment heat exchanger 12 as the evaporator to the equipment condenser 14 as the condenser. The gas passage section 16 has a lower end connected to the equipment heat exchanger 12 and an upper end connected to the equipment condenser 14. The gas passage portion 16 of the present embodiment is configured by a pipe in which a flow path through which a working fluid flows is formed.

  The liquid passage 18 guides the liquid working fluid condensed in the equipment condenser 14 to the equipment heat exchanger 12. In other words, the liquid passage 18 is a second flow path through which the working fluid flows from the equipment condenser 14 as the condenser to the equipment heat exchanger 12 as the evaporator. The liquid passage 18 has a lower end connected to the equipment heat exchanger 12 and an upper end connected to the equipment condenser 14. The liquid passage portion 18 of the present embodiment is configured by a pipe in which a flow path through which a working fluid flows is formed.

  Subsequently, a basic operation of the device temperature control device 1 of the present embodiment will be described with reference to FIG. The arrow DRg shown in FIG. 2 indicates the direction in which the vertical line extends, that is, the vertical direction.

  In the device temperature control device 1, when the battery temperature Tb of the battery pack BP rises due to self-heating during traveling of the vehicle or the like, the heat of the battery pack BP moves to the device heat exchanger 12. In the equipment heat exchanger 12, a part of the liquid working fluid WF evaporates by absorbing heat from the battery pack BP. The battery pack BP is cooled by the latent heat of vaporization of the working fluid WF existing inside the equipment heat exchanger BP, and its temperature decreases.

  The gaseous working fluid WF evaporated in the equipment heat exchanger 12 flows out of the equipment heat exchanger 12 into the gas passage 16 and passes through the gas passage 16 as shown by an arrow F11 in the figure. Move to the equipment condenser 14.

  In the equipment condenser 14, the gaseous working fluid WF dissipates heat, so that the gaseous working fluid WF condenses. The condensed liquid working fluid WF descends due to gravity. As a result, the liquid working fluid WF condensed in the equipment condenser 14 flows out of the equipment condenser 14 into the liquid passage portion 18 and, as indicated by an arrow F12 in the drawing, flows through the equipment through the liquid passage portion 18. To the heat exchanger 12. Then, in the equipment heat exchanger 12, a part of the inflowing liquid working fluid WF absorbs heat from the battery pack BP and evaporates.

  As described above, the equipment temperature controller 1 circulates between the equipment heat exchanger 12 and the equipment condenser 14 while the working fluid WF changes its phase between the gas state and the liquid state, and The battery pack BP is cooled by transferring heat from the condenser 12 to the equipment condenser 14. Further, the device temperature control device 1 has a configuration in which the working fluid WF naturally circulates inside the device fluid circuit 10 even if there is no driving force required for circulation of the working fluid by the compressor or the like.

  As shown in FIG. 1, the device temperature controller 1 includes a battery temperature sensor 41, a working fluid temperature sensor 42, a refrigerant temperature sensor 43, a working fluid pressure sensor 44, and a refrigerant pressure sensor 45.

  Battery temperature sensor 41 detects battery temperature Tb of battery pack BP. In the present embodiment, the battery temperature sensor 41 is installed above the battery pack BP. If the battery temperature Tb can be detected, the battery temperature sensor 41 may be installed at another place.

  The working fluid temperature sensor 42 detects the working fluid temperature Twf. In the present embodiment, the working fluid temperature sensor 42 is installed on an outer surface of a pipe constituting the liquid passage 18. The working fluid temperature sensor 42 detects the temperature of the pipe as the temperature of the liquid working fluid. As long as the temperature of the liquid working fluid can be detected, the working fluid temperature sensor 42 may be installed at another location. Further, the working fluid temperature sensor 42 may detect the temperature of the gaseous working fluid.

  The refrigerant temperature sensor 43 detects a refrigerant temperature Tr of the refrigerant circuit 22. The refrigerant temperature Tr is the temperature of the refrigerant flowing through the refrigerant-side heat exchange section 14b in the refrigerant circuit 22. In the present embodiment, the refrigerant temperature sensor 43 is installed on the surface of the refrigerant-side heat exchange unit 14b. The refrigerant temperature sensor 43 detects the temperature of the surface of the refrigerant-side heat exchange section 14b as the refrigerant temperature Tr. If the refrigerant temperature Tr can be detected, the refrigerant temperature sensor 43 may be installed at another place.

  The working fluid pressure sensor 44 detects the working fluid pressure Pw. In the present embodiment, the working fluid pressure sensor 44 is installed in the gas passage 16. The working fluid temperature sensor 42 detects the pressure of a gaseous working fluid. As long as the pressure of the gaseous working fluid can be detected, the working fluid pressure sensor 44 may be installed at another location. Further, the working fluid pressure sensor 44 may detect the pressure of a liquid working fluid. However, the pressure of the liquid working fluid fluctuates due to fluctuations in the liquid level. Therefore, it is preferable that the working fluid pressure sensor 44 detects the pressure of the gaseous working fluid.

  The refrigerant pressure sensor 45 detects the refrigerant pressure Pr of the refrigerant circuit 22. The refrigerant pressure Pr is the pressure of the refrigerant flowing through the refrigerant-side heat exchange unit 14b. That is, the refrigerant pressure Pr is the pressure of the refrigerant that has been depressurized by the second expansion valve 32 in the refrigerant circuit 22.

  As shown in FIG. 3, the device temperature control device 1 includes a control device 40. Various sensors such as a battery temperature sensor 41, a working fluid temperature sensor 42, a coolant temperature sensor 43, a working fluid pressure sensor 44, and a coolant pressure sensor 45 are connected to the input side of the control device 40. The components of the refrigeration cycle device 21 such as the compressor 24, the blower 27, and the regulating valve 34 are connected to the output side of the control device 40.

  The control device 40 controls the operation of the components 24, 27, and 34 of the refrigeration cycle device 21 based on input signals from various sensors, as shown in FIG. Each step shown in FIG. 4 configures a function realizing unit that realizes the function of the control device 40. The control flow illustrated in FIG. 4 is repeatedly executed while power is supplied to the control device 40.

  In step S11, control device 40 determines whether battery temperature Tb is higher than predetermined temperature Tth1. The predetermined temperature is, for example, 35 ° C. If the battery temperature Tb is lower than the predetermined temperature Tth1, a NO determination is made and the process proceeds to step S12. If the battery temperature Tb is higher than the predetermined temperature Tth1, a YES determination is made and the process proceeds to step S13.

  In step S12, the control device 40 stops the refrigeration cycle device 21 as the cooling device. That is, the control device 40 stops the compressor 24 and the blower 27. When the compressor 24 and the blower 27 are operated for the purpose of air conditioning, the control device 40 closes the adjustment valve 34 instead of stopping the refrigeration cycle device 21. Thereafter, the control device 40 ends the series of flows shown in FIG. 4, and starts the series of flows shown in FIG. 4 again.

  In step S13, the control device 40 brings the refrigeration cycle device 21 as a cooling device into an operating state. If the refrigeration cycle device 21 is in the stopped state, the control device 40 starts the operation of the refrigeration cycle device 21. That is, the control device 40 opens the adjustment valve 34. The control device 40 operates the compressor 24 and the blower 27. When the compressor 24 and the blower 27 are already operating for the purpose of air conditioning, but the adjustment valve 34 is closed and the cooling of the working fluid by the refrigeration cycle device 21 is stopped, the control device Reference numeral 40 indicates that the regulating valve 34 is in an open state. When the cooling of the working fluid by the refrigeration cycle apparatus 21 is started, the control device 40 sets the operation state of the refrigeration cycle apparatus 21 to the second operation state in which the cooling capacity of the refrigeration cycle apparatus 21 is larger than the first operation state. The operating state of the refrigeration cycle device 21 is the open state of the regulating valve 34 and the operating state of the compressor 24 and the blower 27. The cooling capacity is the ability to cool the working fluid from the first temperature to a second temperature lower than the first temperature.

  Thereby, the refrigerant flows through the second refrigerant circuit. In the equipment condenser 14, the working fluid is cooled by the refrigerant and condensed. In the equipment heat exchanger 12, the working fluid absorbs heat from the battery pack BP and evaporates. As a result, the battery pack BP is cooled. In step S13, if the refrigeration cycle device 21 is already in the operating state, the control device 40 continues the operation of the refrigeration cycle device 21. After step S13, the process proceeds to step S14.

  In step S14, control device 40 determines whether or not temperature difference Dt is smaller than predetermined temperature difference Tth2. The temperature difference Dt is a difference between the battery temperature Tb and the working fluid temperature Twf (that is, Tb-Twf). Control device 40 uses battery temperature sensor 41 and working fluid temperature sensor 42 to detect temperature difference Dt between battery temperature Tb and working fluid temperature Twf. The predetermined temperature difference Tth2 is, for example, 10 ° C. If temperature difference Dt is larger than predetermined temperature difference Tth2, control device 40 makes a NO determination and proceeds to step S15. If temperature difference Dt is smaller than predetermined temperature difference Tth2, control device 40 makes a YES determination and proceeds to step S16.

  In step S15, the control device 40 sets the operation state of the cooling device to the first operation state. If the refrigeration cycle device 21 is operated in the first operation state, the control device 40 continues the operation state.

  If the refrigeration cycle apparatus 21 is operated in the second operation state, the control device 40 changes to the first operation state in which the cooling capacity is smaller than in the second operation state. That is, control device 40 reduces the cooling capacity of refrigeration cycle device 21. Specifically, control device 40 reduces the rotation speed of compressor 24. For example, when the rotation speed of the compressor 24 is set to a second rotation speed larger than the first rotation speed, the control device 40 changes the rotation speed of the compressor 24 from the second rotation speed to the first rotation speed. I do. Thereby, the refrigerant discharge capacity of the compressor 24 is reduced. Further, control device 40 reduces the rotation speed of blower 27. For example, when the rotation speed of the blower 27 is set to a second rotation speed higher than the first rotation speed, the control device 40 changes the rotation speed of the blower 27 from the second rotation speed to the first rotation speed. Thereby, the heat radiation amount of the refrigerant is reduced. Further, the control device 40 reduces the valve opening of the regulating valve 34. For example, when the valve opening of the adjustment valve 34 is set to a second opening larger than the first opening, the control device 40 changes the valve opening of the adjustment valve 34 from the second opening to the first opening. Change to Thereby, the flow rate of the refrigerant in the refrigerant-side heat exchange section 14b is reduced.

  The control device 40 may perform at least one of the reduction of the rotation speed of the compressor 24, the reduction of the rotation speed of the blower 27, and the reduction of the flow rate by the adjustment valve 34. For example, the control device 40 may reduce the valve opening of the adjustment valve 34 without changing the rotation speeds of the compressor 24 and the blower 27. Thus, only the cooling capacity of the working fluid may be reduced without reducing the air conditioning capacity.

  At this time, the control device 40 may reduce the rotation speeds of the compressor 24 and the blower 27 to zero. That is, control device 40 may stop compressor 24 and blower 27 and stop refrigeration cycle device 21. Thereby, the cooling of the working fluid by the refrigeration cycle device 21 is stopped. Further, the control device 40 may stop the flow of the refrigerant to the refrigerant-side heat exchange unit 14b by reducing the valve opening degree until the regulating valve 34 is closed. Thereby, the cooling of the working fluid by the refrigeration cycle device 21 is stopped. Thus, reducing the cooling capacity of the refrigeration cycle device 21 includes stopping the cooling of the working fluid by the refrigeration cycle device 21.

  Thereafter, the control device 40 ends the series of flows shown in FIG. 4, and starts the series of flows shown in FIG. 4 again.

  In step S16, the control device 40 sets the operation state of the refrigeration cycle device 21 to the second operation state. If the refrigeration cycle device 21 is operated in the second operation state, the control device 40 continues the operation state.

  If the refrigeration cycle device 21 is operated in the first operation state, the control device 40 changes to the second operation state. That is, control device 40 increases the cooling capacity of refrigeration cycle device 21. Specifically, control device 40 increases the rotation speed of compressor 24. Thereby, the refrigerant discharge capacity of the compressor 24 increases. Further, control device 40 increases the rotation speed of blower 27. Thereby, the heat radiation amount of the refrigerant increases. Further, the control device 40 increases the valve opening of the regulating valve 34. Thereby, the flow rate of the refrigerant in the refrigerant-side heat exchange section 14b increases. The control device 40 may perform at least one of the increase in the rotation speed of the compressor 24, the increase in the rotation speed of the blower 27, and the increase in the flow rate by the adjustment valve 34.

  Thereafter, the control device 40 ends the series of flows shown in FIG. 4, and starts the series of flows shown in FIG. 4 again.

  Here, unlike the present embodiment, a case where the control device 40 does not perform the above-described step S15 will be described.

  Immediately after the cooling of the working fluid by the refrigeration cycle device 21 is started, the working fluid is cooled by the equipment condenser 14 and the pressure inside the entire equipment fluid circuit 10 is reduced as compared to before the cooling of the working fluid is started. . At this time, as shown in FIG. 5, under the same battery temperature Tb, the temperature difference Dt between the battery temperature Tb and the working fluid temperature Twf increases as the cooling capacity of the refrigeration cycle device 21 increases. When the temperature difference Dt is larger than the predetermined temperature difference Tth2, as shown in FIG. 6, the liquid working fluid causes intense boiling inside the equipment heat exchanger 12.

  Therefore, in the present embodiment, as described in steps S14 and S15, the control device 40 detects the temperature difference Dt between the battery temperature Tb and the working fluid temperature Twf. Then, when the control device 40 determines that the detected temperature difference Dt is larger than the predetermined temperature difference Tth2, the control device 40 controls at least one of the compressor 24, the blower 27, and the adjustment valve 34 to control the refrigeration cycle device 21. Reduce cooling capacity.

  According to this, it is possible to suppress the degree of cooling of the working fluid in the equipment condenser 14 under a condition where intense boiling occurs. That is, the temperature of the working fluid cooled by the refrigeration cycle device 21 can be increased. For this reason, the temperature difference Dt between the assembled battery BP and the working fluid can be made smaller than the predetermined temperature difference Tth2. Thereby, intense boiling inside the equipment heat exchanger 12 can be suppressed. As a result, it is possible to suppress the generation of abnormal noise and reduce the magnitude of the generated abnormal noise.

  As described above, in the present embodiment, the temperature of the working fluid is increased by reducing the cooling capacity of the refrigeration cycle device 21. Therefore, in the present embodiment, the refrigeration cycle device 21 constitutes a temperature adjustment unit that adjusts the temperature of the working fluid.

  Further, according to the present embodiment, it is possible to avoid the installation of the gas-liquid separator and the increase in the diameter of the pipe for preventing abnormal noise. For this reason, vehicle mountability is improved.

  In the present embodiment, a refrigeration cycle device 21 that is shared with an air conditioner is used. For this reason, when a large amount of cold heat is taken to the battery pack BP side by the refrigerant-side heat exchange section 14b during the operation of the air conditioner, the necessary cold heat in the air conditioning evaporator 30 is reduced, and the occupant feels uncomfortable. Air conditioning performance will be reduced. On the other hand, according to the present embodiment, it is possible to prevent the assembled battery BP from taking too much heat. Therefore, it is possible to prevent the air conditioning performance from lowering to an unpleasant level. As described above, when the cooling device that cools the working fluid is used for a purpose other than the cooling of the working fluid, it is possible to easily balance the difference in performance and balance.

  Further, in the present embodiment, the temperature difference Dt between the battery temperature Tb and the working fluid temperature Twf is used in the determination in step S14 of FIG. 4, but the determination is not limited to this. When intense boiling occurs, the temperature difference between the working fluid temperature Twf and the refrigerant temperature Tr is large, and the temperature difference between the battery temperature Tb and the refrigerant temperature Tr is also large. Therefore, in the determination in step S14 of FIG. 4, instead of the temperature difference Dt between the battery temperature Tb and the working fluid temperature Twf, the temperature difference Dt between the working fluid temperature Twf and the coolant temperature Tr, and the battery temperature Tb and the coolant temperature Tr May be used. The temperature difference Dt between the working fluid temperature Twf and the coolant temperature Tr is detected by the working fluid temperature sensor 42 and the coolant temperature sensor 43. The temperature difference Dt between the battery temperature Tb and the refrigerant temperature Tr is detected by the battery temperature sensor 41 and the refrigerant temperature sensor 43.

  As described above, the control device 40 may reduce the cooling capacity of the cooling device when determining that the temperature difference between the working fluid and the cooling source that cools the working fluid in the condensing section is larger than the predetermined temperature difference. . Further, the control device 40 may reduce the cooling capacity of the cooling device when it is determined that the temperature difference between the device and the cooling source that cools the working fluid in the condensing section is larger than the predetermined temperature difference.

(2nd Embodiment)
As shown in FIG. 7, the present embodiment differs from the first embodiment in the control of the control device 40. In the flowchart of FIG. 7, steps S11 and S14 of FIG. 4 are changed to steps S11a and S14a, respectively. The configuration of the device temperature controller 1 is the same as that of the first embodiment.

  When the battery temperature Tb of the battery pack BP rises, the working fluid absorbs heat from the battery pack BP in the equipment heat exchanger 12, so that the temperature of the working fluid also rises. As shown in FIG. 8, when the temperature of the working fluid increases, the saturation pressure of the working fluid also increases. Therefore, when the battery temperature Tb of the battery pack BP increases, the pressure of the working fluid increases.

  Therefore, in the present embodiment, as shown in FIG. 7, in step S11a, the control device 40 determines whether the working fluid pressure Pw is higher than a predetermined pressure Pth1. The predetermined pressure is, for example, 0.8 MPa. Thereby, the control device 40 determines whether the refrigeration cycle device 21 as the cooling device needs to be operated. If the working fluid pressure Pw is lower than the predetermined pressure Pth1, a NO determination is made and the process proceeds to step S12. If the working fluid pressure Pw is higher than the predetermined pressure Pth1, a YES determination is made and the process proceeds to step S13.

  In step S14a following step S13, the control device 40 determines whether the pressure difference Dp is smaller than a predetermined pressure difference Pth2. The pressure difference Dp is a difference between the saturation pressure Pb of the working fluid when the temperature of the working fluid is the battery temperature Tb and the working fluid pressure Pw detected by the working fluid pressure sensor 44 (that is, Pb-Pw). The saturation pressure Pb is calculated using the temperature detected by the battery temperature sensor 41 and the relationship between the saturation pressure and the temperature of the working fluid shown in FIG.

  When the temperature difference Dt between the battery temperature Tb and the working fluid temperature Twf is larger than the predetermined temperature difference Tth2, vigorous boiling occurs in the liquid working fluid. Therefore, in the first embodiment, the temperature difference Dt between the battery temperature Tb and the working fluid temperature Twf is used as an index of a condition under which intense boiling occurs. On the other hand, in the present embodiment, a pressure difference Dp between the conversion value Pb obtained by converting the battery temperature Tb into the pressure of the working fluid and the pressure difference Dp between the working fluid pressure Pw is used as an index of a condition under which severe boiling occurs.

  The predetermined pressure difference Pth2 is set to the magnitude of the pressure difference Dp at which intense boiling starts to occur when the pressure difference Dp increases. In other words, the predetermined pressure difference Pth2 is set such that the level of the abnormal noise generated from the device fluid circuit 10 is an allowable level. The predetermined pressure difference Pth2 is, for example, 0.4 MPa. If pressure difference Dp is greater than predetermined pressure difference Pth2, control device 40 makes a NO determination and proceeds to step S15. If pressure difference Dp is smaller than predetermined pressure difference Pth2, control device 40 makes a YES determination and proceeds to step S16.

  As described above, the controller 40 determines the saturation pressure of the working fluid in the working fluid circuit and the saturation pressure of the working fluid in the working fluid circuit when the temperature of the working fluid in the working fluid circuit is the same as the temperature of the device. Is calculated as the pressure difference. When determining that the calculated pressure difference is larger than the predetermined pressure difference, control device 40 reduces the cooling capacity of the cooling device.

  Also in the present embodiment, the cooling condition of the working fluid in the equipment condenser 14 can be suppressed under the condition where intense boiling occurs. Therefore, effects similar to those of the first embodiment can be obtained.

  In the present embodiment, in the determination in step S14a of FIG. 7, the pressure difference between the saturation pressure Pb of the working fluid calculated using the battery temperature Tb and the working fluid pressure Pw detected by the working fluid pressure sensor 44. Although Dp was used, it is not limited to this. When intense boiling occurs, the temperature difference between the working fluid temperature Twf and the refrigerant temperature Tr is large, and the temperature difference between the battery temperature Tb and the refrigerant temperature Tr is also large.

  Therefore, in the determination in step S14a of FIG. 7, the pressure difference Dp between the working fluid pressure Pw and the saturation pressure Pr of the working fluid calculated using the refrigerant temperature Tr may be used. The saturation pressure Pr is calculated using the temperature detected by the refrigerant temperature sensor 43 and the relationship between the saturation pressure of the working fluid and the temperature shown in FIG. Further, the refrigerant pressure detected by the refrigerant pressure sensor 45 may be used instead of the saturation pressure Pr. As described above, the controller 40 determines the saturation pressure of the working fluid in the working fluid circuit and the saturation of the working fluid in the working fluid circuit when the temperature of the working fluid in the working fluid circuit is the same as the temperature of the cooling source. A pressure difference that is a difference from the pressure may be calculated.

  In the determination in step S14a of FIG. 7, the pressure difference Dp between the working fluid saturation pressure Pb calculated using the battery temperature Tb and the working fluid saturation pressure Pr calculated using the refrigerant temperature Tr is used. You may. Also in this case, the refrigerant pressure detected by the refrigerant pressure sensor 45 may be used instead of the saturation pressure Pr. In this way, the control device 40 determines the saturation pressure of the working fluid in the working fluid circuit when the temperature of the working fluid in the working fluid circuit is the same as the temperature of the device, and A pressure difference that is a difference from the saturation pressure of the working fluid in the working fluid circuit when the temperature is the same as the temperature of the cooling source may be calculated.

(Third embodiment)
As shown in FIG. 9, the present embodiment is different from the first embodiment in that the device temperature controller 1 includes an air-cooled device condenser 50 instead of the device condenser 14.

  The equipment condenser 50 cools and condenses the working fluid of the equipment fluid circuit 10 by heat exchange with the air blown by the blower 51. Therefore, in the present embodiment, the blower 51 and its peripheral devices constitute a cooling device 54 for cooling the working fluid. The equipment condenser 50 constitutes a condensing section in which the working fluid condenses.

  Specifically, the device temperature control device 1 includes a blower 51, a case 52, and a door 53. The blower 51 blows air to the equipment condenser 50. The case 52 houses the blower 51 and the equipment condenser 50. The case 52 forms a ventilation passage in which the blast air flowing toward the equipment condenser 50 flows. The door 53 changes the opening ratio of the ventilation path. In the present embodiment, the case 52 and the door 53 are peripheral devices of the blower 51.

  The device temperature controller 1 includes an air temperature sensor 46 instead of the refrigerant temperature sensor 43 of the first embodiment. The air temperature sensor 46 detects the air temperature Ta. The air temperature Ta is the temperature of the air blown to the equipment condenser 50. In the present embodiment, the air temperature sensor 46 is installed on the surface of the equipment condenser 50. The air temperature sensor 46 detects the temperature of the surface of the equipment condenser 50 as the air temperature Ta. As long as the air temperature Ta can be detected, the air temperature sensor 46 may be installed in another place.

  As shown in FIG. 10, various sensors such as a battery temperature sensor 41, a working fluid temperature sensor 42, an air temperature sensor 46, and a working fluid pressure sensor 44 are connected to an input side of the control device 40. The blower 51 and the door 53 are connected to the output side of the control device 40.

  The control device 40 controls the operation of the blower 51 and the door 53 based on input signals from various sensors according to the flowchart of FIG. 4 described in the first embodiment.

  In the present embodiment, in step S12, the control device 40 stops the blower 51 constituting the cooling device 54. At this time, the control device 40 may make the door 53 closed or the door 53 open.

  In step S13, the control device 40 puts the cooling device 54 into an operating state. That is, if the blower 51 is in the stopped state, the control device 40 starts the operation of the blower 51. At this time, if the door 53 is closed, the control device 40 sets the door 53 to a completely open state. When the cooling of the working fluid by the blower 51 is started, the control device 40 sets the operation state of the cooling device 54 to the second operation state in which the cooling capacity is larger than the first operation state. The operation state of the cooling device 54 is the operation state of the blower 51 and the position state of the door 53.

  Thereby, air is blown to the equipment condenser 50 as indicated by an arrow F51 in FIG. In the equipment condenser 50, the working fluid is cooled by the blast air and condensed. In the equipment heat exchanger 12, the working fluid absorbs heat from the battery pack BP and evaporates. As a result, the battery pack BP is cooled. If the cooling device 54 is in the operating state in step S13, the control device 40 continues the operation of the cooling device 54.

  In step S15, the control device 40 sets the operation state of the cooling device 54 to the first operation state. If the cooling device 54 is operated in the second operation state, the control device 40 changes to the first operation state having a smaller cooling capacity than the second operation state. That is, control device 40 reduces the cooling capacity of cooling device 54.

  Specifically, control device 40 reduces the number of rotations of blower 51. For example, when the rotation speed of the blower 51 is set to a second rotation speed higher than the first rotation speed, the control device 40 changes the rotation speed of the blower 51 from the second rotation speed to the first rotation speed. Furthermore, the control device 40 reduces the opening ratio of the ventilation path by the door 53. For example, when the opening ratio of the ventilation path is set to a second opening ratio larger than the first opening ratio, the control device 40 sets the opening ratio of the ventilation passage from the second opening ratio to the first opening ratio. , The position of the door 53 is changed. As a result, the amount of air blown to the equipment condenser 50 is reduced. The control device 40 may perform only one of the reduction of the rotation speed of the blower 51 and the reduction of the opening ratio of the ventilation path.

  At this time, the control device 40 may reduce the rotation speed of the blower 51 to zero. That is, the control device 40 may stop the blower 51. In addition, the control device 40 may reduce the opening ratio of the door 53 to 0, so that the air supply to the equipment condenser 50 is stopped. Thus, the cooling of the working fluid by the cooling device 54 is stopped. As described above, reducing the cooling capacity of the cooling device 54 includes stopping the cooling of the working fluid by the cooling device 54.

  In step S16, the control device 40 sets the operation state of the cooling device 54 to the second operation state. If the cooling device 54 is operated in the second operation state, the control device 40 continues the operation state. If the cooling device 54 is operated in the first operation state, the control device 40 changes to the second operation state. That is, control device 40 increases the cooling capacity of cooling device 54. For example, the rotation speed of the blower 51 is increased. Thereby, the amount of air blown to the equipment condenser 50 is increased.

  In the present embodiment, the control device 40 controls at least one of the blower 51 and the door 53 to reduce the cooling capacity of the cooling device 54 under a condition where intense boiling occurs. Thereby, the cooling condition of the working fluid in the equipment condenser 50 can be suppressed. That is, the temperature of the working fluid cooled by the cooling device 54 can be increased. Therefore, also in the present embodiment, the same effect as in the first embodiment can be obtained.

  As described above, in the present embodiment, the temperature of the working fluid is increased by reducing the cooling capacity of the cooling device 54. Therefore, in the present embodiment, the cooling device 54 constitutes a temperature adjusting unit that adjusts the temperature of the working fluid.

  In the present embodiment, the control device 40 controls the operation of the blower 51 and the door 53 according to the flowchart of FIG. 4 described in the first embodiment, but according to the flowchart of FIG. 7 described in the second embodiment. The operation of the blower 51 and the door 53 may be controlled.

(Fourth embodiment)
As shown in FIG. 11, the present embodiment is different from the first embodiment in that the device temperature controller 1 includes a water-cooled device condenser 60 instead of the device condenser 14.

  The device temperature controller 1 includes a cooling water circuit 62 through which cooling water circulates. The cooling water is a cooling liquid containing water. The cooling liquid is a liquid heat medium for transporting heat. As the cooling water, for example, antifreeze or water is used.

  The equipment condenser 60 cools the working medium of the equipment fluid circuit 10 by heat exchange with the cooling water of the cooling water circuit 62. Therefore, in the present embodiment, the cooling water circuit 62 and its peripheral devices constitute a cooling device 66 for cooling the working fluid.

  The equipment condenser 60 has a working fluid side heat exchange part 60a through which the working fluid of the equipment fluid circuit 10 flows, and a cooling water side heat exchange part 60b through which the cooling water of the cooling water circuit 62 flows. The working fluid side heat exchange unit 60a and the cooling water side heat exchange unit 60b are thermally connected so that heat exchange between the working fluid and the cooling water is possible. The working fluid inside the working fluid-side heat exchange unit 60a is cooled and condensed. Therefore, the working fluid side heat exchange part 60a constitutes a condensing part in which the working fluid condenses.

  The cooling water circuit 62 is basically formed by connecting the water pump 63, the radiator 64, and the cooling water side heat exchange unit 60b. The device temperature controller 1 has a blower 65 as a peripheral device.

  The water pump 63 forms a cooling water flow by discharging the sucked cooling water. The radiator 64 is a heat exchanger that radiates cooling water by heat exchange with the air blown by the blower 65, that is, the outside air. The cooling water side heat exchange section 60b receives heat from the working fluid to the cooling water by heat exchange with the working fluid flowing through the working fluid side heat exchange section 60a.

  The device temperature controller 1 includes a cooling water temperature sensor 47 instead of the refrigerant temperature sensor 43 of the first embodiment. The cooling water temperature sensor 47 detects a cooling water temperature Twa. The cooling water temperature Twa is the temperature of the cooling water flowing through the equipment condenser 60. In the present embodiment, the cooling water temperature sensor 47 is installed on the surface of the cooling water side heat exchange unit 60b. The cooling water temperature sensor 47 detects the surface temperature of the cooling water side heat exchange unit 60b as the cooling water temperature Twa. As long as the cooling water temperature Twa can be detected, the cooling water temperature sensor 47 may be installed in another place.

  As shown in FIG. 12, various sensors such as a battery temperature sensor 41, a working fluid temperature sensor 42, a cooling water temperature sensor 47, and a working fluid pressure sensor 44 are connected to the input side of the control device 40. The water pump 63 and the blower 65 are connected to the output side of the control device 40.

  The control device 40 controls the operations of the water pump 63 and the blower 65 based on input signals from various sensors according to the flowchart of FIG. 4 described in the first embodiment.

  In the present embodiment, in step S12, the control device 40 stops the cooling device 66. Specifically, the water pump 63 and the blower 65 are stopped.

  In step S13, the control device 40 brings the cooling device 66 into an operating state. That is, if the water pump 63 and the blower 65 are in a stopped state, the operation of the water pump 63 and the blower 65 is started. At this time, the control device 40 sets the operation state of the cooling device 66 to the second operation state in which the cooling capacity is larger than the first operation state. The operation state of the cooling device 66 is an operation state of the water pump 63 and the blower 65.

  Thereby, as indicated by arrows F61 and F62 in FIG. 11, the cooling water flows through the equipment condenser 60. In the equipment condenser 60, the working fluid is cooled by the cooling water and condensed. In the equipment heat exchanger 12, the working fluid absorbs heat from the battery pack BP and evaporates. As a result, the battery pack BP is cooled. In step S13, if the cooling device 66 is already in the operating state, the control device 40 continues the operation of the cooling device 66.

  In step S15, the control device 40 sets the operation state of the cooling device 66 to the first operation state. If the cooling device 66 is operated in the second operation state, the control device 40 changes to the first operation state having a smaller cooling capacity than the second operation state. That is, control device 40 reduces the cooling capacity of cooling device 66.

  Specifically, control device 40 reduces the number of rotations of water pump 63. For example, when the rotation speed of the water pump 63 is set to a second rotation speed greater than the first rotation speed, the control device 40 changes the rotation speed of the water pump 63 from the second rotation speed to the first rotation speed. I do. Thereby, the flow rate of the cooling water flowing through the cooling water circuit 62 is reduced. Further, control device 40 reduces the rotation speed of blower 65. For example, when the rotation speed of the blower 65 is set to a second rotation speed higher than the first rotation speed, the control device 40 changes the rotation speed of the blower 65 from the second rotation speed to the first rotation speed. Thereby, the amount of heat radiation of the cooling water in the radiator 64 is reduced.

  Note that the control device 40 may perform only one of the reduction of the rotation speed of the water pump 63 and the reduction of the rotation speed of the blower 65. Further, the control device 40 may reduce the rotation speed of the water pump 63 to 0 and stop the water pump 63. In addition, the control device 40 may reduce the rotation speed of the blower 65 to 0 and stop the blower 65. Thus, the cooling of the working fluid by the cooling device 66 is stopped. As described above, reducing the cooling capacity of the cooling device 66 includes stopping the cooling of the working fluid by the cooling device 66.

  In step S16, the control device 40 sets the operation state of the cooling device 66 to the second operation state. If the cooling device 66 is operated in the second operation state, the control device 40 continues the operation state. If the cooling device 66 is operated in the first operation state, the control device 40 changes to the second operation state. That is, the control device 40 increases the cooling capacity of the cooling device 66. For example, the rotation speed of the water pump 63 is increased. Thereby, the flow rate of the cooling water flowing through the cooling water circuit 62 is increased.

  In the present embodiment, the control device 40 controls at least one of the water pump 63 and the blower 65 to reduce the cooling capacity of the cooling device 66 under the condition where intense boiling occurs. Thereby, the cooling condition of the working fluid in the equipment condenser 50 can be suppressed. That is, the temperature of the working fluid cooled by the cooling device 66 can be increased. Therefore, also in the present embodiment, the same effect as in the first embodiment can be obtained.

  As described above, in the present embodiment, the temperature of the working fluid is increased by reducing the cooling capacity of the cooling device 66. Therefore, in the present embodiment, the cooling device 66 constitutes a temperature adjusting unit for adjusting the temperature of the working fluid.

  Further, in the present embodiment, the control device 40 controls the operations of the water pump 63 and the blower 65 according to the flowchart of FIG. 4 described in the first embodiment, but according to the flowchart of FIG. 7 described in the second embodiment. , The operation of the water pump 63 and the blower 65 may be controlled.

  In the present embodiment, cooling water, that is, a cooling liquid containing water is used, but a cooling liquid containing no water may be used.

(Fifth embodiment)
As shown in FIG. 13, the present embodiment is different from the first embodiment in that the device temperature controller 1 includes a device condenser 70 that cools a working fluid with a Peltier element 72 instead of the device condenser 14. Different from form. In this embodiment, the Peltier device 72 and its peripheral devices constitute a cooling device 75 for cooling the working fluid.

  The equipment condenser 70 includes a working fluid-side heat exchange unit 70a through which the working fluid flows, and a Peltier element 72 that cools the working fluid. The equipment condenser 70 cools and condenses the working fluid flowing through the working fluid-side heat exchange section 70 a by the Peltier element 72. Therefore, the working fluid side heat exchange part 70a constitutes a condensing part in which the working fluid condenses.

  The Peltier element 72 is a thermoelectric element that converts electric energy into heat energy. The Peltier element 72 has a cooling surface 72a and a heat radiation surface 72b. The cooling surface 72a is thermally connected to the working fluid side heat exchange unit 70a. The heat radiation surface 72b is provided with heat radiation fins 73 for promoting heat radiation. The device temperature control device 1 includes a blower 74 that forms a flow of air that passes through the radiation fins 73. The heat is radiated from the radiation fins 73 to the air by the blower 74. In this embodiment, the radiation fins 73 and the blower 74 are peripheral devices of the Peltier element 72.

  The device temperature controller 1 includes a cooling surface temperature sensor 48 instead of the refrigerant temperature sensor 43 of the first embodiment. The cooling surface temperature sensor 48 detects a cooling surface temperature Tp of the Peltier element 72. In the present embodiment, the cooling surface temperature sensor 48 is provided on the cooling surface 72 a of the Peltier device 72.

  As shown in FIG. 14, various sensors such as a battery temperature sensor 41, a working fluid temperature sensor 42, a cooling surface temperature sensor 48, and a working fluid pressure sensor 44 are connected to the input side of the control device 40. The Peltier device 72 and the blower 74 are connected to the output side of the control device 40.

  The control device 40 controls the operation of the Peltier element 72 and the blower 74 based on input signals from various sensors according to the flowchart of FIG. 4 described in the first embodiment.

  In the present embodiment, in step S12, the control device 40 stops the Peltier device 72 and the blower 74 constituting the cooling device 75.

  In step S13, the control device 40 brings the cooling device 75 into an operating state. That is, when the Peltier element 72 and the blower 74 are in a stopped state, the control device 40 starts the operation of the Peltier element 72 and the blower 74. At this time, the control device 40 sets the operation state of the cooling device 75 to the second operation state in which the cooling capacity is larger than the first operation state. The operation state of the cooling device 75 is an operation state of the Peltier element 72 and the blower 74.

  Thereby, the temperature of the cooling surface 72a of the Peltier element 72 becomes lower than the temperature of the heat radiation surface 72b. In the equipment condenser 70, the cooling surface 72a absorbs heat from the working fluid, and the heat radiation surface 72b radiates heat to the blown air. Thus, the working fluid is cooled and condensed in the equipment condenser 70. In the equipment heat exchanger 12, the working fluid absorbs heat from the battery pack BP and evaporates. As a result, the battery pack BP is cooled. If the cooling device 75 is in the operating state in step S13, the control device 40 continues the operation of the cooling device 75.

  In step S15, the control device 40 sets the operation state of the cooling device 75 to the first operation state. If the cooling device 75 is operated in the second operation state, the control device 40 changes to the first operation state having a smaller cooling capacity than the second operation state. That is, the control device 40 reduces the cooling capacity of the cooling device 75.

  Specifically, control device 40 reduces the amount of power supplied to Peltier element 72. Thus, the temperature of the cooling surface 72a increases. Further, control device 40 reduces the number of rotations of blower 74. Thereby, the amount of heat radiation from the heat radiation surface 72b is reduced. This also raises the temperature of the cooling surface 72a.

  The control device 40 may perform only one of the reduction of the amount of power supplied to the Peltier element 72 and the reduction of the rotation speed of the blower 74. Further, control device 40 may reduce the supplied power amount to 0 and stop Peltier element 72. Further, control device 40 may reduce the number of revolutions of blower 74 to 0 and stop blower 74. Thus, the cooling of the working fluid by the cooling device 75 is stopped. As described above, reducing the cooling capacity of the cooling device 75 includes stopping the cooling of the working fluid by the cooling device 75.

  In the present embodiment, the control device 40 controls at least one of the Peltier element 72 and the blower 74 to reduce the cooling capacity of the cooling device 75 under a condition where intense boiling occurs. Thereby, the cooling condition of the working fluid in the equipment condenser 50 can be suppressed. That is, the temperature of the working fluid cooled by the cooling device 75 can be increased. Therefore, also in the present embodiment, the same effect as in the first embodiment can be obtained.

  As described above, in the present embodiment, the temperature of the working fluid is increased by reducing the cooling capacity of the cooling device 75. Therefore, in the present embodiment, the cooling device 75 constitutes a temperature adjusting unit for adjusting the temperature of the working fluid.

  Further, in the present embodiment, the control device 40 controls the operation of the Peltier element 72 and the blower 74 according to the flowchart of FIG. 4 described in the first embodiment, but according to the flowchart of FIG. 7 described in the second embodiment. , The operation of the Peltier element 72 and the blower 74 may be controlled.

(Sixth embodiment)
As shown in FIG. 15, the present embodiment is different from the first embodiment in that the device temperature controller 1 includes a variable thermal resistor 80. Other configurations are the same as those of the first embodiment.

  The variable thermal resistor 80 is provided in the equipment condenser 14. The variable thermal resistor 80 is sandwiched between a working fluid side heat exchange part 14a as a working fluid condensing part and a refrigerant side heat exchange part 14b as a refrigerant evaporating part. The variable thermal resistor 80 is disposed in the entire area or a part between the working fluid side heat exchange section 14a and the refrigerant side heat exchange section 14b. Thereby, the variable thermal resistor 80 is thermally connected between the working fluid side heat exchange part 14a and the refrigerant side heat exchange part 14b.

  The variable thermal resistor 80 is capable of changing the thermal resistance when an external stimulus such as electricity, movement, or heat is applied. In the present embodiment, a thermal switch element 81 is used as the variable thermal resistor 80. As described in WO2004 / 068604, the thermal switching element 81 includes a material whose thermal conductivity changes when electric energy is applied.

  As shown in FIG. 16, various sensors 41 to 45 are connected to the input side of the control device 40. The components 24, 27, and 34 of the refrigeration cycle device 21 are connected to the output side of the control device 40. Further, a variable thermal resistor 80 is connected to the output side of the control device 40. The control device 40 changes the thermal resistance of the variable thermal resistor 80 by outputting a control signal to the variable thermal resistor 80. That is, the control device 40 controls the variable thermal resistor 80 to change the thermal resistance between the working fluid side heat exchange unit 14a and the refrigerant side heat exchange unit 14b.

  As shown in FIG. 17, the control device 40 controls the operation of the components 24, 27, and 34 of the refrigeration cycle device 21 and the thermal resistance of the variable thermal resistor 80 based on input signals from various sensors. . Note that each step illustrated in FIG. 17 configures a function implementing unit that implements the function of the control device 40. In the flowchart of FIG. 17, steps S15 and S16 of FIG. 4 are changed to steps S21 and S22, respectively.

  In the present embodiment, in step S12, the control device 40 brings the refrigeration cycle device 21 into a stopped state.

  In step S13, the control device 40 puts the refrigeration cycle device 21 into an operating state. When the operation of the refrigeration cycle apparatus 21 is started, the operation state of the refrigeration cycle apparatus 21 is set to have a predetermined cooling capacity. Thereby, the refrigerant of the refrigeration cycle device 21 flows through the equipment condenser 14. In the equipment condenser 14, the working fluid is cooled by the refrigerant and condensed. Further, when the operation of the refrigeration cycle device 21 is started, the control device 40 sets the state of the variable thermal resistor 80 to the second state in which the thermal resistance is smaller than the first state.

  In step S14, if the determination is NO, the process proceeds to step S21, and if the determination is YES, the process proceeds to step S22.

  In step S21, the control device 40 increases the thermal resistance of the variable thermal resistor 80. If the variable thermal resistor 80 is in the second state, the control device 40 changes to the first state in which the thermal resistance is higher than the second state. When the variable thermal resistor 80 is in the first state, the thermal resistance of the variable thermal resistor 80 is not changed. After that, the control device 40 ends the series of flows shown in FIG. 17, and starts the series of flows shown in FIG. 17 again.

  In step S22, the control device 40 reduces the thermal resistance of the variable thermal resistor 80. If the variable thermal resistor 80 is in the second state where the thermal resistance is smaller than the first state, the thermal resistance of the variable thermal resistor 80 is not changed. If the variable thermal resistor 80 is in the first state, the control device 40 changes to the second state. After that, the control device 40 ends the series of flows shown in FIG. 17, and starts the series of flows shown in FIG. 17 again.

  In the present embodiment, in steps S14 and S21, when the controller 40 determines that the detected temperature difference Dt is larger than the predetermined temperature difference Tth2, the controller 40 increases the thermal resistance of the variable thermal resistor 80.

  According to this, heat transfer between the working fluid-side heat exchange unit 14a and the refrigerant-side heat exchange unit 14b can be suppressed under the condition where intense boiling occurs. For this reason, the cooling condition of the working fluid in the equipment condenser 14 can be suppressed. That is, the temperature of the working fluid cooled by the refrigeration cycle device 21 can be increased. Therefore, according to the present embodiment, the same effect as that of the first embodiment can be obtained.

  As described above, in the present embodiment, the temperature of the working fluid is increased by the variable thermal resistor 80. Therefore, in the present embodiment, the variable thermal resistor 80 constitutes a temperature adjusting unit for adjusting the temperature of the working fluid.

  In the present embodiment, the thermal switch element 81 is employed as the variable thermal resistor 80, but the present invention is not limited to this. As the variable thermal resistor 80, a contact-type thermal resistor using a bimetal may be employed. This includes, for example, two members and a connecting part connecting the two members. The connection is made of bimetal. When the control device 40 operates the heater, heat is applied to the bimetal. The bimetal deforms when heat is applied. Thereby, the connection part is separated from at least one of the two members. Therefore, the thermal connection between the two members is switched from the connected state to the disconnected state. As a result, the thermal resistance increases.

  Further, as the variable thermal resistor 80, a contact thermal resistor using an electric motor may be employed. This includes, for example, two members and a connecting part connecting the two members. The connecting portion is movable by an electric motor. The control device 40 outputs a control signal to operate the electric motor. That is, electric power is supplied to the electric motor. Thereby, the connection part is separated from at least one of the two members. Therefore, the thermal connection between the two members is switched from the connected state to the disconnected state. As a result, the thermal resistance increases.

(Seventh embodiment)
As shown in FIG. 18, the present embodiment differs from the sixth embodiment in the control of the control device 40. In the flowchart of FIG. 18, steps S11 and S14 of FIG. 17 are changed to steps S11a and S14a, respectively, as in the second embodiment. The configuration of the device temperature controller 1 is the same as that of the sixth embodiment.

  Thus, in step S11a, the determination may be made using the working fluid pressure Pw. In step S14a, the determination may be made using the pressure difference Dp.

(Eighth embodiment)
As shown in FIG. 19, the present embodiment is different from the third embodiment in that the device temperature controller 1 includes a variable thermal resistor 80.

  The variable thermal resistor 80 is provided in the air-cooled device condenser 50. The equipment condenser 50 includes a working fluid-side heat exchange part 50 a and a radiation fin 55. The working fluid side heat exchanging section 50a is a working fluid condensing section. The radiating fins 55 are radiating portions that radiate heat to the air blown from the blower 51. In the present embodiment, the cooling fins 55 are composed of the radiation fins 55 in addition to the blower 51 and the like.

  The variable thermal resistor 80 is sandwiched between the working fluid side heat exchange part 50 a and the radiation fin 55. Thus, the variable thermal resistor 80 is thermally connected between the working fluid side heat exchange part 50 a and the radiation fin 55. That is, the working fluid-side heat exchange unit 50 a is thermally connected to the cooling device 54 via the variable thermal resistor 80.

  Further, an air temperature sensor 46 is provided on the surface of the radiation fin 55. As long as the air temperature Ta can be detected, the air temperature sensor 46 may be installed in another place.

  As shown in FIG. 20, various sensors 41, 42, 44, and 46 are connected to the input side of the control device 40, as in the third embodiment. On the output side of the control device 40, a blower 51 and a variable thermal resistor 80 are connected.

  The control device 40 controls the operation of the blower 51 and the thermal resistance of the variable thermal resistor 80 based on input signals from various sensors according to the flowchart of FIG. 17 described in the sixth embodiment.

  In the present embodiment, in step S12, the control device 40 puts the cooling device 54 into a stopped state. In step S13, the control device 40 puts the cooling device 54 into an operating state. When the operation of the cooling device 54 is started, the operation state of the cooling device 54 is set so as to have a predetermined cooling capacity. Thereby, air is blown to the equipment condenser 50. In the equipment condenser 50, the working fluid is cooled by the blast air and condensed. Further, when the operation of the cooling device 54 is started, the state of the variable thermal resistor 80 is set to the second state having a smaller thermal resistance than the first state.

  Also in the present embodiment, the control device 40 increases the thermal resistance of the variable thermal resistor 80 in the conditions of intense boiling in steps S14 and S21. Thereby, the cooling condition of the working fluid in the equipment condenser 50 can be suppressed. That is, the temperature of the working fluid cooled by the cooling device 54 can be increased. Therefore, also in the present embodiment, the same effect as in the first embodiment can be obtained.

  Thus, also in the present embodiment, the temperature of the working fluid is raised by the variable thermal resistor 80. Therefore, the variable thermal resistor 80 constitutes a temperature adjusting unit for adjusting the temperature of the working fluid.

  Further, in the present embodiment, the control device 40 controls according to the flowchart of FIG. 17, but controls the operation of the blower 51 and the thermal resistance of the variable thermal resistor 80 according to the flowchart of FIG. 18 described in the seventh embodiment. You may.

(Ninth embodiment)
As shown in FIG. 21, the present embodiment is different from the fourth embodiment in that the device temperature controller 1 includes a variable thermal resistor 80.

  The variable thermal resistor 80 is provided in the water-cooled device condenser 60. The variable thermal resistor 80 is interposed between the working fluid side heat exchange part 60 a and the radiation fin 55. Thus, the variable thermal resistor 80 is thermally connected between the working fluid side heat exchange unit 60a and the cooling water side heat exchange unit 60b. That is, the working fluid-side heat exchange unit 60 a is thermally connected to the cooling device 66 via the variable heat resistor 80.

  As shown in FIG. 22, various sensors 41, 42, 44, and 47 are connected to the input side of the control device 40, as in the fourth embodiment. The water pump 63, the blower 65, and the variable thermal resistor 80 are connected to the output side of the control device 40.

  The control device 40 controls the operation of the water pump 63 and the blower 65 and the thermal resistance of the variable thermal resistor 80 based on input signals from various sensors according to the flowchart of FIG. 17 described in the sixth embodiment. .

  In the present embodiment, in step S12, the control device 40 brings the cooling device 66 into a stopped state. In step S13, the control device 40 puts the cooling device 66 into an operating state. When the operation of the cooling device 66 is started, the operation state of the cooling device 66 is set to have a predetermined cooling capacity. As a result, the cooling water flows through the equipment condenser 60. In the equipment condenser 60, the working fluid is cooled by the cooling water and condensed. Further, when the operation of the cooling device 66 is started, the state of the variable thermal resistor 80 is set to the second state having a smaller thermal resistance than the first state.

  Also in the present embodiment, the control device 40 increases the thermal resistance of the variable thermal resistor 80 in the conditions of intense boiling in steps S14 and S21. Thereby, the cooling condition of the working fluid in the equipment condenser 50 can be suppressed. That is, the temperature of the working fluid cooled by the cooling device 66 can be increased. Therefore, also in the present embodiment, the same effect as in the first embodiment can be obtained.

  Thus, also in the present embodiment, the temperature of the working fluid is raised by the variable thermal resistor 80. Therefore, the variable thermal resistor 80 constitutes a temperature adjusting unit for adjusting the temperature of the working fluid.

  Further, in the present embodiment, the control device 40 controls according to the flowchart of FIG. 17, but according to the flowchart of FIG. 18 described in the seventh embodiment, the operation of the water pump 63 and the blower 65 and the heat of the variable thermal resistor 80 are controlled. The resistance may be controlled.

(Tenth embodiment)
As shown in FIG. 23, the present embodiment is different from the first embodiment in that the device temperature controller 1 includes a heating element 90. Other configurations are the same as those of the first embodiment.

  The heating element 90 is attached to an outer surface of a pipe constituting the liquid passage portion 18. The heating element 90 heats the working fluid inside the liquid passage 18 by generating heat. More specifically, the heating element 90 heats the liquid working fluid falling from the equipment condenser 14. That is, the heating element 90 heats the working fluid cooled by the equipment condenser 14. As the heating element 90, a resistance heating element, a Peltier element, or the like is used.

  The heating element 90 can be switched between operation and stop. When the heating element 90 operates, the working fluid is heated. Thereby, the temperature of the working fluid increases as compared to before the operation of the heating element 90 starts. When the heating element 90 has been operated but stopped, the heating of the working fluid is stopped. As a result, the temperature of the working fluid decreases as compared to when the heating element 90 is operating. Therefore, in the present embodiment, the heating element 90 constitutes a temperature adjusting section for adjusting the temperature of the working fluid.

  As shown in FIG. 24, various sensors 41 to 45 are connected to the input side of the control device 40. The components 24, 27, and 34 of the refrigeration cycle device 21 are connected to the output side of the control device 40. Further, a heating element 90 is connected to the output side of the control device 40. The control device 40 controls the operation and stop of the heating element 90 by outputting a control signal to the heating element 90.

  As shown in FIG. 25, the control device 40 controls the operation of the components 24, 27, and 34 of the refrigeration cycle device 21 and the operation of the heating element 90 based on input signals from various sensors. Each step illustrated in FIG. 25 configures a function realizing unit that realizes the function of the control device 40. In the flowchart of FIG. 25, steps S15 and S16 of FIG. 4 are changed to steps S31 and S32, respectively.

  In the present embodiment, in step S12, the control device 40 brings the refrigeration cycle device 21 into a stopped state.

  In step S13, the control device 40 puts the refrigeration cycle device 21 into an operating state. When the operation of the refrigeration cycle apparatus 21 is started, the operation state of the refrigeration cycle apparatus 21 is set to have a predetermined cooling capacity. Thereby, the refrigerant of the refrigeration cycle device 21 flows through the equipment condenser 14. In the equipment condenser 14, the working fluid is cooled by the refrigerant and condensed. Further, at the time of starting the operation of the refrigeration cycle device 21, the control device 40 stops the heating element 90.

  In step S14, if the determination is NO, the process proceeds to step S31, and if the determination is YES, the process proceeds to step S32.

  In step S31, the control device 40 sets the heating element 90 to an operating state. After that, the control device 40 ends the series of flows shown in FIG. 25, and starts the series of flows shown in FIG. 25 again.

  In step S32, the control device 40 brings the heating element 90 into a stopped state. After that, the control device 40 ends the series of flows shown in FIG. 25, and starts the series of flows shown in FIG. 25 again.

  In the present embodiment, in steps S14 and S31, the control device 40 activates the heating element 90 when determining that the detected temperature difference Dt is larger than the predetermined temperature difference Tth2.

  According to this, it is possible to increase the temperature of the working fluid cooled by the refrigeration cycle device 21 under the condition where intense boiling occurs. Therefore, according to the present embodiment, the same effect as that of the first embodiment can be obtained.

  In the present embodiment, when the heating element 90 operates, the working fluid condensed in the equipment condenser 14 re-boils. Thereby, the amount of the liquid working fluid returning to the equipment heat exchanger 12 is reduced.

  Further, in the present embodiment, the heating element 90 is attached to the outer surface of the pipe constituting the liquid passage portion 18, but is not limited to this. The heating element 90 may be arranged inside a pipe constituting the liquid passage section 18. Further, the heating element 90 may be disposed inside or outside the heat exchanger 12 for equipment. Thereby, the liquid working fluid inside the equipment heat exchanger 12 may be heated. As described above, the heating element 90 only needs to be installed at a portion where the liquid working fluid in the device fluid circuit 10 can be heated.

(Eleventh embodiment)
As shown in FIG. 26, the present embodiment is different from the tenth embodiment in the control of the control device 40. In the flowchart of FIG. 26, steps S11 and S14 of FIG. 25 are changed to steps S11a and S14a, respectively, as in the second embodiment. The configuration of the device temperature controller 1 is the same as that of the tenth embodiment.

  Thus, in step S11a, the determination may be made using the working fluid pressure Pw. In step S14a, the determination may be made using the pressure difference Dp.

(Twelfth embodiment)
As shown in FIG. 27, the present embodiment is different from the third embodiment in that the device temperature controller 1 includes a heating element 90.

  The heating element 90 is the same as in the tenth embodiment. In the present embodiment, similarly to the third embodiment, the working fluid is cooled by the cooling device 54 including the blower 51 in the equipment condenser 50.

  As shown in FIG. 28, various sensors 41, 42, 44, and 46 are connected to the input side of the control device 40, as in the third embodiment. On the output side of the control device 40, a blower 51 and a heating element 90 are connected.

  The control device 40 controls the operation of the blower 51 and the operation of the heating element 90 based on input signals from various sensors according to the flowchart of FIG. 25 described in the tenth embodiment.

  In the present embodiment, in step S12, the control device 40 puts the cooling device 54 into a stopped state. In step S13, the control device 40 puts the cooling device 54 into an operating state. When the operation of the cooling device 54 is started, the operation state of the cooling device 54 is set so as to have a predetermined cooling capacity. Thereby, air is blown to the equipment condenser 50. In the equipment condenser 50, the working fluid is cooled by the blast air and condensed.

  Also in this embodiment, similarly to the tenth embodiment, the control device 40 activates the heating element 90 in steps S14 and S31 under the condition where intense boiling occurs. Thereby, the temperature of the working fluid cooled by the cooling device 54 can be increased. Therefore, according to the present embodiment, the same effect as that of the first embodiment can be obtained.

  In the present embodiment, the control device 40 controls the operation of the blower 51 and the heating element 90 according to the flowchart of FIG. 25, but may control the operation according to the flowchart of FIG. 26 described in the eleventh embodiment.

(Thirteenth embodiment)
As shown in FIG. 29, the present embodiment is different from the fourth embodiment in that the device temperature controller 1 includes a heating element 90.

  The heating element 90 is the same as in the tenth embodiment. In the present embodiment, similarly to the fourth embodiment, in the equipment condenser 60, the working fluid is cooled by the cooling device 66 including the cooling water circuit 62.

  As shown in FIG. 30, various sensors 41, 42, 44, and 47 are connected to the input side of the control device 40, as in the fourth embodiment. The water pump 63, the blower 65, and the heating element 90 are connected to the output side of the control device 40.

  The control device 40 controls the operation of the water pump 63 and the blower 65 and the operation of the heating element 90 based on input signals from various sensors according to the flowchart of FIG. 25 described in the tenth embodiment.

  In the present embodiment, in step S12, the control device 40 brings the cooling device 66 into a stopped state. In step S13, the control device 40 puts the cooling device 66 into an operating state. When the operation of the cooling device 66 is started, the operation state of the cooling device 66 is set to have a predetermined cooling capacity. As a result, the cooling water flows through the equipment condenser 60. In the equipment condenser 60, the working fluid is cooled by the cooling water and condensed. When the operation of the cooling device 66 is started, the heating element 90 is stopped.

  Also in this embodiment, similarly to the tenth embodiment, the control device 40 activates the heating element 90 in steps S14 and S31 under the condition where intense boiling occurs. Thus, the temperature of the working fluid cooled by the cooling device 66 can be increased. Therefore, according to the present embodiment, the same effect as that of the first embodiment can be obtained.

  In the present embodiment, the control device 40 controls the operations of the water pump 63, the blower 65, and the heating element 90 according to the flowchart in FIG. 25, but controls according to the flowchart in FIG. 26 described in the eleventh embodiment. Is also good.

(Other embodiments)
(1) In the tenth to thirteenth embodiments, the device temperature control device 1 includes the cooling device that cools the working fluid in the condensing unit, but may not include the cooling device.

  (2) In the first, sixth, and tenth embodiments, in the refrigeration cycle apparatus 21, the refrigerant-side heat exchange section 14b of the equipment condenser 14 is connected in parallel to the air conditioning evaporator 30. , But is not limited to this. The refrigerant-side heat exchange section 14b may be connected in series with the refrigerant flow downstream of the evaporator 30 for air conditioning.

  (3) In the first, sixth, and tenth embodiments, the refrigeration cycle device 21 is used for the equipment temperature controller 1 and the vehicle air conditioner, but is not limited thereto. The refrigeration cycle device 21 may be dedicated to the device temperature control device 1.

  (4) In each of the above embodiments, the equipment heat exchanger 12 has only the cooling function of cooling the battery pack BP. However, the equipment heat exchanger 12 has a cooling function of heating the battery. It may have a function. That is, the device temperature controller 1 may adjust the battery temperature of the battery pack BP by cooling or heating the battery pack BP.

  (5) In each of the above embodiments, the object to be cooled by the device temperature controller 1 is a battery, but is not limited thereto. The object to be cooled may be an electronic device mounted on a vehicle other than the battery. Further, the object to be cooled is not limited to the electronic device installed in the vehicle. The object to be cooled may be an electronic device installed in a place other than the vehicle.

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

  (7) In each of the above embodiments, the control device 40 increases the temperature of the working fluid in the device fluid circuit 10 when the temperature difference between the device and the liquid working fluid is larger than a predetermined temperature difference. Although the temperature controller is controlled, the invention is not limited to this. When the temperature difference between the device and the liquid working fluid is larger than the predetermined temperature difference, the control device 40 may control the temperature adjustment unit so as to suppress a decrease in the temperature of the working fluid in the device fluid circuit 10. . According to this, it is possible to suppress an increase in the temperature difference between the device and the liquid working fluid as compared to a case where the temperature decrease of the working fluid is not suppressed. For this reason, intense boiling generated in the equipment heat exchanger 12 can be suppressed.

  To suppress the temperature decrease of the working fluid, when the temperature of the working fluid changes to the side where the temperature of the working fluid decreases with the passage of time, the temperature of the working fluid after the control of the temperature adjustment unit is set to the temperature. This includes making the temperature of the working fluid equal to the temperature at a certain point before the control of the adjusting unit. For example, in the first embodiment, the predetermined temperature difference in step S14 is changed to a value smaller than the predetermined temperature difference Tth2 in FIG. Thus, the control device 40 performs steps S14 and S15 before the temperature difference Dt reaches the predetermined temperature difference Tth2. In step S15, the control device 40 controls the operation of the refrigeration cycle device 21 so as to maintain the temperature of the working fluid. According to this, it is possible to prevent the temperature difference Dt from becoming larger than the predetermined temperature difference Tth2.

  Note that the predetermined temperature difference in step S14 may be the predetermined temperature difference Tth2 in FIG. In this case, the temperature difference Dt does not increase any more by performing the step S15 by the control device 40. For this reason, the intensity of boiling can be reduced as compared with the case where the temperature difference Dt becomes larger than that.

  Further, to suppress the temperature decrease of the working fluid, when the temperature of the working fluid changes to the side where the temperature of the working fluid decreases with time, the temperature of the working fluid of the device fluid circuit 10 decreases. This includes making the gradient of the temperature change smaller than in the case where it is not suppressed. For example, in the first embodiment, the predetermined temperature difference in step S14 is changed to a value smaller than the predetermined temperature difference Tth2 in FIG. Thus, the control device 40 performs steps S14 and S15 before the temperature difference Dt reaches the predetermined temperature difference Tth2. In step S15, the operation of the refrigeration cycle device 21 is controlled such that the gradient of the temperature change of the working fluid when the temperature of the working fluid changes to the side where the temperature decreases is reduced. According to this, the expansion of the temperature difference Dt can be suppressed. That is, it is possible to prevent the temperature difference Dt from becoming larger than the predetermined temperature difference Tth2. Alternatively, even when the temperature difference Dt becomes larger than the predetermined temperature difference Tth2, it is possible to suppress the temperature difference Dt from being much larger than the predetermined temperature difference Tth2. For this reason, the intensity of boiling can be reduced.

  (8) The present disclosure is not limited to the embodiments described above, and can be appropriately modified within the scope described in the claims, and also includes various modified examples and modifications within equivalent ranges. In addition, the above embodiments are not irrelevant to each other, and can be appropriately combined unless a combination is clearly impossible. In each of the above embodiments, it is needless to say that the elements constituting the embodiments are not necessarily essential, unless otherwise clearly indicated as being essential or in principle considered to be clearly essential. No. In each of the above embodiments, when a numerical value such as the number, numerical value, amount, range, or the like of the constituent elements of the exemplary embodiment is mentioned, it is particularly limited to a specific number when it is clearly stated that it is essential and in principle. The number is not limited to the specific number unless otherwise specified. Further, in each of the above embodiments, when referring to the material, shape, positional relationship, and the like of the constituent elements, unless otherwise specified, and in principle, it is limited to a specific material, shape, positional relationship, and the like. It is not limited to the material, shape, positional relationship, and the like.

(Summary)
According to a first aspect shown in a part or all of the above embodiments, the device temperature control device includes a working fluid circuit that forms a thermosiphon heat pipe, and a temperature control device that controls the temperature of the working fluid. And a control device for controlling the operation of the temperature adjustment unit. The working fluid circuit has an evaporating section in which the working fluid evaporates due to heat absorption from the device, and a condensing section in which the working fluid evaporated in the evaporating section is cooled and condensed. When the temperature difference between the device and the liquid working fluid is larger than a predetermined temperature difference, the control device controls the temperature adjustment unit to suppress a decrease in the temperature of the working fluid in the working fluid circuit.

  According to a second aspect, the temperature adjustment unit is a cooling device that cools the working fluid in the condensation unit. The control device reduces the cooling capacity of the cooling device when the cooling device is operating and the temperature difference is larger than the predetermined temperature difference. In the first aspect, specifically, the configuration of the second aspect can be adopted.

  According to a third aspect, the device temperature control device includes a cooling device that cools the working fluid in the condensing section. The temperature adjusting unit is a variable thermal resistor that is provided between the condenser and the cooling device and that can change the thermal resistance between the condenser and the cooling device. The control device increases the thermal resistance of the variable thermal resistor when the cooling device is operating and the temperature difference is larger than the predetermined temperature difference. In the first aspect, specifically, the configuration of the third aspect can be adopted.

  According to the fourth aspect, the temperature adjustment unit is a heating element that is provided in the working fluid circuit separately from the device and that can be switched between operation and stop. The control device activates the heating element when the temperature difference is larger than the predetermined temperature difference. In the first aspect, specifically, the configuration of the fourth aspect can be adopted.

  According to a fifth aspect, the device temperature control device includes a cooling device that cools the working fluid in the condensing section. The control device activates the heating element when the cooling device is operating and the temperature difference is larger than the predetermined temperature difference. In the fourth aspect, the configuration of the fifth aspect can be adopted.

  According to a sixth aspect, the cooling device is a refrigeration cycle device. In the second, third, or fifth aspects, the configuration of the sixth aspect can be adopted.

  According to a seventh aspect, the cooling device has a blower that blows air to the condensing section. In the second, third, or fifth aspects, the configuration of the seventh aspect can be adopted.

  According to the eighth aspect, the cooling device has a coolant circuit in which a coolant for cooling the working fluid circulates. In the second, third, or fifth aspects, the configuration of the eighth aspect can be adopted.

  According to a ninth aspect, a cooling device has a Peltier device. In the second aspect, the configuration of the ninth aspect can be adopted.

Claims (4)

An equipment temperature controller for adjusting the temperature of the equipment,
A working fluid circuit (10) that constitutes a thermosiphon type heat pipe and circulates a working fluid;
A temperature adjusting unit for adjusting the temperature of the working fluid in the working fluid circuit,
A control device (40) for controlling the operation of the temperature adjustment unit,
The working fluid circuit includes:
An evaporating section (12) in which the working fluid evaporates by heat absorption from the device (BP);
A condenser (14a, 50, 60a, 70a) for cooling and condensing the working fluid evaporated in the evaporator,
When the temperature difference between the device and the liquid working fluid is larger than a predetermined temperature difference, the control device controls the temperature adjustment unit to suppress a decrease in the temperature of the working fluid in the working fluid circuit ,
The device temperature controller includes a cooling device (21, 54, 66, 75) for cooling a working fluid in the condensing section,
The temperature adjustment unit is a variable thermal resistor (80) that is provided between the condensation unit and the cooling device and that can change the thermal resistance between the condensation unit and the cooling device.
The controller is a device temperature controller that increases the thermal resistance of the variable thermal resistor when the cooling device is operating and the temperature difference is larger than a predetermined temperature difference . The device temperature controller according to claim 1 , wherein the cooling device is a refrigeration cycle device (21). The device temperature controller according to claim 1 , wherein the cooling device (54) includes a blower (51) for blowing air to the condensing section. The device temperature controller according to claim 1 , wherein the cooling device (66) has a cooling liquid circuit (62) through which a cooling liquid for cooling the working fluid circulates.

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