JP2018179331A - Gas-liquid separator and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas-liquid separator which can properly separate refrigeration machine oil from a liquid phase refrigerant, when separating gas and liquid of a refrigerant whose specific gravity in a gas phase is larger than specific gravity of the refrigeration machine oil.SOLUTION: A gas-liquid separator includes: a body part 140 formed by a tubular member for forming a refrigerant passage whose passage cross sectional area is constant; and a case part 145 for housing a part of the body part 140. A gas phase refrigerant outlet 14c is formed at an end part at a lower side of the body part 140, a plurality of communication holes 141a are formed at a spiral-like part 141 of the body part 140, and a liquid storage space 145a for storing a liquid phase refrigerant which has flowed out from the communication holes 141a and a liquid phase refrigerant outlet 14b for allowing the liquid phase refrigerant stored in the liquid storage space 145a to flow out are formed at the case part 145. Furthermore, by setting the total opening area of the communication holes 141a arranged at a refrigerant flow upstream side larger than the total opening area of the communication holes 141a arranged at a refrigerant flow downstream side, flowing out of the gas phase refrigerant and refrigerant machine oil into the liquid storage space 145a can be suppressed.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a gas-liquid separator that separates gas and liquid of refrigerant, and a refrigeration cycle apparatus including the same.

  BACKGROUND ART Conventionally, Patent Document 1 discloses a gas-liquid separator applied to an ejector-type refrigeration cycle which is a vapor compression refrigeration cycle apparatus including an ejector. In the ejector-type refrigeration cycle, the gas-liquid separator of Patent Document 1 separates the gas-liquid of the refrigerant that has flowed out of the ejector, and causes the separated liquid-phase refrigerant to flow out to the inlet side of the evaporator. The refrigerant flows out to the suction side of the compressor.

  Furthermore, the gas-liquid separator of Patent Document 1 includes an oil separation unit in addition to the refrigerant gas-liquid separation unit that separates the gas-liquid of the refrigerant that has flowed out of the ejector. The oil separation unit is a part that separates the refrigerator oil for lubricating the compressor from the liquid phase refrigerant separated by the refrigerant gas-liquid separation unit. Moreover, in patent document 1, it is trying to achieve size reduction as the whole gas-liquid separator by forming a refrigerant | coolant gas-liquid separation part and an oil separation part by the double pipe | tube curved in helical shape.

  More specifically, in a portion of the double pipe in which the refrigerant gas-liquid separation portion is formed, a plurality of communication holes communicating the inside and the outside of the inner pipe are formed on the outer peripheral side of the central axis of the spiral of the inner pipe. Then, the gas-liquid of the refrigerant flowing in the inner pipe is separated by the action of the centrifugal force, and the separated liquid-phase refrigerant is formed by the space between the inner pipe and the outer pipe through the plurality of communication holes together with the refrigeration oil. Spilled to the oil separation section side.

  Moreover, in the part which forms an oil separation part among double pipes, refrigeration oil is isolate | separated from liquid phase refrigerant | coolant by the effect | action of gravity. Then, the liquid phase refrigerant is made to flow out to the inlet side of the evaporator from the liquid phase refrigerant outlet provided in the outer pipe. Furthermore, with regard to the vapor phase refrigerant separated in the refrigerant gas-liquid separation unit, the refrigerant flow from the gas phase refrigerant outlet provided on the refrigerant flow most downstream side of the inner pipe together with the refrigeration oil separated in the oil separation unit It is made to flow out to the suction side.

Unexamined-Japanese-Patent No. 2007-322001

Incidentally, in the refrigerant cycle of patent document 1, as a refrigerant, the specific gravity when that is the liquid phase is adopted carbon dioxide (CO ₂₎ less than the specific gravity of refrigerating machine oil. For this reason, in the oil separation part of patent document 1, refrigerating machine oil is stored in the downward side of the space between an inner side pipe | tube and an outer side pipe | tube. Then, an oil return hole for returning the refrigeration oil to the gas phase refrigerant side is formed in the lowermost portion of the inner pipe forming the oil separation portion.

  Therefore, when the gas-liquid separator of Patent Document 1 is applied to a refrigeration cycle apparatus that circulates a refrigerant whose specific gravity in the liquid phase is larger than that of the refrigeration oil, the refrigeration oil separated in the oil separation unit Can not be returned to the suction side of the compressor, which may adversely affect the service life of the compressor.

  The present invention, in view of the above points, is capable of appropriately separating refrigerator oil from liquid phase refrigerant when separating gas and liquid of refrigerant whose specific gravity in liquid phase is larger than that of refrigerator oil. It aims to provide a separator.

  Further, the present invention provides a gas-liquid separator capable of appropriately separating refrigerator oil from liquid-phase refrigerant when separating gas-liquid of refrigerant having a specific gravity in liquid phase larger than that of refrigerator oil. Another object of the present invention is to provide a refrigeration cycle apparatus having the same.

The present invention has been made to achieve the above object, and the invention according to claim 1 is a refrigeration cycle in which a refrigerant having a specific gravity in the liquid phase larger than that of the refrigerator oil is circulated. A gas-liquid separator that is applied to the device (10) to separate refrigerant gas and liquid,
A main body (140) forming a refrigerant passage having a constant passage cross-sectional area, and a case (145) accommodating at least a part of the main body,
The main body portion is formed of a tubular member having a spirally curved helical portion (141) and separates the gas and liquid of the refrigerant flowing through the refrigerant passage by the action of the centrifugal force, and the refrigerant flow of the main body portion The most downstream portion is provided with a gas phase refrigerant outlet (14c) for discharging the separated gas phase refrigerant, and on the outer peripheral side of the central axis of the spiral of the main body portion, a plurality of communication for communicating the inside and outside of the main body portion A hole (141a) is formed, and a liquid storage space (145a) for storing liquid-phase refrigerant flowing out of the communication hole is formed in the inside of the case part, and the case part is stored in the liquid storage space A liquid-phase refrigerant outlet (14b) for letting out the liquid-phase refrigerant,
The total opening area of the communication holes opened on the refrigerant flow upstream side of the middle part of the range in which the communication holes are formed in the main body part is greater than the total opening area of the communication holes opened on the refrigerant flow downstream side of the intermediate part It is a growing gas-liquid separator.

  According to this, since the specific gravity of the liquid phase refrigerant is larger than the specific gravity of the refrigeration oil, the refrigerant flowing through the refrigerant passage of the spiral portion (141) has the liquid phase refrigerant on the central axis outer peripheral side of the spiral by the action of centrifugal force. Are easy to distribute. Therefore, the liquid-phase refrigerant separated in the main body (140) can be made to flow over the communication hole (141a) to the liquid storage space (145a) by prioritizing the refrigeration oil and the gas-phase refrigerant.

  At this time, the total opening area of the communication holes (141a) opening on the refrigerant flow upstream side of the middle part is larger than the total opening area of the communication holes (141a) opening on the refrigerant flow downstream side of the middle part Accordingly, the gas phase refrigerant and the refrigerating machine oil can be effectively prevented from flowing out to the liquid storage space (145a) through the communication hole (141a).

  More specifically, a refrigerant having a relatively low dryness flows on the upstream side of the middle portion of the refrigerant passage in the range in which the communication hole (141a) of the main body portion (140) is formed. For this reason, the amount of liquid-phase refrigerant distributed on the outer peripheral side of the central axis of the spiral also increases.

  Therefore, even if the total opening area of the communication holes (141a) opened to the refrigerant flow upstream side of the intermediate portion is set relatively large, the gas phase refrigerant and the refrigerator oil are not discharged from the communication holes (141a) And the liquid phase refrigerant can flow out.

  Furthermore, since the liquid-phase refrigerant flows out from the upstream communication hole (141a) on the downstream side of the middle portion of the refrigerant passage in the range in which the communication hole (141a) of the main body (140) is formed, A relatively dry refrigerant flows. For this reason, the amount of liquid-phase refrigerant distributed on the outer peripheral side of the central axis of the spiral also decreases.

  Therefore, by setting the total opening area of the communication holes (141a) opened to the refrigerant flow downstream side of the intermediate portion relatively small, the gas phase refrigerant and the refrigerator oil are caused to flow out from the communication holes (141a) Can be suppressed.

  As a result, the liquid phase refrigerant stored in the liquid storage space (145a) can be made to flow out from the liquid phase refrigerant outlet (14b). Furthermore, the gas phase refrigerant and the refrigerator oil that did not flow out to the liquid storage space (145a) side can flow out from the gas phase refrigerant outlet (14c).

  That is, according to the first aspect of the present invention, the refrigerant oil is properly separated from the liquid phase refrigerant when separating the gas-liquid of the refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil. A possible gas-liquid separator can be provided.

According to the seventh aspect of the present invention, there is provided a compressor (11) for sucking and compressing a refrigerant mixed with refrigerating machine oil, a radiator (12) for radiating the refrigerant discharged from the compressor, and a radiator The refrigerant is drawn from the refrigerant suction port (13c) by the suction action of the jetted refrigerant injected from the nozzle portion (13a) that decompresses the refrigerant flowing out from (12), and the jetted refrigerant and the suctioned refrigerant drawn from the refrigerant suction port And a gas-liquid separator (14) for separating the gas and liquid of the refrigerant flowing out of the ejector and for discharging the separated gas phase refrigerant to the suction side of the compressor; An evaporator (15) for evaporating the liquid-phase refrigerant separated by the separator and flowing it out to the refrigerant suction port side;
As the refrigerant, a refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil is adopted,
The gas-liquid separator has a main body (140) forming a refrigerant passage having a constant passage cross-sectional area, and a case (145) accommodating at least a part of the main body, the main body curving in a spiral shape It is formed of a tubular member having a spiral portion (141) to separate the gas and liquid of the refrigerant flowing through the refrigerant passage by the action of centrifugal force, and is separated at the most downstream portion of the refrigerant flow in the refrigerant passage. A gas phase refrigerant outlet (14c) is provided to allow the gas phase refrigerant to flow out, and a plurality of communication holes (141a) communicating the inside and the outside of the body portion are formed on the outer peripheral side of the central axis of the spiral of the body portion. A liquid storage space (145a) for storing the liquid phase refrigerant flowing out of the communication hole is formed inside the case part, and the liquid in the case part allows the liquid phase refrigerant stored in the liquid storage space to flow out. Phase refrigerant outlet (14b) is provided The total opening area of the communication holes opened on the refrigerant flow upstream side of the middle portion of the range in which the communication holes are provided is larger than the total opening area of the communication holes opened on the refrigerant flow downstream side of the middle portion Refrigeration cycle device.

  According to this, similar to the invention described in claim 1, when the gas-liquid separator (14) separates the gas-liquid of the refrigerant, the refrigerator oil can be properly separated from the liquid-phase refrigerant.

  That is, according to the invention as set forth in claim 7, when separating the gas and liquid of the refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil, the refrigerator oil is properly separated from the liquid phase refrigerant It is possible to provide a refrigeration cycle apparatus equipped with a possible gas-liquid separator. Then, protection of the compressor (11) can be achieved by returning the separated refrigeration oil together with the gas phase refrigerant to the suction side of the compressor (11).

  Furthermore, in the refrigeration cycle apparatus (10) of a cycle configuration that causes the ejector (13) to suck the refrigerant flowing out of the evaporator (15), the suction capacity of the ejector (13) tends to decrease during low load operation and the like. Therefore, in this type of refrigeration cycle apparatus (10), the ability to properly separate refrigeration oil from liquid phase refrigerant in the gas-liquid separator (14) means that refrigeration oil is stagnated in the evaporator (15) Is extremely effective in that it can

  Here, as a range in which the communication hole (141a) is provided in the main body (140) recited in the claims, the communication hole (141a) disposed on the most upstream side of the refrigerant flow in the main body (140) ) To the communication hole (141a) disposed on the most downstream side of the refrigerant flow.

  In addition, the liquid phase refrigerant outlet (14b) described in the claims is not limited to the refrigerant outlet that allows only the liquid phase refrigerant to flow out, and it has a relatively low dryness to mainly cause the liquid phase refrigerant to flow out. A refrigerant outlet from which a gas-liquid two-phase refrigerant flows out is also included.

  In addition, the gas phase refrigerant outlet (14c) described in the claims is not limited to the refrigerant outlet which allows only the gas phase refrigerant to flow out, and it is relatively dry, in order to mainly cause the gas phase refrigerant to flow out. A refrigerant outlet from which a gas-liquid two-phase refrigerant flows out is also included.

  In addition, the code | symbol in the parenthesis of each means described by this column and the claim is an example which shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is an external appearance perspective view of the gas-liquid separator of 1st Embodiment. It is an external appearance perspective view which shows the main-body part of the gas-liquid separator of 1st Embodiment. It is an external appearance perspective view which shows the main-body part of the gas-liquid separator of 2nd Embodiment. It is an external appearance perspective view which shows the main-body part of the gas-liquid separator of 3rd Embodiment.

First Embodiment
A first embodiment of the present invention will be described using FIGS. 1 to 3. The ejector-type refrigeration cycle 10 according to the present embodiment is applied to a vehicle air conditioner, and has a function of cooling the air that is blown into the vehicle compartment, which is a space to be air conditioned. Therefore, the fluid to be cooled of the ejector-type refrigeration cycle 10 of the present embodiment is blowing air.

  In the ejector-type refrigeration cycle 10, an HFC refrigerant (specifically, R134a) is adopted as the refrigerant, and a subcritical refrigeration cycle in which the high pressure side refrigerant pressure of the cycle does not exceed the critical pressure of the refrigerant is configured. Furthermore, the refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates the cycle together with the refrigerant.

  As this refrigerator oil, PAG oil (polyalkylene glycol oil) compatible with liquid phase refrigerant is employed. Therefore, in the present embodiment, a refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil is employed.

  In the ejector-type refrigeration cycle 10 shown in the overall configuration diagram of FIG. 1, the compressor 11 sucks, compresses and discharges the refrigerant. More specifically, the compressor 11 according to the present embodiment is an electric compressor configured by housing a fixed displacement type compression mechanism and an electric motor for driving the compression mechanism in one housing.

  As this compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be adopted. In addition, the electric motor has its rotation speed (that is, the refrigerant discharge capacity) controlled by a control signal output from the air conditioning control device 20 described later, and either an AC motor or a DC motor is adopted. May be

  The refrigerant inlet side of the radiator 12 is connected to the discharge port of the compressor 11. The radiator 12 is a heat-dissipation heat exchanger that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the air outside the vehicle (outside air) blown by the cooling fan 12 a to dissipate the high-pressure refrigerant and cool it. The cooling fan 12 a is an electric blower whose number of rotations (the amount of blowing air) is controlled by a control voltage output from the air conditioning controller 20.

  The inlet side of the nozzle portion 13 a of the ejector 13 is connected to the refrigerant outlet of the radiator 12. The ejector 13 has a nozzle portion 13a that decompresses and injects the refrigerant flowing out of the radiator 12, and functions as a refrigerant decompression device. Furthermore, the ejector 13 functions as a refrigerant circulating device that sucks and circulates the refrigerant from the outside by the suction action of the injected refrigerant injected from the refrigerant injection port of the nozzle portion 13a.

  In addition to this, the ejector 13 converts the kinetic energy of the mixed refrigerant of the injected refrigerant injected from the nozzle portion 13a and the suctioned refrigerant drawn from the refrigerant suction port 13c into pressure energy, and converts the energy of the mixed refrigerant into pressure It functions as a device.

  More specifically, the ejector 13 has a nozzle portion 13a and a body portion 13b. The nozzle portion 13a is formed of a substantially cylindrical metal (in the present embodiment, a stainless steel alloy) or the like which gradually tapers in the flow direction of the refrigerant. The nozzle portion 13a is configured to decompress and expand a refrigerant isentropically in a refrigerant passage formed inside.

  In the refrigerant passage formed inside the nozzle portion 13a, a throat portion which reduces the passage cross-sectional area most and a diverging portion where the passage cross-sectional area gradually expands as it goes from the throat to the refrigerant injection port for injecting the refrigerant. Is formed. That is, the nozzle part 13a of this embodiment is comprised as a Laval nozzle.

  Furthermore, in the present embodiment, as the nozzle portion 13a, a nozzle portion set so that the flow velocity of the injected refrigerant injected from the refrigerant injection port during normal operation of the cycle is equal to or higher than the speed of sound is employed. Of course, the nozzle portion 13a may be configured by a tapered nozzle.

  The body portion 13b is formed of a substantially cylindrical metal (in the present embodiment, aluminum). The body portion 13 b functions as a fixing member for supporting and fixing the nozzle portion 13 a inside and forms an outer shell of the ejector 13. More specifically, the nozzle portion 13a is fixed by press-fitting so as to be accommodated inside the one end side in the longitudinal direction of the body portion 13b. The body portion 13b may be made of resin.

  A refrigerant suction port 13c is formed in a portion corresponding to the outer peripheral side of the nozzle portion 13a in the outer peripheral surface of the body portion 13b so as to penetrate the inside and the outside and communicate with the refrigerant injection port of the nozzle portion 13a. ing. The refrigerant suction port 13 c is a through hole for drawing the refrigerant flowing out of the evaporator 15 described later into the inside of the ejector 13 by the suction action of the injected refrigerant injected from the nozzle portion 13 a.

  Inside the body portion 13b, a suction passage for guiding the suctioned refrigerant sucked from the refrigerant suction port 13c to the refrigerant injection port side of the nozzle portion 13a, and a pressure increasing portion for mixing the suctioned refrigerant and the injected refrigerant and boosting the pressure. A diffuser portion 13d is formed.

  The suction passage is formed in the space between the outer peripheral side around the tapered tip of the nozzle portion 13a and the inner peripheral side of the body portion 13b, and the refrigerant passage area of the suction passage is directed to the refrigerant flow direction It is shrinking gradually. As a result, the flow velocity of the suction refrigerant flowing through the suction passage is gradually increased, and the energy loss (that is, the mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser portion 13d is reduced.

  The diffuser portion 13d is a frusto-conical refrigerant passage disposed continuously with the outlet of the suction passage. In the diffuser portion 13d, the passage cross-sectional area gradually expands toward the refrigerant flow downstream side. The diffuser portion 13 d converts kinetic energy of the mixed refrigerant into pressure energy by such a passage shape.

  More specifically, the cross-sectional shape of the inner peripheral wall surface of the body portion 13b forming the diffuser portion 13d of the present embodiment is formed by combining a plurality of curves. Then, since the degree of spread of the refrigerant passage cross-sectional area of the diffuser portion 13 d gradually increases in the refrigerant flow direction and then decreases again, the refrigerant can be isentropically pressurized.

  Further, in the ejector-type refrigeration cycle 10 of the present embodiment, the refrigerant flowing out of the diffuser portion 13d during normal operation becomes a gas-liquid two-phase refrigerant. More specifically, in the ejector-type refrigeration cycle 10 of the present embodiment, the refrigerant is charged such that the dryness of the refrigerant flowing out of the diffuser portion 13d during normal operation is 0.4 or more and 0.8 or less. It is done.

  The refrigerant inlet 14 a side of the gas-liquid separator 14 is connected to the outlet of the diffuser portion 13 d. The gas-liquid separator 14 separates the gas-liquid of the refrigerant flowing out of the diffuser portion 13 d, and causes the separated liquid-phase refrigerant to flow out to the refrigerant inlet side of the evaporator 15 described later, and compresses the separated gas-phase refrigerant It flows out to the suction side of the machine 11.

  The detailed configuration of the gas-liquid separator 14 will be described with reference to FIGS. 2 and 3. In addition, each arrow of the upper and lower sides in FIG. 2 grade | etc., Has shown each direction of the upper and lower sides in the state which mounted the gas-liquid separator 14 in the vehicle. The gas-liquid separator 14 has a main body portion 140 and a case portion 145, as shown in FIG.

  As shown in FIG. 3, the main body portion 140 is formed of a metal (in this embodiment, aluminum) tubular member forming a refrigerant passage having a constant passage cross-sectional area. The passage cross section of the main body portion 140 is circular. The main body portion 140 is roughly divided into an upstream side cylindrical portion 142 formed in a cylindrical shape, a spiral portion 141 curved in a spiral shape, and a downstream side cylindrical portion 143 formed in a cylindrical shape.

  The spiral portion 141 is a portion that functions to separate gas and liquid of the refrigerant by applying a centrifugal force to the refrigerant flowing in the refrigerant passage formed inside. In the present embodiment, the number of turns of the spiral portion 141 is four in order to ensure sufficient gas-liquid separation performance. Further, on the outer peripheral side of the central axis of the spiral of the spiral portion 141, a plurality of (eight in the present embodiment) communication holes 141a are formed which allow the inside and the outside of the spiral portion 141 to communicate.

  The communication hole 141 a is a liquid return hole for causing the liquid-phase refrigerant separated in the spiral portion 141 to flow out to the outside of the spiral portion 141 (specifically, to a liquid storage space 145 a described later). Each communication hole 141a is formed in a circular shape. The centers of the respective communication holes 141 a are arranged at equal angular intervals around the central axis of the spiral when viewed from the central axis direction of the spiral.

  Furthermore, in the present embodiment, the opening area of the communication hole 141a disposed on the refrigerant flow downstream side of the adjacent communication holes 141a is set equal to or less than the opening area of the communication hole 141a disposed on the refrigerant flow upstream side. . Thus, the total opening area of the communication hole 141a that opens on the refrigerant flow upstream side of the intermediate portion of the range in which the communication hole 141a is formed in the spiral portion 141 communicates on the refrigerant flow downstream side of the intermediate portion It is larger than the total opening area of the holes.

  Here, the range in which the plurality of communication holes 141 a in the main body portion 140 is formed is the communication downstream of the communication hole 141 a disposed on the most upstream side of the refrigerant flow in the spiral portion 141. It can be defined as the range to the hole 141a. Furthermore, the middle part is a middle part in the refrigerant flow direction in the range.

  Furthermore, as understood from FIG. 3, the plurality of communication holes 141 a are formed in the fourth turn of the spiral portion 141 (that is, one turn on the most downstream side of the refrigerant flow). For this reason, all the communication holes 141 a are disposed closer to the gas phase refrigerant outlet 14 c provided in the downstream cylindrical portion 143 than the refrigerant inlet 14 a provided in the upstream cylindrical portion 142.

  The upstream cylindrical portion 142 is disposed on the upper side of the spiral portion 141, and forms a refrigerant inlet 14a into which the refrigerant flowing out of the diffuser portion 13d flows. In other words, in the gas-liquid separator 14, the refrigerant inlet 14 a for allowing the refrigerant to be separated into gas and liquid to flow is provided at the most upstream portion of the refrigerant flow of the main body portion 140.

  Further, the center line of the upstream side cylindrical portion 142 extends in the tangential direction of the center line of the refrigerant passage of the spiral portion 141. For this reason, the refrigerant inlet 14a is opened so as to allow the refrigerant flowing out of the diffuser portion 13d to flow in the tangential direction of the center line of the refrigerant passage of the spiral portion 141. Here, the center line of the refrigerant passage of the spiral portion 141 can be defined by a line connecting the center of gravity of the passage cross section of the spiral portion 141 or the like, and is drawn in a spiral shape.

  The downstream side cylindrical portion 143 is disposed on the lower side of the spiral portion 141, and forms a gas phase refrigerant outlet 14c that causes the gas phase refrigerant to flow out to the suction side of the compressor 11. In other words, in the gas-liquid separator 14, the gas phase refrigerant outlet 14 c that causes the gas phase refrigerant separated in the inside of the main body 140 to flow out is provided at the refrigerant flow most downstream part of the main body 140.

  Furthermore, the center line of the downstream side cylindrical portion 143 extends in the tangential direction of the center line of the refrigerant passage of the spiral portion 141. For this reason, the gas phase refrigerant outlet 14 c is opened so that the separated gas phase refrigerant flows out in the tangential direction of the center line of the refrigerant passage of the spiral portion 141.

  Next, as shown in FIG. 2, the case portion 145 has a container structure made of metal (in this embodiment, made of aluminum) that accommodates at least a part of the main body portion 140. Inside the case portion 145, a liquid storage space 145a is formed, which accommodates a part of the main body portion 140 and stores liquid phase refrigerant flowing out from the plurality of communication holes 141a formed in the spiral portion 141.

  The liquid storage space 145a is a cylindrical space, and the central axis of the liquid storage space 145a and the central axis of the spiral of the spiral portion 141 are coaxially arranged. Furthermore, the gas-liquid separator 14 is disposed such that the central axis of the liquid storage space 145a and the central axis of the spiral of the spiral portion 141 are in the vertical direction.

  Then, the upstream side cylindrical portion 142 of the main body portion 140 protrudes from the side surface on the upper side of the case portion 145 to open the refrigerant inlet 14 a. The downstream side cylindrical portion 143 of the main body portion 140 protrudes from the lower side surface of the case portion 145 and opens the gas phase refrigerant outlet 14 c. Therefore, the gas phase refrigerant outlet 14c is opened below the refrigerant inlet 14a.

  Furthermore, a liquid-phase refrigerant outlet 14 b is formed on the bottom surface of the liquid storage space 145 a of the case portion 145 and at a portion that forms the lowermost portion of the liquid storage space 145 a. For this reason, the liquid-phase refrigerant outlet 14b opens below the liquid surface of the liquid-phase refrigerant stored in the liquid storage space 145a. As shown in FIG. 1, the refrigerant inlet side of the evaporator 15 is connected to the liquid-phase refrigerant outlet 14 b of the gas-liquid separator 14.

  The evaporator 15 is an endothermic heat exchanger that evaporates the low-pressure refrigerant to exhibit a heat absorbing function by heat exchange between the low-pressure refrigerant flowing into the interior and the blowing air blown toward the vehicle interior from the blower 15a. is there. The blower 15a is an electric blower whose number of rotations (the amount of blowing air) is controlled by a control voltage output from the air conditioning control device 20. The refrigerant suction port 13 c side of the ejector 13 is connected to the refrigerant outlet of the evaporator 15.

  Next, the electric control unit of the ejector-type refrigeration cycle 10 of the present embodiment will be described. The air conditioning control unit 20 (not shown) comprises a known microcomputer including a CPU, a ROM, a RAM and the like and its peripheral circuits, performs various calculations and processing based on a control program stored in the ROM, and outputs It controls the operation of the connected various control target devices 11, 12a, 15a and the like.

  Further, the air conditioning control device 20 includes an inside air temperature sensor for detecting the temperature inside the vehicle, an outside air temperature sensor for detecting the outside air temperature, a solar radiation sensor for detecting the amount of solar radiation in the vehicle compartment, and a temperature of air blown out from the evaporator 15 ( A sensor group such as an evaporator temperature sensor that detects the evaporator temperature is connected, and detection signals of these air conditioning sensor groups are input.

  Furthermore, an operation panel (not shown) is connected to the input side of the air conditioning control device 20, and operation signals from various operation switches provided on the operation panel are input to the air conditioning control device 20. As various operation switches provided on the operation panel, an air conditioning operation switch requiring air conditioning, a vehicle interior temperature setting switch for setting a vehicle interior temperature, and the like are provided.

  Note that the air conditioning control device 20 of the present embodiment is integrally configured with a control unit that controls the operation of various control target devices connected to the output side of the air conditioning control device 20. The configuration (hardware and software) for controlling the operation of the control target device constitutes the control unit of each control target device. For example, the configuration for controlling the operation of the compressor 11 constitutes a discharge capacity control unit.

  Next, the operation of the ejector-type refrigeration cycle 10 of the present embodiment in the above configuration will be described. When the air conditioning operation switch of the operation panel is turned on (ON), the air conditioning control device 20 operates the compressor 11, the cooling fan 12a, the blower 15a, and the like.

  Thereby, the compressor 11 sucks, compresses and discharges the refrigerant. The high-temperature high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The refrigerant flowing into the radiator 12 exchanges heat with the outside air blown from the cooling fan 12a, and is cooled and condensed.

  The refrigerant flowing out of the radiator 12 flows into the nozzle portion 13a of the ejector 13, isentropically depressurized and jetted. Then, the refrigerant flowing out of the evaporator 15 is drawn from the refrigerant suction port 13 c by the suction action of the injected refrigerant.

  The injection refrigerant injected from the nozzle portion 13a and the suction refrigerant drawn from the refrigerant suction port 13c flow into the diffuser portion 13d. In the diffuser portion 13d, the velocity energy of the refrigerant is converted into pressure energy by the expansion of the refrigerant passage area. Thereby, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant is increased. The gas-liquid two-phase refrigerant pressurized by the diffuser portion 13 d flows into the refrigerant inlet 14 a of the gas-liquid separator 14.

  The refrigerant in the gas-liquid two-phase state that has flowed into the gas-liquid separator 14 is separated into gas and liquid by the action of centrifugal force when flowing through the spiral portion 141 of the main body portion 140. The liquid-phase refrigerant separated by the spiral portion 141 flows into the liquid storage space 145 a of the case portion 145 through the communication hole 141 a. The liquid phase refrigerant stored in the liquid storage space 145a flows out from the liquid phase refrigerant outlet 14b. In addition, the gas phase refrigerant separated by the spiral portion 141 flows out from the gas phase refrigerant outlet 14c.

  The refrigerant flowing out of the liquid-phase refrigerant outlet 14 b flows into the evaporator 15 while reducing the pressure when flowing through the refrigerant flow path from the gas-liquid separator 14 to the evaporator 15. The refrigerant that has flowed into the evaporator 15 absorbs heat from the blown air blown by the blower 15a and evaporates. Thereby, the blowing air is cooled. The refrigerant flowing out of the evaporator 15 is drawn from the refrigerant suction port 13 c of the ejector 13. The gas phase refrigerant flowing out of the gas phase refrigerant outlet 14c is sucked into the compressor 11 and compressed again.

  The ejector-type refrigeration cycle 10 of the present embodiment can operate as described above to cool the blown air blown into the vehicle compartment.

  In the ejector-type refrigeration cycle 10, the refrigerant pressurized by the diffuser portion 13 d of the ejector 13 is sucked into the compressor 11. Therefore, according to the ejector-type refrigeration cycle 10, the consumption power of the compressor 11 is reduced compared to a conventional refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the compressor suction refrigerant are substantially equal. The coefficient of performance (COP) can be improved.

  Furthermore, in the ejector-type refrigeration cycle 10 of the present embodiment, a refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil is employed. Therefore, in the refrigerant flowing through the refrigerant passage of the spiral portion 141 of the gas-liquid separator 14, the liquid phase refrigerant is likely to be distributed on the outer peripheral side of the central axis of the spiral by the action of the centrifugal force.

  As a result, the liquid-phase refrigerant separated in the refrigerant passage of the spiral portion 141 can be given priority over the refrigeration oil and the gas-phase refrigerant, and can flow out from the communication hole 141a to the liquid storage space 145a. This is the same even if the liquid-phase refrigerant and the refrigerator oil are compatible with each other. That is, even if they have compatibility, the liquid phase refrigerant is more likely to be distributed on the central axis outer peripheral side of the spiral than the refrigerant machine oil due to the action of the centrifugal force.

  At this time, in the gas-liquid separator 14 of the present embodiment, the total opening area of the communication holes 141a opened on the refrigerant flow upstream side of the intermediate portion is the total opening of the communication holes opened on the refrigerant flow downstream side of the intermediate portion. Since the area is larger than the area, it is possible to effectively suppress the gas phase refrigerant and the refrigerator oil from flowing out through the communication hole 141a.

  More specifically, a refrigerant having a relatively low dryness flows in the upstream side of the middle portion of the refrigerant passage in the range where the communication hole 141a of the main body portion 140 is formed. For this reason, the amount of liquid-phase refrigerant distributed on the outer peripheral side of the central axis of the spiral also increases. Therefore, even if the total opening area of the communication hole 141a opened to the refrigerant flow upstream side of the middle portion is set relatively large, the liquid phase refrigerant does not cause the gas phase refrigerant and the refrigerator oil to flow out from the communication hole 141a. Can be drained.

  Furthermore, on the downstream side of the middle portion of the refrigerant passage in the range where the communication hole 141a of the main body portion 140 is formed, the liquid phase refrigerant flows out from the communication hole 141a disposed on the refrigerant flow upstream side of the middle portion. As it goes, a relatively dry refrigerant flows. For this reason, the amount of liquid-phase refrigerant distributed on the outer peripheral side of the central axis of the spiral also decreases.

  Therefore, by setting the total opening area of the communication holes 141a opened to the refrigerant flow downstream side of the intermediate portion relatively small, it is possible to suppress the gas phase refrigerant and the refrigerator oil from flowing out from the communication holes 141a. be able to. As a result, the liquid-phase refrigerant stored in the liquid storage space 145a can flow out of the liquid-phase refrigerant outlet 14b. Furthermore, the gas phase refrigerant and the refrigerator oil that have not flowed out to the liquid storage space 145a side can be made to flow out from the gas phase refrigerant outlet 14c.

  That is, according to the gas-liquid separator 14 of this embodiment, when separating the gas-liquid of the refrigerant whose specific gravity in the liquid phase is larger than the specific gravity of the refrigerator oil, the refrigerator oil is appropriately selected from the liquid-phase refrigerant Can be separated. Further, since the refrigeration oil appropriately separated can be returned to the suction side of the compressor 11 together with the gas phase refrigerant, the compressor 11 can be protected.

  Further, in the gas-liquid separator 14 of the present embodiment, since the liquid-phase refrigerant outlet 14b is opened at a portion forming the bottom surface of the liquid storage space 145a of the case portion 145, the gas phase refrigerant in the liquid storage space 145a is It is possible to suppress the occurrence of so-called gas phase refrigerant biting, which is drawn into the liquid phase refrigerant and flows out from the liquid phase refrigerant outlet 14b together with the liquid phase refrigerant.

  The entrapment of the gas phase refrigerant causes pressure fluctuation in the liquid storage space 145a. Therefore, the ability to suppress the occurrence of the gas phase refrigerant entrapment is effective in that the gas-liquid separation performance of the gas-liquid separator 14 can be stabilized.

  Further, in the cycle configuration in which the refrigerant flowing out of the evaporator 15 is sucked by the ejector 13 as in the ejector-type refrigeration cycle 10 of the present embodiment, the suction capacity of the ejector 13 is likely to decrease during low load operation. For this reason, in the ejector-type refrigeration cycle 10, the ability to properly separate the refrigeration oil from the liquid phase refrigerant in the gas-liquid separator 14 is extremely effective in that the refrigeration oil can be prevented from staying in the evaporator 15. It is valid.

  Further, in order to sufficiently obtain the COP improvement effect by the pressurizing action of the ejector 13 described above, the gas-liquid separator 14 disposed between the outlet side of the diffuser portion 13 d of the ejector 13 and the suction side of the compressor 11 It is desirable to reduce the pressure loss that occurs in the refrigerant.

  On the other hand, in the gas-liquid separator 14 of the present embodiment, the refrigerant inlet 14 a of the upstream cylindrical portion 142 flows the refrigerant flowing out of the diffuser portion 13 d in the tangential direction of the center line of the refrigerant passage of the spiral portion 141 It is open to let you Therefore, the refrigerant flowing out of the diffuser portion 13d can smoothly flow into the spiral portion 141, and the pressure loss generated when the refrigerant flows can be reduced.

  Further, the gas phase refrigerant outlet 14 c of the gas phase refrigerant outlet 14 c is opened so as to allow the gas phase refrigerant to flow out tangentially to the center line of the refrigerant passage of the spiral portion 141. Therefore, the refrigerant can smoothly flow out from the spiral portion 141, and the pressure loss generated when the refrigerant flows out can be reduced.

  In addition to this, since the passage cross-sectional area of the main body portion 140 is formed to be constant, the passage cross-sectional area of the region through which the gas phase refrigerant flows in the main body portion 140 changes rapidly and pressure loss occurs. Can be suppressed. Therefore, according to the gas-liquid separator 14 of the present embodiment, the pressure loss generated in the refrigerant can be reduced, and the COP improvement effect of the ejector-type refrigeration cycle 10 can be sufficiently obtained.

  Further, in the gas-liquid separator 14 of the present embodiment, since the spiral portion 141 is provided, the number of turns on the upstream side of the portion where the plurality of communication holes 141 a are formed in the spiral portion 141 is adjusted. Thus, the gas-liquid separation performance can be adjusted.

  Here, according to the study of the present inventor, as in the ejector-type refrigeration cycle 10 of the present embodiment, the liquid-phase refrigerant separated by the gas-liquid separator 14 disposed downstream of the diffuser portion 13d is evaporated. In the cycle configuration in which the refrigerant flows into the cooling unit 15, the dryness of the refrigerant flowing out of the diffuser portion 13d is 0.4 or more, and 0. 0 or more in order to supply the refrigerant at an appropriate flow rate to the evaporator 15 regardless of load fluctuation. It is desirable to set to 8 or less. More preferably, it is desirable to set this dryness to 0.5 or more and 0.7 or less.

  Therefore, in the gas-liquid separator 14 applied to the ejector-type refrigeration cycle 10, sufficient gas-liquid separation performance is achieved when the dryness of the refrigerant flowing into the refrigerant inlet 14a is in the range of 0.4 or more and 0.8 or less. By adjusting the gas-liquid separation performance so as to exert it, the ejector-type refrigeration cycle 10 can exhibit a sufficient refrigeration capacity.

  Further, in the present embodiment, since all the communication holes 141a are disposed closer to the gas phase refrigerant outlet 14c than the refrigerant inlet 14a, the gas phase flowing in the passage from the communication hole 141a to the gas phase refrigerant outlet 14c The pressure loss generated in the refrigerant can be further suppressed.

Second Embodiment
In the first embodiment, an example in which the opening area of the plurality of communication holes 141a is changed has been described, but in the present embodiment, as shown in FIG. 4, the distance between adjacent communication holes is changed. An example will be described in which the total opening area of the communication holes 141a opening on the refrigerant flow upstream side of the middle part is larger than the total opening area of the communication holes opening on the refrigerant flow downstream side of the middle part.

  4 is a drawing corresponding to FIG. 3 described in the first embodiment, and in FIG. 4, the same or equivalent parts as in the first embodiment are given the same reference numerals. The same applies to the following drawings.

  More specifically, in the present embodiment, the opening areas of the plurality of communication holes 141a are all set to be the same. Moreover, the centers of the plurality of communication holes 141a are not arranged at equal angular intervals around the central axis of the spiral when viewed from the central axis direction of the spiral. Further, the distance between the adjacent communication holes 141a is wider as it is disposed on the downstream side of the refrigerant flow.

  The configuration and operation of the other gas-liquid separator 14 and ejector-type refrigeration cycle 10 are the same as in the first embodiment. Therefore, also in the gas-liquid separator 14 of this embodiment, when separating the gas-liquid of the refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil, the refrigerator oil is appropriately selected from the liquid-phase refrigerant It can be separated.

Third Embodiment
In the present embodiment, an example in which a gas return pipe 146 is added as shown in FIG. 5 to the gas-liquid separator 14 of the first embodiment will be described. The gas return pipe 146 is a tubular member for returning the gas phase refrigerant in the liquid storage space 145 a into the refrigerant passage of the main body 140. The gas return pipe 146 is formed of the same kind of metal as the main body 140.

  The gas return pipe 146 of the present embodiment is connected to the downstream side of the helical portion 141 of the main body portion 140 (that is, the downstream cylindrical portion 143). The gas return pipe 146 is disposed such that the central axis extends in the vertical direction. For this reason, the gas inlet 146a of the gas return pipe 146 is opened above the communication holes 141a.

  The configuration and operation of the other gas-liquid separator 14 and ejector-type refrigeration cycle 10 are the same as in the first embodiment. Therefore, also in the gas-liquid separator 14 of this embodiment, when separating the gas-liquid of the refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil, the refrigerator oil is appropriately selected from the liquid-phase refrigerant It can be separated.

  Furthermore, in the gas-liquid separator 14 of the present embodiment, the gas return pipe 146 is connected to the main body portion 140 (specifically, the downstream cylindrical portion 143), so the gas phase refrigerant described in the first embodiment Can be effectively suppressed. Further, since the gas inlet 146a is opened above the communication hole 141a, it is possible to suppress that the liquid phase refrigerant flowing out from the communication hole 141a flows into the gas return pipe 146 again.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) The opening shape, number, arrangement, and the like of the plurality of communication holes 141a are not limited to those disclosed in the above-described embodiment. That is, if the total opening area of the communication holes 141a opening on the refrigerant flow upstream side of the middle part can be made larger than the total opening area of the communication holes 141a opening on the refrigerant flow downstream side of the middle part The opening shape, the number, the arrangement, and the like of the communication holes 141a can be changed as appropriate.

  In the above-described embodiment, the center line of the upstream cylindrical portion 142 has been described as extending in a tangential direction of the center line of the refrigerant passage of the spiral portion 141. The direction and the tangential direction of the center line of the refrigerant passage of the spiral portion 141 do not have to be completely coincident.

  For example, when the center line of the upstream cylindrical portion 142 extends in the tangential direction of the center line of the refrigerant passage of the spiral portion 141 when viewed from the central axis direction of the spiral of the spiral portion 141, the same effect is obtained. You can get The same applies to the center line of the downstream cylindrical portion 143.

  (2) Each component apparatus which comprises the ejector-type refrigerating cycle 10 is not limited to what was disclosed by the above-mentioned embodiment.

  For example, although the above-mentioned embodiment explained the example which adopted an electric compressor as compressor 11, it drives by the rotational driving force transmitted from the engine for vehicle travel via a pulley, a belt, etc. as compressor 11. Engine driven compressors may be employed. Furthermore, as an engine-driven compressor, it is possible to adjust the refrigerant discharge capacity by changing the operation rate of the compressor by changing the discharge capacity of the variable displacement compressor capable of adjusting the refrigerant discharge capacity by changing the discharge capacity or the electromagnetic clutch. Fixed displacement compressor can be adopted.

  In the above embodiment, although the detailed configuration of the radiator 12 is not mentioned, a receiver integrated type condenser having a receiver unit (in other words, a liquid receiver) for storing condensed refrigerant as the radiator 12 May be adopted. Furthermore, a so-called subcool type condenser may be employed, which is configured to have a subcooling section for subcooling the liquid phase refrigerant flowing out of the receiver section.

  Further, a flow rate adjustment mechanism for adjusting the flow rate of the refrigerant flowing into the nozzle portion 13a of the ejector 13 may be added to the above-described embodiment. In such a flow rate adjusting mechanism, the temperature at which the valve opening degree is changed so that the degree of superheat of the evaporator 15 outlet side refrigerant (that is, the refrigerant drawn from the refrigerant suction port 13c) approaches a predetermined reference degree of superheat. An expansion valve etc. can be adopted.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted R134a as a refrigerant | coolant, a refrigerant | coolant is not limited to this. For example, R1234yf, R600a, R410A, R404A, R32, R407C, and the like may be adopted as long as the refrigerant has a specific gravity in the liquid phase larger than that of the refrigeration oil. Or you may employ | adopt the mixed refrigerant etc. which mixed multiple types among these refrigerant | coolants.

  (3) In each embodiment described above, the ejector-type refrigeration cycle 10 according to the present invention is applied to a vehicle air conditioner, but the application of the ejector-type refrigeration cycle 10 is not limited to this. For example, the present invention may be applied to stationary air conditioners, cold storages, other cooling and heating devices, and the like.

  (4) Also, the means disclosed in each of the above embodiments may be combined as appropriate in the feasible range. For example, the gas return pipe 146 described in the third embodiment may be connected to the main body 140 described in the second embodiment.

  Furthermore, the total opening area of the communication hole 141a opened on the refrigerant flow upstream side of the middle portion of the range in which the plurality of communication holes 141a is formed in the main body portion 140 communicates on the refrigerant flow downstream side of the middle portion The shape and number of the communication holes 141a are not limited to those disclosed in the above embodiments as long as they are larger than the total opening area of the holes 141a.

DESCRIPTION OF SYMBOLS 10 Ejector type refrigeration cycle 14 Gas-liquid separator 140 Body part 14a Refrigerant inlet 14b Liquid-phase refrigerant outlet 14c Gas-phase refrigerant outlet 141 Communication hole 145 Case part 145a Liquid storage space

Claims (7)

A gas-liquid separator that is applied to a refrigeration cycle apparatus (10) that circulates a refrigerant whose specific gravity in the liquid phase is larger than that of a refrigerator oil, and separates gas and liquid of the refrigerant,
A main body (140) forming a refrigerant passage having a constant passage cross-sectional area;
And a case portion (145) for housing at least a part of the main body portion,
The main body portion is formed of a tubular member having a spirally curved helical portion (141) and separates gas and liquid of the refrigerant flowing through the refrigerant passage by the action of centrifugal force.
A gas phase refrigerant outlet (14c) is provided at the most downstream portion of the refrigerant flow of the main body portion, for discharging the separated gas phase refrigerant,
A plurality of communication holes (141a) communicating the inside and the outside of the main body portion are formed on the outer peripheral side of the central axis of the spiral of the main body portion,
A liquid storage space (145a) for storing the liquid phase refrigerant flowing out of the communication hole is formed inside the case portion,
The case portion is provided with a liquid-phase refrigerant outlet (14b) that allows the liquid-phase refrigerant stored in the liquid storage space to flow out;
The total opening area of the communication hole opened on the refrigerant flow upstream side of the middle portion of the range in which the plurality of communication holes are formed in the main body portion is the communication hole opened on the refrigerant flow downstream side of the intermediate portion A gas-liquid separator that is larger than the total opening area.   The gas-liquid separation according to claim 1, wherein the opening area of the communication hole disposed downstream of the refrigerant flow among the adjacent communication holes is smaller than the opening area of the communication hole disposed upstream of the refrigerant flow. vessel.   The gas-liquid separator according to claim 1, wherein the distance between the adjacent communication holes is wider as it is disposed downstream of the refrigerant flow.   The gas-liquid separator according to any one of claims 1 to 3, wherein the liquid-phase refrigerant outlet is opened in a portion of the case portion which forms the bottom surface of the liquid storage space.   The gas-liquid separator according to any one of claims 1 to 4, wherein a gas return pipe (164) to which the gas phase refrigerant in the liquid storage space flows is connected to the main body.   The gas-liquid separator according to any one of claims 1 to 5, wherein the refrigerant flowing into the refrigerant passage is a gas-liquid two-phase refrigerant having a dryness of 0.4 or more and 0.8 or less. A compressor (11) which sucks in and compresses a refrigerant mixed with refrigeration oil;
A radiator (12) for radiating the refrigerant discharged from the compressor;
The refrigerant is sucked from the refrigerant suction port (13c) by the suction action of the jetted refrigerant injected from the nozzle portion (13a) for decompressing the refrigerant flowing out from the radiator (12), and suctioned from the jetted refrigerant and the refrigerant suction port An ejector (13) for boosting the pressure of the mixed refrigerant with the suctioned refrigerant;
A gas-liquid separator (14) for separating gas and liquid of the refrigerant flowing out from the ejector and causing the separated gas phase refrigerant to flow out to the suction side of the compressor;
An evaporator (15) for evaporating the liquid-phase refrigerant separated by the gas-liquid separator and flowing it out to the refrigerant suction port side;
As the refrigerant, a refrigerant whose specific gravity in the liquid phase is larger than that of the refrigerator oil is employed,
The gas-liquid separator is
A main body (140) forming a refrigerant passage having a constant passage cross-sectional area, and a case (145) accommodating at least a part of the main body,
The main body portion is formed of a tubular member having a spirally curved helical portion (141) and separates gas and liquid of the refrigerant flowing through the refrigerant passage by the action of centrifugal force.
At the most downstream portion of the refrigerant flow in the refrigerant passage, there is provided a gas phase refrigerant outlet (14c) for discharging the separated gas phase refrigerant,
A plurality of communication holes (141a) communicating the inside and the outside of the main body portion are formed on the outer peripheral side of the central axis of the spiral of the main body portion,
A liquid storage space (145a) for storing the liquid phase refrigerant flowing out of the communication hole is formed inside the case portion,
The case portion is provided with a liquid-phase refrigerant outlet (14b) that allows the liquid-phase refrigerant stored in the liquid storage space to flow out;
The total opening area of the communication hole opened on the refrigerant flow upstream side of the middle portion of the range in which the plurality of communication holes are formed in the main body portion is the communication hole opened on the refrigerant flow downstream side of the intermediate portion A refrigeration cycle device that is larger than the total opening area.

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