JP6854973B2 - Compressor - Google Patents

Description

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

In recent years, the flow rate of the refrigerant has increased due to the increase in the capacity of the rotary compressor and the inverter, and the amount of lubricating oil taken out from the closed container has increased accordingly. When the lubricating oil is taken out of the closed container, the sliding parts provided in the closed container are not sufficiently lubricated, which reduces the reliability of the compressor and the operating efficiency of the air conditioner. To do. Therefore, in the rotary compressor, various oil separation measures are taken to prevent the lubricating oil from being taken out of the closed container.

For example, Patent Document 1 discloses a closed compressor in which an oil separating plate that rotates together with a drive shaft having an oil supply passage is attached to the upper space of the electric motor. The oil separation plate has a recess formed in the center thereof so as to protrude downward. The oil separation plate has a configuration in which an opening on the lower end side of the discharge pipe is inserted into the recess, and the upper side of the insertion hole of the rotor is closed by the recess to prevent oil from being pumped from the oil supply passage to the discharge space. Further, 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 inside the recess is not sucked into the discharge pipe.

Jikkenhei 2-107783

Generally, in a high-pressure shell type compressor, a high-pressure refrigerant gas and a lubricating oil are mixed and discharged from a compression chamber into a closed container. The refrigerant gas is also referred to as a discharge gas. The lubricating oil that has not been separated in the closed container is finally discharged from the discharge pipe to the outside of the closed container. In the closed compressor of Patent Document 1, when the flow rate of the refrigerant gas increases, the pressure loss of the discharge pipe increases and the suction force increases, overcoming the oil discharge capacity of the oil discharge hole and the amount of oil flowing out from the discharge pipe. May increase. That is, in this closed compressor, the lubricating oil may not 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 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 has a closed container forming an outer shell, a compression mechanism portion provided below the closed container, a stator and a rotor, and is provided in the closed container from the compression mechanism portion. Above the motor unit provided above, the drive shaft connecting the rotor and the compression mechanism unit, the oil separating member connected to the upper end of the drive shaft and rotating, and above the oil separating member. In a compressor provided with a discharge pipe, the oil separating member is provided on a plate portion that rotates in conjunction with the drive shaft and an upper surface of the plate portion, and faces the discharge pipe together with the upper surface. It has a side wall portion that forms a recess to be formed, and an oil drainage passage that protrudes from the outer peripheral surface of the side wall portion.

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

It is a vertical cross-sectional view which showed the whole structure of the compressor which concerns on Embodiment 1 of this invention. It is an enlarged view of the main part which showed the upper part of the compressor which concerns on Embodiment 1 of this invention. It is a 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 operation speed of a compressor, and the representative diameter of the oil droplet which flows out from a compression mechanism. (A) is an explanatory diagram showing the operation of the conventional oil separating member, and (B) is an explanatory diagram showing the operation of the oil separating member according to the first embodiment of the present invention. (A) is an explanatory diagram showing the principle of the oil drainage path of the conventional compressor, and (B) is an explanatory diagram showing the principle of the oil drainage path of the compressor according to the first embodiment of the present invention. It is a graph which showed the relationship between the magnitude of the negative pressure generated in the oil drainage passage of the compressor of Embodiment 1 of this invention, and the gas flow rate. It is an enlarged view of the main part which showed the modification of the oil separation member of the compressor which concerns on Embodiment 1 of this invention. It is a 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 component member of the oil separation member of the compressor which concerns on Embodiment 2 of this invention. It is a modification 1 of the compressor which concerns on Embodiment 2 of this invention, and is the perspective view which showed the oil separation member. It is a development view of the oil separation member shown in FIG. FIG. 2 is a modified example 2 of the compressor according to the second embodiment of the present invention, and is a developed view of an oil separating member. It is a perspective view which showed the oil separation member of the compressor which concerns on Embodiment 3 of this invention. It is a distribution figure of the pressure acting on the oil separation member of the compressor which concerns on Embodiment 3 of this invention. It is a perspective view which showed the oil separation member of the compressor which concerns on Embodiment 4 of this invention. It is a 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 each figure, the same or corresponding parts are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, etc. of the configurations shown in each figure can be appropriately changed within the scope of the present invention.

Embodiment 1.
FIG. 1 is a vertical cross-sectional view showing the overall configuration of the compressor according to the first embodiment of the present invention. FIG. 2 is an enlarged view of a main part showing the upper part of the compressor according to the first embodiment of the present invention. FIG. 3 is a perspective view showing an oil separating member of the compressor according to the first embodiment of the present invention.

[Configuration description]
As shown in FIG. 1, the compressor 80 according to the first embodiment includes a closed container 1 having an oil storage portion 1a for storing the lubricating oil 4 at the bottom. Inside the closed container 1, a compression mechanism unit 3 driven by the electric motor unit 2 and the electric motor unit 2 is installed. The closed container 1 is composed of 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 closed state. A suction pipe 6 to which the 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 connecting pipe for sending the low-temperature low-pressure gas refrigerant flowing in through the suction muffler 5 into the compression mechanism unit 3. The discharge pipe 7 is a connecting pipe for allowing the high-temperature and high-pressure gas refrigerant in the closed 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 closed container 1 and a rotatable rotor 22 arranged inside the stator 21 and to which a drive shaft 23 is connected. The stator 21 is fixed to the inner peripheral surface of the central container 11. The rotor 22 is provided so that the outer peripheral surface faces the inner peripheral surface of the stator 21. A preset distance, that is, an air gap 2a is provided between the outer peripheral surface of the rotor 22 and the inner peripheral surface of the stator 21. A drive shaft 23 extending 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 23a opened on the bottom side of the closed container 1 is provided in the axial center portion of the drive shaft 23. A centrifugal pump 23b having a spiral stirring plate is provided in the oil suction hole 23a.

The compression mechanism portion 3 is fixed to the central container 11 by providing a lower space A below the electric motor portion 2. In the first embodiment, a 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 portion 3 includes a cylindrical cylinder 31, a piston 32, a vane 33, an upper bearing 34, and a lower bearing 35. Further, the upper bearing 34 is provided with an upper muffler 36. The lower bearing 35 is provided with a lower muffler 37. Further, a refueling pipe 40 extending downward through the lower muffler 37 is fixed to the lower portion of the compression mechanism portion 3 with a gap between it and the drive shaft 23.

The central axis of the cylinder 31 is arranged eccentrically 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. Further, the cylinder 31 is provided with a groove (not shown) for communicating the discharge port 34a provided in the upper bearing 34 and the discharge port 35a provided in the lower bearing 35 with 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 portion of the cylinder 31 to the oil storage portion 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 with the drive shaft 23. Further, the vane 33 is slidably housed in the piston 32. The upper bearing 34 and the lower bearing 35 each have a disk portion, and the disk portions block the upper and lower end surfaces of the cylinder 31. The discharge port 34a is formed on the disk portion of the upper bearing 34. The discharge port 35a is formed on the disk 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 to supply the gas refrigerant. It is configured to be compressed.

The upper muffler 36 is provided above the disk portion of the upper bearing 34, that is, above the compression mechanism portion 3 so as to cover the discharge port 34a. A muffler discharge hole 36a is formed in the upper muffler 36. The lower muffler 37 is provided below the disk portion of the lower bearing 35 so as to cover the discharge port 35a.

The lubricating oil 4 stored in the oil storage portion 1a in the closed container 1 is sucked into the oil suction hole 23a via the oil supply pipe 40 by the centrifugal pump 23b that rotates together with the drive shaft 23. Then, the lubricating oil 4 sucked up into the oil suction hole 23a flows from the upper oil supply port 23c between the upper bearing 34 and the drive shaft 23, and also flows between the upper bearing 34 and the upper surface of the piston 32. Further, the lubricating oil 4 flows from the lower oil filler port 23d between the lower bearing 35 and the drive shaft 23, and also 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 the supply of the lubricating oil 4. Further, the lubricating oil 4 is also supplied to the vane 33 side so that the vane 33 can be smoothly slid.

Further, as shown in FIGS. 2 and 3, in the upper space B of the electric motor portion 2 in the closed container 1, the lubricating oil 4 is separated from the gas mixed with the gas refrigerant and the lubricating oil 4 and inside the closed container 1. An oil separating member 100 used to return to the bottom of the is provided. The oil separating member 100 is connected to the upper end of the drive shaft 23 and rotates. Specifically, the oil separating member 100 is provided on a disk-shaped plate portion 100a that is connected to the protruding portion 23e of the drive shaft 23 and rotates in conjunction with the drive shaft 23, and on the upper surface of the plate portion 100a. It has a side wall portion 100b that forms a recess 8 facing the discharge pipe 7 together with the upper surface.

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

[Operation description]
Next, the operation of the compressor 80 of the first embodiment will be described with reference to FIGS. 1 and 2. In the compressor 80, when the drive shaft 23 is rotated by the drive of the electric motor unit 2, the piston 32 in the cylinder 31 also rotates together with the drive shaft 23. Due to the rotation of the piston 32, the vane 33 housed in the piston 32 rotates 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 via the suction pipe 6. Then, the gas refrigerant in the compression chamber is compressed as the volume of the compression chamber becomes smaller 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 is in a state of being mixed with the gas refrigerant.

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

As shown by the arrow X in FIG. 2, the mixed gas discharged into the lower space A has an air gap 2a provided between the gas hole 22a provided in the rotor 22 and the stator 21 and the rotor 22. And, respectively, to flow into the upper space B in the closed container 1. The mixed gas that has flowed 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 discharged gas is aggregated, falls downward by gravity against the flow of the gas, and is separated.

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 difference in density between the lubricating oil 4 and the refrigerant gas contained in the mixed gas, and the larger the particle size of the lubricating oil 4, the larger the centrifugal force acts. Therefore, the lubricating oil 4 follows a motion locus having a turning radius larger than that of the refrigerant gas, collides with the inner peripheral surface of the closed container 1, and is separated from the refrigerant gas.

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

As shown in FIG. 2, the discharge pipe 7 is installed near the upper surface of the plate portion 100a. The distance between the open end of the discharge pipe 7 and the upper surface of the plate portion 100a is set at a position where the amount of lubricating oil 4 flowing out of the compressor 80 is minimized. That is, there is an optimum point at the distance between the open end of the discharge pipe 7 and the plate portion 100a, and the optimum point is the effect of making it difficult for the lubricating oil 4 to flow out (a) and the effect of making it easy for the lubricating oil 4 to flow out (b). ). The oil droplet behaviors of (a) and (b) will be described below.

Oil droplet behavior of (a) When the distance between the open end of the discharge pipe 7 and the plate portion 100a is reduced, the oil droplets having a small particle size contained in the gas are directly sent to the open end of the discharge pipe 7 by the side wall portion 100b. You can prevent the situation of entering. In addition, the effect of shielding oil droplets that are about to enter the recess 8 surrounded by the side wall portion 100b is enhanced.

Oil drop behavior of (b) When the distance between the opening end of the discharge pipe 7 and the plate portion 100a is reduced, as shown by the arrow in FIG. 2, the gas refrigerant exceeding the height of the side wall portion 100b opens the discharge pipe 7. It flows toward the end along the upper surface of the plate portion 100a. At this time, fine oil droplets contained in the gas refrigerant flowing in the recess 8 surrounded by the side wall portion 100b collide with the upper surface of the plate portion 100a or the inside of the side wall portion 100b on the side facing the discharge pipe 7. 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 recess 8, the layer of oil staying in the recess 8 becomes thick and a large amount of oil is sucked into the discharge pipe 7. Therefore, in order to efficiently separate the oil from the mixed gas in the high rotation speed operation, the lubricating oil 4 that has once flowed 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 the first embodiment has an oil drainage 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 the conventional oil separating member and the oil separating member 100 in the first embodiment]
Next, based on FIGS. 5 and 6, the operation of the oil separating member 100 according to the first embodiment will be described in detail while comparing with the operation of the conventional oil separating member 90. FIG. 5A is an explanatory view showing the operation of the conventional oil separating member, and FIG. 5B is an explanatory view showing the operation of the oil separating member according to the first embodiment of the present invention. FIG. 6A is an explanatory diagram showing the principle of the oil drainage path of the conventional compressor, and FIG. 6B is an explanatory diagram showing the principle of the oil drainage path of the compressor according to the first embodiment of the present invention. is there. In FIGS. 5 (A) and 5 (B), the broken line arrow indicates the gas flow, and the white arrow indicates the rotation direction of the rotor 22. The arrows shown in FIGS. 6 (A) and 6 (B) indicate the gas flow. Further, reference numerals W in FIGS. 6 (A) and 6 (B) indicate the liquid stored in the container.

As shown in FIG. 5, a swirling flow (broken line arrow) is generated at the outer peripheral portion of the conventional oil separating member 90 and the outer peripheral portion of the oil separating member 100 according to the first embodiment, respectively. In the oil separation member 100 of the first embodiment shown in FIG. 5B, since the oil drainage passage 100c is provided so as to protrude in the radial direction on the side wall portion 100b, the outlet end of the oil drainage passage 100c is the motor portion 2. It is moving at a rotational speed. Therefore, the moving speed of the outlet end of the oil drainage passage 100c is much higher than the speed of the swirling flow in the region several mm away from the side wall portion 100b, and the pipe of the oil drainage passage 100c is relatively in the direction of the arrow Y. A flow of refrigerant gas that collides with the wall and bends occurs. At this time, a vortex is generated at the outlet end of the oil drainage passage 100c, and a local pressure drop occurs. On the other hand, as shown in FIG. 5A, since the conventional oil separating member 90 has a configuration in which the discharge hole 90c is formed in the side wall portion 90b, the flow Y generated in the oil separating member 100 according to the first embodiment is generated. do not.

The principle of the oil drainage passage 100c of the oil separating member 100 in the first embodiment uses the principle used for spraying or spraying. The pipe 90d shown in FIG. 6A corresponds to the discharge hole 90c of the conventional oil separating member 90 shown in FIG. 5A. 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 ambient pressure, the liquid W does not rise in the pipe 90d and does not flow out from the pipe 90d. On the other hand, the pipe 100d shown in FIG. 6B corresponds to the oil drainage 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 drops below the ambient pressure, the liquid W rises in the pipe 100d and flows out from the upper end of the pipe 100d under the influence of the gas flow. To do. That is, the compressor 80 of 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 the first embodiment of the present invention and the gas flow velocity. The horizontal axis of FIG. 7 shows the gas velocity. The vertical axis of FIG. 7 shows the magnitude of the generated negative pressure. FIG. 7A shows the magnitude of the negative pressure generated in the oil drainage passage 100c of the compressor 80. FIG. 7B shows the magnitude of the negative pressure generated in the oil separating member having an opening formed on the outer peripheral surface of the side wall portion as an oil drainage path.

As shown in FIG. 7A, in the oil separating member 100 according to the first embodiment, the negative pressure generated in the oil drainage passage 100c increases as the gas flow velocity increases. On the other hand, as shown in FIG. 7B, in the oil separation member in which an opening is simply formed on the outer peripheral surface of the side wall portion as an oil drainage passage, the negative pressure does not increase even if the gas flow velocity 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 utilizing the negative pressure generated in the oil drain passage 100c.

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

Therefore, in the compressor 80, when the oil separating member 100 rotates, a speed difference occurs 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 The flow can cause a pressure loss at the outlet end of the drainage channel. That is, since the oil draining capacity can be increased by the pressure drop at the outlet end of the oil drainage passage 100c, the lubricating oil 4 is discharged from the side wall portion 100b regardless of the flow rate of the refrigerant gas to be efficiently separated. Can be done. Therefore, the compressor 80 can reduce the lubricating oil 4 flowing out from the discharge pipe 7, does not cause insufficient lubrication to the sliding portion, and can obtain a highly reliable compressor.

Next, a modified example of the compressor according to the first embodiment will be described with reference to FIG. FIG. 8 is a modified example of the compressor according to the first embodiment of the present invention, and is an enlarged view of a main part of the oil separating member. The oil drainage passage 100c shown in FIG. 8 is characterized in that the front portion of the drive shaft 23 in the rotation direction protrudes outward from the rear portion of the drive shaft 23 in the rotation direction. Specifically, the end surface on the outlet side of the oil drainage passage 100c is 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 100c is an inclined surface that inclines from the front to the rear in the rotation direction of the drive shaft 23, so that the side wall portion 100b is several mm. The swirling flow in a distant region can be adjusted, and the negative pressure generated at the outlet end of the oil drainage passage 100c can be adjusted.

The oil drainage passage 100c may have, for example, a configuration in which the end surface on the outlet side is a curved surface that descends from the front to the rear in the rotation direction of the drive shaft 23 toward the side wall portion 100b, or may have other shapes. Further, the configuration of the oil drainage channel 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.
Next, the compressor according to the second embodiment of the present invention will be described with reference to FIGS. 9 to 13. FIG. 9 is a perspective view showing an oil separating member of the compressor according to the second embodiment of the present invention. FIG. 10 is an explanatory view showing a constituent member of the oil separating member according to the second embodiment of the present invention. In the second embodiment, only the parts different from the configuration described in the first embodiment will be described. Further, the same configurations as those of the compressor described in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted as appropriate.

As shown in FIG. 9, the oil separating member 100 of the compressor 80 according to the second embodiment has a structure in which a side wall portion 101b provided on the upper surface of the plate portion 101a forms a concave portion 8 having a quadrangular plan view shape. is there. The side wall portion 101b can generate a swirling flow stronger than that of the concave portion 8 having a circular shape in a plan view described in the first embodiment. This is because the surrounding gas can be agitated by the flat side wall portion 101b.

Further, the oil drainage passage 101c is provided at one of the opposite apex portions of the side wall portion 101b. Lubricating oil 4 after colliding with the inner wall of the side wall portion 101b is aggregated at the apex portion. That is, by providing the side wall portion 101b at the apex portion, the lubricating oil 4 can be efficiently discharged to the outside of the side wall portion 101b. In the illustrated example, the oil drainage passages 101c are provided at two apex portions, but the oil drainage passages 101c may be provided at the other apex portions, and a higher oil drainage effect can be obtained. ..

As shown in FIG. 10, the oil separating member 101 according to the second embodiment is formed by bending a part of the side wall portion 101b to form the oil drainage passage 101c. By bending a part of the side wall portion 101b to form the oil drainage passage 101c, the processing cost can be suppressed. However, the oil drainage channel 101c may be formed as a separate body and then attached to the side wall portion 101b. Although not shown, in the second embodiment, each edge of the rectangular plate portion 101a may be bent to form the side wall portion 101b.

Next, a modified example of the compressor according to the second embodiment of the present invention will be described with reference to FIGS. 11 to 13. FIG. 11 is a modification 1 of the compressor according to the second embodiment of the present invention, and is a perspective view showing an oil separating member. FIG. 12 is a developed view of the oil separating member shown in FIG. In FIG. 12, the solid line indicates the outer shell or the cut portion, and the broken line indicates the bent portion.

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

The oil drainage channel 102c is provided at the apex of the side wall portion 102b. Lubricating oil 4 after colliding with the inner wall of the side wall portion 102b is aggregated at the apex portion. That is, by providing the side wall portion 102b at the apex portion, the lubricating oil 4 can be efficiently discharged to the outside of the side wall portion 102b. The oil drainage passage 102c may be provided at all the apex portions shown in the figure, or may be provided only at a part of the apex portions.

As shown in FIG. 12, the oil separating member 102 has a structure formed by bending a single plate material. Specifically, side wall portions 102b are formed on each edge of the hexagonal plate portion 102a. Oil drainage passage pieces 102d forming a part of the oil drainage passage 102c are formed at both ends of the side wall portion 102b. The oil drainage channel 102c is formed by combining adjacent oil drainage channel pieces 102d. Of the adjacent oil drainage passage pieces 102d, a fitting hole 102e is formed on one side, and a fitting claw portion 102f is formed on the other side. The fitting hole 102e and the fitting claw portion 102f are formed on 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 drainage passage pieces 102d are joined to form the oil drainage passage 102c. The configuration for connecting the adjacent oil drainage passage pieces 102d is not limited to the form shown in FIGS. 11 and 12. Other forms may be used as long as the adjacent oil drainage passage pieces 102d can be combined to form the oil drainage passage 102c.

FIG. 13 is a modification 2 of the compressor according to the second embodiment of the present invention, and is a developed view of an oil separating member. The oil separating member 103 shown in FIG. 13 is also a side wall portion 103b provided on the upper surface of the plate portion 103a, and has a configuration in which a recess 8 having a hexagonal plan view shape is formed. The oil separation member 103 shown in FIG. 13 is formed by combining three constituent members 9 having a plate portion 103a, a side wall portion 103b, and a part of the oil drainage passage 103c, respectively.

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

As shown in FIG. 13, in order to form the oil separating member 103, first, three constituent members 9 arranged at different angles so that the plan view shape becomes a hexagon are overlapped, and the position of the connecting hole 103 g is determined. Match. Then, the connecting claw portion 103h is attached to the connecting hole 103g to join the three constituent members 9. Next, the fitting hole 103e and the fitting claw portion 103f are fitted together, and the adjacent oil drainage passage pieces 103d are joined to form the oil drainage passage 103c. The configuration for connecting the adjacent oil drainage passage pieces 103d is not limited to the form shown in FIG. Other forms may be used as long as the adjacent oil drainage passage pieces 103d can be combined to form the oil drainage passage 103c. Further, the method of joining the three constituent members 9 is not limited to the illustrated form, and may be another form. Further, the number of the constituent members 9 is not limited to the three shown in the figure, and may be two or more.

The oil separating 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 has a plan view shape of, for example, a triangle or an octagon. It may have a polygonal configuration.

As described above, the compressor 80 according to the second embodiment has a configuration in which the side wall portions 101b, 102b or 103b form a concave portion 8 having a polygonal plan view shape. The oil drainage passages 101c, 102c or 103c are provided at at least one of the plurality of vertices of the polygon. Therefore, the compressor 80 according to the second embodiment can efficiently discharge the lubricating oil 4 aggregated at the apex portion of the polygon to the outside of the side wall portions 101b, 102b or 103b, so that the oil drainage is higher. The effect can be obtained.

Embodiment 3.
Next, the compressor according to the third embodiment of the present invention will be described with reference to FIGS. 14 and 15. FIG. 14 is a perspective view showing an oil separating member of the compressor according to the third embodiment of the present invention. FIG. 15 is a distribution diagram of the pressure acting on the oil separating member of the compressor according to the third embodiment of the present invention. In the third embodiment, only the parts different from the configurations described in the first and second embodiments will be described. Further, the same configurations as those of the compressors described in the first and second embodiments are designated by the same reference numerals, and the description thereof will be omitted as appropriate.

As shown in FIG. 14, in the oil separating member 104 of the compressor 80 according to the third embodiment, an oil drainage passage 104c protruding outward is formed in the central portion of the side wall surface on the upper surface of the disc-shaped plate portion 104a. This is a configuration in which four flat side wall portions 104b are provided to form recesses 8 having a quadrangular plan view shape. The oil drainage channel 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 portion 104b is provided between the adjacent side wall portions 104b. Specifically, the gap 104d is provided at the apex of the quadrangle. 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 case of the illustrated example, the oil drainage passage 104c is provided near the central portion of each side wall surface that is closest to the discharge pipe 7. This is to suppress a situation in which the lubricating oil 4 flows out from the discharge pipe 7 by generating a negative pressure that opposes the suction force of the discharge pipe 7. However, the oil drainage channel 104c is not limited to being provided near the central portion, and may be provided at another location on the side wall surface. Further, the oil drainage channel 104c is not limited to the illustrated shape, and may have, for example, a circular tubular shape as shown in FIG. 3 or another shape.

As shown in FIG. 15, in the recess 8 formed by the side wall portion 104b in the third embodiment, the negative pressure region due to the flow pressure loss of the discharge pipe 7 is formed in the portion surrounded by the broken line in the central portion of the oil separation member 104. I) has occurred. Further, when the side wall portion 104b forms the concave portion 8 having a quadrangular plan view shape, the rotation of the side wall portion 104b generates a negative pressure region (II) from the center of the side wall portion 104b in the counter-rotation direction side. 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 droplet is reduced. However, since the compressor 80 of the third embodiment is provided with the oil drainage passage 104c, the lubricating oil 4 from the stagnation region can be discharged to the outside of the side wall portion 102b, and the oil can be separated efficiently. Can be done.

Although the configuration in which the gap 104d is provided at the apex of the side wall portion 104b is shown in the third embodiment, the oil drainage passage 104c may be provided at any or all of the apex portions instead of the gap 104d. That is, by increasing the oil drainage passage 104c, a higher separation effect can be obtained. Further, in the oil separating member 104 according to the third embodiment, by forming the plate portion 104a into a quadrangular shape, one plate can be bent and processed, and the processing cost can be suppressed. The oil separation member 104 may be processed as a separate member and finally combined. Further, in the compressor 80 of the third embodiment, the side wall portion 104b may be arranged so that the concave portion 8 has a polygonal shape such as a hexagon or an octagon in a plan view.

Embodiment 4.
Next, the compressor 80 according to the fourth embodiment of the present invention will be described with reference to FIGS. 16 and 17. FIG. 16 is a perspective view showing an oil separating member of the compressor according to the fourth embodiment of the present invention. In the fourth embodiment, only the parts different from the configurations described in the first to third embodiments will be described. Further, the same configurations as those of the compressors described in the first to third embodiments are designated by the same reference numerals, and the description thereof will be omitted as appropriate.

As shown in FIG. 16, the oil separating member 105 of the compressor 80 according to the fourth embodiment is provided on the disc-shaped plate portion 105a and the upper surface of the plate portion 105a, and faces the discharge pipe 7 together with the upper surface. It has an annular side wall portion 105b forming the recess 8 and an oil drainage passage 105c protruding from the outer peripheral surface of the side wall portion 105b. As an example, four oil drainage passages 105c are provided at intervals along the circumferential direction of the side wall portion 105b. The oil drainage channel 105c has a configuration in which the tip portion is bent downward so that the outlet end is on the lower side of the closed container 1 than the upper surface of the plate portion 105a. That is, by pointing the outlet end of the oil drainage passage 105c downward, the lubricating oil 4 sucked into the oil drainage passage 105c from 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 of.

Further, in the compressor 80 according to the fourth embodiment, the tip portion of the oil drainage passage 105c is bent downward to a position away from the side wall portion 105b, so that the compressor 80 is swiveled by the rotation of the oil separation member 105. The flow becomes smaller, and the gas velocity flowing around the oil drainage channel 103c becomes relatively large. As already described with reference to FIG. 7, the larger the gas flow velocity, the larger the negative pressure generated. Therefore, the compressor 80 according to the fourth embodiment can also increase the negative pressure generated in the oil drainage passage 105c, so that the oil drainage capacity can be improved.

FIG. 17 is a perspective view showing a modified example of the oil separating member of the compressor according to the fourth embodiment of the present invention. The oil separating member 106 shown in FIG. 17 includes a disc-shaped plate portion 106a, an annular side wall portion 106b provided on the upper surface of the plate portion 106a and forming a recess 8 facing the discharge pipe 7 together with the upper surface. It is configured to have an oil drainage passage 106c protruding from the outer peripheral surface of the side wall portion 106b. As an example, four oil drainage passages 106c are provided at intervals along the circumferential direction of the side wall portion 106b. The oil drainage channel 106c is configured to be inclined downward so that the outlet end is on the lower side of the closed container 1 with respect to the upper surface of the plate portion 106a. Even with this configuration, the same effect as that of the oil separating member 105 shown in FIG. 16 can be obtained.

Although the present invention has been described above based on the embodiments, the present invention is not limited to the configuration of the above-described embodiments. For example, the internal configuration of the illustrated compressor 80 is an example and is not limited to the above-mentioned contents, and may include other components. Further, the oil drainage channel may be configured to protrude from the outer peripheral surface of the side wall portion in a direction different from the radial direction. In short, the present invention includes a range of design changes and application variations normally performed by those skilled in the art, as long as the technical idea is not deviated.

1 Closed container, 1a Oil storage part, 2 Electric motor part, 2a Air gap, 3 Compression mechanism part, 4 Lubricating oil, 5 Suction muffler, 6 Suction pipe, 7 Discharge pipe, 8 Recesses, 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 refueling port, 23d Lower refueling port, 23e protruding part, 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 exhaust Oil holes, 90d piping, 100, 101, 102, 103, 104, 105, 106 Oil separation members, 100a, 101a, 102a, 103a, 104a, 105a Plates, 100b, 101b, 102b, 103b, 104b, 105b, 106b Side wall, 100c, 101c, 102c, 103c, 104c, 105c, 106c Oil drainage channel, 100d piping, 102d, 103d Oil drainage channel piece, 102e, 103e Fitting hole, 102f, 103f Fitting claw, 103g connecting hole, 103h connecting claw, 104d gap, A lower space, B upper space.

Claims (9)

The closed container that forms the outer shell and
A compression mechanism unit provided below the closed container and
An electric motor unit having a stator and a rotor and provided above the compression mechanism unit in the airtight container, and an electric motor unit.
A drive shaft connecting the rotor and the compression mechanism unit,
An oil separating member that is connected to the upper end of the drive shaft and rotates,
In a compressor provided with a discharge pipe provided above the oil separating member,
The oil separating member is
A plate that rotates in conjunction with the drive shaft,
A side wall portion provided on the upper surface of the plate portion and forming a recess facing the discharge pipe together with the upper surface portion, and a side wall portion.
A compressor having an oil drainage passage protruding from the outer peripheral surface of the side wall portion. The compressor according to claim 1, wherein the oil drainage channel has a configuration protruding in the radial direction from the outer peripheral surface of the side wall portion. The compressor according to claim 1 or 2, wherein the oil drainage channel is formed of a pipeline. The side wall portion is configured to form a concave portion having a polygonal shape in a plan view.
The compressor according to any one of claims 1 to 3, wherein the oil drainage channel is provided at at least one apex of a plurality of polygonal vertices. The side wall portion is configured to form a concave portion having a polygonal shape in a plan view.
The compressor according to any one of claims 1 to 3, wherein the oil drainage channel is provided on at least one side wall surface among a plurality of side wall surfaces forming a polygon. The oil drainage path according to any one of claims 1 to 5, wherein the front portion of the drive shaft in the rotation direction protrudes outward from the rear portion of the drive shaft in the rotation direction. Compressor. The oil drainage channel according to any one of claims 1 to 6, wherein the end portion on the outlet side is located below the closed container with respect to the upper surface of the plate portion provided with the side wall portion. 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 passage are formed by bending one plate material. The compressor according to any one of claims 1 to 7, wherein the oil separating member is formed by combining a plurality of constituent members having the plate portion, the side wall portion, and a part of the oil drainage channel.

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