KR101510697B1 - Rotation shaft and hermetic compressor having the same and refrigerator having the same - Google Patents

Abstract

The present invention relates to a rotary shaft, a hermetic compressor using the rotary shaft, and a refrigeration apparatus using the same. According to the present invention, both ends of the rotary shaft are supported by the bearings, and thus the efficiency of the compressor and the refrigerating machine can be greatly improved by preventing frictional noise or frictional loss from occurring when the rotor strikes the stator. Further, since the auxiliary bearing is installed as a ball bearing or a roller, the capacity of the compressor increases and the length of the upper bearing or the lower bearing is not required to be long even if the size of the rotor is increased. Therefore, the friction loss is not increased, And the efficiency of the refrigerating machine can be greatly improved. Further, by forming the oil hole and the oil groove on the rotary shaft in contact with the auxiliary bearing, it is possible to prevent friction loss or wear due to an assembly error or the like, thereby further improving the efficiency and reliability of the compressor and the refrigerating machine.

Compressor, auxiliary bearing, ball bearing, friction, oil hole, oil groove

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a rotary shaft, a hermetic compressor using the rotary shaft,

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic compressor and a technology capable of stably supporting a rotary shaft at both ends in a refrigerating machine using the same.

Generally, a hermetic compressor is provided with a driving motor for generating a driving force in an internal space of a sealed casing, and a compression section for being coupled to the driving motor to compress the refrigerant. The hermetic compressor may be divided into a reciprocating type, a scroll type, a rotary type, and an oscillating type depending on a method of compressing a refrigerant. The reciprocating type, the scroll type, and the rotary type are methods using the rotational force of the driving motor, and the oscillating type is a method using the reciprocating motion of the driving motor.

Among the hermetic compressors described above, the drive motor of the hermetic compressor using the rotational force is provided with a rotation shaft, and is configured to transmit the rotational force of the drive motor to the compression unit. For example, the driving motor of the rotary hermetic compressor (hereinafter referred to as a rotary compressor) includes a stator fixed to the casing, a rotor inserted in the stator with a predetermined gap and rotated by interaction with the stator, And a rotary shaft coupled to the rotary shaft and transmitting the rotational force of the rotor to the compression unit. The compression unit includes a compression member coupled to the rotary shaft and configured to suck, compress, and discharge the refrigerant while rotating inside the cylinder, and a plurality of bearing members, which support the compression member and form a compression space together with the cylinder, Lt; / RTI > The bearing member is usually disposed on one side of the drive motor to support the rotation shaft.

However, in the conventional rotary compressor as described above, since the bearing member is installed only on one side of the rotary shaft, the eccentric load generated when the rotary shaft rotates can not be sufficiently canceled, so that the bending of the rotary shaft can be generated, There is a problem that the rotor collides with the stator to generate noise or damage. Particularly, in the case of a doubled rotary compressor having a plurality of cylinders, the height of the motor is increased to improve the efficiency of the compressor. However, in this case, the rotor is stuck to the stator due to the magnetic force generated when the initial power is applied, and at the same time, the rotation shaft starts to rotate in a state in which the rotating shaft is bent, thereby increasing friction noise and wear.

In addition, when the height of the bearing member is increased in consideration of this, there is a problem that the friction area is increased as the bearing member is elevated, adversely affecting the efficiency of the compressor.

SUMMARY OF THE INVENTION The present invention has been made to solve the problems of the conventional hermetic compressor, and it is an object of the present invention to provide a rotary shaft capable of minimizing the efficiency deterioration of the compressor while suppressing the bending of the rotary shaft, a hermetic compressor using the rotary shaft, There is a purpose of.

In order to solve the object of the present invention, there is provided a rotary shaft which is press-fitted into a center of a rotor to transmit a rotary force and has an oil passage formed in an axial direction thereof, There is provided a rotary shaft in which the first oil hole and the second oil hole are formed so as to penetrate from the oil passage to the outer peripheral surface.

In the rotary shaft, the outer circumferential surface of the rotary shaft is provided with at least one oil groove, which is linearly or inclined in the axial direction at the end of the rotary shaft, Is provided.

Further, a casing; A stator fixed to the casing; A rotor rotatably installed in the stator; A rotary shaft coupled to the rotor and having an oil passage formed therein; At least one rolling piston eccentrically coupled to one end of the rotary shaft; At least one cylinder receiving the rolling piston; At least one vane for compressing the refrigerant with the rolling piston; A first bearing coupled to the cylinder to form at least one compression space and to support one side of the rotating shaft about the stator; And at least one second bearing supporting the other side of the rotation shaft about the stator, wherein the rotation shaft is formed with an oil groove or an oil hole communicating with the oil passage to supply oil to the second bearing A hermetic compressor is provided.

Also, in a refrigeration apparatus comprising a refrigerant compression refrigeration cycle including a compressor, a condenser, an expansion valve, and an evaporator, the compressor is provided with the above-described rotary shaft and a compressor.

The hermetic compressor according to the present invention and the refrigeration apparatus using the hermetic compressor can prevent the rotating shaft from being bent during operation by supporting the rotating shaft in both the upper and lower sides of the rotating shaft in the radial direction, thereby preventing frictional noise and wear between the rotor and the stator . In addition, it is possible to reduce friction loss between the rotary shaft and the bearing while stably supporting the rotary shaft, thereby improving the efficiency of the compressor and the refrigerating machine to which the rotary compressor is applied.

Hereinafter, a hermetic compressor according to the present invention will be described in detail with the capacity variable type rotary compressor shown in the attached drawings as an example.

1, the variable displacement type rotary compressor 1 according to the present invention is provided with a drive motor 200 for generating a driving force on the upper side of an inner space of a closed casing 100, A first compression unit 300 and a second compression unit 400 for compressing the refrigerant by the power generated by the driving motor 200 are installed on the lower side of the inner space. And a mode switching unit 500 for switching the operation mode of the compressor so that the second compression unit 400 idles as needed, is provided outside the casing 100.

The internal space of the casing 100 maintains the discharge pressure state by the refrigerant discharged from the first compression unit 300 and the second compression unit 400 or the first compression unit 300, One gas suction pipe 140 is connected to the lower half of the lower main surface of the casing 100 so that the refrigerant is sucked between the first compression unit 300 and the second compression unit 400, One gas discharge pipe 150 is connected to the refrigerant compression unit 300 and the second compression unit 400 so that the refrigerant compressed and discharged is transferred to the refrigeration system.

The driving motor 200 includes a stator 210 fixed to an inner circumferential surface of the casing 100, a rotor 220 rotatably disposed in the stator 210, And a rotary shaft 230 for transferring the rotational force of the driving motor 200 to the compressing units 300 and 400 while rotating together. The drive motor 200 may be a constant speed motor or an inverter motor. However, considering the cost, the driving motor 200 uses a constant speed motor and idles one of the first compressing unit 300 and the second compressing unit 400 as necessary to vary the operation mode of the compressor .

The rotary shaft 230 includes a shaft portion 231 coupled to the rotor 220 and a first eccentric portion 232 and a second eccentric portion 233 which are eccentrically formed on the left and right sides of the lower end portion of the shaft portion 231, ). The first eccentric part 232 and the second eccentric part 233 are formed symmetrically with a phase difference of about 180 ° and the first and second rolling pistons 340 and 430, . An oil passage 234 is formed in the rotation shaft 230 in the axial direction so that the oil of the casing 100 is sucked.

The first compression unit 300 includes a first cylinder 310 formed in an annular shape and installed inside the casing 100 and a second cylinder 310 rotatably coupled to the first eccentric portion 232 of the rotation shaft 230 A first rolling piston 320 which rotates in a first compression space V1 of the first cylinder 310 and compresses a refrigerant; a second rolling piston 320 which is coupled to the first cylinder 310 so as to be movable in a radial direction, A first vane 330 contacting the outer circumferential surface of the first rolling piston 320 with a sealing surface and partitioning the first compression space V1 of the first cylinder 310 into a first suction chamber and a first discharge chamber; And a vane spring 340 as a compression spring to elastically support the rear side of the first vane 330. Reference numeral 350, which is a reference numeral, is a first discharge valve, and 360 is a first muffler.

The second compression unit 400 includes a second cylinder 410 formed in an annular shape and installed in the casing 100 under the first cylinder 310 and a second cylinder 410 installed in the second eccentric part A second rolling piston rotatably coupled to the second cylinder and rotating in the second compression space V2 of the second cylinder and compressing the refrigerant; And the second compression space (V2) of the second cylinder (410) is partitioned into a second suction chamber and a second discharge chamber, respectively, or the second rolling chamber And a second vane (430) spaced apart from an outer circumferential surface of the piston (420) to allow the second suction chamber and the second discharge chamber to communicate with each other. Reference numeral 440 denotes a second discharge valve, and reference numeral 450 denotes a second muffler.

An upper bearing plate (hereinafter referred to as an upper bearing) 110 for supporting the rotary shaft in the radial direction is formed on the upper side of the first cylinder 310 with a first compression space formed with the first cylinder A lower bearing plate (hereinafter referred to as a lower bearing) 120 for supporting the rotary shaft in the radial direction is formed at the lower side of the second cylinder 410, and a second compression space is formed together with the second cylinder do.

The first compression space V1 and the second compression space V2 are defined between the lower side of the first cylinder 310 and the upper side of the second cylinder 410 and the rotary shaft 230 is axially An intermediate bearing plate (hereinafter, referred to as an intermediate bearing) 130 is installed.

The upper bearing 110 and the lower bearing 120 are formed in the shape of a disk and a shaft hole 111 and a shaft hole 121 are formed at the centers of the upper and lower bearings 110 and 120 so that the shaft portion 231 of the rotation shaft 230 is radially supported. The bearing portions 112 and 122 are protruded. The intermediate bearing 130 is formed in an annular shape having an inner diameter to the extent that the eccentric portion of the rotation shaft 230 passes through. The intermediate bearing 130 is connected to the communication passage 131 to communicate with the gas suction pipe 140, And the communication passage 131 communicates with a first suction port (not shown) of the first cylinder 310 and a second suction port (not shown) of the second cylinder 410.

The mode switching unit 500 includes a low pressure side connecting pipe 510 having one end connected to the gas suction pipe 140 and a high pressure side connecting pipe 520 having one end connected to the internal space of the casing 100, A common side connection pipe 530 having one end connected to the vane chamber 413 of the second cylinder 410 and selectively communicating with the low pressure side connection pipe 510 and the high pressure side connection pipe 520, A first mode switching valve 540 connected to the vane chamber S of the second cylinder 410 via the common side connection pipe 530 and a second mode switching valve 540 connected to the first mode switching valve 540, And a second mode switching valve 550 for controlling the opening and closing operation of the one mode switching valve 540.

The operation and effect of the capacity variable type rotary compressor according to the present invention are as follows.

That is, when power is applied to the stator 210 of the driving motor 200 and the rotor 220 rotates, the rotation shaft 230 rotates together with the rotor 220 to rotate the driving motor 200, The first compression unit 300 and the second compression unit 400 transfer the rotational force of the first compression unit 300 and the second compression unit 400 to the first compression unit 300 and the second compression unit 400, 2 rolling piston 420 is eccentrically rotated in the first compression space V1 and the second compression space V2 and the first vane 330 and the second vane 430 move in the first and second compression spaces V1, The first and second rolling pistons 320 and 420 form compression spaces V1 and V2 having a phase difference of 180 °, respectively, while alternately sucking the refrigerant through the communication passage and the suction holes, compressing and discharging the refrigerant.

When the compressor operates in the power mode, the high-pressure gas in the casing 100 is supplied to the second cylinder 410 through the high-pressure side connection pipe 520 by the first mode switching valve 540, The second vane 430 is pushed by the high-pressure refrigerant filled in the vane chamber S and kept in a state of being in pressure contact with the second rolling piston 420 by being supplied to the vane chamber S, The refrigerant gas flowing into the second compression space V2 is normally compressed so that the compressor or the air conditioner to which the compressor is applied operates 100%.

When the compressor is operated as in the case of starting the compressor, a part of the low-pressure refrigerant gas sucked into the second cylinder 410 by the first mode switching valve 540 flows into the vane chamber S, The second vane 430 is pushed by the refrigerant compressed in the second compression space V2 and stored inside the second vane slot (not shown). As a result, the suction chamber of the second compression space (V2) communicates with the discharge chamber and the refrigerant gas sucked into the second compression space (V2) is not compressed, and the refrigerant gas The compressor or the air conditioner to which the compressor is applied is operated only by the capacity of the first compression space.

The driving motor 200 rotates together with the rotating shaft 230 by pushing the rotating shaft 230 into the rotor 220. The rotating shaft 230 rotates about one side of the rotor 220 in the axial direction, The eccentric mass is generated when the rotary shaft 230 rotates at a high speed as it is supported by the bearing 110 and the lower bearing 120. The upper portion of the rotation shaft 230, that is, the portion where the rotor 220 is engaged, is bent by the eccentric mass, so that the rotor 220 may strike the stator 210.

In particular, in the case of the capacity variable type rotary compressor having a plurality of compressors as in the present embodiment, the length of the drive motor 200 including the rotor 220 is increased to increase compressor efficiency. In this case, The degree of bending of the rotating shaft 230 increases together with the length of the stator 210 and the frictional loss between the stator 210 and the rotor 220 can be further increased. In this case, the length of the upper bearing 110 may be increased. However, as described above, the frictional loss between the rotary shaft 230 and the upper bearing 110 increases, so that the compressor efficiency can be reduced.

1 and 2, an upper bearing 110 and a lower bearing 120 (including an upper bearing and a lower bearing) are disposed at an upper end of the rotation shaft 230, that is, The auxiliary bearing 600 (which may be referred to as a second bearing) is provided on the opposite side of the rotating shaft 230 to support the rotating shaft 230 at both the upper and lower ends.

3 and 4, the auxiliary bearing 600 includes a support frame 610 fixed to the inner circumferential surface of the casing 100, and a support frame 610 installed on the support frame 610 to support the rotation shaft 230 And a bearing housing 630 which receives the ball bearing 620 and is fixed to the support frame 610. The bearing housing 630 is fixed to the support frame 610 in a radial direction.

The supporting frame 610 is annularly formed with a supporting portion 611 and a plurality of fixing protrusions 612 are formed which extend radially from the outer circumferential surface of the supporting portion 611 and are welded to the inner circumferential surface of the casing 100 do. The bearing portion 611a is formed so that the bearing portion 611a is stepped on the inner circumferential surface of the support portion 611 so that the ball bearing 620 is placed thereon. The bearing seating portion 611a is formed such that its inner diameter is larger than the outer diameter of the rotary shaft 230 and is larger than the outer diameter of the ball bearing 620, which is larger than the inner diameter of the outer ring 622, Is formed smaller than the outer diameter. The support frame 610 is made of a material and a thickness that can have a strength enough to support the rotation shaft 230.

The ball bearings 620 are interposed between the inner and outer rings 621 and 622 while retaining a gap between the inner and outer rings 621 and 622 by retainers (not shown) So that they can perform mutual motion. The inner circumferential surface of the inner ring 621 may have a predetermined gap with respect to the outer circumferential surface of the rotating shaft 230.

The bearing housing 630 is formed with a flange portion 631 to be fixed to the support frame 610 and a receiving portion 632 is formed on a central portion of the flange portion 631 to receive the ball bearing 623. [ Is protruded. A through hole 633 is formed at the center of the receiving portion 632 to allow the rotation shaft 230 to pass therethrough and an inner diameter of the through hole 633 is larger than the supporting portion 611, (611a) but larger than the inner diameter of the ball bearing (620). However, the bearing housing 630 may be configured such that the receiving portion 633 is closed so that the oil taken up through the oil passage 234 of the rotary shaft 230 is not scattered into the inner space of the casing 100.

In the capacity variable type rotary compressor having the above-described auxiliary bearing, the lower end of the rotary shaft is supported by the upper bearing 110 and the lower bearing 120 corresponding to the first bearing, and the upper end of the rotary shaft 230 is supported by the second bearing The upper and lower ends of the rotary shaft 230 are supported by bearings so that the rotary shaft 230 can be prevented from being bent when the compressor starts or when the compressor continues to operate.

Accordingly, it is possible to prevent the occurrence of friction noise or friction loss due to the impact of the rotor 220 against the stator 210, thereby improving the efficiency of the compressor. In addition, since the auxiliary bearing 600 is installed as a ball bearing, the capacity of the compressor increases and the length of the upper bearing 110 or the lower bearing 120 does not need to be increased even if the size of the rotor 220 increases The friction loss is not increased and the efficiency of the compressor can be greatly improved.

However, the rotation shaft 230 and the ball bearing 620 are assembled with a predetermined clearance. However, the rotation shaft 230 and the ball bearing 620 are formed by an error occurring during assembly or a bending phenomenon occurring during rotation of the rotation shaft 230, The friction between the rotating shaft 230 and the ball bearing 620 may be lost or abrasion may occur.

1 to 5, the first and second bearings 110 and 210 are disposed on the upper and lower sides of the rotation shaft 230, more precisely on both upper and lower sides in the axial direction about the rotor 220 The first oil holes 235a and 235b and the second oil hole 236 are formed to supply oil to the first bearing 120 and the second bearing 600, respectively. The first oil holes 235a and 235b and the second oil holes 236b are formed in the outer circumferential surface of the rotary shaft 230, The first oil grooves 237a and 237b and the second oil groove 238 may be formed so that the first oil groove 236 and the second oil groove 236 are accommodated.

The second oil groove 238 corresponding to the second bearing 600 is extended in the axial direction by a predetermined length at the end of the rotary shaft 230 so as to communicate with the oil passage 234, 2 oil groove 238 may be formed in such a length that a part of the oil groove 238 can overlap within the axial range of the second bearing 600. [ As shown in FIGS. 4 and 5, the second oil groove 238 may be formed to be straight in the same direction as the axial direction, but it may be formed in a spiral shape so as to be inclined in some cases.

The second oil hole 236 may be formed within the axial range of the second bearing 600. Since the bubble may move through the oil passage 234, The second bearing 600 may be formed outside the axial range of the second bearing 600 to prevent the second bearing 600 from being introduced into the bearing surface of the second bearing 600.

When the second oil hole 236 and the second oil groove 238 are formed at the upper end of the rotary shaft 230, that is, the portion corresponding to the second bearing 600, The oil sucked through the oil passage 234 is mixed with a part of the refrigerant compressed by the compressors 300 and 400 and is taken up along the oil passage 234 and is sucked through the oil passage 234 The oil is supplied between the rotating shaft 230 and the second bearing 600 through the second oil hole 236 and the second oil groove 238. Thus, as the oil is supplied and lubricated between the rotating shaft 230 and the second bearing 600, the clearance between the rotating shaft 230 and the second bearing 600 is narrowed due to an assembly error, shaft bending, It is possible to prevent the occurrence of friction loss or abrasion. Thereby reducing the noise of the compressor and improving energy efficiency.

Other embodiments of the auxiliary bearing according to the present invention are as follows.

That is, in the above-described embodiment, the auxiliary bearing is formed of a ball bearing, and is constituted by a support frame, a bearing, and a housing. In this embodiment, a roller 640 may be applied instead of the ball bearing as shown in FIG. In this case, the auxiliary bearing 600 may include a support frame 610, a roller 640, and a bearing housing 630 for supporting the roller 640.

The support frame 610 and the bearing housing 630 may be formed in the same manner as in the previous embodiment and the roller 640 may be formed in a cylindrical shape so that the inner circumferential surface of the roller 640 may slide on the outer circumferential surface of the rotation shaft 230, It can be formed so as to have a diameter capable of movement, that is, a predetermined gap. The outer diameter of the roller 640 may be formed to have a diameter capable of sliding with the inner diameter of the support portion 611 of the support frame 610.

6, the roller 640 may have a cylindrical shape having the same diameter in the axial direction. However, in order to reduce frictional loss, the inner circumferential surface or the outer circumferential surface of the roller 640 may be formed on the outer circumferential surface of the rotation shaft 230, Shaped bearing portion in a circular cross-sectional shape along the circumferential direction so as to be in line contact with the inner circumferential surface of the frame 610. The bearing portion may be formed on the inner circumferential surface of the support frame 610 where the outer circumferential surface of the roller 640 is opposed.

The roller 640 may be formed of a self-lubricating member such that friction loss is reduced even when oil is worn during start-up, or a lubrication layer may be coated on the inner circumferential surface and the outer circumferential surface of the roller 640, or may be formed of a lubricative material such as Teflon .

A second oil hole 236 and a second oil groove 238 are formed on the rotation shaft 230 corresponding to the roller 640. Since the position and shape of the second oil hole 236 and the second oil groove 238 and the operation and effect of the second oil hole 236 and the second oil groove 238 are similar to those of the above-described embodiment, a detailed description thereof will be omitted.

Meanwhile, when the hermetic compressor according to the present invention is applied to a refrigerating machine, the noise of the refrigerating machine can be reduced and the efficiency can be improved.

For example, as shown in FIG. 7, in a refrigeration apparatus 700 having a refrigerant compression refrigeration cycle including a compressor, a condenser, an expander, and an evaporator, the refrigerating apparatus 700 includes a main substrate 710 for controlling the entire operation of the refrigerating apparatus A first bearing and a second bearing may be respectively installed on both ends of a rotary shaft of the motor which is connected to the compressor C and installed in the compressor. The oil hole and the oil groove are formed on the rotary shaft corresponding to the second bearing, so that friction loss or wear between the rotary shaft and the second bearing can be prevented in advance.

In this way, the frictional noise in the compressor is reduced and the friction loss is reduced, so that the noise of the refrigerating appliance to which the compressor is applied can be reduced and the energy efficiency can be improved.

Although the hermetic compressor according to the present invention is applied to the capacity variable type rotary compressor, the present invention can also be applied to a single rotary compressor having a compression unit. The hermetic compressor according to the present invention can be equally applied to refrigeration equipment such as household or industrial air conditioners.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view showing the inside of a rotary compressor of the present invention,

FIG. 2 is a perspective view showing bearings for supporting both ends of a drive motor in the rotary compressor according to FIG. 1,

Figure 3 is a perspective view of the second bearing according to Figure 1,

FIG. 4 is a longitudinal sectional view showing an embodiment of the second bearing according to FIG. 1;

FIG. 5 is a perspective view showing a rotation axis according to FIG. 1,

FIG. 6 is a longitudinal sectional view showing another embodiment of the second bearing according to FIG. 1;

Figure 7 is a schematic view of an air conditioner equipped with the rotary compressor according to Figure 1;

DESCRIPTION OF REFERENCE NUMERALS

100: casing 130: intermediate bearing

131: communication channel 140: gas suction pipe

230: rotation shaft 231:

232, 233: eccentric portion 234:

235a, 235b: first oil hole 236: second oil hole

237a, 237b: first oil groove 238: second oil groove

310: first cylinder 320: first rolling piston

330: first vane 410: second cylinder

510: Low pressure side connection pipe 520: High pressure side connection pipe

530: Common side connector 540,550: Mode switching valve

600: auxiliary bearing 610: support frame

611: Support portion 612: Fixed projection portion

620: ball bearing 630: bearing housing

631: flange portion 632:

640: Rollers

Claims (14)

A rotary shaft which is press-fitted into the center of the rotor to transmit a rotational force and has an oil passage formed therein in an axial direction, A first oil hole and a second oil hole are formed in the upper and lower sides of the shaft axially so as to penetrate from the oil passage to the outer circumferential surface, At least one of the first oil hole and the second oil hole is formed to be accommodated in the oil groove provided on the outer circumferential surface, Wherein the oil groove extends axially or straightly from an end of the shaft. delete delete A rotary shaft which is press-fitted into the center of the rotor to transmit a rotational force and has an oil passage formed therein in an axial direction, Wherein at least one oil groove is formed on an outer circumferential surface of the rotary shaft in a straight or inclined manner in an axial direction at an end of the rotary shaft. 5. The method of claim 4, Wherein the oil groove has an oil hole penetrating through the oil passage. Casing; A stator fixed to the casing; A rotor rotatably installed in the stator; A rotary shaft coupled to the rotor and having an oil passage formed therein; At least one rolling piston eccentrically coupled to one end of the rotary shaft; At least one cylinder receiving the rolling piston; At least one vane for compressing the refrigerant with the rolling piston; A first bearing coupled to the cylinder to form at least one compression space and to support one side of the rotating shaft about the stator; And And at least one second bearing supporting the other side of the rotation shaft about the stator, Wherein the rotary shaft further includes an oil hole formed to communicate the oil passage with an outer circumferential surface and an oil groove formed on an outer circumferential surface of the rotary shaft so as to communicate with the oil hole and supply oil to the second bearing, Wherein the oil groove is formed so as to at least partially overlap within an axial range of the second bearing. delete The method according to claim 6, Wherein the oil groove is formed on an outer circumferential surface of the rotating shaft by extending straight or inclined axially from the shaft end. The method according to claim 6, Wherein an oil groove is formed in an outer circumferential surface of the rotary shaft and an oil hole penetrating through the oil passage is formed in the oil groove. 10. The method of claim 9, Wherein the oil hole is formed outside an axial extent of the second bearing. delete The method according to claim 6, Wherein at least one of the vanes is selectively supported by a refrigerant filled in the inner space of the casing and a refrigerant sucked into the compression space of the cylinder. The method according to claim 6, Wherein at least one vane of the vanes is restrained or restrained by a pressure difference between a refrigerant filled in the inner space of the casing and a refrigerant supporting the vane. A refrigerating device comprising a refrigerant compression refrigeration cycle including a compressor, a condenser, an expansion valve, and an evaporator, Wherein the compressor comprises the compressor of any one of claims 6, 8 to 10, and 12 to 13.

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