JP2010169387A - Composite device including internal heat exchanger and accumulator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a composite device including a liquid coolant storage space of an accumulator above an internal heat exchanger, and also including a discharge room beside the internal heat exchanger. <P>SOLUTION: The internal heat exchanger 9 is eccentrically arranged at a fluid sealing room 2, and the discharge room 25 is provided beside the internal heat exchanger 9. An exterior dimension of the composite device is reduced and made to be easier to be assembled in an air conditioning circuit in an engine room without increasing a diameter of the fluid sealing room 2 and without extending the fluid sealing room 2 below the internal heat exchanger 9. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a composite apparatus including an internal heat exchanger, which is a component of an air conditioning circuit, and an accumulator in the field of an air conditioning circuit including heating, ventilation and / or an air conditioning apparatus for an automobile. Furthermore, the present invention also relates to an air conditioning circuit provided with this composite device.

  Generally, automobiles are equipped with heating, ventilation, and / or air conditioning devices to control the thermal factors of the air in the passenger compartment. This air conditioner provided in the air conditioning circuit cools the air before being supplied into the passenger compartment. This air conditioning circuit is provided with many devices, for example, a supercritical refrigerant fluid such as carbon dioxide known as R744 circulates. These devices include at least a compressor, a gas cooler, an internal heat exchanger, an expansion valve, an evaporator, and an accumulator.

  The refrigerant flows from the compressor to the gas cooler, then flows through the high pressure section of the internal heat exchanger to the expansion valve, then flows through the evaporator to the accumulator, and finally passes through the low pressure section of the internal heat exchanger to the compressor. Returned.

  The compressor compresses the sucked gaseous refrigerant to a high pressure. The gas cooler cools the compressed refrigerant under a relatively constant pressure and dissipates heat to the surroundings. The expansion valve reduces the pressure of the refrigerant flowing from the gas cooler and is at least partially liquefied. In the evaporator, the liquid refrigerant flowing from the expansion valve takes heat from the air flow passing through the evaporator and is converted into a gaseous refrigerant under a relatively constant pressure. Thereafter, the evaporated refrigerant fluid is sucked by the compressor. In this configuration, the refrigerant fluid has a high pressure in the “high pressure” section of the internal heat exchanger and a low pressure in the “low pressure” section.

The air conditioning circuit includes a “high pressure” circuit that begins at the compressor outlet and ends at the inlet of the expansion valve in the flow direction of the refrigerant fluid in the air conditioning circuit, and the “high pressure” section of the gas cooler and the internal heat exchanger is It is provided between the two.

The air conditioning circuit also includes a “low pressure” circuit that begins at the outlet of the expansion valve and ends at the inlet of the compressor in the flow direction of the refrigerant fluid in the air conditioning circuit, and includes an evaporator, an accumulator, and an internal heat exchanger 5. A “low pressure” section is provided between the two points.

The accumulator has a function of separating the gaseous refrigerant and the liquid refrigerant. Therefore, the accumulator includes a gas-liquid separation space for performing this separation function. This accumulator also plays a role of storing the circulating refrigerant fluid depending on the use conditions of the air conditioning circuit. Therefore, the accumulator has a liquid refrigerant storage space for storing the liquid refrigerant fluid that has flowed from the evaporator. In general, an accumulator is composed of a fluid-tight chamber having a gas-liquid separation space and a liquid-refrigerant storage space, and the fluid-tight chamber has a bottom wall for forming the liquid-refrigerant storage space in the lower part of the fluid-tight chamber. I have. Therefore, the liquid refrigerant fluid flowing from the evaporator is separated into a gaseous refrigerant and a liquid refrigerant, and the latter liquid refrigerant is stored on the lower wall of the liquid refrigerant storage space by gravity.

  In the internal heat exchanger, the refrigerant circulating in the “high pressure” section can exchange heat with the refrigerant circulating in the “low pressure” section. Therefore, heat is exchanged with the same fluid circulating at different positions in the air conditioning circuit without exchanging heat with air.

  Japanese Patent Application Laid-Open No. 2004-26883, filed by the Japan Research Institute and Denso, describes a combined apparatus in which an internal heat exchanger and an accumulator are combined. In general, the accumulator is provided with the above-described fluid sealing chamber, and the fluid sealing chamber has an opening closed by a cover. In addition, the fluid hermetic chamber is provided with an internal heat exchanger that covers the liquid refrigerant storage space at the use position of the composite device of the air conditioning circuit.

  The high-pressure refrigerant flowing from the gas cooler flows into the composite device through the “high-pressure” refrigerant inlet provided in the fluid-sealed chamber, circulates in the internal heat exchanger, and finally, It exits the composite device through a “low pressure” refrigerant inlet provided in the fluid tight chamber.

  The low-pressure refrigerant flowing from the evaporator flows into the composite apparatus from the low-pressure refrigerant inlet provided in the fluid tight chamber. The liquid low-pressure refrigerant is stored on the lower wall of the fluid-tight chamber due to its gravity, and the gaseous low-pressure refrigerant tends to collect in the upper space of the fluid-tight chamber. A conduit bent in a U-shape is provided in the upper space of the fluid tight chamber, and the other end of the conduit communicating with the internal heat exchanger is sucked in gaseous low-pressure refrigerant from one end of the conduit. Led to. Within the internal heat exchanger, the high pressure refrigerant fluid radiates heat to the low pressure refrigerant fluid. Gaseous low-pressure refrigerant fluid flows out of the internal heat exchanger and the composite device via a “low-pressure” refrigerant outlet formed in the wall of the fluid tight chamber.

  However, this composite device in the prior art has major drawbacks.

  The composite device described in Patent Document 1 does not take into account that it is incorporated in the engine room of an automobile. Regarding the configuration of the air conditioning circuit, it appears that the inlet and outlet of the high-pressure refrigerant and the low-pressure refrigerant are limited to those provided on the same side, in other words, the configuration that flows to the top of the fluid tight chamber. Furthermore, when this composite device is assembled in an automobile, a technical solution is required to minimize the space occupied by each part.

Japanese Patent Laid-Open No. 10-19421

  Accordingly, the object of the present invention is firstly to eliminate the aforementioned drawbacks by making the arrangement of the internal heat exchanger in the fluid tight chamber of the accumulator ingenious. Therefore, in order to reduce the external dimension of the composite device, the internal heat exchanger is arranged eccentrically in the fluid tight chamber. This arrangement provides a lateral discharge chamber in the internal heat exchanger without increasing the diameter of the fluid sealed chamber or extending the fluid sealed chamber under the internal heat exchanger to provide a discharge chamber. be able to.

  Accordingly, the present invention relates to a composite apparatus including a fluid-sealed chamber containing at least one internal heat exchanger and a liquid refrigerant storage space, the fluid-sealed chamber extending in a first central axis direction and the internal heat exchange. The main feature of the container is that it extends in the direction of the second central axis, and the first central axis is offset from the second central axis.

  According to the first feature of the present invention, the distance between the first central axis and the second central axis is 1 to 25 mm.

  According to the second feature of the present invention, the fluid tight chamber and the internal heat exchanger are cylindrical.

  According to another feature of the invention, the internal heat exchanger comprises at least one first flat tube wound around a second central axis.

  According to another feature of the invention, the first flat tube comprises a plurality of channels.

According to another feature of the invention, the internal heat exchanger comprises a suction chamber directed towards the center of the first flat tube wrapped around itself.

  The composite apparatus includes a discharge chamber located at least partially around the inner heat exchanger, and the discharge chamber is formed by an outer wall of the inner heat exchanger and an inner wall of the fluid tight chamber. It is desirable.

  The internal heat exchanger includes a first circulation path formed by a number of flow paths of the first flat tube, and the first circulation path communicates with the suction chamber by the first end of the flat tube. However, it is preferable that the second end portion of the flat tube communicates with the discharge chamber.

  The first circulation path is preferably formed by a second flat tube wound together with the first flat tube.

  The internal heat exchanger includes a second circulation path formed by a number of flow paths of the third flat tube, which is wound together with the first flat tube.

  According to another feature of the invention, the second circulation path is on one hand in communication with a first passage arranged on the outer periphery of the internal heat exchanger, and on the other hand, the axis is aligned with the second central axis. It communicates with the second passage.

  The first flat tube, the second flat tube, the third flat tube, the first passage, and the second passage are formed as an integrated assembly part.

  Furthermore, the fluid tight chamber is closed by an upper cover and a lower cover, and the liquid refrigerant storage space includes a lower wall located at the boundary between the internal heat exchanger and the liquid refrigerant storage space.

  The composite apparatus of the present invention includes a first conduit that passes through the upper cover and communicates with a gas-liquid separation space that exists in a fluid-tight chamber above the liquid refrigerant storage space.

  Finally, the composite device includes a second conduit that passes through the lower cover and leads to the discharge chamber.

  The invention also relates to an air conditioning circuit incorporating a composite device comprising at least one of the aforementioned features.

  A very advantageous first feature of the present invention is that the external volume can be reduced in the first circulation passage without increasing the internal head loss. Thereby, the composite apparatus of this invention can be easily assembled in the engine room where the space is gradually becoming smaller.

  Other features, detailed structures, and advantages of the present invention will become more apparent from the following detailed description and accompanying drawings.

It is a longitudinal cross-sectional view of the composite apparatus of this invention. It is a cross-sectional view in an internal heat exchanger part of the composite apparatus of this invention.

  FIG. 1 shows a composite device 1 according to the invention comprising an upper cover 3, also called an upper lid, and a fluid tight chamber 2 closed by a lower cover 4, also called a lower lid.

The fluid sealing chamber 2 extends in the longitudinal direction around the first central axis A. Although the cross-sectional shape of the fluid tight chamber 2 is cylindrical, it may be a parallelepiped, square, rectangle or the like. The length of the fluid tight chamber 2 in the direction of the first central axis A is larger than its outer diameter orthogonal to the first central axis A.

The composite device 1 also includes a “high pressure” refrigerant inlet 5 through which refrigerant 16 from the gas cooler flows into the composite device 1. The “high pressure” refrigerant inlet 5 is formed in a first tubular passage 12 that penetrates the lower cover 4 and is connected to the internal heat exchanger 9. The composite device 1 also includes a “high pressure” refrigerant outlet 6 through which high pressure refrigerant flows from the composite device 1 to the expansion valve. The “high pressure” refrigerant outlet 6 is formed in the second tubular passage 13, which starts from the internal heat exchanger 9 portion, passes through the inside of the fluid tight chamber, and passes through the top cover 3. It penetrates.

The composite device 1 also includes a “low pressure” refrigerant inlet 7 through which refrigerant from the evaporator flows into the composite device 1. The “low pressure” refrigerant inlet 7 is formed in a first conduit 14 that penetrates the upper cover 3. The composite device 1 also includes a “low pressure” refrigerant outlet 8 through which low-pressure refrigerant flows from the composite device 1 to the compressor. This “low pressure” refrigerant outlet 8 is formed in a second conduit 15 that passes through the lower cover 4.

The composite apparatus 1 includes a fluid tight chamber 2 that is sealed to the outside. The fluid sealed chamber 2 includes an internal heat exchanger 9, a gas-liquid separation space 10 that separates the refrigerant from the evaporator into a gaseous refrigerant 16a and a liquid refrigerant 16b, and a liquid refrigerant from the evaporator or, in particular, a gas refrigerant. A liquid refrigerant storage space 11 that stores the liquid refrigerant from the liquid separation space 10 is incorporated.

In the gas-liquid separation space 10, the first conduit 14 is separated from the first central axis A of the fluid hermetic chamber of the composite device 1, and the refrigerant fluid from the evaporator is tangential to the gas-liquid separation space 10. It is preferable that the structure has a cyclone type that can flow in from the inside. The inflow from the tangential direction is performed by a hole 17 provided in the cylindrical wall portion of the first conduit 14. By this arrangement, separation of the gaseous refrigerant 16a and the liquid refrigerant 16b is promoted. The end of the first conduit 14 located in the inner volume of the fluid tight chamber 2 is closed by a plate 18. The plate 18 extends in a direction perpendicular to the first central axis A of the fluid tight chamber 2. A small gap is provided between the outer periphery of the plate 18 and the inner wall 19 of the fluid tight chamber 2 so that the liquid refrigerant 16b of the refrigerant 16 can be lowered into the liquid refrigerant storage space 11 by gravity. Yes.

The liquid refrigerant storage space 11 is between the lower wall 20 and below the plate 18, and the liquid refrigerant 16b from the evaporator is stored on the lower wall 20 by gravity. Since the “low pressure” refrigerant inlet 7 is located above the lower wall 20 at the use position of the composite apparatus 1 for the air conditioning circuit and / or the operation position of the composite apparatus 1 alone, the liquid refrigerant 16b is Due to gravity, it naturally descends from the “low pressure” refrigerant inlet 7 toward the lower wall 20 and finally accumulates on the lower wall 20. The lower wall 20 is firmly placed on the inner wall 19 of the fluid tight chamber 2.

A second tubular passage 13 passes through the liquid refrigerant storage space 11, and an intermediate conduit 21 also passes through the liquid refrigerant storage space 11. The first end 21 a of the intermediate conduit 21 communicates with the gas-liquid separation space 10 and protrudes several mm from the upper surface of the plate 18. Therefore, the liquid refrigerant 16 b of the refrigerant 16 does not return to the intermediate conduit 21, and only the gaseous refrigerant 16 a of the refrigerant 16 can pass through the intermediate conduit 21. The intermediate conduit 21 has a second end 21 b that passes through the lower wall 21 and communicates with the internal heat exchanger 9. In the first embodiment shown in FIG. 1, the intermediate conduit 21 is larger in diameter than the second tubular passage 13 and is coaxially attached to the second tubular passage 13. Accordingly, the axes of both the intermediate conduit 21 and the second tubular passage 13 are characterized by being separated from the first central axis A of the fluid tight chamber 2. In the second embodiment, not shown, the intermediate conduit 21 has a diameter larger than that of the second tubular passage 13, and the central axis of the intermediate conduit 21 is coaxial with the first central axis A. Accordingly, the intermediate conduit 21 is located at the cylindrical center of the fluid tight chamber 2. However, even in this embodiment of the invention, the internal heat exchanger 9 is always spaced. As a result, the second tubular passages 13 are separated inside the intermediate conduit 21. In other words, the central axis of the intermediate conduit 21 is coaxial with the first central axis A, and the central axis of the second tubular passage 13 is not coaxial with the central axis of the intermediate conduit 21.

While the gaseous refrigerant 16 descends toward the internal heat exchanger 9, the refrigerant flowing in the second tubular passage 13 rises in the direction of the upper cover 3. This circulation in the composite device is called “counterflow”.

The lower wall 20 is preferably perpendicular to the first central axis A of the fluid tight chamber 2 of the composite device 1.

The gas-liquid separation space 10 is adjacent to the upper cover 3 and is located immediately below the upper cover 3. As a result, the liquid refrigerant storage space 11 is located between the gas-liquid separation space 10 and the lower wall 20, and the plate 18 is provided between the gas-liquid separation space 10 and the liquid refrigerant storage space 11. .

The lower wall 20 that is the bottom of the liquid refrigerant storage space 11 is located above the internal heat exchanger 9. The liquid refrigerant storage space 11 is arranged above the internal heat exchanger 9 along the gravity axis.

The cross-sectional shapes of the fluid tight chamber 2 and the internal heat exchanger 9 are both cylindrical and are fully coordinated.

The liquid refrigerant storage space 11 covering the internal heat exchanger 9 or located above the internal heat exchanger 9 on the first central axis A of the fluid tight chamber 2 is more than the internal heat exchanger 9. High position.

The internal heat exchanger 9 is composed of a first flat tube 22 wound around the second central axis B, and the second central axis B is the first center of the fluid tight chamber 2 of the composite apparatus 1. It is not coaxial with the axis A but is separated. The distance d of the first central axis A from the second central axis B allows the second conduit 15 to be attached to the lower cover 4 without increasing the external dimensions of the fluid tight chamber 2 and thus the overall composite device. It can be installed easily. The first central axis A and the second central axis B are characterized by being parallel.

The 1st flat tube 22 is equipped with many exit holes 23 also called the micro flow path for low pressure refrigerant | coolants. The multiple outlet holes 23 are first circulation passages for low-pressure refrigerant. The first circulation passage communicates with the suction chamber 24 and the discharge chamber 25. The suction chamber 24 is formed by the second end portion 21 b of the intermediate conduit 21, the portion of the first flat tube 22 wound around itself, and the lower cover 4.

The discharge chamber 25 includes a first flat tube 22 that forms the outer wall of the internal heat exchanger 9 and / or a winding portion on the outer periphery of a third flat tube 27 that will be described in detail later, the lower wall 20, the lower cover 4, Finally, it is formed by the inner wall 19 of the fluid tight chamber 2 in which the internal heat exchanger 9 is arranged. Along with the distance d between the first central axis A and the second central axis, the cross-sectional shape of the discharge chamber is oval.

The first circulation passage includes a second flat tube 26 having a number of outlet holes 23. The second flat tube 26 is wound around the first flat tube 22, and the first circulation passage for the “low pressure” refrigerant 16 is formed by both tubes.

The internal heat exchanger 9 also includes a third flat tube 27 having a number of outlet holes 23 that form a second circulation passage for “high pressure” refrigerant. The third flat tube 27 communicates with the first tubular passage 12 disposed on the outer peripheral portion of the internal heat exchanger on the one hand and is coaxial with the second central axis B of the internal heat exchanger 9 on the other hand. The second tubular passage 13 is communicated with. The first tubular passage 12 is firmly connected to the end of the third flat tube 27 by, for example, welding, brazing, or the like, and a number of outlet holes 23 communicate with the inside of the first tubular passage 12. ing. Similarly, the other end of the third flat tube 27 communicates with the second tubular passage 13.

If the internal heat exchanger 9 does not include the second flat tube 26, the internal heat exchanger 9 includes the first flat tube 22 and the third flat tube 27 that are wound together, and each tube. However, the first circulation passage and the second circulation passage are formed.

In this embodiment, the first circulation passage includes a first flat tube 22 and a second flat tube 26, and the third flat tube 27 is inserted between the first flat tube 22 and the second flat tube 26. Or are pinched.

In this case, the first, second, and third flat tubes are wound around the second central axis B of the internal heat exchanger 9 so as to be alternately arranged.

An intermediate subassembly composed of the first flat tube 22, the second flat tube 26, the third flat tube 27, the first tubular passage 12, and the second tubular passage 13 is a single assembly. This assembly part is assembled by connecting the aforementioned parts without destroying a single assembly part. In this assembly, each part is made strong by, for example, brazing or welding.

FIG. 2 shows a cross section perpendicular to the first central axis A of the fluid tight chamber 2 of the present invention. The intersection of the alternate long and short dash line EE and the alternate long and short dash line FF indicates the first central axis A of the fluid tight chamber 2 and is the central axis of the volume in the inner wall 19. In FIG. 2, the thickness of the fluid tight chamber 2 is schematically shown so as not to complicate the drawing.

The intersection of the alternate long and short dash line CC and the alternate long and short dash line FF indicates the second central axis B of the internal heat exchanger 9. The separation amount d is the distance between the first central axis A of the fluid tight chamber 2 and the second central axis B of the internal heat exchanger 9, and if the separation amount d is 1 mm or less, which is the minimum value, the internal heat exchange is performed. The space in the lateral direction of the vessel 9 becomes insufficient. The maximum value of the separation amount d is 25 mm, which is a value necessary to satisfy both the outer diameter of the internal heat exchanger 9 and the outer diameter of the fluid hermetic chamber 2.

Between these two values, the side space of the internal heat exchanger 9 is made large, and this space is used as a discharge chamber. Without increasing the diameter of the fluid sealed chamber 2, the internal heat exchanger 9, the fluid sealed chamber 2, and the second conduit 15 each having a constant diameter can be easily arranged.

One end portion of the third flat tube 27 is connected to the first tubular passage 12 located on the outer peripheral portion of the internal heat exchanger 9, and similarly, the other end portion is the second central axis of the internal heat exchanger 9. A second tubular passage 13 coaxial with B is connected.

The first flat tube 22 and the second flat tube 26 suck the gaseous “low-pressure” refrigerant in the suction chamber from their ends. The “low pressure” refrigerant flows in the first flat tube 22 and the second flat tube 26 so as to face the “high pressure” refrigerant flowing in the third flat tube 27. Thereafter, the “low pressure” refrigerant flows out from the end portions of the first flat tube 22 and the second flat tube 26 to the discharge chamber, and flows out from the composite device 1 through the second conduit 15.

The composite device 1 can be fluidly coupled to the air conditioning circuit by the upper cover 3 and the lower cover 4. One compressor and the other gas cooler in the composite apparatus 1 are connected by a conduit provided in the lower cover 4, while one evaporator and the other expansion valve are provided in the upper cover 3. Connected by a conduit. With this configuration, it is easy to incorporate the composite apparatus 1 into the air conditioning circuit, and hence into the engine room of the automobile.

“Upper”, “lower”, “cover”, “lower”, and “upper” depend on the use position of the composite apparatus 1. This use position is easily determined by installing the composite apparatus 1 of the present invention in the air conditioning circuit. However, the use position can be determined by the composite apparatus 1 alone, in other words, can be determined regardless of the arrangement in the air conditioner according to the actual operation.

DESCRIPTION OF SYMBOLS 1 Composite apparatus 2 Fluid sealing chamber 3 Upper cover 4 Lower cover 5 "High pressure" refrigerant inlet 6 "High pressure" refrigerant outlet 7 "Low pressure" refrigerant inlet 8 "Low pressure" refrigerant outlet 9 Internal heat exchanger 10 Gas-liquid separation Space 11 Liquid refrigerant storage space 12 First tubular passage 13 Second tubular passage 14 First conduit 15 Second conduit 16 Refrigerant 16a Gaseous refrigerant 16b Liquid refrigerant 17 Hole 18 Plate 19 Inner wall 20 Lower wall 21 Intermediate conduit 21a First end Portion 21b second end portion 22 first flat tube 23 outlet hole 24 suction chamber 25 discharge chamber 26 second flat tube 27 third flat tube A first central axis B second central axis d separation amount

Claims (16)

  A fluid sealed chamber (2) containing at least one internal heat exchanger (9) and a liquid refrigerant storage space (11) is provided, and the fluid sealed chamber (2) has a first central axis (A) direction. In the composite device (1) in which the internal heat exchanger (9) faces the direction of the second central axis (B), the first central axis (A) is the second central axis (B). A composite device (1) characterized by being spaced apart from each other. The composite apparatus (1) according to claim 1, wherein the distance (d) between the first central axis (A) and the second central axis (B) is 1 to 25 mm. The composite device (1) according to claim 1 or 2, characterized in that the fluid-tight chamber (2) and the internal heat exchanger (9) are cylindrical. The internal heat exchanger (9) comprises at least one first flat tube (22) wound around the second central axis (B). A composite device (1) according to the above. The composite device (1) according to claim 4, wherein the first flat tube (22) comprises a number of flow paths (23). 6. The composite device according to claim 4, wherein the internal heat exchanger (9) comprises a suction chamber (24) facing the center of the wound first flat tube (22). 1). A discharge chamber (25) located at least partially is provided around the internal heat exchanger (9). The discharge chamber (25) includes an outer wall of the internal heat exchanger (9) and a fluid-tight chamber. The composite device (1) according to any one of claims 1 to 6, characterized in that it is formed by the inner wall (19) of (2). The internal heat exchanger (9) includes a first circulation passage formed by a number of flow paths (23) of the first flat tube (22), and the first circulation passage is formed by the flat tube (22). The first end portion communicates with the suction chamber (24) and the second end portion of the flat tube (22) communicates with the discharge chamber (25). A composite device (1) according to claim 7. The composite device (1) according to claim 8, wherein the first circulation passage is formed by a second flat tube (26) wound together with the first flat tube (22). The internal heat exchanger (9) includes a second circulation passage formed by a number of flow paths (23) of a third flat tube (27) wound together with the first flat tube (22). A composite device (1) according to any of claims 3 to 9, characterized in that. On the one hand, the second circulation passage communicates with the first passage (12) arranged on the outer periphery of the internal heat exchanger (9), and on the other hand, the axis coincides with the second central axis. 11. The composite device (1) according to claim 10, characterized in that it communicates with the second passage (13). The first flat tube (22), the second flat tube (26), the third flat tube (27), the first passage (12), and the second passage (13) are formed as a single assembly part. 12. The composite device (1) according to claim 11, wherein the composite device (1) is provided. The fluid tight chamber (2) is closed by an upper cover (3) and a lower cover (4), and the liquid refrigerant storage space (11) is an internal heat exchanger (9) and the liquid refrigerant storage space (11). 13. The composite device (1) according to any one of claims 1 to 12, characterized in that it comprises a lower wall (20) arranged at the boundary of. A first conduit (14) passing through the upper cover (3) and leading to a gas-liquid separation space (10) above the liquid refrigerant storage space (11) of the fluid tight chamber (2); 14. A composite device (1) according to claim 13, characterized in that 15. The composite according to claim 7, further comprising a second conduit (15) penetrating the lower cover (4) and leading to the discharge chamber (25). Device (1). An air-conditioning circuit comprising the composite device (1) according to any one of claims 1 to 15.

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