JP7235451B2 - accumulator - Google Patents

Description

The present invention relates to accumulators.

Refrigerating systems often use an accumulator to separate the refrigerant from liquid and gas so that the liquid refrigerant is not supplied to the compressor.
Patent Literature 1 describes an accumulator for a refrigerator. In this patent document 1, one accumulator is provided for a plurality of compressors. The accumulator disclosed in Patent Document 1 includes U-shaped tubes that are connected to a plurality of compressors. These U-shaped tubes are housed in one container. In the accumulator of Patent Document 1, refrigerant is introduced from an inlet pipe connected to the top of the container. Of the refrigerant introduced from this inlet pipe, the liquid refrigerant moves downward due to its own weight and accumulates in the lower portion of the container. On the other hand, the gaseous refrigerant is discharged from the accumulator through the flow path in the U-shaped tube from the suction port of the U-shaped tube located in the upper part of the container.

Japanese Patent No. 4442384

As in the accumulator described in Patent Document 1, when the refrigerant is introduced from the inlet pipe connected to the upper part of the container, the gas-liquid mixed refrigerant flowing from the inlet pipe flows through the inner wall surface of the container and the U-shaped pipe. It can collide with the supporting bracket. In this way, when the refrigerant collides with the inner wall surface, brackets, etc., the liquid refrigerant scatters due to the rebounding, etc., and enters the inside of the U-shaped pipe from the suction port of the U-shaped pipe, and the liquid refrigerant is discharged from the accumulator as it is. may be lost.

The present invention has been made in view of the above circumstances, and provides an accumulator capable of improving the efficiency of gas-liquid separation.

In order to solve the above problems, the following configuration is adopted.
According to a first aspect of the invention, an accumulator includes a container, a U-tube, an internal flow path forming portion, and an inlet pipe. The container has a body portion formed in a cylindrical shape with an axis extending in the vertical direction and two end plate portions closing both end portions of the body portion, and has an internal space for gas-liquid separation of the refrigerant. The U-shaped pipe has a straight pipe portion and a curved pipe portion. The straight tube portion is formed in a circular tube shape centering on the axis extending vertically in the internal space, and has a suction port for taking in gaseous refrigerant at the top. The curved tube portion is arranged outside the container and is formed so as to bend upward from the lower end portion of the straight tube portion. The internal flow path forming portion has a circular cross section perpendicular to the axis that is larger in diameter than the straight pipe portion and concentric with the straight pipe portion, and has a downward opening. The internal flow path forming portion is formed in a cylindrical shape having a peripheral wall arranged concentrically with the straight pipe portion and having a constant dimension in a radial direction about the axis so as to cover at least the suction port in the horizontal direction. are placed. The internal flow path forming portion forms an internal flow path that guides the gas refrigerant from the internal space to the suction port only through the lower opening. The inlet pipe has an injection port disposed at the same position as the inner wall surface of the container in the radial direction and for injecting the refrigerant into the container above the lower edge of the internal flow path forming portion. . In the inlet pipe, a first imaginary straight line extending in a direction of injecting the refrigerant from the injection port when viewed from above and below is inclined with respect to a second imaginary straight line passing through the center of the injection port and the center of the straight pipe portion. are arranged to The first imaginary straight line passes through a position that does not contact the outer peripheral surface of the straight pipe portion.
In this first aspect, the suction port of the U-shaped pipe is covered from the horizontal direction by the internal flow path forming portion. Further, in this first aspect, the injection port of the inlet pipe is arranged above the lower edge of the internal flow path forming portion. Therefore, of the refrigerant separated into gas and liquid in the container, the gaseous refrigerant reaches the suction port through the internal flow path from the lower opening of the internal flow path forming portion. On the other hand, the liquid refrigerant that scatters when the refrigerant is injected from the injection port does not directly enter the inside of the U-shaped tube from the suction port.
In this first aspect, the inlet pipe is arranged so that the first imaginary straight line extending in the direction of injecting the refrigerant from the injection port when viewed from above is relative to the second imaginary straight line passing through the center of the injection port and the center of the straight pipe portion. arranged to be slanted. Therefore, the refrigerant injected from the injection port is guided by the inner wall surface of the container and becomes a swirling flow. Due to the centrifugal force caused by this swirling and the density difference between the gaseous coolant and the liquid coolant, the liquid coolant swirls outside the gaseous coolant and adheres to the inner wall surface of the container. The liquid refrigerant adhering to the inner wall surface flows down along the inner wall surface of the container due to gravity. On the other hand, inside the inner wall surface of the container, the gaseous refrigerant flows toward the suction port. Therefore, it is possible to suppress the entry of the liquid refrigerant into the suction port and improve the efficiency of the gas-liquid separation.

Furthermore , since only the straight pipe portion is arranged inside the container, the center of whirl of the refrigerant can be formed in a straight line extending in the vertical direction. Therefore, since the refrigerant can be swirled more smoothly, the efficiency of gas-liquid separation can be improved.

Further, the cross section of the internal flow path forming portion perpendicular to the axis line has a larger diameter than the straight pipe portion and has a circular shape concentric with the straight pipe portion. can be made

According to the second aspect of the present invention, the suction port according to the first aspect may be formed in an elliptical shape with a major axis extending in the vertical direction.

According to the third aspect of the present invention, the suction port according to the first aspect may be formed in a vertically elongated rectangular shape.
By configuring as in the second and third modes, the area of the suction port can be increased compared to the case where the suction port is formed in a circular shape. Therefore, obstruction of the flow of the gaseous coolant can be suppressed, and the gaseous coolant can be discharged smoothly.

According to the fourth aspect of the present invention, a plurality of suction ports according to any one of the first to third aspects may be formed at intervals in the circumferential direction and the axial direction of the straight pipe portion. .
By configuring in this way, it is possible to prevent the flow of the gaseous refrigerant from being obstructed and to smoothly discharge the gaseous refrigerant, as compared with the case where only one suction port is formed.

According to a fifth aspect of the present invention, the upper end of the straight pipe portion according to the first aspect may be arranged at a position where it is horizontally covered by the internal flow path forming portion. The suction port may be formed at the upper end of the straight pipe portion and open upward.
By configuring in this way, the suction port can be easily formed.

According to the sixth aspect of the present invention, the refrigeration cycle includes a circulation line through which a refrigerant flows, an accumulator according to any one of the first to fifth aspects, a compressor, a first heat exchanger, a second A heat exchanger and an expansion valve are provided. A compressor compresses the gaseous refrigerant separated by the accumulator. The first heat exchanger is arranged in the circulation line and exchanges heat between the refrigerant flowing in the circulation line and the first medium to change the phase of the refrigerant. The second heat exchanger is arranged in the circulation line and exchanges heat between the refrigerant flowing through the circulation line and the second medium to change the phase of the refrigerant. It is arranged in the circulation line, in which the compressor is not arranged, among the circulation lines between the first heat exchanger and the second heat exchanger.
This sixth aspect includes the accumulator according to any one of the first to fifth aspects. Therefore, it is possible to improve the efficiency of gas-liquid separation of the refrigerant by the accumulator. Therefore, the supply of liquid refrigerant to the compressor can be suppressed without increasing the size of the accumulator, and the reliability of the refrigeration cycle can be improved.

The above accumulator and refrigeration cycle can improve the efficiency of gas-liquid separation.

1 is a configuration diagram showing a schematic configuration of a refrigeration cycle in an embodiment of the invention; FIG. It is a perspective view which shows schematic structure of the accumulator in embodiment of this invention. It is a longitudinal cross-sectional view of the upper part of the accumulator in embodiment of this invention. It is a horizontal sectional view near the entrance pipe of the accumulator in the embodiment of this invention. It is a longitudinal cross-sectional view corresponding to FIG. 3 in the first modified example of the embodiment of the invention. It is a longitudinal cross-sectional view corresponding to FIG. 3 in the second modified example of the embodiment of the invention. It is a longitudinal cross-sectional view corresponding to FIG. 3 in the third modified example of the embodiment of the invention.

Next, an accumulator and a refrigerating cycle according to embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a configuration diagram showing a schematic configuration of a refrigeration cycle according to an embodiment of the invention.
As shown in FIG. 1, the refrigeration cycle 100 of this embodiment includes a circulation line 10, an accumulator 5, a compressor 60, a first heat exchanger 1, a second heat exchanger 2, an expansion valve 3, A four-way switching valve 4 is provided. The refrigeration cycle 100 of this embodiment can be used, for example, in a refrigeration unit for land transportation (also referred to as a land refrigeration unit). In the following description, normally, the first heat exchanger 1 functions as a condenser, and the second heat exchanger 2 functions as an evaporator. 1 function and the function of the second heat exchanger may be switched.

The circulation line 10 forms a flow path through which the coolant R circulates. The circulation line 10 connects the accumulator 5 , the compressor 60 , the first heat exchanger 1 , the expansion valve 3 , the second heat exchanger 2 , and the four-way switching valve 4 .

The accumulator 5 has a function of temporarily storing the refrigerant R and separating the liquid-phase refrigerant R (hereinafter simply referred to as liquid refrigerant RL) and the gas-phase refrigerant R (hereinafter simply referred to as gaseous refrigerant RG). have The accumulator 5 separates the gas-liquid mixture of the refrigerant R from the refrigerant inlet 5a and discharges the gaseous refrigerant RG from the refrigerant outlet 5b.

The compressor 60 compresses the gas refrigerant RG discharged from the refrigerant outlet 5 b of the accumulator 5 . The compressor 60 compresses the gaseous refrigerant RG that has flowed in from the suction port 65 and discharges it from the discharge port 66 . The gaseous refrigerant RG compressed by this compressor 60 is supplied to the first heat exchanger 1 via the first port 4 a and the second port 4 b of the four-way switching valve 4 .

The first heat exchanger 1 exchanges heat between the compressed gaseous refrigerant RG and the first medium M1 to change the phase of the gaseous refrigerant RG. More specifically, since the first heat exchanger 1 normally functions as a condenser, it exchanges heat between the gaseous refrigerant RG compressed by the compressor 60 and the outside air. The first heat exchanger 1 draws heat from the gaseous refrigerant RG that has flowed in through the first refrigerant port 1a, condenses it, and discharges the condensed liquid refrigerant RL through the second refrigerant port 1b.

The expansion valve 3 adiabatically expands the liquid refrigerant RL. More specifically, the expansion valve 3 adiabatically expands the liquid refrigerant RL discharged from the second refrigerant port 1 b of the first heat exchanger 1 and feeds it into the second heat exchanger 2 .

The second heat exchanger 2 exchanges heat between the adiabatically expanded liquid refrigerant RL (refrigerant R) and the second medium M2 to change the phase of the liquid refrigerant RL. More specifically, since the second heat exchanger 2 normally functions as an evaporator, it exchanges heat between the liquid refrigerant RL adiabatically expanded by the expansion valve 3 and the air to be cooled in the room or the like. . The second heat exchanger 2 heats and evaporates the liquid refrigerant RL that has flowed in from the first refrigerant port 2a, thereby producing a refrigerant R in a gas-liquid mixed state of the evaporated gaseous refrigerant RG and the unevaporated liquid refrigerant RL. It is discharged from the second refrigerant port 2b. Refrigerant R discharged from the second heat exchanger 2 is supplied to the accumulator 5 via the fourth port 4 d and the third port 4 c of the four-way switching valve 4 .

The four-way switching valve 4 has four ports, a first port 4a, a second port 4b, a third port 4c and a fourth port 4d. The four-way switching valve 4 can selectively change the state of communication between each port. Specifically, the four-way switching valve 4 of this embodiment can select either the first connection form or the second connection form. The first connection form allows communication between the first port 4a and the second port 4b, and communication between the third port 4c and the fourth port 4d. The second connection form allows communication between the second port 4b and the third port 4c, and communication between the fourth port 4d and the first port 4a. That is, according to the four-way switching valve 4, it is possible to reverse the direction of the refrigerant R flowing in the circulation line 10 by switching between the first connection mode and the second connection mode. The functions of the heat exchanger 1 and the functions of the second heat exchanger 2 can be interchanged.

FIG. 2 is a perspective view showing a schematic configuration of the accumulator in the embodiment of this invention.
As shown in FIG. 2 , the accumulator 5 includes a container 21 , a U-shaped tube 22 , an internal flow passage forming portion 23 and an inlet pipe 24 . The container 21 has an internal space S1 for gas-liquid separation of the refrigerant R supplied from the first heat exchanger 1 or the second heat exchanger 2 functioning as an evaporator. The container 21 exemplified in this embodiment includes a cylindrical body portion 21A and two end plate portions 21B closing both ends of the body portion 21A. The container 21 is arranged adjacent to the compressor 60, for example, in a posture in which the axis O1 of the body 21A extends vertically (more specifically, vertically). In this embodiment, the case where the end plate portion 21B has a spherical surface is exemplified, but the shape of the end plate portion 21B is not limited to this shape.

The U-tube 22 forms a flow path for discharging the gaseous refrigerant RG out of the refrigerant R separated from gas and liquid. The U-shaped tube 22 has a straight tube portion 26 and a curved tube portion 27 .
The straight pipe portion 26 is formed in a tubular shape (in other words, circular tubular shape) with a circular cross section extending vertically inside the internal space S1. The straight pipe portion 26 has a suction port 28 at its upper portion that takes in the gaseous refrigerant RG in the internal space S1. The suction port 28 in this embodiment is formed in an elliptical shape elongated in the vertical direction.

The curved tube portion 27 is formed in a U shape so as to fold upward from the lower end portion of the straight tube portion 26 .
In this embodiment, the curved pipe portion 27 is arranged outside the container 21 and the straight pipe portion 26 vertically penetrates the container 21 . An upper portion and a lower portion of the straight tube portion 26 are supported by the container 21 respectively. Specifically, the upper portion and the lower portion of the straight pipe portion 26 are fixed around the through hole of the container 21 via a welded portion M such as brazing. The straight tube portion 26 is arranged so that its central axis overlaps with the axis O1 of the container 21 .

FIG. 3 is a vertical cross-sectional view of the upper part of the accumulator in the embodiment of this invention.
As shown in FIGS. 2 and 3, the internal flow path forming portion 23 has a lower opening 31 that covers the suction port 28 from the horizontal direction and faces downward. The internal flow path forming portion 23 forms an internal flow path F1 that guides the gas refrigerant RG from the internal space S1 to the suction port 28 via the lower opening 31 . The internal flow path forming portion 23 in this embodiment is formed in a cylindrical shape. The internal flow path forming portion 23 has a peripheral wall arranged concentrically with the straight pipe portion 26 and formed to have a larger diameter than the straight pipe portion 26 .

The internal flow path F<b>1 is formed between the inner peripheral surface 23 i of the internal flow path forming portion 23 and the outer peripheral surface 26 o of the straight tube portion 26 . The internal flow path forming portion 23 in this embodiment is arranged concentrically with the straight tube portion 26 . Therefore, the dimension of the internal flow path F1 in the radial direction about the axis O1 is constant in all circumferential directions about the axis O1. An upper end portion 23t of the internal flow path forming portion 23 exemplified in this embodiment is in contact with the lower surface 21Bu of the end plate portion 21B arranged above. That is, the internal flow path F1 communicates with the internal space S1 of the container 21 only through the lower opening 31 .

Here, if the flow velocity of the gas refrigerant RG flowing through the internal flow path F1 from the lower opening 31 toward the suction port 28 becomes too high, the liquid refrigerant RL adhering to the periphery of the lower opening 31 is pushed upward by the gas refrigerant RG. , and may enter the straight pipe portion 26 from the suction port 28 . Therefore, the distance between the inner peripheral surface 23i of the internal flow path forming portion 23 and the outer peripheral surface 26o of the straight tube portion 26 in the radial direction about the axis O1 is such that the flow velocity of the gas refrigerant RG in the internal flow path F1 becomes too high. There is no distance.

FIG. 4 is a horizontal sectional view of the vicinity of the inlet pipe of the accumulator in the embodiment of this invention.
As shown in FIGS. 3 and 4 , the inlet pipe 24 has an injection port 33 for injecting the coolant R into the container 21 . The injection port 33 is arranged above the lower edge 23 a of the internal flow path forming portion 23 . The inlet pipe 24 in this embodiment is formed in a circular tubular shape. The injection port 33 in this embodiment is arranged at the same position (in other words, flush) with the inner wall surface 21i of the container 21 in the radial direction of the body portion 21A.

Here, as shown in FIG. 4, a straight line extending in the direction in which the coolant R is injected from the center of the injection port 33 when viewed from above and below is defined as a first imaginary straight line IL1. Further, a straight line passing through the center of the injection port 33 and the center of the straight pipe portion 26 (in other words, the axis O1) is defined as a second imaginary straight line IL2. Then, the first imaginary straight line IL1 in this inlet pipe 24 is inclined with respect to the second imaginary straight line IL2. Note that the closer the first imaginary straight line IL1 is to the inclination angle of the tangential line of the container 21 at the position of the injection port 33 in the cross-sectional view of FIG. becomes.

The first imaginary straight line IL1 in this embodiment exemplifies the case where it passes through a position that does not come into contact with the outer peripheral surface 26o of the straight pipe portion 26. As shown in FIG. By arranging the inlet pipe 24 in this way, the coolant R injected from the injection port 33 is formed in a cylindrical shape between the outer peripheral surface 23o of the internal flow path forming portion 23 and the inner wall surface 21i of the container 21. The internal space S1 becomes a swirling flow that swirls around the internal flow path forming portion 23 . In addition, the diameter of the injection port 33 may be large enough to obtain the flow velocity necessary for the swirling flow. In the above-described embodiment, the case where the diameter of the inlet pipe 24 and the diameter of the injection port 33 are the same is exemplified, but the diameter of the injection port 33 may be smaller than the diameter of the inlet pipe 24 .

As shown in FIG. 2, the U-shaped pipe 22 in this embodiment has a pressure equalizing pipe 35 that connects the downstream uppermost portion of the curved pipe portion 27 and the uppermost portion of the straight pipe portion 26 . This pressure equalizing pipe 35 is formed to have a diameter smaller than that of the U-shaped pipe 22 . The pressure equalizing pipe 35 prevents a pressure difference between the internal space S1 of the container 21 and the outlet of the U-shaped pipe 22 even after the refrigeration cycle 100 is stopped.
In addition, the straight pipe portion 26 has an oil return hole 36 at the bottom inside the container 21 . This oil return hole 36 can introduce into the U-shaped tube 22 liquid refrigerant containing lubricating oil stored in the lower portion of the container 21 .

In the above-described embodiment, the suction port 28 of the U-shaped tube 22 is horizontally covered by the internal flow path forming portion 23 . Furthermore, the injection port 33 of the inlet pipe 24 is arranged above the lower edge of the internal flow path forming portion 23 . Therefore, the gaseous refrigerant (indicated by hatched arrows in FIGS. 3 and 4) RG among the refrigerants R separated into gas and liquid in the container 21 flows from the lower opening 31 of the internal flow passage forming portion 23 to the internal flow passage F1. It reaches the suction port 28 through. On the other hand, the liquid refrigerant RL that scatters when the refrigerant R is injected from the injection port 33 does not directly enter the inside of the U-shaped tube 22 from the suction port 28 .

In the embodiment described above, the inlet pipe 24 is arranged so that the first imaginary straight line IL1 is inclined with respect to the second imaginary straight line. Therefore, the coolant R injected from the injection port 33 is guided by the inner wall surface 21i of the container 21 and becomes a swirling flow. Due to the centrifugal force due to this swirling flow and the density difference between the gas refrigerant RG and the liquid refrigerant RL, the liquid refrigerant (indicated by the black arrows in FIGS. 3 and 4) RL is swirled outside the gas refrigerant RG and the container 21 adheres to the inner wall surface 21i. The liquid refrigerant RL adhering to the inner wall surface 21i flows down along the inner wall surface 21i of the container 21 due to gravity. On the other hand, inside the inner wall surface 21 i of the container 21 , the gas refrigerant RG flows toward the suction port 28 .
Therefore, the liquid refrigerant RL is prevented from entering the suction port 28, and the efficiency of the gas-liquid separation of the refrigerant R can be improved. In particular, when there is a restriction on the arrangement space of the accumulator 5 such as a land reflex unit, it is advantageous in that the gas-liquid separation efficiency can be improved without increasing the size of the accumulator 5 .

In the embodiment described above, only the straight pipe portion 26 of the U-shaped pipe 22 is arranged inside the container 21 . In other words, the curved tube portion 27 is not arranged inside the container 21 . Therefore, it becomes a straight line extending vertically around the swirl center of the coolant R swirling.
Furthermore, since the upper portion and the lower portion of the straight pipe portion 26 can be supported by the container 21 respectively, a bracket or the like for supporting the straight pipe portion 26 inside the container 21 can be omitted.
Therefore, since the refrigerant R can be swirled more smoothly, the efficiency of gas-liquid separation can be improved.

In the above-described embodiment, the straight tube portion 26 is formed in a circular tube shape centering on the axis O1, and the internal flow path forming portion 23 is a cylinder having a diameter larger than that of the straight tube portion 26 and concentric with the straight tube portion 26. constitutes Therefore, compared with the case where the straight pipe portion 26 and the internal flow path forming portion 23 are formed in a square tube shape, the flow path resistance of the swirling flow can be suppressed. Therefore, a swirl flow can be generated more smoothly in the container 21 .

In the above-described embodiment, the suction port 28 is formed in an elliptical shape with the major axis extending in the vertical direction. Therefore, the area of the suction port 28 can be increased compared to when the suction port 28 is formed in a circular shape. Therefore, it is possible to prevent the flow of the gaseous refrigerant RG from being obstructed, and to smoothly discharge the gaseous refrigerant RG.

A refrigerating cycle 100 of this embodiment includes an accumulator 5 having the configuration described above. Therefore, the efficiency of gas-liquid separation of the refrigerant R by the accumulator 5 can be improved. Therefore, the supply of the liquid refrigerant RL to the compressor 60 can be suppressed without increasing the size of the accumulator 5, and the reliability of the refrigeration cycle 100 can be improved.

(Other modifications)
The present invention is not limited to the above-described embodiments, but includes various modifications of the above-described embodiments within the scope of the present invention. That is, the specific shapes, configurations, and the like given in the embodiments are merely examples, and can be changed as appropriate.
For example, in the above-described embodiment, the curved tube portion 27 is arranged outside the container 21 , but the curved tube portion 27 may be arranged inside the container 21 .

FIG. 5 is a cross-sectional view corresponding to FIG. 3 in the first modification of the embodiment of the invention. FIG. 6 is a cross-sectional view corresponding to FIG. 3 in a second modification of the embodiment of the invention. FIG. 7 is a cross-sectional view corresponding to FIG. 3 in a third modification of the embodiment of the invention.
In the above-described embodiment, the case where the suction port 28 is elliptical has been described. However, like the suction port 128 of the first modified example shown in FIG. 5, it may be formed in a rectangular shape elongated in the vertical direction. Furthermore, like the suction port 228 of the second modified example shown in FIG.
Although illustration is omitted, the suction port 28 may be an elongated hole elongated in the vertical direction. Furthermore, when a plurality of suction ports 28 are formed, the suction ports 28, 128, 228, etc. having the shapes illustrated in the above-described embodiment and modifications may be used in appropriate combination.

In the above-described embodiment, the case where the upper portion of the straight pipe portion 26 penetrates the container 21 has been described, but the upper portion of the straight pipe portion 26 may not penetrate the container 21 .
In this way, when the upper portion of the straight pipe portion 26 does not penetrate the container 21, for example, as in the third modification shown in FIG. , and a suction port 328 opening upward may be formed at the upper end of the straight tube portion 26 . In this case, the pressure equalizing pipe 35 may be connected to the end plate portion 21B so as to communicate with the curved pipe portion 27 and the internal space S1. By configuring like this third modification, the suction port 328 can be easily formed.

In the above-described embodiment, the case where the straight pipe portion 26 and the internal flow path forming portion 23 both have circular cross-sections perpendicular to the axis O has been described. However, the cross-sectional shapes of the straight tube portion 26 and the internal flow path forming portion 23 are not limited to circular shapes. For example, it may be polygonal.

In the above-described embodiment, the case where the central axes of the straight pipe portion 26 and the internal flow path forming portion 23 are arranged on the axis O has been described, but the present invention is not limited to this configuration.
In the embodiment, the injection port 33 is arranged at the same position as the inner wall surface 21i of the container 21 in the radial direction of the body portion 21A. However, the injection port 33 may be arranged so as to protrude radially inward from the inner wall surface 21 i of the container 21 .

1 First heat exchanger 1a First refrigerant port 1b Second refrigerant port 2 Second heat exchanger 2a First refrigerant port 2b Second refrigerant port 3 Expansion valve 4 Four-way switching valve 4a First port 4b Second port 4c Third Port 4d Fourth port 5 Accumulator 5a Refrigerant inlet 5b Refrigerant outlet 10 Circulation line 21 Vessel 21A Body portion 21B Head plate portion 21Bu Lower surface 21i Inner wall surface 22 U-tube 23 Internal flow passage forming portion 23a Lower edge 23i Inner peripheral surface 23o Outer peripheral surface 23t Upper end portion 24 Inlet pipe 26 Straight pipe portion 26o Outer peripheral surface 27 Bent pipe portions 28, 128, 228 Suction port 31 Lower opening 33 Injection port 35 Pressure equalizing pipe 36 Oil return hole 60 Compressor 65 Suction port 66 Discharge port 100 Refrigerating cycle IL1 First Virtual straight line IL2 Second virtual straight line

Claims (6)

a container having an inner space for gas-liquid separation of the refrigerant, the container having a body portion formed in a cylindrical shape with an axis extending in the vertical direction and two end plate portions closing both end portions of the body portion;
A straight tube portion formed in a circular tube shape centered on the axis extending in the vertical direction in the internal space and having a suction port for taking in a gaseous refrigerant at an upper portion thereof; a U-shaped tube having a curved tube portion formed so as to bend upward from the lower end;
A cross section perpendicular to the axis has a circular shape that is larger in diameter than the straight pipe portion and concentric with the straight pipe portion, has a lower opening facing downward, and has a peripheral wall arranged concentrically with the straight pipe portion . is formed in a cylindrical shape with a constant dimension in the radial direction about the axis, is arranged to cover at least the suction port in the horizontal direction, and allows the gaseous refrigerant to flow from the internal space only through the lower opening. an internal flow path forming portion that forms an internal flow path leading to the suction port;
A jetting port arranged in the same position as the inner wall surface of the container in the radial direction and for jetting a coolant into the inside of the container is provided above a lower edge of the internal flow path forming part , and is viewed from the vertical direction. an inlet pipe in which a first imaginary straight line extending from the injection port in the direction of injecting the refrigerant is inclined with respect to a second imaginary straight line passing through the center of the injection port and the center of the straight pipe portion;
with
The accumulator , wherein the first imaginary straight line passes through a position that does not contact the outer peripheral surface of the straight pipe portion . 2. The accumulator according to claim 1, wherein said suction port is formed in an elliptical shape with a major axis extending in the vertical direction. The accumulator according to claim 1, wherein the suction port is formed in a rectangular shape elongated in the vertical direction. The accumulator according to any one of claims 1 to 3 , wherein a plurality of suction ports are formed at intervals in the circumferential direction and the axial direction of the straight pipe portion. The upper end of the straight pipe portion is arranged at a position covered in the horizontal direction by the internal flow path forming portion,
2. The accumulator according to claim 1, wherein the suction port is formed at the upper end of the straight pipe portion and opens upward. a circulation line through which the refrigerant flows;
The accumulator according to any one of claims 1 to 5 , which separates the refrigerant into gas and liquid;
a compressor for compressing the gaseous refrigerant separated by the accumulator;
a first heat exchanger arranged in the circulation line to exchange heat between the refrigerant flowing through the circulation line and the first medium to change the phase of the refrigerant;
a second heat exchanger arranged in the circulation line to exchange heat between the refrigerant flowing through the circulation line and a second medium to change the phase of the refrigerant;
an expansion valve arranged in the circulation line on the side of the circulation line between the first heat exchanger and the second heat exchanger on which the compressor is not arranged;
refrigeration cycle.

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