REFRIGERANT RESERVOIR CONTAINER AND REFRIGERATION CYCLE DEVICE INCLUDING THE SAME

A refrigerant reservoir container includes: a container body reserving refrigerant; an inflow pipe inserted into an upper space of the container body, the inflow pipe having an inlet through which the refrigerant flows into the container body; and an outflow pipe inserted into the upper space of the container body, the outflow pipe having an outlet through which the refrigerant flows out from the container body, wherein a cross-sectional area of an inner space of the container body where the outlet of the outflow pipe is located is larger towards a bottom of the container body and away from the outlet.

TECHNICAL FIELD

The present disclosure relates to a refrigerant reservoir container reserving refrigerant therein, and also relates to a refrigeration cycle device including the refrigerant reservoir container.

BACKGROUND

In a refrigeration cycle device, when a compressor suctions liquid refrigerant, refrigerating machine oil in a shell of the compressor is diluted with the liquid refrigerant, which causes seizure of sliding parts of the compressor. In view of that, a configuration of a refrigeration cycle device is proposed, in which a refrigerant reservoir container is provided upstream of a suction port through which a compressor suctions refrigerant. The refrigerant reservoir container is configured to separate two-phase gas-liquid refrigerant into gas refrigerant and liquid refrigerant and reserve the liquid refrigerant in the container. For example, Patent Literature 1 discloses a gas-liquid separator located in a refrigeration cycle to separate refrigerant into liquid refrigerant and gas refrigerant. The gas-liquid separator has a function of the refrigerant reservoir container, and includes a gas-phase refrigerant outflow pipe provided in an upper portion of the container to allow the gas refrigerant to flow out from the gas-liquid separator, a liquid-phase refrigerant outflow pipe provided in a lower portion of the container to allow the liquid refrigerant to flow out from the gas-liquid separator, a first plate configured to partition a refrigerant inflow chamber from a liquid-phase refrigerant accumulation chamber, and a second plate configured to partition the refrigerant inflow chamber from a gas-phase refrigerant collection chamber.

PATENT LITERATURE

Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2015-172469

In the gas-liquid separator described in Patent Literature 1, since the first plate partitions the refrigerant inflow chamber from the liquid-phase refrigerant accumulation chamber, the accumulating liquid refrigerant is restrained from rolling up and entering the refrigerant inflow chamber. In addition, since the second plate partitions the refrigerant inflow chamber from the gas-phase refrigerant collection chamber, refrigerant having flowed into the refrigerant inflow chamber and having become liquid droplets is restrained from entering the gas-phase refrigerant collection chamber. As a result, in the gas-liquid separator in Patent Literature 1, the accumulating liquid refrigerant is restrained from entering the refrigerant outflow pipe through which gas refrigerant flows out.

However, as disclosed in Patent Literature 1, the plates are used to simply partition a region into which refrigerant flows, a region in which liquid refrigerant is reserved, and a region in which gas refrigerant is reserved, from each other. This cannot always suppress roll-up of the accumulating liquid refrigerant, or restrain scattering liquid droplets from entering the refrigerant outflow pipe. For example, when liquid refrigerant is reserved up to the upper portion of the container, the reserved liquid refrigerant may ripple and scatter, and the scattering liquid droplets may reach the refrigerant outflow pipe and flow into the compressor along with gas refrigerant. As the area of gas-liquid interface increases, ripples of the liquid refrigerant spread more widely over the gas-liquid interface in the refrigerant reservoir container. In addition, the volume of scattering liquid droplets increases in proportion to the area of gas-liquid interface. For this reason, even when the volume of liquid refrigerant reserved is below the maximum reservoir volume, the liquid refrigerant that ripples over the gas-liquid interface and thus scatters may still reach the refrigerant outflow pipe and may flow out along with the gas refrigerant from the refrigerant reservoir container.

SUMMARY

The present disclosure has been made in view of the above problems, and it is an object of the present disclosure to provide a refrigerant reservoir container that restrains liquid refrigerant from flowing out along with gas refrigerant from the refrigerant reservoir container, and a refrigeration cycle device including the refrigerant reservoir container.

A refrigerant reservoir container according to one embodiment of the present disclosure includes: a container body reserving refrigerant; an inflow pipe inserted into an upper space of the container body, the inflow pipe having an inlet through which the refrigerant flows into the container body; and an outflow pipe inserted into the upper space of the container body, the outflow pipe having an outlet through which the refrigerant flows out from the container body, wherein a cross-sectional area of an inner space of the container body where the outlet of the outflow pipe is located is larger towards a bottom of the container body and away from the outlet.

A refrigeration cycle device according to another embodiment of the present disclosure includes: the refrigerant reservoir container described above; and a compressor connected to the refrigerant reservoir container through the outflow pipe.

According to one embodiment of the present disclosure, in the container body of a gas-liquid reservoir container, the cross-sectional area of the inner space where the outlet of the outflow pipe is located, through which refrigerant flows out from the gas-liquid reservoir container, increases towards the bottom of the container body. The outflow pipe is inserted into the upper space of the container body, and thus the cross-sectional area of the inner space near the outlet is smaller than the cross-sectional area of the inner space near the bottom of the container body. With this configuration, even when liquid refrigerant is reserved up to the vicinity of the outlet, ripples of the liquid refrigerant are generated still on a small area of gas-liquid interface. This can reduce the volume of scattering liquid droplets. Therefore, the liquid droplets scattering from the gas-liquid interface are restrained from reaching the refrigerant outflow pipe and flowing along with gas refrigerant into the compressor.

DETAILED DESCRIPTION

Hereinafter, a refrigerant reservoir container according to the present embodiment and a refrigeration cycle device including the refrigerant reservoir container will be described with reference to the drawings. The present disclosure is not limited to the embodiments described below, and can be variously modified without departing from the gist of the present disclosure. In addition, the present disclosure includes all combinations of configurations that can be combined among the configurations shown in the embodiments described below. The configurations of the refrigerant reservoir container and the refrigeration cycle device are illustrated in the drawings merely as examples. The refrigerant reservoir container and the refrigeration cycle device illustrated in the drawings are not intended to limit the configurations of the present disclosure. In the descriptions below, terms that represent directions (for example, “up,” “down,” “right,” “left,” “front,” and “rear”) are appropriately used for the sake of easy understanding. However, these terms are used merely for description purposes, and are not intended to limit the present disclosure.

In the drawings, the same reference signs denote the same or equivalent components, which are common throughout the entire specification. Note that the relative relationship of sizes of the constituent components, the shapes of the constituent components, and the like in the drawings may differ from those of actual ones. In the drawings, the X-direction shows a left-right direction of the refrigerant reservoir container, and is illustrated with the arrow pointing to the leftward direction from the rightward side. The Y-direction shows a front-rear direction of the refrigerant reservoir container, and is illustrated with the arrow pointing to the rearward direction from the forward side. The Z-direction shows an up-down direction of the refrigerant reservoir container, and is illustrated with the arrow pointing to the upward direction from the downward side.

With reference toFIG.1, a refrigeration cycle device100including a refrigerant reservoir container101according to Embodiment 1 is described below.FIG.1is a refrigerant circuit diagram of the refrigeration cycle device100including the refrigerant reservoir container101according to Embodiment 1. As illustrated inFIG.1, the refrigeration cycle device100according to Embodiment 1 includes a compressor10, a flow switching device11, an outdoor heat exchanger12, an expansion mechanism13, an indoor heat exchanger14, and the refrigerant reservoir container101. The compressor10, the flow switching device11, the outdoor heat exchanger12, the expansion mechanism13, the indoor heat exchanger14, and the refrigerant reservoir container101are connected by a refrigerant pipe15. With this connection, a refrigerant circuit200is formed in which refrigerant circulates through the refrigerant pipe15.

In the refrigeration cycle device100, the refrigerant reservoir container101is connected to the compressor10through an outflow pipe3that is a portion of the refrigerant pipe15. The compressor10suctions refrigerant, compresses the suctioned refrigerant into a high-temperature high-pressure state, and discharges the compressed refrigerant. The compressor10is, for example, an inverter compressor. Refrigerant discharged from the compressor10flows into the outdoor heat exchanger12or the indoor heat exchanger14via the flow switching device11.

The flow switching device11has a function of switching between refrigerant flow passages. The flow switching device11switches operation between cooling and heating. In the cooling operation, refrigerant discharged from the compressor10flows through the outdoor heat exchanger12, the expansion mechanism13, the indoor heat exchanger14, and the refrigerant reservoir container101in this order, and flows back to the compressor10. In contrast, in the heating operation, refrigerant discharged from the compressor10flows through the indoor heat exchanger14, the expansion mechanism13, the outdoor heat exchanger12, and the refrigerant reservoir container101in this order, and flows back to the compressor10. That is, during the cooling operation in a room, the outdoor heat exchanger12serves as a condenser, while the indoor heat exchanger14serves as an evaporator. During the heating operation in a room, the indoor heat exchanger14serves as a condenser, while the outdoor heat exchanger12serves as an evaporator. The flow switching device11is, for example, a four-way valve. The flow switching device11may be made up of a combination of two-way valves or three-way valves.

The expansion mechanism13is a pressure-reducing device configured to reduce the pressure of refrigerant flowing in the refrigerant circuit200to expand the refrigerant. The expansion mechanism13is constituted by, for example, an electronic expansion valve whose opening degree is variably controlled.

In the refrigeration cycle device100, it is optimal that superheated gas is suctioned into the compressor10as refrigerant. However, the state of refrigerant to be suctioned into the compressor10depends on a refrigerant distribution in the refrigerant circuit200. Thus, refrigerant containing liquid refrigerant may sometimes be suctioned into the compressor10. When the liquid refrigerant is suctioned into the compressor10, refrigerating machine oil in a shell of the compressor10is diluted with the liquid refrigerant. This may cause seizure of sliding parts of the compressor10. In view of that, in the refrigeration cycle device100, the refrigerant reservoir container101is installed upstream of the compressor10in the refrigerant flow direction. Two-phase gas-liquid refrigerant flowing out from the evaporator and passing through the flow switching device11flows into the refrigerant reservoir container101from an inflow pipe2that is a portion of the refrigerant pipe15. The two-phase gas-liquid refrigerant flowing into the refrigerant reservoir container101is separated into gas refrigerant and liquid refrigerant. The liquid refrigerant accumulates in the refrigerant reservoir container101. The gas refrigerant passes through the outflow pipe3, flows out from the refrigerant reservoir container101, and is suctioned into the compressor10. Therefore, in the refrigeration cycle device100according to the present embodiment, liquid refrigerant is separated from the two-phase gas-liquid refrigerant and reserved in the refrigerant reservoir container101, so that the liquid refrigerant can be restrained from being suctioned into the compressor10.

Note that the refrigeration cycle device100is not limited to being an air-conditioning apparatus capable of switching operation between cooling and heating as described above. The refrigerant reservoir container101may be applied to a refrigeration cycle device such as a dehumidifier or a refrigerator-freezer.

The refrigerant reservoir container101according to the present embodiment is described below with reference toFIGS.2and3.FIG.2is a front view of the refrigerant reservoir container101according to Embodiment 1. The arrows inFIG.2conceptually illustrate a refrigerant flow.FIG.3is a plan view of the refrigerant reservoir container101according to Embodiment 1.

As illustrated inFIG.2, the refrigerant reservoir container101includes a container body1, the inflow pipe2, and the outflow pipe3. The container body1has a substantially truncated conical shape with its inner space having a cross-sectional area that gradually increases from the upper end towards the bottom. Refrigerant accumulates in the inner space of the container body1. The inflow pipe2and the outflow pipe3are inserted into the upper space of the container body1. As illustrated inFIG.2, the inflow pipe2and the outflow pipe3may be inserted from the upper end portion of the container body1. Although not illustrated, the inflow pipe2and the outflow pipe3may be inserted from a lateral surface of the container body1such that the inflow pipe2and the outflow pipe3are located in the upper space of the container body1.

Refrigerant in a two-phase gas-liquid state passes through the inflow pipe2, and flows into the container body1from an inlet2aof the inflow pipe2. Liquid refrigerant flowing into the container body1from the inlet2adrops to the bottom of the container body1due to gravity and accumulates in the container body1. As the volume of liquid refrigerant that accumulates in the container body1increases, the level of a gas-liquid interface GLI rises. In other words, as the volume of liquid refrigerant that accumulates in the container body1increases, the gas-liquid interface GLI moves towards the upper portion of the container body1. Accordingly, as the volume of accumulating liquid refrigerant increases, the gas-liquid interface GLI becomes closer to the inflow pipe2and the outflow pipe3in distance.

Gas refrigerant entering the container body1from the inlet2aflows into the outflow pipe3from an outlet3a. The gas refrigerant flowing into the outflow pipe3passes through the outflow pipe3, flows out from the container body1, and is suctioned into the compressor10.

As illustrated inFIGS.2and3, an end portion of the inflow pipe2is located in the container body1and has a bent portion2bthat is bent in the X-direction. The inlet2ais provided at the bent portion2bto be opposite to the lateral surface of the container body1. The inlet2ais provided to be opposite to the lateral surface of the container body1, so that the distance between the inlet2aand the outlet3acan be increased. Therefore, this can reduce the likelihood that liquid refrigerant flows into the outlet3afrom the inlet2a. Also, the velocity of liquid refrigerant flowing through the inflow pipe2is reduced by the bent portion2b. Consequently, the liquid refrigerant flowing out from the inlet2areduces its momentum, so that when the liquid refrigerant drops to the gas-liquid interface GLI, ripples over the gas-liquid interface GLI can be suppressed. Note that it is desirable for the inlet2ato be provided at a location where the inlet2adoes not overlap the outflow pipe3in the up-down direction of the container body1.

Next, the container body1is described with reference toFIGS.4and5.FIG.4illustrates a relationship between a height and a cross-sectional area of the container body1of the refrigerant reservoir container101according to Embodiment 1.FIG.5illustrates a relationship between the height and an inner volume of the container body1of the refrigerant reservoir container101according to Embodiment 1. As described above, the container body1has a substantially truncated conical shape with its inner space having a cross-sectional area that gradually increases from the upper end towards the bottom.FIGS.4and5illustrate a virtual container body VC with a cylindrical shape by the dotted line in the container body1for the purpose of comparison with the container body1with a substantially truncated conical shape.

FIG.4illustrates, on the right side of the drawing, a cross-sectional area relationship diagram showing the relationship between the height of the container body and the cross-sectional area of the container body.FIG.4illustrates, on the left side of the drawing, the container body1of the refrigerant reservoir container101and the virtual container body VC. In the container body1, a first height position HPt1and a second height position HPt2are illustrated, each of which shows a height position. In the cross-sectional area relationship diagram, the height corresponding to the first height position HPt1is illustrated as a first reference line L1, while the height corresponding to the second height position HPt2is illustrated as a second reference line L2.

In the cross-sectional area relationship diagram, the vertical axis represents the height of the container body1and the virtual container body VC, while the horizontal axis represents the cross-sectional area of the container body1and the virtual container body VC. On the vertical axis, the height increases towards the upper side of the drawing, while on the horizontal axis, the cross-sectional area increases towards the right side of the drawing. In the cross-sectional area relationship diagram, the relationship between the height and the cross-sectional area of the container body1is illustrated by the solid line, while the relationship between the height and the cross-sectional area of the virtual container body VC is illustrated by the thick dotted line. The container body1has a substantially truncated conical shape with its cross-sectional area increasing towards the bottom, and thus the cross-sectional area of the container body1decreases towards the upper portion. In contrast, the virtual container body VC has a cylindrical shape, and thus the cross-sectional area of the virtual container body VC is constant regardless of its height.

As illustrated inFIG.4, at the first height position HPt1, the cross-sectional area of the container body1is equal to the cross-sectional area of the virtual container body VC. Accordingly, in the cross-sectional area relationship diagram, the point showing the cross-sectional area of the container body1at the first height position HPt1coincides, at a first point XPt1, with the point showing the cross-sectional area of the virtual container body VC at the first height position HPt1. In the cross-sectional area relationship diagram, the point showing the cross-sectional area of the container body1at the second height position HPt2is illustrated as a third point XPt3. Further, in the cross-sectional area relationship diagram, the point showing the cross-sectional area of the virtual container body VC at the second height position HPt2is illustrated as a second point XPt2. At the second height position HPt2, the cross-sectional area of the container body1is larger than the cross-sectional area of the virtual container body VC. Accordingly, the third point XPt3is located on the right side relative to the second point XPt2.

FIG.5illustrates, on the right side of the drawing, an inner volume relationship diagram showing the relationship between the height of the container body and the inner volume of the container body. Similar toFIG.4,FIG.5illustrates, on the left side of the drawing, the container body1and the virtual container body VC along with the first height position HPt1and the second height position HPt2.FIG.5also illustrates a third height position HPt3showing the upper end portion of the container body1and the virtual container body VC. In the inner volume relationship diagram, the height corresponding to the third height position HPt3is illustrated as a third reference line L3.

In the inner volume relationship diagram inFIG.5, the vertical axis represents the height of the container body1and the virtual container body VC, while the horizontal axis represents the inner volume of the container body1and the virtual container body VC. On the vertical axis, the height increases towards the upper side of the drawing, while on the horizontal axis, the inner volume increases towards the right side of the drawing. In the inner volume relationship diagram, the relationship between the height and the inner volume of the container body1is illustrated by the solid line, while the relationship between the height and the inner volume of the virtual container body VC is illustrated by the thick dotted line. Since the container body1has a substantially truncated conical shape with its cross-sectional area increasing towards the bottom, the inner volume of the container body1increases at a greater rate closer to the bottom. In contrast, since the virtual container body VC has a cylindrical shape, the inner volume of the virtual container body VC increases at a constant rate regardless of its height.

As illustrated inFIG.5, between the first height position HPt1and the third height position HPt3, the container body1has the same shape as the shape of the virtual container body VC, and thus their shapes overlap each other. In other words, the inner volume of the container body1increases between the first height position HPt1and the third height position HPt3at the same rate as the increase in the inner volume of the virtual container body VC between the first height position HPt1and the third height position HPt3. Accordingly, between the first reference line L1and the third reference line L3in the inner volume relationship diagram, the difference in inner volume between the container body1and the virtual container body VC remains unchanged. In the inner volume relationship diagram, the point showing the inner volume of the container body1at the second height position HPt2is illustrated as a fifth point XPt5. Further, in the inner volume relationship diagram, the point showing the inner volume of the virtual container body VC at the second height position HPt2is illustrated as a fourth point XPt4. At the second height position HPt2, the inner volume of the container body1is larger than the inner volume of the virtual container body VC. Accordingly, the fifth point XPt5is located on the right side relative to the fourth point XPt4.

As described above, the container body1has a substantially truncated conical shape. Thus, the inner volume of the container body1is larger than that of the virtual container body VC with a cylindrical shape, provided that the container body1and the virtual container body VC with a cylindrical shape both have the same height and the same shape of the upper end portion. Accordingly, the container body1can reserve a greater volume of liquid refrigerant than the volume of liquid refrigerant that can be reserved in the virtual container body VC. In addition, since the container body1has a substantially truncated conical shape, the volume of liquid refrigerant per unit height is larger closer to the bottom. Consequently, a longer time is spent for the gas-liquid interface GLI to become close to the outlet3ain distance, compared to the virtual container body VC. In other words, in the container body1, liquid refrigerant can be kept reserved for a longer time with an adequate distance kept between the outlet3aand the gas-liquid interface GLI. In the container body1, ripples may be generated on the gas-liquid interface GLI due to an inertial force of the two-phase gas-liquid refrigerant flowing into the container body1. When ripples are generated on the gas-liquid interface GLI, the liquid refrigerant scatters as liquid droplets in the container body1. In a case where the outlet3aand the gas-liquid interface GLI are adequately distanced from each other, even when the liquid droplets scatter from the gas-liquid interface GLI, the liquid droplets are still less likely to reach the outlet3a. Accordingly, the liquid refrigerant can be restrained from flowing out from the container body1.

As the area of the gas-liquid interface GLI increases, ripples spread more widely over the gas-liquid interface GLI. Further, the volume of scattering liquid droplets increases in proportion to the area of the gas-liquid interface GLI. In the container body1, when the gas-liquid interface GLI becomes close to the outlet3ain distance, the cross-sectional area on the gas-liquid interface GLI is smaller compared to the cross-sectional area at the bottom of the container body1. Accordingly, the volume of scattering liquid droplets can be reduced, so that the liquid droplets are less likely to reach the outlet3a. With this configuration, the container body1can reserve a relatively large volume of liquid refrigerant at a location away from the outlet3a, and can reduce the likelihood that the liquid droplets reach the outlet3awhen the gas-liquid interface GLI becomes close to the outlet3ain distance.

As described above, the refrigerant reservoir container101according to the present embodiment includes the container body1reserving refrigerant, the inflow pipe2inserted into the upper space of the container body1and having the inlet2athrough which the refrigerant flows into the container body1, and the outflow pipe3inserted into the upper space of the container body1and having the outlet3athrough which the refrigerant flows out from the container body1. The cross-sectional area of the inner space of the container body1where the outlet3aof the outflow pipe3is located is larger towards the bottom of the container body1and away from the outlet3a.

In this configuration, the cross-sectional area of the inner space of the container body1is smaller closer to the outlet3a. That is, even when liquid refrigerant accumulates in the container body1, and the gas-liquid interface GLI becomes close to the outlet3ain distance, the volume of liquid droplets that scatter due to ripples of the liquid refrigerant over the gas-liquid interface GLI is still reduced. Accordingly, the liquid refrigerant can be restrained from flowing out from the container body1.

In the configuration of the refrigerant reservoir container101according to the present embodiment, the inflow pipe2and the outflow pipe3are inserted from the upper end portion of the container body1, and the inlet2aof the inflow pipe2is located on the lower side relative to the outlet3aof the outflow pipe3. With this configuration, the inlet2ais located on the lower side relative to the outlet3a, so that the liquid refrigerant that drops from the inlet2ais less likely to flow into the outlet3a. In addition, since the outlet3ais located on the upper side relative to the inlet2a, even when liquid refrigerant flowing into the container body1from the inlet2aripples over the gas-liquid interface GLI and thus liquid droplets scatter, the scattering liquid droplets are still less likely to flow into the outlet3a.

In the configuration of the refrigeration cycle device100according to the present embodiment, the refrigeration cycle device100includes the refrigerant reservoir container101described above, and the compressor10connected to the refrigerant reservoir container101through the outflow pipe3. With this configuration, liquid refrigerant can be restrained from being suctioned into the compressor10from the refrigerant reservoir container101through the outflow pipe3. Therefore, this configuration can reduce the likelihood that refrigerating machine oil in the compressor10is diluted with the liquid refrigerant, which causes seizure of sliding parts of the compressor10.

A container body1A and an inflow pipe2A of a refrigerant reservoir container101A according to the present embodiment are different in configuration from the container body1and the inflow pipe2in Embodiment 1, respectively. The refrigerant reservoir container101A in the present embodiment is described below, mainly focusing on the differences from the refrigerant reservoir container101in Embodiment 1. Note that in the refrigeration cycle device100in Embodiment 1, the refrigerant reservoir container101according to Embodiment 1 can be replaced with the refrigerant reservoir container101A according to the present embodiment. The configuration of the refrigeration cycle device100, other than the refrigerant reservoir container, is the same as that in Embodiment 1, and therefore descriptions of the configuration are omitted. The same constituent elements as those in Embodiment 1 are denoted by the same reference signs, and descriptions thereof are appropriately omitted.

With reference toFIGS.6and7, the container body1A is described below.FIG.6is a front view of the refrigerant reservoir container101A according to Embodiment 2. The solid-line arrows inFIG.6conceptually illustrate a refrigerant flow.FIG.7is a sectional view illustrating the A-A cross section ofFIG.6. As illustrated inFIG.6, the container body1A of the refrigerant reservoir container101A according to the present embodiment has a cylindrical shape. In the container body1A, a shielding plate4is provided. The inflow pipe2A and the outflow pipe3are inserted into the upper space of the container body1A. As illustrated inFIG.6, the inflow pipe2A and the outflow pipe3may be inserted from the upper end portion of the container body1A.

The shielding plate4partitions the interior of the container body1A into a first region SP1where the outlet3aof the outflow pipe3is located, and a second region SP2where the inlet2aof the inflow pipe2A is located. As illustrated inFIG.6, the shielding plate4is provided such that the cross-sectional area of the inner space of the container body1A where the outlet3ais located is larger towards the bottom of the container body1A and away from the outlet3a. In other words, in the present embodiment, while the container body1A has a cylindrical shape, the inner space where the outlet3ais located is formed as the first region SP1with a truncated conical shape by providing the shielding plate4in the container body1A.

The inner space of the container body1A is partitioned into the first region SP1surrounded by the shielding plate4, the second region SP2formed between the lateral surface of the container body1A and the shielding plate4, and a third region SP3formed between a lower end portion of the shielding plate4and the bottom of the container body1A. The first region SP1and the second region SP2both connect to the third region SP3. Accordingly, the first region SP1, the second region SP2, and the third region SP3communicate with each other. The outlet3ais located in the first region SP1, while the inlet2ais located in the second region SP2.

Two-phase gas-liquid refrigerant flows into the second region SP2from the inlet2a. Gas refrigerant passes through the third region SP3and flows into the first region SP1. Gas refrigerant flowing into the first region SP1enters the outflow pipe3from the outlet3aand flows out from the container body1A. Liquid refrigerant passes through the second region SP2and accumulates in the third region SP3. As the volume of accumulating liquid refrigerant increases, the level of the gas-liquid interface GLI rises. When the volume of accumulating liquid refrigerant exceeds the volume of the third region SP3, the excessive volume of liquid refrigerant accumulates in the first region SP1and the second region SP2. Consequently, the gas-liquid interface GLI is located in the first region SP1and the second region SP2. The second region SP2and the third region SP3serve as a passage through which refrigerant flowing from the inlet2areaches the first region SP1and the outlet3a.

InFIG.6, the shielding plate4is connected to the upper end portion of the container body1A. However, the shielding plate4may be connected to a lateral surface of the container body1A. For example, the shielding plate4may be connected to an inner lateral surface of the container body1A through a hook attached to the inner lateral surface of the container body1A.

The shielding plate4may be provided with a through hole through which the outflow pipe3passes. When the inflow pipe2A is inserted from the lateral surface of the container body1A, the outflow pipe3passes through the through hole and reaches the first region SP1. Accordingly, it is possible to locate the outlet3ain the first region SP1. In this case, the inflow pipe2A may be inserted into the second region SP2from the upper end portion of the container body1A, or may be inserted into the second region SP2from the lateral surface of the container body1A.

As illustrated inFIG.7, in the configuration of the present embodiment, the shielding plate4separates the inflow pipe2A from the outflow pipe3. With this configuration, liquid refrigerant is prevented from directly flowing into the outlet3afrom the inlet2a. Liquid droplets are generated on the gas-liquid interface GLI in the second region SP2due to ripples of the liquid refrigerant flowing out from the inlet2aand dropping to the gas-liquid interface GLI. Thus, there is no likelihood that the liquid droplets reach the outlet3alocated in the first region SP1partitioned off by the shielding plate4. For this reason, in the present embodiment, it is allowable that the inlet2aand the outlet3aare not greatly distanced from each other, or the flow rate of refrigerant flowing into the container body1A is not decreased. Therefore, as illustrated inFIGS.6and7, it is allowable that the inflow pipe2A does not have the bent portion2b.

The refrigerant reservoir container101A according to the present embodiment includes the shielding plate4provided in the container body1A. The shielding plate4partitions the interior of the container body1A into the first region SP1that is an inner space where the outlet3aof the outflow pipe3is located, and the second region SP2where the inlet2aof the inflow pipe2A is located. The third region SP3is formed between the lower end portion of the shielding plate4and the bottom of the container body1A. The first region SP1and the second region SP2connect to the third region SP3.

In this configuration, the inlet2ais separated from the outlet3aby the shielding plate4. Accordingly, it is possible to restrain liquid refrigerant flowing out from the inlet2afrom flowing into the outlet3a. The container body1A has a cylindrical shape, and thus can reserve an increased volume of liquid refrigerant compared to a container body with a truncated conical shape, provided that the container body with the truncated conical shape and the container body1A both have the same height and the same cross-sectional area of the bottom. Further, the shielding plate4is provided in the container body1A with a cylindrical shape. Thus, even when the gas-liquid interface GLI becomes close to the outlet3ain distance, the cross-sectional area on the gas-liquid interface GLI near the outlet3ais still smaller than the cross-sectional area of the bottom of the container body1A. Therefore, even when the gas-liquid interface GLI becomes close to the outlet3ain distance, ripples are generated still in a small area over the gas-liquid interface GLI. This can reduce the volume of scattering liquid droplets.

In the refrigerant reservoir container101A according to the present embodiment, the shielding plate4has a hollow truncated conical shape widening from the upper end portion of the container body1A towards the bottom, and being open on a top base and a bottom base. The first region SP1is an inner space surrounded by the shielding plate4, while the second region SP2is a space between the lateral surface of the container body1A and the shielding plate4. This configuration can be obtained by solely connecting the shielding plate4with a hollow truncated conical shape to the container body1A with a cylindrical shape, and thus does not complicate the manufacturing process of the refrigerant reservoir container101A.

A shielding plate4A of a refrigerant reservoir container101B according to the present embodiment is different in configuration from the shielding plate4in Embodiment 2. The shielding plate4A in the present embodiment is described below, mainly focusing on the differences from the shielding plate4in Embodiment 2. Note that in the refrigeration cycle device100in Embodiment 1, the refrigerant reservoir container101according to Embodiment 1 can be replaced with the refrigerant reservoir container101B according to the present embodiment. The configuration of the refrigeration cycle device100, other than the refrigerant reservoir container, is the same as that in Embodiment 1, and therefore descriptions of the configuration are omitted. The same constituent elements as those in Embodiments 1 and 2 are denoted by the same reference signs, and descriptions thereof are appropriately omitted.

With reference toFIGS.8to10, the shielding plate4A is described below.FIG.8is a front view of the refrigerant reservoir container101B according to Embodiment 3. The solid-line arrows inFIG.8conceptually illustrate a refrigerant flow.FIG.9is a sectional view illustrating the B-B cross section ofFIG.8.FIG.10is a sectional view illustrating the C-C cross section ofFIG.8. As illustrated inFIGS.8and10, the shielding plate4A has a plurality of through holes6. Each of the through holes6has, for example, a round shape. Each of the through holes6may have an elliptical shape. All of the plurality of through holes6do not necessarily have the same shape or the same size. Note that in the container body1A in the present embodiment, the B-B cross section illustrated inFIG.8, in which the through holes6are not provided, is identical to the A-A cross section of the container body1A illustrated inFIG.6in Embodiment 2. Therefore,FIGS.7and9illustrate the identical cross-sectional view.

As illustrated inFIG.8, the plurality of through holes6are provided at the same height position in the up-down direction of the container body1A. As illustrated inFIG.10, the plurality of through holes6are provided in the circumferential direction of the shielding plate4A. Note that whileFIG.10illustrates two through holes6, it is sufficient that one or more through holes6are provided. In the up-down direction of the container body1A, another through hole6may be provided at a different height position in addition to the plurality of through holes6provided at the same height position.

In the container body1A, the volume of accumulating liquid refrigerant that exceeds the volume of the third region SP3accumulates in the first region SP1and the second region SP2. When the liquid refrigerant accumulates in the first region SP1, the second region SP2, and the third region SP3, the pressure in the second region SP2is higher than the pressure in the first region SP1. This causes pulsation of the refrigerant between the first region SP1and the second region SP2. However, since the shielding plate4is provided with the through holes6in the present embodiment, gas refrigerant flows into the first region SP1from the second region SP2through the through holes6. This suppresses an increase in the pressure in the second region SP2. Therefore, pulsation of the refrigerant between the first region SP1and the second region SP2is suppressed.

In the refrigerant reservoir container101B according to the present embodiment, the shielding plate4A has the through holes6, and the first region SP1and the second region SP2communicate with each other through the through holes6. With this configuration, gas refrigerant flowing into the second region SP2passes through the through holes6and enters the first region SP1. This reduces variations in the pressure in the container body1A, and as a consequence, suppresses pulsation of the refrigerant.

In the refrigerant reservoir container101B according to the present embodiment, the shielding plate4A has the plurality of through holes6. At least two or more of the plurality of through holes6are provided at the same height position in the up-down direction of the container body1A. With this configuration, gas refrigerant flows more efficiently from the second region SP2to the first region SP1, compared to a configuration in which the through holes6are arranged in a line in the up-down direction of the container body1A.

While Embodiments 1 to 3 have been described above, the refrigerant reservoir containers101,101A, and101B, and the refrigeration cycle device100are not limited to Embodiments 1 to 3 described above. Various modifications and applications can be made without departing from the summary of the present disclosure. For example, the refrigerant reservoir container may employ a configuration in which the container body1in Embodiment 1 is provided with the shielding plate4in Embodiment 2. For another example, the refrigerant reservoir container may employ a configuration in which the container body1A in Embodiment 2 is provided with the inflow pipe2in Embodiment 1. Embodiments 1 to 3 can be combined with each other within the range not impairing the functions or structures of each of Embodiments 1 to 3.