JP5618011B2 - Control method of cooling device - Google Patents

Description

  The present invention relates to a control method for a cooling device, and more particularly to a control method for a cooling device that cools a heat generation source using a vapor compression refrigeration cycle.

  In recent years, attention has been focused on hybrid vehicles, fuel cell vehicles, electric vehicles, and the like that travel with the driving force of a motor as one of the environmental countermeasures. In such a vehicle, electric devices such as a motor, a generator, an inverter, a converter, and a battery generate heat when power is transferred. Therefore, it is necessary to cool these electric devices. In view of this, a technique for cooling a heating element using a vapor compression refrigeration cycle used as a vehicle air conditioner has been proposed.

  For example, Japanese Patent Laid-Open No. 2006-290254 (Patent Document 1) includes a compressor capable of sucking and compressing a gas refrigerant, a main condenser capable of being cooled with ambient air for condensing a high-pressure gas refrigerant, and a low-temperature liquid refrigerant. Cooling of a hybrid vehicle comprising an evaporator capable of cooling a refrigerant to be cooled and a pressure reducing means, wherein a heat exchanger capable of absorbing heat from a motor and a second pressure reducing means are connected in parallel to the pressure reducing means and the evaporator. A system is disclosed. JP 2007-69733 A (Patent Document 2) includes a heat exchanger that exchanges heat with air for air conditioning, a heat exchanger that exchanges heat with a heating element, in a refrigerant passage from an expansion valve to a compressor, Are arranged in parallel, and a system for cooling a heating element using a refrigerant for an air conditioner is disclosed.

  Japanese Patent Laid-Open No. 2005-90862 (Patent Document 3) is provided with a heating element cooling means for cooling a heating element in a bypass passage that bypasses a decompressor, an evaporator and a compressor of a refrigeration cycle for air conditioning. A cooling system is disclosed. In Japanese Patent Laid-Open No. 2001-309506 (Patent Document 4), the refrigerant of the refrigeration cycle device for vehicle air conditioning is recirculated to the cooling member of the inverter circuit unit that drives and controls the vehicle travel motor, and cooling of the air-conditioning air flow is unnecessary. Discloses a cooling system that suppresses cooling of an air-conditioned air flow by an evaporator of a vehicle air-conditioning refrigeration cycle apparatus.

JP 2006-290254 A JP 2007-69733 A JP-A-2005-90862 JP 2001-309506 A

  In the cooling devices disclosed in Patent Documents 2 and 3, a cooling path for cooling a heat source such as an electric device is incorporated in the vapor compression refrigeration cycle, and when the heat source is cooled, a decompressor is used. The refrigerant in the gas-liquid two-phase state after passing is introduced into the refrigerant path for cooling the heat generation source. When the flow rate of the liquid-phase refrigerant for cooling the heat source decreases, there is a problem that the cooling performance of the heat source deteriorates.

  This invention is made | formed in view of said subject, The main objective is to provide the control method of the cooling device which can cool a heat-generation source stably.

  The control method according to the present invention is a control method for a cooling device that cools a heat source. The cooling device includes a compressor for circulating the refrigerant, a heat exchanger that exchanges heat between the refrigerant and the outside air, a cooling unit that cools the heat source using the refrigerant, and a liquid that is condensed by the heat exchanger. A first accumulator that stores the refrigerant, a first passage through which the refrigerant discharged from the compressor flows to the cooling section via the heat exchanger and the accumulator, and heat without applying power when the compressor stops. A second passage for circulating the refrigerant between the exchanger and the cooling unit, and a switching valve for switching between communication of the first passage and communication of the second passage. The control method increases the amount of liquid refrigerant stored in the accumulator after the step of blocking the first passage and the step of blocking from the state where the first passage communicates and the second passage is blocked. And a step of allowing the second passage to communicate with each other while maintaining the interruption of the first passage after the increasing step.

  Preferably, in the above control method, the switching valve includes a first opening / closing valve that switches between communication and blocking of the first passage, and a second switching valve that switches between communication and blocking of the second passage, and the step of blocking Includes a step of closing the first on-off valve, and the step of communicating includes the step of opening the second on-off valve.

  Preferably, in the above control method, the cooling device further includes and blocks an expansion valve that depressurizes the refrigerant, and a second heat exchanger that exchanges heat between the refrigerant depressurized by the expansion valve and the air-conditioning air. The step includes a step of decreasing the opening degree of the expansion valve.

  Preferably, in the above control method, the expansion valve is a temperature-type expansion valve, and the cooling device further includes an air-conditioning fan for supplying air-conditioning air to the second heat exchanger. Reduce the number of revolutions.

  Preferably, in the above control method, the cooling device further includes a third heat exchanger that is provided between the heat exchanger and the expansion valve and exchanges heat between the refrigerant and the outside air.

  Preferably, in the above control method, the cooling device includes an outside air supply fan for supplying outside air to the heat exchanger, and the increasing step includes a step of increasing the rotational speed of the outside air supply fan.

  According to the cooling device of the present invention, the flow rate of the liquid-phase refrigerant flowing to the heat source can be secured, so that a decrease in the cooling capacity of the heat source can be suppressed and the heat source can be stably cooled.

It is the schematic which shows the structure of the vehicle to which a cooling device is applied. 2 is a schematic diagram illustrating a configuration of a cooling device according to Embodiment 1. FIG. It is a Mollier diagram which shows the state of the refrigerant | coolant of a vapor compression refrigeration cycle. It is a schematic diagram which shows the flow of the refrigerant | coolant which cools EV apparatus during the driving | operation of a vapor compression refrigeration cycle. It is a schematic diagram which shows the flow of the refrigerant | coolant which cools EV apparatus during the stop of a vapor compression refrigeration cycle. It is a figure which shows the setting of the compressor for every operation mode of a cooling device, a flow regulating valve, and an on-off valve. It is a block diagram which shows the detail of a structure of a control part. It is a flowchart which shows an example of the control method of a cooling device. It is a schematic diagram which shows the state of the cooling device after the step (S20) shown in FIG. It is a flowchart which shows the other example of the control method of a cooling device. It is a schematic diagram which shows the state of the cooling device after the step (S120) shown in FIG.

  Embodiments of the present invention will be described below with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.

(Embodiment 1)
FIG. 1 is a schematic diagram illustrating a configuration of a vehicle 1000 to which the cooling device 1 is applied. A vehicle 1000 according to the present embodiment includes an engine 100 that is an internal combustion engine, a drive unit 200 that is an electric motor, a PCU (Power Control Unit) 700, and a traveling battery 400. This is a hybrid vehicle using the drive unit 200 as a power source. Note that the cooling device 1 of the present invention is not limited to a hybrid vehicle that uses an engine and an electric motor as power sources, but also to a vehicle that uses only an electric motor as a power source (in this specification, both are referred to as an electric vehicle). Applicable.

  Engine 100 may be a gasoline engine or a diesel engine. Drive unit 200 generates a driving force for driving vehicle 1000 together with engine 100. Engine 100 and drive unit 200 are both provided in the engine room of vehicle 1000. Drive unit 200 is electrically connected to PCU 700 via cable 500. PCU 700 is electrically connected to traveling battery 400 via cable 600.

  FIG. 2 is a schematic diagram illustrating a configuration of the cooling device 1 according to the first embodiment. As shown in FIG. 2, the cooling device 1 includes a vapor compression refrigeration cycle 10. The vapor compression refrigeration cycle 10 is mounted on the vehicle 1000 in order to cool the inside of the vehicle, for example. The cooling using the vapor compression refrigeration cycle 10 is selected, for example, when the switch for performing the cooling is turned on or the automatic control mode for automatically adjusting the temperature of the vehicle interior to the set temperature is selected. This is performed when the temperature in the passenger compartment is higher than the set temperature.

  The vapor compression refrigeration cycle 10 includes a compressor 12, a heat exchanger 14 as a first heat exchanger, a heat exchanger 15 as a third heat exchanger, an expansion valve 16 as an example of a decompressor, And a heat exchanger 18 as a second heat exchanger. The vapor compression refrigeration cycle 10 also includes a gas-liquid separator 40 disposed on the refrigerant path between the heat exchanger 14 and the heat exchanger 15.

  The compressor 12 operates using a motor or engine mounted on the vehicle as a power source, and compresses the refrigerant gas in an adiabatic manner to form an overheated refrigerant gas. The compressor 12 sucks and compresses the refrigerant flowing from the heat exchanger 18 when the vapor compression refrigeration cycle 10 is operated, and discharges a high-temperature and high-pressure gas-phase refrigerant into the refrigerant passage 21. The compressor 12 circulates the refrigerant in the vapor compression refrigeration cycle 10 by discharging the refrigerant into the refrigerant passage 21.

  The heat exchangers 14 and 15 dissipate the superheated refrigerant gas compressed in the compressor 12 isothermally to an external medium to obtain a refrigerant liquid. The high-pressure gas-phase refrigerant discharged from the compressor 12 is condensed (liquefied) by releasing heat to the surroundings in the heat exchangers 14 and 15 and being cooled. The heat exchangers 14 and 15 include tubes through which the refrigerant flows, and fins for exchanging heat between the refrigerant flowing through the tubes and the air around the heat exchangers 14 and 15.

  The heat exchangers 14 and 15 exchange heat between the cooling air and the refrigerant. The cooling air may be supplied to the heat exchangers 14 and 15 by natural ventilation generated by traveling of the vehicle. Alternatively, the cooling air may be supplied to the heat exchangers 14 and 15 by forced ventilation from an external air supply fan such as the condenser fan 42 or a radiator fan for cooling the engine. By the heat exchange in the heat exchangers 14 and 15, the temperature of the refrigerant is lowered and the refrigerant is liquefied.

  The expansion valve 16 expands by injecting a high-pressure liquid-phase refrigerant flowing through the refrigerant passage 25 from a small hole, and changes it into a low-temperature / low-pressure mist refrigerant. The expansion valve 16 depressurizes the refrigerant liquid condensed by the heat exchangers 14 and 15 to obtain wet steam in a gas-liquid mixed state.

  The heat exchanger 18 absorbs heat of ambient air introduced so as to come into contact with the heat exchanger 18 by vaporizing the mist refrigerant flowing through the heat exchanger 18. The heat exchanger 18 uses the refrigerant depressurized by the expansion valve 16 to absorb the heat of vaporization when the refrigerant's wet vapor evaporates into the refrigerant gas from the air conditioning air flowing into the vehicle interior, Cool the interior of the vehicle. The air-conditioning air whose temperature has been reduced by the heat being absorbed by the heat exchanger 18 is returned again to the vehicle interior, thereby cooling the vehicle interior. The refrigerant absorbs heat from the surroundings in the heat exchanger 18 and is heated.

  The heat exchanger 18 includes a tube through which the refrigerant flows, and fins for exchanging heat between the refrigerant flowing through the tube and the air around the heat exchanger 18. A wet steam refrigerant circulates in the tube. When the refrigerant circulates in the tube, it evaporates by absorbing the heat of the air in the vehicle interior as latent heat of evaporation via the fins, and further becomes superheated steam by sensible heat. The vaporized refrigerant flows to the compressor 12 via the refrigerant passage 27. The compressor 12 compresses the refrigerant flowing from the heat exchanger 18.

  The vapor compression refrigeration cycle 10 also includes a refrigerant passage 21 that communicates the compressor 12 and the heat exchanger 14, a refrigerant passage 22, 23, and 24 that communicates the heat exchanger 14 and the heat exchanger 15, and heat exchange. A refrigerant passage 25 communicating with the heat exchanger 15 and the expansion valve 16, a refrigerant passage 26 communicating with the expansion valve 16 and the heat exchanger 18, and a refrigerant passage 27 communicating with the heat exchanger 18 and the compressor 12. Including.

  The refrigerant passage 21 is a passage for circulating the refrigerant from the compressor 12 to the heat exchanger 14. The refrigerant flows between the compressor 12 and the heat exchanger 14 from the outlet of the compressor 12 toward the inlet of the heat exchanger 14 via the refrigerant passage 21. The refrigerant passages 22 to 25 are passages for circulating the refrigerant from the heat exchanger 14 to the expansion valve 16. The refrigerant flows between the heat exchanger 14 and the expansion valve 16 from the outlet of the heat exchanger 14 toward the inlet of the expansion valve 16 via the refrigerant passages 22 to 25.

  The refrigerant passage 26 is a passage for circulating the refrigerant from the expansion valve 16 to the heat exchanger 18. The refrigerant flows between the expansion valve 16 and the heat exchanger 18 from the outlet of the expansion valve 16 toward the inlet of the heat exchanger 18 via the refrigerant passage 26. The refrigerant passage 27 is a passage for circulating the refrigerant from the heat exchanger 18 to the compressor 12. The refrigerant flows between the heat exchanger 18 and the compressor 12 from the outlet of the heat exchanger 18 toward the inlet of the compressor 12 via the refrigerant passage 27.

  The vapor compression refrigeration cycle 10 is configured by connecting a compressor 12, heat exchangers 14 and 15, an expansion valve 16, and a heat exchanger 18 through refrigerant passages 21 to 27. As the refrigerant of the vapor compression refrigeration cycle 10, for example, carbon dioxide, hydrocarbons such as propane and isobutane, ammonia, chlorofluorocarbons or water can be used.

  The gas-liquid separator 40 separates the refrigerant flowing out from the heat exchanger 14 into a gas phase refrigerant and a liquid phase refrigerant. Inside the gas-liquid separator 40, a refrigerant liquid that is a liquid phase refrigerant and a refrigerant vapor that is a gas phase refrigerant are stored. Refrigerant passages 22 and 23 and a refrigerant passage 34 are connected to the gas-liquid separator 40.

  On the outlet side of the heat exchanger 14, the refrigerant is in a gas-liquid two-phase wet steam state in which a saturated liquid and a saturated steam are mixed. The refrigerant that has flowed out of the heat exchanger 14 is supplied to the gas-liquid separator 40 through the refrigerant passage 22. The gas-liquid two-phase refrigerant flowing into the gas-liquid separator 40 from the refrigerant passage 22 is separated into a gas phase and a liquid phase inside the gas-liquid separator 40. The gas-liquid separator 40 separates the refrigerant condensed by the heat exchanger 14 into a liquid refrigerant liquid and a gaseous refrigerant vapor and temporarily stores them.

  The separated refrigerant liquid flows out of the gas-liquid separator 40 via the refrigerant passage 34. The end of the refrigerant passage 34 disposed in the liquid phase in the gas-liquid separator 40 forms an outlet for the liquid-phase refrigerant from the gas-liquid separator 40. The separated refrigerant vapor flows out of the gas-liquid separator 40 via the refrigerant passage 23. An end portion of the refrigerant passage 23 arranged in the gas phase in the gas-liquid separator 40 forms an outlet from the gas-liquid separator 40 for the gas-phase refrigerant. The vapor-phase refrigerant vapor derived from the gas-liquid separator 40 is condensed by releasing heat to the surroundings and cooling in the heat exchanger 15 provided between the heat exchanger 14 and the expansion valve 16.

  Inside the gas-liquid separator 40, the refrigerant liquid accumulates on the lower side and the refrigerant vapor accumulates on the upper side. The end portion of the refrigerant passage 34 for leading the refrigerant liquid from the gas-liquid separator 40 is connected to the bottom of the gas-liquid separator 40. Only the refrigerant liquid is sent out of the gas-liquid separator 40 from the bottom side of the gas-liquid separator 40 via the refrigerant passage 34. The end portion of the refrigerant passage 23 for leading the refrigerant vapor from the gas-liquid separator 40 is connected to the ceiling portion of the gas-liquid separator 40. Only the refrigerant vapor is sent out of the gas-liquid separator 40 from the ceiling side of the gas-liquid separator 40 via the refrigerant passage 23. As a result, the gas-liquid separator 40 can reliably separate the gas-phase refrigerant and the liquid-phase refrigerant.

  The path through which the refrigerant flowing from the outlet of the heat exchanger 14 toward the inlet of the expansion valve 16 flows is the refrigerant passage 22 extending from the outlet side of the heat exchanger 14 to the gas-liquid separator 40 and from the gas-liquid separator 40 to the refrigerant. The refrigerant flows through the expansion valve 16 from the refrigerant passage 23 through which the steam flows out and passes through a flow rate adjusting valve 28 described later, the refrigerant passage 24 connected to the inlet side of the heat exchanger 15, and the outlet side of the heat exchanger 15. Refrigerant passage 25. The refrigerant passage 23 is a passage through which the gas-phase refrigerant separated by the gas-liquid separator 40 flows.

  The refrigerant path that flows between the heat exchanger 14 and the heat exchanger 15 also connects the refrigerant passage 34 that connects the gas-liquid separator 40 and the cooling unit 30, and the cooling unit 30 and the refrigerant passage 24. Refrigerant passage 36. The refrigerant liquid flows from the gas-liquid separator 40 to the cooling unit 30 via the refrigerant passage 34. The refrigerant that has passed through the cooling unit 30 returns to the refrigerant passage 24 via the refrigerant passage 36. The cooling unit 30 is provided on a refrigerant path that flows from the heat exchanger 14 toward the heat exchanger 15.

  A point D shown in FIG. 2 indicates a connection point of the refrigerant passage 23, the refrigerant passage 24, and the refrigerant passage 36. That is, the point D is an end portion on the downstream side (side near the heat exchanger 15) of the refrigerant passage 23, an end portion on the upstream side (side near the heat exchanger 14) of the refrigerant passage 24, and the refrigerant passage 36. The downstream end of is shown. The refrigerant passage 23 forms a part of the path through which the refrigerant from the gas-liquid separator 40 to the expansion valve 16 flows, from the gas-liquid separator 40 to the point D.

  The cooling device 1 includes a refrigerant path arranged in parallel with the refrigerant passage 23, and the cooling unit 30 is provided on the refrigerant path. The cooling unit 30 is provided in one of a plurality of passages connected in parallel in the path of the refrigerant flowing between the heat exchanger 14 and the expansion valve 16 from the gas-liquid separator 40 toward the heat exchanger 15. It has been. The cooling unit 30 includes an EV (Electric Vehicle) device 31 that is an electric device mounted on an electric vehicle, and a cooling passage 32 that is a pipe through which a refrigerant flows. The EV device 31 is an example of a heat source. One end of the cooling passage 32 is connected to the refrigerant passage 34. The other end of the cooling passage 32 is connected to the refrigerant passage 36.

  The refrigerant path connected in parallel to the refrigerant passage 23 between the gas-liquid separator 40 and the point D shown in FIG. 2 is the refrigerant on the upstream side (the side close to the gas-liquid separator 40) from the cooling unit 30. A passage 34, a cooling passage 32 included in the cooling unit 30, and a refrigerant passage 36 downstream of the cooling unit 30 (side closer to the heat exchanger 15) are included. The refrigerant passage 34 is a passage through which a liquid-phase refrigerant flows from the gas-liquid separator 40 to the cooling unit 30. The refrigerant passage 36 is a passage for circulating the refrigerant from the cooling unit 30 to the point D. Point D is a branch point between the refrigerant passages 23 and 24 and the refrigerant passage 36.

  The refrigerant liquid that has flowed out of the gas-liquid separator 40 flows through the refrigerant passage 34 toward the cooling unit 30. The refrigerant flowing to the cooling unit 30 and flowing through the cooling passage 32 takes heat from the EV device 31 as a heat generation source and cools the EV device 31. The cooling unit 30 cools the EV device 31 using a liquid-phase refrigerant that is separated in the gas-liquid separator 40 and flows to the cooling passage 32 via the refrigerant passage 34. In the cooling unit 30, the refrigerant flowing in the cooling passage 32 and the EV device 31 exchange heat, whereby the EV device 31 is cooled and the refrigerant is heated. The refrigerant further flows from the cooling unit 30 toward the point D via the refrigerant passage 36 and reaches the heat exchanger 15 via the refrigerant passage 24.

  The cooling unit 30 is provided so as to have a structure capable of exchanging heat between the EV device 31 and the refrigerant in the cooling passage 32. In the present embodiment, the cooling unit 30 includes, for example, the cooling passage 32 formed so that the outer peripheral surface of the cooling passage 32 directly contacts the housing of the EV device 31. The cooling passage 32 has a portion adjacent to the housing of the EV device 31. In this portion, heat exchange can be performed between the refrigerant flowing through the cooling passage 32 and the EV device 31.

  The EV device 31 is directly connected to the outer peripheral surface of the cooling passage 32 that forms part of the refrigerant path from the heat exchanger 14 to the heat exchanger 15 of the vapor compression refrigeration cycle 10 to be cooled. Since the EV device 31 is disposed outside the cooling passage 32, the EV device 31 does not interfere with the flow of the refrigerant flowing through the cooling passage 32. Therefore, since the pressure loss of the vapor compression refrigeration cycle 10 does not increase, the EV device 31 can be cooled without increasing the power of the compressor 12.

  Alternatively, the cooling unit 30 may include any known heat pipe that is disposed between the EV device 31 and the cooling passage 32. In this case, the EV device 31 is connected to the outer peripheral surface of the cooling passage 32 via a heat pipe, and is cooled by transferring heat from the EV device 31 to the cooling passage 32 via the heat pipe. Heat transfer efficiency between the cooling passage 32 and the EV device 31 can be increased by using the EV device 31 as a heat pipe heating portion and the cooling passage 32 as a heat pipe cooling portion. Therefore, the cooling efficiency of the EV device 31 can be increased. Can be improved. For example, a wick-type heat pipe can be used.

  Since heat can be reliably transferred from the EV device 31 to the cooling passage 32 by the heat pipe, there may be a distance between the EV device 31 and the cooling passage 32, and the cooling passage 32 is brought into contact with the EV device 31. Therefore, it is not necessary to arrange the cooling passage 32 in a complicated manner. As a result, the degree of freedom of arrangement of the EV device 31 can be improved.

  The EV device 31 includes an electric device that generates heat when power is transferred. The electrical equipment includes, for example, an inverter for converting DC power to AC power, a motor generator that is a rotating electrical machine, a battery that is a power storage device, a boost converter that boosts the voltage of the battery, and a voltage that lowers the voltage of the battery. It includes at least one of a DC / DC converter and the like. The battery is a secondary battery such as a lithium ion battery or a nickel metal hydride battery. A capacitor may be used instead of the battery.

  The heat exchanger 18 is disposed inside a duct 90 through which air flows. The heat exchanger 18 exchanges heat between the refrigerant and the air-conditioning air flowing through the duct 90 to adjust the temperature of the air-conditioning air. The duct 90 has a duct inlet 91 that is an inlet through which air-conditioning air flows into the duct 90, and a duct outlet 92 that is an outlet through which air-conditioning air flows out from the duct 90. An air conditioning fan 93 is arranged in the vicinity of the duct inlet 91 inside the duct 90. The air conditioning fan 93 is connected to a motor 94 that rotationally drives the air conditioning fan 93.

  When the air conditioning fan 93 is driven, air flows through the duct 90 and air is supplied to the heat exchanger 18. When the air conditioning fan 93 is in operation, the air conditioning air flows into the duct 90 via the duct inlet 91. The air flowing into the duct 90 may be outside air or air in the vehicle interior. An arrow 95 in FIG. 2 indicates the flow of air-conditioning air that circulates through the heat exchanger 18 and exchanges heat with the refrigerant of the vapor compression refrigeration cycle 10. During the cooling operation, the air-conditioning air is cooled in the heat exchanger 18, and the refrigerant is heated by receiving heat transfer from the air-conditioning air. An arrow 96 indicates the flow of air-conditioning air that is temperature-adjusted by the heat exchanger 18 and flows out of the duct 90 via the duct outlet 92.

  The refrigerant passes through the refrigerant circulation passage in which the compressor 12, the heat exchangers 14 and 15, the expansion valve 16, and the heat exchanger 18 are sequentially connected by the refrigerant passages 21 to 27, and passes through the vapor compression refrigeration cycle 10. Circulate. The refrigerant flows through the vapor compression refrigeration cycle 10 through the points A, B, C, D, E, and F shown in FIG. 2 in order, and the compressor 12 and the heat exchangers 14 and 15 The refrigerant circulates through the expansion valve 16 and the heat exchanger 18.

  FIG. 3 is a Mollier diagram showing the state of the refrigerant in the vapor compression refrigeration cycle 10. The horizontal axis in FIG. 3 indicates the specific enthalpy of the refrigerant, and the vertical axis indicates the absolute pressure of the refrigerant. The unit of specific enthalpy is kJ / kg, and the unit of absolute pressure is MPa. The curves in the figure are the saturated vapor line and saturated liquid line of the refrigerant.

  In FIG. 3, the refrigerant flows from the refrigerant passage 22 at the outlet of the heat exchanger 14 into the refrigerant passage 34 via the gas-liquid separator 40, cools the EV device 31, and passes through the point D from the refrigerant passage 36. The thermodynamic state of the refrigerant at each point in the vapor compression refrigeration cycle 10 (ie, points A, B, C, D, E, and F) returning to the refrigerant passage 24 at the inlet of the heat exchanger 15 is shown. A path through which the refrigerant flows, that is, the refrigerant path 21, the refrigerant path 22, the refrigerant path 34, the refrigerant path 36, and the refrigerant paths 24 to 27 form a first path.

  As shown in FIG. 3, the superheated vapor refrigerant (point A) sucked into the compressor 12 is adiabatically compressed in the compressor 12 along the isoentropic curve. As the compressor is compressed, the pressure and temperature of the refrigerant rise and become high-temperature and high-pressure superheated steam with a high degree of superheat (point B), and the refrigerant flows to the heat exchanger 14. The gas-phase refrigerant discharged from the compressor 12 is condensed (liquefied) by releasing heat to the surroundings in the heat exchanger 14 and being cooled. By the heat exchange with the outside air in the heat exchanger 14, the temperature of the refrigerant is lowered and the refrigerant is liquefied. The high-pressure refrigerant vapor that has entered the heat exchanger 14 changes from superheated steam to dry saturated vapor while maintaining the same pressure in the heat exchanger 14, releases latent heat of condensation, gradually liquefies, and becomes wet vapor in a gas-liquid mixed state. . Of the refrigerant in the gas-liquid two-phase state, the condensed refrigerant is in a saturated liquid state (point C).

  The refrigerant is separated into a gas phase refrigerant and a liquid phase refrigerant in the gas-liquid separator 40. Among the gas-liquid separated refrigerant, the liquid-phase refrigerant liquid flows from the gas-liquid separator 40 through the refrigerant passage 34 to the cooling passage 32 of the cooling unit 30 to cool the EV device 31. In the cooling unit 30, the EV device 31 is cooled by releasing heat to the liquid refrigerant in the saturated liquid state that is condensed after passing through the heat exchanger 14. By the heat exchange with the EV device 31, the refrigerant is heated and the dryness of the refrigerant increases. The refrigerant receives the latent heat from the EV device 31 and partially evaporates to become wet steam in which the saturated liquid and saturated steam are mixed (point D).

  Thereafter, the refrigerant flows into the heat exchanger 15. The wet steam of the refrigerant is condensed again by exchanging heat with the outside air in the heat exchanger 15 and is condensed again. When all of the refrigerant is condensed, it becomes a saturated liquid and further subcooled by releasing sensible heat. Become liquid (point E). Thereafter, the refrigerant flows into the expansion valve 16 via the refrigerant passage 25. In the expansion valve 16, the refrigerant in the supercooled liquid state is squeezed and expanded, the specific enthalpy does not change, the temperature and pressure are reduced, and the low temperature and low pressure gas-liquid mixed vapor is obtained (point F).

  The wet steam refrigerant that has flowed out of the expansion valve 16 flows into the heat exchanger 18 via the refrigerant passage 26. A wet steam refrigerant flows into the tube of the heat exchanger 18. When the refrigerant circulates in the tube of the heat exchanger 18, it absorbs the heat of the air in the vehicle interior via the fins as latent heat of vaporization, and evaporates at a constant pressure. When all the refrigerants are dry and become saturated vapor, the temperature of the refrigerant vapor further rises due to sensible heat and becomes superheated vapor (point A). Thereafter, the refrigerant is sucked into the compressor 12 via the refrigerant passage 27. The compressor 12 compresses the refrigerant flowing from the heat exchanger 18.

  In accordance with such a cycle, the refrigerant continuously repeats the compression, condensation, throttle expansion, and evaporation state changes. In the above description of the vapor compression refrigeration cycle, the theoretical refrigeration cycle is described. However, in the actual vapor compression refrigeration cycle 10, it is necessary to consider the loss in the compressor 12, the pressure loss of the refrigerant, and the heat loss. Of course there is.

  During the operation of the vapor compression refrigeration cycle 10, the refrigerant absorbs heat of vaporization from the air in the vehicle interior when evaporating in the heat exchanger 18 acting as an evaporator, thereby cooling the vehicle interior. In addition, the high-pressure liquid refrigerant that has flowed out of the heat exchanger 14 and separated into gas and liquid by the gas-liquid separator 40 flows to the cooling unit 30, and heat-exchanges with the EV device 31 to cool the EV device 31. The cooling device 1 cools an EV device 31 that is a heat source mounted on a vehicle by using a vapor compression refrigeration cycle 10 for air conditioning in a vehicle interior. The temperature required for cooling the EV device 31 is desirably a temperature lower than the upper limit value of the target temperature range as the temperature range of the EV device 31.

  Since the EV equipment 31 is cooled using the vapor compression refrigeration cycle 10 provided to cool the part to be cooled in the heat exchanger 18, a dedicated water circulation pump is used to cool the EV equipment 31. Or it is not necessary to provide equipment, such as a cooling fan. Therefore, the configuration necessary for the cooling device 1 of the EV device 31 can be reduced and the device configuration can be simplified, so that the manufacturing cost of the cooling device 1 can be reduced. In addition, it is not necessary to operate a power source such as a pump or a cooling fan for cooling the EV device 31, and power consumption for operating the power source is not required. Therefore, power consumption for cooling the EV device 31 can be reduced.

  In the heat exchanger 14, it is only necessary to cool the refrigerant to a wet steam state, the refrigerant in the gas-liquid mixed state is separated by the gas-liquid separator 40, and only the refrigerant liquid in the saturated liquid state is supplied to the cooling unit 30. . The refrigerant in the state of wet steam that has received the latent heat of vaporization from the EV device 31 and is partially vaporized is cooled again by the heat exchanger 15. The refrigerant changes its state at a constant temperature until the wet vapor state refrigerant is condensed and completely saturated. The heat exchanger 15 further subcools the liquid refrigerant to a degree of supercooling necessary for cooling the vehicle interior. Since it is not necessary to excessively increase the degree of supercooling of the refrigerant, the capacity of the heat exchangers 14 and 15 can be reduced. Therefore, the cooling capacity for the passenger compartment can be ensured, and the size of the heat exchangers 14 and 15 can be reduced, so that the cooling device 1 that is downsized and advantageous for in-vehicle use can be obtained.

  A refrigerant passage 23 that forms a part of the refrigerant path from the outlet of the heat exchanger 14 to the inlet of the expansion valve 16 is provided between the heat exchanger 14 and the heat exchanger 15. The refrigerant flow from the gas-liquid separator 40 to the expansion valve 16 is a refrigerant path 23 that is a path that does not pass through the cooling unit 30 and a refrigerant path that cools the EV device 31 via the cooling unit 30. The refrigerant passages 34 and 36 and the cooling passage 32 are provided in parallel. The cooling system of the EV device 31 including the refrigerant passages 34 and 36 is connected in parallel with the refrigerant passage 23. Therefore, only a part of the refrigerant that has flowed out of the heat exchanger 14 flows to the cooling unit 30. An amount of refrigerant necessary for cooling the EV device 31 is circulated to the cooling unit 30, and the EV device 31 is appropriately cooled. Therefore, it is possible to prevent the EV device 31 from being overcooled.

  A refrigerant path flowing directly from the heat exchanger 14 to the heat exchanger 15 and a refrigerant path flowing from the heat exchanger 14 to the heat exchanger 15 via the cooling unit 30 are provided in parallel, and only a part of the refrigerants are provided. Is allowed to flow through the refrigerant passages 34 and 36, so that pressure loss when the refrigerant flows into the cooling system of the EV device 31 can be reduced. Since all the refrigerant does not flow to the cooling unit 30, it is possible to reduce pressure loss related to the circulation of the refrigerant passing through the cooling unit 30, and accordingly, consumption necessary for the operation of the compressor 12 for circulating the refrigerant. Electric power can be reduced.

  When the low-temperature and low-pressure refrigerant that has passed through the expansion valve 16 is used for cooling the EV device 31, the cooling capacity of the air in the passenger compartment in the heat exchanger 18 decreases, and the cooling capacity for the passenger compartment decreases. On the other hand, in the cooling device 1 of the present embodiment, the high-pressure refrigerant discharged from the compressor 12 in the vapor compression refrigeration cycle 10 is converted into the heat exchanger 14 as the first condenser, and the second It is condensed by both the heat exchanger 15 as a condenser. The two-stage heat exchangers 14 and 15 are disposed between the compressor 12 and the expansion valve 16, and the cooling unit 30 that cools the EV device 31 is provided between the heat exchanger 14 and the heat exchanger 15. ing. The heat exchanger 15 is provided on the path of the refrigerant that flows from the cooling unit 30 toward the expansion valve 16.

  The refrigerant heated by receiving the latent heat of vaporization from the EV device 31 is sufficiently cooled in the heat exchanger 15, so that the refrigerant at the outlet of the expansion valve 16 has a temperature originally required for cooling the vehicle interior. And having pressure. Therefore, the amount of heat received from the outside when the refrigerant evaporates in the heat exchanger 18 can be sufficiently increased. Thus, by defining the heat dissipation capability of the heat exchanger 15 that can sufficiently cool the refrigerant, the EV device 31 can be cooled without affecting the cooling capability of cooling the air in the passenger compartment. Therefore, both the cooling capacity of the EV device 31 and the cooling capacity for the passenger compartment can be reliably ensured.

  The refrigerant flowing from the heat exchanger 14 to the cooling unit 30 receives heat from the EV device 31 and is heated when the EV device 31 is cooled. When the refrigerant is heated to the saturated vapor temperature or higher in the cooling unit 30 and the entire amount of the refrigerant is vaporized, the amount of heat exchange between the refrigerant and the EV device 31 is reduced, and the EV device 31 cannot be efficiently cooled. Pressure loss during flow increases. Therefore, it is desirable to cool the refrigerant sufficiently in the heat exchanger 14 so that the entire amount of the refrigerant does not vaporize after the EV device 31 is cooled.

  Specifically, the state of the refrigerant at the outlet of the heat exchanger 14 is brought close to the saturated liquid, and typically, the refrigerant is on the saturated liquid line at the outlet of the heat exchanger 14. As a result of the heat exchanger 14 having the ability to sufficiently cool the refrigerant in this way, the heat dissipating ability for releasing heat from the refrigerant of the heat exchanger 14 is higher than the heat dissipating ability of the heat exchanger 15. By sufficiently cooling the refrigerant in the heat exchanger 14 having a relatively large heat dissipation capability, the refrigerant that has received heat from the EV device 31 can be kept in a wet steam state, and heat exchange between the refrigerant and the EV device 31 can be achieved. Since the decrease in the amount can be avoided, the EV device 31 can be cooled sufficiently efficiently. The refrigerant in the state of wet steam after cooling the EV device 31 is efficiently cooled again in the heat exchanger 15 and cooled to the state of the supercooled liquid below the saturation temperature. Therefore, it is possible to provide the cooling device 1 that secures both the cooling capacity for the passenger compartment and the cooling capacity of the EV device 31.

  The refrigerant in a gas-liquid two-phase state at the outlet of the heat exchanger 14 is separated into a gas phase and a liquid phase in the gas-liquid separator 40. The gas-phase refrigerant separated by the gas-liquid separator 40 flows through the refrigerant passages 23 and 24 and is directly supplied to the heat exchanger 15. The liquid phase refrigerant separated by the gas-liquid separator 40 flows through the refrigerant passage 34 and is supplied to the cooling unit 30 to cool the EV device 31. This liquid-phase refrigerant is a truly saturated liquid refrigerant with no excess or deficiency. By extracting only the liquid-phase refrigerant from the gas-liquid separator 40 and flowing it to the cooling unit 30, the EV device 31 can be cooled by utilizing the capacity of the heat exchanger 14 to the maximum, so that the EV device 31 is cooled. The cooling device 1 with improved performance can be provided.

  By introducing the refrigerant in a saturated liquid state at the outlet of the gas-liquid separator 40 into the cooling passage 32 for cooling the EV device 31, the refrigerant flows through the cooling system of the EV device 31 including the refrigerant passages 34 and 36 and the cooling passage 32. Among the refrigerants, the gas-phase refrigerant can be minimized. Therefore, the flow velocity of the refrigerant vapor flowing through the cooling system of the EV device 31 can be prevented from increasing and the pressure loss can be suppressed, and the power consumption of the compressor 12 for circulating the refrigerant can be reduced. Therefore, the vapor compression refrigeration cycle 10 The deterioration of the performance can be avoided.

  A refrigerant liquid in a saturated liquid state is stored inside the gas-liquid separator 40. The gas-liquid separator 40 functions as a liquid accumulator that temporarily stores a liquid refrigerant that is a liquid refrigerant. By storing a predetermined amount of the refrigerant liquid in the gas-liquid separator 40, the flow rate of the refrigerant flowing from the gas-liquid separator 40 to the cooling unit 30 can be maintained even when the load changes. Since the gas-liquid separator 40 has a liquid reservoir function and becomes a buffer against load fluctuations and can absorb the load fluctuations, the cooling performance of the EV device 31 can be stabilized.

  Returning to FIG. 2, the cooling device 1 includes a flow rate adjusting valve 28. The flow regulating valve 28 is disposed in the refrigerant passage 23 that forms one of the paths connected in parallel in the refrigerant path from the heat exchanger 14 to the expansion valve 16. The flow rate adjusting valve 28 varies the valve opening degree and increases / decreases the pressure loss of the refrigerant flowing through the refrigerant passage 23, whereby the flow rate of the refrigerant flowing through the refrigerant passage 23 and the cooling system of the EV device 31 including the cooling passage 32. The flow rate of the refrigerant flowing through is arbitrarily adjusted.

  For example, when the flow rate adjustment valve 28 is fully closed and the valve opening degree is 0%, the entire amount of the refrigerant that has exited the heat exchanger 14 flows from the gas-liquid separator 40 into the refrigerant passage 34. If the valve opening degree of the flow rate adjustment valve 28 is increased, the flow rate of the refrigerant flowing from the heat exchanger 14 to the refrigerant passage 22 directly flowing to the heat exchanger 15 via the refrigerant passage 23 increases, and the refrigerant passage 34 is The refrigerant flows through the cooling passage 32 and cools the EV device 31 to reduce the flow rate of the refrigerant. If the valve opening degree of the flow rate adjusting valve 28 is reduced, the flow rate of the refrigerant flowing from the heat exchanger 14 to the refrigerant passage 22 directly flowing to the heat exchanger 15 via the refrigerant passage 23 is reduced, and the cooling passage 32 is The flow rate of the refrigerant that cools the EV device 31 through the flow increases.

  When the valve opening degree of the flow rate adjusting valve 28 is increased, the flow rate of the refrigerant that cools the EV device 31 is decreased, and the cooling capacity of the EV device 31 is decreased. When the valve opening degree of the flow rate adjusting valve 28 is reduced, the flow rate of the refrigerant that cools the EV device 31 is increased, and the cooling capacity of the EV device 31 is improved. Since the amount of the refrigerant flowing to the EV device 31 can be optimally adjusted using the flow rate adjusting valve 28, the overcooling of the EV device 31 can be reliably prevented, and in addition, the refrigerant of the cooling system of the EV device 31 It is possible to reliably reduce the pressure loss and the power consumption of the compressor 12 for circulating the refrigerant.

  The cooling device 1 further includes a communication path 51. The communication passage 51 is a refrigerant downstream of the cooling unit 30 among the refrigerant passage 21 through which the refrigerant flows between the compressor 12 and the heat exchanger 14 and the refrigerant passages 34, 36 through which the refrigerant flows through the cooling unit 30. The passage 36 communicates with the passage 36. The refrigerant passage 36 is divided into a refrigerant passage 36 a upstream from the branch with the communication passage 51 and a refrigerant passage 36 b downstream from the branch with the communication passage 51.

  The refrigerant passage 36 and the communication passage 51 are provided with a switching valve 52 that switches the communication state between the communication passage 51 and the refrigerant passages 21 and 36. The switching valve 52 enables or disables the circulation of the refrigerant via the communication path 51 by switching its opening and closing. By switching the refrigerant path using the switching valve 52, the refrigerant after cooling the EV device 31 passes through the refrigerant passages 36 b and 24 to the heat exchanger 15, or the communication passage 51 and the refrigerant passage 21. Any of the paths to the heat exchanger 14 via can be arbitrarily selected and distributed.

  More specifically, two on-off valves 57 and 58 are provided as the switching valve 52. The switching valve 52 includes an on-off valve 57 as a first on-off valve and an on-off valve 58 as a second on-off valve. The on-off valve 57 is provided in the refrigerant passage 36b and switches between communication and blocking of the refrigerant passage 36b. By switching the opening / closing of the on-off valve 57, the communication state of the first passage including the refrigerant passage 36b is switched. The on-off valve 58 is provided in the communication path 51 and switches between communication and blocking of the communication path 51. By switching the opening / closing of the on-off valve 58, the communication state of the second passage, which will be described later, including the communication passage 51 is switched.

  During the cooling operation of the vapor compression refrigeration cycle 10, the opening / closing valve 57 is fully opened (valve opening degree 100%), the opening / closing valve 58 is fully closed (valve opening degree 0%), and the valve opening degree of the flow control valve 28 is set. It adjusts so that sufficient refrigerant | coolant may flow into the cooling part 30. FIG. Thereby, the refrigerant | coolant which distribute | circulates the refrigerant path 36a after cooling the EV apparatus 31 can be reliably distribute | circulated to the heat exchanger 15 via the refrigerant path 36b.

  On the other hand, while the vapor compression refrigeration cycle 10 is stopped, the open / close valve 58 is fully opened, the open / close valve 57 is fully closed, and the flow rate adjustment valve 28 is fully closed. Accordingly, the refrigerant flowing through the refrigerant passage 36a after cooling the EV device 31 is circulated to the heat exchanger 14 via the communication passage 51, and the cooling unit 30 and the heat exchanger are not passed through the compressor 12. 14 can form an annular path for circulating the refrigerant.

  FIG. 4 is a schematic diagram showing a refrigerant flow for cooling the EV device 31 during operation of the vapor compression refrigeration cycle 10. FIG. 5 is a schematic diagram showing the flow of the refrigerant that cools the EV device 31 while the vapor compression refrigeration cycle 10 is stopped. FIG. 6 is a diagram illustrating settings of the compressor 12, the flow rate adjustment valve 28, and the on-off valves 57 and 58 for each operation mode of the cooling device 1. Among the operation modes shown in FIG. 6, the “air-conditioner operation mode” refers to a case where the vapor compression refrigeration cycle 10 shown in FIG. 4 is operated, that is, the compressor 12 is operated and a refrigerant is introduced into the entire vapor compression refrigeration cycle 10. Is shown. On the other hand, the “heat pipe operation mode” refers to a case where the vapor compression refrigeration cycle 10 shown in FIG. 5 is stopped, that is, the compressor 12 is stopped and an annular path connecting the cooling unit 30 and the heat exchanger 14 is passed. In this case, the refrigerant is circulated.

  As shown in FIGS. 4 and 6, when in the “air conditioner operation mode” in which the compressor 12 is driven and the vapor compression refrigeration cycle 10 is operating, the flow rate adjustment valve 28 allows sufficient refrigerant to flow through the cooling unit 30. Thus, the valve opening is adjusted. The switching valve 52 is operated so that the refrigerant flows from the cooling unit 30 to the expansion valve 16 via the heat exchanger 15. That is, the refrigerant path is selected so that the refrigerant flows through the entire cooling device 1 by fully opening the on-off valve 57 and fully closing the on-off valve 58. Therefore, the cooling capacity of the vapor compression refrigeration cycle 10 can be ensured and the EV device 31 can be efficiently cooled.

  As shown in FIGS. 5 and 6, in the “heat pipe operation mode” in which the compressor 12 is stopped and the vapor compression refrigeration cycle 10 is stopped, the refrigerant is circulated from the cooling unit 30 to the heat exchanger 14. The switching valve 52 is operated. That is, the on-off valve 57 is fully closed, the on-off valve 58 is fully opened, and the flow rate adjustment valve 28 is fully closed, so that the refrigerant does not flow from the refrigerant passage 36a to the refrigerant passage 36b but flows through the communication passage 51. To do. Accordingly, the heat exchanger 14 reaches the cooling unit 30 through the refrigerant passage 22 and the refrigerant passage 34 in order, and further passes through the refrigerant passage 36a, the communication passage 51, and the refrigerant passage 21 in order to the heat exchanger 14. A closed, closed circular path is formed. A path through which the refrigerant flows, that is, the refrigerant path 21, the refrigerant path 22, the refrigerant path 34, the refrigerant path 36a, and the communication path 51 form a second path.

  Via this annular path, the refrigerant can be circulated between the heat exchanger 14 and the cooling unit 30 without operating the compressor 12. When the EV device 31 is cooled, the refrigerant receives evaporation latent heat from the EV device 31 and evaporates. The refrigerant vapor evaporated by heat exchange with the EV device 31 flows to the heat exchanger 14 through the refrigerant passage 36a, the communication passage 51, and the refrigerant passage 21 in order. In the heat exchanger 14, the refrigerant vapor is cooled and condensed by the running air of the vehicle or the ventilation from the condenser fan 42 or the radiator fan for cooling the engine. The refrigerant liquid liquefied by the heat exchanger 14 returns to the cooling unit 30 via the refrigerant passages 22 and 34.

  In this way, a heat pipe is formed by the annular path passing through the cooling unit 30 and the heat exchanger 14, with the EV device 31 as a heating unit and the heat exchanger 14 as a cooling unit. Therefore, even when the vapor compression refrigeration cycle 10 is stopped, that is, when cooling for the vehicle is stopped, the EV device 31 can be reliably cooled without having to start the compressor 12. Since it is not necessary to always operate the compressor 12 for cooling the EV equipment 31, the power consumption of the compressor 12 can be reduced and the fuel consumption of the vehicle can be improved. In addition, the compressor 12 has a long service life. Therefore, the reliability of the compressor 12 can be improved.

  An occupant of an electric vehicle switches the cooling of the passenger compartment from ON to OFF by operating an air conditioning control panel provided on an instrument panel in front of the vehicle. With this operation, the operation mode of the cooling device 1 for cooling the EV device 31 is switched from the air conditioner operation mode to the heat pipe operation mode. That is, the compressor 12 is stopped and the on-off valve 57 is fully closed. Thereby, the 1st channel | path for flowing the refrigerant | coolant discharged from the compressor 12 to the cooling part 30 and cooling the EV apparatus 31 is interrupted | blocked. In addition, the flow rate adjustment valve 28 is fully closed and the on-off valve 58 is fully opened. As a result, the second passage for circulating the refrigerant by natural circulation is communicated between the heat exchanger 14 and the cooling unit 30, and the refrigerant can be supplied to the cooling unit 30 without going through the compressor 12. .

  By switching the opening / closing of the switching valve 52, the communication of the first passage and the communication of the second passage are switched. Thereby, the EV device 31 is cooled from the air conditioner operation mode in which the first passage is communicated and the second passage is blocked to the heat pipe operation mode in which the first passage is blocked and the second passage is communicated. Therefore, the operation mode of the cooling device 1 is switched. In this way, even when the compressor 12 is stopped, the cooling capacity of the EV device 31 by the cooling device 1 is maintained.

  4 and 5 show the ground surface 60. The cooling unit 30 is disposed below the heat exchanger 14 in the vertical direction perpendicular to the ground 60. In an annular path for circulating the refrigerant between the heat exchanger 14 and the cooling unit 30, the cooling unit 30 is disposed below and the heat exchanger 14 is disposed above. The heat exchanger 14 is disposed at a position higher than the cooling unit 30.

  In this case, the refrigerant vapor heated and vaporized in the cooling unit 30 rises in the annular path and reaches the heat exchanger 14, is cooled in the heat exchanger 14, is condensed and becomes a liquid refrigerant, and acts by gravity. It descends in the annular path and returns to the cooling unit 30. That is, a thermosiphon heat pipe is formed by the cooling unit 30, the heat exchanger 14, and the refrigerant path (that is, the second passage) connecting them. Since the heat transfer efficiency from the EV device 31 to the heat exchanger 14 can be improved by forming the heat pipe, the EV can be applied without applying power even when the vapor compression refrigeration cycle 10 is stopped. The device 31 can be cooled more efficiently.

  The cooling device 1 further includes a check valve 54. The check valve 54 is disposed on the refrigerant passage 21 between the compressor 12 and the heat exchanger 14 on the side closer to the compressor 12 than the connection point between the refrigerant passage 21 and the communication passage 51. The check valve 54 allows the refrigerant flow from the compressor 12 to the heat exchanger 14 and prohibits the reverse refrigerant flow. In this way, in the heat pipe operation mode shown in FIG. 5, a closed loop refrigerant path for circulating the refrigerant between the heat exchanger 14 and the cooling unit 30 can be reliably formed.

  If the check valve 54 is not provided, the refrigerant may flow from the communication passage 51 to the refrigerant passage 21 on the compressor 12 side. By providing the check valve 54, the flow of the refrigerant from the communication path 51 toward the compressor 12 can be surely prohibited. Therefore, the stop of the vapor compression refrigeration cycle 10 using the heat pipe formed by the annular refrigerant path is used. It is possible to prevent a decrease in the cooling capacity of the EV device 31 at the time. Therefore, the EV device 31 can be efficiently cooled even when the cooling for the passenger compartment of the vehicle is stopped.

  In addition, when the amount of refrigerant in the closed loop refrigerant path is insufficient while the vapor compression refrigeration cycle 10 is stopped, the compressor 12 is operated only for a short time, thereby passing through the check valve 54. Thus, the refrigerant can be supplied to the closed loop path. Thereby, the refrigerant | coolant amount in a closed loop can be increased and the heat exchange processing amount of a heat pipe can be increased. Therefore, since the amount of refrigerant in the heat pipe can be ensured, it is possible to avoid insufficient cooling of the EV device 31 due to insufficient refrigerant amount.

  As the switching valve 52 that switches the communication state between the communication passage 51 and the refrigerant passages 21, 36, the pair of on-off valves 57, 58 described above may be used. An arranged three-way valve may be used. The on-off valves 57 and 58 are inexpensive because they have a simple structure capable of opening and closing the refrigerant passage. By using the two on-off valves 57 and 58, it is possible to provide the cooling device 1 at a lower cost. it can. On the other hand, it is considered that the space required for the arrangement of the three-way valve may be smaller than the arrangement of the two on-off valves 57, 58. 1 can be provided.

  In both cases where the switching valve 52 includes two on-off valves 57 and 58 and when the switching valve 52 is a three-way valve, the EV equipment 31 is used both when the vapor compression refrigeration cycle 10 is operated and when it is stopped. Can be efficiently cooled. A three-way valve may be disposed as a first on-off valve at the branch between the refrigerant passage 36 and the communication passage 51, and a three-way valve may be further disposed at the branch between the refrigerant passage 21 and the communication passage 51 as a second on-off valve. In this case, since the communication state between the communication passage 51 and the refrigerant passage 21 can be switched more reliably, the refrigerant flow can be more reliably formed between the refrigerant passage 21 and the communication passage 51, or The flow of the refrigerant between the communication passage 51 can be more reliably blocked. Since the three-way valve arranged at the branch of the refrigerant passage 21 and the communication passage 51 can be set to open / close so as to prohibit the flow of refrigerant from the communication passage 51 to the compressor 12, in this case, the check valve 54 is provided. It can be omitted.

  Hereinafter, control of the cooling device 1 of this Embodiment is demonstrated. FIG. 7 is a block diagram showing details of the configuration of the control unit 80. The control unit 80 illustrated in FIG. 7 includes an ECU (Electric Control Unit) 81 that performs control of the cooling device 1. The ECU 81 receives a signal indicating ON / OFF of the air conditioner from the air conditioner switch 82. The air conditioner switch 82 is provided, for example, on an instrument panel on the front side in the passenger compartment. When the vehicle occupant operates the air conditioner switch 82, the air conditioner is switched between ON and OFF, and cooling of the vehicle interior is started or stopped.

  ECU 81 receives a signal indicating temperature from temperature input unit 84. The temperature of the refrigerant at the inlet / outlet of the cooling unit 30 is input to the temperature input unit 84 from sensors that detect the temperature of the refrigerant flowing into the cooling unit 30 and the refrigerant flowing out of the cooling unit 30. The temperature input unit 84 may also be input with the temperature of the outside air near the cooling device 1 and the temperature of the air-conditioning air whose temperature is adjusted by heat exchange in the heat exchanger 18.

  The control unit 80 also includes a compressor control unit 85 that controls the start and stop of the compressor 12, a motor control unit 86 that controls the number of revolutions of the motors 44 and 94, and the flow rate adjustment valve 28 and the on-off valves 57 and 58. And a valve control unit 87 that controls opening and closing. The control unit 80 also includes a memory 89 such as a RAM (Random Access Memory) and a ROM (Read Only Memory). The cooling device 1 is controlled by the ECU 81 executing various processes according to the control program stored in the memory 89.

  The compressor control unit 85 receives the control command transmitted from the ECU 81, and transmits a signal C <b> 1 commanding activation or stop of the compressor 12 to the compressor 12. The valve control unit 87 receives the control command transmitted from the ECU 81, transmits a signal V1 for instructing the opening degree of the flow regulating valve 28 to the flow regulating valve 28, and opens and closes a signal V2 for instructing opening / closing setting of the on / off valve 57. The signal V 3 is transmitted to the valve 57, and a signal V 3 for commanding the opening / closing setting of the opening / closing valve 58 is transmitted to the opening / closing valve 58. The motor control unit 86 receives the control command transmitted from the ECU 81, transmits a signal M 1 for instructing the rotation speed of the motor 44 to the motor 44, and transmits a signal M 2 for instructing the rotation speed of the motor 94 to the motor 94.

  The ECU 81 operates and stops the compressor 12, the number of rotations of the motors 44 and 94, the opening degree of the flow rate adjustment valve 28, and the switching based on the ON / OFF of the air conditioner and various temperatures input to the temperature input unit 84. Controls the opening / closing setting of the valve 52. The ECU 81 has a function as an operation mode switching unit that switches the operation mode of the cooling device 1.

  The motor 44 is connected to the condenser fan 42 and rotationally drives the condenser fan 42. When the rotation speed of the motor 44 is changed, the heat exchange amount between the refrigerant and the outside air in the heat exchanger 14 is controlled. If the rotational speed of the motor 44 is increased and the rotational speed of the condenser fan 42 is increased, the flow rate of air supplied to the heat exchanger 14 increases, and the amount of heat exchange between the refrigerant and the outside air in the heat exchanger 14 increases. The refrigerant cooling capacity of the heat exchanger 14 is improved. If the rotational speed of the motor 44 is reduced and the rotational speed of the condenser fan 42 is reduced, the flow rate of air supplied to the heat exchanger 14 is reduced, and the amount of heat exchange between the refrigerant and the outside air in the heat exchanger 14 is reduced. The refrigerant cooling capacity of the heat exchanger 14 is reduced.

  When the number of revolutions of the motor 94 is changed, the amount of heat exchange between the refrigerant and the air for air conditioning in the heat exchanger 18 is controlled. When the rotational speed of the motor 94 is increased and the rotational speed of the air conditioning fan 93 is increased, the flow rate of the air conditioning air supplied to the heat exchanger 18 is increased, and heat exchange between the refrigerant and the air conditioning air in the heat exchanger 18 is performed. Since the amount increases, the cooling capacity for cooling the air-conditioning air by the heat exchanger 18 is improved. When the rotational speed of the motor 94 is decreased and the rotational speed of the air conditioning fan 93 is decreased, the flow rate of the air conditioning air supplied to the heat exchanger 18 is decreased, and heat exchange between the refrigerant and the air conditioning air in the heat exchanger 18 is performed. Since the amount decreases, the cooling capacity in the heat exchanger 18 decreases.

  FIG. 8 is a flowchart illustrating an example of a method for controlling the cooling device 1. FIG. 8 shows an example of a control flow for switching the operation mode of the cooling device 1 from the air conditioner operation mode to the heat pipe operation mode.

  As shown in FIG. 8, first, in step (S10), the flow rate adjustment valve 28 is closed. By setting the opening degree of the flow rate adjusting valve 28 to 0%, there is no refrigerant flow through the refrigerant passage 23. Thereby, the refrigerant condensed in the heat exchanger 14 does not flow through the refrigerant passage 23. The refrigerant condensed in the heat exchanger 14 is stored in the gas-liquid separator 40. All of the refrigerant flowing out of the gas-liquid separator 40 flows toward the cooling unit 30 via the refrigerant passage 34.

  Next, in step (S20), the on-off valve 57 is closed. At this time, both the opening / closing valve 57 and the opening / closing valve 58 are set to 0% in opening, and the refrigerant path between the cooling unit 30 and the heat exchanger 15 is blocked. The refrigerant flow toward 15 is stopped. While the refrigerant after heat exchange with the EV device 31 in the cooling unit 30 does not flow to the heat exchanger 18, the compressor 12 continues to operate.

  In this state, the refrigerant liquid adiabatically compressed by the compressor 12 and condensed by the heat exchanger 14 flows into the gas-liquid separator 40 and the supply of the refrigerant liquid to the gas-liquid separator 40 is continued. The liquid does not flow out from the gas-liquid separator 40. For this reason, the amount of liquid refrigerant stored in the gas-liquid separator 40 increases. FIG. 9 is a schematic diagram showing the state of the cooling device 1 after the step (S20) shown in FIG. The dotted line in FIG. 9 shows a path | route without a refrigerant | coolant flow among refrigerant paths.

  Next, in step (S30), the rotational speed of the condenser fan 42 is increased. By transmitting the signal M1 from the motor control unit 86 to the motor 44, the rotation speed of the motor 44 is increased. As the rotational speed of the motor 44 increases, the rotational speed of the condenser fan 42 connected to the motor 44 also increases. By rotating the condenser fan 42 at a high speed, the amount of air supplied from the condenser fan 42 to the heat exchanger 14 increases. Therefore, the amount of heat exchange between the refrigerant and the outside air in the heat exchanger 14 increases, and the ability to cool the refrigerant in the heat exchanger 14 increases.

  Thereby, since the liquefaction of the refrigerant in the heat exchanger 14 is promoted, the amount of the refrigerant in the liquid phase at the outlet of the heat exchanger 14 increases. Typically, all the refrigerant is liquefied in the heat exchanger 14, and the refrigerant flowing out of the heat exchanger 14 and flowing through the refrigerant passage 22 is in a saturated liquid or supercooled liquid state. Thus, by improving the refrigerant cooling capacity in the heat exchanger 14, the amount of the refrigerant liquid stored in the gas-liquid separator 40 can be increased more efficiently.

  After the operation of the compressor 12 is continued for a predetermined time in steps (S20) to (S30) to increase the amount of liquid refrigerant in the gas-liquid separator 40, the compressor 12 is then stopped in step (S40). . Subsequently, in step (S50), the on-off valve 58 is opened, the opening degree of the on-off valve 58 is set to 100%, and a path for the refrigerant flowing from the cooling unit 30 to the heat exchanger 14 via the communication path 51 is formed. Thereby, the setting of all the devices for switching the operation mode of the cooling device 1 is completed, and the operation mode of the cooling device 1 becomes the heat pipe operation mode shown in FIGS. 5 and 6. Switching of the switching valve 52 is completed by switching the opening / closing of the opening / closing valve 58, cooling of the EV device 31 is started while the compressor 12 is stopped, and the refrigerant circulates in the closed loop path shown in FIG.

  As described above, the cooling device 1 according to the present embodiment generates heat sources in both the “air conditioner operation mode” for driving the compressor 12 and the “heat pipe operation mode” for stopping the compressor 12. The EV device 31 can be cooled. In the heat pipe operation mode, the EV device 31 can be reliably cooled without the need to start the compressor 12, and therefore it is not necessary to always operate the compressor 12 for cooling the EV device 31. Therefore, the power consumption of the compressor 12 can be reduced and the fuel consumption of the vehicle can be improved. In addition, the life of the compressor 12 can be extended, so the reliability of the compressor 12 can be improved.

  The open / close state of the switching valve 52 is controlled in accordance with the start or stop of the compressor 12 for switching the operation mode of the cooling device 1. Thereby, switching between an air-conditioner operation mode and a heat pipe operation mode can be performed reliably, and a refrigerant | coolant can be distribute | circulated to the suitable path | route for each operation mode.

  Switching of the operation mode of the cooling device 1 can be performed by a passenger of the electric vehicle manually operating the control panel to switch the air conditioner on / off. When air conditioning in the passenger compartment is not necessary, if the passenger turns off the air conditioner, the operation mode of the cooling device 1 is switched so as to cool the EV device 31 in the heat pipe operation mode. Since the compressor 12 stops when the heat pipe operation mode is selected, the operation time of the compressor 12 can be further shortened. As a result, the effects of reducing the power consumption of the compressor 12 and improving the reliability of the compressor 12 can be obtained more significantly.

  The driving force for moving the refrigerant in the closed loop refrigerant path forming the thermosiphon heat pipe is only gravity acting on the liquid refrigerant and buoyancy acting on the gaseous refrigerant. Compared to the “air conditioner operation mode”, the driving force acting on the refrigerant is relatively small in the “heat pipe operation mode”. In particular, immediately after the compressor 12 is stopped for switching from the “air conditioner operation mode” to the “heat pipe operation mode”, the driving force for circulating the liquid refrigerant is reduced at a stretch, and as a result, the refrigerant liquid is supplied to the cooling unit 30. Is not supplied, and the refrigerant is gasified in the cooling unit 30, and there is a concern that the EV device 31 may not be sufficiently cooled (dry out).

  In the cooling device 1 of the present embodiment, both the on-off valve 57 and the on-off valve 58 are formed before the closed-loop refrigerant path is formed by devising the order of switching the switching valve 52 and stopping the compressor 12. The operation of the compressor 12 is continued in the fully closed state. The compressor 12 gives a driving force to the refrigerant, and the liquid refrigerant condensed in the heat exchanger 14 flows into the gas-liquid separator 40, whereby the amount of the liquid refrigerant in the gas-liquid separator 40 is increased. When the compressor 12 is stopped and the driving force of the refrigerant for cooling the EV device 31 that is a heat source is reduced, the refrigerant liquid is circulated from the gas-liquid separator 40 to the refrigerant passage 34. Thereby, the initial driving force of the loop heat pipe system is increased, and a decrease in the flow rate of the liquid-phase refrigerant supplied to the cooling unit 30 is suppressed.

  In this way, by replenishing the refrigerant circulation path with the refrigerant liquid stored in the gas-liquid separator 40, it is possible to secure the flow rate of the liquid-phase refrigerant flowing to the cooling unit 30. Therefore, a decrease in the cooling capacity of the EV device 31 at the start of the “heat pipe operation mode” can be suppressed, the cooling performance of the EV device 31 can be secured, and the EV device 31 can be stably cooled. Therefore, the occurrence of dryout can be suppressed, or even if the dryout occurs, the dryout can be eliminated at an early stage, so that the temperature rise of the EV device 31 can be effectively suppressed.

  By improving the control of the cooling device 1, the refrigerant is supplied to the gas-liquid separator 40 for a predetermined time (for example, a time during which the refrigerant liquid in the gas-liquid separator 40 can be sufficiently increased, for example, several seconds) before switching the refrigerant flow. The liquid refrigerant can be stored in the gas-liquid separator 40 by continuing the supply. When the operation mode is switched to the “heat pipe operation mode”, there is no need for new parts or devices for additionally supplying the liquid refrigerant to the closed loop refrigerant path. Therefore, it is possible to reliably maintain the cooling capacity of the EV device 31 when the operation mode is switched, and it is possible to avoid an increase in cost and an increase in the size of the device due to the addition of the configuration to the cooling device 1.

(Embodiment 2)
FIG. 10 is a flowchart illustrating another example of the control method of the cooling device 1. FIG. 10 shows another example of the control flow when the operation mode of the cooling device 1 is switched from the air conditioner operation mode to the heat pipe operation mode.

  As shown in FIG. 10, first, in step (S <b> 110), the flow rate adjustment valve 28 is closed as in step (S <b> 10) of the first embodiment, and the refrigerant does not flow through the refrigerant passage 23.

  Next, in step (S120), the rotational speed of the air conditioning fan 93 is decreased. By transmitting the signal M2 from the motor controller 86 to the motor 94, the rotational speed of the motor 94 is reduced. As the rotational speed of the motor 94 decreases, the rotational speed of the air conditioning fan 93 connected to the motor 94 also decreases. By rotating or stopping the air conditioning fan 93 at a low speed, the amount of air supplied from the air conditioning fan 93 to the heat exchanger 18 is reduced. Therefore, the amount of heat exchange between the refrigerant in the heat exchanger 18 and the air for air conditioning is reduced, and the vaporization of the refrigerant in the heat exchanger 18 is suppressed. When the ability to heat the refrigerant in the heat exchanger 18 is reduced, the degree of superheat of the refrigerant flowing out of the heat exchanger 18 is reduced.

  As the expansion valve 16, a temperature type expansion valve that is low in cost and does not require a control circuit is used. The expansion valve 16 senses the temperature of the refrigerant at the outlet of the heat exchanger 18 and automatically changes the opening according to the temperature of the refrigerant. The expansion valve 16 automatically opens as the temperature of the refrigerant in the heat exchanger 18 is suppressed, the degree of superheating of the refrigerant at the outlet of the heat exchanger 18 is reduced, and the temperature of the refrigerant is relatively lowered. And the flow rate of the refrigerant flowing through the expansion valve 16 decreases. Typically, the valve opening of the expansion valve 16 is reduced to 0%, thereby interrupting the flow of refrigerant through the expansion valve 16. That is, the opening degree of the expansion valve 16 is reduced by reducing the rotational speed of the air conditioning fan 93 in step (S120).

  FIG. 11 is a schematic diagram showing the state of the cooling device 1 after the step (S120) shown in FIG. The dotted line in FIG. 11 shows the path | route without a refrigerant | coolant flow among refrigerant paths. When the opening degree of the expansion valve 16 decreases and typically the opening degree of the expansion valve 16 becomes 0%, the flow of the refrigerant toward the heat exchanger 18 via the expansion valve 16 is stopped. At this time, since the compressor 12 continues to operate, the amount of liquid refrigerant stored in the gas-liquid separator 40 increases. In this state, the refrigerant that has exchanged heat with the cooling unit 30 is allowed to flow to the heat exchanger 15, and the refrigerant that has been heated by the cooling unit 30 and partially vaporized is condensed again and liquefied by the heat exchanger 15.

  Next, in step (S130), the rotational speed of the condenser fan 42 is increased. By increasing the rotation speed of the motor 44 and rotating the condenser fan 42 connected to the motor 44 at a high speed, the amount of air supplied from the condenser fan 42 to the heat exchanger 14 is increased. Thereby, since the liquefaction of the refrigerant in the heat exchanger 14 is promoted, the amount of the refrigerant in the liquid phase at the outlet of the heat exchanger 14 increases. By improving the refrigerant cooling capacity in the heat exchanger 14, the amount of the refrigerant liquid stored in the gas-liquid separator 40 can be increased more efficiently.

  After the operation of the compressor 12 is continued for a predetermined time in steps (S120) to (S130) to increase the amount of liquid refrigerant in the gas-liquid separator 40, the compressor 12 is then stopped in step (S140). . Subsequently, in step (S150), the switching setting of the switching valve 52 is switched. Specifically, the opening / closing valve 57 is closed to make the opening degree of the opening / closing valve 57 0%, and the opening / closing valve 58 is opened to make the opening degree of the opening / closing valve 58 100%. Thereby, the setting of all the devices for switching the operation mode of the cooling device 1 is completed, and the operation mode of the cooling device 1 becomes the heat pipe operation mode shown in FIGS. 5 and 6. When the switching between opening and closing of the on-off valves 57 and 58 is completed, cooling of the EV device 31 is started while the compressor 12 is stopped, and the refrigerant circulates in the closed loop path shown in FIG.

  In the cooling device 1 according to the second embodiment, similarly to the first embodiment, before the closed-loop refrigerant path is formed, the operation of the compressor 12 is continued and the amount of liquid refrigerant in the gas-liquid separator 40 is increased. Increase. When the compressor 12 is stopped, the flow rate of the liquid-phase refrigerant flowing to the cooling unit 30 can be secured by flowing the refrigerant liquid from the gas-liquid separator 40 to the refrigerant passage 34 and supplementing the refrigerant liquid. Therefore, a decrease in the cooling capacity of the EV device 31 at the start of the “heat pipe operation mode” can be suppressed, the cooling performance of the EV device 31 can be secured, and the EV device 31 can be stably cooled. Therefore, the occurrence of dryout can be suppressed, or even if the dryout occurs, the dryout can be eliminated at an early stage, so that the temperature rise of the EV device 31 can be effectively suppressed.

  When the operation of the compressor 12 is continued for a predetermined time with both of the on-off valves 57 and 58 described in the first embodiment being fully closed, if the EV device 31 generates a large amount of heat, it is heated by the cooling unit 30. The vaporized refrigerant stays in the cooling unit 30. The cooling unit 30 cools the EV device 31 using latent heat generated when the refrigerant in the saturated liquid state evaporates. Therefore, when the gas refrigerant fills the cooling unit 30, dryout occurs and the refrigerant is discharged from the EV device 31. There is a possibility that the amount of heat transfer to the battery will be significantly reduced, and as a result, the cooling of the EV device 31 may be insufficient.

  On the other hand, in the cooling device 1 according to the second embodiment, the gas refrigerant generated in the cooling unit 30 can be liquefied by the heat exchanger 15, so that the refrigerant vapor can be prevented from accumulating in the cooling unit 30. Therefore, since the EV device 31 can be prevented from being insufficiently cooled, the cooling capacity of the EV device 31 can be more reliably ensured. When the heat generation amount of the heat generation source is large due to the running state of the vehicle or the type of equipment to be cooled in the cooling unit 30, the heat generation source is further reliably cooled by cooling the heat generation source by the control of the second embodiment. Can be cooled. If the rotational speed of the fan that supplies the cooling air to the heat exchanger 15 is changed, the cooling capacity of the refrigerant in the heat exchanger 15 can be improved, and the cooling capacity of the EV device 31 can be ensured more reliably.

  Although the embodiments of the present invention have been described above, the configurations of the embodiments may be appropriately combined. In addition, it should be considered that the embodiment disclosed this time is illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  The cooling device control method of the present invention is a cooling method for cooling an electric device using a vapor compression refrigeration cycle for cooling the inside of the vehicle such as an electric vehicle equipped with an electric device such as a motor generator and an inverter. It can be applied particularly advantageously to the control of the device.

  DESCRIPTION OF SYMBOLS 1 Cooling device, 10 Vapor compression refrigeration cycle, 12 Compressor, 14, 15, 18 Heat exchanger, 16 Expansion valve, 21, 22, 23, 24, 25, 26, 27, 34, 36, 36a, 36b Refrigerant Passage, 28 Flow control valve, 30 Cooling unit, 31 EV equipment, 32 Cooling passage, 40 Gas-liquid separator, 42 Condenser fan, 44, 94 Motor, 51 Communication passage, 52 Switching valve, 54 Check valve, 57, 58 On-off valve, 60 ground, 80 control unit, 93 air conditioning fan.

Claims (6)

A control method of the cooling device (1) for cooling the heat source (31),
The cooling device (1)
A compressor (12) for circulating the refrigerant;
A heat exchanger (14) for exchanging heat between the refrigerant and outside air;
A cooling unit (30) for cooling the heat generation source (31) using the refrigerant;
A reservoir (40) for storing the liquid refrigerant condensed by the heat exchanger (14);
First passages (21, 22, 34, 36) through which the refrigerant discharged from the compressor (12) flows to the cooling unit (30) via the heat exchanger (14) and the accumulator (40) , 24-27),
When the compressor (12) stops, a second passage (21, 22, 34, circulates) the refrigerant between the heat exchanger (14) and the cooling unit (30) without applying power. 36a, 51),
A switching valve (52) for switching between communication of the first passage (21, 22, 34, 36, 24-27) and communication of the second passage (21, 22, 34, 36a, 51),
From the state where the first passages (21, 22, 34, 36, 24 to 27) communicate and the second passages (21, 22, 34, 36a, 51) are blocked, the first passages (21, 22). , 34, 36, 24-27),
After the blocking step, increasing the amount of liquid refrigerant stored in the reservoir (40);
After the increasing step, communicating the second passages (21, 22, 34, 36a, 51) while maintaining the blocking of the first passages (21, 22, 34, 36, 24-27); A method for controlling the cooling device (1). The switching valve (52) includes a first on-off valve (57) for switching communication and blocking of the first passage (21, 22, 34, 36, 24-27) and the second passage (21, 22, 34, 36a, 51) and a second on-off valve (58) for switching between communication and shut-off,
The blocking step includes a step (S20) of closing the first on-off valve (57),
The method for controlling the cooling device (1) according to claim 1, wherein the communicating step includes a step (S50) of opening the second on-off valve (58). The cooling device (1) includes an expansion valve (16) for decompressing the refrigerant, and a second heat exchanger (18) for exchanging heat between the refrigerant decompressed by the expansion valve (16) and air for air conditioning. ) And
The method for controlling the cooling device (1) according to claim 1, wherein the step of blocking includes a step (S120) of reducing an opening degree of the expansion valve (16). The expansion valve (16) is a temperature type expansion valve,
The cooling device (1) further includes an air conditioning fan (93) for supplying the air for air conditioning to the second heat exchanger (18),
The control method of the cooling device (1) according to claim 3, wherein the number of rotations of the air conditioning fan (93) is decreased in the decreasing step (S120).   The cooling device (1) further includes a third heat exchanger (15) that is provided between the heat exchanger (14) and the expansion valve (16) and exchanges heat between the refrigerant and outside air. The control method of the cooling device (1) of Claim 3 or Claim 4 included. The cooling device (1) includes an outside air supply fan (42) for supplying the outside air to the heat exchanger (14),
The method for controlling the cooling device (1) according to any one of claims 1 to 5, wherein the increasing step includes a step (S30, S130) of increasing the rotational speed of the outside air supply fan (42). .

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