JP6479206B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor used in a refrigeration cycle apparatus.

  As a conventional rotary compressor used in a refrigeration cycle apparatus, in Patent Document 1, an introduction plate that covers a part of the upper surface of the upper bearing of the compression mechanism is provided to reduce the amount of lubricating oil scattered into the high-pressure space. Is disclosed.

JP 2007-315261 A

  However, in the rotary compressor described in Patent Document 1, when the amount of lubricating oil used is reduced, the amount of oil supplied to the spiral groove provided in the shaft is reduced, so that the oil supplied to the vane groove provided in the cylinder is reduced. The amount is also reduced. Also, the lubricating oil scattered in the high-pressure space and adhering to the sealed container or the electric motor flows in the direction of the oil sump at the bottom of the rotary compressor by the action of gravity, but the introduction plate is configured to cover the vane groove. Therefore, the lubricating oil splashed into the high-pressure space is not supplied to the vane groove. Further, during high-speed operation such as when the rotary compressor is started, the amount of oil supplied to the sliding portion of the rotary compressor increases, and the amount of lubricating oil in the vane groove may be exhausted. Therefore, in the rotary compressor described in Patent Document 1, the vane may be seized due to the exhaustion of the lubricating oil in the vane groove, so that the durability of the compression mechanism portion is reduced and the reliability of the rotary compressor is reduced. There was a problem.

  In particular, when the refrigeration cycle apparatus is configured as an air conditioner, in recent years, measures to reduce the amount of refrigerant used in the air conditioner are required to prevent global warming. As an example of a method for reducing the amount of refrigerant, focusing on the fact that the refrigerant dissolves in the lubricating oil at a certain rate, a method for reducing the amount of the refrigerant used by reducing the amount of the lubricating oil used is considered. When the amount of lubricating oil used in the rotary compressor described in Patent Document 1 is reduced, the amount of oil supplied to the sliding portion of the rotary compressor is reduced. The possibility of getting on is further increased. Therefore, when the usage amount of the lubricating oil is reduced, in the rotary compressor described in Patent Document 1, the problems regarding the durability of the compression mechanism and the reliability of the rotary compressor become more remarkable.

  The present invention has been made to solve the above-described problems, and provides a rotary compressor capable of avoiding exhaustion of lubricating oil in a vane groove and maintaining the durability and reliability of a compression mechanism section. The purpose is to do.

A rotary compressor according to the present invention includes a crankshaft having a rolling piston that rotates eccentrically, a cylinder that houses the rolling piston, a main bearing and a sub-bearing that support the crankshaft and are fixed to the cylinder, and the cylinder And is surrounded by the cylinder, the main bearing, the auxiliary bearing, the vane, and the rolling piston by a rotational driving force transmitted from the crankshaft. A compression mechanism that compresses the gas refrigerant in the open space, a sealed container that accommodates the crankshaft and the compression mechanism, and a gas refrigerant that is disposed inside the sealed container and discharged from the compression mechanism. and a partition member for separating the refrigerating machine oil is, the partition member is hollow disc shape viewed from the top Has has a slope portion which moves in the direction of the vane by its own weight and the separated refrigerating machine oil, and a supply unit for supplying the refrigerating machine oil is moved in the direction of the vane to the vane.
The rotary compressor of the present invention includes a crankshaft including a rolling piston that rotates eccentrically, a cylinder that houses the rolling piston, a main bearing and a sub-bearing that support the crankshaft and are fixed to the cylinder, A vane disposed in the cylinder and integrally formed with the rolling piston; and by the rotational driving force transmitted from the crankshaft, the cylinder, the main bearing, the sub-bearing, the vane, and the rolling piston; A compression mechanism that compresses a gas refrigerant in a space surrounded by a gas, a sealed container that houses the crankshaft and the compression mechanism, and a gas that is disposed inside the sealed container and is discharged from the compression mechanism A partition for separating the refrigerating machine oil contained in the refrigerant, and the partition is a hollow circle in a top view. Has Jo shape, has a slope portion which moves in the direction of the vane by its own weight and the separated refrigerating machine oil, and a supply unit for supplying the refrigerating machine oil is moved in the direction of the vane to the vane.

  In the present invention, since the slope portion of the partition is configured to move the refrigeration oil recovered by the partition in the direction of the vane by its own weight, the refrigeration oil recovered by the partition is reliably supplied to the vane. Can do. Therefore, according to the present invention, it is possible to provide a rotary compressor capable of avoiding exhaustion of lubricating oil in the vane grooves and vanes and maintaining the durability and reliability of the compression mechanism portion.

It is a longitudinal section showing roughly an example of rotary compressor 1 concerning Embodiment 1 of the present invention. It is the schematic which expanded a part of longitudinal section of the rotary compressor 1 which concerns on Embodiment 1 of this invention. It is the schematic which expanded a part of cross section of the rotary compressor 1 which concerns on Embodiment 1 of this invention. It is the schematic which expanded a part of longitudinal section of the rotary compressor 1 which concerns on Embodiment 2 of this invention. It is the schematic which expanded a part of cross section of the rotary compressor 1 which concerns on Embodiment 2 of this invention. It is the schematic which expanded a part of longitudinal section of the rotary compressor 1 which concerns on Embodiment 3 of this invention. It is the schematic which expanded a part of cross section of the rotary compressor 1 which concerns on Embodiment 3 of this invention.

Embodiment 1 FIG.
The configuration of the rotary compressor 1 according to Embodiment 1 of the present invention will be described with reference to FIG. FIG. 1 is a longitudinal sectional view schematically showing an example of a rotary compressor 1 according to the first embodiment. In the refrigeration cycle apparatus, the rotary compressor 1 is an element constituting a refrigeration cycle circuit.

  In the following drawings including FIG. 1, the refrigeration cycle circuit and other components constituting the refrigeration cycle circuit such as a radiator, an evaporator, and a decompression device are not shown. In the following drawings, the dimensional relationship and shape of each component may be different from the actual one. Moreover, in the following drawings, the same code | symbol is attached | subjected to the same or similar member or part, or the code | symbol is abbreviate | omitted. In addition, the positional relationship between the constituent members of the rotary compressor 1 in the following description, for example, the positional relationship such as the vertical relationship, is basically the positional relationship when the rotary compressor 1 is installed in a usable state. .

  The rotary compressor 1 is a fluid machine that discharges a low-pressure gas refrigerant sucked into the rotary compressor 1 as a high-pressure gas refrigerant. In FIG. 1, a rolling piston type rotary compressor 1 is illustrated as an example. The casing of the rotary compressor 1 is configured as a cylinder-shaped sealed container 2. The hermetic container 2 includes a main body 2a having a U-shaped longitudinal section and a lid 2b having an inverted U-shaped longitudinal section, and the outer surface of the opening of the lid 2b is an opening of the main body 2a. It is fixed to the inner surface of the. The fixed portion between the main body 2a and the lid 2b is joined by welding or the like, for example. Moreover, the base 3 for arrange | positioning the rotary compressor 1 to a vertical installation type | mold is provided in the outer surface of the bottom face of the main-body part 2a. In FIG. 1, the rotary compressor 1 is configured as a vertical compressor, but may be configured as a horizontal compressor.

  A housing 4 a of the suction muffler 4 is fixed to a support member 2 c disposed on the outer surface of the sealed container 2 on the outer surface of the main body 2 a of the sealed container 2. An inflow pipe 4b is fixed to the top of the housing 4a of the suction muffler 4 through the housing 4a. The inflow pipe 4b is, for example, a refrigerant pipe through which a low-pressure gas refrigerant or a two-phase refrigerant having a high dryness flowing out from the evaporator of the refrigeration cycle apparatus flows into the housing 4a of the suction muffler 4. In addition, one end of the suction pipe 5 is fixed to the bottom of the housing 4a of the suction muffler 4 and the other end of the suction pipe 5 passes through the side surface of the main body 2a of the sealed container 2. Is fixed.

  The suction muffler 4 is a silencer that reduces or eliminates noise generated by the refrigerant flowing from the inflow pipe 4b. The suction muffler 4 also has an accumulator function, and has a refrigerant storage function for storing surplus refrigerant and a gas-liquid separation function for retaining liquid refrigerant that is temporarily generated when the operating state changes. Have. Due to the gas-liquid separation function of the suction muffler 4, it is possible to prevent a large amount of liquid refrigerant from flowing into the sealed container 2 and liquid compression in the rotary compressor 1.

  The suction pipe 5 is a refrigerant pipe that sucks low-pressure gas refrigerant into the sealed container 2. The fixed portion between the suction pipe 5 and the main body 2a is joined, for example, by brazing. An oil return hole 5 a is provided on the side surface of the suction pipe 5. In the refrigeration cycle apparatus, the lubricating oil component contained in the gas refrigerant discharged from the rotary compressor 1 is separated, for example, in an oil separator. The oil return hole 5a functions as a return port for the lubricating oil component that returns the lubricating oil component separated in the oil separator to the inside of the sealed container 2 via the suction pipe 5.

  The discharge pipe 6 through which the discharge pipe 6 penetrates and is fixed to the upper surface of the lid portion 2 b of the closed container 2 is a refrigerant pipe that discharges a high-pressure gas refrigerant to the outside of the closed container 2. The fixed portion between the discharge pipe 6 and the lid 2b is joined, for example, by brazing.

  In addition, a charge pipe 7 is fixed through the upper surface of the lid 2b of the sealed container 2. The charge pipe 7 can be configured such that the inside of the sealed container 2 is evacuated and a gas refrigerant can be sealed inside the sealed container 2. Further, the charge pipe 7 may be configured so that lubricating oil can be sealed inside the sealed container 2.

  Furthermore, a glass terminal 8 is disposed on the upper surface of the lid 2b of the sealed container 2. The glass terminal 8 provides an interface for connecting an external power source. The external power supply is a power supply device that supplies power to the rotary compressor 1, and a general commercial AC power supply with an AC frequency of 50 Hz or 60 Hz, or an inverter power supply that can change the AC frequency is used. When the frequency variable inverter power supply is used, the rotational speed of the rotary compressor 1 can be changed. Therefore, the rotary compressor 1 can control the discharge amount of the high-pressure gas refrigerant from the discharge pipe 6. In the following description, the external power source connected to the glass terminal 8 is not shown in the following drawings including FIG.

  An electric motor unit 10, a crankshaft 20, and a compression mechanism unit 30 are accommodated in the sealed container 2. The electric motor unit 10 is disposed above a fixed portion between the main body 2a and the suction pipe 5. The crankshaft 20 extends in the vertical direction between the electric motor unit 10 and the compression mechanism unit 30 at the center of the sealed container 2, and forms the center of the sealed container 2. The compression mechanism portion 30 is configured such that the side surface portion of the compression mechanism portion 30 covers a fixed portion between the main body portion 2 a and the suction pipe 5, and the inside of the compression mechanism portion 30 communicates with the suction pipe 5. That is, the electric motor unit 10 is disposed above the compression mechanism unit 30 inside the sealed container 2. Further, the hollow space inside the sealed container 2 above the compression mechanism unit 30 is filled with a high-pressure gas refrigerant compressed by the compression mechanism unit 30.

  The electric motor unit 10 is configured as a motor that generates a rotational driving force using electric power supplied from an external power source and transmits the rotational driving force to the compression mechanism unit 30 via the crankshaft 20. The electric motor unit 10 includes a stator 12 having a hollow cylindrical appearance in a top view, and a cylindrical rotor 14 that is rotatably arranged inside the inner surface of the stator 12. The stator 12 is fixed to the inner surface of the main body 2 a of the sealed container 2, and is connected to the glass terminal 8 through a conducting wire 16. The electric motor unit 10 can rotate the rotor 14 inside the inner surface of the stator 12 by supplying electric power from an external power source to the coil wound around the stator 12 via the conductive wire 16. In the rotary compressor 1, for example, a DC brushless motor or the like is used as the electric motor unit 10.

  A crankshaft 20 is fixed to the center of the rotor 14 through the rotor 14. The crankshaft 20 is a rotating shaft that fixes the rotor 14 with a fixed surface 20 a that is a part of the outer surface of the crankshaft 20 and transmits the rotational driving force of the rotor 14 to the compression mechanism 30. The crankshaft 20 extends from the fixed surface 20a in the vertical direction, that is, in the direction of the lid 2b of the sealed container 2 and the direction of the bottom of the main body 2a of the sealed container 2. An oil separation plate 22 is provided above the fixed surface 20a. The oil separation plate 22 separates the lubricating oil contained in the high-pressure gas refrigerant discharged from the compression mechanism 30 by the centrifugal force generated by the rotation of the crankshaft 20, and drops it to the bottom of the main body 2a by the action of gravity. It is configured.

  The crankshaft 20 has a cylindrical eccentric portion 24 that is located below the fixed surface 20 a and is disposed inside the compression mechanism portion 30. A rolling piston 26 is attached to the outer surface of the eccentric portion 24 so as to be rotatable along the outer surface of the eccentric portion 24. An oil hole 28 extending upward from the lower end of the crankshaft 20 and through which lubricating oil flows is provided at the center of the crankshaft 20. A first oil supply port 28 a and a second oil supply port 28 b are provided on the outer surface of the crankshaft 20 so as to communicate with the oil hole 28 and supply lubricating oil to the compression mechanism 30.

  A spiral centrifugal pump 29 is disposed at the lower end of the oil hole 28 of the crankshaft 20. The centrifugal pump 29 is a fluid machine that sucks up the refrigerating machine oil 40 stored at the bottom of the main body 2a of the sealed container 2 by the centrifugal force generated by the rotational movement of the crankshaft 20. The refrigerating machine oil 40 sucked up by the centrifugal pump 29 is supplied to a sliding portion between the crankshaft 20 and the compression mechanism unit 30. As the refrigerating machine oil 40, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil, or the like is used.

  Next, the structure of the compression mechanism unit 30 of the rotary compressor 1 will be described.

  The compression mechanism unit 30 compresses the low-pressure gas refrigerant sucked into the low-pressure space of the sealed container 2 from the suction pipe 5 into the high-pressure gas refrigerant by the rotational driving force supplied from the electric motor unit 10 and compresses the compressed high-pressure gas. The refrigerant is discharged above the compression mechanism unit 30.

  The compression mechanism unit 30 includes a hollow cylindrical cylinder 31. The outer surface of the cylinder 31 is fixed to the inner surface of the main body 2 a of the sealed container 2. The hollow portion 31 a of the cylinder 31 accommodates the eccentric portion 24 of the crankshaft 20 and the rolling piston 26. That is, the cylinder 31 is configured such that the eccentric portion 24 of the crankshaft 20 and the rolling piston 26 can rotate eccentrically by the rotation of the crankshaft 20 in the hollow portion 31 a of the cylinder 31.

  The cylinder 31 is provided with a suction port 31 b that communicates between the suction pipe 5 and the hollow portion 31 a of the cylinder 31 and allows low-pressure gas refrigerant to flow from the suction pipe 5 into the hollow portion 31 a of the cylinder 31. In addition, the cylinder 31 is provided with a vane groove 31c extending in a radial direction from the inner surface of the cylinder 31 constituting the hollow portion 31a of the cylinder 31 when viewed from above. An opening 31d that penetrates the vane groove 31c is provided on the hollow disk surface that is the upper surface of the cylinder 31.

  A vane 32 is accommodated in the vane groove 31 c of the cylinder 31. The vane 32 is pressed against the surface of the rolling piston 26 by the restoring force of an elastic body such as a spring provided inside the vane groove 31c, and reciprocates inside the vane groove 31c by the eccentric motion of the rolling piston 26. This is a sliding member configured as described above.

  On the hollow disk surface on the upper side of the cylinder 31, that is, on the hollow disk surface on the lid portion 2 b side of the sealed container 2, a main bearing 33 that is a slide bearing is disposed. A sub-bearing 34 is disposed on the hollow disk surface on the lower side of the cylinder 31, that is, on the hollow disk surface on the bottom surface side of the main body 2 a of the sealed container 2. The main bearing 33 and the sub bearing 34 are sliding bearings that slidably support the crankshaft 20.

  The main bearing 33 has a hollow disk shape when viewed from above. The main bearing 33 includes a fixed portion 33a that is fixed to the upper hollow disk surface of the cylinder 31, and a bearing portion 33b that supports the outer surface of the crankshaft 20 so as to be slidable. The main bearing 33 is displayed as two L-shaped members in the longitudinal sectional view of FIG. Moreover, the main bearing 33 is being fixed to the hollow disc surface above the cylinder 31 with the volt | bolt etc., for example.

  The auxiliary bearing 34 has a hollow disk shape when viewed from below. The sub-bearing 34 has a fixed portion 34a that is fixed to the lower hollow disk surface of the cylinder 31, and a bearing portion 34b that slidably supports the outer surface of the crankshaft 20. The sub-bearing 34 is displayed as two L-shaped members in the longitudinal sectional view of FIG. Further, the auxiliary bearing 34 is fixed to the upper hollow disk surface of the cylinder 31 with, for example, a bolt or the like.

  In the compression mechanism portion 30, a sealable space surrounded by the rolling piston 26, the cylinder 31, the vane 32, the fixing portion 33 a of the main bearing 33, and the fixing portion 34 a of the auxiliary bearing 34 is sucked from the suction pipe 5. A compression chamber for compressing the low-pressure gas refrigerant is configured. The high-pressure gas refrigerant compressed in the compression chamber is discharged from a discharge port provided in the main bearing 33. The discharge port provided in the main bearing 33 is not shown in the following drawings including FIG.

  A silencer 35 is disposed on the upper surface side of the fixed portion 34 a of the main bearing 33. The silencer 35 covers the fixed part 34a of the main bearing 33 and a part of the bearing part 34b, and is configured to remove or reduce noise generated when the refrigerant is compressed in the compression mechanism part 30. In addition, the silencer 35 is provided with a plurality of openings 35 a for discharging high-pressure gas refrigerant flowing from the discharge port provided in the main bearing 33 into the sealed container 2. The silencer 35 is fixed to the hollow disk surface on the upper side of the cylinder 31 via the main bearing 33 with, for example, bolts.

  Next, the partition 50 provided in the rotary compressor 1 of the first embodiment will be described with reference to FIGS. 2 and 3 in addition to FIG. FIG. 2 is an enlarged schematic view of a part of a longitudinal section of the rotary compressor 1 according to the first embodiment. FIG. 3 is an enlarged schematic view of a part of the cross section of the rotary compressor 1 according to the first embodiment.

  The partition body 50 is disposed in a high-pressure space located between the electric motor unit 10 and the compression mechanism unit 30 inside the sealed container 2. For example, as illustrated in FIG. 3, the partition 50 has a hollow disk shape when viewed from above, and is configured to surround the silencer 35. By configuring the partition 50 to surround the silencer 35, the plurality of openings 35 a provided in the silencer 35 are not blocked by the partition 50. Therefore, by configuring the partition 50 so as to surround the silencer 35, it is possible to reduce the discharge pressure loss in the rotary compressor 1 and prevent the performance of the rotary compressor 1 from being deteriorated. Further, by configuring the partition body 50 so as to surround the silencer 35, the fluid resistance prevents the lubricating oil from being mixed into the high-pressure gas refrigerant due to the foaming phenomenon that occurs when the rotary compressor 1 is started. The partition 50 can be functioned. The foaming phenomenon in the rotary compressor 1 occurs when the refrigerant dissolved in the refrigerating machine oil 40 evaporates when the rotary compressor 1 is started. In particular, HFO refrigerants such as R1234yf refrigerant or R1234ze (E) refrigerant, or HC refrigerants such as R290 refrigerant, which are sometimes used as the working fluid of the rotary compressor 1, have a low global warming potential, but are soluble in the refrigerator oil 40. Is high, the foaming phenomenon becomes remarkable. However, even when the above-described refrigerant is used, if the partition 50 is configured to surround the silencer 35, it is possible to prevent the lubricating oil from being mixed into the high-pressure gas refrigerant. It is possible to prevent exhaustion of the refrigerating machine oil 40 stored at the bottom of the main body 2a. In addition, although not shown in figure, the partition 50 is being fixed to the hollow disc surface of the upper end of the cylinder 31, for example with the volt | bolt etc. via the support member.

  The partition 50 is configured to recover the lubricating oil contained in the high-pressure gas refrigerant discharged from the compression mechanism unit 30 and supply the recovered lubricating oil to the vane 32. The partition 50 collects the lubricating oil from the high-pressure gas refrigerant, and moves the collected lubricating oil in the direction of the vane 32 by its own weight, and the lubricating oil moved in the direction of the vane 32 to the vane 32. And a supply unit 54 for supply. In addition, the inclined surface portion 52 of the partition 50 is configured such that the lubricating oil is separated from the swirling flow when the swirling flow of the high-pressure gas refrigerant generated by the rotation of the rotor 14 of the electric motor unit 10 collides with the inclined surface portion 52. Can be configured.

  As shown in FIGS. 1 and 2, the slope portion 52 of the partition 50 penetrates the vane groove 31 c so that the lubricating oil collected by the slope portion 52 flows in the direction of the vane 32 by its own weight in the longitudinal section. It is inclined obliquely downward toward the direction of the opening 31d. Moreover, the supply part 54 of the partition 50 is configured to be parallel to the hollow disk surface on the upper side of the cylinder 31 in the longitudinal section, and the supply part 54 of the partition 50 is provided with an opening 54a. Yes.

  The opening 54 a of the supply portion 54 of the partition 50 can be configured in a shape and size that can supply the recovered lubricating oil to the opening 31 d of the cylinder 31. For example, as shown in FIG. 3, the opening 54 a of the supply unit 54 of the partition 50 can be configured to have the same shape and size as the opening 31 d of the cylinder 31 in a top view.

  Next, the operation of the rotary compressor 1 according to the first embodiment will be described.

  When the crankshaft 20 is rotated by driving the electric motor unit 10, the eccentric portion 24 and the rolling piston 26 housed in the cylinder 31 are eccentrically rotated together with the crankshaft 20. In conjunction with the eccentric rotation of the rolling piston 26, the vane 32 provided inside the vane groove 31c of the cylinder 31 performs a piston motion. The low-pressure gas refrigerant that has flowed into the compression mechanism portion 30 from the suction pipe 5 through the suction port 31b enters the rolling piston 26, the cylinder 31, the vane 32, the fixed portion 33a of the main bearing 33, and the fixed portion 34a of the auxiliary bearing 34. It flows into the compression chamber which is an enclosed sealed space. The low-pressure gas refrigerant flowing into the compression chamber is compressed into the high-pressure gas refrigerant as the volume of the compression chamber decreases due to the eccentric rotation of the rolling piston 26.

  The refrigerating machine oil 40 stored at the bottom of the main body 2 a in the sealed container 2 is sucked up from the lower end of the oil hole 28 by the centrifugal pump 29 that rotates together with the crankshaft 20. The refrigerating machine oil 40 sucked up from the lower end portion of the oil hole 28 flows as a lubricating oil between the bearing portion 33b of the main bearing 33 and the crankshaft 20 from the first oil supply port 28a. In addition, the lubricating oil flows between the bearing portion 34b of the auxiliary bearing 34 and the crankshaft 20 from the second oil supply port 28b. The lubricating oil flows into the sliding portion between the crankshaft 20 and the bearing portion 33b of the main bearing 33 or the bearing portion 34b of the auxiliary bearing 34, whereby the crankshaft 20 smoothly transmits the rotational driving force to the rolling piston 26. can do.

  Further, the lubricating oil flowing from the first oil supply port 28 a flows between the fixed portion 33 a of the main bearing 33 and the upper surface of the rolling piston 26. Further, the lubricating oil flowing from the second oil supply port 28 b flows between the fixed portion 34 a of the sub bearing 34 and the lower surface of the rolling piston 26. The lubricating oil is used to smoothly rotate the rolling piston 26, but a part of the lubricating oil is compressed together with the low-pressure gas refrigerant and discharged in a state of being contained in the high-pressure gas refrigerant.

  The high-pressure gas refrigerant containing the lubricating oil flows into the silencer 35 from the cylinder 31 through the discharge port provided in the main bearing 33. The high-pressure gas refrigerant inside the silencer 35 is discharged from a plurality of openings 35 a provided in the silencer 35 into a high-pressure space inside the sealed container 2 positioned between the electric motor unit 10 and the compression mechanism unit 30. The

  The high-pressure gas refrigerant discharged into the high-pressure space is attracted by the swirling flow generated by the rotation of the rotor 14 and the crankshaft 20 of the electric motor unit 10 and flows in the rotation direction of the rotor 14 and the crankshaft 20. The high-pressure gas refrigerant that flows in the rotating direction of the rotor 14 and the crankshaft 20 flows around the silencer 35 and comes into contact with the upper and lower surfaces of the slope portion 52 of the partition 50. In the slope portion 52 of the partition 50, the lubricating oil contained in the high-pressure gas refrigerant is separated from the high-pressure gas refrigerant by the collision or contact of the high-pressure gas refrigerant. The separated lubricating oil is recovered by adhering to the upper and lower surfaces of the slope portion 52 of the partition 50. The high-pressure gas refrigerant including the lubricating oil that has not adhered to the partition 50 flows through the gap provided in the stator 12 and the rotor 14 toward the upper portion of the crankshaft 20. In the upper part of the crankshaft 20, the lubricating oil component is separated from the high-pressure gas refrigerant by the centrifugal force generated by the rotation of the oil separation plate 22. The lubricating oil separated by the oil separation plate 22 adheres to the inner surface of the sealed container 2 and falls downward by gravity through an outer groove provided in the stator 12. The high-pressure gas refrigerant from which the lubricating oil component has been separated by the oil separation plate 22 reaches the lid portion 2 b of the sealed container 2 and is discharged out of the sealed container 2 through the discharge pipe 6.

  The lubricating oil that adheres to and is collected on the upper surface of the slope portion 52 of the partition 50 flows in the direction of the vane 32 due to its own weight, and flows out from the opening 54 a provided in the supply portion 54 of the partition 50. The lubricating oil that has flowed out of the opening 54 a is supplied to the vane groove 31 c through the opening 31 d of the cylinder 31 by its own weight. The lubricating oil supplied to the vane groove 31c is supplied to the vane 32 when the vane 32 passes through the vane groove 31c by reciprocation. The lubricating oil that has not been supplied to the vane 32 is collected at the bottom of the sealed container 2.

  In addition, the lubricating oil particles scattered from the bottom of the main body 2 a of the closed container 2 due to the foaming phenomenon adhere to the lower surface of the partition 50 configured to surround the silencer 35. The lubricating oil that adheres to and is collected on the lower surface of the slope portion 52 of the partition 50 flows in the direction of the vane 32 due to its own weight, and reaches the supply portion 54 of the partition 50. The lubricating oil that has reached the supply unit 54 is supplied to the vane groove 31c through the opening 31d of the cylinder 31 by its own weight. The lubricating oil that has not been supplied to the vane 32 is collected at the bottom of the sealed container 2.

  As described above, the rotary compressor 1 according to the first embodiment supports the crankshaft 20 including the rolling piston 26 that rotates eccentrically, the cylinder 31 that houses the rolling piston 26, and the crankshaft 20. The main bearing 33 and the sub-bearing 34 fixed to 31, and the vane 32 disposed on the cylinder 31 and pressed against the rolling piston 26. A compression mechanism 30 that compresses the gas refrigerant in a space surrounded by the bearing 33, the sub-bearing 34, the vane 32, and the rolling piston 26; the sealed container 2 that houses the crankshaft 20 and the compression mechanism 30; 2, the refrigerating machine oil 40 contained in the gas refrigerant discharged from the compression mechanism 30 is The partition 50 is provided with a separating portion 50, and the partition 50 supplies the vane 32 with the slope portion 52 that moves the separated refrigerating machine oil 40 in the direction of the vane 32 by its own weight, and the refrigerating machine oil 40 that is moved in the direction of the vane 32. Supply section 54.

  In the first embodiment, the slope portion 52 of the partition 50 is configured so that the recovered refrigeration oil 40 can be moved in the direction of the vane 32 by its own weight. 40 can be reliably supplied to the vane 32. According to the configuration of the first embodiment, even when the amount of the refrigerating machine oil 40 used is small, the exhaust of the refrigerating machine oil 40 in the vane groove 31c and the vane 32 of the refrigerating machine oil 40 can be avoided. Therefore, in the first embodiment, it is possible to provide the rotary compressor 1 capable of maintaining the durability of the compression mechanism unit 30 and the reliability of the rotary compressor 1.

  Further, the rotary compressor 1 of the first embodiment has a stator 12 and a rotor 14 disposed inside the stator 12, which is accommodated in the hermetic container 2, and is rotated by the rotation of the rotor 14. The crankshaft 20 is provided with an electric motor unit 10 that generates a rotational driving force. The inclined surface 52 of the partition 50 is separated from the gas refrigerant by revolving and colliding the gas refrigerant with the rotation of the rotor 14. Can be configured. According to this configuration, since the refrigerating machine oil 40 contained in the high-pressure gas refrigerant can be separated from the swirling flow of the high-pressure gas refrigerant generated by the rotation of the rotor 14, the refrigerating machine oil 40 is recovered more efficiently. be able to.

  Further, the rotary compressor 1 according to the first embodiment can be configured such that the supply section 54 of the partition 50 is provided with an opening 54a. According to this configuration, the refrigerating machine oil 40 that has moved in the direction of the vane 32 due to its own weight on the slope portion 52 of the partition 50 is passed through the opening 54 a provided in the supply portion 54 of the partition 50, and the vane groove 31 c. Can be reliably supplied.

  The rotary compressor 1 of the first embodiment further includes a silencer 35 that covers a part of the main bearing 33, and the partition 50 is configured to surround the silencer 35 in a top view. ing. According to this configuration, the partition 50 can prevent the lubricating oil from being mixed into the high-pressure gas refrigerant due to the foaming phenomenon when the rotary compressor 1 is started.

  Moreover, in the rotary compressor 1 of this Embodiment 1, R1234yf refrigerant | coolant, R1234ze (E) refrigerant | coolant, or R290 refrigerant | coolant can be used as a working fluid. The R1234yf refrigerant, the R1234ze (E) refrigerant, or the R290 refrigerant has a low global warming potential, but has a high solubility in the refrigeration oil 40. Therefore, the main body portion of the sealed container 2 is caused by a foaming phenomenon when the rotary compressor 1 is started. The amount of lubricant particles scattered from the bottom of 2a increases. However, as described above, according to the first embodiment, the refrigerating machine oil 40 contained in the high-pressure gas refrigerant can be separated from the swirling flow of the high-pressure gas refrigerant generated by the rotation of the rotor 14. Therefore, even if the refrigerating machine oil 40 is mixed into the high-pressure gas refrigerant due to the foaming phenomenon, the refrigerating machine oil 40 can be efficiently recovered. Further, as described above, the rotary compressor 1 according to the first embodiment is configured so that the partition 50 surrounds the silencer 35 in a top view, thereby mixing the lubricating oil into the high-pressure gas refrigerant. Can be prevented. In addition, since the lubricating oil particles scattered from the bottom of the main body 2a of the sealed container 2 due to the foaming phenomenon adhere to the lower surface of the slope portion 52 of the partition 50, the refrigerating machine oil 40 can be efficiently recovered. From the above, as a method for reducing the amount of refrigerant for preventing global warming, the lubricating oil will not be depleted even when the amount of lubricating oil used is reduced. It is also effective as a countermeasure against crystallization.

  In the first embodiment, the rotary compressor 1 is configured as a rolling piston type compressor, but may be configured as a swing vane type swing compressor. In the swing compressor of the swing vane system, a piston that integrates a rolling piston portion corresponding to the rolling piston 26 of the first embodiment and a vane portion corresponding to the vane 32 of the first embodiment is provided inside the cylinder 31. In preparation. In addition, the swing vane type swing compressor includes a bush for swinging the piston. The bushes are a pair of semi-cylindrical rocking members that are disposed in the cylinder 31 and are supported with the vane portion of the piston interposed therebetween. Since the swing vane type swing compressor has a bush, the number of swinging parts is larger than that of the rolling piston type compressor, so the supply amount of the refrigerating machine oil 40 to the vane portion is reduced or depleted, and the swing Sexuality is likely to deteriorate. However, even when configured as a swing compressor, the refrigerating machine oil 40 can be efficiently supplied to the vane portion, so that the exhaust of the lubricating oil is avoided and the durability and reliability of the compression mechanism portion are maintained. It is possible to provide a swing compressor that can be used.

Embodiment 2. FIG.
A rotary compressor 1 according to Embodiment 2 of the present invention will be described with reference to FIGS. 4 and 5.

  FIG. 4 is an enlarged schematic view of a part of a longitudinal section of the rotary compressor 1 according to the second embodiment. FIG. 5 is an enlarged schematic view of a part of the cross section of the rotary compressor 1 according to the second embodiment. The rotary compressor 1 according to the second embodiment is a modification of the structure of the partition body 50 according to the first embodiment described above, and other structures of the rotary compressor 1 according to the first embodiment described above. This is the same as the rotary compressor 1.

  In the partition 150 of the rotary compressor 1 according to the second embodiment, the slope portion 152 and the supply portion 154 are configured as flat plates. Further, the inclination angle θ1 of the supply unit 154 is configured to be equal to or larger than the inclination angle θ2 of the inclined surface portion 152, that is, θ1 ≧ θ2> 0. The inclination angle θ1 is an angle of the supply unit 154 in the longitudinal section with respect to the direction perpendicular to the central axis of the crankshaft 20, that is, the horizontal direction in FIG. In addition, the inclination angle θ2 is an angle of the slope portion 152 in the longitudinal section with respect to the direction perpendicular to the central axis of the crankshaft 20, that is, the horizontal direction in FIG. Further, as shown in FIG. 5, the tip 154a of the supply unit 154 is configured to have a tapered shape when viewed from above. Other structures and the like of the partition 150 are the same as those of the partition 50 of the first embodiment.

  In the partition 150 of the rotary compressor 1 according to the second embodiment, the refrigerating machine oil 40 that has moved in the direction of the vane 32 due to its own weight on the inclined surface 152 of the partition 150 is provided in the supply unit 154 of the partition 150. It is possible to reliably supply the vane groove 31c through the tapered tip portion 154a. Therefore, according to this configuration, the refrigerating machine oil 40 can be efficiently supplied to the vane groove 31 c and the vane 32.

Embodiment 3 FIG.
A rotary compressor 1 according to Embodiment 3 of the present invention will be described with reference to FIGS. 6 and 7.

  FIG. 6 is an enlarged schematic view of a part of a longitudinal section of the rotary compressor 1 according to the third embodiment. FIG. 7 is an enlarged schematic view of a part of the cross section of the rotary compressor 1 according to the third embodiment. The rotary compressor 1 according to the third embodiment is a modification of the structure of the partition body 50 according to the above-described first embodiment and the partition body 150 according to the above-described second embodiment. This structure is the same as that of the rotary compressor 1 according to the first and second embodiments described above.

  As shown in FIG. 6, a concave portion 252 c that guides the refrigerating machine oil 40 in the direction of the vane 32 is provided on the inclined surface portion 252 of the partition body 250 of the rotary compressor 1 in the third embodiment. The recess 252c is a region surrounded by the bottom surface portion 252a of the slope portion 252 and the side surface portion 252b extending obliquely upward from the peripheral edge portion of the bottom surface portion 252a. Moreover, the supply part 254 of the partition 250 is comprised as the opening part 254a connected with the recessed part 252c provided in the slope part 252. FIG. The opening 254a can be configured in a shape and size that can supply the recovered lubricating oil to the opening 31d of the cylinder 31. For example, as shown in FIG. 7, the opening 254a can be configured to have the same shape and size as the opening 31d of the cylinder 31 when viewed from above. Other structures and the like of the partition 250 are the same as those of the partition 50 of the first embodiment. Note that the side surface portion 252b of the slope portion 252 may be made of the same material as the bottom surface portion 252a of the slope portion 252 or may be made of a separate material.

  In the partition 250 of the rotary compressor 1 according to the third embodiment, the refrigerating machine oil 40 guided to the concave portion 252c of the inclined surface portion 252 can flow out from the opening 254a. Therefore, according to this configuration, the refrigerating machine oil 40 can be prevented from flowing out to a place other than the opening 31d of the cylinder 31, and the refrigerating machine oil 40 can be efficiently supplied to the vane groove 31c and the vane 32. Can do.

Other embodiments.
The above-described embodiment can be variously modified without departing from the gist of the present invention. For example, in Embodiment 1 described above, the rotary compressor 1 is configured as a hermetic compressor, but may be configured as a semi-hermetic or open compressor.

  In Embodiment 1 described above, the rotary compressor 1 is configured as a one-cylinder compressor, but may be configured as a compressor having two or more cylinders 31.

  DESCRIPTION OF SYMBOLS 1 Rotary compressor, 2 Airtight container, 2a Main body part, 2b Cover part, 2c Support member, 3 units, 4 Suction muffler, 4a Case, 4b Inlet pipe, 5 Intake pipe, 5a Oil return hole, 6 Discharge pipe, 7 Charge pipe, 8 Glass terminal, 10 Motor part, 12 Stator, 14 Rotor, 16 Conductor, 20 Crankshaft, 20a Fixed surface, 22 Oil separation plate, 24 Eccentric part, 26 Rolling piston, 28 Oil hole, 28a 1st Oil supply port, 28b second oil supply port, 29 centrifugal pump, 30 compression mechanism part, 31 cylinder, 31a hollow part, 31b suction port, 31c vane groove, 31d opening part, 32 vane, 33 main bearing, 33a fixing part, 33b Bearing part, 34 Sub bearing, 34a Fixed part, 34b Bearing part, 35 Silencer, 35a Opening part, 40 Refrigerating machine oil, 50 Cut, 52 Slope, 54 Supply, 54a Opening, 150 Partition, 152 Slope, 154 Supply, 154a Tip, 250 Partition, 252 Slope, 252a Bottom, 252b Side, 252c Recess, 254 supply unit, 254a opening.

Claims (9)

A crankshaft with a rolling piston rotating eccentrically;
A cylinder that accommodates the rolling piston; a main bearing and a secondary bearing that support the crankshaft and are fixed to the cylinder; and a vane that is disposed on the cylinder and is pressed against the rolling piston. A compression mechanism that compresses a gas refrigerant in a space surrounded by the cylinder, the main bearing, the sub-bearing, the vane, and the rolling piston by a rotational driving force transmitted from a shaft;
A sealed container that houses the crankshaft and the compression mechanism;
A partition that is disposed inside the sealed container and separates refrigeration oil contained in the gas refrigerant discharged from the compression mechanism,
The partition is
It has a hollow disk shape when viewed from above,
A rotary compressor having a slope portion that moves separated refrigeration oil in the direction of the vane by its own weight, and a supply portion that supplies the refrigeration oil moved in the direction of the vane to the vane. A crankshaft with a rolling piston rotating eccentrically;
A cylinder that accommodates the rolling piston; a main bearing and a secondary bearing that support the crankshaft and are fixed to the cylinder; and a vane that is disposed in the cylinder and integrally formed with the rolling piston, A compression mechanism that compresses a gas refrigerant in a space surrounded by the cylinder, the main bearing, the sub-bearing, the vane, and the rolling piston by a rotational driving force transmitted from a crankshaft;
A sealed container that houses the crankshaft and the compression mechanism;
A partition that is disposed inside the sealed container and separates refrigerating machine oil contained in the gas refrigerant discharged from the compression mechanism section;
With
The partition is
It has a hollow disk shape when viewed from above,
A slope portion that moves the separated refrigeration oil in the direction of the vane by its own weight; and a supply portion that supplies the refrigeration oil moved in the direction of the vane to the vane.
Rotary compressor. The slope portion and the supply portion are configured as flat plates, and the inclination angle of the supply portion with respect to a direction perpendicular to the central axis of the crankshaft is equal to or greater than the inclination angle of the slope portion, and the tip portion of the supply portion is an upper surface. rotary compressor according to claim 1 or 2 has a tapered shape in view. The slope is provided with a recess for guiding the refrigeration oil in the direction of the vane,
The supply unit is provided on the inclined surface portion, the rotary compressor according to claim 1 or 2 which is an opening communicating with said recess. The supply part is provided with an opening.
The rotary compressor according to claim 1 or 2. The motor is housed in the hermetic container, includes a stator and a rotor disposed inside the stator, and includes an electric motor unit that generates a rotational driving force on the crankshaft by the rotation of the rotor,
The slope portion is configured such that refrigeration oil is separated from the gas refrigerant when the gas refrigerant swirls and collides with the rotation of the rotor.
The rotary compressor as described in any one of Claims 1-5. The partition is disposed between the compression mechanism and the electric motor.
The rotary compressor according to claim 6. It further includes a silencer that covers a part of the main bearing,
The rotary compressor according to any one of claims 1 to 7 , wherein the partition is configured to surround the silencer in a top view. The rotary compressor according to any one of claims 1 to 8 , wherein the gas refrigerant is an R1234yf refrigerant, an R1234ze (E) refrigerant, or an R290 refrigerant.

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