WO2021019750A1

WO2021019750A1 - Hermetic compressor and refrigeration cycle device

Info

Publication number: WO2021019750A1
Application number: PCT/JP2019/030101
Authority: WO
Inventors: 平野　浩二; 勝吾志田; 隼戸田; 功川辺; 平山　卓也
Original assignee: 東芝キヤリア株式会社
Priority date: 2019-07-31
Filing date: 2019-07-31
Publication date: 2021-02-04
Also published as: JP7242862B2; CN114072582A; EP3988792A4; CN114072582B; EP3988792A1; JPWO2021019750A1

Abstract

This hermetic compressor (2) is provided with a cylinder (31), a rotary shaft (32), a first bearing (33), a second bearing (34), and a hermetic container (10). The rotary shaft has: a main shaft part (32a) supported by the first bearing on one end side thereof in the axial direction thereof with an eccentric section (32c) as a boundary; and a sub shaft part (32b) supported by the second bearing on the other end side thereof. The sub shaft part has, on the outer circumferential surface (32g) thereof, an oil flow groove (54) which is for a lubrication oil (I) and spirally extends toward the one axial end side along the rotational direction (R) of the rotary shaft from the one axial end side, rather than the other axial end, that serves as a base end (54a). The second bearing has a flange part (34b) and a cylindrical part (34a) protruding from the flange part, wherein the wall thickness of a portion of the cylindrical part, which is the other axial end section and overlaps the base end of the oil flow groove when viewed in the radial direction of the rotary shaft, is smaller than those of other sections of the cylindrical part.

Description

Closed compressor and refrigeration cycle device

An embodiment of the present invention relates to a closed compressor and a refrigerating cycle device provided with the closed compressor.

A closed compressor is installed in refrigeration cycle devices such as air conditioners. The closed compressor includes a compression mechanism unit and an electric motor unit as main elements. These are housed in a closed container with the electric motor unit located above and the compression mechanism unit below. The compression mechanism portion has a rotating shaft having an eccentric portion, and is connected to the electric motor portion via the rotating shaft. The rotating shaft is supported by the upper first bearing (main bearing) and the lower second bearing (secondary bearing), respectively, and is rotated by the rotational driving force of the electric motor portion. The electric motor unit includes a rotor (rotor) attached to a rotating shaft and a stator (stator) arranged so as to surround the rotor.

The sliding parts of the main bearing and the auxiliary bearing and the rotating shaft are lubricated by using, for example, the rotational force of the rotating shaft. As an example of the lubrication structure, a structure is known in which the rotation shaft is hollow in the axial direction, and a radiation hole communicating with the hollow portion (hollow hole) and an oil groove communicating with the radiation hole are provided. The hollow hole sucks the refrigerating machine oil (lubricating oil) stored in the bottom of the closed container to the radiation hole by the rotational force of the rotating shaft. The radiation hole is provided on the rotating shaft perpendicular to the axial direction, and the lubricating oil sucked up by the hollow hole is supplied to the sliding portion between the bearing and the rotating shaft. The oil groove is provided on either the outer peripheral surface of the rotating shaft or the inner peripheral surface of the bearing, for example, and the lubricating oil is distributed over the entire sliding portion between the bearing and the rotating shaft. The lubricating oil that lubricates the sliding portion is returned to the bottom of the closed container.

Special Publication No. 61-45079 Jitsukaisho 61-94296 JP-A-2018-165502

The lubricity of the sliding part between the bearing and the rotating shaft is maintained by supplying lubricating oil to the minimum gap between the bearing and the rotating shaft to form an oil film. However, in the process of compressing the refrigerant in the compression mechanism, a compressive load acts on the rotating shaft, which causes bending and deformation of the rotating shaft. Therefore, it is not easy to properly manage this extremely small gap in which the oil film exists. Absent. In particular, in order to improve the lubricity of the part below the eccentric part of the rotating shaft and the sliding part between the part supported by the auxiliary bearing and the auxiliary bearing, a minimum gap between them should be made. More appropriate management is required.

An object of the present invention is a closed-type compressor that promotes lubrication to a sliding portion between the auxiliary bearing and the rotating shaft to improve lubricity in the sliding portion, and a refrigeration equipped with the closed-type compressor. The purpose is to provide a cycle device.

According to the embodiment, the closed compressor rotatably supports the cylinder forming the cylinder chamber, the rotating shaft having an eccentric portion arranged in the cylinder chamber, and the rotating shaft, and the shaft of the rotating shaft in the cylinder chamber. Lubricating oil that accommodates a compression mechanism including a first bearing that defines one end face in the core direction and a second bearing that defines the other end face, and lubricates the sliding portion of the compression mechanism. It is equipped with a closed container for storing. The rotating shaft has a main shaft portion supported by the first bearing on one end side in the axis direction with the eccentric portion as a boundary, and a sub-shaft portion supported by the second bearing on the other end side. The outer peripheral surface of the sub-shaft has a lubricating oil passage groove that spirally continues to one end in the axial direction along the rotation direction of the rotating shaft, with one end side of the other end in the axial direction as the base end. Have. The second bearing has a flange portion and a tubular portion protruding from the flange portion, and is the other end portion of the tubular portion in the axial direction and the base end of the oil passage groove when viewed from the radial direction of the rotating shaft. The wall thickness of the part that wraps with is thinner than the wall thickness of the other part of the cylinder part.

It is a figure which shows schematicly the refrigerating cycle apparatus (air conditioner) provided with the closed type compressor which concerns on embodiment. It is a figure which enlarges and shows the compression mechanism part of the closed type compressor which concerns on embodiment.

It is a perspective view which shows the indoor unit of an air conditioner by disassembling.
It is a vertical sectional view which shows an example of the structure of the 2nd bearing of the closed type compressor which concerns on embodiment. It is a vertical cross-sectional view which shows another example of the structure of the 2nd bearing of the closed type compressor which concerns on embodiment. It is a top view which shows the balancer cover of the closed type compressor which concerns on embodiment from below. It is a schematic diagram for demonstrating the condition for the particles of lubricating oil rising on an inclined surface in the closed type compressor which concerns on embodiment.

Hereinafter, one embodiment will be described with reference to FIGS. 1 to 6.
FIG. 1 is a diagram schematically showing an air conditioner 1 which is an example of a refrigeration cycle device according to the present embodiment. The air conditioner 1 includes a closed compressor 2, a condenser 3, an expansion device 4, an evaporator 5, and an accumulator 6 as main elements. In the air conditioner 1, the refrigerant as the working fluid circulates in the circulation circuit 7 while changing the phase between the gas phase refrigerant and the liquid phase refrigerant. The circulation circuit 7 is a circuit that reaches the suction side (suction pipe 36) from the discharge side (discharge pipe 10b) of the closed compressor 2 via the condenser 3, the expansion device 4, the evaporator 5, and the accumulator 6. .. As the refrigerant, an HFC-based refrigerant such as R410A or R32, an HFO-based refrigerant such as R1234yf or R1234ze, or a natural refrigerant such as carbon dioxide (CO ₂ ) can be appropriately used.

The condenser 3 dissipates heat from the high-temperature, high-pressure gas-phase refrigerant discharged from the closed compressor 2 and changes it into a high-pressure liquid-phase refrigerant.
The expansion device 4 decompresses the high-pressure liquid-phase refrigerant derived from the condenser 3 and changes it into a low-pressure gas-liquid two-phase refrigerant.
The evaporator 5 exchanges heat with air for a low-pressure gas-liquid two-phase refrigerant derived from the condenser 3. At that time, the gas-liquid two-phase refrigerant takes heat from the air and evaporates, and changes into a low-temperature / low-pressure gas-phase refrigerant. The air passing through the evaporator 5 is cooled by the latent heat of vaporization of the liquid phase refrigerant, becomes cold air, and is sent to a place to be air-conditioned (cooled).

The low-temperature / low-pressure vapor-phase refrigerant that has passed through the evaporator 5 is guided to the accumulator 6. When the liquid phase refrigerant that has not completely evaporated is mixed in the refrigerant, it is separated into the liquid phase refrigerant and the gas phase refrigerant here. The low-temperature, low-pressure vapor-phase refrigerant separated from the liquid-phase refrigerant is sucked into the closed compressor 2 from the accumulator 6 through the suction pipe 36, and is again converted into the high-temperature, high-pressure vapor refrigerant by the closed compressor 2. It is compressed and discharged from the discharge pipe 10b.

Next, the specific configuration of the sealed compressor 2 used in the air conditioner 1 will be described. As shown in FIG. 1, the closed compressor 2 is a so-called vertical rotary compressor, and includes a closed container 10, an electric motor portion 11, and a compression mechanism portion 12 as main elements. Note that FIG. 1 shows a state in which the closed compressor 2 is vertically traversed on two predetermined surfaces including the central axis O1 of the closed container 10, which will be described later.

The closed container 10 has a cylindrical peripheral wall 10a and stands up along the vertical direction. A discharge pipe 10b is provided at the upper end of the closed container 10. The discharge pipe 10b is connected to the condenser 3 via a circulation circuit 7. Further, an oil reservoir 10c for storing the lubricating oil I is provided in the lower part of the closed container 10.

As the lubricating oil I, for example, polyol ester oil, polyvinyl ether oil, polyalkylene glycol oil, mineral oil and the like can be applied.

The electric motor unit 11 is housed in an intermediate portion along the central axis O1 of the closed container 10 so as to be located between the compression mechanism unit 12 and the discharge pipe 10b. The electric motor unit 11 includes a so-called inner rotor type motor, and includes a rotor 21 and a stator 22.

FIG. 2 is an enlarged view showing the configuration of the compression mechanism unit 12 in FIG. 1. As shown in FIGS. 1 and 2, the compression mechanism portion 12 is housed in the lower part of the closed container 10 so as to be immersed in the lubricating oil I. The compression mechanism portion 12 has a single cylinder structure, and includes a cylinder 31, a rotating shaft 32, a first bearing 33, and a second bearing 34 as main elements. The compression mechanism unit 12 is not limited to the single type, and may be provided with two or more cylinders.

The cylinder 31 is fixed to the inner peripheral surface of the peripheral wall 10a of the closed container 10. A first bearing 33 is fixed above the cylinder 31, and a second bearing 34 is fixed below the cylinder 31. The inner diameter portion of the cylinder 31, the space surrounded by the first bearing 33 and the second bearing 34 constitutes the cylinder chamber 35. The cylinder chamber 35 is arranged coaxially with the central axis O1 of the closed container 10. The cylinder chamber 35 is connected to the accumulator 6 via a suction pipe 36 which is a part of the circulation circuit 7. The gas phase refrigerant separated from the liquid phase refrigerant by the accumulator 6 is guided to the cylinder chamber 35 through the suction pipe 36.

The cylinder 31 is provided with a vane (not shown) that divides the cylinder chamber 35 into a suction chamber and a compression chamber. A vane groove (not shown) extending outward in the radial direction is formed in the inner peripheral portion of the cylinder 31. The vane is urged inward in the radial direction by an urging means (not shown), and is supported by the cylinder 31 in a state where the tip portion is pressed against the outer peripheral surface of the roller 37 described later. As the roller 37 rotates eccentrically, the vane moves back and forth into the cylinder chamber 35. As a result, the volumes of the suction chamber and the compression chamber of the cylinder chamber 35 change, and the gas phase refrigerant sucked from the suction pipe 36 into the cylinder chamber 35 is compressed.

The axis of the rotating shaft 32 is located coaxially with the central axis O1 of the closed container 10 and penetrates the first bearing 33, the cylinder chamber 35, and the second bearing 34. In the present embodiment, the axis (central axis O1) of the rotating shaft 32 extends vertically, and one end side along the axis of the rotating shaft 32 corresponds to the upper side and the other end side corresponds to the lower side.

The rotating shaft 32 has a main shaft portion 32a, a sub shaft portion 32b, and an eccentric portion 32c interposed between them.
The spindle portion 32a extends toward one end (upper end) of the rotating shaft 32 in the axis direction (hereinafter, simply referred to as the axis direction) with the eccentric portion 32c as a boundary. The rotor 21 of the electric motor portion 11 is attached to the upper portion of the spindle portion 32a. The sub-shaft portion 32b extends toward the other end (lower end) in the axial direction with the eccentric portion 32c as a boundary. When the rotating shaft 32 rotates, the main shaft portion 32a rotates (slides) while sliding in contact with the first bearing 33, and the sub-shaft portion 32b slides with the second bearing 34. That is, the spindle portion 32a is a part of the rotating shaft 32 that slides on the first bearing 33 on one end side (upper end side) in the axial direction with respect to the eccentric portion 32c. The sub-shaft portion 32b is a part of the rotating shaft 32 that slides on the second bearing 34 on the other end side (lower end side) in the axis direction with respect to the eccentric portion 32c.

The eccentric portion 32c is eccentric with respect to the axis (central axis O1) of the rotating shaft 32 (main shaft portion 32a and sub-shaft portion 32b) and is arranged in the cylinder chamber 35. A roller 37 is fitted on the outer peripheral surface of the eccentric portion 32c. A slight gap is provided between the inner peripheral surface of the roller 37 and the outer peripheral surface of the eccentric portion 32c to allow the roller 37 to rotate with respect to the eccentric portion 32c. As a result, when the rotating shaft 32 rotates, the roller 37 rotates eccentrically with respect to the axis of the rotating shaft 32 in the cylinder chamber 35, and a part of the outer peripheral surface thereof passes through an oil film on the inner peripheral surface of the cylinder chamber 35. Contact.

The rotating shaft 32 is provided with a balancer 38 at the other end in the axial direction. In the present embodiment, the sub-shaft portion 32b projects below the second bearing 34, and the balancer 38 is arranged at the projecting portion 32d. The shape of the balancer 38 is not particularly limited, but is, for example, a disk shape or a semicircular plate shape. The balancer 38 is formed with a through hole 38a in the axial direction. The protruding portion 32d of the auxiliary shaft portion 32b is fixed to the through hole 38a by press fitting or screwing. The center of the balancer 38 is eccentric with respect to the axis (central axis O1) of the rotating shaft 32 in a direction opposite to the eccentric direction of the eccentric portion 32c. That is, the balancer 38 and the eccentric portion 32c are arranged with a phase difference of 180 ° in the circumferential direction of the rotating shaft 32. The arrangement angle of the balancer 38 differs depending on the number of eccentric portions.

In the present embodiment, the auxiliary shaft portion 32b has a shorter length in the axial core direction than the main shaft portion 32a. Therefore, by providing the balancer 38 on the sub-shaft portion 32b, for example, as compared with the case where the balancer is provided on the upper surface of the rotor 21 of the electric motor unit 11, a second support for the sub-shaft portion 32b, which is an arrangement portion of the balancer 38, is provided. The distance between the bearing 34 and the balancer 38 can be shortened. As a result, the rotational balance of the rotating shaft 32 having the eccentric portion 32c is stabilized, and the bending of the rotor 21 is suppressed.

The balancer 38 is covered with the balancer cover 39. The balancer cover 39 is fixed to the second bearing 34 with bolts 40 (see FIG. 5) and covers the balancer 38 from below. The balancer cover 39 includes a bottom portion 39a, a wall portion 39b that rises from the bottom portion 39a, and a flange portion 39c that is continuous with the wall portion 39b.

The bottom portion 39a is in contact with the other end surface of the rotating shaft 32, that is, the lower end surface 32e of the sub shaft portion 32b. The contact portion is a thrust support portion 39d that receives a load acting on the rotating shaft 32 in the axial direction and slidably supports the lower end surface 32e. The thrust support portion 39d is provided so as to raise the bottom portion 39a upward. The upper surface (contact surface with the lower end surface 32e) of the thrust support portion 39d has a flat shape orthogonal to the axis direction. An oil supply hole 39e penetrating in the vertical direction is formed in the central portion of the thrust support portion 39d, and the lower end thereof faces the lubricating oil I stored in the oil reservoir portion 10c of the closed container 10. The wall portion 39b is a portion that covers the outer periphery of the balancer 38. The flange portion 39c is a portion fixed to the second bearing 34 by a bolt 40, and has a claw 39f that supports the second flange portion 34b, which will be described later, from the circumferential direction.

The first bearing 33 and the second bearing 34 rotatably support the rotating shaft 32. The first bearing 33 defines the upper surface 35a of the cylinder chamber 35, and the second bearing 34 defines the lower surface 35b of the cylinder chamber 35. The upper surface 35a is an end surface on one end side of the rotating shaft 32 in the axial direction, and the lower surface 35b is an end surface on the other end side of the rotating shaft 32 in the axial direction. That is, the first bearing 33 corresponds to a member that closes the cylinder chamber 35 from above, and the second bearing 34 corresponds to a member that closes the cylinder chamber 35 from below.

The first bearing 33 includes a first flange portion 33b and a first tubular portion 33a protruding from the first flange portion 33b.
The first flange portion 33b is located at the lower end of the first tubular portion 33a and extends outward in the radial direction. The first flange portion 33b has a portion on the inner circumference that is rotatably supported by inserting the spindle portion 32a. The first flange portion 33b is formed with a first discharge hole 33d for discharging the refrigerant from the compression chamber of the cylinder chamber 35. The first discharge hole 33d penetrates a part of the first flange portion 33b up and down and communicates with the compression chamber of the cylinder chamber 35. The first discharge hole 33d is opened and closed by the first discharge valve mechanism 33e. The first discharge valve mechanism 33e opens the first discharge hole 33d as the pressure in the compression chamber rises, and discharges high-temperature and high-pressure vapor-phase refrigerant from the cylinder chamber 35.

Above the first bearing 33, a muffler 41 covering the first bearing 33 is provided. The muffler 41 has a communication hole 41a that communicates inside and outside (upper and lower) of the muffler 41. The high-temperature, high-pressure vapor-phase refrigerant discharged through the first discharge hole 33d is discharged into the closed container 10 through the communication hole 41a.

The first tubular portion 33a is a portion that protrudes from the upper end of the first flange portion 33b and rotatably supports the first bearing 33 through the rotating shaft 32, specifically, the main shaft portion 32a. In the state where the spindle portion 32a is inserted into the first cylinder portion 33a, the outer peripheral surface 32f slides with respect to the inner peripheral surface 33c of the first cylinder portion 33a.

The second bearing 34 includes a second flange portion 34b and a second tubular portion 34a protruding from the second flange portion 34b.
The second flange portion 34b is located at the upper end of the second tubular portion 34a and extends outward in the radial direction. The second flange portion 34b has a portion on the inner circumference that is rotatably supported by inserting the auxiliary shaft portion 32b. The second flange portion 34b is formed with a second discharge hole (hereinafter, referred to as a discharge port) 34d for discharging the refrigerant from the compression chamber of the cylinder chamber 35. The discharge port 34d penetrates a part of the second flange portion 34b up and down and communicates with the compression chamber of the cylinder chamber 35. The discharge port 34d is opened and closed by the second discharge valve mechanism 34e. The second discharge valve mechanism 34e opens the discharge port 34d as the pressure in the compression chamber rises, and discharges high-temperature and high-pressure vapor-phase refrigerant from the cylinder chamber 35. The high-temperature, high-pressure vapor-phase refrigerant discharged through the discharge port 34d is discharged into the cover space 42 of the balancer cover 39. The cover space 42 is a space in which the balancer cover 39 covers the balancer 38 from below, and is a space surrounded by a bottom portion 39a and a wall portion 39b.

The second tubular portion 34a is a portion that protrudes from the lower end of the second flange portion 34b and rotatably supports the second bearing 34 through the rotating shaft 32, specifically, the sub-shaft portion 32b. In the state where the auxiliary shaft portion 32b is inserted into the second tubular portion 34a, the outer peripheral surface 32g slides with respect to the inner peripheral surface 34c of the second tubular portion 34a.

The first bearing 33, the cylinder 31, and the second bearing 34 have a communication passage 43 that communicates the space above the lubricating oil storage surface Is in the closed container 10 with the cover space 42. The communication passage 43 penetrates the first flange portion 33b, the cylinder 31, and the second flange portion 34b up and down. The communication passage 43 is configured, for example, as a pipe body penetrating the first flange portion 33b, the cylinder 31, and the second flange portion 34b, or by communicating through holes formed in each of these portions. The opening 43a on the one end (upper end) side of the communication passage 43 faces the inside of the muffler 41, and the opening 43b on the other end (lower end) side faces the cover space 42.

The number of passages 43 is not particularly limited. In this embodiment, as an example, two communication passages 431 and 432 are provided (see FIG. 5). Details of these communication passages 431 and 432 will be described later.

In the compression mechanism portion 12 having the above-described configuration, each sliding portion between the elements is lubricated by the lubricating oil I. Next, the lubrication structure of the compression mechanism portion 12 in the present embodiment, specifically, the lubrication structure for the sliding portion (hereinafter, referred to as the bearing lubrication portion) between the rotating shaft 32 and the first bearing 33 and the second bearing 34. Will be described.

The rotating shaft 32 has an oil supply passage 51 for supplying lubricating oil I to the bearing lubricating portion from the oil sump portion 10c of the closed container 10. The refueling passage 51 includes a main refueling passage 52 and sub refueling passages 53a and 53b.

The main oil supply passage 52 is configured such that a part of the rotating shaft 32 is hollow in the axial direction.
The lower end of the main oil supply passage 52 is opened by the lower end surface 32e of the rotating shaft 32 (sub shaft portion 32b). The opening 52a communicates with the oil supply hole 39e of the balancer cover 39. That is, the lower end of the main oil supply passage 52 communicates with the inside of the closed container 10, specifically, the oil sump portion 10c through the opening 52a and the oil supply hole 39e. As a result, the rotating shaft 32 rotates, so that the lubricating oil I is sucked up from the oil sump portion 10c into the main oil supply passage 52.

The upper end portion 52b of the main oil supply passage 52 ends in the middle portion in the axial direction of the rotating shaft 32, specifically, near the lower end portion of the main shaft portion 32a. The position of the upper end portion 52b (height from the lower end portion in the axial direction) may reach at least the position of the cylinder 31. For example, the main oil supply passage 52 may be opened at the upper end surface of the rotating shaft 32 (main shaft portion 32a). Further, the inner peripheral surface of the main oil supply passage 52 may be provided with a spiral guide or the like that promotes the rise of the lubricating oil I as the rotating shaft 32 rotates.

The sub refueling passages 53a and 53b branch from the main refueling passage 52 and extend in a direction (diameter direction) orthogonal to the axis direction, and are open to the outer

peripheral surfaces

32f and 32g of the rotating shaft 32. That is, the auxiliary refueling passages 53a and 53b are radial passages extending from the main refueling passage 52.

Of the two auxiliary oil supply passages 53a and 53b branching from the main oil supply passage 52, one is the first auxiliary oil supply passage 53a formed in the main shaft portion 32a, and the other is the second auxiliary oil supply passage 53a formed in the sub shaft portion 32b. It is a sub-fueling passage 53b.

The first auxiliary oil supply passage 53a is formed at a connecting portion with the eccentric portion 32c in the spindle portion 32a. The first auxiliary oil supply passage 53a opens on the outer peripheral surface 32f of the spindle portion 32a, and the opening 53c faces the inner peripheral surface 33c of the first flange portion 33b of the first bearing 33.

The second auxiliary oil supply passage 53b is formed above the lower end (position of the lower end surface 32e) of the auxiliary shaft portion 32b when viewed from the radial direction of the rotating shaft 32. The second auxiliary oil supply passage 53b opens on the outer peripheral surface 32g of the auxiliary shaft portion 32b, and the opening 53d faces the inner peripheral surface 34c of the second tubular portion 34a of the second bearing 34.

In addition to these main oil supply passages 52 and auxiliary oil supply passages 53a and 53b, the auxiliary shaft portion 32b has an oil passage groove 54 for distributing the lubricating oil I to the sliding portion with the second bearing 34. The oil passage groove 54 is formed on the outer peripheral surface 32g of the auxiliary shaft portion 32b. The oil passage groove 54 is in the axial core direction along the rotation direction (direction indicated by the arrow R shown in FIG. 2) of the auxiliary shaft portion 32b (in short, the rotation shaft 32) starting from the second auxiliary oil supply passage 53b. It is a groove that spirally continues to one end (upper end) side. The spiral is continuous so as to rise the outer peripheral surface 32g in the rotation direction of the sub-shaft portion 32b. The continuous length of the oil passage groove 54 is arbitrary, and the auxiliary shaft portion 32b may not be wound or may be wound more than once. FIG. 2 shows, as an example, an oil passage groove 54 in which the auxiliary shaft portion 32b is not wound. The oil passage groove 54 faces the inner peripheral surface 34c of the second flange portion 34b from the second cylinder portion 34a of the second bearing 34 over the entire length.

The base end 54a of the oil passage groove 54 communicates with the opening 53d on the outer peripheral surface 32g of the second auxiliary oil supply passage 53b. That is, the second auxiliary oil supply passage 53b opens at the bottom of the oil passage groove 54, and the opening 53d serves as the base end 54a of the oil passage groove 54. Therefore, the base end 54a is located above the lower end (position of the lower end surface 32e) of the sub-shaft portion 32b when viewed from the radial direction of the rotating shaft 32. The position of the base end 54a is defined as the central position of the opening 53d. The tip of the oil passage groove 54 reaches the upper end portion of the sub-shaft portion 32b, in other words, the connection portion with the eccentric portion 32c.

When the rotating shaft 32 rotates, the lubricating oil I sucked up to the main oil supply passage 52 through the oil supply hole 39e passes through the first auxiliary oil supply passage 53a and passes through the opening 53c to the second cylinder portion of the second bearing 34. It is discharged toward the inner peripheral surface 34c of 34a. Then, the lubricating oil I is a sliding portion (inner circumference) between the first cylinder portion 33a and the first flange portion 33b of the first bearing 33 and the spindle portion 32a as the rotating shaft 32 (spindle portion 32a) rotates. It spreads over the surface 33c and the outer peripheral surface 32f) S1 and lubricates the sliding portion S1.

Further, the lubricating oil I sucked up by the main oil supply passage 52 is guided from the second auxiliary oil supply passage 53b to the oil passage groove 54 through the opening 53d. The lubricating oil I guided to the oil passing groove 54 rises from the base end 54a to the tip along the oil passing groove 54. During that time, the lubricating oil I is charged with the sliding portion between the second cylinder portion 34a and the second flange portion 34b of the second bearing 34 and the sub-shaft portion 32b as the rotating shaft 32 (sub-shaft portion 32b) rotates. The inner peripheral surface 34c and the outer peripheral surface 32g) spread over S2 and lubricate the sliding portion S2.

In the present embodiment, the first bearing 33 has a first support end portion 61 at one end (upper end) in the axial direction, and the second bearing 34 has a first support end 61 at the other end (lower end) in the axial direction. It has a second support end 62. The wall thickness of the second support end 62 of the second bearing 34 (T1 shown in FIG. 2) is thinner than the wall thickness of the first support end 61 of the first bearing 33. The wall thickness T1 of the second support end portion 62 is the wall thickness at the thinnest position of the second support end portion 62.

The first support end portion 61 is one end portion in the axial core direction of the support portion of the spindle portion 32a in the first bearing 33. In other words, it is a part of the portion where the spindle portion 32a slides in the first cylinder portion 33a, and is the upper end portion in the axial direction. In the present embodiment, as an example, the first support end portion 61 corresponds to a thin-walled portion formed so that the first tubular portion 33a tapers toward the upper end portion.

In this way, by making the first support end portion 61 thinner than the other portion of the first cylinder portion 33a on which the spindle portion 32a slides, the support of the first cylinder portion 33a with respect to the sliding spindle portion 32a The pressure does not become excessive and is maintained appropriately.

The second support end portion 62 is the other end portion in the axial direction of the support portion of the sub-shaft portion 32b in the second bearing 34. In other words, it is a part of the portion where the sub-shaft portion 32b slides in the second cylinder portion 34a, and is the lower end portion in the axial direction. Hereinafter, a specific configuration of the second support end portion 62 will be described.

3 and 4 are vertical cross-sectional views showing a configuration example of the second bearing 34. It should be noted that FIGS. 3 and 4 show a state in which the second bearing 34 is vertically traversed on two predetermined surfaces including the central axis O1 of the closed container 10.

In the configuration example shown in FIG. 3, the second support end portion 62 is configured as an inner wall portion 63a of the groove 63 provided on the lower end surface 34f of the second cylinder portion 34a. The groove 63 is continuously provided on the lower end surface 34f in the circumferential direction, and is composed of an inner wall portion 63a, an outer wall portion 63b, and a bottom portion 63c. The inner wall portion 63a is a portion that defines the inner groove wall (inner peripheral surface) in the radial direction, and the outer wall portion 63b is a portion that defines the outer groove wall (outer peripheral surface) in the radial direction. The bottom portion 63c is a portion that defines a groove bottom (bottom surface) sandwiched between the inner wall portion 63a and the outer wall portion 63b. As a result, the lower end of the second tubular portion 34a is divided into an inner wall portion 63a and an outer wall portion 63b by the groove 63. The inner wall portion 63a is a portion on which the sub-shaft portion 32b slides at the lower end portion of the second cylinder portion 34a. The inner wall portion 63a is thinner than the wall thickness of the other portion of the support portion of the sub-shaft portion 32b in the second tubular portion 34a of the second bearing 34.

Further, a groove 64 is provided on the upper end surface 34g of the second flange portion 34b so as to substantially face the groove 63 in the axial direction. The groove 64 is continuously provided on the upper end surface 34g in the circumferential direction, and is composed of an inner wall portion 64a, an outer wall portion 64b, and a bottom portion 64c that define each portion in the same manner as the groove 63. As a result, the upper end portion of the second flange portion 34b is divided into an inner wall portion 64a and an outer wall portion 64b by the groove 64. The inner wall portion 64a is a portion on which the sub-shaft portion 32b slides at the upper end portion of the second flange portion 34b. The outer wall portion 64b is continuous with a portion of the second flange portion 34b that extends in the radial direction of the rotating shaft 32.

In the configuration example shown in FIG. 4, the second support end portion 62 is configured as a thin-walled portion 65 formed so that the second cylinder portion 34a tapers toward the lower end portion. The thin-walled portion 65 is continuously formed in the circumferential direction at the lower end portion of the second tubular portion 34a. As a result, unlike the inner wall portion 63a shown in FIG. 3, the thin-walled portion 65 is a portion in which the second tubular portion 34a is thinned over the entire circumference of the lower end portion itself. The thin-walled portion 65 is a portion on which the auxiliary shaft portion 32b slides at the lower end portion of the second cylinder portion 34a. The thin wall portion 65 is thinner than the wall thickness of the other portion of the support portion of the sub-shaft portion 32b in the second tubular portion 34a of the second bearing 34.

Further, the upper end surface 34g of the second tubular portion 34a is provided with a groove 64 composed of an inner wall portion 64a, an outer wall portion 64b, and a bottom portion 64c, as in the configuration example shown in FIG. In this case, the groove 64 is provided so that the inner wall portion 64a is arranged so as to substantially overlap the thin-walled portion 65 when viewed from the axial direction.

In this way, in addition to the groove 64, the inner wall portion 63a (groove 63 in another way) and the thin wall portion as the second support end portion 62 having a wall thickness thinner than the other wall thickness of the second cylinder portion 34a. Since the second bearing 34 has the portion 65, the flexibility of the second tubular portion 34a can be increased and the structure can be easily elastically deformed. As a result, when an outward load in the radial direction is applied to the second tubular portion 34a from the auxiliary shaft portion 32b, the second support end portion 62 can be slightly deformed in addition to the inner wall portion 64a. As a result, the gap between the sliding portion (inner peripheral surface 34c and outer peripheral surface 32g) S2 between the second tubular portion 34a and the sub-shaft portion 32b can be expanded.

Therefore, even when the base end 54a of the oil passage groove 54 is located above the lower end (position of the lower end surface 32e) of the sub-shaft portion 32b when viewed from the radial direction of the rotating shaft 32, it slides. Lubricating oil I can be distributed to every corner of the portion S2 to improve the lubricating performance. At that time, since the base end 54a is located above the lower end of the auxiliary shaft portion 32b, it is possible to prevent the lubricating oil I from falling into the oil sump portion 10c without contributing to the lubrication of the sliding portion S2. it can. By improving the lubrication performance by these, it becomes possible to improve the reliability of the sealed compressor 2.

Further, the second support end portion 62 is arranged so that the base end 54a of the oil passage groove 54 wraps with the second support end portion 62 when viewed from the radial direction of the rotation shaft 32, specifically, the sub shaft portion 32b. ing.

For example, when the second support end portion 62 is the inner wall portion 63a, the central position of the base end 54a, specifically, the opening 53d in the axial direction is the axis of the inner wall portion 63a when viewed from the radial direction of the sub-shaft portion 32b. Wrap with the position in the core direction. From another point of view, the center position of the opening 53d is located above the tip of the inner wall portion 63a and below the bottom portion 63c corresponding to the base end portion when viewed from the radial direction of the sub-shaft portion 32b. Just do it.
When the second support end portion 62 is the thin-walled portion 65, the center position of the opening 53d wraps with the position in the axial center direction of the thin-walled portion 65 when viewed from the radial direction of the sub-shaft portion 32b. Another way of thinking is that the center position of the opening 53d may be above the tip of the thin wall portion 65 and below the base end portion 65a when viewed from the radial direction of the sub-shaft portion 32b.

By arranging the second support end portion 62 (inner wall portion 63a or thin-walled portion 65) in this way, the lubricating oil I discharged from the opening 53d is a sliding portion between the second cylinder portion 34a and the auxiliary shaft portion 32b. (Inner peripheral surface 34c and outer peripheral surface 32g) With respect to S2, the lubricating oil I can be supplied to the upper side of the sliding portion S2 through the oil passage groove 54, and the lubricating oil I can be supplied downward from the base end 54a. Can be refueled. At that time, since the inner wall portion 64a and the second support end portion 62 can be slightly deformed to expand the gap of the sliding portion S2, the lubricating oil I can be applied to both above and below the sliding portion S2. It becomes possible to spread evenly. Further, since the base end 54a of the oil passage groove 54 and the second support end portion 62 are arranged so as to wrap when viewed from the radial direction of the sub-shaft portion 32b, the inner wall portion 64a and the second support end portion 62 The minute deformation makes it easier to supply the lubricating oil I below the sliding portion S2. Further, since the base end 54a of the oil passage groove 54 does not reach the lower end of the sub-shaft portion 32b and the inner wall portion 64a and the second support end portion 62 are slightly deformed, the sub-shaft portion 32b is viewed from the lower end. Excessive outflow of lubricating oil I can be prevented.

Since the sub-shaft portion 32b is shorter in the axial core direction than the main shaft portion 32a, the second tubular portion 34a of the second bearing 34 that rotatably supports the sub-shaft portion 32b has a second cylinder portion 34a that rotatably supports the main shaft portion 32a. It is shorter than the first tubular portion 33a of the bearing 33 of 1. Therefore, from the viewpoint of the length in the axial direction, the second tubular portion 34a is less likely to bend than the first tubular portion 33a. However, in the present embodiment, since the second support end portion 62, which is thinner than the first support end portion 61 of the first bearing 33, is provided in the second bearing 34, the second cylinder portion 34a is the first cylinder. It can be bent in the same manner as the portion 33a. Therefore, it is possible to secure a gap of the sliding portion S2 equal to the gap of the sliding portion S1 and lubricate them evenly.

At that time, the lubricating oil I that lubricates the sliding portion S2 is supplied to the gap created by the minute deformation of the second cylinder portion 34a (inner wall portion 64a and the second support end portion 62), so that the sliding portion S2 The amount of oil required for sliding reliability can be kept small. Therefore, it is not necessary to supply a short amount of oil to the sliding portion S1 and other sliding portions. That is, it is possible to prevent a decrease in the lubrication performance of the sliding portion S1 and other sliding portions, and to improve the lubrication performance of the sliding portion S2.

As described above, according to the present embodiment, the lubrication performance of the bearing lubrication portion of the compression mechanism portion 12, particularly the sliding portion S2 between the second bearing 34 (second cylinder portion 34a) and the sub-shaft portion 32b is enhanced. Can be done. On the other hand, the lubricating oil I sucked up from the oil supply hole 39e into the main oil supply passage 52 enters the cover space 42 from the sliding gap between the thrust support portion 39d of the balancer cover 39 and the lower end surface 32e of the auxiliary shaft portion 32b. May infiltrate. In this case, for example, when the balancer 38 stirs the infiltrated lubricating oil I, an extra resistance may occur in the rotation of the rotating shaft 32 depending on the magnitude of the resistance.

Therefore, the present embodiment is provided with a discharge structure for efficiently discharging the infiltrated lubricating oil I from the cover space 42. As a result, for example, deterioration of the rotational performance of the rotating shaft 32 due to the stirring resistance of the lubricating oil of the balancer 38 can be suppressed. The discharge structure will be described below.

As shown in FIG. 2, the balancer cover 39 has an inclined portion 71 that inclines from the other end (lower end) side of the rotating shaft 32 toward the communication passage 43. The inclined portion 71 is a portion in which at least a part of the wall portion 39b is inclined in the radial direction of the rotating shaft 32 with respect to the bottom portion 39a. For example, the inclined portion 71 may be provided over the entire circumference of the wall portion 39b, or may be provided at a part in the circumferential direction.

FIG. 5 is a plan view showing the configuration of the balancer cover 39 from below. As shown in FIG. 5, the balancer cover 39 has a plurality of branch portions 72 and a fixed portion 73.
The branch chamber portion 72 divides the cover space 42 so as to avoid the fixing portion 73 by the bolt 40. The fixing portion 73 is a fixing portion to the second bearing 34 via a bolt 40. In the configuration example shown in FIG. 5, the balancer cover 39 is fixed to the second bearing 34 with five bolts 40, and has five fixing portions 73a to 73f corresponding to the second bearing 34. Therefore, the balancer cover 39 has five branch chambers 72a to 72e, avoiding these five fixed portions 73a to 73f. The divided chamber portions 72 and the fixed portions 73 are arranged alternately in the circumferential direction at substantially equal intervals (in the same phase). Therefore, in a plan view as shown in FIG. 5, the balancer cover 39 has a shape of a substantially star shape with five vertices. The number of branch chambers 72, the number of bolts 40, and the number of fixing portions 73 are not limited to five, and may be two or more, four or less, or six or more.

The plurality of (five as an example) branch rooms 72 communicate with each other in the cover space 42. In the configuration example shown in FIG. 5, the cover space 42 forms one space as a whole in a state of being divided into five by five branch chambers 72a to 72e.

Of the five branch chambers 72a to 72e, the first branch chamber 72a communicates with the discharge port 34d of the second bearing 34. That is, the first branch chamber portion 72a can communicate with the compression chamber of the cylinder chamber 35 via the discharge port 34d. Therefore, when the discharge port 34d is opened by the second discharge valve mechanism 34e, the high-temperature, high-pressure vapor-phase refrigerant is discharged from the compression chamber of the cylinder chamber 35 to the first branch chamber portion 72a. The discharged high-temperature, high-pressure vapor-phase refrigerant flows from the first branch chamber 72a into the other compartments 72b to 72e that communicate with each other.

Further, at least one of the five branch chambers 72a to 72e communicates with the communication passage 43. As described above, in the present embodiment, as an example, two communication passages 431 and 432 are provided. As shown in FIG. 5, these communication passages 431 and 432 are arranged with a predetermined phase difference (center angle difference) in the circumferential direction. Specifically, the communication passages 431 and 432 are first fixed portions (first) located from the discharge port 34d in the rotation direction of the rotation shaft 32 (direction indicated by the arrow R shown in FIG. 5) when viewed from the axis direction. The fixed portion) communicates with the branch portions 72b and 72c at a position of a central angle larger than the central angle (α1) up to 73a.

That is, these communication passages 431 and 432 have a predetermined phase difference (center angle difference) in the circumferential direction, that is, two adjacent two of the five branch portions 72 (branch portions 72b, 72c) arranged at substantially equal intervals. ) Are arranged according to the arrangement interval (with a phase difference of about 72 °). As a result, the second branch chamber 72b communicates with the communication passage 431, and the third branch chamber 72c communicates with the communication passage 432. Therefore, the second branch chamber 72b communicates with the space above the lubricating oil storage surface Is in the closed container 10 via the communication passage 431 and the third branch 72c communicates with the space above the lubricating oil storage surface Is in the closed container 10 via the communication passage 432.

In this case, in the rotation direction of the rotating shaft 32, the center angle (α2) from the discharge port 34d to the communication passage 431 is larger than the center angle (α1) of the first fixing portion 73a to the bolt 40. Further, the central angle (α3) from the discharge port 34d to the communication passage 432 is further larger than the center angle (α2) to the communication passage 431 (α1 <α2 <α3). The specified positions of the center angle are the position of the axis (center axis O1) of the rotating shaft 32, the rotation center Cb of the bolt 40, the opening center C1 of the opening 34h of the discharge port 34d, and the opening 43b of the communication passages 431 and 432. The center of opening C2 and C3.

An inclined portion 71 is provided in each of the second branch portion 72b and the third branch portion 72c. The inclined portion 71 of the second branch portion 72b has an inclined surface 74b that approaches the communication passage 431 as it goes outward in the radial direction of the rotating shaft 32 (sub-shaft portion 32b). Further, the inclined portion 71 of the third branch chamber portion 72c has an inclined surface 74c that approaches the communication passage 432 as it goes outward in the radial direction of the rotating shaft 32 (sub-shaft portion 32b).

In the present embodiment, the roller 37 rotates eccentrically in the cylinder chamber 35 due to the rotation of the rotating shaft 32. As a result, the high-temperature, high-pressure vapor-phase refrigerant compressed in the compression chamber of the cylinder chamber 35 is discharged from the discharge port 34d into the cover space 42 of the balancer cover 39. Further, as described above, the lubricating oil I sucked up from the oil supply hole 39e into the main oil supply passage 52 is covered from the sliding gap between the thrust support portion 39d of the balancer cover 39 and the lower end surface 32e of the auxiliary shaft portion 32b. It may invade 42.

In this case, the lubricating oil I is subjected to a pulling force into the cover space 42 due to the flow velocity of the high-temperature, high-pressure vapor-phase refrigerant (hereinafter referred to as discharge gas) discharged from the discharge port 34d. Further, the centrifugal force from the balancer 38 acts on the lubricating oil I that has entered the cover space 42, and the drawing force due to the discharged gas continues to act on the lubricating oil I.

Therefore, as shown by the arrow A2 in FIG. 2, the lubricating oil I rises along the

inclined surfaces

74b and 74c and is guided from the opening 43b to the communication passage 43 (431,432). The lubricating oil I guided to the communication passage 43 (431, 432) is discharged into the muffler 41 from the opening 43a, and is discharged into the space above the lubricating oil storage surface Is in the closed container 10.

At that time, the lubricating oil I is mist-ized and rises on the

inclined surfaces

74b and 74c. FIG. 6 shows the conditions for the particles P of the lubricating oil I misted on the inclined surface SS whose inclination angle with respect to the horizontal plane GS is θ to rise. As shown in FIG. 6, in order for the mist-formed lubricating oil I particles P to rise on the inclined surface SS by centrifugal force, it is necessary to satisfy the following relational expression (1).
Fcosθ> μ × Fsinθ That is, tanθ <1 / μ ... (1)
F is the centrifugal force acting on the particles P of the mist-ized lubricating oil I, θ is the inclination angle of the inclined surface SS with respect to the horizontal plane GS, and the value of the inclination angle θ1 of the

inclined surfaces

74b and 74c shown in FIG. 2 is used. This is the specified angle. μ is the coefficient of friction between the particles P of the mist-ized lubricating oil I and the inclined surface SS.

The value of the coefficient of friction (μ) differs depending on various conditions for the lubricating oil I and the inclined surface SS. In the present embodiment, assuming a general value of about 0.25 to 0.3, if the inclination angle (θ) is 70 ° or less, the particles P of the lubricating oil I rise the inclined surface SS by centrifugal force. It will be possible. Therefore, in the present embodiment, the inclination angles of the

inclined surfaces

74b and 74c (angle θ1 shown in FIG. 2) are set to 70 ° or less with respect to the horizontal plane as an example.

According to such a discharge structure of the lubricating oil I, even when the lubricating oil I has infiltrated into the cover space 42, the lubricating oil I is brought into the inclined surface 74b by the centrifugal force of the balancer 38 and the drawing force of the discharged gas. It can lead to 74c. Since the inclination angle (θ1) of the

inclined surfaces

74b and 74c is set to a predetermined angle, the lubricating oil I can be raised along the

inclined surfaces

74b and 74c. As a result, the lubricating oil I can be discharged from the cover space 42 from the

inclined surfaces

74b and 74c through the communication passages 431 and 432. As a result, the atmosphere around the balancer 38 can be maintained by the discharged gas. Therefore, for example, the stirring resistance of the lubricating oil of the balancer 38 can be reduced, and the deterioration of the rotational performance of the rotating shaft 32 can be suppressed.

As an example, the

inclined surfaces

74b and 74c are set to 70 ° or less with respect to the horizontal plane. Therefore, when the friction coefficient (μ) between the oil droplets (mist) of the lubricating oil I scattered in the cover space 42 and the

inclined surfaces

74b and 74c is relatively high, it is about 0.25 to 0.3 as an example. Even if there is, the lubricating oil I can be discharged from the cover space 42 along the

inclined surfaces

74b and 74c.

Further, the

inclined surfaces

74b and 74c are provided in the branch chamber portions 72 (72b and 72c) arranged so as to avoid the fixing portion 73 of the bolt 40. Therefore, not only can the balancer cover 39 be firmly fixed to the second bearing 34 by the bolt 40, but also the lubricating oil I can be efficiently discharged from the cover space 42.

That is, in the present embodiment, the communication passages 431 and 432 are arranged so as to communicate with the branch chamber portions 72b and 72c avoiding the fixing portion 73 of the bolt 40. Therefore, the communication passages 431 and 432 can be arranged and opened closer to the outer periphery of the branch chambers 72b and 72c, that is, to the

inclined surfaces

74b and 74c. In addition to the centrifugal force from the balancer 38, a propulsive force acts on the mistized particles of the lubricating oil I and the discharge gas from the discharge port 34d in the tangential direction of the rotation of the rotating shaft 32 (sub-shaft portion 32b). .. Therefore, by arranging the communication passages 431 and 432 closer to the

inclined surfaces

74b and 74c, a larger centrifugal force and propulsive force can be applied to the lubricating oil I and the discharged gas. Therefore, by placing the lubricating oil I on the discharged gas, it can be discharged from the cover space 42 more efficiently.

Further, the central angle (α2, α3) from the discharge port 34d to the communication passages 431, 432 is larger than the central angle (α1) of the first fixing portion 73a to the bolt 40. Therefore, centrifugal force and propulsive force are applied to the particles and the discharged gas of the lubricating oil I, respectively, so that the lubricating oil I can be reliably guided to the communication passages 431 and 432. At the same time, the fixing portions 73 can be arranged at predetermined intervals to secure a stable fixing position of the balancer cover 39 by the bolts 40.

As described above, according to the present embodiment, in addition to enhancing the lubrication performance for the bearing lubricating portion, the lubricating oil I can be efficiently discharged from the cover space 42, thereby further improving the reliability of the sealed compressor 2. It becomes possible to plan.

Although the embodiments of the present invention have been described above, such embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

For example, in the above-described embodiment, the closed compressor 2 is a single rotary compressor model having one cylinder 31, but may be a multi-cylinder rotary compressor model having two or more cylinders. In this case, each cylinder may have the same or different cylinder chamber volumes. Further, the sealed compressor may be a swing type in which a vane and a roller are integrated.

1 ... Refrigeration cycle device (air conditioner), 2 ... Sealed compressor, 3 ... Condenser, 4 ... Expander, 5 ... Evaporator, 6 ... Accumulator, 7 ... Circulation circuit, 10 ... Sealed container, 10c ... Oil Reservoir, 11 ... Electric motor, 12 ... Compression mechanism, 31 ... Cylinder, 32 ... Rotating shaft, 32a ... Main shaft, 32b ... Sub-shaft, 32c ... Eccentric, 32e ... Lower end surface, 32f, 32g ... Outer surface , 33 ... 1st bearing, 33a ... 1st cylinder part, 33b ... 1st flange part, 34 ... 2nd bearing, 34a ... 2nd cylinder part, 34b ... 2nd flange part, 34d ... 2nd discharge hole ( Discharge port), 34h ... opening, 35 ... cylinder chamber, 35a ... top surface, 35b ... bottom surface, 38 ... balancer, 39 ... balancer cover, 39a ... bottom, 39b ... wall part, 39c ... flange part, 39e ... lubrication hole, 40 ... bolt, 42 ... cover space, 43 (431,432) ... communication passage, 43a, 43b ... opening, 51 ... refueling passage, 52 ... main refueling passage, 53a ... first sub refueling passage, 53b ... second Sub-lubricating passages, 53c, 53d ... opening, 54 ... oil flow groove, 54a ... base end, 61 ... first support end, 62 ... second support end, 63, 64 ... groove, 63a, 64a ... inner wall Parts, 63b, 64b ... Outer wall part, 63c, 64c ... Bottom, 65 ... Thin-walled part, 71 ... Inclined part, 72 (72a-72f) ... Branch chamber part, 73 (73a-73f) ... Fixed part, 74b, 74c ... Inclined Surface, C1, C2, C3 ... Opening center, Cb ... Bolt rotation center, I ... Lubricating oil, Is ... Lubricating oil storage surface, O1 ... Central axis of closed container, S1, S2 ... Sliding part, T1 ... Second support The wall thickness of the end.

Claims

The cylinder that forms the cylinder chamber and
A rotating shaft having an eccentric portion arranged in the cylinder chamber and
A first bearing that rotatably supports the rotating shaft and defines one end surface of the rotating shaft on the axial core direction and a second bearing that defines the other end surface of the rotating shaft in the cylinder chamber are provided. Accommodates the compression mechanism and
A closed container for storing lubricating oil that lubricates the sliding portion of the compression mechanism is provided.
The rotating shaft includes a main shaft portion supported by the first bearing on one end side in the axis direction with the eccentric portion as a boundary, and a sub-shaft portion supported by the second bearing on the other end side. Have,
The sub-shaft portion is spirally continuous from one end side of the other end in the axis direction to one end side in the axis direction along the rotation direction of the rotation shaft. It has a groove on the outer peripheral surface and
The second bearing has a flange portion and a tubular portion projecting from the flange portion, and is the other end portion of the tubular portion in the axial core direction and is viewed from the radial direction of the rotating shaft. A closed compressor in which the wall thickness of the portion that wraps with the base end of the oil groove is thinner than the wall thickness of the other portion of the tubular portion.
The portion that wraps with the base end of the oil passage groove when viewed from the radial direction of the rotation shaft is the inner wall portion of the groove provided in the other end of the cylinder portion in the axial direction and continuous in the circumferential direction, or the cylinder. The closed compressor according to claim 1, which is one of thin-walled portions continuous in the circumferential direction provided at the other end of the portion in the axial direction.
A balancer provided at the other end of the rotating shaft in the axial direction, and
A balancer cover that covers the balancer is further provided.
The second bearing communicates a discharge hole that discharges the working fluid compressed in the cylinder chamber into the cover space of the balancer cover, and the cover space and the space above the lubricating oil storage surface in the closed container. With a continuous passage,
The closed compressor according to claim 1, wherein the balancer cover has an inclined portion inclined from the other end side of the rotating shaft toward the communication passage.
The balancer cover is bolted to the second bearing, and has a plurality of branch portions that partition the cover space and communicate with each other in the cover space while avoiding the fixing portion by the bolt.
At least one of the plurality of branch chambers communicates with the communication passage,
The closed compressor according to claim 3, wherein the branch chamber portion communicating with the communication passage is provided with an inclined portion having an inclined surface that approaches the communication passage toward the outside in the radial direction of the rotation shaft. ..
The closed compressor according to claim 4, wherein the inclined surface has an inclination angle of 70 ° or less with respect to a horizontal plane.
The center angle of the rotation shaft from the opening center of the discharge hole to the opening center of the communication path with respect to the shaft core in the rotation direction of the rotation shaft when viewed from the axis direction is first located from the opening center of the discharge hole. The sealed compressor according to claim 4 or 5, which is larger than the center angle with respect to the shaft core to the rotation center of the bolt.
The sealed compressor according to any one of claims 1 to 6.
A condenser connected to the closed compressor and
An expansion device connected to the condenser and
A refrigeration cycle device comprising an evaporator connected to the expansion device.