JP2016070607A - Oil separator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further improve refrigerating machine oil separation characteristics when a refrigerant introduced into a container from an introduction pipe descends and ascends.SOLUTION: An oil separator 10a which separates a refrigerating machine oil contained in a gas phase refrigerant from the gas phase refrigerant includes: a cylindrical container 20; an introduction pipe 11 for introducing the refrigerant in which the refrigerating machine oil is mixed into the container 20; a delivery pipe 13 in which an opening 14 is provide below an opening 12 of the introduction pipe 11, and which delivers the refrigerant in which the refrigerating machine oil is separated to the outside of the container 20 from the opening 14; and a funnel-like partition member 15 which is connected to the opening 14 of the delivery pipe 13 and in which a diameter expands toward a bottom part of the container 20.SELECTED DRAWING: Figure 3

Description

  The present invention relates to an oil separator that separates refrigerating machine oil from a gas-phase refrigerant containing refrigerating machine oil discharged from a compressor.

  A compressor is used in a heat pump cycle such as an air conditioner. And in order to lubricate each sliding part of this compressor, refrigerator oil is generally used. This refrigerating machine oil circulates in the refrigerant circulation system with the refrigerant flowing in the refrigerant circulation system.

  The refrigerating machine oil sucked from the suction side of the compressor or the refrigerating machine oil stored in the shell container including the compressor is supplied to each sliding part inside the compressor, and lubrication of each sliding part is performed. Used for. In addition, the refrigerating machine oil is supplied to the working chamber of the compressor and is used to prevent the leakage of the vaporized refrigerant by sealing the gap in the working chamber.

  By the way, in the above refrigerant circulation system, if the refrigerant discharged from the compressor contains a large amount of refrigerating machine oil, the refrigerating machine oil tends to adhere to the inner wall surface of the heat transfer tube of the heat exchanger. The refrigerating machine oil adhering to the inner wall surface of the heat transfer tube hinders the heat transfer of the heat transfer tube, deteriorates the heat transfer efficiency of the heat exchanger, and increases the pressure loss.

  In order to avoid such a situation, an oil separator is provided in the refrigerant circulation system. The oil separator separates the refrigerating machine oil from the refrigerant discharged from the compressor, and returns the refrigerating machine oil to the suction side of the compressor.

  Conventionally, as shown in Patent Document 1, an upper end plate of a pressure vessel is provided with an introduction tube and a lead-out tube, is provided vertically below an inner wall of the upper end plate, has a diameter that decreases downward, and is open at its lower end. An oil separator provided with a conical partition member is known.

  FIG. 1 is a diagram showing a configuration of a conventional oil separator 1. FIG. 1 is a cross-sectional view of a conventional oil separator 1 cut through a plane parallel to the central axis of the pressure vessel. In FIG. 1, the solid line arrows indicate the movement of the gas-phase refrigerant, and the broken line arrows indicate the movement of the refrigerating machine oil.

  In the oil separator 1, a mixture of the gas-phase refrigerant and the refrigerating machine oil flowing from the introduction pipe 3 (hereinafter referred to as a mixture) is directed to the inner wall of the substantially conical partition member 4 provided in the pressure vessel 2. And refrigeration oil is separated by inertia force.

  Moreover, in the oil separator 1, the mixture which collided with the inner wall of the partition member 4 is rotated at high speed while descending along the inner wall surface, and the refrigerating machine oil is separated by centrifugal force.

  Further, in the oil separator 1, the mixture that has reached the bottom of the pressure vessel 2 is rotated at high speed while rising between the partition member 4 and the inner wall of the pressure vessel 2, and the refrigerating machine oil is separated by centrifugal force.

  In the oil separator 1, the mixture rising between the partition member 4 and the inner wall of the pressure vessel 2 is passed through a mesh member 5 provided between the partition member 4 and the inner wall of the pressure vessel 2, thereby Refrigerating machine oil is separated by collection by member 5.

Japanese Patent Laid-Open No. 10-9723

  By the way, in the above-described conventional oil separator 1, the opening of the introduction pipe 3 is disposed in the internal space 6 of the partition member 4 provided in the pressure vessel 2. Therefore, the mixture flowing in from the introduction pipe 3 becomes a swirling flow descending in the internal space 6 of the partition member 4. The swirl flow reaches the bottom of the pressure vessel 2 and then turns into a swirl flow that rises, passes between the outer wall of the partition member 4 and the inner wall of the pressure vessel 2, and is led out on the upper side surface of the pressure vessel 2. It is discharged from the tube 7.

  However, in the conventional oil separator 1, the oil droplets of the refrigerating machine oil separated from the gas-phase refrigerant in the internal space 6 of the partition member 4 adheres to the inner wall surface of the partition member 4, falls from the lower end of the partition member 4, Oil droplets are caught in the swirling flow that is reversed and raised. However, the swirling flow that has been reversed and raised passes through the outer periphery of the partition member 4, so that the flow velocity is reduced and it is difficult to effectively separate the entrained oil droplets. As a result, there is a problem that the separation rate of the refrigerating machine oil is reduced.

  An object of the present invention is to provide an oil separator capable of enhancing the collision separation effect on the refrigeration oil and improving the separation rate of the refrigeration oil in a configuration including a partition member in the pressure vessel.

  The oil separator of the present invention includes a cylindrical container, an introduction pipe for introducing a refrigerant mixed with refrigerating machine oil into the container, and an opening provided below the opening of the introduction pipe. A lead-out pipe that guides the refrigerant from which the refrigerating machine oil is separated to the outside of the container, and a funnel-shaped partition member that is connected to the opening of the lead-out pipe and that expands toward the bottom of the container. Take the configuration.

  ADVANTAGE OF THE INVENTION According to this invention, in the structure provided with the partition member in the pressure vessel, the collision separation effect with respect to refrigerating machine oil can be improved, and the separation rate of refrigerating machine oil can be improved.

Diagram showing the configuration of a conventional oil separator Refrigerant circuit diagram showing the overall configuration of the outdoor unit of the air-conditioning apparatus according to Embodiments 1 to 4 of the present invention. Sectional drawing of the oil separator which concerns on Embodiment 1 of this invention The graph which shows the relationship between the ratio of the internal diameter of the expansion side end surface of a partition member with respect to the difference of the internal diameter of a pressure vessel, and the outer diameter of an outlet pipe, and the separation rate of refrigerator oil The graph which shows the relationship between the ratio of the distance from the enlarged part end surface of the partition member to the oil surface of the oil reservoir with respect to the distance from the enlarged side end face of the partition member to the bottom of the pressure vessel, and the separation rate of the chiller oil The graph which shows the relationship between the ratio of the height of a partition member with respect to the distance from the diameter-expansion side end surface of a partition member to the lowest part of a pressure vessel, and the separation rate of refrigerator oil Sectional drawing of the oil separator which concerns on Embodiment 2 of this invention. Sectional drawing of the oil separator which concerns on Embodiment 3 of this invention. Sectional drawing of the oil separator which concerns on Embodiment 4 of this invention. Sectional drawing which shows the modification of the partition member which concerns on Embodiment 1-4 of this invention

  Embodiments of the present invention will be described below with reference to the drawings. Note that the present invention is not limited to the following embodiments.

  First, an outdoor unit of an air conditioner according to an embodiment of the present invention will be described.

  FIG. 2 is a refrigerant circuit diagram showing the overall configuration of the outdoor unit 100 of the air-conditioning apparatus according to the embodiment of the present invention. This outdoor unit 100 is an example of an outdoor unit to which oil separators 10a to 10d according to Embodiments 1 to 4 described later are applied. Therefore, the application range of the oil separators 10a to 10d is not limited to the outdoor unit 100 shown in FIG.

  The outdoor unit 100 includes an oil separator 10, a variable capacity compressor (DC inverter compressor) 30, an outdoor heat exchanger 31, an expansion valve 32, a four-way valve 33, a receiver tank 34, and an accumulator 35. .

  A suction pipe 41 extending through an accumulator 35 is connected to the suction port of the compressor 30. A discharge pipe 42 </ b> A is connected to the discharge port of the compressor 30. The discharge pipe 42A is connected to the introduction pipe 11 of the oil separator 10 (see FIGS. 3 and 7 to 9 described later). Further, the discharge pipe 42 </ b> B is connected to the outlet pipe 13 (see FIGS. 3 and 7 to 9 described later) and the four-way valve 33 of the oil separator 10.

  One end of the outdoor heat exchanger 31 and the discharge pipe 42 </ b> B are connected via a four-way valve 33. One end of the outdoor heat exchanger 31 and the pipe line 43 are also connected via a four-way valve 33. The pipe 43 is connected to the suction pipe 41 of the compressor 30 via the accumulator 35.

  Further, the discharge pipe 42 </ b> B and the gas pipe 46 are connected via a four-way valve 33. The pipe 43 and the gas pipe 46 are also connected via the four-way valve 33.

  The other end of the outdoor heat exchanger 31 is connected to the expansion valve 32 and the receiver tank 34, and further connected to the liquid pipe 45 via the refrigerant pipe 44.

  The oil separator 10 is connected to an oil outlet pipe 24 that returns the refrigeration oil accumulated in the oil separator 10 to the suction pipe 41 of the compressor 30. The oil outlet pipe 24 is connected to the suction pipe 41 through an oil return pipe 47.

  The refrigerating machine oil described above is a lubricating oil for the compressor 30 included in the gas-phase refrigerant discharged from the compressor 30. The oil separator 10 separates the refrigeration oil from the gas-phase refrigerant discharged from the compressor 30, returns the separated refrigeration oil to the suction side of the compressor 30, and supplies the gas-phase refrigerant from which the refrigeration oil has been removed to the four-way valve 33. Supply.

  The outdoor unit 100 is connected to an indoor unit (not shown) by a liquid pipe 45 and a gas pipe 46. The air conditioner according to each embodiment of the present invention is configured to perform a cooling operation or a heating operation by circulating a refrigerant between the outdoor unit 100 and the indoor unit and switching the four-way valve 33. ing.

  Hereinafter, the first to fourth embodiments of the oil separator 10 described above will be described.

(Embodiment 1)
In the first embodiment, the oil separator includes a funnel-shaped partition member having an enlarged diameter toward the bottom of the pressure vessel at the tip of the outlet pipe in the pressure vessel, and is provided between the outer wall of the partition member and the inner wall of the pressure vessel. The gas phase refrigerant is caused to flow into the space, and the gas phase refrigerant is caused to flow out from the inside of the partition member.

  First, the configuration of the oil separator 10a according to the present embodiment will be described with reference to FIG. FIG. 3 is a cross-sectional view of the oil separator 10a when cut along a plane that passes through the central axis of the pressure vessel and is parallel to the central axis.

  As shown in FIG. 3, the oil separator 10a includes a pressure vessel 20 that is a cylindrical sealed vessel. The pressure vessel 20 includes a cylindrical body container 23 having upper and lower ends opened, an upper end panel 18 connected to the upper end of the body container 23, and a lower end panel 19 connected to the lower end of the body container 23.

  The upper end plate 18 and the body container 23 and the lower end panel 19 and the body container 23 are joined by welding or the like. Thereby, the opening part of the both ends of the trunk | drum container 23 is sealed. The upper end plate 18 and the body container 23 or the lower end panel 19 and the body container 23 may be integrally formed.

  Vapor phase refrigerant containing refrigerating machine oil discharged by the compressor 30 is introduced into an upper space 21 that is an inner space of the upper end plate 18 from an opening 12 of the introduction pipe 11 described later. In the lower space 22, which is the space inside the lower end plate 19, the refrigerating machine oil separated from the gas-phase refrigerant in the pressure vessel 20 is temporarily stored, and an oil reservoir 27 is formed.

  The upper end plate 18 is formed with an introduction tube insertion hole 28 and a lead-out tube insertion hole 29. The introduction pipe 11 and the lead-out pipe 13 are inserted in the introduction pipe insertion hole 28 and the lead-out pipe insertion hole 29 in the vertical direction or the substantially vertical direction, respectively, and the outer circumferences of the introduction pipe 11 and the lead-out pipe 13 are closed by brazing. Sealed.

  The introduction pipe 11 and the lead-out pipe 13 are provided in parallel or substantially parallel to the central axis AX of the pressure vessel 20 and penetrate the upper end plate 18. The outlet pipe 13 is provided at the position of the center C of the pressure vessel 20. On the other hand, the introduction pipe 11 is provided at a position shifted from the center C of the pressure vessel 20. Thus, the introduction pipe 11 and the outlet pipe 13 are arranged so as not to interfere with each other.

  As described above, the discharge pipe 42 </ b> A extending from the discharge port of the compressor 30 is connected to the introduction pipe 11. Therefore, the gas-phase refrigerant including the refrigerating machine oil discharged by the compressor 30 is introduced into the introduction pipe 11 through the discharge pipe 42A.

  The introduction pipe 11 is provided with an opening 12 that opens vertically downward or substantially vertically downward toward the bottom of the pressure vessel 20. From the opening 12, the gas-phase refrigerant including the refrigeration oil discharged from the compressor 30 is sent to the upper space 21 of the pressure vessel 20. The gas-phase refrigerant becomes a downward flow that moves toward the bottom of the pressure vessel 29.

  The outlet pipe 13 is provided with an opening 14 that opens vertically downward or substantially vertically downward toward the bottom of the pressure vessel 20 at a position below the opening 12. The center of the opening 14 is preferably on the central axis AX of the pressure vessel 20. From this opening 14, a gas-phase refrigerant (upflow) that rises in an internal space 26 of a partition member 15 described later flows into the outlet pipe 13.

  As described above, the discharge pipe 13 is connected to the discharge pipe 42 </ b> B connected to the four-way valve 33. Therefore, the gas-phase refrigerant from which the refrigerating machine oil is separated in the pressure vessel 20 is led out of the pressure vessel 20 from the lead-out pipe 13 and flows into the discharge pipe 42B.

  An upper end opening portion of a funnel-shaped partition member 15 whose upper and lower ends are opened is inserted into the opening portion 14, and is fixed to the outer periphery of the outlet tube 13 by brazing. The center of the opening of the partition member 15 is preferably on the central axis AX of the pressure vessel 20. Note that cost reduction may be achieved by integrally forming the outlet tube 13 and the partition member 15.

  The diameter of the partition member 15 increases toward the bottom of the pressure vessel 20, and the flow path cross-sectional area (horizontal cross-sectional area) gradually increases toward the bottom of the pressure vessel 20. Therefore, the cross-sectional area of the flow path, which is the space between the outer wall of the partition member 15 and the inner wall of the pressure vessel 20, decreases as it goes toward the bottom of the pressure vessel 20.

  An oil outlet pipe insertion hole 36 is formed in the lower end plate 19. The oil outlet pipe 24 is inserted into the oil outlet pipe insertion hole 36.

  As described above, the oil outlet pipe 24 is connected to the oil return pipe 47. Therefore, the refrigerating machine oil forming the oil reservoir 27 in the lower space 22 is discharged from the oil outlet pipe 24 to the outside of the pressure vessel 20 and flows into the oil return pipe 47.

  Further, the lower end plate 19 is provided with two leg portions 25. The upper end of the leg portion 25 is joined to the outer peripheral surface of the lower end plate 19 by welding or the like. The lower end portion of the leg portion 25 is bent so as to be parallel to the ground plane (the bottom plate of the outdoor unit 100). That is, the leg part 25 is formed in a substantially L shape.

  The pressure vessel 20 is configured to be installed vertically with a space between the pressure vessel 20 and the grounding surface in a state where the pressure vessel 20 stands by the leg portion 25. In the example of FIG. 3, the number of leg portions 25 is two, but may be three or more.

  Next, the flow of the gas-phase refrigerant and the refrigerating machine oil in the oil separator 10a according to the present embodiment will be described with reference to FIG.

  In the oil separator 10 a, the high-temperature gas phase refrigerant discharged from the compressor 30 is introduced into the upper space 21 through the opening 12 of the introduction pipe 11. As described above, this gas-phase refrigerant contains refrigeration oil.

  The gas-phase refrigerant introduced into the upper space 21 becomes a downward flow that flows down toward the bottom surface of the pressure vessel 20. When this downward flow collides with the outer wall (inclined surface) of the partition member 15, the refrigerating machine oil is separated from the gas-phase refrigerant by the inertial force because of its higher density than the gas-phase refrigerant (impact separation effect). As a result, the refrigerating machine oil adhering to the outer wall of the partition member 15 moves downward along the outer wall of the partition member 15 and falls from the end surface of the partition member 15 to the bottom of the pressure vessel 29 to form an oil reservoir 27.

  Then, the downward flow increases the flow velocity when passing through the flow path gradually narrowed by the expansion of the partition member 15 (that is, the space between the outer wall of the partition member 15 and the inner wall of the body container 23), It collides with the bottom of the pressure vessel 20. At this time, the refrigerating machine oil is separated from the gas-phase refrigerant by the collision separation effect. The separated refrigerating machine oil forms an oil reservoir 27.

  Next, the downward flow that has reached the bottom of the pressure vessel 20 becomes an upward flow that reverses and rises. This upward flow flows in a space above the oil level (liquid level) of the oil reservoir 27. Specifically, the upward flow passes through the internal space 26 of the partition member 15 and flows toward the opening 14 of the outlet pipe 15. At this time, the upward flow collides with the inner wall of the partition member 15, and the refrigerating machine oil is separated from the gas phase refrigerant. Thereby, the refrigerating machine oil adhering to the inner wall of the partition member 15 falls to the bottom of the pressure vessel 29 by its own weight and forms an oil reservoir 27.

  Thereafter, the gas-phase refrigerant that has passed through the internal space 26 as an upward flow enters the outlet pipe 13 through the opening 14 and is supplied to the four-way valve 33 via the discharge pipe 42B.

  Note that the refrigeration oil in the oil reservoir 27 is led out of the pressure vessel 20 from the oil outlet pipe 24 provided in the lower end plate 19 as described above, and returned to the suction port of the compressor 30 through the oil return pipe 47. .

  Next, the separation rate of refrigerating machine oil obtained as a result of numerical simulation in the oil separator 10a according to the present embodiment will be described.

  4 to 6 are graphs showing the separation rate of refrigerating machine oil obtained by numerical simulation using the Monte Carlo method in the oil separator 10a. 4 to 6, the vertical axis indicates the separation rate of the refrigerating machine oil, and the relative evaluation is performed so that the separation rate becomes 100% when the separation rate is the maximum value.

  Here, each value in FIGS. 4 to 6 is defined as follows. That is, as shown in FIG. 3, the inner diameter of the diameter-expansion side end face (lower end opening) of the partition member 15 is D (hereinafter referred to as the inner diameter D). Further, the distance from the position of the opening 14 of the outlet pipe 13 to the diameter-enlarged end face of the partition member 15, that is, the height of the internal space 26 of the partition member 15 is L (hereinafter referred to as height L). In addition, the distance from the end surface on the enlarged diameter side of the partition member 15 to the bottom of the pressure vessel 20 is defined as H (hereinafter referred to as distance H). Further, the distance from the end surface on the enlarged diameter side of the partition member 15 to the oil surface of the oil reservoir 27 is defined as Y (hereinafter referred to as distance Y). In addition, the inner diameter of the body container 23 of the pressure vessel 20 is D1 (hereinafter referred to as an inner diameter D1), and the outer diameter of the outlet tube 13 is D2 (hereinafter referred to as an outer diameter D2).

  First, FIG. 4 will be described. FIG. 4 is a graph showing the relationship between the ratio of the inner diameter D to the difference between the inner diameter D1 and the outer diameter D2 (D / (D1-D2)) and the separation rate of the refrigerating machine oil.

  As shown in FIG. 4, when D / (D1-D2) is less than 20%, the separation rate of the refrigerating machine oil is about 97% or less. On the other hand, as shown in FIG. 4, when D / (D1-D2) is larger than 60%, the flow path greatly expands from the diameter-enlarged side end face of the partition member 15 toward the bottom of the pressure vessel 20. The pressure loss of the separator 10a increases. Since pressure loss is analytically proportional to the square of the increase in flow rate obtained from the flow path cross-sectional area reduction rate, when D / (D1-D2) is 60%, it is approximately compared to when it is 100%. Tripled.

  Therefore, in order to suppress an increase in pressure loss while suppressing a decrease in the refrigerating machine oil separation rate to about 3% from the maximum value of the refrigerating machine oil separation rate, in the oil separator 10a, 20% ≦ D / (D1-D2) × 100 ≦ 60% is desirable to be satisfied.

  Next, FIG. 5 will be described. FIG. 5 is a graph showing the relationship between the ratio of the distance Y to the distance H and the refrigerating machine oil separation rate.

  As shown in FIG. 5, when the value of Y / H is 70% or less, the space inside the pressure vessel 20 decreases due to the rise of the oil level of the oil reservoir 27, and therefore the separation rate of the refrigerating machine oil is 99.5. % Or less.

  For this reason, even when all the refrigerating machine oil present in the refrigerating machine circuit is stored in the oil separator 10a, the decrease in the refrigerating machine oil separation rate is about 0.5% or less from the maximum value of the refrigerating machine oil separation rate. Therefore, the oil separator 10a is configured such that the height (H-Y) of the refrigerating machine oil that can store the maximum amount in the oil separator 10a satisfies 70% ≦ Y / H × 100 ≦ 100%. Is desirable.

  Next, FIG. 6 will be described. FIG. 6 is a graph showing the relationship between the ratio of the height L to the distance H and the separation rate of the refrigerating machine oil.

  As shown in FIG. 6, when the value of L / H is less than 60%, the refrigerating machine oil separation rate is about 99.5% or less.

  Therefore, in order to suppress the decrease in the separation rate of the refrigerating machine oil to about 0.5% or less from the maximum value of the refrigerating machine oil separation rate, 60% ≦ L / H × 100 ≦ in the oil separator 10a. It is desirable to configure so as to satisfy 100%.

  As described above, the oil separator according to the present embodiment includes a funnel-shaped partition member having a diameter expanded toward the bottom of the pressure vessel at the tip of the outlet pipe in the pressure vessel, and the outer wall of the partition member and the pressure vessel The gas phase refrigerant is caused to flow into a space between the inner wall and the gas phase refrigerant to flow out from the inside of the partition member. Since the inner diameter of the partition member is smaller than the inner diameter of the pressure vessel (body vessel), the upward flow speed is higher than the downward flow speed. Therefore, even when the rising flow entrains oil droplets falling from the lower end of the partition member, the entraining oil droplets can be efficiently separated by colliding with the inner wall of the partition member. That is, in the oil separator according to the present embodiment, it is possible to enhance the collision separation effect on the refrigerating machine oil and improve the refrigerating machine oil separation rate.

(Embodiment 2)
In Embodiment 2, the oil separator is provided with a through-hole in the funnel-shaped partition member for returning the oil droplets of the refrigerating machine oil captured by the inner wall surface into the pressure vessel.

  The configuration of the oil separator 10b according to the present embodiment will be described with reference to FIG. FIG. 7 is a cross-sectional view of the oil separator 10b when cut along a plane that passes through the central axis of the pressure vessel and is parallel to the central axis. In FIG. 7, the same components as those in FIG. 3 are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 7, in the oil separator 10 b, a plurality of through holes 16 are formed in the partition member 15 in the vicinity of the connection portion with the outlet pipe 13. In addition, although the number of the through-holes 16 is arbitrary, it is preferable to form at equal intervals along the outer periphery of the partition member 15, for example. Moreover, the through-hole 16 is not limited to the elliptical shape shown in FIG. 7, For example, circular, a rectangular shape, etc. may be sufficient.

  The refrigerating machine oil separated in the internal space 26 of the partition member 15 moves along the inner wall of the partition member 15 along with the upward flow (or upward swirl flow) rising in the internal space 6, and travels toward the outlet pipe 13. At this time, a large oil droplet of the refrigerating machine oil transmitted through the inner wall of the partition member 15 falls toward the bottom of the pressure vessel 20 due to its own weight.

  On the other hand, small oil droplets (oil droplets of a size that does not fall due to their own weight) out of the refrigerating machine oil that travels on the inner wall of the partition member 15 pass through the through hole 16 and pass through the outer wall of the partition member 15. Move to the side. The oil droplets that have moved onto the outer wall of the partition member 15 are guided downward by a downward flow that descends between the outer wall of the partition member 15 and the inner wall of the pressure vessel 20. Then, it falls from the end face of the partition member 15 to the oil reservoir 27.

  As described above, the oil separator according to the present embodiment includes the plurality of through holes 16 in the partition member 15, whereby the refrigerating machine oil separated in the internal space 26 of the partition member 15 flows into the outlet pipe 13. Since it can return to the pressure vessel 20 again before, the separation rate of refrigerating machine oil can be improved greatly.

  In the oil separator of the present embodiment, when the oil level of the oil reservoir 27 rises and reaches the lower end of the partition member 15, the gas-phase refrigerant containing the refrigerating machine oil passes through the through-hole 16 and the outlet pipe 13. More discharged. At this time, since the pressure loss of the oil separator increases, the oil level can be managed using a differential pressure gauge.

(Embodiment 3)
In Embodiment 3, the oil separator includes an introduction pipe inserted substantially perpendicular to the wall surface of the pressure vessel, and the opening direction of the opening of the introduction pipe is set to the horizontal direction or the substantially horizontal direction.

  The configuration of the oil separator 10c according to the present embodiment will be described with reference to FIG. FIG. 8 is a cross-sectional view of the oil separator 10c when cut along a plane passing through the central axis of the pressure vessel and parallel to the central axis. In FIG. 8, the same components as those in FIG. 3 are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 8, in the oil separator 10 c, an introduction tube insertion hole 28 is formed on the wall surface of the body container 23. The introduction tube 11 is inserted into the introduction tube insertion hole 28 in the horizontal direction or the substantially horizontal direction, and the entire outer periphery of the introduction tube 11 is sealed by brazing.

  The introduction pipe 11 is provided with an opening 12 that opens in a horizontal direction or a substantially horizontal direction toward the inner wall surface of the pressure vessel 20 (for example, the body vessel 23). From this opening 12, the gas-phase refrigerant containing the refrigerating machine oil is sent into the pressure vessel 20.

  The gas-phase refrigerant delivered from the opening 12 becomes a collision jet flow that collides with the inner wall of the pressure vessel 20 and then becomes a high-speed downward swirling flow that descends while swirling along the inner wall surface of the pressure vessel 20. .

  When this downward swirling flow collides with the inner wall of the pressure vessel 20 (for example, the body vessel 23), it is separated from the gas phase refrigerant by the collision separation effect. Further, the refrigerating machine oil that has not been separated by the collision separation effect is scattered in the outer radial direction of the pressure vessel 20 by the centrifugal force generated by the swirling of the descending swirl flow and separated from the gas-phase refrigerant (centrifugal effect). . The refrigerating machine oil adhering to the inner wall of the pressure vessel 20 moves downward along the inner wall of the pressure vessel 20 and reaches the bottom of the pressure vessel 20 to form an oil reservoir 27.

  Then, the downward swirling flow passes through a flow path (that is, a space between the outer wall of the partition member 15 and the inner wall of the fuselage container 23) that is gradually narrowed by expanding the diameter of the partition member 15. At this time, since the horizontal cross section of the flow path gradually decreases, the flow velocity of the descending swirl flow increases, and the centrifugal force acting on the oil droplets of the refrigeration oil increases. As a result, in the flow path, more refrigeration oil is separated from the gas phase refrigerant due to the centrifugal separation effect.

  Further, the descending swirl flow with the increased flow velocity collides with the bottom of the pressure vessel 20. At this time, the refrigerating machine oil is separated from the gas-phase refrigerant by the collision separation effect. The separated refrigerating machine oil forms an oil reservoir 27.

  Next, the downward swirling flow that has reached the bottom of the pressure vessel 20 becomes an upward swirling flow that reverses and rises. This upward swirling flow flows in a space above the oil level (liquid level) of the oil reservoir 27. Specifically, the upward swirling flow passes through the internal space 26 of the partition member 15 and flows toward the opening 14 of the outlet pipe 13. At this time, the upward swirling flow collides with the inner wall of the partition member 15, and the refrigerating machine oil is separated from the gas-phase refrigerant by the collision separation effect.

  Moreover, since the horizontal cross section of the internal space 26 is gradually reduced, the flow rate of the upward swirling flow is increased, and the centrifugal force acting on the oil droplets of the refrigerating machine oil is increased. As a result, in the internal space 26, more refrigeration oil is separated from the gas-phase refrigerant due to the centrifugal separation effect. Thus, the refrigerating machine oil adhering to the inner wall of the partition member 15 falls to the bottom of the pressure vessel 20 by its own weight and forms an oil reservoir 27.

  Next, the gas-phase refrigerant that has passed through the internal space 26 as an upward swirling flow enters the outlet pipe 13 through the opening 14 and is supplied to the four-way valve 33 via the discharge pipe 42B.

  Note that the refrigeration oil in the oil reservoir 27 is led out of the pressure vessel 20 from the oil outlet pipe 24 provided in the lower end plate 19 as described above, and returned to the suction port of the compressor 30 through the oil return pipe 47. .

  As described above, in the oil separator according to the present embodiment, the swirling flow of the gas-phase refrigerant is generated by setting the opening direction of the opening portion of the introduction pipe to the horizontal direction or the substantially horizontal direction. Thereby, not only the collision separation effect by the collision jet but also the centrifugal separation effect by the swirling flow can be obtained, and the separation rate of the refrigerating machine oil can be greatly improved.

  Further, when the circulation amount of the gas-phase refrigerant is small, the centrifugal force can be increased by reducing the diameter of the oil separator, but the diameter of the upper end plate 18 must also be reduced, and the introduction pipe and the outlet pipe are provided. It becomes difficult to prepare the upper end plate. On the other hand, in the oil separator according to the present embodiment, since the introduction pipe is provided not in the upper end plate 18 but in the body container 23, even when the diameter of the upper end plate 18 is small, the introduction pipe 11 and the outlet pipe 13 may interfere. Absent.

  Further, as shown in FIG. 8, the outlet pipe 13 and the partition member 15 are arranged such that the center of the opening 14 of the outlet pipe 13 and the center of the opening of the partition member 15 are located on the central axis AX of the pressure vessel 20. When provided, the downward swirling flow swirling along the inner wall surface of the pressure vessel 20 is not disturbed.

  Further, as shown in FIG. 8, the center of the opening 14 of the outlet tube 13 is positioned on the central axis AX of the pressure vessel 20 so that the opening 14 of the outlet tube 13 extends along the inner wall surface of the pressure vessel 20. Since it is located at the center of the swirling downward swirling flow, it is possible to suppress the scattered refrigeration oil from being discharged from the opening 14 of the outlet pipe 13, and the gas-phase refrigerant from which the refrigeration oil is almost removed is connected to the four-way valve 33. To the discharge pipe 42B.

  Further, in the present embodiment, in order to efficiently swirl the gas phase refrigerant sent from the opening 12 into the pressure vessel 20, the opening direction of the opening 12 is set to the inner wall surface of the pressure vessel 20 in the opening direction. It may be non-parallel to the normal direction. As a result, the gas-phase refrigerant delivered from the opening 12 flows in a direction other than the direction perpendicular to the inner wall surface of the pressure vessel 20. As a result, a high-speed downward swirling flow is generated without losing kinetic energy. The separation effect of the refrigerating machine oil can be further improved by the centrifugal separation effect by the high-speed downward swirling flow.

  In addition, the structure which generate | occur | produces the downward swirling flow demonstrated in this Embodiment can also be applied to the oil separator of Embodiment 1 and 2 mentioned above and Embodiment 4 mentioned later. For example, in the case of the oil separator 10a according to the first embodiment shown in FIG. 3, the opening direction of the opening 12 may be set to the horizontal direction or the substantially horizontal direction by curving the introduction pipe 11 in the pressure vessel 20. Thereby, the gas-phase refrigerant containing the refrigerating machine oil is sent out from the opening portion 12 in the horizontal direction or substantially in the horizontal direction, and collides with the inner wall of the pressure vessel 20 (for example, the inner wall of the upper end plate 18 or the inner wall of the body vessel 23), A downward swirling flow is generated. Thereby, also in Embodiment 1, the separation rate of the refrigerating machine oil can be further improved by the centrifugal separation effect by the descending swirl flow as in the present embodiment.

(Embodiment 4)
In Embodiment 4, the oil separator includes a mesh member between the inner wall of the pressure vessel and the outer wall of the partition member.

  The configuration of the oil separator 10d according to the present embodiment will be described with reference to FIG. FIG. 9 is a cross-sectional view of the oil separator 10d when cut along a plane that passes through the central axis of the pressure vessel and is parallel to the central axis. In FIG. 9, the same components as those in FIG.

  As shown in FIG. 9, the oil separator 10 d includes a knitted member 17 such as a mesh filter between the inner wall of the pressure vessel 20 (for example, the trunk vessel 23) and the outer wall of the partition member 15. In the example of FIG. 9, the mesh member 17 is provided in the vicinity of the enlarged diameter side end face of the partition member 15, but the installation position of the mesh shaped member 17 is higher than the enlarged diameter side end face of the partition member 15. It may be.

  When the downward flow (or downward swirling flow) of the gas-phase refrigerant containing the refrigeration oil passes through the stitch member 17, the refrigeration oil is captured by the mesh member 17, and the refrigeration oil is separated from the gas-phase refrigerant.

  As described above, in the oil separator according to the present embodiment, the mesh member is provided between the inner wall of the pressure vessel and the outer wall of the partition member, so that the gas phase refrigerant passes through the stitch member. The refrigerating machine oil can be effectively separated from the refrigerant, and the refrigerating machine oil separation rate can be greatly improved.

  In addition, when the circulation amount of the gas phase refrigerant is large, the time during which the gas phase refrigerant remains in the pressure vessel 20 is reduced. In this case, although the oil separation rate is relatively lowered, the oil separator according to the present embodiment can suppress a reduction in the refrigerating machine oil separation rate by providing the mesh member.

  In addition, the said embodiment is only an example of the specific aspect to which this invention is applied, and does not limit this invention. That is, it is possible to implement the present invention in a mode different from the above embodiment.

  For example, in the above embodiment, the case where the oil separator 10 (that is, the oil separators 10a to 10d) is used in an air conditioner including one inverter-type compressor 30 is described. You may use for the air conditioning apparatus provided with two or more inverter type compressors and constant speed compressors. Oil separator 10 may be used for a gas heat pump type air harmony device. Furthermore, the oil separator 10 is not limited to an air conditioner, and may be used in an apparatus that separates lubricating oil from a gas-phase fluid containing lubricating oil.

  For example, in the said embodiment, although the inclined surface of the funnel-shaped partition member 15 was made into linear form, it is not limited to this. For example, as shown in FIG. 10A, a plurality of steps may be formed on the inclined surface of the partition member 15a. Alternatively, for example, as illustrated in FIG. 10B, the inclined surface of the partition member 15b may be formed in a curved shape. With such a configuration, the area where the gas-phase refrigerant collides with the inclined surface can be increased, and the collision separation effect can be further enhanced.

  The present invention is suitable for use in an oil separator that separates refrigeration oil contained in a gas-phase refrigerant.

1, 10, 10a, 10b, 10c, 10d Oil separator 2, 20 Pressure vessel 3, 11 Inlet tube 4, 15, 15a, 15b Partition member 5, 17 Mesh member 6, 26 Inner space 7, 13 Lead-out tube 12, DESCRIPTION OF SYMBOLS 14 Opening part 16 Through-hole 18 Upper end plate 19 Lower end plate 21 Container upper part 22 Container lower part 23 Body container 24 Oil outlet pipe 25 Leg part 27 Oil reservoir 28 Introduction pipe insertion hole 29 Outlet pipe insertion hole 30 Compressor 31 Outdoor heat exchanger 32 Expansion valve 33 Four-way valve 34 Receiver tank 35 Accumulator 36 Oil outlet pipe insertion hole 41 Suction pipe 42A Discharge pipe 42B Discharge pipe 43 Pipe line 44 Refrigerant pipe 45 Liquid pipe 46 Gas pipe 47 Oil return pipe 100 Outdoor unit

Claims (7)

A cylindrical container;
An introduction pipe for introducing a refrigerant mixed with refrigerating machine oil into the container;
An outlet pipe that is provided with an opening below the opening of the introduction pipe, and leads out the refrigerant from which the refrigerating machine oil is separated from the opening to the outside of the container;
A funnel-shaped partition member connected to the opening of the outlet pipe and having a diameter expanded toward the bottom of the container;
An oil separator characterized by comprising The center of the opening of the outlet pipe and the center of the opening of the partition member are on the central axis of the container,
The oil separator according to claim 1. A plurality of through holes are formed in the partition member,
The oil separator according to claim 1 or 2. The opening of the introduction pipe is open in a horizontal direction or a substantially horizontal direction,
The oil separator according to any one of claims 1 to 3. Further comprising a mesh member between the inner wall of the container and the outer wall of the partition member,
The oil separator according to any one of claims 1 to 4. A plurality of steps are formed on the inclined surface of the partition member.
The oil separator according to any one of claims 1 to 5. The inclined surface of the partition member is curved.
The oil separator according to any one of claims 1 to 5.

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