WO2019220529A1

WO2019220529A1 - Compressor

Info

Publication number: WO2019220529A1
Application number: PCT/JP2018/018730
Authority: WO
Inventors: 下地　美保子; 宏樹長澤; 将吾諸江
Original assignee: 三菱電機株式会社
Priority date: 2018-05-15
Filing date: 2018-05-15
Publication date: 2019-11-21
Also published as: JPWO2019220529A1; JP6854973B2

Abstract

A compressor (80) comprises an airtight container (1) forming the contour, a compression mechanism part (3) provided in the lower part of the airtight container interior, an electric motor part (2) having a stator (21) and a rotor (22) and provided higher than the compression mechanism part in the airtight container interior, a drive shaft connecting the rotor and the compression mechanism part, a rotating oil-separating member (100) connected to the upper end part of the drive shaft, and a discharge tube (7) provided in the upper part of the oil-separating member. The oil-separating member has a plate part (100a) that rotates in tandem with the drive shaft, a side wall part (100b) that is provided to the upper surface of the plate part and that together with the upper surface forms a recess (8) facing the discharge tube, and oil discharge channels (100c) protruding from the outer peripheral surface of the side wall part.

Description

Compressor

The present invention relates to a compressor provided with an oil separating member for separating lubricating oil from a refrigerant.

In recent years, the flow rate of refrigerant has increased due to the increase in capacity and capacity of rotary compressors, and the amount of lubricating oil taken out from sealed containers has increased accordingly. If the lubricating oil is taken out of the sealed container, the sliding parts provided in the sealed container will be insufficiently lubricated, reducing the reliability of the compressor and reducing the operating efficiency of the air conditioner. To do. For this reason, in the rotary compressor, various oil separation measures are taken to prevent the lubricating oil from being taken out of the sealed container.

For example, Patent Document 1 discloses a hermetic compressor in which an oil separation plate that rotates together with a drive shaft having an oil supply passage is attached to an upper space of an electric motor. The oil separation plate is formed with a recess protruding downward in the center. The oil separation plate is configured such that an opening on the lower end side of the discharge pipe is inserted into the recess, the upper side of the insertion hole of the rotor is closed by the recess, and pumping of oil from the oil supply passage to the discharge space is prevented. In addition, the oil separation plate is provided with an oil drain hole on the wall surface of the recess so that the lubricating oil staying at the bottom of the recess is not sucked into the discharge pipe.

Japanese Utility Model Publication No. 2-107783

Generally, in a high-pressure shell type compressor, high-pressure refrigerant gas and lubricating oil are discharged from a compression chamber into a sealed container. The refrigerant gas is also called discharge gas. The lubricating oil that has not been separated in the sealed container is finally discharged out of the sealed container from the discharge pipe. In the hermetic compressor of Patent Document 1, when the flow rate of the refrigerant gas increases, the pressure loss of the discharge pipe increases, the suction force increases, the oil discharge capacity of the oil discharge hole is overcome, and the oil outflow amount from the discharge pipe May increase. That is, in this hermetic compressor, there is a possibility that the lubricating oil cannot be efficiently separated from the refrigerant gas containing the lubricating oil depending on the flow rate of the refrigerant gas.

The present invention has been made to solve the above-described problems, and provides a compressor capable of efficiently separating lubricating oil from refrigerant gas containing lubricating oil regardless of the flow rate of the refrigerant gas. The purpose is to do.

The compressor according to the present invention includes a sealed container that forms an outer shell, a compression mechanism section provided below the sealed container, a stator, and a rotor. An upper motor portion, a drive shaft that connects the rotor and the compression mechanism portion, an oil separation member that rotates by being connected to an upper end portion of the drive shaft, and an upper portion of the oil separation member In the compressor provided with the discharge pipe provided, the oil separation member is provided on the upper surface of the plate portion that rotates in conjunction with the drive shaft, and faces the discharge pipe together with the upper surface. And a drainage path protruding from the outer peripheral surface of the side wall.

According to the present invention, when the oil separating member rotates, a speed difference is generated between the gas speed around the side wall and the rotational speed of the oil drain outlet, and the relative oil flow causes the oil path to flow. Pressure loss can be generated at the outlet end. That is, since the oil drainage capacity can be increased by the pressure drop at the outlet end of the oil drain passage, the lubricating oil can be efficiently separated regardless of the flow rate of the refrigerant gas.

It is the longitudinal cross-sectional view which showed the whole structure of the compressor which concerns on Embodiment 1 of this invention. It is the principal part enlarged view which showed the upper part of the compressor which concerns on Embodiment 1 of this invention. It is the perspective view which showed the oil separation member of the compressor which concerns on Embodiment 1 of this invention. It is a graph which shows an example of the calculation result which showed the relationship between the driving | operation rotation speed of a compressor, and the representative diameter of the oil droplet which flows out out of a compression mechanism. (A) is explanatory drawing which showed operation | movement of the conventional oil separation member, (B) is explanatory drawing which showed operation | movement of the oil separation member in Embodiment 1 of this invention. (A) is explanatory drawing which showed the principle of the oil discharge path of the conventional compressor, (B) is explanatory drawing which showed the principle of the oil discharge path of the compressor of Embodiment 1 of this invention. It is the graph which showed the relationship between the magnitude | size of the negative pressure which generate | occur | produces in the oil discharge path of the compressor of Embodiment 1 of this invention, and a gas flow rate. It is the principal part enlarged view which showed the modification of the oil separation member of the compressor which concerns on Embodiment 1 of this invention. It is the perspective view which showed the oil separation member of the compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing which showed the structural member of the oil separation member of the compressor which concerns on Embodiment 2 of this invention. It is the modification 1 of the compressor which concerns on Embodiment 2 of this invention, Comprising: It is the perspective view which showed the oil separation member. It is an expanded view of the oil separation member shown in FIG. It is the modification 2 of the compressor which concerns on Embodiment 2 of this invention, Comprising: It is an expanded view of an oil separation member. It is the perspective view which showed the oil separation member of the compressor which concerns on Embodiment 3 of this invention. It is a distribution map of the pressure which acts on the oil separation member of the compressor concerning Embodiment 3 of the present invention. It is the perspective view which showed the oil separation member of the compressor which concerns on Embodiment 4 of this invention. It is the perspective view which showed the modification of the oil separation member of the compressor which concerns on Embodiment 4 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof is omitted or simplified as appropriate. Moreover, about the structure as described in each figure, the shape, a magnitude | size, arrangement | positioning, etc. can be suitably changed within the scope of the present invention.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing an overall configuration of a compressor according to Embodiment 1 of the present invention. FIG. 2 is an enlarged view of a main part showing the upper part of the compressor according to Embodiment 1 of the present invention. FIG. 3 is a perspective view showing an oil separation member of the compressor according to Embodiment 1 of the present invention.

[Description of configuration]
As shown in FIG. 1, the compressor 80 according to the first embodiment includes a sealed container 1 having an oil reservoir 1 a that stores the lubricating oil 4 at the bottom. Inside the hermetic container 1, an electric motor unit 2 and a compression mechanism unit 3 driven by the electric motor unit 2 are installed. The sealed container 1 includes a cylindrical central container 11 and an upper container 12 and a lower container 13 that are fitted in the upper and lower openings of the central container 11 in a sealed state. A suction pipe 6 to which a suction muffler 5 is attached is connected to the central container 11. A discharge pipe 7 is connected to the upper container 12. The suction pipe 6 is a connection pipe for sending low-temperature and low-pressure gas refrigerant flowing through the suction muffler 5 into the compression mechanism unit 3. The discharge pipe 7 is a connection pipe for allowing the high-temperature and high-pressure gas refrigerant in the sealed container 1 compressed by the compression mechanism unit 3 to flow into the refrigerant pipe.

The electric motor unit 2 includes a stator 21 provided inside the sealed container 1 and a rotatable rotor 22 disposed inside the stator 21 and connected to a drive shaft 23. The stator 21 is fixed to the inner peripheral surface of the central container 11. The rotor 22 is provided with its outer peripheral surface facing the inner peripheral surface of the stator 21. A preset interval, that is, an air gap 2 a is provided between the outer peripheral surface of the rotor 22 and the inner peripheral surface of the stator 21. A drive shaft 23 that extends downward is connected to the rotor 22. The drive shaft 23 is rotatably supported by the upper bearing 34 and the lower bearing 35 and rotates together with the rotor 22. Further, an oil suction hole 23 a that opens to the bottom side of the sealed container 1 is provided in the shaft center portion of the drive shaft 23. A centrifugal pump 23b having a helical stirring plate is provided in the oil suction hole 23a.

The compression mechanism section 3 is fixed to the central container 11 with a lower space A provided in the lower part of the electric motor section 2. In the first embodiment, the case where the compression mechanism unit 3 is a rotary type will be described as an example. The compression mechanism unit 3 is connected to the drive shaft 23 and has a function of compressing the refrigerant. The compression mechanism unit 3 includes a cylindrical cylinder 31, a piston 32, a vane 33, an upper bearing 34, and a lower bearing 35. The upper bearing 34 is provided with an upper muffler 36. The lower bearing 35 is provided with a lower muffler 37. In addition, an oil supply pipe 40 that extends downward through the lower muffler 37 is fixed to the lower portion of the compression mechanism unit 3 with a gap between the drive shaft 23 and the oil supply pipe 40.

The cylinder 31 has a central axis that is eccentric with respect to the central axis of the drive shaft 23. The cylinder 31 is provided with a suction port 38 to which the suction pipe 6 is connected. In addition, the cylinder 31 is provided with a discharge port 34 a provided in the upper bearing 34 and a groove (not shown) that connects the discharge port 35 a provided in the lower bearing 35 and the inside of the cylinder 31. Further, the cylinder 31 is provided with a through hole (not shown) for returning the lubricating oil 4 separated at the upper part of the cylinder 31 to the oil reservoir 1a.

The piston 32 is coaxial with the central axis of the drive shaft 23 and is fitted to the drive shaft 23 so as to rotate together with the drive shaft 23. A vane 33 is slidably accommodated in the piston 32. Each of the upper bearing 34 and the lower bearing 35 has a disc portion, and the upper and lower end surfaces of the cylinder 31 are closed by the disc portion. The discharge port 34 a is formed in the disc portion of the upper bearing 34. The discharge port 35 a is formed in the disc portion of the lower bearing 35. That is, the compression mechanism unit 3 is connected to the electric motor unit 2 via the drive shaft 23, and the driving force of the electric motor unit 2 is transmitted to the compression mechanism unit 3 via the drive shaft 23, thereby allowing the gas refrigerant to flow. It is configured to compress.

The upper muffler 36 is provided on the upper part of the disk part of the upper bearing 34, that is, on the upper part of the compression mechanism part 3 so as to cover the discharge port 34 a. A muffler discharge hole 36 a is formed in the upper muffler 36. The lower muffler 37 is provided in the lower part of the disk part of the lower bearing 35 so that the discharge outlet 35a may be covered.

The lubricating oil 4 stored in the oil storage section 1a in the sealed container 1 is sucked into the oil suction hole 23a through the oil supply pipe 40 by the centrifugal pump 23b that rotates together with the drive shaft 23. The lubricating oil 4 sucked into the oil suction hole 23 a flows between the upper bearing 34 and the drive shaft 23 from the upper oil supply port 23 c and flows between the upper bearing 34 and the upper surface of the piston 32. Further, the lubricating oil 4 flows between the lower bearing 35 and the drive shaft 23 from the lower oil supply port 23 d and flows between the lower bearing 35 and the lower surface of the piston 32. The drive shaft 23 and the piston 32 rotate smoothly by supplying the lubricating oil 4. Further, the lubricating oil 4 is also supplied to the vane 33 side so that the vane 33 slides smoothly.

As shown in FIGS. 2 and 3, the lubricating oil 4 is separated from the gas mixed with the gas refrigerant and the lubricating oil 4 in the upper space B of the electric motor unit 2 in the sealed container 1. An oil separating member 100 used for returning to the bottom of the oil is provided. The oil separation member 100 is connected to the upper end portion of the drive shaft 23 and rotates. Specifically, the oil separation member 100 is connected to the protruding portion 23e of the drive shaft 23, and is provided on a disk-shaped plate portion 100a that rotates in conjunction with the drive shaft 23, and an upper surface of the plate portion 100a. And a side wall portion 100b forming a recess 8 facing the discharge pipe 7 together with the upper surface.

As shown in FIG. 3, the plate portion 100 a has an outer diameter that is substantially the same as the outer diameter of the rotor 22. That is, the plate portion 100 a covers the upper side of the gas hole 22 a provided in the rotor 22. The side wall part 100b is provided so as to surround the lower part of the discharge pipe 7 along the peripheral edge of the plate part 100a. In the lower part of the side wall part 100b, an oil drainage path 100c protruding in the radial direction from the outer peripheral surface of the side wall part 100b is provided. As an example, four oil drain passages 100c are provided at intervals along the circumferential direction of the side wall portion 100b. The oil drainage path 100c is an oil drainage pipe constituted by a pipe line as an example.

[Description of operation]
Next, based on FIG.1 and FIG.2, operation | movement of the compressor 80 of Embodiment 1 is demonstrated. When the drive shaft 23 is rotated by driving the electric motor unit 2, the compressor 80 rotates the piston 32 in the cylinder 31 together with the drive shaft 23. The rotation of the piston 32 causes the vane 33 accommodated in the piston 32 to rotate eccentrically while moving the piston. At this time, the gas refrigerant enters the compression chamber surrounded by the inner wall of the cylinder 31, the piston 32, and the vane 33 from the suction port 38 of the compression mechanism unit 3 through the suction pipe 6. The gas refrigerant in the compression chamber is compressed as the volume in the compression chamber decreases as the piston 32 rotates. At this time, the lubricating oil 4 that has flowed into the cylinder 31 is compressed together with the gas refrigerant and mixed with the gas refrigerant.

The gas in which the lubricating oil 4 and the gas refrigerant are mixed (hereinafter referred to as a mixed gas) passes through a groove communicating with the inside of the cylinder 31 from the discharge port 34a provided in the upper bearing 34 to the internal space of the upper muffler 36. And flows into the inner space of the lower muffler 37 from the discharge port 35 a provided in the lower bearing 35. The gas refrigerant that has flowed into the inner space of the lower muffler 37 is guided to the inner space of the upper muffler 36 through gas holes (not shown) passing through the lower bearing 35, the cylinder 31, and the upper bearing 34. The gas refrigerant is discharged from the muffler discharge hole 36 a into the lower space A between the electric motor unit 2 and the compression mechanism unit 3.

The mixed gas discharged into the lower space A is, as indicated by an arrow X in FIG. 2, an air gap 2 a provided between the gas hole 22 a provided in the rotor 22 and the stator 21 and the rotor 22. And flow into the upper space B in the upper part of the sealed container 1. The mixed gas flowing into the upper space B collides with the lower surface of the plate portion 100a of the oil separation member 100. At this time, a part of the lubricating oil 4 contained in the discharge gas is agglomerated and separated by falling downward due to gravity against the gas flow.

In the upper space B, a swirling flow is generated by the rotation of the oil separating member 100, and the mixed gas colliding with the lower surface of the plate portion 100a flows in the horizontal direction while being attracted by the swirling flow. There is a density difference between the lubricating oil 4 and the refrigerant gas contained in the mixed gas, and a larger centrifugal force acts as the particle size of the lubricating oil 4 increases. Therefore, the lubricating oil 4 follows a movement trajectory having a turning radius larger than that of the refrigerant gas, and collides with the inner peripheral surface of the sealed container 1 to be separated from the refrigerant gas.

FIG. 4 is a graph showing an example of a calculation result showing the relationship between the operating rotational speed of the compressor and the representative diameter of oil droplets flowing out from the compression mechanism. The horizontal axis of FIG. 4 represents the operating rotational speed [rps] of the compressor. The vertical axis in FIG. 4 indicates the representative oil droplet diameter [μm] flowing out from the compression mechanism. The graph shown in FIG. 4 is calculated using the equation of Tatterson et al. (Corona “Revised Gas-Liquid Two-Phase Flow Technology Handbook”, P301) under the conditions assuming heating operation. From the graph shown in FIG. 4, it can be seen that the average particle size of the oil droplets becomes smaller as the number of revolutions increases.

As shown in FIG. 2, the discharge pipe 7 is installed in the vicinity of the upper surface of the plate portion 100a. The distance between the opening end of the discharge pipe 7 and the upper surface of the plate portion 100a is set at a position where the outflow amount of the lubricating oil 4 flowing out of the compressor 80 is minimized. That is, there is an optimum point in the distance between the opening end of the discharge pipe 7 and the plate portion 100a. The optimum point has an effect (a) in which the lubricating oil 4 hardly flows out and an effect (b) in which the lubricating oil 4 easily flows out. ). The oil droplet behavior of (a) and (b) will be described below.

(A) Oil Drop Behavior When the distance between the opening end of the discharge pipe 7 and the plate portion 100a is reduced, the oil droplet having a small particle diameter contained in the gas is directly applied to the opening end of the discharge pipe 7 by the side wall portion 100b. You can prevent entry. Moreover, the effect which shields the oil droplet which tries to penetrate | invade into the recessed part 8 enclosed by the side wall part 100b increases.

(B) Oil droplet behavior When the distance between the opening end of the discharge pipe 7 and the plate portion 100a is reduced, the gas refrigerant exceeding the height of the side wall portion 100b as shown by the arrow in FIG. It flows along the upper surface of the plate part 100a toward the end. At this time, fine oil droplets contained in the gas refrigerant that has flowed into the recess 8 surrounded by the side wall portion 100b collide with the upper surface of the plate portion 100a on the side facing the discharge pipe 7 or the inside of the side wall portion 100b. Then, it becomes an oil film, stays in the recess 8, and is sucked into the discharge pipe 7. Here, if the lubricating oil 4 is not discharged from the recessed portion 8, the oil layer staying in the recessed portion 8 becomes thick and a lot of oil is sucked into the discharge pipe 7. Therefore, in order to efficiently perform oil separation from the mixed gas at high rotational speed operation, the lubricating oil 4 once flowing into the recess 8 is discharged so as not to stay in the recess 8 and be sucked into the discharge pipe 7. There is a need to.

Since the oil separation member 100 of the compressor 80 according to Embodiment 1 has the oil discharge passage 100c protruding from the outer peripheral surface of the side wall portion 100b, the lubricating oil 4 can be efficiently separated from the mixed gas. it can.

[Comparison of Operation of Conventional Oil Separation Member and Oil Separation Member 100 in Embodiment 1]
Next, based on FIGS. 5 and 6, the operation of the oil separation member 100 according to Embodiment 1 will be described in detail while comparing with the operation of the conventional oil separation member 90. FIG. 5A is an explanatory view showing the operation of a conventional oil separation member, and FIG. 5B is an explanatory view showing the operation of the oil separation member in Embodiment 1 of the present invention. FIG. 6A is an explanatory view showing the principle of the oil discharge passage of the conventional compressor, and FIG. 6B is an explanatory view showing the principle of the oil discharge passage of the compressor according to Embodiment 1 of the present invention. is there. 5A and 5B, the broken line arrows indicate the gas flow, and the white arrows indicate the rotation direction of the rotor 22. In addition, the arrows shown in FIGS. 6A and 6B indicate the gas flow. Moreover, the code | symbol W of FIG. 6 (A) and FIG. 6 (B) has shown the liquid stored in the container.

As shown in FIG. 5, swirl flows (broken arrows) are generated in the outer periphery of the conventional oil separation member 90 and the outer periphery of the oil separation member 100 according to the first embodiment. In the oil separation member 100 of the first embodiment shown in FIG. 5 (B), the oil drain passage 100c is provided in the side wall portion 100b so as to protrude in the radial direction. It is moving at the rotation speed. Therefore, the moving speed of the outlet end of the oil drain passage 100c is much higher than the speed of the swirl flow in the region several mm away from the side wall 100b, and the pipe of the oil drain passage 100c is relatively in the direction of the arrow Y. A flow of refrigerant gas that bends against the wall is generated. At this time, a vortex is generated at the outlet end of the oil discharge passage 100c, and a local pressure drop occurs. On the other hand, as shown in FIG. 5A, in the conventional oil separation member 90, the discharge hole 90c is formed in the side wall portion 90b, so that the flow Y generated in the oil separation member 100 according to the first embodiment is generated. do not do.

The principle of the oil drainage passage 100c of the oil separation member 100 in the first embodiment uses the principle used for spraying or spraying. A pipe 90d shown in FIG. 6 (A) corresponds to the discharge hole 90c of the conventional oil separation member 90 shown in FIG. 5 (A). In the example shown in FIG. 6A, since there is no difference between the pressure at the outlet end of the pipe 90d and the surrounding pressure, the liquid W does not rise in the pipe 90d and does not flow out of the pipe 90d. On the other hand, the pipe 100d shown in FIG. 6B corresponds to the oil drain passage 100c of the oil separation member 100 in the first embodiment. As shown in FIG. 6B, since the pressure at the outlet end of the pipe 100d falls below the ambient pressure, the liquid W rises in the pipe 100d and flows out from the upper end of the pipe 100d due to the influence of the gas flow. To do. That is, the compressor 80 according to the first embodiment applies the above principle, and separates the lubricating oil 4 from the refrigerant by utilizing the difference between the pressure at the outlet end of the pipe 100d and the ambient pressure. .

FIG. 7 is a graph showing the relationship between the magnitude of the negative pressure generated in the oil drainage path of the compressor according to Embodiment 1 of the present invention and the gas flow rate. The horizontal axis in FIG. 7 indicates the gas velocity. The vertical axis in FIG. 7 indicates the magnitude of the negative pressure generated. (A) shown in FIG. 7 shows the magnitude of the negative pressure generated in the oil drain passage 100c of the compressor 80. (B) shown in FIG. 7 has shown the magnitude | size of the negative pressure generate | occur | produced in the oil separation member which formed the opening part in the outer peripheral surface of a side wall part as an oil drainage path.

As shown in FIG. 7A, in the oil separation member 100 according to the first embodiment, the negative pressure generated in the oil discharge passage 100c increases as the gas flow rate increases. On the other hand, as shown in FIG. 7 (b), in the oil separation member in which an opening is formed on the outer peripheral surface of the side wall as an oil drainage path, the negative pressure does not increase even if the gas flow rate increases. That is, according to the compressor 80 of the first embodiment, the lubricating oil 4 staying in the recess 8 can be discharged to the outside of the side wall portion 100b by using the negative pressure generated in the oil discharge passage 100c.

[Effect of Compressor according to Embodiment 1]
The compressor 80 according to the first embodiment of the present invention includes an oil separation member 100 that is connected to the upper end portion of the drive shaft 23 and rotates, and a discharge pipe 7 provided above the oil separation member 100. Yes. The oil separating member 100 includes a plate portion 100a that rotates in conjunction with the drive shaft 23, a side wall portion 100b that is provided on the upper surface of the plate portion 100a, and that forms a recess 8 that faces the discharge pipe 7 together with the upper surface, and a side wall portion. And an oil drain passage 100c protruding from the outer peripheral surface of 100b.

Therefore, when the oil separation member 100 rotates, the compressor 80 generates a speed difference between the gas speed around the side wall portion 100b and the rotation speed at the outlet end of the oil drainage passage 100c, and the relative gas flow is reduced. The flow can generate a pressure loss at the outlet end of the oil discharge passage. In other words, since the oil drainage capacity can be increased by the pressure drop at the outlet end of the oil drain passage 100c, the lubricating oil 4 is discharged from the side wall portion 100b and efficiently separated regardless of the flow rate of the refrigerant gas. Can do. Therefore, the compressor 80 can reduce the lubricating oil 4 flowing out from the discharge pipe 7, and there is no shortage of oil supply to the sliding portion, and a highly reliable compressor can be obtained.

Next, a modification of the compressor according to Embodiment 1 will be described based on FIG. FIG. 8 is a modification of the compressor according to Embodiment 1 of the present invention, and is an enlarged view of the main part of the oil separation member. The oil drainage passage 100c shown in FIG. 8 is characterized in that the front portion in the rotation direction of the drive shaft 23 protrudes outward from the rear portion in the rotation direction of the drive shaft 23. Specifically, the end surface on the outlet side of the oil drainage passage 100c is configured as an inclined surface that inclines toward the side wall portion 100b from the front to the rear in the rotation direction of the drive shaft 23.

Like the compressor 80 shown in FIG. 8, the end surface on the outlet side of the oil drainage passage 100 c is an inclined surface that inclines from the front to the rear in the rotational direction of the drive shaft 23, so that a few mm from the side wall 100 b. The swirling flow in the remote area can be adjusted, and the negative pressure generated at the outlet end of the oil drain passage 100c can be adjusted.

In addition, the oil drainage path 100c may have a configuration in which, for example, the end surface on the outlet side is a curved surface that descends toward the side wall portion 100b from the front to the rear in the rotation direction of the drive shaft 23, or may have another shape. Further, the configuration of the oil discharge passage 100c is not limited to the compressor of the first embodiment, and can be applied to the compressors of the second to fourth embodiments described below.

Embodiment 2. FIG.
Next, a compressor according to Embodiment 2 of the present invention will be described with reference to FIGS. FIG. 9 is a perspective view showing an oil separation member of the compressor according to Embodiment 2 of the present invention. FIG. 10 is an explanatory view showing constituent members of the oil separation member according to Embodiment 2 of the present invention. In the second embodiment, only the parts different from the configuration described in the first embodiment will be described. Moreover, about the same structure as the compressor demonstrated in Embodiment 1, the same code | symbol is attached | subjected and the description is abbreviate | omitted suitably.

As shown in FIG. 9, the oil separation member 100 of the compressor 80 according to the second embodiment has a configuration in which a side wall portion 101 b provided on the upper surface of the plate portion 101 a is formed with a concave portion 8 having a square shape in plan view. is there. The side wall portion 101b can generate a swirl flow stronger than the concave portion 8 having a circular shape in plan view described in the first embodiment. This is because the surrounding gas can be stirred by the planar side wall portion 101b.

Further, the oil drain passage 101c is provided at one opposing vertex of the side wall 101b. Lubricating oil 4 after colliding with the inner wall of the side wall 101b is agglomerated at the apex. That is, the lubricating oil 4 can be efficiently discharged to the outside of the side wall 101b by providing the side wall 101b at the apex. In addition, in the example of illustration, although the structure which provided the oil draining path 101c in two places of the vertex part was shown, the oil draining path 101c may be provided also in another vertex part, and a higher oil draining effect can be acquired. .

As shown in FIG. 10, the oil separation member 101 according to the second embodiment is formed by bending a part of the side wall portion 101b to form an oil drain passage 101c. By bending a part of the side wall portion 101b to form the oil drain passage 101c, the processing cost can be reduced. However, the oil drain passage 101c may be formed as a separate body and then attached to the side wall 101b. Although illustration is omitted, in the second embodiment, the side wall portion 101b may be formed by bending each edge of the rectangular plate portion 101a.

Next, a modification of the compressor according to Embodiment 2 of the present invention will be described with reference to FIGS. FIG. 11 is a perspective view showing an oil separation member, which is Modification Example 1 of the compressor according to Embodiment 2 of the present invention. 12 is a development view of the oil separating member shown in FIG. In FIG. 12, the solid line indicates the outline or the cut portion, and the broken line indicates the bent portion.

The oil separation member 102 shown in FIG. 11 has a configuration in which a concave portion 8 having a hexagonal shape in plan view is formed on a side wall portion 102b provided on the upper surface of the plate portion 102a. This side wall portion 102b can also generate a swirl flow stronger than the concave portion 8 having a circular shape in plan view described in the first embodiment.

The oil drainage path 102c is provided at the apex of the side wall 102b. Lubricating oil 4 after colliding with the inner wall of the side wall 102b is agglomerated at the apex. That is, the lubricating oil 4 can be efficiently discharged to the outside of the side wall 102b by providing the side wall 102b at the apex. It should be noted that the oil drain passage 102c may be provided at all the apexes shown in the figure, or may be provided only at some apexes.

As shown in FIG. 12, the oil separation member 102 is formed by bending a single plate material. Specifically, the side wall part 102b is formed in each edge of the hexagonal board part 102a. Oil drain passage pieces 102d constituting part of the oil drain passage 102c are formed at both ends of the side wall portion 102b. The oil drain passage 102c is formed by combining adjacent oil drain passage pieces 102d. Of the adjacent oil drain passage pieces 102d, one has a fitting hole 102e and the other has a fitting claw 102f. The fitting hole 102e and the fitting claw 102f are formed in a portion that becomes the upper surface of the oil drainage passage 102c. The fitting hole 102e and the fitting claw portion 102f are fitted together, and the adjacent oil drain passage pieces 102d are coupled to form the oil drain passage 102c. In addition, the structure which couple | bonds the adjacent oil draining path piece 102d is not limited to the form shown in FIG.11 and FIG.12. Other forms may be used as long as adjacent oil drain passage pieces 102d can be joined to form the oil drain passage 102c.

FIG. 13 is a second variation of the compressor according to the second embodiment of the present invention, and is an exploded view of the oil separation member. The oil separation member 103 shown in FIG. 13 also has a configuration in which the side wall portion 103b provided on the upper surface of the plate portion 103a is a concave portion 8 having a hexagonal shape in plan view. The oil separation member 103 shown in FIG. 13 is formed by combining three constituent members 9 each having a part of the plate portion 103a, the side wall portion 103b, and the oil discharge passage 103c.

Each component 9 has the same configuration. The component member 9 is formed by bending a rectangular plate material. An intermediate portion of the plate material corresponds to the plate portion 103a. Side wall portions 103b are formed at both ends in the longitudinal direction of each plate material. An oil drain passage piece 103d constituting a part of the oil drain passage 103c is formed at both left and right ends of the side wall portion 103b. A fitting hole 103e is formed in one of the adjacent oil drain passage pieces 103d, and a fitting claw 103f is formed in the other. The fitting hole 103e and the fitting claw 103f are formed in a portion that becomes the upper surface of the oil drainage passage 103c. In addition, a connecting hole 103g is formed in the central portion of each plate material. Since the component member 9 has a simple shape and can be easily molded, the component member 9 can contribute to a reduction in manufacturing cost of the oil separation member 103.

As shown in FIG. 13, in order to form the oil separating member 103, first, the three component members 9 arranged at different angles so that the shape in plan view is a hexagon are overlapped, and the position of the connecting hole 103g is set. Match. And the connection claw part 103h is attached to the connection hole 103g, and the three structural members 9 are joined. Next, the fitting hole 103e and the fitting claw portion 103f are fitted together to connect the adjacent oil drainage passage pieces 103d to form the oil drainage passage 103c. In addition, the structure which couple | bonds the adjacent oil draining path piece 103d is not limited to the form shown in FIG. Other forms may be used as long as the oil drainage passage 103c can be formed by combining adjacent oil drainage passage pieces 103d. Moreover, the method of joining the three component members 9 is not limited to the illustrated form, and other forms may be used. Further, the number of the constituent members 9 is not limited to three as illustrated, and may be two or more.

The

oil separation member

101, 102 or 103 in the second embodiment is a

side wall portion

101b, 102b or 103b provided on the upper surface of the

plate portion

101a, 102a or 103a, and the shape in plan view is, for example, a triangle or an octagon. A polygonal configuration may be used.

As described above, the compressor 80 according to the second embodiment is configured such that the

side wall portion

101b, 102b, or 103b forms the concave portion 8 having a polygonal shape in plan view. The

oil drain passages

101c, 102c, or 103c are provided at at least one vertex among the plurality of polygonal vertexes. Therefore, the compressor 80 according to the second embodiment can efficiently discharge the lubricating oil 4 aggregated at the apex of the polygon to the outside of the

side wall portion

101b, 102b or 103b. An effect can be obtained.

Embodiment 3 FIG.
Next, based on FIG.14 and FIG.15, the compressor which concerns on Embodiment 3 of this invention is demonstrated. FIG. 14 is a perspective view showing an oil separation member of a compressor according to Embodiment 3 of the present invention. FIG. 15 is a distribution diagram of pressure acting on the oil separation member of the compressor according to Embodiment 3 of the present invention. In the third embodiment, only parts different from the configurations described in the first and second embodiments will be described. The same components as those described in the first and second embodiments are denoted by the same reference numerals, and the description thereof is omitted as appropriate.

As shown in FIG. 14, in the oil separation member 104 of the compressor 80 according to the third embodiment, an oil drain passage 104c is formed on the upper surface of the disk-shaped plate portion 104a so as to protrude outward at the center portion of the side wall surface. The four flat side wall portions 104b are provided, and the concave portion 8 having a square shape in plan view is formed. The oil drainage passage 104c has a gate shape and is formed at substantially the same height as the side wall portion 104b. A gap 104d for discharging the lubricating oil 4 to the outside of the side wall part 104b is provided between the adjacent side wall parts 104b. Specifically, the gap 104d is provided at the apex of the rectangle. This is because the lubricating oil 4 after colliding with the inner wall of the side wall portion 101b aggregates at the apex portion. That is, the lubricating oil 4 aggregated through the gap 104d can be efficiently discharged to the outside of the side wall portion 104b. In the illustrated example, the oil drain passage 104c is provided in the vicinity of the center of each side wall surface that is closest to the discharge pipe 7. This is because a negative pressure that opposes the suction force of the discharge pipe 7 is generated to prevent the lubricating oil 4 from flowing out of the discharge pipe 7. However, the oil drainage path 104c is not limited to being provided in the vicinity of the central portion, and may be provided at other locations on the side wall surface. Further, the oil drainage passage 104c is not limited to the illustrated shape, and may be, for example, a circular tube as shown in FIG. 3 or another shape.

As shown in FIG. 15, in the recess 8 formed by the side wall portion 104 b in the third embodiment, a negative pressure region (due to flow pressure loss of the discharge pipe 7) is surrounded by a broken line at the center of the oil separation member 104. I) has occurred. When the concave portion 8 having a square shape in plan view is formed in the side wall portion 104b, a negative pressure region (II) is generated from the center of the side wall portion 104b to the counter-rotation direction side by the rotation of the side wall portion 104b. Due to the influence of the negative pressure regions (I) and (II), a partial stagnation region is formed, and the centrifugal force separation effect of the oil droplets is reduced. However, in the compressor 80 according to the third embodiment, since the oil discharge passage 104c is provided, the lubricating oil 4 from the stagnation region can be discharged to the outside of the side wall portion 102b, and oil separation can be performed efficiently. Can do.

In the third embodiment, the configuration is shown in which the gap 104d is provided at the apex of the side wall 104b. However, the oil drainage path 104c may be provided at any or all apexes instead of the gap 104d. In other words, a higher separation effect can be obtained by increasing the number of oil drain passages 104c. Moreover, the oil separation member 104 in Embodiment 3 can be processed by bending a single plate by forming the plate portion 104a into a quadrangular shape, and processing costs can be reduced. In addition, the oil separation member 104 may process each component member as a separate member, and may combine finally. Moreover, the compressor 80 of Embodiment 3 may arrange | position the side wall part 104b so that the planar view shape may become the polygonal recessed part 8, such as a hexagon or an octagon, for example.

Embodiment 4 FIG.
Next, based on FIG.16 and FIG.17, the compressor 80 which concerns on Embodiment 4 of this invention is demonstrated. FIG. 16 is a perspective view showing an oil separation member of a compressor according to Embodiment 4 of the present invention. In the fourth embodiment, only parts different from the configurations described in the first to third embodiments will be described. The same components as those described in the first to third embodiments are denoted by the same reference numerals, and the description thereof is omitted as appropriate.

As shown in FIG. 16, the oil separation member 105 of the compressor 80 according to the fourth embodiment is provided on the disk-shaped plate portion 105a and the upper surface of the plate portion 105a, and faces the discharge pipe 7 together with the upper surface. This is a configuration having an annular side wall portion 105b that forms the recess 8 and an oil drain passage 105c protruding from the outer peripheral surface of the side wall portion 105b. As an example, four oil drain passages 105c are provided at intervals along the circumferential direction of the side wall portion 105b. The oil drainage passage 105c has a configuration in which the tip end is bent downward so that the outlet end is located below the upper surface of the plate portion 105a. That is, by setting the outlet end of the oil discharge passage 105c downward, the lubricating oil 4 sucked into the oil discharge passage 105c from the inside of the recess 8 of the oil separation member 105 is dropped downward by its own weight, and the oil separation member 105 Can be efficiently discharged to the outside.

Further, the compressor 80 according to the fourth embodiment has a swirl generated by the rotation of the oil separation member 105 by bending the front end portion of the oil discharge passage 105c downward and away from the side wall portion 105b. The flow becomes smaller and the velocity of gas flowing around the oil drainage passage 103c becomes relatively larger. As already described with reference to FIG. 7, the negative pressure generated increases as the gas flow rate increases. Therefore, the compressor 80 according to Embodiment 4 can also increase the negative pressure generated in the oil discharge passage 105c, so that the oil discharge capability can be improved.

FIG. 17 is a perspective view showing a modified example of the oil separation member of the compressor according to Embodiment 4 of the present invention. The oil separation member 106 shown in FIG. 17 is provided with a disk-shaped plate portion 106a, an annular side wall portion 106b that is provided on the upper surface of the plate portion 106a and forms a concave portion 8 that faces the discharge pipe 7 together with the upper surface. The oil drain passage 106c protrudes from the outer peripheral surface of the side wall 106b. As an example, four oil drain passages 106c are provided at intervals along the circumferential direction of the side wall 106b. The oil drain passage 106c is configured to be inclined downward so that the outlet end is located on the lower side of the sealed container 1 with respect to the upper surface of the plate portion 106a. Even if it is the said structure, the effect similar to the oil separation member 105 shown in FIG. 16 can be acquired.

Although the present invention has been described above based on the embodiment, the present invention is not limited to the configuration of the embodiment described above. For example, the illustrated internal configuration of the compressor 80 is an example, and is not limited to the above-described content, and may include other components. Moreover, the structure which protruded in the direction different from radial direction from the outer peripheral surface of a side wall part may be sufficient as an oil drainage path. In short, the present invention includes a range of design changes and application variations usually made by those skilled in the art without departing from the technical idea thereof.

1 sealed container, 1a oil reservoir, 2 motor section, 2a air gap, 3 compression mechanism section, 4 lubricating oil, 5 suction muffler, 6 suction pipe, 7 discharge pipe, 8 recess, 9 components, 11 central container, 12 Upper container, 13 Lower container, 21 Stator, 22 Rotor, 22a Gas hole, 23 Drive shaft, 23a Oil suction hole, 23b Centrifugal pump, 23c Upper oil supply port, 23d Lower oil supply port, 23e Projection, 31 Cylinder, 32 Piston, 33 vane, 34 upper bearing, 34a discharge port, 35 lower bearing, 35a discharge port, 36 upper muffler, 36a muffler discharge hole, 37 lower muffler, 38 suction port, 40 oil supply pipe, 80 compressor, 90 oil separation member , 90c oil drain hole, 90d piping, 100, 101, 102, 103, 104, 10 , 106 Oil separation member, 100a, 101a, 102a, 103a, 104a, 105a Plate part, 100b, 101b, 102b, 103b, 104b, 105b, 106b Side wall part, 100c, 101c, 102c, 103c, 104c, 105c, 106c Oil passage, 100d piping, 102d, 103d oil drain passage piece, 102e, 103e fitting hole, 102f, 103f fitting claw, 103g connecting hole, 103h connecting claw, 104d gap, A lower space, B upper space.

Claims

An airtight container forming an outer shell;
A compression mechanism provided below the sealed container;
An electric motor section having a stator and a rotor, and provided above the compression mechanism section in the sealed container;
A drive shaft connecting the rotor and the compression mechanism;
An oil separation member connected to the upper end of the drive shaft and rotating;
In a compressor provided with a discharge pipe provided above the oil separation member,
The oil separating member is
A plate portion that rotates in conjunction with the drive shaft;
A side wall portion that is provided on the upper surface of the plate portion and forms a concave portion that faces the discharge pipe together with the upper surface;
And a drainage passage projecting from the outer peripheral surface of the side wall portion.
The compressor according to claim 1, wherein the oil drainage path is configured to project radially from the outer peripheral surface of the side wall portion.
The compressor according to claim 1 or 2, wherein the oil drainage path is formed by a pipe line.
The side wall portion is configured to form a polygonal concave portion in plan view,
The compressor according to any one of claims 1 to 3, wherein the oil drainage passage is provided at at least one vertex portion among a plurality of vertex portions of a polygon.
The side wall portion is configured to form a polygonal concave portion in plan view,
The compressor according to any one of claims 1 to 3, wherein the oil drainage path is provided on at least one side wall surface among a plurality of side wall surfaces constituting a polygon.
The drainage path according to any one of claims 1 to 5, wherein a front portion in the rotation direction of the drive shaft protrudes outward from a rear portion in the rotation direction of the drive shaft. Compressor.
The outlet side end portion of the oil drainage path is located below the airtight container with respect to the upper surface of the plate portion on which the side wall portion is provided. Compressor.
The compressor according to any one of claims 1 to 7, wherein the side wall portion and the plate portion or the oil drainage path are formed by bending a single plate material.
The compressor according to any one of claims 1 to 7, wherein the oil separation member is formed by combining a plurality of constituent members having the plate portion, the side wall portion, and part of the oil drainage passage.