JP2013105880A - Cooling device for electrical apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling device for an electrical apparatus in which dispersion of cooling efficiency is suppressed.SOLUTION: A cooling device for an electrical apparatus comprises a refrigerant passage formation member 120 which has a flat plate shape and is connected with an inverter element included in an EV device. The refrigerant passage formation member 120 forms a refrigerant passage 32 in which a refrigerant for vehicle internal air-conditioning flows in a direction of the flat plate, and a refrigerant arrangement space 181 which is arranged piled on the refrigerant passage 32 in a thickness direction to arrange a refrigerant. The refrigerant passage 32 includes: a porous conduit part 151A which has a porous conduit shape arranged in parallel with the flow direction of the refrigerant; a porous conduit part 151B which has a porous conduit shape arranged in parallel with the flow direction of the refrigerant, and is separated from the porous conduit part 151A by a partition 127 extending in parallel with the flow direction of the refrigerant; and a reversal space part which communicates the porous conduit part 151A and the porous conduit part 151B to reverse the flow direction of the refrigerant between the porous conduit part 151A and the porous conduit part 151B.

Description

  The present invention generally relates to a cooling device for an electric device mounted on a vehicle, and more specifically, relates to a cooling device for an electric device that uses a refrigerant for air conditioning in a passenger compartment.

  Regarding a conventional cooling apparatus for electric equipment, for example, Japanese Patent Laying-Open No. 2005-191527 discloses a stacked type cooler intended to have an excellent cooling capacity (Patent Document 1). The stacked cooler disclosed in Patent Document 1 includes a plurality of cooling rods in which refrigerant flow paths for circulating a cooling medium are formed, and a communication member that communicates between the plurality of cooling rods. The cooling pipe is provided with an electronic component in which a semiconductor element such as an IGBT and a diode, which constitute a part of the inverter for an automobile, are built in contact with each other. As the cooling medium, ethylene glycol antifreeze is used.

  Japanese Patent Application Laid-Open No. 2010-245158 discloses a water-cooled cooler used for cooling a heating element such as a power device, which is intended to improve the cooling performance (patent). Reference 2). In the cooler disclosed in Patent Document 2, a refrigerant flow path is formed between the cooler top plate and the cooler bottom plate. In the coolant channel, two corrugated fins are stacked via a plate-like body.

  Japanese Patent Application Laid-Open No. 2001-168254 discloses a heat exchanger that facilitates manufacture, reduces the manufacturing unit price, and improves heat exchange efficiency (Patent Document 3). The heat exchanger disclosed in Patent Document 3 includes a center plate, a base place connected to the heat generating member, and a fin member. The center plate is mainly composed of an extruded multi-hole rod having a plurality of flow paths formed therein.

  Japanese Patent Application Laid-Open No. 2010-140964 discloses a cooler for semiconductor elements intended to improve heat dissipation performance while suppressing an increase in pressure loss (Patent Document 4). The semiconductor element cooler disclosed in Patent Document 4 is provided with a casing provided with an inlet and an outlet for a refrigerant, an insulating substrate provided on an outer surface of the casing, to which an IGBT is attached, and an inner surface of the casing. It has corrugated fins to define. The corrugated fin is divided into a plurality of blocks in the flow direction of the refrigerant, and the pitch is shifted between adjacent blocks in a direction perpendicular to the flow direction of the refrigerant.

JP 2005-191527 A JP 2010-245158 A JP 2001-168254 A JP 2010-140964 A

  As a device for cooling an electric device mounted on a vehicle, a technology using a vapor compression refrigeration cycle for air conditioning in a vehicle interior has been proposed.

  In such a cooling device, since a refrigerant with a change in state between the gas phase and the liquid phase is used, the refrigerant is easily gasified, the specific gravity difference between the gas phase and the liquid phase of the refrigerant is large, and the response of the refrigerant cycle There is a characteristic that the nature is slow. Due to these characteristics, when heat generation conditions such as heat spots or sudden fluctuations in heat load occur in electrical equipment, the refrigerant can be bubbled and the bubbles can interfere with each other or cause local dryout. There is sex. As a result, there is a concern that the cooling efficiency of the electrical equipment varies.

  Accordingly, an object of the present invention is to solve the above-described problem and to provide a cooling device for an electric device in which variation in cooling efficiency is suppressed.

  The cooling device for electric equipment according to the present invention is a cooling device for electric equipment mounted on a vehicle. The cooling device for an electric device has a flat plate shape and includes a refrigerant passage forming member to which a heat source included in the electric device is connected. The refrigerant passage forming member is formed with a refrigerant passage through which the refrigerant for air conditioning in the passenger compartment flows in the plane direction and a refrigerant arrangement space in which the refrigerant passage is stacked in the thickness direction and in which the refrigerant is arranged. The refrigerant passage has a first porous ridge portion having a porous ridge shape arranged in parallel with the refrigerant flow direction, and a porous ridge shape arranged in parallel with the refrigerant flow direction, with respect to the refrigerant flow direction. A second porous flange portion separated from the first porous flange portion by a partition wall extending in parallel with each other, the first porous flange portion and the second porous flange portion communicate with each other, and the first porous flange portion, And an inversion space portion for reversing the flow direction of the refrigerant with the second porous ridge portion.

  According to the cooling device for an electric device configured as described above, the refrigerant arrangement space in which the refrigerant is arranged with respect to the refrigerant passage is affected by the effect of the cooling efficiency reduction caused by the refrigerant for the passenger compartment air conditioning generated in the refrigerant passage. It can be relieved by stacking. Further, by providing the inversion space portion between the first porous ridge portion and the second porous ridge portion, it is possible to agitate the refrigerant having a temperature difference while inverting the flow direction of the refrigerant. Thereby, it can suppress that dispersion | variation arises in the cooling efficiency of an electric equipment.

  Preferably, the heat generation source is connected to the refrigerant passage forming member such that a refrigerant arrangement space is located between the heat generation source and the refrigerant passage. A refrigerant having a specific heat larger than that of the refrigerant flowing through the refrigerant passage is arranged in the refrigerant arrangement space.

  According to the cooling device for an electrical device configured as described above, the refrigerant arrangement space positioned between the heat generation source and the refrigerant passage can be used as a heat storage layer that temporarily stores heat transmitted from the heat generation source. Accordingly, it is possible to suppress a phenomenon in which the refrigerant for the air conditioning in the passenger compartment is gasified due to the heat generation fluctuation in the heat generation source.

  Preferably, a refrigerant different from the refrigerant flowing through the refrigerant passage is stored in the refrigerant arrangement space. Preferably, a refrigerant different from the refrigerant flowing through the refrigerant passage is circulated in the refrigerant arrangement space.

  According to the cooling device for an electrical device configured as described above, the refrigerant stored or distributed in the refrigerant arrangement space can mitigate the influence of the cooling efficiency reduction caused by the refrigerant for the passenger compartment air conditioning generated in the refrigerant passage. Can do.

  Also preferably, the first porous ridge has a porous ridge shape different from the porous ridge shape of the second porous ridge. According to the electrical apparatus cooling device configured as described above, the refrigerant flow form changes between the first porous ridge portion and the second porous ridge portion, so that the refrigerant is agitated in the inversion space portion. Can be promoted.

  Preferably, the refrigerant passage forming member has an extrusion molding material for forming the first porous ridge portion and the second porous ridge portion. According to the cooling device for an electric device configured as described above, the pressure resistance of the first porous ridge portion and the second porous ridge portion can be ensured at low cost.

  As described above, according to the present invention, it is possible to provide a cooling device for an electric device in which variation in cooling efficiency is suppressed.

It is the schematic which shows the vehicle with which the cooling device of the electric equipment in Embodiment 1 of this invention is applied. It is a figure which shows typically the structure of the cooling device of the electric equipment in Embodiment 1 of this invention. It is a Mollier diagram which shows the state of the refrigerant | coolant in the vapor compression refrigeration cycle in FIG. 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 open / close state of a flow regulating valve and a switching valve in the cooling device for electric equipment in Embodiment 1 of the present invention. FIG. 3 is a front view showing the structure of a cooling unit in FIG. 2 in the electric apparatus cooling apparatus according to Embodiment 1 of the present invention. It is sectional drawing which shows the cooling part along the VIII-VIII line in FIG. It is sectional drawing which shows the 1st modification of the porous ridge shape which the porous ridge part in FIG. 8 has. It is sectional drawing which shows the 2nd modification of the porous ridge shape which the porous ridge part in FIG. 8 has. It is a front view which shows the modification of the cooling part in FIG. It is sectional drawing which shows the cooling part along the XII-XII line | wire in FIG. In the cooling device of the electric equipment in Embodiment 2 of this invention, it is a front view which shows the structure of the cooling part in FIG. It is sectional drawing which shows the cooling part along the XIV-XIV line | wire in FIG. It is a front view which shows the modification of the cooling unit in FIG. It is a rear view which shows the cooling part in FIG. It is sectional drawing which shows the cooling part along the XVII-XVII line | wire in FIG. It is a perspective view which shows the cooling device of the battery mounted in a vehicle.

  Embodiments of the present invention will be described with reference to the drawings. In the drawings referred to below, the same or corresponding members are denoted by the same reference numerals.

(Embodiment 1)
FIG. 1 is a schematic diagram showing a vehicle to which a cooling device for electric equipment according to Embodiment 1 of the present invention is applied.

  A vehicle 1000 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. The hybrid uses the engine 100 and the drive unit 200 as power sources. It is a car.

  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. The drive unit 200 is electrically connected to the PCU 700 by a cable 500. PCU 700 is electrically connected to traveling battery 400 by cable 600.

  FIG. 2 is a diagram schematically showing the configuration of the cooling device for an electric device according to Embodiment 1 of the present invention.

  Referring to FIG. 2, the cooling device for electric equipment in the present embodiment includes a vapor compression refrigeration cycle 10. The vapor compression refrigeration cycle 10 is mounted on the vehicle 1000, for example, for cooling the passenger compartment. For cooling using the vapor compression refrigeration cycle 10, for example, when a switch for performing cooling is turned on, or an automatic control mode for automatically adjusting the temperature in the passenger compartment to a set temperature is selected. And 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, an expansion valve 16 as an example of a decompressor, and a second heat exchanger. And a heat exchanger 18. The vapor compression refrigeration cycle 10 includes a gas-liquid separator 40 disposed on a 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 have tubes that circulate the refrigerant, and fins for exchanging heat between the refrigerant that circulates in 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. The cooling air may be supplied to the heat exchangers 14 and 15 by forced ventilation from a cooling 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. Note that the decompressor for decompressing the refrigerant liquid is not limited to the expansion valve 16 that is squeezed and expanded, and may be a capillary tube.

  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 decompressed 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 room. The air-conditioning air whose temperature has been lowered by the heat being absorbed by the heat exchanger 18 is returned to the passenger compartment, thereby cooling the passenger compartment. The refrigerant absorbs heat from the surroundings in the heat exchanger 18 and is heated.

  The heat exchanger 18 has a tube that circulates the refrigerant, and fins that exchange heat between the refrigerant that circulates in 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, the refrigerant 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 includes a refrigerant passage 21 that communicates the compressor 12 and the heat exchanger 14, refrigerant passages 22, 23, and 24 that communicate the heat exchanger 14 and the heat exchanger 15, and a heat exchanger. 15 and a refrigerant passage 25 that communicates the expansion valve 16, a refrigerant passage 26 that communicates the expansion valve 16 and the heat exchanger 18, and a refrigerant passage 27 that communicates the heat exchanger 18 and the compressor 12.

  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 is provided on the refrigerant path between the heat exchanger 14 and the heat exchanger 15. 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 as the third heat exchanger.

  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 into the expansion valve 16 from the outlet side of the heat exchanger 15, the refrigerant passage 23 connected to the inlet side of the heat exchanger 15, and the refrigerant passage 23 through which the steam flows out and flows through the flow rate adjusting valve 28 described later. And a refrigerant passage 25 to be made. 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 includes a refrigerant passage 34 that communicates the gas-liquid separator 40 and the cooling unit 30, and a refrigerant that communicates the cooling unit 30 and the refrigerant passage 24. And a 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, point D is an end on the downstream side (side close to the heat exchanger 15) of the refrigerant passage 23, an end on the upstream side (side close to the heat exchanger 14) of the refrigerant passage 24, and the refrigerant passage. The downstream end of 36 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 electric device cooling apparatus according to the present embodiment includes a refrigerant path arranged in parallel with the refrigerant path 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 the vehicle, and a refrigerant passage 32 through which a refrigerant for air conditioning of the passenger compartment flows. The EV device 31 includes a heat source that generates heat during the exercise. One end of the refrigerant passage 32 is connected to the refrigerant passage 34. The other end of the refrigerant 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. The passage 34, the refrigerant passage 32 included in the cooling unit 30, and the refrigerant passage 36 on the downstream side (side closer to the heat exchanger 15) than the cooling unit 30. 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 via the refrigerant passage 32 takes heat from the heat source included in the EV device 31 as an electric device, and cools the EV device 31. The cooling unit 30 cools the EV device 31 using a liquid-phase refrigerant separated in the gas-liquid separator 40 and flowing to the refrigerant passage 32 via the refrigerant passage 34. In the cooling unit 30, the refrigerant flowing through the refrigerant passage 32 and the heat source included in 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 refrigerant passage 32. The structure of the cooling unit 30 will be described later in detail.

  The EV device 31 is disposed outside the refrigerant passage 32. In this case, the EV device 31 does not interfere with the flow of the refrigerant flowing through the refrigerant passage 32. For this reason, 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.

  The EV device 31 is an electrical 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. A fan 93 is disposed in the vicinity of the duct inlet 91 inside the duct 90.

  When the fan 93 is driven, air flows in the duct 90. When the fan 93 is in operation, air for air conditioning 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 in FIG. 2. 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. The 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.

  Referring to FIG. 3, the superheated vapor refrigerant (point A) sucked into compressor 12 is adiabatically compressed along isoentropic lines in compressor 12. 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 decreases and the refrigerant liquefies. 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 refrigerant 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 electric device cooling apparatus according to the present embodiment 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 passenger compartment. 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. For this reason, since a structure required for the cooling device of the EV equipment 31 can be reduced and the device structure can be simplified, the manufacturing cost of the cooling device 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 a cooling device for electric equipment 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 refrigerant 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. For this reason, 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 refrigerant is 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. In contrast, in the electrical apparatus cooling apparatus according to the present embodiment, in the vapor compression refrigeration cycle 10, the high-pressure refrigerant discharged from the compressor 12 is converted into a heat exchanger 14 as a first condenser, It is condensed by both the heat exchanger 15 as a second 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. For this reason, 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. For this reason, it is desirable to cool the refrigerant sufficiently in the heat exchanger 14 so that the entire amount of the refrigerant is not vaporized 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 a cooling device for an electric device that secures both the cooling capability for the passenger compartment and the cooling capability 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. It is possible to provide a cooling device for electric equipment with improved performance.

  By introducing the refrigerant in a saturated liquid state at the outlet of the gas-liquid separator 40 into the refrigerant passage 32 that cools 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 refrigerant passage 32. Among the refrigerants, the gas-phase refrigerant can be minimized. For this reason, since 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. 10 performance degradation 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.

  Referring to FIG. 2, the cooling device for electrical equipment in the present embodiment includes a flow rate adjustment 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 or 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 refrigerant 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 flow rate of the refrigerant that flows to the refrigerant passage 32 via the cooling line and cools the EV device 31 is reduced. 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 refrigerant 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 electric device cooling apparatus according to the present embodiment further includes a refrigerant passage 51. The refrigerant 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 and 36 through which the refrigerant flows through the cooling unit 30. The passage 36 communicates. The refrigerant passage 36 is divided into a refrigerant passage 36 a upstream from the branch with the refrigerant passage 51 and a refrigerant passage 36 b downstream from the branch with the refrigerant passage 51.

  The refrigerant passage 36 and the refrigerant passage 51 are provided with a switching valve 52 that switches the communication state between the refrigerant passage 51 and the refrigerant passages 21 and 36. The switching valve 52 enables or disables the circulation of the refrigerant through the refrigerant passage 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 refrigerant passage 51 and the refrigerant passage 21. Any route to the heat exchanger 14 via can be arbitrarily selected and distributed.

  More specifically, two valves 57 and 58 are provided as the switching valve 52. During the cooling operation of the vapor compression refrigeration cycle 10, the valve 57 is fully opened (valve opening degree 100%), the valve 58 is fully closed (valve opening degree 0%), and the valve opening degree of the flow control valve 28 is set to the cooling unit. 30 is adjusted so that sufficient refrigerant flows. 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 valve 58 is fully opened, the valve 57 is fully closed, and the flow rate adjustment valve 28 is fully closed. As a result, the refrigerant flowing through the refrigerant passage 36 a after cooling the EV device 31 is circulated to the heat exchanger 14 via the refrigerant passage 51, and the cooling unit 30 and the heat exchanger without passing through the compressor 12. 14 can form an annular path for circulating the refrigerant.

  FIG. 4 is a schematic diagram showing a flow of a refrigerant for cooling the EV equipment during operation of the vapor compression refrigeration cycle. FIG. 5 is a schematic diagram showing a flow of a refrigerant that cools the EV equipment while the vapor compression refrigeration cycle is stopped. FIG. 6 is a diagram showing an open / close state of the flow rate adjustment valve and the switching valve in the cooling apparatus for electric equipment according to Embodiment 1 of the present invention.

  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.

  Referring to 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 adjusting 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, when the valve 57 is fully opened and the valve 58 is fully closed, the refrigerant path is selected so that the refrigerant flows through the entire cooling device. For this reason, while being able to ensure the cooling capacity of the vapor compression refrigeration cycle 10, the EV equipment 31 can be efficiently cooled.

  With reference to FIGS. 5 and 6, when 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 valve 57 is fully closed, the valve 58 is fully opened, and the flow rate adjustment valve 28 is fully closed, whereby the refrigerant flows through the refrigerant passage 51 without flowing from the refrigerant passage 36a to the refrigerant passage 36b. 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 refrigerant passage 51, and the refrigerant passage 21 in order to the heat exchanger 14. A closed, closed circular path is formed. The 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 refrigerant 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 refrigerant 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.

  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, the 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.

  As the switching valve 52 for switching the communication state between the refrigerant passage 51 and the refrigerant passages 21, 36, the above-described pair of valves 57, 58 may be used, or arranged at a branch between the refrigerant passage 36 and the refrigerant passage 51. It is also possible to use a three-way valve. In any case, the EV apparatus 31 can be efficiently cooled both when the vapor compression refrigeration cycle 10 is operated and when it is stopped. The valves 57 and 58 are inexpensive because they only need to have a simple structure capable of opening and closing the refrigerant passage. By using the two valves 57 and 58, it is possible to provide a cooling structure for electric equipment 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 valves 57 and 58. By using the three-way valve, the electric device having a smaller size and excellent vehicle mountability can be obtained. A cooling structure can be provided.

  The cooling structure for electrical equipment in the present embodiment 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 refrigerant 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 refrigerant passage 51 to the refrigerant passage 21 on the compressor 12 side. Since the check valve 54 is provided, the flow of the refrigerant from the refrigerant passage 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.

  That is, the cooling device for electric equipment in the present embodiment constitutes a vapor compression refrigeration cycle, and includes refrigerant passages 21 to 27 as circulation passages through which refrigerant for vehicle air conditioning circulates, refrigerant passages 21 to 27, and refrigerant. Refrigerant passages 34, 36, 51 serving as communication passages communicating with the passage 32, and refrigerant flow between the refrigerant passages 21-27 and the refrigerant passage 32, provided on the passages of the refrigerant passages 34, 36, 51. And a switching valve 52 (valve 57 and valve 58) for allowing or shutting off.

  Next, the structure of the cooling unit 30 in FIG. 2 that constitutes the cooling device for the electric equipment in the present embodiment will be described in detail. FIG. 7 is a front view showing the structure of the cooling unit in FIG. 2 in the electrical apparatus cooling apparatus according to Embodiment 1 of the present invention. FIG. 8 is a cross-sectional view showing the cooling unit along the line VIII-VIII in FIG. 7.

  Referring to FIGS. 7 and 8, cooling unit 30 includes a refrigerant passage forming member 120, a refrigerant supply pipe 141, and a refrigerant discharge pipe 142.

  The refrigerant passage forming member 120 has a flat plate shape. In the present embodiment, refrigerant passage forming member 120 has a rectangular parallelepiped shape having a size of a (vertical) × b (horizontal) × t (thickness) (a, b> t). The refrigerant passage forming member 120 is made of a material having excellent thermal conductivity. The refrigerant passage forming member 120 is made of a metal such as aluminum or copper.

  The refrigerant passage forming member 120 has an element mounting surface 122. The element mounting surface 122 has a size of a (vertical) × b (horizontal), and is a side surface having the largest area among a plurality of side surfaces of the refrigerant passage forming member 120. In this specification, the direction in which the element mounting surface 122 extends is referred to as the planar direction of the refrigerant passage forming member 120. The direction orthogonal to the element mounting surface 122, that is, the direction in which the end side having the thickness t of the refrigerant passage forming member 120 extends is referred to as the thickness direction of the refrigerant passage forming member 120.

  A plurality of inverter elements 110 are connected to the refrigerant passage forming member 120. The plurality of inverter elements 110 are joined to the element mounting surface 122. The plurality of inverter elements 110 are arranged in a matrix on the element mounting surface 122 at intervals. When the EV device 31 in FIG. 2 is an inverter, the inverter element 110 is provided as a heat source included in the inverter.

  The refrigerant passage forming member 120 is formed with the refrigerant passage 32 in FIG. A refrigerant for vehicle air conditioning (A / C (Air Conditioner) refrigerant) is circulated through the refrigerant passage 32. The refrigerant passage 32 is formed so that the A / C refrigerant flows in the plane direction of the refrigerant passage forming member 120. The refrigerant passage 32 is formed to extend in a plane parallel to the element mounting surface 122. The heat generated in the inverter element 110 is transferred to the refrigerant passage forming member 120 and is radiated to the A / C refrigerant flowing through the refrigerant passage 32.

  The refrigerant supply pipe 141 is connected to the refrigerant passage forming member 120 as a refrigerant supply unit for supplying the A / C refrigerant to the refrigerant passage 32. The refrigerant discharge pipe 142 is connected to the refrigerant passage forming member 120 as a refrigerant discharge portion for discharging the A / C refrigerant from the refrigerant passage 32.

  The refrigerant passage 32 includes a plurality of porous ridge portions 151 having a porous ridge shape arranged in parallel with the flow direction of the A / C refrigerant, and a plurality of reset space portions 157 for discharging bubbles contained in the A / C refrigerant. And a plurality of sections including a reversal space 156 for reversing the refrigerant flow.

  The plurality of porous ridges 151 are arranged at intervals in the flow direction of the A / C refrigerant. The reset space 157 is disposed between the porous flanges 151 adjacent to each other in the flow direction of the A / C refrigerant. The inversion space portion 156 is disposed between the porous flange portions 151 adjacent to each other in the flow direction of the A / C refrigerant. The inversion space portion 156 is provided so as to reverse the flow direction of the refrigerant between the porous flange portions 151 arranged on both sides thereof.

  More specifically, the plurality of porous ridges 151 are provided in two rows in the flow direction of the A / C refrigerant. Among the plurality of porous ridges 151, the one provided in the first row is referred to as a plurality of porous ridges 151Y, and the one provided in the second row is referred to as a plurality of porous ridges 151X. The plurality of porous ridges 151X are provided such that the flow direction of the refrigerant is the same between the plurality of porous ridges 151X. The plurality of porous ridges 151Y are provided such that the flow direction of the refrigerant is the same between the plurality of porous ridges 151Y.

  Of the plurality of porous ridges 151X, one disposed at one end is particularly referred to as a porous ridge 151A, and among the plurality of porous ridges 151X, one disposed at the other end is particularly referred to as a porous ridge 151B. Of the plurality of porous ridges 151Y, the one disposed at one end is particularly referred to as a porous ridge 151C, and among the plurality of porous ridges 151Y, the one disposed at the other end is particularly referred to as a porous ridge 151D.

  A reset space portion 157 is provided between the adjacent porous flange portions 151X. A reset space 157 is provided between the adjacent porous flanges 151Y. An inversion space portion 156 is provided at a position adjacent to the porous flange portion 151A and the porous flange portion 151C. The inversion space portion 156 is disposed on the opposite side of the reset space portion 157 with respect to the porous flange portion 151A and the porous flange portion 151C. A refrigerant discharge pipe 142 is connected to the perforated portion 151B. A refrigerant supply pipe 141 is connected to the perforated portion 151D.

  The refrigerant passage forming member 120 includes a case body 126, a lid body 121, a partition wall 127, and a plurality of extrusion molding materials 131. The case body 126 has a housing shape that opens in one direction. The lid 121 is provided so as to close the opening of the case body 126. The lid 121 is joined to the case body 126 by brazing. The partition wall 127 is accommodated in the case body 126. The partition wall 127 is provided so as to separate the plurality of porous ridges 151X and the plurality of porous ridges 151Y.

  The extrusion molding material 131 forms a porous flange 151. The extruded material 131 is formed by extruding a metal such as aluminum. The extrusion molding material 131 has a flat plate-like appearance. At the time of extrusion molding, the extrusion molding material 131 is formed with a plurality of holes 152 that form the flow path of the A / C refrigerant in the porous flange 151. The extrusion molding material 131 is accommodated in the case body 126 and disposed at a position corresponding to each of the plurality of porous flanges 151. The extrusion molding material 131 that forms the porous flange portion 151X and the extrusion molding material 131 that forms the porous flange portion 151Y are disposed on both sides of the partition wall 127.

  A reset space 157 is formed in the space between the extrusion molding materials 131 adjacent to each other. In the reset space 157, a plurality of holes 152 of the extrusion molding 131 disposed on both sides thereof are opened. The plurality of holes 152 of the extrusion molding material 131 are opened to one space in the reset space 157. The flow path cross section of the A / C refrigerant in the reset space 157 is larger than the flow path cross section of the A / C refrigerant in the porous flange 151. The reset space 157 is formed in a space surrounded by two extruded moldings 131, a case body 126, a lid body 121, and a partition wall 127 arranged on both sides thereof.

  An inversion space portion 156 is formed in a space adjacent to the extrusion molding material 131 that forms the porous flange portion 151A and the extrusion molding material 131 that forms the porous flange portion 151C. In the inversion space portion 156, a plurality of holes 152 of the extrusion molding material 131 forming the porous flange portion 151A and a plurality of holes 152 of the extrusion molding material 131 forming the porous flange portion 151C are opened. The inversion space portion 156 is surrounded by the extrusion molding material 131 that forms the porous flange portion 151A, the extrusion molding material 131 that forms the porous flange portion 151C, the case body 126, the lid body 121, and the partition wall 127. It is formed in space.

  The refrigerant passage forming member 120 is provided with a gas recovery mechanism (not shown) for recovering bubbles discharged in the reset space portion 157 and the inversion space portion 156. The gas recovery mechanism is configured by, for example, a valve that is opened when the pressure becomes equal to or higher than a certain pressure, and is provided on the upper surfaces of the reset space 157 and the inversion space 156. The bubbles recovered by the gas recovery mechanism are returned to the gas-liquid separator 40 as a gas-phase refrigerant through the refrigerant passage 35 connecting the cooling unit 30 and the gas-liquid separator 40 shown in FIG.

  The A / C refrigerant supplied to the refrigerant passage 32 through the refrigerant supply pipe 141 flows alternately through the porous ridges 151 and the reset space 157, and then flows into the reversal space 156 from the porous ridges 151C. The A / C refrigerant reverses the flow direction in the inversion space portion 156 and flows into the porous ridge portion 151A. Further, the A / C refrigerant flows alternately through the perforated wall portion 151 and the reset space portion 157, and then is discharged from the refrigerant passage 32 through the refrigerant discharge pipe 142. While the A / C refrigerant flows through the refrigerant passage 32, the A / C refrigerant cools the EV device 31 by exchanging heat with the refrigerant passage forming member 120 transferred from the inverter element 110. The refrigerant passage forming member 120 functions as a heat exchanger that performs heat exchange between the EV device 31 and the A / C refrigerant.

  In the present embodiment, the plurality of porous ridges 151 are provided in two rows. However, the present invention is not limited to this, and the plurality of porous ridges 151 may be provided in three or more rows. In this case, the inversion space portions 156 are alternately provided at one end and the other end of the plurality of porous flange portions 151 arranged in each row, and the A / C refrigerant flows through the refrigerant passage 32 while meandering.

  In the electric device cooling apparatus according to the present embodiment, a refrigerant for air conditioning of the passenger compartment (A / C refrigerant) is used for cooling the EV device 31. The A / C refrigerant is easy to gasify (evaporate) and has a feature such as a large specific gravity difference between the gas state and the liquid state. When such an A / C refrigerant is used, in the inverter element 110 that is the heat generation source of the EV device 31, if heat generation like a heat spot occurs or the heat generation load fluctuates in a short time, heat is generated as latent heat of evaporation. The absorbed A / C refrigerant is bubbled, and interference between the bubbles may occur. As a result, there is a concern that the cooling efficiency of the EV device 31 varies.

  On the other hand, in the present embodiment, a reset space 157 in which a flow path formed in the porous ridge portion 151 is opened is provided between the adjacent porous ridge portions 151. With such a configuration, in the reset space portion 157, it is possible to discharge the A / C refrigerant bubbles generated in the perforated trough 151, or to suppress the temperature difference of the A / C refrigerant by stirring the A / C refrigerant. . Moreover, in this Embodiment, the flow of an A / C refrigerant | coolant is made into a reciprocating (U-turn) flow by forming the inversion space part 156 between the porous collar part 151A and the porous collar part 151C. Thereby, in the reversal space 156, the A / C refrigerant having a temperature difference can be stirred while the flow direction of the A / C refrigerant is reversed, or the bubbles in the A / C refrigerant can be discharged. Thereby, since the A / C refrigerant having a more uniform temperature is supplied to the perforated flange 151 in a state in which bubbles are not included, it is possible to suppress variation in the cooling efficiency of the EV device 31.

  Further, when the EV apparatus 31 is cooled using an A / C refrigerant, the heat exchanger is required to have a planar shape so as to easily take heat and to have high pressure resistance (for example, 3 MPa or more). Is done. In this Embodiment, such a request can be implement | achieved by low cost by using the extrusion molding material 131 for the porous collar part 151. FIG.

  In addition, since A / C refrigerant | coolant is a gas-liquid two-phase fluid within a heat exchanger, a gaseous-phase ratio increases with heat absorption (dryness increases). That is, the A / C refrigerant flows through the heat exchanger while changing the dryness. For this reason, when using an A / C refrigerant, the gas escapes upward when the A / C refrigerant is supplied from the lower side of the heat exchanger and the A / C refrigerant is discharged from the upper side of the heat exchanger. It is advantageous because it is easy. The heat exchanger may be tilted so that the refrigerant discharge part is on the upper side.

  The plurality of porous ridges 151 are composed of two types of porous ridges 151p as first porous ridges and porous ridges 151q as second porous ridges. The porous flange 151p and the porous flange 151q are arranged adjacent to each other in the flow direction of the A / C refrigerant. The porous ridges 151p and the porous ridges 151q are alternately arranged in the flow direction of the refrigerant. The types of the porous flange 151A and the porous flange 151C that are adjacent to each other across the inversion space 156 are the porous flange 151p and the porous flange 151q, respectively.

  The porous ridge shape of the porous ridge portion 151p is different from the porous ridge shape of the porous ridge portion 151q. The shape, number, and position of the holes 152 that form the flow path of the A / C refrigerant are different between the shape of the perforated portion of the perforated portion 151p and the shape of the perforated portion of the perforated portion 151q. As shown in FIG. 8, in the present embodiment, the porous ridge portion 151 q has a porous ridge shape including four holes having a rectangular cross section and two holes having a circular cross section disposed on both sides thereof. On the other hand, the porous ridge portion 151p has a porous ridge shape composed of nine holes having a circular cross section.

  According to such a configuration, a change occurs in the form of the flow of the A / C refrigerant between the porous ridge portion 151p and the porous ridge portion 151q having different porous ridge shapes. For this reason, in the reset space part 157 and the inversion space part 156, discharge of bubbles and stirring of the A / C refrigerant can be promoted.

  FIG. 9 is a cross-sectional view showing a first modified example of a porous ridge shape which the porous ridge portion in FIG. 8 has. FIG. 10 is a cross-sectional view showing a second modified example of the porous ridge shape of the porous ridge portion in FIG.

  Referring to FIG. 9, in the present modification, the multi-hole ridge portion 151q has a multi-pore shape including five holes having a circular cross section, whereas the multi-hole portion 151p includes seven holes having a circular cross section. It has a porous shape. Referring to FIG. 10, in the present modification, the multi-hole ridge portion 151q includes three holes having a triangular cross section disposed at both ends and the center, and two rectangular cross sections disposed between the holes of the triangular cross section. While the perforated portion 151p has a rectangular cross section disposed between three holes of a rectangular cross section arranged at both ends and the center, and a hole of the rectangular cross section It has a perforated shape consisting of two holes.

  Also in these modified examples, it is possible to obtain the effect of promoting the discharge of bubbles and the stirring of the A / C refrigerant in the reset space 157 and the inversion space 156.

  FIG. 11 is a front view showing a modification of the cooling unit in FIG. FIG. 12 is a cross-sectional view showing the cooling unit along the line XII-XII in FIG.

  With reference to FIG. 11 and FIG. 12, in the present modification, a plurality of porous ridge portions 151 are provided side by side in a direction orthogonal to the flow direction of the refrigerant flowing through each porous ridge portion 151. The inversion space portion 156 is disposed between the porous flange portions 151 adjacent to each other in the flow direction of the A / C refrigerant. The inversion space portion 156 is provided so as to invert the flow of the A / C refrigerant between the porous flange portions 151 disposed on both sides thereof. The plurality of porous ridges 151 are composed of two types of porous ridges 151p and porous ridges 151q. The porous flange 151p and the porous flange 151q are arranged adjacent to each other in the flow direction of the A / C refrigerant. The porous ridges 151p and the porous ridges 151q are alternately arranged in the flow direction of the refrigerant.

  The A / C refrigerant supplied to the refrigerant passage 32 through the refrigerant supply pipe 141 flows alternately through the perforated flange portion 151 and the inversion space portion 156 while meandering, and is discharged from the refrigerant passage 32 through a refrigerant discharge pipe (not shown). The

  In this modification, the reset space 157 in FIG. 7 is provided as the same space as the inversion space 156.

  The structure of the electric device cooling apparatus according to Embodiment 1 of the present invention described above will be described together. The electric apparatus cooling device according to the present embodiment is an EV apparatus 31 as an electric apparatus mounted on a vehicle. The cooling device. The cooling device for an electric device has a flat plate shape and includes a refrigerant passage forming member 120 to which an inverter element 110 as a heat source included in the EV device 31 is connected. The refrigerant passage forming member 120 is formed with a refrigerant passage 32 through which a refrigerant for air conditioning in the passenger compartment flows. The refrigerant passage 32 has a plurality of porous flanges 151 arranged in parallel to the refrigerant flow direction, and a plurality of porous flanges 151 arranged at intervals from each other, and the porous flanges 151 adjacent to each other in the refrigerant flow direction. The reset space 157 that discharges bubbles contained in the refrigerant and the porous flanges 151 that are adjacent to each other in the refrigerant flow direction communicate with each other, and the refrigerant flows between the adjacent porous flanges 151 And an inversion space portion 156 for inverting the direction.

  According to the electrical apparatus cooling device in Embodiment 1 of the present invention configured as described above, by providing the reset space portion 157 or the inversion space portion 156 between the adjacent porous flange portions 151, the A / The bubbles of C refrigerant can be discharged, or the A / C refrigerant having a temperature difference can be stirred. As a result, the cooling efficiency of the EV device 31 varies depending on the cooling structure using the A / C refrigerant that is easily gasified and has a large specific gravity difference between the gas state and the liquid state. Can be suppressed.

(Embodiment 2)
FIG. 13 is a front view showing the structure of the cooling unit in FIG. 2 in the cooling apparatus for electric equipment according to Embodiment 2 of the present invention. FIG. 14 is a cross-sectional view showing the cooling unit along line XIV-XIV in FIG. 13. Hereinafter, in the description of the structure of the cooling device for electric equipment in the present embodiment, the description of the structure that overlaps with the cooling device for electric equipment in Embodiment 1 will not be repeated.

  Referring to FIGS. 13 and 14, cooling unit 30 includes a refrigerant passage forming member 120, a refrigerant supply pipe and a refrigerant discharge pipe 142 (not shown). In the refrigerant passage forming member 120, a refrigerant arrangement space 181 is formed in addition to the refrigerant passage 32 in FIG.

  The refrigerant passage 32 is formed from a plurality of sections including a plurality of porous ridge portions 151 having a porous ridge shape arranged in parallel with the flow direction of the A / C refrigerant, and an inversion space portion 156 for inverting the flow of the refrigerant. It is configured. The plurality of porous ridges 151 are provided side by side in a direction orthogonal to the flow direction of the refrigerant flowing through each porous ridge 151.

  In the range shown in FIG. 13, the porous flange 151 provided on the upstream side of the refrigerant flow is referred to as a porous flange 151 </ b> A, adjacent to the porous flange 151 </ b> A in the refrigerant flow direction, and downstream of the refrigerant flow. The perforated portion 151 provided on the side is referred to as a perforated portion 151B. The inversion space portion 156 is disposed between the porous flange portions 151 adjacent to each other in the flow direction of the A / C refrigerant. The inversion space portion 156 is provided so that the perforated trough portion 151A and the perforated trough portion 151B communicate with each other. The inversion space portion 156 is provided so as to invert the flow of the A / C refrigerant between the porous flange portions 151A and the porous flange portions 151B arranged on both sides thereof.

  The plurality of porous ridges 151 are composed of two types of porous ridges 151p and porous ridges 151q. The porous flange 151p and the porous flange 151q are arranged adjacent to each other in the flow direction of the A / C refrigerant. The porous ridges 151p and the porous ridges 151q are alternately arranged in the flow direction of the refrigerant. Both the perforated portion 151p and the perforated portion 151q have a perforated shape including four holes having a rectangular cross section, but the cross-sectional sizes of the holes are different from each other.

  The A / C refrigerant supplied to the refrigerant passage 32 through a refrigerant supply pipe (not shown) alternately flows through the perforated portion 151 and the inversion space portion 156 while meandering, and is discharged from the refrigerant passage 32 through the refrigerant discharge pipe 142. Is done.

  The refrigerant arrangement space 181 is formed by a path independent of the refrigerant passage 32. The refrigerant arrangement space 181 is provided so as to be stacked with the refrigerant passage 32 in the thickness direction of the refrigerant passage forming member 120. When the element mounting surface 122 is viewed from the front, the refrigerant arrangement space 181 and the refrigerant passage 32 overlap each other. The refrigerant arrangement space 181 is provided between the refrigerant passage 32 and the inverter element 110 mounted on the element mounting surface 122.

  A refrigerant is arranged in the refrigerant arrangement space 181. In the present embodiment, the refrigerant is stored in the refrigerant arrangement space 181. The refrigerant is hermetically arranged in the refrigerant arrangement space 181.

  The refrigerant stored in the refrigerant arrangement space 181 is a refrigerant different from the A / C refrigerant circulated through the refrigerant passage 32. The refrigerant stored in the refrigerant arrangement space 181 has a specific heat larger than the specific heat of the A / C refrigerant flowing through the refrigerant passage 32. That is, the refrigerant stored in the refrigerant arrangement space 181 has a characteristic that it is harder to be warmed and harder to cool than the A / C refrigerant circulated in the refrigerant passage 32. As the refrigerant stored in the refrigerant arrangement space 181, for example, a gel medium having good thermal conductivity is used.

  The refrigerant passage forming member 120 includes an extrusion molding material 161, a partition wall 127, a lid body 162, and a lid body 163.

  The extrusion molding material 161 forms a porous flange 151, a reversal space 156, and a refrigerant arrangement space 181. The extrusion molding material 161 is formed by extrusion molding a metal such as aluminum. The extruded material 161 has a flat plate-like appearance. At the time of extrusion molding, the extrusion molding material 161 is formed with a plurality of holes 152 that form a flow path of the A / C refrigerant in the porous flange 151 and holes 186 that define the refrigerant arrangement space 181. By processing the opening end face of the extrusion molding material 161 that is performed after the extrusion molding, a space that forms the flow path of the A / C refrigerant in the reversal space portion 156 is formed.

  The partition wall 127 is formed integrally with the extrusion molding material 161. The partition wall 127 is provided so as to separate the two porous flange portions 151 adjacent to each other. The lid body 162 and the lid body 163 are provided so as to block the open ends on both sides of the extrusion molding material 161, respectively. The lid body 162 and the lid body 163 are joined to the extrusion molding material 161 by brazing. The inversion space portion 156 is formed in a space surrounded by the extrusion molding material 161, the lid body 162, and the lid body 163.

  In the present embodiment, the inversion space portion 156 is formed between the porous ridge portion 151 (151A) and the porous ridge portion 151 (151B) that are adjacent to each other in the flow direction of the A / C refrigerant. Is a reciprocating (U-turn) flow. Thereby, in the reversal space 156, the A / C refrigerant having a temperature difference can be stirred while the flow direction of the A / C refrigerant is reversed, or the bubbles in the A / C refrigerant can be discharged. Thereby, since the A / C refrigerant having a more uniform temperature is supplied to the perforated flange 151 in a state in which bubbles are not included, it is possible to suppress variation in the cooling efficiency of the EV device 31.

  In the present embodiment, a refrigerant arrangement space 181 in which a refrigerant having a specific heat larger than that of the A / C refrigerant is stored between the inverter element 110 serving as a heat generation source and the refrigerant passage 32 through which the A / C refrigerant flows. Is provided. With such a configuration, the refrigerant stored in the refrigerant arrangement space 181 is caused to function as a heat storage medium that stores heat transferred from the inverter element 110. Thereby, even if the heat generation in the inverter element 110 fluctuates greatly in a short time, boiling (gasification) of the A / C refrigerant like a heat spot can be suppressed. In addition, the refrigeration cycle is characterized in that the system responsiveness is delayed because the A / C refrigerant is accompanied by a change in the state of gas and liquid. However, the influence of such a delay in system responsiveness can be reduced.

  In particular, the parts constituting the EV device 31 have a high heat generation density, and it is assumed that the heat generation amount fluctuates greatly in a short time as described above. Therefore, the heat exchanger having a two-story structure in the present embodiment is used. Applied more effectively.

  Further, in the present embodiment, the heat exchanger having a two-story structure is integrally formed by the extrusion molding material 161. With such a configuration, a flat plate heat exchanger exhibiting high pressure resistance can be realized at low cost.

  FIG. 15 is a front view showing a modification of the cooling unit in FIG. 16 is a rear view showing the cooling unit in FIG. In FIG. 16, the inverter element 110 mounted on the element mounting surface 122 is omitted. FIG. 17 is a cross-sectional view showing the cooling unit along the line XVII-XVII in FIG. 15.

  With reference to FIGS. 15 to 17, in this modification, the refrigerant is circulated in the refrigerant arrangement space 181.

  More specifically, the cooling unit 30 further includes a refrigerant supply pipe 143 provided for the refrigerant arrangement space 181 and a refrigerant discharge pipe (not shown). The refrigerant supply pipe 143 is connected to the refrigerant passage forming member 120 as a refrigerant supply unit for supplying the refrigerant to the refrigerant arrangement space 181. A refrigerant discharge pipe (not shown) is connected to the refrigerant passage forming member 120 as a refrigerant discharge portion for discharging the refrigerant from the refrigerant arrangement space 181.

  In the present embodiment, the positions of the refrigerant supply pipe and the refrigerant discharge pipe provided for the refrigerant arrangement space 181 are vertically changed from the positions of the refrigerant supply pipe and the refrigerant discharge pipe provided for the refrigerant passage 32. Inverted.

  The refrigerant arrangement space 181 includes a plurality of sections including a plurality of linear portions 182 and an inversion space portion 183. The straight portion 182 has a perforated shape aligned in parallel with the refrigerant flow direction. The plurality of straight portions 182 are provided side by side in a direction orthogonal to the flow direction of the refrigerant flowing through each straight portion 182. Each of the plurality of linear portions 182 is provided at a position overlapping with the plurality of porous flange portions 151. The inversion space portion 183 is disposed between the linear portions 182 adjacent to each other in the flow direction of the A / C refrigerant. The inversion space portion 183 is provided so as to invert the flow of the A / C refrigerant between the linear portions 182 arranged on both sides thereof.

  In addition, although the path | route of the refrigerant | coolant flow path formed in the refrigerant | coolant arrangement | positioning space 181 is not restricted to the said structure, the shape shape | molded simultaneously with the porous collar part 151 of the refrigerant path 32 at the time of extrusion molding of the extrusion molding material 161 is preferable.

  The refrigerant circulated in the refrigerant arrangement space 181 is a refrigerant different from the A / C refrigerant circulated in the refrigerant passage 32. The refrigerant circulated in the refrigerant arrangement space 181 has a specific heat larger than the specific heat of the A / C refrigerant circulated in the refrigerant passage 32. For example, LLC (Long Life Coolant) is used as the refrigerant circulated in the medium arrangement space 181.

  According to such a configuration, the heat exchange performance between the refrigerant flowing through the refrigerant arrangement space 181 and the A / C refrigerant flowing through the refrigerant passage 32 is improved, and the responsiveness of the cooling performance in the cooling unit 30 is improved. Can be increased.

  The structure of the electric device cooling apparatus according to Embodiment 2 of the present invention described above will be described together. The electric apparatus cooling device according to the present embodiment is an EV apparatus 31 as an electric apparatus mounted on a vehicle. The cooling device. The cooling device for an electric device has a flat plate shape and includes a refrigerant passage forming member 120 to which an inverter element 110 as a heat source included in the EV device 31 is connected. The refrigerant passage forming member 120 has a refrigerant passage 32 through which a refrigerant for air conditioning of the passenger compartment flows in the plane direction, and a refrigerant arrangement space 181 in which the refrigerant passage 32 is stacked in the thickness direction and in which the refrigerant is arranged. It is formed. The refrigerant passage 32 has a perforated portion 151A as a first perforated portion having a perforated shape arranged in parallel with the refrigerant flow direction, and a perforated shape formed in parallel with the refrigerant flow direction. , The porous ridge portion 151B as the second porous ridge portion separated from the porous ridge portion 151A by the partition wall 127 extending in parallel with the refrigerant flow direction, and the porous ridge portion 151A and the porous ridge portion 151B communicate with each other. And a reversal space 156 that reverses the flow direction of the refrigerant between the perforated portion 151A and the perforated portion 151B.

  According to the cooling device for electric equipment according to Embodiment 2 of the present invention configured as described above, by providing the inversion space portion 156 between the adjacent porous flange portions 151 in the refrigerant passage 32, the A / C The bubbles of the refrigerant can be discharged, or the A / C refrigerant having a temperature difference can be stirred. Even if the cooling efficiency by the A / C refrigerant is locally reduced in the refrigerant passage 32 due to the two-story structure of the refrigerant passage 32 and the refrigerant arrangement space 181, the influence is exerted on the refrigerant arrangement space 181. It can be mitigated by the arranged refrigerant. As a result, the cooling efficiency of the EV device 31 varies depending on the cooling structure using the A / C refrigerant that is easily gasified and has a large specific gravity difference between the gas state and the liquid state. Can be suppressed.

  Note that a new cooling device may be configured by appropriately combining the structure of the cooling device for an electric device described in the first embodiment and the second embodiment. For example, in the cooling unit 30 shown in FIGS. 11 and 13, as shown in FIG. 7, a plurality of porous ridges 151 may be provided along the refrigerant flow direction with the reset space 157 interposed therebetween. .

  In the first and second embodiments, the case where the present invention is applied to the cooling of the EV device 31 mounted on the hybrid vehicle has been described. However, the following is an example of the electric device to be cooled. However, it is not limited to this.

  FIG. 18 is a perspective view showing a battery cooling device mounted on a vehicle. Referring to FIG. 18, a battery 190 is configured by stacking a plurality of battery cells 191 in one direction. On both sides of battery 190, refrigerant passage forming members 120 described in the first and second embodiments are provided.

  The embodiment disclosed this time should be considered as 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 present invention is applied to a vehicle such as a hybrid vehicle or an electric vehicle on which electric devices such as a motor generator and an inverter are mounted.

  10 Vapor compression refrigeration cycle, 12 compressor, 14, 15, 18 heat exchanger, 16 expansion valve, 21, 22, 23, 24, 25, 26, 27, 32, 34, 35, 36, 36a, 36b, 51 Refrigerant passage, 28 Flow control valve, 30 Cooling unit, 31 EV equipment, 40 Gas-liquid separator, 42 Condenser fan, 52 Switching valve, 54 Check valve, 57, 58 Valve, 60 Ground, 90 Duct, 91 Duct inlet , 92 Duct outlet, 93 Fan, 100 Engine, 110 Inverter element, 120 Refrigerant passage forming member, 121, 162, 163 Lid, 122 Element mounting surface, 126 Case body, 127 Partition wall, 131, 161 Extruded molding material, 141 , 143 Refrigerant supply pipe, 142 Refrigerant discharge pipe, 151, 151A, 151B, 151C, 151 , 151X, 151Y, 151p, 151q Porous collar part, 152 holes, 156, 183 Inverted space part, 157 Reset space part, 181 Refrigerant arrangement space, 182 Linear part, 190 Battery, 191 Battery cell, 200 Drive unit, 400 For traveling Battery, 500,600 cable, 1000 vehicle.

Claims (6)

A cooling device for electric equipment mounted on a vehicle,
It has a flat plate shape, and includes a refrigerant passage forming member to which a heat source included in an electric device is connected,
The refrigerant passage forming member is provided with a refrigerant passage through which a refrigerant for air conditioning of the passenger compartment flows in the plane direction, and a refrigerant arrangement space in which the refrigerant passage is arranged in the thickness direction so as to be disposed. ,
The refrigerant passage has a first porous ridge portion having a porous ridge shape arranged in parallel with the refrigerant flow direction, and a porous ridge shape arranged in parallel with the refrigerant flow direction, in the refrigerant flow direction. A second porous flange part separated from the first porous flange part by a partition wall extending in parallel with the first porous flange part, and the first porous flange part and the second porous flange part, and A cooling device for an electric device, comprising: a reversing space portion for reversing the flow direction of the refrigerant between the porous reed portion and the second porous reed portion. The heat generation source is connected to the refrigerant passage forming member such that the refrigerant arrangement space is located between the heat generation source and the refrigerant passage,
The cooling device for an electric device according to claim 1, wherein a refrigerant having a specific heat larger than that of the refrigerant flowing through the refrigerant passage is arranged in the refrigerant arrangement space.   The cooling device for an electric device according to claim 1, wherein a refrigerant different from the refrigerant flowing through the refrigerant passage is stored in the refrigerant arrangement space.   The cooling device for an electric device according to claim 1, wherein a refrigerant different from the refrigerant flowing through the refrigerant passage is circulated in the refrigerant arrangement space.   5. The cooling device for an electric device according to claim 1, wherein the first porous ridge part has a porous ridge shape different from the porous ridge shape of the second porous ridge part. 6.   The cooling of an electric device according to any one of claims 1 to 5, wherein the refrigerant passage forming member has an extrusion molding material for forming the first porous ridge portion and the second porous ridge portion. apparatus.

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