JP2014112021A - Gas-liquid separator and refrigeration device with gas-liquid separator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil separator which improves an oil separation performance, improves mass-productivity, is low-priced and improves pressure resistance.SOLUTION: A cylindrical oil separator comprises, in an upper part of an oil storage chamber, a separation chamber which is formed with a diameter equal to or smaller than that of the oil storage chamber. In the oil separator, an oil feed pipe is connected to a lower-end diameter-reduced part of the oil storage chamber, a discharge pipe is connected to an upper-end diameter-reduced part of the separation chamber, further, an inflow pipe for a two-phase flow of oil and a gas refrigerant is introduced from a tangential direction of a separation chamber rising wall, and oil in the refrigerant is separated within the separation chamber using a centrifugal force. When an average height of a space formed from an upper end portion of the inflow pipe, an inner surface of a rising wall higher than the upper end portion of the inflow pipe and an inner surface of a ceiling wall is defined as Hm and an inner diameter of the separation chamber is defined as Di, Hm/Di≤0.25 is satisfied. The separation chamber is configured by contraction, forging or pressing and further the rising wall and the ceiling wall of the separation chamber are configured integrally or separately.

Description

  The present invention relates to a gas-liquid separator that separates a liquid phase from a liquid phase and a gas phase two-phase flow such as a refrigeration cycle and a vapor cycle, and a technique for obtaining a device such as a refrigeration apparatus and a vapor cycle using the same.

There exists patent document 1 (Unexamined-Japanese-Patent No. 2009-109102) in the example of the conventional gas-liquid separator.
In this case, as described in Patent Document 1, the two-phase flow of the oil and the gas refrigerant taken into the chamber 35 from the inflow pipe 31 is swirled by centrifugal force, and the oil is converted from the gas refrigerant to the oil in the chamber 35. The oil is stored in the oil storage part and returned to the compressor or the like through the oil feed pipe 40 at the bottom.
In this, a cylindrical tube is made by machining the chamber 35 and the oil storage part from a round bar, and this is used as the chamber 35 and the oil storage part 37. Therefore, the material cost as well as the processing cost are increased, and this is provided. The refrigeration equipment was expensive.
Further, in this case, the inflow pipe 31 is introduced into the chamber 35 from the tangential direction of the chamber 35. Regarding the influence of the upper space of the inflow pipe formed above the inflow pipe 31 on the oil separation performance. I did not consider it at all.

  In the gas-liquid separator of Patent Document 2 (Patent No. 2011-247575), an inlet pipe 2 and a gas-phase outlet pipe 3 are provided at the upper part of the container 1, and the two-phase flow flowing from the inlet pipe is separated from the liquid phase and the gas by centrifugal force. Although they are separated into phases, no consideration was given to the influence of the upper space of the inlet pipe 2 on the gas-liquid separation performance.

  JP 2009-109102 A   JP2011-247575A

Since the oil separator shown in Patent Document 1 is machined in each of the swivel unit and the oil storage chamber, there are problems such as poor mass productivity and high cost.
Another problem is to clarify the influence of the upper space of the inflow pipe formed above the inflow pipe on the oil separation performance.

As shown in FIG. 1 of Patent Document 2, in the conventional centrifugal force type oil separator, the positional relationship between the inlet of the inlet pipe and the inlet of the outlet pipe is from the inlet of the inlet pipe to the inlet of the outlet pipe. And the suction port of the discharge pipe is generally configured at a position lower than the inflow pipe.
In addition, in an oil separator processed by a throttle or the like, an inflow pipe upper space is inevitably formed in the upper part of the upper end surface of the inflow pipe, as shown in FIG. The effects were not considered.

  The present invention has been made in order to solve the above-mentioned problems, and an object of the present invention is to provide an oil separator having good oil separation performance, mass productivity, low cost, and excellent pressure resistance. It is in.

The present invention has been made for the purpose of solving the above problems.
That is, a cylindrical gas-liquid separator having a separation chamber formed at the upper part of the liquid storage chamber having the same diameter as or smaller than the diameter of the liquid storage chamber, and the liquid is fed to the lower diameter reduced portion of the liquid storage chamber. Connect the pipe and the discharge pipe to the reduced diameter part of the upper end of the separation chamber, and introduce the inflow pipe of the two-phase flow of liquid phase and gas phase from the tangential direction of the rising wall of the separation chamber, and use centrifugal force In a gas-liquid separator configured to separate a liquid phase and a gas phase two-phase flow in a separation chamber, a space formed by an upper end of the inflow pipe, an inner surface of the rising wall above the upper end of the inflow pipe, and an inner surface of the ceiling wall When the average height is Hm and the inner diameter of the separation chamber is Di, Hm / Di ≦ 0.25, and the separation chamber is configured by drawing, forging, or pressing, and the rising wall of the separation chamber This is a gas-liquid separator in which the ceiling wall is constructed as a single body or as a separate body.

  Further, with respect to a tangent of a circle with a radius R at a connection point X between an arc having a radius R (hereinafter referred to as a corner arc radius R) connecting the rising wall inner surface and the ceiling wall inner surface and a ceiling wall inner surface arc connecting smoothly. This is a gas-liquid separator in which an angle θ (hereinafter referred to as an angle θ) formed by a plane perpendicular to the axis of the outer body is 5 degrees ≦ θ ≦ 28 degrees.

  Further, the gas-liquid separator has a radius R of the corner arc of R ≦ 2.5 mm.

  In addition, from the tangential direction of the rising wall of the separation chamber, an inclined portion is formed by crushing a part of the side of the pipe facing the discharge pipe toward the center of the pipe at the tip of the inflow pipe introduced into the separation chamber. This is a gas-liquid separator that avoids the discharge pipe provided at the substantially axial center of the separation chamber at the inclined portion.

  Further, the inner surface of the ceiling wall constituting the separation chamber is a rough surface, which is a gas-liquid separator in which the swirling flow velocity is reduced to suppress the rise of the two-phase flow of liquid, liquid phase and gas phase.

  In addition, the gas-liquid separator has a lower diameter smaller than an upper diameter in the separation chamber to prevent the centrifugal force from increasing or decreasing.

  In addition, the separator is a gas-liquid separator in which the discharge pipe of the separator and a connector connected to the cycle are integrated.

  In addition, the throttle, the separation chamber, and the liquid storage chamber that connect the discharge pipe of the outer shell configured in the cylindrical gas-liquid separator are integrally formed, and the lid is configured at the lower end of the liquid storage chamber. It is a gas-liquid separator.

  In addition, the gas-liquid separator is formed by integrally forming a throttle portion that connects a discharge pipe of an outer shell constituting the cylindrical gas-liquid separator, a separation chamber, and a liquid storage chamber.

  Further, the gas-liquid separator is provided with a reinforcing bead on the outer periphery of the outer shell of the cylindrical gas-liquid separator.

  In addition, the outer body constituting the cylindrical gas-liquid separator is an A outer body and a B outer body, and the A outer body is a cylindrical outer shell formed with an upper diameter-reduced portion connecting a discharge pipe, a separation chamber, and a liquid storage chamber. The outer shell B is a lid that covers the bottom of the liquid storage chamber, a liquid reservoir that guides the liquid to the liquid feed pipe side, and a gas-liquid formed with a lower diameter reduced diameter portion to which the liquid feed pipe is connected. Separator.

  In addition, the gas-liquid separator is configured such that a locking piece provided on the outer periphery of the baffle plate is locked in a concave groove provided in a lower portion of the separation chamber by utilizing elastic deformation of the baffle plate.

  Further, the gas-liquid separator is configured such that the wall of the rising wall constituting the separation chamber is thicker than the thickness of the liquid storage chamber, and a concave groove for fixing the baffle plate is formed at the thickly configured position.

  Moreover, the gas-liquid separator provided with the said structure is the freezing apparatus provided in the refrigerating cycle.

  Moreover, it is a steam cycle apparatus which provided the gas-liquid separator provided with the said structure in the steam cycle.

  In the oil separator of the present invention, the separation chamber is formed by drawing, forging, or pressing, and the rising wall and the ceiling wall of the separation chamber are formed integrally or separately to form an inflow pipe formed at the upper part of the separation chamber. Since the upper space is minimized, the oil separator has good oil separation performance, mass productivity, low cost, and excellent pressure resistance.

  It is a section explanatory view showing Embodiment 1 of an oil separator provided with the present invention.   It is AA sectional drawing of FIG.   It is a principal part enlarged view of the oil separator of FIG.   It is principal part explanatory drawing of the oil separator of FIG.   It is the Q section enlarged view of FIG.   It is explanatory drawing which shows the relationship between Hm / Di and oil separation performance.   It is explanatory drawing which shows the relationship between angle (theta) and oil separation performance.   It is explanatory drawing which shows the relationship between the radius R of a corner circular arc, and oil separation performance.   It is an example in which a ceiling partition plate is provided in the upper part of the separation chamber in a sectional view showing the second embodiment different from FIG.   It is sectional drawing of the separator explaining other Embodiment 2 of this invention, and is the example which provided the separate separation chamber ceiling wall in the separation chamber upper part.   It is sectional drawing of the oil separator explaining Embodiment 3 different from FIG.   It is sectional drawing of the oil separator explaining Embodiment 4 different from FIG.   It is sectional drawing explaining the fixing structure of the baffle board different from the baffle board used for FIG. (Embodiment 5)   It is sectional drawing of the oil separator explaining the separation chamber structure different from FIG. (Embodiment 6)   FIG. 2 is a cross-sectional view of an oil separator in which a separation chamber and an oil storage chamber of FIG. (Embodiment 7)   It is sectional drawing of the oil separator which comprised the separation chamber and oil storage chamber of FIG. 1 with the same diameter. (Embodiment 8)   It is an oil separator explaining other Embodiment 9 of this invention.   It is a perspective view of the oil separator explaining Embodiment 10 different from FIG.   It is a front view of FIG. (Embodiment 10)   It is a top view of FIG. (Embodiment 10)   It is a front view of the oil separator explaining Embodiment 10 different from FIG.   It is a front view of the oil separator explaining Embodiment 10 different from FIG.   It is a front view of the oil separator explaining Embodiment 10 different from FIG.   It is a front view of the oil separator explaining Embodiment 10 different from FIG.   It is a front view of the oil separator explaining Embodiment 10 different from FIG.   It is explanatory drawing which incorporated the oil separator provided with this invention in the freezing apparatus. (Embodiment 11)   It is explanatory drawing which incorporated the oil separator provided with this invention in the steam cycle apparatus as a mist separator. (Embodiment 12)

  Embodiments of the present invention will be described below with reference to the drawings. In addition, this invention is not limited by this embodiment.

Embodiment 1

The first embodiment will be described with reference to FIGS.
1 is a cross-sectional view showing an oil separator according to a first embodiment including the present invention, FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1, and FIG. 3 is a schematic diagram of the oil separator including the present invention. FIG. 4 is an explanatory view of a main part of an oil separator provided with the present invention, and FIG. 5 is an enlarged view of a Q part in FIG.
In FIG. 1 to FIG. 5, reference numeral 1 denotes a cylindrical oil separator that is incorporated in a refrigeration cycle or the like. The oil separator 1 is formed in the upper part of the oil storage chamber 3 to have a diameter smaller than the diameter of the oil storage chamber 3. A separation chamber 4 is provided. Reference numeral 12 denotes a slope provided at the upper portion of the oil storage chamber 3. The slope 12 connects the inner diameter of the oil storage chamber 3 and the inner diameter of the separation chamber 4 together. The outer body 2 of the oil separator 1 is composed of an oil storage chamber 3 and a separation chamber 4 which are formed by drawing, forging, pressing or the like. The separation chamber 4 includes a rising wall 4a and a downward bellmouth shaped ceiling wall 4b. The upper diameter reduced portion 6 is formed so as to be connected to the downward bellmouth-shaped ceiling wall 4b. Further, a discharge pipe 8 is connected to the upper diameter reduced diameter portion 6. Further, the separation chamber 4 has an inflow pipe 9 for taking the two-phase flow of oil and gas refrigerant into the separation chamber 4 from the tangential direction of the separation chamber 4. The inflow pipe 9 is located in the upper part of the oil separator 1.

As shown in FIG. 2, the inflow pipe 9 is introduced into the separation chamber 4 from the tangential direction of the separation chamber 4. In addition, the inflow pipe 9 has an inclined part 9a at the distal end portion, which is a part of the pipe facing the discharge pipe 8 in a direction toward the pipe center side. The inflow pipe 9 is disposed so as to pass through the discharge pipe 8 introduced into the substantially axial center of the separation chamber 4 by the inclined portion 9a and to approach the rising wall inner surface 4c constituting the separation chamber 4, It is configured not to hit the discharge pipe 8. Then, the two-phase flow of the oil droplet 30 and the gas refrigerant flowing in from the inflow pipe 9 is vigorously applied to the rising wall 4a of the separation chamber 4, and the two-phase flow of the oil droplet 30 and the gas refrigerant is swirled to cause the oil to flow by centrifugal force. The separation is performed efficiently.
The discharge pipe suction port 8a of the discharge pipe 8 reaches the vicinity of the flat baffle plate 13a provided at the bottom of the separation chamber 4.

  The flat baffle plate 13a is locked to the rising wall 4a. Further, a bead 11 is provided on the outer shell 2a. Further, an A lid 14a covering the bottom of the oil storage chamber 3 and a B outer body 2b forming a lower end reduced diameter portion 5 are welded to the lower end of the A outer body 2a, and the lower end reduced diameter portion 5 of the B outer body 2b is fed to the lower end reduced diameter portion 5. An oil pipe 7 is connected. The A lid 14a has been drawn, forged, or pressed.

In the above configuration, the operation of oil separation in the separation chamber 4 will be described below.
In the oil separator 1 shown in FIG. 3, the action of promoting oil separation in the separation chamber 4 is that most of the two-phase flow of oil and gas refrigerant flowing into the separation chamber 4 from the inflow pipe 9 is in the separation chamber 4. It flows below the inflow pipe 9 while swirling along the rising wall inner surface 4c like the A swirl flow 37a. Meanwhile, the oil droplets 30 having a larger specific gravity than the gas refrigerant become a downward oil film 31 along the rising wall inner surface 4c of the separation chamber 4 by the centrifugal force generated by the A swirl flow 37a and flow into the lower oil storage chamber 3 while swirling. . On the other hand, as an action to prevent oil separation, in the oil separator 1 shown in FIG. 3, the gas refrigerant from which the oil has been separated turns into the A swirl flow 37 a while swirling in the separation chamber 4, and reaches the lower part of the discharge pipe 8 to be discharged. It is sucked from the tube suction port 8a. In this type of oil separator, depending on the use conditions, fine oil droplets 30 may not be captured on the rising wall inner surface 4c of the separation chamber 4 by centrifugal force, and the fine oil droplets 30 that could not be captured are discharged. It is sucked together with the gaseous refrigerant from the pipe suction port 8a, and this phenomenon makes it difficult to make the oil separation performance 100%.

  On the other hand, the factor that lowers the oil separation performance is also in the inflow pipe upper space 4e above the inflow pipe upper end portion 9b. The problem will be described below. The inflow pipe upper space 4e is a space constituted by an inflow pipe upper end portion 9b, a rising wall inner surface 4c and a ceiling wall inner surface 4d above the inflow tube upper end portion 9b. As shown in FIG. 3 and FIG. 4, when the inflow pipe upper space 4e exists on the inflow pipe upper end portion 9b, a part of the two-phase flow that flows into the separation chamber 4 from the inflow pipe 9 enters the inflow pipe upper space 4e. The two-phase flow flows upward while swirling like a B swirl flow 37b in the inflow pipe upper space 4e. Here, the oil droplet 30 having a larger specific gravity than the gas refrigerant becomes an upward oil film 32 along the rising wall inner surface 4c of the separation chamber 4 due to the centrifugal force generated by swirling, and flows upward while swirling. It reaches a connection point Q (hereinafter referred to as Q point) between the arc R of radius R (hereinafter referred to as corner radius R) connecting the ceiling wall inner surface 4d and the rising wall inner surface 4c. At this time, as shown in FIG. 5, the angle θ formed by the tangent of the circle of radius R at the connection point X between the radius R of the corner arc and the ceiling wall inner surface arc smoothly connected and the plane perpendicular to the axis of the outer shell When the angle (hereinafter referred to as the angle θ) is large, the oil that has reached the point Q while turning along the separation chamber rising wall inner surface 4c further flows along the ceiling wall inner surface 4d. Thereafter, the oil becomes an oil film 33 along the outer surface of the discharge pipe, falls, and is sucked together with the gaseous refrigerant from the lower end of the discharge pipe suction port 8a, which causes a decrease in oil separation performance. In order to prevent the deterioration of the oil separation performance, the flow of the upward oil film 32 that attempts to rise to the ceiling wall inner surface 4d side through the Q point is reduced by reducing the angle θ. The upward rising oil film 32 is a flow that rises while swirling like the B swirling flow 37b. Further, it is possible to reduce the radius R (shown in FIG. 5) of the corner arc.

  On the other hand, the two-phase gaseous refrigerant flowing into the inflow pipe upper space 4e also flows upward while swirling in the upper part of the inflow pipe, but is discharged from the inner surface 4d of the ceiling wall of the inflow pipe upper space 4e as shown by the broken line in FIG. A downward gas flow 34 along the vicinity of the pipe is obtained. At that time, the fine oil droplets 30 that cannot be separated are entrained, and the fine oil droplets 30 are sucked together with the gaseous refrigerant from the discharge pipe suction port 8a, which causes a decrease in oil separation performance.

All the phenomena described above are caused by the oil droplets 30 in the inflow pipe upper space 4e. The smaller the volume V of the inflow pipe upper space 4e, the smaller the amount of oil droplets 30 present in that space. By reducing the volume V of the pipe upper space 4e, the cause of the decrease in oil separation performance can be eliminated.
Based on the above concept, the relationship between Hm / Di and oil separation performance, angle θ and oil separation performance, and the radius R of the corner arc and oil separation performance are clarified through experiments, respectively. It is shown in FIG.

なお、ＯＣＲとは、Ｏｉｌ Ｃｉｒｃｕｌａｔｉｏｎ Ｒａｔｉｏ の略である。
図６に示すとおり、油分離性能にはＨｍ／Ｄｉ＝０．２５に変曲点があり、Ｈｍ／Ｄｉ≦０．２５とすることで良好な油分離効果を発揮する。
なお、このときの入口流量をＧｉ、当該油分離器の許容最大流量をＧｍａｘとしたとき、Ｇｉ／Ｇｍａｘ＝０．４〜０．６の場合である。FIG. 6 shows the relationship of oil separation performance with respect to Hm / Di. Here, the value obtained by dividing the volume V of the inflow pipe upper space 4e by the separation chamber horizontal sectional area S is the average height Hm of the inflow pipe upper space 4e. Therefore, Hm / Di means a dimensionless average height obtained by dividing the average height Hm by the separation chamber diameter Di. The oil separation performance on the vertical axis is a value obtained by the following equation when the oil content of the two-phase flow flowing in from the inflow pipe 9 is OCR1 and the oil content of the two-phase flow flowing out of the discharge pipe 8 is OCR2. is there.

OCR is an abbreviation for Oil Circulation Ratio.
As shown in FIG. 6, the oil separation performance has an inflection point at Hm / Di = 0.25, and a good oil separation effect is exhibited by setting Hm / Di ≦ 0.25.
In this case, Gi / Gmax = 0.4 to 0.6, where Gi is the inlet flow rate and Gmax is the maximum allowable flow rate of the oil separator.

FIG. 7 shows the relationship between the angle θ and the oil separation performance, where the horizontal axis is the angle θ and the vertical axis is the oil separation performance. From this figure, the performance degradation becomes significant when the angle is larger than 28 degrees. Therefore, by setting the angle θ ≦ 28 degrees, the flow of oil going up to the ceiling wall inner surface 4d side is divided, so that a good oil separation effect is exhibited.
The concept of the lower limit value of the angle θ will be described below. In FIG. 4, 4 is a separation chamber, 4a is a rising wall, 4b is a ceiling wall of the separation chamber, and 6 is a reduced diameter portion at the upper end.
In the figure, when processing the ceiling wall 4b, the ceiling wall inner surface 4d may be processed to have an angle of 0 degrees in order to reduce the volume V of the inflow pipe upper space 4e described above. When processing is performed, the amount of plastic deformation at the time of processing increases, so the processing time becomes longer. Therefore, since the machining time can be shortened by setting the angle θ to 5 degrees or more instead of 0 degrees, the lower limit angle is set to 5 degrees, and the range of the angle θ is set to 5 degrees ≦ angle θ ≦ 28 degrees. .

  FIG. 8 shows the relationship between the radius R of the corner arc and the oil separation performance. The horizontal axis is the radius R of the corner arc, and the vertical axis is the oil separation performance. From this figure, when the radius R of the corner arc is larger than 2.5 mm, the performance deterioration becomes remarkable. Therefore, by setting the radius of the corner arc R ≦ 2.5 mm, the flow of the oil going to rise toward the ceiling wall inner surface 4d side is divided, so that a good oil separation effect is exhibited.

  As described above, the volume V of the inflow pipe upper space 4e is reduced by reducing the angle θ, reducing the radius R of the corner arc, and making the ceiling wall inner surface 4d downward bellows as shown in FIG. Can be reduced, good oil separation performance can be obtained, and the overall height can be reduced.

  Furthermore, by making the ceiling wall inner surface 4d rough, it is possible to suppress the increase in the two-phase flow of oil and oil and gas refrigerant that lowers the swirling flow velocity and rises toward the ceiling wall inner surface 4d side, and has good oil separation performance. can get.

  Further, in the present embodiment of FIG. 1, an oil sump 10 is provided in the A lid 14 a that covers the bottom of the oil storage chamber 3, and oil is easily guided to the oil feed pipe 7 even when the oil separator 1 is inclined.

  In this embodiment, the A lid body 14a is welded in accordance with the diameter of the lower end portion of the outer body 2 to be divided into two parts, so that options such as drawing, forging, and pressing can be expanded as a processing method for the A outer body 2a. At the same time, it is possible to check the finish of the internal configuration, increasing reliability.

Next, the baffle plate will be described.
The action and effect of the baffle plate are prevention of winding-up due to the swirling flow of oil in the oil storage chamber and suppression of oil swirling in the oil storage chamber. The baffle plate may constitute an oil separator without being provided depending on the application.
In FIG. 1, 13a is a flat baffle plate, and 13c is a hole for flowing oil provided in the flat baffle plate 13a.

  In order to lock the position of the flat baffle plate 13a in the axial direction and the height direction with high accuracy, the rising wall inner surface 4c of the A outer body 2a may be cut. In the present invention, the thickness (t2) of the separation chamber rising wall 4a processed to be thicker than the oil storage chamber 3 side wall thickness (t1) is set to be thick in advance, and the dimensions of the cutting process are taken into consideration.

  The flat baffle plate 13a is generally fixed by plastically deforming the outer periphery of the rising wall 4a. The flat plate baffle plate 13a is fixed using a punch or the like on the outer periphery of the rising wall 4a. It is partially punched to form and fix the A protrusion piece 15a. Also in this case, since the rising wall 4a is thickened in advance, the axial and height positions of the flat baffle plate 13a can be accurately locked without impairing pressure resistance. Further, the flat baffle plate 13a can be fixed by continuously forming the baffle plate 13a in the outer peripheral direction of the outer shell 2 like a B projection piece 15b shown in FIG.

  Reference numeral 11 denotes a reinforcing bead. This reinforcing bead 11 is provided on the outer peripheral portion of the outer body 2 to increase the rigidity of the outer body 2 and increase the pressure resistance, and to minimize deformation of the oil storage chamber. By forming a plurality of reinforcing beads 11 as required, even a thin-walled material can have pressure resistance and can be made inexpensive.

Embodiment 2

The second embodiment will be described with reference to FIGS. 9 and 10.
In Embodiment 1, the rising wall 4a and the ceiling wall 4b forming the separation chamber 4 are integrated, and the inflow pipe upper space 4e is included up to the space formed by the ceiling wall 4b as shown in FIG. In the second embodiment, the space formed by the ceiling wall 4b is eliminated. That is, what is shown in FIG. 9 is provided with a ceiling partition plate 35, and FIG. 10 is a separate ceiling wall of the separation chamber 4. By doing so, the volume V of the inflow pipe upper space 4e can be reduced and the oil separation performance can be improved. In the embodiment shown in FIGS. 9 and 10, the above-described corner R can be eliminated.
That is, FIG. 9 and FIG. 10 of the third embodiment will be described with reference to FIG.
6, since Hm / Di can be further reduced as compared with the first embodiment, high oil separation performance can be obtained.
As the first means, as shown in FIG. 9, the ceiling partition plate 35 is provided on the upper portion of the rising wall 4 a, and the ceiling partition plate lower surface 35 a substantially functions as the ceiling wall of the separation chamber 4. The ceiling partition plate 35 is fixed to the discharge pipe 8. In such a configuration, the volume V of the inflow pipe upper space 4e can be reduced by reducing the distance H between the ceiling partition plate lower surface 35a and the inflow pipe upper end portion 9b as much as possible, and Hm / Di ≦ 0.25. realizable. Moreover, even if it is the structure which fills the part above the ceiling partition plate lower surface 35a position, an effect | action and an effect are the same.
9 is the same as that of FIG. 1 except for the above-described configuration, and the operation and effect thereof are the same.
The second means uses the ceiling wall of the separation unit 4 shown in FIG. 10 as a separate separation chamber ceiling wall 36 and is joined to the rising wall 4 a of the separation unit 4. In such a configuration, by reducing the distance H between the separate separation chamber ceiling wall inner surface 36a and the inflow pipe upper end portion 9b as much as possible, the volume V of the inflow pipe upper space 4e can be reduced, and Hm / Di ≦ 0. .25 can be realized.
Except for the above-described configuration in FIG. 10, the configuration is the same as that in FIG. 1, and the operation and effect are the same.

Embodiment 3

The third embodiment will be described with reference to FIG.
In the first embodiment, the A lid 14a is welded in accordance with the diameter of the lower end portion of the outer body 2, but in the third embodiment, the cutting that covers the bottom of the oil storage chamber 3 as shown in FIG. A B lid body 14b formed by processing or the like is welded to form a B lid body 14b.
By cutting the B lid 14b, the position of the oil feeding pipe 7 can be easily changed to an arbitrary position of the B lid. Furthermore, it is set as the structure which expands the choice of the welding method by changing the thickness of B cover 14b. Further, the B lid 14b is provided with a B lid inclined portion 29 so that the oil can be easily guided to the oil feeding pipe 7 even when the oil separator 1 is inclined.
Except for the above configuration in FIG. 11, the configuration is the same as that in FIG. 1, and the operation and effect are the same.

Embodiment 4

The fourth embodiment will be described with reference to FIG.
In the first embodiment, the A lid 14a is welded according to the diameter of the lower end portion of the outer body 2. However, in the fourth embodiment, the oil reservoir chamber diameter of the outer body 2 is reduced as shown in FIG. The diameter of the part B21 is reduced, and the C lid 14c is welded in accordance with the reduced diameter.
By reducing the diameter of the lower end of the outer body 2, the weld length with the C lid 14c is shortened, and the reliability can be increased. Furthermore, since the pressure receiving area of the C lid 14c is reduced and the force acting on the C lid 14c is reduced, the pressure resistance is excellent. The oil separator 1 is configured such that the inner diameter of the throttle portion 2 of the outer body 2 to which the C lid 14c is welded is larger than the outer diameter of the baffle plate, and the baffle plate can be incorporated into the separation chamber 4 from the oil storage chamber 3 side.
Other than the above-described configuration in FIG. 12, the configuration is the same as in FIG. 1, and the operation and effect are the same.

Embodiment 5

Embodiment 5 will be described with reference to FIG.
In the first embodiment, the flat baffle plate 13a is partially punched from the outer periphery using a punch or the like (t2) of the separation chamber rising wall 4a processed to be thicker than the oil storage chamber 3 side wall thickness (t1). It was the structure which fixes it with A protrusion piece 15a. Another means will be described in Embodiment 5 with reference to FIG. As shown in FIG. 13, the spring baffle plate 13b has a hole 13c for flowing oil, and an elastic locking piece 13d is provided on the outer periphery of the spring baffle plate 13b. Reference numeral 17 denotes a groove provided on the rising wall inner surface 4 c side of the separation chamber 4, which is a groove for locking the locking piece 13 d of the spring baffle plate 13, and this groove is formed on the rising wall 4 a of the separation chamber 4. It is provided by machining. The locking piece 13d of the spring baffle plate 13b can be fitted into the concave groove 17 while being elastically deformed, and can be easily fixed.
Except for the above-described configuration in FIG. 13, the configuration is the same as in FIG. 1, and the operations and effects are the same.

Embodiment 6

Embodiment 6 will be described with reference to FIG.
In FIG. 14, 1 is an oil separator, 2 is an outer body, 3 is an oil storage chamber, 4 is a separation chamber, 5 is a reduced diameter portion at the lower end, 6 is a reduced diameter portion at the upper end, 7 is an oil supply pipe, 8 is a discharge pipe, 9 Is an inflow pipe, and 13a is a flat baffle plate.
In the oil separator 1 shown in the present embodiment, the lower diameter 28 is made thinner than the upper diameter 27 of the separation chamber 4 with respect to the first embodiment.
With this configuration, in the separation chamber 4, the oil separation performance can be improved by gradually increasing or preventing the centrifugal force from decreasing downward.
14 is the same as FIG. 1 except for the above-described configuration in FIG.

Embodiment 7

Embodiment 7 will be described with reference to FIG.
In FIG. 15, 1 is an oil separator, 2c is an integral outer body having the same diameter and integrated with the separation chamber 4 and the oil storage chamber 3, and a downward bellmouth shaped ceiling wall is formed on the upper portion of the integral outer body 2c. 4b is connected to an upper end reduced diameter portion 6 at the upper part of the ceiling wall 4b, and a discharge pipe 8 is connected thereto. An oil storage chamber reduced diameter portion 20 is provided at the lower portion, a lower end reduced diameter portion 5 is connected to the lower portion of the oil storage chamber reduced diameter portion 20, and an oil feed pipe 7 is connected thereto.
In FIG. 15, the structure without the baffle plate is used, but the separation chamber 4 at this time is substantially above the two-dot chain line. In this case, the outer body can be integrally formed without being divided, and the reliability is improved by reducing the number of joints, and the number of processing steps is shortened. When a baffle plate is configured, the diameter of the upper diameter reduced portion 6 or the lower diameter reduced portion 5 may be reduced after the baffle plate is inserted and fixed.
Other than the above configuration in FIG. 15, the configuration is the same as that in FIG.

Embodiment 8

Embodiment 8 will be described with reference to FIG.
In FIG. 16, 1 is an oil separator, 2 is an outer body, 3 is an oil storage chamber, 4 is a separation chamber, 5 is a reduced diameter portion at a lower end, 6 is a reduced diameter portion at an upper end, 7 is an oil supply pipe, 8 is a discharge pipe, 9 Is an inflow pipe, and 13a is a flat baffle plate.
In the oil separator 1 shown in the present embodiment, the separation chamber 4 and the oil storage chamber 3 described above are formed with the same diameter.
Further, the upper and lower sides of the flat baffle plate are fixed by the protruding pieces 15b. By the protruding piece 15b, the same operation and effect as the bead 11 can be obtained.
Except for the above-described configuration in FIG. 16, the configuration is the same as in FIG. 1, and the operation and effect are the same.

Embodiment 9

Embodiment 9 will be described with reference to FIG.
16 is an integrated connector, 4a is a rising wall, 4c is an inner surface of the rising wall, 4b is a ceiling wall having a downward bell mouth shape, 4d is an inner surface of the ceiling wall, 9 is an inflow pipe, 9b is an upper end surface of the inflow pipe, 6 The upper diameter reduced portion, 19 is a brazing material, and 18 is a brazing material receiving portion. The brazing material receiving portion 18 is formed at the time of manufacturing the previous A outer body 2a.
Here, the inner side of the integrated connector 16 is configured to match the inner diameter of the discharge pipe 8 of FIG. 1, and the outer side is configured to have a larger outer diameter as close as possible to the inflow pipe upper end portion 9a of the inflow pipe 9. Thus, the inflow pipe upper space 4e can be reduced, and the separation performance can be improved.
Further, by using the integrated connector 16, the product can be reduced in size and the reliability in welding is increased.
In addition, when the upper diameter reduced portion 6 is configured, the brazing material receiving portion 18 is processed to be thick so that the brazing material 19 used when welding the integrated connector 16 is held by the brazing material receiving portion 18, and the ceiling wall 4b is prevented from overflowing.
Except for the above-described configuration in FIG. 17, the configuration is the same as that in FIG. 1, and the operation and effect are the same.

Embodiment 10

The tenth embodiment will be described with reference to FIGS.
In the figure, 1 is an oil separator, 2 is an outer body, 3 is an oil storage chamber, 4 is a separation chamber, 5 is a reduced diameter portion at the lower end, 6 is a reduced diameter portion at the upper end, 7 is an oil supply pipe, 8 is a discharge pipe, 9 is It is an inflow pipe.
In the oil separator 1 shown in the present embodiment, FIG. 18 is formed by integrally forming the outer body 2 (A outer body, B outer body), FIG. 19 is a front view of FIG. 18, and FIG. FIG. FIG. 21 shows the separation chamber 4 and a part of the oil storage chamber formed by the A outer body 2a, and the oil storage chamber 3 formed by the B outer body 2b, and FIG. 22 shows that the B outer body 2b of FIG. It is divided into parts. Further, what is shown in FIG. 23 to FIG. 25 is one in which the outer body 2 is divided or changed in combination within the scope of the present invention.
In FIGS. 18 to 25, each of the outer shells 2a is configured such that the separation chamber is formed by drawing, forging, or pressing, and the rising wall and the ceiling wall of the separation chamber are formed integrally or separately. is there.
18 to 25, the oil feeding pipe 7, the discharge pipe 8, and the inflow pipe 9 are not straight pipes but may be bent in an arbitrary direction. Furthermore, the outer diameter ratio between the separation chamber and the oil storage chamber is not limited and can be changed as appropriate, facilitating application to a product. 18 to 24 may be configured as a separate separation chamber ceiling wall 36 as shown in FIG.
Others have the same configuration as the first embodiment, and have the same effect.

Embodiment 11

An example in which the oil separator described above is applied to a refrigeration apparatus such as an air conditioner will be described with reference to FIG.
In FIG. 26, the refrigerant evaporates in the evaporator 25, where it takes heat and gasifies, and the gaseous refrigerant is sucked and compressed by the compressor 22. The high-temperature and high-pressure gas refrigerant discharged from the compressor 22 flows out of the compressor 22 with oil for lubricating and sealing required in the compressor. When the contained oil stays in parts other than the compressor 22, the lubricating action of the compressor 22 is lost, and in some cases, the compressor 22 may break down. In addition, if the heat stays in the condenser 23 and the evaporator 25 for heat exchange, the heat exchange efficiency is lowered and the capacity of the entire air conditioner is lowered. Therefore, an oil separator is disposed downstream of the compressor 22. Is provided.
The oil separator 1 described above is applied to this oil separator.

The two-phase flow of oil and gaseous refrigerant that has entered the separation chamber 4 from the compressor 22 via the inflow pipe 9 is swirled by centrifugal force to separate the oil. Then, the separated gas refrigerant goes out to the condenser 23 side from the discharge pipe 8, and the separated oil is accumulated in the oil storage chamber 3. The accumulated oil returns to the compressor 22 through the oil feed pipe 7 due to a high-low pressure difference in the compressor 22, and lubricates the bearing portion and the sliding portion of the compressor 22.
The gaseous refrigerant discharged from the discharge pipe 8 of the oil separator 1 becomes a liquid refrigerant by exchanging heat with the outside in the condenser 23, and enters the evaporator 25 through the expansion valve 24.
By repeating this, the air conditioner ensures a predetermined performance.
At this time, the oil separator 1 provided with the present invention has the effects described above.

Embodiment 12

Embodiment 12 will be described with reference to FIG.
In the above embodiment, the oil was separated as an example. However, this separator is not limited to oil, and water mist can be used as a mist separator.
Next, an example in which the above-described mist separator is applied to a steam cycle device will be described with reference to FIG.
In FIG. 27, the water compressed by the feed water pump 38 is heated by the boiler 39 to become high-pressure steam. At this time, water droplet mist is mixed in the high-pressure steam, and when the water droplet mist flows into the turbine 40, the turbine blade is damaged. Therefore, the mist separator 1 is provided before entering the turbine 40, the high-pressure steam mixed with the water droplet mist is introduced from the inflow pipe 9 to the mist separator 1, and the high-pressure steam from which the water droplet mist has been removed is transferred from the discharge pipe 8 to the turbine 40. Lead. The high-pressure steam expands in the turbine 40 to generate power, and the generator 41 generates power. The expanded low-pressure steam condenses in the condenser 42, becomes water, and is supplied to the feed water pump 38. On the other hand, the water droplet mist separated by the mist separator 1 is returned to the suction side of the water supply pump 38 from the liquid feeding pipe 7.
By repeating this, the steam cycle apparatus ensures a predetermined function.
As described above, the gas-liquid separator of the present invention can be extended to the above cycle.

Since the present invention has the configuration described above, it has the following effects.
That is, a cylindrical oil separator having a separation chamber formed in the upper part of the oil storage chamber having the same diameter as or smaller than the diameter of the oil storage chamber, and an oil feed pipe is separated at the lower diameter reduced portion of the oil storage chamber. A discharge pipe is connected to each of the upper diameter-reduced portions of the chamber, and an inflow pipe for two-phase flow of oil and gas refrigerant is introduced from the tangential direction of the rising wall of the separation chamber, and the oil and gas are separated in the separation chamber using centrifugal force. In the oil separator configured to separate the two-phase flow of the refrigerant, the average height of the space formed by the rising pipe inner surface and the ceiling wall inner surface above the inlet pipe upper end and the inlet pipe upper end is Hm, and the separation chamber When the inner diameter of the separator is Di, Hm / Di ≦ 0.25, the separation chamber is formed by drawing, forging, or pressing, and the rising wall and ceiling wall of the separation chamber are integrated or separated. It is the comprised oil separator.
This makes it possible to reduce the space that impedes performance (= inlet pipe upper space), perform efficient oil separation, and reduce the size of the oil separator.

Further, a tangent line of a circle of radius R at a connection point X between an arc of radius R connecting the inner surface of the rising wall and the inner surface of the ceiling wall and an arc of the ceiling wall inner surface connected to the slider and a plane perpendicular to the axis of the outer shell In this oil separator, the angle θ formed is 5 degrees ≦ θ ≦ 28 degrees.
This makes it possible to reduce the space that hinders performance (= the upper space of the inflow pipe) as well as the mass productivity, and to reduce the two-phase flow of oil and gas refrigerant toward the ceiling wall. Since it can suppress, efficient oil separation can be performed and the size of the oil separator can be reduced.

Further, the oil separator has an arc of radius R connecting the inner surface of the rising wall and the inner surface of the ceiling wall, with R ≦ 2.5 mm.
This reduces the volume of the space that hinders performance (= inlet pipe upper space), suppresses the flow of oil and gas refrigerant to the ceiling wall side, and enables efficient oil separation. In addition, the oil separator can be miniaturized.

In addition, from the tangential direction of the rising wall of the separation chamber, an inclined portion is formed by crushing a part of the side of the pipe facing the discharge pipe toward the center of the pipe at the tip of the inflow pipe introduced into the separation chamber. The oil separator is configured to avoid the discharge pipe provided in the substantially axial center of the separation chamber at the inclined portion.
As a result, it is possible to prevent the two-phase flow of oil and gas refrigerant flowing into the separation chamber from the inflow pipe from spreading to the center side of the separation chamber, so that efficient oil separation can be achieved and the size of the oil separator can be reduced. It is.

In addition, the ceiling wall inner surface constituting the separation chamber is a rough surface, and is an oil separator that reduces the swirling flow rate and suppresses the increase in the two-phase flow of oil and oil and gas refrigerant.
As a result, the flow of oil and the two-phase flow of oil and gas refrigerant to the ceiling wall side can be suppressed, and efficient oil separation can be achieved.

Further, the oil separator is configured such that the lower diameter is made thinner than the upper diameter in the separation chamber to prevent the centrifugal force from increasing or decreasing.
This ensures a centrifugal force and enables efficient oil separation.

In addition, the separator is an oil separator in which a discharge pipe of the separator and a connector connected to the cycle are integrated.
As a result, the size can be reduced, and the number of connection points is reduced and the reliability is increased.

In addition, an oil separator in which a throttle portion, a separation chamber, and an oil storage chamber for connecting a discharge pipe of an outer shell configured in a cylindrical oil separator are integrally formed, and a lid is formed at the lower end portion of the oil storage chamber It is.
This expands options such as drawing, forging, and pressing as processing methods. Since the baffle plate can be assembled after the outer body is manufactured, an oil separator excellent in mass productivity can be obtained. Furthermore, by dividing the outer body and the lid, the finish of the internal configuration can be confirmed, and an oil separator with excellent reliability can be obtained.

In addition, the oil separator is formed by integrally forming a throttle portion that connects a discharge pipe of an outer shell constituting the cylindrical oil separator, a separation chamber, and an oil storage chamber.
This improves reliability by reducing the number of joints. Furthermore, it is possible to obtain an oil separator that has good mass productivity and is inexpensive.

Further, the oil separator is provided with a reinforcing bead on the outer peripheral portion of the outer shell of the cylindrical oil separator.
This increases the rigidity of the oil storage chamber, so that an oil separator that has pressure resistance even with a thin material and is inexpensive can be obtained.

  Further, the outer body constituting the cylindrical oil separator is an A outer body and a B outer body, and the A outer body has a cylindrical shape in which an upper diameter reduced portion for connecting a discharge pipe, a separation chamber, and an oil storage chamber are formed. The outer shell is a lid that covers the bottom of the oil storage chamber, and an oil reservoir that guides oil to the oil feed pipe and a lower diameter reduced portion to which the oil feed pipe is connected are formed on the lid. Oil separator. As a result, the outer body can be manufactured by dividing it into two parts, so that the outer body A can be integrally formed by drawing and the like, and an oil reservoir for guiding oil can be easily formed on the outer body B. is there.

In addition, the oil separator is configured such that a locking piece provided on the outer periphery of the baffle plate is locked in a concave groove provided in a lower portion of the separation chamber by utilizing elastic deformation of the baffle plate.
As a result, the baffle plate can be attached without using any special parts, so that an oil separator that is excellent in mass productivity and inexpensive can be obtained.

Further, the oil separator is configured such that the wall of the rising wall constituting the separation chamber is thicker than the thickness of the oil storage chamber, and a concave groove for fixing the baffle plate is formed at the thickly configured position.
As a result, the groove can be formed without impairing pressure resistance, and an inexpensive oil separator can be obtained because it is not necessary to use a thick material.

  An oil separator having the above configuration is provided in a refrigeration cycle. Thus, an efficient refrigeration apparatus can be obtained, and a refrigeration apparatus with improved reliability can be obtained.

  In the present embodiment, the oil separator that separates the two-phase flow of oil and gas refrigerant in the refrigeration cycle is described.

  The separator of the present invention can also be applied as a mist separator for separating water and water vapor such as a steam cycle. As a result, in the steam cycle device, water droplet mist that damages the turbine blades can be reduced, and a steam cycle device with improved reliability can be obtained.

By incorporating the gas-liquid separator of the present invention into a refrigeration apparatus such as an air conditioner or a steam cycle apparatus, an inexpensive refrigeration apparatus or steam cycle apparatus with improved efficiency and reliability can be obtained. .

1 Oil separator (mist separator)
2 outer body 2a A outer body 2b B outer body 2c integral outer body 3 oil storage chamber 3a peripheral wall 4 separation chamber 4a rising wall 4b ceiling wall 4c inner surface of rising wall
4d inner surface of ceiling wall 4e upper space of inflow pipe (space that hinders oil separation performance)
5 Lower end diameter-reduced part 6 Upper end diameter-reduced part 7 Oil supply pipe 8 Discharge pipe 8a Discharge pipe suction port 9 Inlet pipe 9a Inclined part 9b Inlet pipe upper end part 10 Oil sump part 11 Bead 12 Slope 13a Flat plate baffle plate 13b Spring baffle plate 13c Hole 13d Locking piece 14a A lid 14b B lid 14c C lid 15a A projection piece 15b B projection piece 16 Integrated connector 17 Groove 18 Brazing material receiving part 19 Brazing material 20 Oil storage chamber reduced diameter part A
21 Oil storage chamber reduced diameter part B
22 Compressor 23 Condenser 24 Expansion valve 25 Evaporator 26 Rough surface 27 Upper diameter 28 Lower diameter 29 B lid inclined part 30 Oil droplet 31 Downward oil film 32 Upward oil film 33 Oil film 34 along the outer surface of the discharge pipe Downward Gas flow 35 Ceiling partition plate 35a Ceiling partition plate lower surface 36 Separate separation chamber ceiling wall 36a Separate separation chamber ceiling wall inner surface 37a A swirl flow 37b B swirl flow 38 Water supply pump 39 Boiler 40 Turbine 41 Generator 42 Condenser

Claims (15)

  A cylindrical gas-liquid separator having a separation chamber having the same diameter as or smaller than the diameter of the liquid storage chamber at the upper part of the liquid storage chamber, and a liquid feed pipe at the lower diameter reduced portion of the liquid storage chamber; In addition, a discharge pipe is connected to the upper diameter reduced part of the separation chamber, and an inflow pipe of a two-phase flow of liquid phase and gas phase is introduced from the tangential direction of the rising wall of the separation chamber, and centrifugal force is used to separate the separation chamber. In the gas-liquid separator designed to separate the liquid phase and the gas phase two-phase flow, the average height of the space composed of the upper end of the inflow pipe, the inner surface of the rising wall above the upper end of the inflow pipe and the inner surface of the ceiling wall When the height is Hm and the inner diameter of the separation chamber is Di, Hm / Di ≦ 0.25, the separation chamber is configured by drawing, forging, or pressing, and the rising wall and ceiling wall of the separation chamber A gas-liquid separator characterized by comprising a single body or a separate body.   A cylindrical gas-liquid separator having a separation chamber having the same diameter as or smaller than the diameter of the liquid storage chamber at the upper part of the liquid storage chamber, and a liquid feed pipe at the lower diameter reduced portion of the liquid storage chamber; In addition, a discharge pipe is connected to the upper diameter reduced part of the separation chamber, and an inflow pipe of a two-phase flow of liquid phase and gas phase is introduced from the tangential direction of the rising wall of the separation chamber, and centrifugal force is used to separate the separation chamber. In the gas-liquid separator configured to separate the liquid phase and the gas phase two-phase flow, the connection point X between the arc of radius R connecting the rising wall inner surface and the ceiling wall inner surface and the ceiling wall inner surface arc connecting smoothly The gas-liquid separator is characterized in that an angle θ formed by a plane perpendicular to the axis of the outer shell with respect to a tangent line of a circle having a radius R is 5 degrees ≦ θ ≦ 28 degrees.   A cylindrical gas-liquid separator having a separation chamber having the same diameter as or smaller than the diameter of the liquid storage chamber at the upper part of the liquid storage chamber, and a liquid feed pipe at the lower diameter reduced portion of the liquid storage chamber; In addition, a discharge pipe is connected to the upper diameter reduced part of the separation chamber, and an inflow pipe of a two-phase flow of liquid phase and gas phase is introduced from the tangential direction of the rising wall of the separation chamber, and centrifugal force is used to separate the separation chamber. In the gas-liquid separator configured to separate the liquid-phase and gas-phase two-phase flow, an arc having a radius R connecting the inner surface of the rising wall and the inner surface of the ceiling wall is set to R ≦ 2.5 mm. Liquid separator.   Provided from the tangential direction of the separation chamber rising wall to the tip of the inflow pipe introduced into the separation chamber is an inclined portion in which a part of the side of the pipe facing the discharge pipe is crushed in the direction toward the center of the pipe. The gas-liquid separator according to any one of claims 1 to 3, wherein a discharge pipe provided at a substantially axial center of the separation chamber is avoided at the inclined portion.   The inner surface of the ceiling wall constituting the separation chamber is a rough surface, and the swirling flow rate is reduced to suppress the rise of the two-phase flow of liquid and liquid phase and gas phase. Gas-liquid separator.   The gas-liquid separator according to any one of claims 1 to 4, wherein the lower diameter is made thinner than the upper diameter in the separation chamber to prevent the centrifugal force from being increased or decreased.   The gas-liquid separator according to any one of claims 1 to 4, wherein the discharge pipe of the separator and a connector connected to the cycle are integrated.   In the cylindrical gas-liquid separator, the throttle part for connecting the discharge pipe of the outer shell, the separation chamber, and the liquid storage chamber are integrally formed, and a separate lid is formed at the lower end of the liquid storage chamber. The gas-liquid separator according to any one of claims 1 to 4, wherein the gas-liquid separator is configured.   5. The gas / liquid according to claim 1, wherein a throttle part for connecting a discharge pipe of an outer shell constituting the cylindrical gas / liquid separator, a separation chamber, and a liquid storage chamber are integrally formed. Separator.   The gas-liquid separator according to any one of claims 1 to 4, wherein a reinforcing bead is provided on the outer periphery of the outer shell of the cylindrical gas-liquid separator.   The outer bodies constituting the cylindrical gas-liquid separator are the A outer body and the B outer body, and the A outer body is a cylindrical outer body in which an upper diameter reducing portion connecting the discharge pipe, a separation chamber and a liquid storage chamber are formed. The outer shell B is a lid that covers the bottom of the liquid storage chamber, and a liquid reservoir portion that is inclined to guide the liquid to the liquid feeding tube side and a lower diameter reduced portion to which the liquid feeding tube is connected are formed on the lid body. The gas-liquid separator according to any one of claims 1 to 4, wherein   The locking piece provided on the outer periphery of the baffle plate is locked in a concave groove provided in the lower part of the separation chamber by utilizing elastic deformation of the baffle plate. Gas-liquid separator.   The thickness of the rising wall constituting the separation chamber is configured to be thicker than the thickness of the liquid storage chamber, and a concave groove for fixing the baffle plate is formed at the thickly configured position. Gas-liquid separator.   A refrigeration apparatus comprising a gas-liquid separator comprising the first to thirteenth aspects in a refrigeration cycle.   A vapor cycle apparatus comprising a vapor cycle provided with the gas-liquid separator provided with claim 1.

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