JP2013250035A - Heat siphon-type refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration cycle device capable of switching between a refrigeration cycle mode operation and a heat siphon mode operation.SOLUTION: A refrigeration cycle device includes: a condenser (11) installed vertically above an evaporator (13); a bypass passage (19) disposed to connect an inlet of the condenser (11) and an outlet of the evaporator (13) by bypassing a compressor (10); and a check valve (18) composed of a valving element (18-1), a valve seat (18-2) and a spring (18-3), disposed in the bypass passage (19). The check valve (18) is configured to be closed by a differential pressure (ΔP) between front and rear sides of the check valve (18) while the compressor (10) is operated, and to be opened while the compressor (10) is stopped.

Description

  The present invention relates to a heat siphon refrigeration cycle apparatus. The present invention is particularly applied to an air conditioner for an electric vehicle such as an electric vehicle or a hybrid vehicle, and a heating / cooling device for automobile components such as a battery, a motor, and an inverter.

  In an electric vehicle such as an electric vehicle or a hybrid vehicle, electric energy stored in a power storage device such as a secondary battery is supplied to a motor via an inverter or the like to run. These electronic devices such as batteries, inverters, and motors generate heat when they are in use, such as when they are traveling, and not only do not have sufficient functions at high temperatures, but also cause deterioration and damage to the devices. A cooling means for maintaining the temperature is required. On the other hand, especially in the case of batteries, the input / output characteristics deteriorate not only at high temperatures but also at low temperatures such as in winter, resulting in problems such as inability to obtain sufficient power for driving, and inability to charge and regenerate. . For this reason, in order to draw out sufficient performance, not only cooling but also heating means are required. Therefore, it is important to control the battery temperature within a certain optimum temperature range.

  As a general temperature adjusting means, there is a method of cooling and heating using a refrigeration cycle (including a heat pump). However, when adjusting the temperature of the battery pack, it is necessary to always operate the compressor, and the power consumption of the compressor is generated. For this reason, there has been a problem that the EV travel distance becomes short, or conversely, it is necessary to increase the number of cells in order to secure the travel distance, and the cost increases. (Hereinafter, temperature adjustment is also referred to as temperature control.)

  Patent Document 1 discloses a technology in which a natural liquefaction heat radiation mode is added to a refrigeration cycle in order to reduce power consumption and improve the life of a compressor by not operating the compressor at a low outdoor temperature in a cooling system for building equipment. It is disclosed. This conventional technique switches the operation mode when the temperature difference between the outside air temperature and the object to be cooled is 5 ° C. or more, and a temperature sensing sensor, control ECU, solenoid valve, etc. are necessary for the switching. Thus, there is a problem that the circuit configuration and control become complicated. In particular, when a general solenoid valve is used, there are problems such as power consumption for operating the valve and complicated control of the valve, which may contradict the reduction of power consumption, which is the original purpose. It was.

JP 2000-356421 A

  In view of the above problems, the present invention provides a heat siphon type refrigeration cycle apparatus capable of switching between a refrigeration cycle mode and a heat siphon mode operation by a valve that does not require electric power or a control signal.

  In order to solve the above problems, the invention of claim 1 is directed to a refrigeration cycle apparatus having a refrigerant circuit including a compressor (10), a condenser (11), an expansion valve (12), and an evaporator (13). (11) is installed vertically above the evaporator (13), and in the refrigerant circuit, between the inlet of the condenser (11) and the outlet of the evaporator (13), the compressor (10) A bypass passage (19) for bypassing and connecting is provided, and the bypass passage (19) includes a valve body (18-1), a valve seat (18-2), and a spring (18-3). A check valve (18) is provided, and the check valve (18) is closed by the differential pressure (ΔP) before and after the check valve (18) when the compressor (10) is operated. The time of stopping the presser (10) is a refrigeration cycle apparatus that is open.

  In addition, the code | symbol attached | subjected above is an example which shows a corresponding relationship with the specific embodiment as described in embodiment mentioned later.

1 is a schematic diagram of a first embodiment of the present invention. It is explanatory drawing of the refrigerating cycle operation mode (battery pack cooling mode) and heat siphon operation mode in 1st Embodiment of this invention. It is explanatory drawing of the refrigerating cycle operation mode (battery pack heating mode) in 1st Embodiment of this invention. It is the schematic of 2nd Embodiment of this invention. It is the schematic of the valve used for 2nd Embodiment of this invention. It is other schematic of the valve used for 2nd Embodiment of this invention. It is the schematic of 3rd Embodiment of this invention.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. About each embodiment, the same code | symbol is attached | subjected to the part of the same structure, and the description is abbreviate | omitted. The heat siphon type refrigeration cycle apparatus according to the present invention is used in, for example, an automobile using an internal combustion engine as a driving source for traveling, a hybrid automobile, an electric vehicle using a motor as a driving source. In this case, the temperature adjustment target is a space, a device, or the like provided in the vehicle and capable of blowing temperature-controlled air whose temperature is adjusted. For example, the present invention can be applied to vehicle interiors, battery packs, electric devices such as inverters and motors, intercoolers that adjust the temperature of supercharged air, heat exchangers that adjust the temperature of oil such as engines and ATF, and the like. Of course, the refrigeration cycle apparatus of the present invention is not necessarily limited to vehicles, and can be widely applied to a temperature adjustment apparatus that requires an energy saving effect.

(First embodiment)
The first embodiment, which is an embodiment of the present invention, can be applied to an air conditioner for an electric vehicle such as an electric vehicle or a hybrid vehicle, or a heating / cooling device for an automobile component such as a battery, a motor, or an inverter. Of these, the temperature adjusting device 1 of the battery pack 8 will be described below as an example. First, the operating principle of the heat siphon refrigeration cycle apparatus according to the present invention will be briefly described with reference to FIGS. Here, it is important that the capacitor 11 is disposed vertically above the evaporator 13. The two do not necessarily have to be arranged in a line in the vertical direction.

  In FIG. 1, a solid arrow A indicates the flow direction of the refrigerant when the normal refrigeration cycle mode operates. On the other hand, a dotted arrow B indicates the flow direction of the refrigerant when the heat siphon mode is activated. In the refrigeration cycle mode, the refrigerant circuit is configured by connecting at least the compressor 10, the condenser 11, the electric expansion valve 12, and the evaporator 13 in a ring shape. In the refrigeration cycle mode, the air switching doors 3 to 6 of the temperature adjusting device 1 can be opened and closed to cool and heat the battery pack (details will be described later).

  Next, the heat siphon mode will be schematically described with reference to FIGS. In FIG. 2, the air discharged from the battery pack 8 passes through the evaporator 13 and is blown to the battery pack 8 by the blower 2. Outside air (vehicle traveling wind) is introduced into the condenser 11 from the outside air intake passage 16, and the air switching doors 3 to 6 are switched so as to be discharged out of the outdoor discharge passage 17. Here, in FIG. 1, the compressor 10 is turned off and the electric expansion valve 12 is opened. Since the evaporator 13 is disposed below, the liquid refrigerant in the refrigeration cycle accumulates in the evaporator 13. When the high-temperature air discharged from the battery pack 8 passes through the evaporator 13, the liquid refrigerant evaporates, and the cooled air is supplied to the battery pack 8.

  In the open / closed state of the air switching doors 3 and 4 (5 and 6) in FIG. 2, the gas refrigerant evaporated by the high-temperature air discharged from the battery pack 8 is supplied to the capacitor 11 via the bypass passage 19 in FIG. Then, it is cooled by the vehicle traveling wind from the outside air intake passage 16. The liquid refrigerant condensed in the condenser 11 is supplied again to the evaporator 13 by natural fall due to its own weight (at this time, the electric expansion valve 12 is opened). That is, since the condenser 11 is a gas refrigerant condensing part and the evaporator 13 is a liquid refrigerant evaporating part, the pressure of the gas refrigerant is high on the evaporator 13 side and low on the condenser 11 side. Accordingly, a pressure gradient of the gas refrigerant is generated in the bypass passage 19, whereby the gas refrigerant moves from the evaporator 13 to the capacitor 11. The necessary cooling capacity in the heat siphon mode is adjusted by the opening degree of the electric expansion valve 12. Thus, without driving the compressor 10, the battery can be cooled by circulating the refrigerant on the same principle as that of the heat pipe.

  In this embodiment, as shown in the enlarged view of FIG. 1, a special check valve 18 that is normally open is used. Since the pressure difference in the heat siphon mode is very small (10 kPa or less) and there is no pressure difference enough to push open a general check valve, a known general check valve cannot be used. The check valve 18 is released from the valve seat 18-2 when there is no differential pressure ΔP between the condenser 11 inlet side and the evaporator 13 outlet side (referred to as front and rear). ing. That is, the spring pressure of the spring 18-3 is set so as to be released from the valve seat 18-2 in a state where there is no differential pressure ΔP. When the condenser 11 inlet side becomes higher than the evaporator 13 outlet side (differential pressure ΔP is generated before and after the check valve 18), the valve body 18-1 comes into contact with the valve seat 18-2, and the bypass circuit 19 automatically Closed. For this reason, when the compressor 10 is turned on, the check valve 18 functions as a normal check valve. The spring 18-3 is not limited to the helical spring, but may be another elastic body (including a pneumatic spring).

  Briefly explaining the peculiarity of this valve, in a general check valve, the spring pressure is large and the valve element 18-1 contacts the upper end surface 18-4 in the enlarged view of FIG. In the check valve 18 that is normally open, the valve body 18-1 is not in contact with the upper end surface 18-4 and is free from the valve seat 18-2 in a state where there is no differential pressure ΔP. . In the enlarged view of FIG. 1, the check valve 18 is displayed in the vertical direction, but can be installed in any direction by adjusting the spring pressure.

  The valve structure of the present embodiment is in an open state when there is no differential pressure ΔP. Therefore, when the compressor is not operating (OFF), a thermosiphon is always available. For this reason, when the battery temperature is higher than the outside air, the battery can be automatically cooled in the heat siphon mode, so that control for switching between the refrigeration cycle mode and the heat siphon mode is not required.

  Furthermore, the first embodiment of the present invention will be described in detail with reference to FIG. In FIG. 2, the air flow when the mode for cooling the battery pack 8 is performed is indicated by arrows. The secondary battery constituting the battery pack 8 is chargeable / dischargeable, and is used for supplying electric power to a vehicle driving motor or the like. Each unit cell is, for example, a nickel metal hydride secondary battery, a lithium ion secondary battery, or an organic radical battery. For example, the unit cell is housed in a casing, and is located below the floor of the automobile, under the seat, between the rear seat, and the trunk room. And the space between the driver seat and the passenger seat.

  The temperature adjusting device 1 blows a battery pack 8 composed of a plurality of single cells connected to be energized and air (hereinafter also referred to as “temperature-controlled air”) adjusted in temperature for the plurality of single cells. The air blower 2, the condenser 11 and the evaporator 13 for adjusting the temperature of the air, the air switching doors 3, 4, 5, 6 for changing the air passage through which the temperature-controlled air flows according to the operation mode, and the operation of each part. A control device 9 (not shown) for controlling is provided. In the battery pack 8, cooling and heating are controlled by electronic parts used for charging, discharging, and temperature adjustment of a plurality of unit cells, and the temperature of each unit cell is adjusted by air flowing around.

  The refrigeration cycle is a refrigerant circuit configured by connecting at least the compressor 10, the condenser 11, the expansion valve 12, and the evaporator 13 in an annular shape. In the present embodiment, the compressor 10 is a scroll compressor that is driven by an electric motor 101 and has a compression mechanism 110 composed of a turning scroll and a fixed scroll. However, the present invention is not limited to this. A compressor of the form Further, instead of driving by the electric motor 101, a belt transmission type may be used. The condenser 11 is a component included in the refrigeration cycle, and is an example of a heat exchanger for heating that generates temperature-controlled air by heating the air blown to the battery pack 8. The condenser 11 is a heat exchanger that heats the passing air by the action of the refrigerant compressed by the compressor 10 in the refrigeration cycle radiating heat to the air passing through the heat exchanging portion 11a in the heating mode.

  The heat exchanging portion 11a of the capacitor 11 includes tubes and outer fins that are alternately arranged, and these are laminated and integrated. The refrigerant flows through the tubes, and the heated air passes through the outer fins existing between the tubes in a direction orthogonal to the refrigerant flow direction. One end of the plurality of tubes is connected to the upper tank 11b, and the other end is connected to the lower tank 11c. The upper tank 11b and the lower tank 11c communicate with each other through the inside of a plurality of tubes. That is, the refrigerant flowing into the lower tank 11c can flow into the upper tank 11b through the inside of the tube.

  Similarly, the heat exchanging portion 13a of the evaporator 13 includes alternately arranged tubes and outer fins, and these are laminated and integrated. One end of the plurality of tubes is connected to the upper tank 13b, and the other end is connected to the lower tank 13c. The upper tank 13b and the lower tank 13c communicate with each other through the inside of the plurality of tubes. That is, the refrigerant that has flowed into the lower tank 13c can flow into the upper tank 13b through the inside of the tube.

  As shown in FIG. 1, the evaporator 13 is disposed at a position lower than the capacitor 11. That is, the capacitor 11 is located higher than the evaporator 13 in a state where it is installed in the vehicle. Further, the outlet portion of the condenser 11 from which the refrigerant flows out to the evaporator 13 is provided in the lower tank 11c, and is connected to the expansion valve 12 through a refrigerant pipe. In order for the capacitor 11 and the evaporator 13 to function as the heat siphon mode, the outlet portion of the capacitor 11 is preferably disposed at the lower portion of the capacitor 11. The expansion valve 12 is connected to the upper tank 13b of the evaporator 13 through a refrigerant pipe. The refrigeration cycle of the present embodiment includes a bypass passage 19 that connects the evaporator 13 and the condenser 11 so that the compressor 10 can be bypassed, and the check valve 18 described above.

  The portion of the capacitor 11 connected to the discharge pipe 103 of the compressor 10 is not limited to the upper tank 11b, and the height position may be arbitrarily set. Further, the portion of the evaporator 13 connected to the suction pipe 102 of the compressor 10 is not limited to the upper tank 13b, and the height position thereof may be arbitrarily set. The portion of the evaporator 13 connected to the outlet portion of the expansion valve 12 is not limited to the lower tank 13c, and the height position thereof may be arbitrarily set. For example, you may provide in the upper tank 13c.

  As shown in FIG. 2, the temperature adjusting device 1 includes a battery passage of the battery pack 8, a heat exchanger upstream passage 14, a heat exchanger downstream passage 15, an outside air intake passage 16 communicating with the outside of the vehicle compartment, And an outdoor discharge passage 17 that leads to the air passage, and these air passages are formed inside the duct. The electric fan 7 is disposed at a position where a forced flow of the outside air from the outside air intake passage 16 to the outdoor discharge passage 17 can be created. The blower 2 is disposed between the air flow downstream side of the heat exchanger downstream side passage 15 and the air flow upstream side of the battery passage, and creates an air flow from the heat exchanger downstream side passage 15 to the battery passage. The battery pack 8 is provided with a battery temperature sensor 21 that detects the temperature of the unit cell. The battery temperature sensor 21 is an example of a device temperature detection unit that detects the temperature to be adjusted.

  The heat exchanger upstream side passage 14 is a passage located upstream of the air flow with respect to the condenser 11 and the evaporator 13, and two passages leading from the heat exchanger upstream side passage 14 to the respective inlet portions of the condenser 11 and the evaporator 13. Branch into the passage. The heat exchanger downstream passage 15 is a passage located downstream of the air flow with respect to the condenser 11 and the evaporator 13, and the two passages extending from the respective outlet portions of the condenser 11 and the evaporator 13 are the heat exchanger downstream passages. Merge to 15. The outside air intake passage 16 is a passage located upstream of the air flow with respect to the condenser 11 and the evaporator 13. The outdoor discharge passage 17 is a passage located downstream of the air flow with respect to the condenser 11 and the evaporator 13.

  The air switching doors 3 to 6 are air path switching means for switching the air path through which the temperature-controlled air flows according to the operation mode. The door 3 is located downstream of the heat exchanger upstream passage 14 and upstream of the condenser 11 so that the inlet of the condenser 11 communicates with either the heat exchanger upstream passage 14 or the outside air intake passage 16. It is an air path switching means set to the opening position switched to. The door 4 is located downstream of the condenser 11 and upstream of the heat exchanger downstream passage 15, and has an opening degree for switching the outlet of the condenser 11 to either the heat exchanger downstream passage 15 or the outdoor discharge passage 17. Air path switching means set at the position.

  As shown in FIG. 3, the positions of the door 3 and the door 4 are such that, during the heating operation for heating the battery pack 8, the air passage through which the temperature-controlled air passes through the heat exchange part 11 a of the capacitor 11 and the battery passage of the battery pack 8 It is set to form a circulating air path. The door 5 is located downstream of the heat exchanger upstream passage 14 and upstream of the evaporator 13 so that the inlet portion of the evaporator 13 communicates with either the heat exchanger upstream passage 14 or the outside air intake passage 16. It is an air path switching means set to the position switched to. The door 6 is located on the downstream side of the evaporator 13 and on the upstream side of the heat exchanger downstream side passage 15, and is positioned to switch the outlet portion of the evaporator 13 to either the heat exchanger downstream side passage 15 or the outdoor discharge passage 17. Air path switching means to be set. As shown in FIG. 2, the opening positions of the door 5 and the door 6 are the air passage through which the temperature-controlled air passes through the heat exchanging portion 13 a of the evaporator 13 and the battery of the battery pack 8 during the cooling operation for cooling the battery pack 8. It is set to form an air path that circulates through the passage.

Next, the operation mode of this embodiment will be described.
(Refrigeration cycle operation mode)
By operating the compressor 10, the high-temperature and high-pressure gas refrigerant is sent to the condenser 11, and the refrigerant is liquefied by being cooled by the outside air in the condenser 11. This liquid refrigerant is decompressed by the expansion valve 12, and the cooled refrigerant is sent to the evaporator 13 to exchange heat with air to produce cooling air. The expansion valve 12 is controlled such that the degree of heating (SH) at the outlet of the evaporator 13 becomes an appropriate value (about 10 ° C.). At this time, since the check valve 18 installed in the bypass circuit 19 of the compressor 10 is shut by the high / low pressure difference (differential pressure ΔP) of the refrigeration cycle, the refrigerant does not flow.

When the air switching doors 3 to 6 are set as shown in FIG. 2, the cooling mode is set. Moreover, when the air switching doors 3 to 6 are set as shown in FIG. 3, the heating mode is set. The cooling mode is activated when the battery temperature is 40 ° C. or higher, as shown in the table of FIG. 2 as an example.
On the other hand, the heating mode is performed when the battery temperature detected by the battery temperature sensor 21 is lower than a predetermined temperature in winter or the like, and is a mode that exhibits a large heating capacity. This predetermined temperature is set to a low temperature at which the original charge / discharge capacity cannot be exhibited when the battery temperature becomes lower than that. As the predetermined temperature, for example, 10 ° C. can be adopted. When control device 9 determines that the detected battery temperature is less than 10 ° C., it determines that the battery is in a state that requires immediate warm-up, and executes the heating mode. This heating mode is continued until the detected battery temperature reaches 10 ° C. or higher. When it is determined that the battery temperature is 10 ° C. or higher, the heating mode ends.

(Heat siphon operation mode)
When the compressor 10 is stopped, the high and low differential pressure before and after the compressor, that is, the differential pressure ΔP before and after the check valve 18 disappears, so that the check valve 18 is opened by a spring.
(1) When outside air temperature <battery temperature By operating the blower 2 in FIG. 2, since the outside air temperature <battery temperature, the liquid refrigerant accumulated in the evaporator 13 on the lower side is heated and gasified. The gasified refrigerant is liquefied by being cooled by outside air in the condenser 11 and supplied to the evaporator 13 by gravity. The refrigerant circulation (heat siphon operation) described above enables the battery to be cooled even when the compressor is not operated.
(2) When outside air temperature ≧ battery temperature The refrigerant pressure in the cycle is a saturation pressure determined by the battery temperature. For this reason, the refrigerant in the refrigeration cycle is not liquefied by gas → liquefaction due to the heat of the outside air. Therefore, since there is no refrigerant circulation (heat siphon) in the refrigeration cycle, battery cooling is not performed.
If an example of the operation mode of battery cooling is given, since generally the operating temperature range of Li battery is said to be the range of 0-40 degreeC, an example of an operation mode is shown in the table below FIG.

(Second Embodiment)
The second embodiment is an embodiment in which the bypass circuit 19 is installed inside the compressor 10. FIG. 4 shows an example of an electric compressor. The suction refrigerant enters the electric motor chamber from the suction pipe 102, is sucked into the compression mechanism portion 110 of the compressor 10, and is discharged from the reed valve 108 through the discharge port 107. The refrigerant discharged from the reed valve 108 is separated from oil by a well-known centrifugal oil separator (not shown), the gas refrigerant passes to the condenser 11, and the oil passes through the oil return hole 109 and the oil is taken into the suction side (electric motor). To the room).

  In the second embodiment, a bypass circuit 19 is installed inside the compressor 10, but the bypass circuit 19 is provided in the path of the oil return hole 109 as a path connecting the high pressure side and the low pressure side. And this oil return hole part is functioned as the non-return valve 18 of this embodiment. In this case, a small hole diameter 18-5 for returning only the oil separated by the oil separator is required in the refrigeration cycle operation mode, and a gap through which the gas refrigerant can pass is required in the heat surfone operation mode. Therefore, the check valve 18 in this case needs to have a structure that does not completely shut down during the refrigeration cycle operation. As an example of the means for this purpose, (1) a small hole 18-5 is added to the check valve 18 body (FIG. 5), (2) the seat surface 18-2 of the check valve 18 or the valve body 18-1. It is preferable to add a convex portion 18-6 (FIG. 6) to the seat surface side so that a gap for returning only the oil is intentionally opened at the time of closing.

  According to this embodiment, it is not necessary to newly set the bypass circuit 19 that bypasses the compressor 10 as the refrigerant pipe (improvement of mounting by integration). Further, when the compressor 10 is cooled, liquid refrigerant accumulates inside the compressor 10, and the refrigerant necessary for the heat siphon operation mode may be insufficient. By adding the bypass circuit 19 in the compressor, the refrigerant path is almost the same as that in the refrigeration cycle mode operation, so that excess refrigerant is reduced. For this reason, it is not necessary to consider the fluctuation of the refrigerant amount, and the modulator that stores the excess refrigerant can be downsized.

(Third embodiment)
As shown in FIG. 7, the third embodiment is an embodiment in which a bypass circuit 19 is additionally installed in the joint portion of the suction pipe 102 and the discharge pipe 103 of the compressor. Since there are many cases where a sub-block for changing the pipe take-out direction is added, a bypass circuit 19 is installed inside such a sub-block 120 and a check valve 18 is added. In this case, in order to prevent liquid refrigerant from accumulating in the compressor, the joint portions of the suction pipe 102 and the discharge pipe 103 of the compressor 10 are arranged close to each other on the lower side. In this way, it is not necessary to newly set the bypass circuit 19 that bypasses the compressor 10 as the refrigerant pipe, and the mountability can be improved. Further, an existing compressor can be used in the present invention only by installing the sub-block 120 without changing specifications of the compressor 10 newly.

DESCRIPTION OF SYMBOLS 10 Compressor 11 Condenser 12 Expansion valve 13 Evaporator 18 Check valve 19 Bypass passage

Claims (7)

In a refrigeration cycle apparatus having a refrigerant circuit including a compressor (10), a condenser (11), an expansion valve (12), and an evaporator (13),
The capacitor (11) is installed vertically above the evaporator (13), and
In the refrigerant circuit, a bypass passage (19) for bypassing and connecting the compressor (10) is provided between the inlet of the condenser (11) and the outlet of the evaporator (13).
The bypass passage (19) is provided with a check valve (18) including a valve body (18-1), a valve seat (18-2), and a spring (18-3). 18) is a refrigeration cycle apparatus that is closed by a differential pressure (ΔP) before and after the check valve (18) when the compressor (10) is operated, and opened when the compressor (10) is stopped.   The refrigeration cycle apparatus according to claim 1, wherein the check valve (18) is configured to close at a differential pressure (ΔP) of 10 to 100 kPa.   The refrigeration cycle apparatus according to claim 1 or 2, wherein the check valve (18) is provided integrally with the compressor (10).   The refrigeration cycle apparatus according to claim 3, wherein the check valve (18) is provided in an oil return hole (109) path in the compressor (10).   The check valve (18) is provided in a sub-block (120) connected to a joint portion of a suction pipe (102) and a discharge pipe (103) of the compressor (10). The refrigeration cycle apparatus according to 1 or 2.   The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the check valve (18) is a normally open type electromagnetic valve.   The refrigeration cycle apparatus according to any one of claims 1 to 6, wherein the refrigeration cycle apparatus is applied to an air conditioner for an electric vehicle or a heating or cooling device for automobile components.

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