Liquid receiver

Abstract

This liquid receiver (10) comprises: a cylindrical container part (20) having a predetermined axial center (CL); a refrigerant introduction part (30) for introducing a refrigerant into an internal space of the container part; and a refrigerant lead-out part (40) including a discharge pipe part (41) for leading out the liquid-phase refrigerant stored in the internal space to the outside of the internal space.　The refrigerant introduction part has: a supply pipe part (31) that guides the refrigerant to the inside of the container part; and a jetting part (32, 32A) connected to the supply pipe part and including a jet opening (323) for jetting the refrigerant flowing through the supply pipe part into the internal space. The opening area of the jet opening is larger than the passage cross-sectional area of the supply pipe part.

Description

Receiver CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2024-099789, filed on June 20, 2024, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to a liquid receiver that is applied to an apparatus that constitutes a vapor compression refrigeration cycle.

[0003] This type of receiver functions not only as a gas-liquid separator that separates the refrigerant that has passed through the condenser into gas and liquid phases, but also as a liquid storage section that temporarily stores the separated liquid phase refrigerant. Known receivers are those that set the refrigerant ejection direction away from the center of the receiver to prevent disturbance of the liquid phase refrigerant level when the refrigerant that has passed through the condenser is ejected inside the receiver (see, for example, Patent Document 1).

[0004] Japanese Patent Application Laid-Open No. 2021-169881

[0005] In a refrigeration cycle, increasing the flow rate of the refrigerant circulating within the cycle can improve the heat dissipation and heat absorption performance. However, when the receiver is compact, as in Patent Document 1, increasing the flow rate of the refrigerant flowing through the cycle creates a trade-off: the gas-liquid separation performance of the receiver is reduced.

[0006] An object of the present disclosure is to provide a receiver that can ensure gas-liquid separation performance while being miniaturized.

[0007] According to one aspect of the present disclosure, the receiver is applied to an apparatus that constitutes a vapor compression refrigeration cycle, and comprises: a cylindrical container portion having a predetermined axis; a refrigerant inlet portion that introduces a refrigerant into an internal space of the container portion; and a refrigerant outlet portion that includes a discharge pipe portion that discharges the refrigerant in a liquid phase state stored in the internal space to the outside of the internal space, wherein the refrigerant inlet portion has: a supply pipe portion that introduces the refrigerant into the container portion; and an ejection portion that is connected to the supply pipe portion and includes an ejection opening portion for ejecting the refrigerant flowing through the supply pipe portion into the internal space, and the opening area of ​​the ejection opening portion is larger than the flow path cross-sectional area of ​​the supply pipe portion.

[0008] As the refrigerant flow rate increases, the refrigerant flow velocity also increases. When refrigerant with a high flow velocity is sprayed into the internal space of the container, the liquid and gas phase refrigerant stored inside the receiver tend to be agitated, and the liquid level tends to fluctuate. These factors can reduce the gas-liquid separation performance of the receiver.

[0009] In contrast, in the receiver of the present disclosure, the opening area of ​​the ejection opening is larger than the flow cross-sectional area of ​​the supply pipe. This reduces the flow velocity of the refrigerant ejected into the internal space of the container, suppressing agitation of the liquid and gas refrigerant stored inside the receiver and fluctuations in the liquid level, making it easier to ensure the gas-liquid separation performance of the receiver. In addition, the receiver can be made smaller than when both the opening area of ​​the ejection opening and the flow cross-sectional area of ​​the supply pipe are increased.

[0010] Therefore, according to the receiver of the present disclosure, it is possible to ensure gas-liquid separation performance while achieving miniaturization.

[0011] 1 is a schematic configuration diagram of a refrigeration cycle apparatus including a receiver according to a first embodiment. FIG. 1 is a schematic perspective sectional view of the receiver according to the first embodiment. FIG. 1 is a schematic sectional view of the receiver according to the first embodiment. FIG. 2 is a schematic perspective view of the jetting portion of the receiver according to the first embodiment. FIG. 3 is an explanatory view for explaining the relationship between the flow path cross-sectional area of ​​the supply pipe section and the opening area of ​​the jetting opening. FIG. 4 is a sectional view taken along VI-VI of FIG. 3. FIG. 5 is an explanatory view for explaining the flow pattern of refrigerant in the receiver according to a first modified example of the first embodiment. FIG. 6 is an explanatory view for explaining the arrangement of a desiccant in a receiver according to a first modified example of the first embodiment. FIG. 7 is a schematic perspective sectional view of the receiver according to a second embodiment. FIG. 8 is a schematic sectional view of the receiver according to the second embodiment. FIG. 9 is a schematic perspective view of the jetting portion of the receiver according to a first modified example of the second embodiment. FIG. 10 is a schematic perspective sectional view of the receiver according to a third embodiment. FIG. 11 is a schematic sectional view of the receiver according to the third embodiment. FIG. 12 is a schematic sectional view of the receiver according to the third embodiment. FIG. 13 is a schematic perspective view of the jetting portion of the receiver according to the third embodiment. FIG. 14 is an explanatory view for explaining the arrangement of a desiccant in a receiver according to a first modified example of the third embodiment.

[0012] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, parts that are the same as or equivalent to those described in the preceding embodiments will be given the same reference numerals, and their description may be omitted. Furthermore, in the embodiments, when only some of the components are described, the components described in the preceding embodiments can be applied to the remaining components. The following embodiments can be partially combined with each other, as long as there is no particular problem with the combination, even if not specifically stated.

[0013] First Embodiment This embodiment will be described with reference to Figures 1 to 7. In this embodiment, an example will be described in which a liquid receiver 10 according to the present disclosure is applied to a refrigeration cycle apparatus 1, which is one of the devices constituting a vapor compression refrigeration cycle.

[0014] The refrigeration cycle device 1 is applied to, for example, a vehicle air conditioner mounted on an electric vehicle that obtains driving power for the vehicle from an electric motor. The refrigeration cycle device 1 functions as an air conditioner that adjusts the temperature of air blown into the vehicle cabin, which is the space to be air-conditioned, and also functions as a cooling device for the battery that supplies power to the electric motor for vehicle driving.

[0015] The refrigeration cycle apparatus 1 employs, for example, an HFC refrigerant as a refrigerant. The refrigeration cycle apparatus 1 of this embodiment configures a subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 2 does not exceed the critical pressure of the refrigerant. Refrigerant oil is mixed into the refrigerant to lubricate the compressor 2. A portion of the refrigerant oil circulates within the cycle together with the refrigerant. Note that a refrigerant other than an HFC refrigerant may be employed.

[0016] As shown in Fig. 1, the refrigeration cycle device 1 is configured as a vapor compression refrigeration cycle in which evaporated refrigerant is compressed by a compressor 2. In addition to the compressor 2, the refrigeration cycle device 1 includes a condenser 3, a receiver 10, a subcooler 4, a first expansion valve 5, an indoor evaporator 6, a second expansion valve 7, a chiller 8, and an evaporation pressure regulating valve 9.

[0017] In the refrigeration cycle apparatus 1, the compressor 2 draws in refrigerant and discharges the compressed refrigerant toward the condenser 3. The compressor 2 is an electric compressor whose refrigerant discharge capacity is controlled by a control signal output from an air conditioning control unit (not shown). The condenser 3 is connected downstream of the compressor 2 in the refrigerant flow. The condenser 3 is a radiator that condenses the refrigerant by dissipating heat through heat exchange with a gas or liquid heat medium. The receiver 10 is connected downstream of the condenser 3 in the refrigerant flow. The receiver 10 separates the refrigerant that has passed through the condenser 3 into gas and liquid phases and stores a portion of the separated liquid-phase refrigerant. The receiver 10 has a refrigerant outlet for discharging the liquid-phase refrigerant. Details of the receiver 10 will be described later.

[0018] The supercooler 4 is connected to the refrigerant outlet side of the receiver 10. The supercooler 4 is a radiator that dissipates heat by exchanging heat between the liquid-phase refrigerant that has passed through the receiver 10 and a gas or liquid heat medium. The refrigerant is cooled and its temperature is reduced by the heat exchange with the heat medium in the supercooler 4. The condenser 3 and the supercooler 4 may be configured as an integrated heat exchanger or as separate heat exchangers.

[0019] A branching section BP1 that branches the refrigerant flow is provided on the refrigerant outlet side of the subcooler 4. This branching section BP1 is provided with a first expansion valve 5 on one outlet side and a second expansion valve 7 on the other outlet side. The first expansion valve 5 and the second expansion valve 7 are pressure reducing devices that reduce the pressure of the refrigerant in a liquid phase. The first expansion valve 5 and the second expansion valve 7 are configured as solenoid valves whose throttle openings can be controlled by control signals output from an air conditioning control unit (not shown).

[0020] The first expansion valve 5 functions as a pressure reducing unit that reduces the pressure of the refrigerant flowing into the interior evaporator 6, which is connected downstream of the first expansion valve 5 in the refrigerant flow direction, and as a flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing into the interior evaporator 6. In this embodiment, the first expansion valve 5 is configured to be fully closable. The interior evaporator 6 is a heat absorber that evaporates the refrigerant decompressed by the first expansion valve 5 by heat exchange with the air being blown into the vehicle cabin. In other words, the interior evaporator 6 is a cooling heat exchanger that cools the air being cooled, which is the fluid to be cooled, using the latent heat of vaporization of the refrigerant after passing through the first expansion valve 5. The inlet side of the evaporation pressure adjustment valve 9 is connected to the refrigerant outlet side of the interior evaporator 6. The evaporation pressure adjustment valve 9 is a pressure adjusting unit that maintains the refrigerant evaporation pressure in the interior evaporator 6 at or above a predetermined reference pressure. The evaporation pressure adjustment valve 9 is configured as a mechanical variable throttle mechanism that increases its valve opening as the refrigerant pressure at the refrigerant outlet side of the interior evaporator 6 increases. The evaporation pressure regulating valve 9 is adapted to maintain the refrigerant evaporation temperature in the indoor evaporator 6 at or above a reference temperature (e.g., 1°C) that can suppress frost formation on the indoor evaporator 6. A junction BP2 is connected to the refrigerant outlet side of the evaporation pressure regulating valve 9. This junction BP2 merges the refrigerant flowing out from the evaporation pressure regulating valve 9 and the refrigerant flowing out from the chiller 8. The refrigerant outlet side of the junction BP2 is connected to the refrigerant suction side of the compressor 2.

[0021] The second expansion valve 7 functions as a pressure reducing section that reduces the pressure of the refrigerant to be flowed into the chiller 8, which is connected downstream of the second expansion valve 7 in the refrigerant flow, and also functions as a flow rate adjusting section that adjusts the flow rate of the refrigerant to be flowed into the chiller 8. In this embodiment, the second expansion valve 7 is configured to be fully closable. The chiller 8 is a heat absorber that evaporates the refrigerant by exchanging heat with a heat medium that adjusts the temperature of on-board equipment such as a battery, with the refrigerant decompressed by the second expansion valve 7. A junction BP2 is connected to the refrigerant outlet side of the chiller 8. The refrigerant outlet side of the junction BP2 is connected to the refrigerant suction side of the compressor 2.

[0022] The refrigeration cycle apparatus 1 configured in this manner has a plurality of heat absorbers, such as the indoor evaporator 6 and the chiller 8, connected in parallel. The refrigeration cycle apparatus 1 is configured to be switchable between a multi-operation mode in which a refrigerant is supplied to each of the plurality of heat absorbers connected in parallel, and a single operation mode in which a refrigerant is supplied to one of the plurality of heat absorbers.

[0023] If the refrigerant discharge rate from compressor 2 is the same in multi-operation mode and single-operation mode, the flow rate of refrigerant passing through each of indoor evaporator 6 and chiller 8 in multi-operation mode will be significantly lower than in single-operation mode. For this reason, in multi-operation mode, it is necessary to increase the refrigerant discharge capacity of compressor 2 and increase the flow rate of refrigerant flowing in the cycle compared to single-operation mode, thereby ensuring heat absorption and heat release performance.

[0024] Furthermore, in the refrigeration cycle apparatus 1, in consideration of mountability in a vehicle, the receiver 10 may be made smaller by reducing its aspect ratio, etc. However, when attempting to make the receiver 10 smaller, there is a trade-off in that if the flow rate of the refrigerant circulating in the cycle is increased, the gas-liquid separation performance of the receiver 10 will be reduced.

[0025] In consideration of these factors, the receiver 10 of this embodiment is configured to ensure gas-liquid separation performance while being compact. The specific configuration of the receiver 10 of this embodiment will be described below with reference to Figures 2 to 5. As shown in Figures 2 and 3, the receiver 10 includes a container 20, a refrigerant inlet 30, and a refrigerant outlet 40.

[0026] The container 20 constitutes the outer shell of the receiver 10. The internal space IS of the container 20 functions as a storage space for temporarily storing the refrigerant in a liquid phase. The internal space IS of the container 20 is a space surrounded by an upper wall 20a, a lower wall 20b, and a side wall 20c connecting the upper wall 20a and the lower wall 20b of the container 20. In other words, the internal space IS of the container 20 is formed by the upper wall 20a, the lower wall 20b, and the side wall 20c.

[0027] The container 20 is composed of a cylindrical member having a predetermined axis CL. The container 20 of this embodiment has a circular cross section to ensure pressure resistance. Specifically, the container 20 includes a cylindrical portion 21, a disk-shaped top plate 22 that closes the opening at the upper end of the cylindrical portion 21, and a disk-shaped bottom plate 23 that closes the opening at the lower end of the cylindrical portion 21. The container 20 is constructed, for example, by hermetically joining the top plate 22 to a member in which the cylindrical portion 21 and the bottom plate 23 are integrally molded, by welding or the like. The top plate 22 is formed with a first through hole 221 and a second through hole 222 that penetrate from the front to the back. The first through hole 221 and the second through hole 222 are formed at positions different from the axis CL of the container 20.

[0028] Although not shown, a pipe through which the refrigerant that has passed through the condenser 3 flows is connected to the upper opening of the first through hole 221 via an adapter, and a refrigerant inlet 30 is connected to the lower opening by joining means such as press-fitting or welding. Furthermore, although not shown, a pipe through which the refrigerant flows to the subcooler 4 is connected to the upper opening of the second through hole 222 via an adapter, and a refrigerant outlet 40 is connected to the lower opening by joining means such as press-fitting or welding. As a result, in the receiver 10, the refrigerant that has passed through the condenser 3 flows to the subcooler 4 via the receiver 10.

[0029] The refrigerant introduction section 30 is a member that introduces the refrigerant into the internal space IS of the container section 20. The refrigerant introduction section 30 has a supply pipe section 31 that introduces the refrigerant into the container section 20, and an ejection section 32 that is connected to the supply pipe section 31 and ejects the refrigerant flowing through the supply pipe section 31 into the internal space IS.

[0030] The supply pipe section 31 is formed of a pipe through which the refrigerant flows. The supply pipe section 31 is arranged so that at least a portion thereof extends linearly along the vertical direction Dg inside the container section 20. The length of the supply pipe section 31 in the vertical direction Dg is equal to or greater than half the length of the internal space IS of the container section 20 in the vertical direction Dg. The supply pipe section 31 also has a substantially constant flow path cross-sectional area. In this embodiment, the supply pipe section 31 constitutes a "vertical section" through which the refrigerant flows along the vertical direction Dg. The upper end of the supply pipe section 31 is connected to the first through-hole 221. The ejection section 32 is connected to the lower end of the supply pipe section 31. The flow path cross-sectional area is the area of ​​a region surrounded by an inner wall that forms the flow path, and is calculated, for example, as the area of ​​a cross section perpendicular to the main flow direction of the fluid flowing through the flow path.

[0031] The jetting part 32 has a connection part 321 to which the lower end of the supply pipe part 31 is connected, a flow path forming part 322 that forms a refrigerant flow path through which the refrigerant flows from the supply pipe part 31, and an jetting opening part 323 for jetting into the internal space IS of the container part 20. The jetting part 32 is configured as an integrally molded product in which the connection part 321, the flow path forming part 322, and the jetting opening part 323 are integrally molded.

[0032] 4 and 5 , the connection portion 321 is a cylindrical portion that protrudes upward. The lower end of the supply pipe portion 31 is connected to the connection portion 321 by connection means such as press-fitting or welding. The connection portion 321 is provided at the upper part of the flow path forming portion 322.

[0033] The flow path forming portion 322 has a substantially semicircular outer shape. The flow path forming portion 322 has an inlet portion 322a near the center of the arc, which receives the refrigerant from the supply pipe portion 31 via the connection portion 321. The inlet portion 322a is bent so that the flow direction of the refrigerant is redirected from the vertical direction Dg to a direction intersecting the vertical direction. This intersecting direction is closer to the horizontal direction Dh than the vertical direction Dg. Specifically, the inlet portion 322a is bent in an L-shape so that the direction of the refrigerant flowing from the supply pipe portion 31 is redirected. That is, the inlet portion 322a is bent so that the direction of the refrigerant flowing from the supply pipe portion 31 is redirected to a substantially horizontal direction. In this embodiment, the inlet portion 322a of the flow path forming portion 322 constitutes a "bent portion" that allows the refrigerant to flow in a direction intersecting the vertical direction Dg.

[0034] Furthermore, a plurality of ejection flow paths 322b extending radially from the inlet portion 322a toward the outer edge of the arc are formed in the flow path forming portion 322. The plurality of ejection flow paths 322b extend in a direction away from the axis CL of the container portion 20. In this example, seven ejection flow paths 322b are formed in the flow path forming portion 322, but the number of ejection flow paths 322b may be six or less, or eight or more.

[0035] Each ejection flow path 322b extends toward the side wall 20c so that at least a portion of the refrigerant flowing through the ejection flow path 322b collides with the side wall 20c of the container 20. The upstream side of the ejection flow paths 322b in the refrigerant flow direction communicates with the inlet 322a, and the downstream side of the refrigerant flow direction communicates with the ejection opening 323. In this embodiment, the ejection flow paths 322b constitute an "extension portion" through which the refrigerant that has passed through the inlet 322a, which constitutes a "bent portion," flows and extends in a direction away from the axis CL.

[0036] The ejection opening 323 is formed of a plurality of ejection holes 323a that open at the downstream ends of the ejection flow paths 322b in the refrigerant flow direction. As shown in Fig. 5, the opening area of ​​the ejection opening 323 is larger than the flow path cross-sectional area of ​​the supply pipe portion 31.

[0037] Here, the opening area of ​​the ejection opening 323 is the sum of the opening areas of the ejection holes 323a. For example, if the opening of each ejection hole 323a is a square with one side of 6 mm, the opening area of ​​each ejection hole 323a is 36 mm. ２ multiplied by the numerical aperture "7", that is, 252 mm ２ When the inner diameter of the supply pipe 31 is 6 mm, the flow path cross-sectional area of ​​the supply pipe 31 is approximately 28.3 mm ２ In this case, the opening area of ​​the jetting opening 323 is sufficiently larger than the cross-sectional area of ​​the flow path in the supply pipe portion 31.

[0038] In the present embodiment, the ejection opening 323 has each ejection hole 323a formed such that the opening direction faces the side wall 20c of the container 20. As shown in Fig. 6 , the ejection opening 323 is formed in a portion of the flow path forming portion 322 facing the side wall 20c so that the distance La from the side wall 20c of the container 20 is constant. Specifically, the ejection opening 323 has each ejection hole 323a formed such that it faces a portion of the side wall 20c that is below the middle position in the vertical direction Dg. Furthermore, the ejection opening 323 has each ejection hole 323a positioned closer to the side wall 20c than the axis CL of the container 20 so that the refrigerant ejected from each ejection hole 323a is more likely to collide with the side wall 20c. That is, the distance La from each ejection hole 323 a to the side wall portion 20 c is smaller than the distance from each ejection hole 323 a to the axis CL of the container portion 20 .

[0039] The refrigerant outlet 40 is a member that discharges the liquid-phase refrigerant present in the internal space IS of the container 20 to the outside of the internal space IS. The refrigerant outlet 40 has a discharge pipe 41 that discharges the refrigerant to the outside of the container 20.

[0040] The discharge pipe 41 is formed of a pipe through which the refrigerant flows. The discharge pipe 41 is arranged so that at least a portion thereof extends linearly along the vertical direction Dg inside the container 20. The length of the discharge pipe 41 in the vertical direction Dg is equal to or greater than half the length of the internal space IS of the container 20 in the vertical direction Dg. The upper end of the discharge pipe 41 is connected to the second through-hole 222. A suction port 411 is formed at the lower end of the discharge pipe 41. Although not shown, a filter for removing foreign matter is provided at the lower end of the discharge pipe 41.

[0041] The discharge pipe section 41 in this embodiment is disposed at a position opposite the supply pipe section 31 across the axis CL. Furthermore, the discharge pipe section 41 has an opening position of the suction port 411 set at a position closer to the axis CL than the opening position of the ejection opening 323. For example, the discharge pipe section 41 has a distance R1 from the axis CL to the suction port 411 that is shorter than a distance R2 from the axis CL to the opening position of the ejection opening 323. In other words, when an imaginary circle IC is defined as a circle having a radius equal to the distance R2 from the axis CL to the opening position of the ejection opening 323, the suction port 411 of the discharge pipe section 41 is set inside the imaginary circle IC.

[0042] Furthermore, the opening position of the suction port 411 of the discharge pipe section 41 is set at a position not higher than the opening position of the ejection opening 323. That is, the opening position of the suction port 411 of the discharge pipe section 41 is set at a position similar to or lower than the opening position of the ejection opening 323.

[0043] Here, the lower side of the internal space IS of the container 20 is filled with liquid-phase refrigerant, and the upper side is filled with gas-phase refrigerant. The height of the liquid-phase refrigerant stored in the internal space IS of the container 20 varies depending on the operating state of the refrigeration cycle device 1. When the refrigeration cycle device 1 is operating normally, the height of the liquid-phase refrigerant fluctuates within a range that does not fall below a predetermined lower limit position. This "lower limit position" is a height position that is the lowest limit that is presumed in advance in accordance with the appropriate amount of refrigerant to be charged in the refrigeration cycle device 1.

[0044] In the present embodiment, the opening position of the suction port 411 of the discharge pipe section 41 is set at a position not higher than the lower limit position. That is, the opening position of the suction port 411 of the discharge pipe section 41 is set at a position similar to or lower than the lower limit position.

[0045] In the refrigeration cycle apparatus 1 configured as above, when the compressor 2 is driven, the refrigerant is compressed in the compressor 2 to a high pressure and then discharged. The refrigerant compressed in the compressor 2 is condensed by heat exchange with the heat medium as it passes through the condenser 3. The refrigerant that has passed through the condenser 3 becomes a gas-liquid two-phase state and is supplied to the receiver 10.

[0046] 7, in the receiver 10, the refrigerant flows downward through the supply pipe 31, and then the flow direction of the refrigerant is turned approximately horizontally at the inlet 322a of the jet portion 32, which forms the bent portion. Then, after passing through each jet flow path 322b of the jet portion 32, the refrigerant is jetted out of the multiple jet holes 323a of the jet opening 323 into the internal space IS of the container 20.

[0047] In the refrigerant introduction section 30 of this embodiment, the opening area of ​​the ejection opening 323 is larger than the flow path cross-sectional area of ​​the supply pipe section 31. Furthermore, the refrigerant introduction section 30 is configured to bend the direction of the refrigerant flowing down along the vertical direction Dg to a direction intersecting the vertical direction Dg. As a result, the flow velocity of the refrigerant ejected from the ejection opening 323 into the internal space IS is smaller than the flow velocity of the refrigerant passing through the supply pipe section 31.

[0048] Additionally, in the refrigerant introduction section 30, the ejection flow path 322b of the ejection section 32 extends toward the side wall 20c so that at least a portion of the refrigerant passing through the ejection flow path 322b collides with the side wall 20c of the container section 20. This reduces the kinetic energy of the refrigerant due to its collision with the side wall 20c, thereby suppressing agitation of the refrigerant and fluctuations in the liquid level.

[0049] The refrigerant ejected into the internal space IS of the container 20 is separated into gas and liquid in the internal space IS, and the liquid-phase refrigerant is stored in the internal space IS. The liquid-phase refrigerant stored in the internal space IS of the container 20 is then sucked through the suction port 411 of the discharge pipe 41 and then discharged to the outside via the discharge pipe 41, etc.

[0050] The liquid-phase refrigerant delivered from the receiver 10 is cooled by heat exchange with the heat medium in the subcooler 4. The refrigerant that has passed through the subcooler 4 is depressurized by at least one of the first expansion valve 5 and the second expansion valve 7, and then absorbs heat from the heat medium in at least one of the heat absorbers of the indoor evaporator 6 and the chiller 8 to evaporate. The refrigerant vaporized in at least one of the heat absorbers of the indoor evaporator 6 and the chiller 8 is drawn into the compressor 2 and compressed again.

[0051] In the receiver 10 described above, the opening area of ​​the jet opening 323 is larger than the flow path cross-sectional area of ​​the supply pipe 31. This reduces the flow velocity of the refrigerant jetted into the internal space IS of the container 20, suppressing agitation of the liquid and gas phase refrigerants stored inside the receiver 10 and fluctuations in the liquid level, making it easier to ensure the gas-liquid separation performance of the receiver 10. In addition, the receiver 10 of this embodiment can be made smaller than when both the opening area of ​​the jet opening 323 and the flow path cross-sectional area of ​​the supply pipe 31 are enlarged. Therefore, the receiver 10 of this embodiment can ensure gas-liquid separation performance while being compact.

[0052] The receiver 10 of this embodiment also has the following features: (1) The discharge pipe 41 includes a suction port 411 that draws in liquid-phase refrigerant present in the internal space IS of the receiver 10. The opening position of the suction port 411 is set at a position not higher than the opening position of the ejection opening 323. Accordingly, if the opening position of the suction port 411 of the discharge pipe 41 is set at a position not higher than the opening position of the ejection opening 323, refrigerant agitated by the refrigerant ejected from the ejection opening 323 is prevented from being drawn into the suction port 411 of the discharge pipe 41. Furthermore, if the opening position of the suction port 411 of the discharge pipe 41 is set at a lower position, liquid-phase refrigerant stored below the internal space IS of the receiver 10 is more easily drawn into the suction port 411.

[0053] (2) The refrigerant introduction section 30 includes the supply pipe section 31 as a vertical section through which the refrigerant flows along the vertical direction Dg, and the inlet section 322a as a bent section that changes the flow direction of the refrigerant from the vertical direction Dg to a direction intersecting the vertical direction Dg. This reduces the flow velocity of the refrigerant when it passes through the inlet section 322a that constitutes the bent section.

[0054] (3) The cross direction is closer to the horizontal direction Dh than to the vertical direction Dg, which reduces the flow velocity of the refrigerant when it passes through the inlet portion 322a that forms the bent portion.

[0055] (4) The container 20 has an internal space IS formed by an upper wall 20a, a lower wall 20b, and a side wall 20c connecting the upper and lower walls 20a and 20b. The refrigerant introduction section 30 includes a jet flow passage 322b extending away from the axial center CL, through which refrigerant flows after passing through the inlet 322a, which forms a bent portion. The jet flow passage 322b extends toward the side wall 20c so that at least a portion of the refrigerant passing through the jet flow passage 322b impinges on the side wall 20c. If the refrigerant introduction section 30 is configured to actively impinge the refrigerant against the side wall 20c of the container 20, the kinetic energy of the refrigerant can be reduced by the impingement of the refrigerant against the side wall 20c. This suppresses agitation of the liquid and gas refrigerants stored inside the receiver 10 and fluctuations in the liquid level, thereby ensuring sufficient gas-liquid separation performance of the receiver 10. It is preferable that the coolant introduction portion 30 is configured so that the coolant collides perpendicularly with the side wall portion 20c.

[0056] (5) The container 20 is disposed so that its axis CL extends along the vertical direction Dg. The outlet pipe 41 has an opening position of the suction port 411 that is closer to the axis CL than the opening position of the ejection opening 323. In this manner, if the suction port 411 of the outlet pipe 41 is disposed closer to the axis CL of the container 20, the influence of fluctuations in the liquid level when the liquid-phase refrigerant flows down along the side wall 20c of the container 20 can be suppressed.

[0057] (6) The ejection opening 323 has a plurality of ejection holes 323a that eject the refrigerant flowing through the ejection portion 32 into the internal space IS of the container 20. If the ejection opening 323 has a plurality of ejection holes 323a in this way, the opening area of ​​the ejection opening 323 can be increased, thereby reducing the flow rate of the refrigerant ejected into the internal space IS of the container 20.

[0058] (7) The ejection opening 323 is formed in a portion of the ejection flow passage 322b that constitutes the extension portion, facing the side wall 20c, so that the distance from the side wall 20c is constant. This allows the refrigerant ejected from the ejection opening 323 to collide with the side wall 20c regardless of the ejection position of the refrigerant, thereby reducing the flow velocity.

[0059] (First Modification of First Embodiment) As shown in Fig. 8 , in the receiver 10, a desiccant 50 that adsorbs moisture contained in the refrigerant is disposed in the internal space IS of the container 20. The desiccant 50 is configured by accommodating a desiccant such as a molecular sieve inside a felt bag. The desiccant 50 is disposed in a position that does not face the ejection opening 323 so that the refrigerant ejected from the ejection opening 323 does not directly impinge on the desiccant 50. Specifically, the desiccant 50 is disposed in the internal space IS of the container 20 at a position opposite the ejection portion 32 across the axis CL.

[0060] This allows the moisture in the refrigerant to be appropriately adsorbed by the desiccant 50. In addition, since the refrigerant injected from the ejection opening 323 is less likely to collide with the desiccant 50, deterioration of the desiccant 50 due to the collision of the refrigerant can be suppressed.

[0061] (Another Modification of the First Embodiment) In the first embodiment, the ejection section 32 has a plurality of ejection flow paths 322b that extend with a constant width so as to approach the side wall section 20c, but is not limited to this. In the ejection section 32, the flow path width of each ejection flow path 322b may increase as it approaches the side wall section 20c.

[0062] In the ejection unit 32 of the first embodiment, the flow path forming portion 322 has a substantially semicircular outer shape, but is not limited to this. The flow path forming portion 322 may have, for example, a fan-shaped outer shape. Furthermore, the flow path forming portion 322 may have slits penetrating from the front to the back between the multiple ejection flow paths 322b.

[0063] Second Embodiment Next, a second embodiment will be described with reference to Figures 9 to 11. In this embodiment, differences from the first embodiment will be mainly described.

[0064] As shown in Figures 9 and 10, the ejection section 32A is composed of a first plate section 301 that extends in a direction intersecting the vertical direction Dg, and a second plate section 302 that forms an ejection flow path 322b between the first plate section 301 and the second plate section 302, through which the refrigerant flows after passing through the supply pipe section 31.

[0065] As shown in FIG. 11 , the first plate portion 301 and the second plate portion 302 are formed of disk-shaped plate members of the same size. Specifically, the outer diameters of the first plate portion 301 and the second plate portion 302 are equal to or slightly smaller than the inner diameter of the side wall portion 20c. The first plate portion 301 and the second plate portion 302 are disposed inside the container portion 20 with their plate surfaces aligned along the horizontal direction Dh. The first plate portion 301 and the second plate portion 302 are also disposed side by side in the vertical direction Dg so as to overlap each other in the vertical direction Dg. In this embodiment, the first plate portion 301 is disposed above the second plate portion 302.

[0066] The first plate portion 301 and the second plate portion 302 are provided with a spacing defining portion 33 that defines the spacing between the first plate portion 301 and the second plate portion 302. The spacing defining portion 33 is composed of a first convex portion 331 provided on the surface of the first plate portion 301 facing the second plate portion 302 and a second convex portion 332 provided on the surface of the second plate portion 302 facing the first plate portion 301. The first convex portion 331 and the second convex portion 332 are arranged in positions that overlap each other in the vertical direction Dg. The spacing defining portion 33 of this embodiment is composed of the first convex portion 331 and the second convex portion 332 that are provided at positions corresponding to the axis CL. The first convex portion 331 and the second convex portion 332 are arranged in positions that overlap each other in the vertical direction Dg. The first plate portion 301 and the second plate portion 302 are in contact only at the first convex portion 331 and the second convex portion 332, and other portions are spaced apart at a substantially constant interval.

[0067] The first plate portion 301 has a connection hole 301a formed near the axis CL to which the supply pipe portion 31 is connected. The first plate portion 301 also has a first through hole 301b formed at a position different from the connection hole 301a, through which the discharge pipe portion 41 passes. The first plate portion 301 has a plurality of ejection holes 301c extending circumferentially at a portion located radially outward of the first through hole 301b. The ejection holes 301c are openings for directing the refrigerant flowing through the ejection flow passage 322b to above the ejection portion 32 in the internal space IS of the container portion 20 and for circulating the refrigerant between above and below the ejection portion 32 in the internal space IS of the container portion 20. In this embodiment, the ejection portion 32A has an inlet portion 322a near the connection hole 301a to which the supply pipe portion 31 is connected, which receives the refrigerant from the supply pipe portion 31.

[0068] The second plate portion 302 has a first through hole 301b formed therein in a position opposite the first through hole 301b in the vertical direction Dg, through which the discharge pipe portion 41 passes. The second plate portion 302 has a plurality of ejection holes 302b extending along the circumferential direction formed therein in a position opposite the ejection holes 301c of the first plate portion 301 in the vertical direction Dg. The ejection holes 302b are openings for guiding the refrigerant flowing through the ejection flow passage 322b below the ejection portion 32 in the internal space IS of the container portion 20, and for allowing the refrigerant to move back and forth between above and below the ejection portion 32 in the internal space IS of the container portion 20.

[0069] In this embodiment, the supply pipe section 31 and the discharge pipe section 41 are provided with a holding section 34 that holds the first plate section 301 and the second plate section 302. The holding section 34 is composed of a first enlarged diameter section 341 provided on the supply pipe section 31 and a second enlarged diameter section 342 provided on the discharge pipe section 41.

[0070] The first enlarged diameter portion 341 has an outer diameter larger than the hole diameter of the connection hole 301a. The first enlarged diameter portion 341 is formed, for example, by enlarging a portion of the supply pipe portion 31 by bulging. The second enlarged diameter portion 342 has an outer diameter larger than the hole diameter of the second through hole 302a. The second enlarged diameter portion 342 is formed, for example, by enlarging a portion of the discharge pipe portion 41 by bulging. The first plate portion 301 and the second plate portion 302 are held in the supply pipe portion 31 and the discharge pipe portion 41 by being sandwiched vertically by the first enlarged diameter portion 341 and the second enlarged diameter portion 342.

[0071] In the receiver 10 configured as described above, the refrigerant flows downward through the supply pipe 31, and then the flow direction of the refrigerant is redirected to a substantially horizontal direction at the inlet 322a of the jet portion 32, which forms the bent portion. As the refrigerant passes through the jet flow path 322b of the jet portion 32, at least a portion of the refrigerant collides with the side wall 20c and is jetted from the jet openings 301c and 302b into the internal space IS of the container 20. The refrigerant jetted into the internal space IS of the container 20 is separated into gas and liquid in the internal space IS, and the liquid-phase refrigerant is stored in the internal space IS. The liquid-phase refrigerant stored in the internal space IS of the container 20 is then sucked through the suction port 411 of the discharge pipe 41 and discharged to the outside via the discharge pipe 41, etc.

[0072] The other points are the same as those in the first embodiment. The receiver 10 of this embodiment can obtain the same effects as those in the first embodiment that are achieved by the configuration common to or equivalent to that of the first embodiment.

[0073] The receiver 10 of this embodiment has the following features: (1) The jet flow passage 322b of the refrigerant inlet 30 extends toward the side wall 20c so that at least a portion of the refrigerant passing through the jet flow passage 322b impinges on the side wall 20c. If the refrigerant inlet 30 is configured to actively impinge the refrigerant against the side wall 20c of the container 20, the kinetic energy of the refrigerant can be reduced by the refrigerant impinging on the side wall 20c. This suppresses agitation of the liquid and gas refrigerants stored inside the receiver 10 and fluctuations in the liquid level, thereby ensuring sufficient gas-liquid separation performance of the receiver 10.

[0074] (2) The ejection portion 32A includes a first plate portion 301 extending in a direction intersecting the vertical direction Dg, and a second plate portion 302 disposed opposite the first plate portion 301 and defining an ejection flow path 322b between the first plate portion 301 and the second plate portion 302, through which the refrigerant flows after passing through the supply pipe portion 31. An ejection opening 323 is formed downstream of the ejection flow path 322b in the refrigerant flow direction. This allows the ejection portion 32A to be configured with a simple structure.

[0075] (3) The ejection opening 323 is open in both the first plate portion 301 and the second plate portion 302. This makes it easier to increase the opening area of ​​the ejection opening 323. Furthermore, of the plate portions 301, 302, the refrigerant in a gas phase can be guided upward into the internal space IS through the ejection holes 301c provided in the upper plate portion, and the refrigerant in a liquid phase can be guided downward into the internal space IS through the ejection holes 302b provided in the lower plate portion.

[0076] (4) The flow path cross-sectional area of ​​the ejection section 32A at the position where the ejection opening 323 is provided is set to be greater than or equal to the flow path cross-sectional area of ​​the ejection flow path 322b, and the flow path cross-sectional area of ​​the ejection flow path 322b is set to be greater than or equal to the flow path cross-sectional area of ​​the supply pipe section 31.

[0077] As a result, the flow velocity of the refrigerant does not increase when passing through the ejection portion 32A, and therefore, refrigerant with a low flow velocity can be ejected from the ejection opening 323. The flow path cross-sectional area at the position where the ejection opening 323 is provided is the cross-sectional area in the vertical direction Dg of the flow path between the first plate portion 301 and the second plate portion 302 that is connected to the ejection opening 323.

[0078] (5) The supply pipe section 31 and the discharge pipe section 41 are provided with holding sections 34 that hold the first plate section 301 and the second plate section 302. In this manner, if the supply pipe section 31 and the discharge pipe section 41 are configured to hold the first plate section 301 and the second plate section 302, there is no need to add dedicated members for holding the respective plate sections 301, 302, and therefore an increase in the number of parts in the receiver 10 can be suppressed.

[0079] (6) The ejection portion 32A is provided with a spacing defining portion 33 that defines the spacing between the first plate portion 301 and the second plate portion 302. By providing the spacing defining portion 33 to the first plate portion 301 and the second plate portion 302 in this manner, there is no need to add a dedicated member for defining the spacing between the plate portions 301, 302, and therefore an increase in the number of parts in the receiver 10 can be suppressed.

[0080] (First Modification of Second Embodiment) The ejection unit 32A of the second embodiment is configured by a disk-shaped first plate portion 301 and a disk-shaped second plate portion 302. However, the ejection unit 32A is not limited to this. For example, as shown in Fig. 12 , the ejection unit 32A may be configured to include a substantially semicircular first plate portion 301, a second plate portion 302 having the same shape as the first plate portion 301, and a third plate portion 303 connecting the linearly extending outer edges of the first plate portion 301 and the second plate portion 302.

[0081] (Another modified example of the second embodiment) As in the second embodiment, it is desirable that the ejection portion 32A is composed of two plate portions, namely, the first plate portion 301 and the second plate portion 302, but this is not limited to this and it may be composed of three or more plate portions.

[0082] As in the second embodiment, it is desirable that the holding portion 34 be formed by an enlarged diameter portion provided in each of the pipe portions 31, 41, but this is not limited to this and the holding portion 34 may be formed by a member separate from each of the pipe portions 31, 41.

[0083] As in the second embodiment, it is desirable that the spacing regulating portion 33 be formed by a convex portion provided on each of the plate portions 301, 302, but this is not limited to this and the spacing regulating portion 33 may be formed by a member separate from each of the plate portions 301, 302.

[0084] In the second embodiment, the ejection part 32 has the ejection flow passage 322b extending toward the side wall 20c so that at least a portion of the refrigerant passing through the ejection flow passage 322b collides with the side wall 20c, but is not limited to this. The ejection part 32 may be configured so that the refrigerant after passing through the ejection flow passage 322b collides with the side wall 20c.

[0085] As in the second embodiment, it is desirable that the ejection holes 301c, 302b are formed in both the first plate portion 301 and the second plate portion 302, but this is not limiting, and the ejection holes 302b may be formed only in the second plate portion 302. Furthermore, the ejection holes 301c, 302b may be formed, for example, as round holes or angular holes, rather than as elongated holes extending along the outer edges of the plate portions 301, 302. Furthermore, the ejection holes 301c, 302b formed in the plate portions 301, 302 may have different shapes.

[0086] As in the second embodiment, the flow path cross-sectional area of ​​the ejection section 32A at the position where the ejection opening 323 is provided is preferably set to be equal to or larger than the flow path cross-sectional area of ​​the ejection flow path 322b, but this need not be the case. Also, the flow path cross-sectional area of ​​the ejection section 32A is preferably set to be equal to or larger than the flow path cross-sectional area of ​​the supply pipe section 31, but this need not be the case.

[0087] Third Embodiment Next, a third embodiment will be described with reference to Figures 13 to 15. In this embodiment, differences from the second embodiment will be mainly described.

[0088] As shown in Figures 13 and 14, the distance between the first plate portion 301 and the second plate portion 302 of the ejection portion 32A is set so that the flow path cross-sectional area at the position where the ejection opening 323 is provided is larger than the flow path cross-sectional area of ​​the ejection flow path 322b.

[0089] As shown in Figure 15, the first plate portion 301 has a first inner diameter portion IP1 including the axis CL, a first outer diameter portion OP1 located on the outer periphery of the first inner diameter portion IP1, and a first step portion SP1 for shifting the position of the first outer diameter portion OP1 relative to the first inner diameter portion IP1 upward in the vertical direction Dg.

[0090] Specifically, the first plate portion 301 has a connecting hole 301a and a first passing hole 301b formed in a first inner diameter portion IP1, and a jetting hole 301c that constitutes the jetting opening portion 323 formed in a first outer diameter portion OP1. The first step portion SP1 is set at a position that is outside the connecting hole 301a and the first passing hole 301b and inside the jetting hole 301c.

[0091] The second plate portion 302 has a second inner diameter portion IP2 including the axis CL, a second outer diameter portion OP2 located on the outer peripheral side of the second inner diameter portion IP2, and a second step portion SP2 for shifting the position of the second outer diameter portion OP2 downward in the vertical direction Dg with respect to the second inner diameter portion IP2. The first plate portion 301 and the second plate portion 302 are arranged so that the distance between the outer diameter portions OP1 and OP2 is larger than the distance between the inner diameter portions IP1 and IP2.

[0092] Specifically, the second plate portion 302 has a second passing hole 302a formed in a second inner diameter portion IP2, and ejection holes 302b that form the ejection opening portion 323 formed in a second outer diameter portion OP2. The second step portion SP2 is set at a position that is outside the second passing hole 302a and inside the ejection holes 302b.

[0093] As a result, in the jetting section 32A of this embodiment, the flow path cross-sectional area at the position where the jetting opening 323 is provided is larger than the flow path cross-sectional area of ​​the jetting flow path 322b. Also, in the jetting section 32A, the flow path cross-sectional area of ​​the jetting flow path 322b is larger than the flow path cross-sectional area of ​​the supply pipe section 31.

[0094] The other points are the same as those in the second embodiment. The receiver 10 of this embodiment can obtain the same effects as those in the second embodiment that are achieved by the common configuration or the equivalent configuration to that in the second embodiment.

[0095] The receiver 10 of this embodiment has the following features: (1) The jet section 32A is designed so that the cross-sectional area of ​​the jet flow path 322b at the position where the jet opening 323 is provided is larger than the cross-sectional area of ​​the jet flow path 322b, which is designed so that the cross-sectional area of ​​the jet flow path 322b is larger than the cross-sectional area of ​​the supply pipe section 31. This reduces the flow velocity of the refrigerant jetted from the jet opening 323.

[0096] (2) The distance between the first plate 301 and the second plate 302 of the ejection section 32A is set so that the cross-sectional area of ​​the flow path at the position where the ejection opening 323 is provided is larger than the cross-sectional area of ​​the flow path of the ejection flow path 322b. This reduces the flow velocity of the refrigerant passing through the ejection section 32A, so that the refrigerant with a low flow velocity can be ejected from the ejection opening 323.

[0097] (First variant of the third embodiment) When placing the desiccant 50 in the internal space IS of the container portion 20, it is desirable that the desiccant 50 be placed in a position that does not face the ejection opening 323 so that the refrigerant ejected from the ejection opening 323 does not directly collide with the desiccant 50.

[0098] 16, the desiccant 50 can be placed above the ejection portion 32A in the internal space IS of the container 20. The desiccant 50 may also be placed below the ejection portion 32A in the internal space IS of the container 20.

[0099] This allows the moisture in the refrigerant to be appropriately adsorbed by the desiccant 50. In addition, since the refrigerant injected from the ejection opening 323 is less likely to collide with the desiccant 50, deterioration of the desiccant 50 due to the collision of the refrigerant can be suppressed.

[0100] (Other Modifications of the Third Embodiment) In the third embodiment, a step portion is provided on both the first plate portion 301 and the second plate portion 302, but the first plate portion 301 and the second plate portion 302 are not limited to this. A step portion may be formed on only one of the first plate portion 301 and the second plate portion 302.

[0101] The holding portion 34 of the third embodiment is configured with enlarged diameter portions 341, 342 provided on both the supply pipe portion 31 and the discharge pipe portion 41, but is not limited to this. For example, as shown in FIG. 16 , the holding portion 34 may be configured with two enlarged diameter portions 342a, 342b provided on the discharge pipe portion 41 of the supply pipe portion 31 and the discharge pipe portion 41 and a reduced diameter portion 20d provided on the side wall portion 20c of the container portion 20. Furthermore, the two enlarged diameter portions 342a, 342b provided on the discharge pipe portion 41 may function as the distance defining portion 33 that defines the distance between the first plate portion 301 and the second plate portion 302. In this case, the convex portions of the first plate portion 301 and the second plate portion 302 can be omitted.

[0102] In the third embodiment, the first plate portion 301 and the second plate portion 302 have their outer diameter portions OP1 and OP2 extending along the horizontal direction Dh so that their outer peripheral ends are perpendicular to the side wall portion 20c. However, this is not limiting. For example, as shown in Fig. 16, the first plate portion 301 and the second plate portion 302 may be configured so that the outer peripheral ends of the outer diameter portions OP1 and OP2 extend along the vertical direction Dg. This stabilizes the posture of the first plate portion 301 and the second plate portion 302.

[0103] Other Embodiments Although typical embodiments of the present disclosure have been described above, the present disclosure is not limited to the above-described embodiments and can be modified in various ways, for example, as follows.

[0104] As in the above-described embodiment, it is desirable that the opening position of the suction port 411 be set at a position not higher than the opening position of the ejection opening 323, but this is not limited to this, and the opening position of the suction port 411 may be set at a position higher than the opening position of the ejection opening 323.

[0105] As in the above-described embodiment, the refrigerant introduction section 30 is preferably configured to redirect the refrigerant flow direction from the vertical direction to a substantially horizontal direction, but is not limited thereto and may be configured to redirect the refrigerant flow direction to a direction that intersects the vertical direction at an angle. Note that the refrigerant introduction section 30 desirably includes a bent portion that redirects the refrigerant flow direction from the vertical direction to a direction that intersects the vertical direction, but this is not required.

[0106] As in the above-described embodiment, it is desirable that the ejection flow passage 322b extend toward the side wall portion 20c so that the refrigerant passing through it or that has passed through it collides with the side wall portion 20c, but this does not have to be the case.

[0107] As in the above-described embodiment, it is desirable that the opening position of the suction port 411 of the exhaust pipe section 41 be set at a position closer to the axis CL than the opening position of the ejection opening 323, but this does not have to be the case.

[0108] As in the first embodiment, the ejection opening 323 preferably has a plurality of ejection holes 323a for ejecting the refrigerant flowing through the ejection portion 32 into the internal space IS, but this is not essential.

[0109] As in the above-described embodiment, it is desirable that the ejection opening 323 be formed in a portion of the ejection flow path 322b facing the side wall portion 20c so that the distance from the side wall portion 20c is constant, but this does not have to be the case.

[0110] In the above embodiment, the detailed structure of the components of the receiver 10 is described, but the components of the receiver 10 are not limited to those described above, and some of them may be different from those described above.

[0111] In the above embodiment, an example has been described in which the receiver 10 of the present disclosure is applied to a refrigeration cycle apparatus 1 that can switch between a multi-operation mode and a single-operation mode, but the receiver 10 can also be applied to apparatuses other than those described above. For example, the receiver 10 can also be applied to a refrigeration cycle apparatus 1 that cannot switch between a multi-operation mode and a single-operation mode.

[0112] In the above-described embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential unless they are specifically stated as essential or are clearly considered essential in principle.

[0113] In the above-described embodiments, when numerical values ​​such as the number, values, amounts, ranges, etc. of components of the embodiments are mentioned, they are not limited to the specific numbers unless they are expressly stated as being essential or are clearly limited to a specific number in principle.

[0114] In the above-described embodiments, when referring to the shapes, positional relationships, etc. of components, etc., the shapes, positional relationships, etc. are not limited to those unless otherwise specified or when they are limited in principle to specific shapes, positional relationships, etc.

[0115] [Aspects of the present disclosure] [First aspect] A receiver applicable to an apparatus (1) constituting a vapor compression refrigeration cycle, comprising: a cylindrical container portion (20) having a predetermined axis (CL); a refrigerant introduction portion (30) that introduces a refrigerant into an internal space of the container portion; and a refrigerant discharge portion (40) including a discharge pipe portion (41) that discharges a liquid phase refrigerant stored in the internal space to the outside of the internal space, wherein the refrigerant introduction portion has: a supply pipe portion (31) that introduces the refrigerant into the container portion; and a jet portion (32, 32A) that is connected to the supply pipe portion and includes a jet opening (323) for jetting the refrigerant flowing through the supply pipe portion into the internal space, wherein the opening area of ​​the jet opening is larger than the flow path cross-sectional area of ​​the supply pipe portion. [Second Aspect] The receiver according to the first aspect, wherein the discharge pipe portion includes a suction port (411) that draws in the refrigerant in a liquid phase present in the internal space, and the opening position of the suction port is set at a position not higher than the opening position of the ejection opening. [Third Aspect] The receiver according to the first or second aspect, wherein the refrigerant introduction portion includes a vertical portion (31) that causes the refrigerant to flow vertically, and a bent portion (322a) that changes the flow direction of the refrigerant from the vertical direction to an intersecting direction that intersects the vertical direction. [Fourth Aspect] The receiver according to the third aspect, wherein the intersecting direction is closer to the horizontal direction than to the vertical direction. [Fifth Aspect] The receiver according to the third or fourth aspect, wherein the internal space of the container is formed by an upper wall (20a), a lower wall (20b), and a side wall (20c) connecting the upper and lower wall portions, the refrigerant introduction portion includes an extension portion (322b) through which the refrigerant that has passed through the bent portion flows and which extends in a direction away from the axial center, and the extension portion extends toward the side wall portion so that at least a portion of the refrigerant that passes through or has passed through the extension portion collides with the side wall portion. [Sixth Aspect] The receiver according to the second aspect, wherein the container is arranged so that the axial center extends along the vertical direction, and the opening position of the suction port of the discharge pipe portion is set at a position closer to the axial center than the opening position of the ejection opening.[Seventh Aspect] The receiver according to any one of the first to sixth aspects, wherein the jet opening has a plurality of jet holes (323a) for jetting the refrigerant flowing through the jet portion into the internal space. [Eighth Aspect] The receiver according to any one of the fifth aspect, wherein the jet opening is formed in a portion of the extended portion facing the side wall portion so that the distance from the side wall portion is constant. [Ninth Aspect] The receiver according to the fifth or eighth aspect, wherein the jet portion includes: a first plate portion (301) extending in the intersecting direction; and a second plate portion (302) disposed opposite the first plate portion and forming a jet flow path (322b) between the first plate portion and the second plate portion, through which the refrigerant flows after passing through the supply pipe portion; and the receiver according to the fifth or eighth aspect, wherein the jet opening is formed downstream of the jet flow path in the refrigerant flow direction. [Tenth Aspect] The receiver according to the ninth aspect, wherein the jet opening is open in both the first plate portion and the second plate portion. [Eleventh Aspect] The receiver according to the ninth or tenth aspect, wherein the jet section has a flow path cross-sectional area set to be equal to or larger than the flow path cross-sectional area of ​​the jet flow path at a position where the jet opening is provided, and the flow path cross-sectional area of ​​the jet flow path is set to be equal to or larger than the flow path cross-sectional area of ​​the supply pipe section. [Twelfth Aspect] The receiver according to any one of the ninth to eleventh aspects, wherein the distance between the first plate section and the second plate section is set so that the flow path cross-sectional area of ​​the jet section at a position where the jet opening is provided is larger than the flow path cross-sectional area of ​​the jet flow path. [Thirteenth Aspect] The receiver according to any one of the ninth to twelfth aspects, wherein at least one of the supply pipe section and the discharge pipe section is provided with a holding section (34) that holds the first plate section and the second plate section. [14th Aspect] The receiver according to any one of the 9th to 13th aspects, wherein the jetting portion is provided with a distance defining portion (33) that defines a distance between the first plate portion and the second plate portion with respect to the first plate portion and the second plate portion. [15th Aspect] The receiver according to any one of the 1st to 14th aspects, further comprising a desiccant (50) that is disposed in the internal space and adsorbs moisture contained in the refrigerant, and the jetting opening and the desiccant are positioned relative to each other so that the refrigerant jetted from the jetting opening does not directly collide with the desiccant.

Claims

1. A liquid receiver applicable to an apparatus (1) constituting a vapor compression refrigeration cycle, comprising: a cylindrical container portion (20) having a predetermined axis (CL); a refrigerant introduction portion (30) for introducing a refrigerant into an internal space of the container portion; and a refrigerant discharge portion (40) including a discharge pipe portion (41) for discharging the refrigerant in a liquid phase state stored in the internal space to the outside of the internal space, wherein the refrigerant introduction portion has: a supply pipe portion (31) for introducing the refrigerant into the inside of the container portion; and a discharge portion (32, 32A) connected to the supply pipe portion and including a discharge opening (323) for spraying the refrigerant flowing through the supply pipe portion into the internal space, wherein the opening area of ​​the discharge opening is larger than the flow path cross-sectional area of ​​the supply pipe portion.

2. The receiver of claim 1, wherein the discharge pipe section includes an intake port (411) for drawing in the liquid-phase refrigerant present in the internal space, and the opening position of the intake port is set at a position not higher than the opening position of the ejection opening.

3. The receiver of claim 1, wherein the refrigerant introduction section includes a vertical section (31) that allows the refrigerant to flow vertically, and a bent section (322a) that changes the direction of the refrigerant flow from the vertical direction to a cross direction that crosses the vertical direction.

4. The receiver according to claim 3, wherein the cross direction is closer to the horizontal direction than to the vertical direction.

5. A receiver as described in claim 3 or 4, wherein the internal space of the container portion is formed by an upper wall portion (20a), a lower wall portion (20b), and a side wall portion (20c) connecting the upper wall portion and the lower wall portion, the refrigerant introduction portion includes an extension portion (322b) through which refrigerant that has passed through the bent portion flows and which extends in a direction away from the axis, and the extension portion extends toward the side wall portion so that at least a portion of the refrigerant that passes through the extension portion or the refrigerant that has passed through the extension portion collides with the side wall portion.

6. A receiver as described in claim 2, wherein the container portion is arranged so that the axis extends along the vertical direction, and the discharge pipe portion has the opening position of the suction port set at a position closer to the axis than the opening position of the ejection opening.

7. The receiver according to claim 1, wherein the jet opening has a plurality of jet holes (323a) for jetting the refrigerant flowing through the jet portion into the internal space.

8. A receiver according to claim 5, wherein the ejection opening is formed in a portion of the extended portion facing the side wall portion so that the distance between the ejection opening and the side wall portion is constant.

9. A receiver as described in claim 5, wherein the ejection portion includes a first plate portion (301) extending in the intersecting direction, and a second plate portion (302) arranged opposite the first plate portion and forming an ejection flow path (322b) between the first plate portion and the second plate portion, through which the refrigerant flows after passing through the supply pipe portion, and the ejection opening is formed on the downstream side of the refrigerant flow of the ejection flow path.

10. A receiver according to claim 9, wherein the ejection opening is open in both the first plate portion and the second plate portion.

11. A receiver as described in claim 9 or 10, wherein the flow path cross-sectional area of ​​the ejection section at the position where the ejection opening is provided is set to be equal to or greater than the flow path cross-sectional area of ​​the ejection flow path, and the flow path cross-sectional area of ​​the ejection flow path is set to be equal to or greater than the flow path cross-sectional area of ​​the supply pipe section.

12. A receiver as described in claim 9 or 10, wherein the distance between the first plate portion and the second plate portion is set so that the flow path cross-sectional area at the position where the ejection opening is provided is larger than the flow path cross-sectional area of ​​the ejection flow path.

13. A receiver as described in claim 9 or 10, wherein at least one of the supply pipe section and the discharge pipe section is provided with a holding section (34) for holding the first plate section and the second plate section.

14. A receiver as described in claim 9 or 10, wherein the ejection portion is provided with a spacing determining portion (33) that determines the spacing between the first plate portion and the second plate portion.

15. A receiver as described in claim 1, further comprising a desiccant (50) disposed in the internal space for adsorbing moisture contained in the refrigerant, wherein the ejection opening and the desiccant are positioned relative to each other so that the refrigerant ejected from the ejection opening does not directly collide with the desiccant.

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