KR100351148B1 - Compressor - Google Patents

Abstract

The present invention relates to a compressor, the present invention is provided with a sealed container provided with a suction tube and a discharge tube in which fluid is sucked and discharged, and an electric motor unit mounted in the sealed container to generate a driving force and a disc portion having a predetermined thickness and outer diameter. A rotating shaft coupled to the rotor and the rotating shaft inserted into the rotating shaft to support the rotating shaft, and having a space forming part for forming a first space together with one surface of the rotating shaft disc part; And a second bearing having a space forming portion for forming a second space together with the other surface of the rotating shaft disc portion and being inserted to be movable to the disc portion of the rotating shaft and moving together with the rotation of the rotating shaft. And vanes for converting the second space into the suction zone and the compressed zone, respectively, and the first and second spaces, respectively. Simplify the structure by including a suction passage formed to suck the refrigerant gas, a discharge passage formed to discharge the refrigerant gas compressed in the first and second spaces, and opening and closing means for opening and closing the discharge passage. By reducing the manufacturing cost and increasing the compression performance, it is possible to realize a relatively small size and to increase the reliability by reducing the vibration noise during operation.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor, and more particularly, to a compressor having a simple structure, excellent reliability, and high compression performance.

In general, the refrigeration cycle device consists of a compressor, condenser, expansion means, evaporator is sequentially connected by a connecting tube. The compressor may suck, compress and discharge the refrigerant gas, and there are various types of compressors such as a rotary compressor, a reciprocating compressor, a scroll compressor, and the like. The configuration of such a compressor is composed of a hermetically sealed container having a predetermined internal space, an electric mechanism part mounted in the hermetically sealed container to generate a driving force, and a compressor mechanism part that compresses gas by receiving a driving force of the electric mechanism part.

In the rotary compressor, as shown in FIG. 1, the rotating shaft 3 press-fitted to the rotor 2 is rotated by the rotation of the rotor 2 of the electric mechanism part M mounted in the sealed container 1. The rolling piston 5 inserted into the eccentric portion 3a of the rotary shaft 3 positioned in the compression space P of the cylinder 4 by the rotation of the rotary shaft 3 is the cylinder compression space P. While in linear contact with the inner circumferential surface and inserted into one side of the cylinder 4 to divide the compressed space P into a high pressure portion and a low pressure portion, the cylinder is rotated in the cylinder compression space P while being in linear contact with a vane (not shown). The process of compressing the refrigerant gas sucked into the suction port 4a formed at 4) and discharging the refrigerant gas through the discharge passage is repeated.

In the reciprocating compressor, as illustrated in FIG. 2, the crankshaft 13 press-fitted to the rotor 12 by the rotation of the rotor 12 of the electric mechanism part M mounted in the sealed container 11. ) Rotates and the piston 14 coupled to the eccentric portion 13a of the crankshaft 13 by the rotation of the crankshaft 13 linearly reciprocating the compression space P of the cylinder 15 while The process of compressing the refrigerant gas sucked through the valve assembly 16 coupled to 15 and simultaneously discharging the refrigerant gas through the valve assembly 16 is repeated.

As shown in FIG. 3, the scroll compressor has an eccentric portion 23a press-fitted to the rotor 22 by the rotation of the rotor 22 of the electric mechanism part M mounted in the sealed container 21. The rotating shaft 23 is rotated and the rotating scroll 24 connected to the eccentric portion 23a of the rotating shaft 23 by the rotation of the rotating shaft 23 is engaged with the fixed scroll 25 to rotate the rotating scroll A plurality of compression pockets formed by the involute curve wraps 24a and 25a respectively formed in the 24 and the fixed scroll 25 move toward the center and at the same time become smaller and continuously inhale, compress, and discharge the refrigerant gas. The process is repeated.

On the other hand, the structural, performance and reliability aspects of the rotary compressor, the reciprocating compressor and the scroll compressor operating by the respective compression mechanisms as described above are as follows.

First, the structural side of the rotary compressor, that is, the side of the compression mechanism, is provided with the eccentric portion 3a on the rotating shaft 3 that is rotated by the driving force, and the rolling piston 5 is inserted into the eccentric portion 3a. Therefore, when the rotation shaft 3 rotates, the eccentric mass forming the rotational imbalance becomes large, causing severe vibration, and a plurality of balance waiters 6 are used to adjust the rotational imbalance, so that the configuration is large and the structure is complicated. In terms of performance, the eccentric portion 3a of the rotating shaft and the rolling piston 5 inserted into the eccentric portion 3a are located in the compression space P of the cylinder 4, so that the compression volume is larger than the size of the compression mechanism. Not only is the compression performance low because only one compression stroke is made when the rotating shaft 3 rotates once. In addition, the rotational torque is increased by the plurality of balance waiters 6, so that the loss of power is large. And in terms of reliability, since the eccentric portion (3a) and the rolling piston (5) formed on the rotating shaft (3) is eccentrically rotated to generate vibration noise during rotation.

In the structural aspect of the reciprocating compressor, the crankshaft 13 is not only provided with an eccentric portion 13a on the crank shaft 13 which is rotated by receiving a driving force, but also the crankshaft 13 because the piston 14 is coupled to and interlocked with the eccentric portion 13a. The eccentric mass forming the rotational imbalance at the time of rotation is increased, causing severe vibration, and a plurality of balance weights 6 are used to adjust the rotational imbalance, so that the configuration is large and the structure is complicated. In terms of performance, since the piston 14 compresses the gas while linearly reciprocating the cylinder compression space P, the amount of compression discharge may be somewhat higher during one revolution of the crankshaft 13, but once per revolution of the crankshaft 13. It is inefficient because of the compression stroke of. In addition, the rotation torque is increased by the eccentric portion 13a and the balance waiter 13b of the crankshaft, so that the loss of power is large and the frictional contact area is large, so that the frictional loss is large. In terms of reliability, since the eccentric portion 13a formed on the crankshaft 13 rotates eccentrically, not only does it generate vibration noise, but also the suction and discharge noise is increased because the valve assembly 16 operates during suction and discharge.

In the structural aspect of the scroll compressor is provided with an eccentric portion (23a) on the rotary shaft 23 is rotated to receive the driving force and the rotating scroll (24) is interlocked to the eccentric portion (23a) to rotate the rotary shaft 23 of the When rotating, the eccentric mass forming the rotational imbalance becomes large, causing severe vibration, and since a plurality of balance waiters 6 are used to adjust the rotational imbalance, there are many components and the structure is complicated. In addition, the processing of the turning scroll 24 and the fixed scroll 25 is very difficult. In terms of performance, since a plurality of compression pockets formed by the lap 24a of the swing scroll and the lap 25a of the fixed scroll continually compress the refrigerant gas, the compression performance is good, but the rotational motion of the swing scroll and the eccentric portion 23a of the rotating shaft Vibration noise is generated by eccentric motion.

As described above, in the rotary compressor, the reciprocating compressor, and the scroll compressor, the balance waiters 6, 13b, and 26 are used due to the eccentric portions 3a, 13a, and 23a of the rotating shaft, which consumes a lot of driving force. In addition, vibration noise is generated during operation, which lowers the reliability. In the case of the rotary compressor and the reciprocating compressor, one compression stroke is performed when the shaft rotates once, which is inefficient. In particular, the rotary compressor has a lot of dead volume has a disadvantage in that the compression performance is lower than the size of the compression mechanism.

It is an object of the present invention to provide a compressor having excellent compression performance per unit volume.

Another object of the present invention is to provide a compressor capable of reducing vibration and noise.

It is a further object of the present invention to provide a compressor which not only simplifies the structure for compressing the refrigerant but also minimizes the components.

1 is a cross-sectional view showing a general rotary compressor,

2 is a cross-sectional view showing a general reciprocating compressor,

3 is a cross-sectional view showing a typical scroll compressor,

4 is a sectional view showing a compressor of the present invention;

5 is a plan view of the compressor of the present invention,

6 and 7 are cross-sectional views taken along line A-A 'and B-B' of FIG. 5;

8 is an exploded perspective view of a compressor of the present invention;

9 is a sectional view showing a modification of the compression mechanism constituting the compressor of the present invention;

10 and 11 are a plan view and a sectional view showing an operating state of the compressor of the present invention;

12, 13 and 14 are plan views showing operating states of the compressor of the present invention, respectively.

(Explanation of symbols for the main parts of the drawing)

30; Hermetic container 31; suction

32; Discharge tube 50; Axis of rotation

52; Disc part 60; First bearing

70; Second bearing 80; Bain

90; Suction flow path 100; Discharge flow path

110; Switching means 120; silencer

200; Oil feeder 300; Balancer

S1; First space S2; Second space

M; Electric mechanism part

An airtight container provided with a suction pipe and a discharge pipe through which a fluid is sucked and discharged in order to achieve the object of the present invention as described above; An electric mechanism part mounted in the sealed container to generate a driving force; A rotating shaft provided with a disc part having a predetermined thickness and an outer diameter and fixedly coupled to the rotor of the electric machine part; A first bearing inserted into the rotating shaft and fixedly coupled to the inner wall of the sealed container to support the rotating shaft, and having an intaglio space forming part for forming a first space together with one surface of the rotating shaft disc part; A second bearing inserted into the rotating shaft and fixedly coupled to the inner wall of the sealed container to support the rotating shaft, and having an intaglio space forming part for forming a second space together with the other surface of the rotating shaft disc part; The first and second spaces are inserted into the disc portions of the rotary shaft so as to partition the first space and the second space, and the first and second spaces are respectively absorbed and compressed in accordance with the rotation of the disc by rotation of the rotary shaft. Vanes for converting; A suction passage formed to suck refrigerant gas into the first and second spaces, respectively; A discharge passage formed to discharge the refrigerant gas compressed in the first and second spaces; It is provided with a compressor comprising an opening and closing means for opening and closing the discharge passage.

Hereinafter, the compressor of the present invention will be described according to the embodiment shown in the accompanying drawings.

4, 5, 6, and 7 show an example of the compressor of the present invention. Referring to this, first, the closed container 30 is formed to have a predetermined internal volume, and a suction pipe into which fluid is introduced into one side thereof. 31 and the discharge tube 32 through which the fluid is discharged are combined.

The electric machine part (M) is composed of a stator 40 fixedly coupled to the hermetic container 30 and a rotor 41 rotatably coupled to the inside of the stator 40.

The rotating shaft 50 is formed to have a predetermined length and outer diameter, and the disk portion 52 formed to have a predetermined thickness and outer diameter following the long shaft portion 51 and the long shaft portion 51 coupled to the rotor 41. ) And a disc portion 53 formed after the disc portion 52 to have a predetermined length and outer diameter. An oil passage 54 through which the oil is supplied passes through the long shaft portion 51, the disc portion 52, and the short axis portion 53. In addition, the outer diameter of the disc portion 52 is formed larger than the outer diameters of the long axis portion 51 and the short axis portion 53, the vane slot 55 is formed through the disc portion 52 to have a predetermined width.

The first bearing 60 has a support portion 62 extending to a predetermined length in the body portion 61 formed in a predetermined shape and the shaft insertion hole into which the rotary shaft 50 is inserted around the support portion 62. (63) is formed through the space forming portion 64 is formed engraved on one side of the body portion (61). The space forming unit 64 includes an intaglio sinusoidal wave surface 65 and an edge wall surface 66 extending perpendicular to the sinusoidal wave surface so as to form a sinusoidal wave shape with respect to the shaft insertion hole 63. The sinusoidal wave surface 65 is provided with a concave line (L) forming a concave inflection point and a convex line (H) forming a convex inflection point, the outer diameter of which corresponds to the outer diameter of the rotating shaft disc portion (52).

The first bearing 60 has a state in which the shaft insertion hole 63 is inserted into the long shaft portion 51 of the rotation shaft 50 and the convex line H is in contact with one side of the rotation shaft disc portion 52. The sinusoidal wave surface 65 is coupled to face the disc portion 52. In this coupled state, the first space S1 is closed by the sinusoidal wave surface 65, the edge wall surface 66, the one surface of the rotation shaft disc portion 52, and the outer circumferential surface of the rotation shaft 50.

The second bearing 70 has a support portion 72 extending to a predetermined length in the body portion 71 formed in a predetermined shape and the shaft insertion hole into which the rotary shaft 50 is inserted around the support portion 72. A 73 is formed through and a space forming portion 74 is engraved on one side of the body portion 71 is formed. The space forming portion 74 is formed to correspond to the space forming portion 64 of the first bearing 60. That is, the body portion 71 is composed of an intaglio sinusoidal wave surface 75 and an edge wall surface 76 extending perpendicular to the sinusoidal wave surface 75 so as to form a sinusoidal wave shape around the shaft insertion hole 73. The sinusoidal wave surface 75 is provided with a concave line (L) forming a concave inflection point and a convex line (H) forming a convex inflection point, the outer diameter of which corresponds to the outer diameter of the rotation shaft disc portion (52).

The second bearing 70 has a shaft insertion hole 73 is inserted into the short axis portion 53 of the rotation shaft 50 and the convex line H is in contact with the other side of the rotation shaft disc portion 52. The sinusoidal wave surface 75 is coupled to face the other side of the disc portion 52. At this time, the convex line H of the second bearing 70 is coupled to the convex line H of the first bearing 60 so as to be 180 degrees out of phase, that is, on the same line. In this coupled state, a second space S2 is formed by the sinusoidal wave surface 75, the edge wall surface 76, the one surface of the rotation shaft disc portion 52, and the outer circumferential surface of the rotation shaft 50. When the space formed by the first space S1 and the second space S2 is radially cut from the center of the rotation shaft 50, the height formed by the space is always constant.

The vanes 80 are formed in a square shape having a predetermined thickness. The vane 80 is inserted into the vane slot 55 formed in the disc portion 52 of the rotation shaft 50 and the vane 80 is inserted to be movable in the axial direction of the rotation shaft 50.

The suction passage 90 and the discharge passage 100 are formed to allow the refrigerant gas to be sucked and discharged into the first space S1 and the second space S2, respectively. That is, the suction passage 90 and the discharge passage 100 communicating with the first space S1 are formed to be located at both sides of the first bearing convex line H, respectively, but the suction passage 90 has a first bearing edge. It is preferably formed in the wall and the discharge flow path 100 is preferably formed in the first bearing body portion 61, the suction flow path 90 and the discharge flow path 100 is discharged based on the rotational direction of the rotary shaft 50 It is formed to be located in the order of the flow path 100 and the suction flow path (90).

In addition, the suction passage 90 and the discharge passage 100 communicating with the second space S2 are formed to be located at both sides of the convex line H of the second bearing 70, respectively, but the suction passage 90 is the second bearing. It is preferably formed in the rim wall 77 of the 70 and the discharge flow path 100 is preferably formed in the second bearing body portion 71, the suction flow path 90 and the discharge flow path 100 is the rotating shaft 50 It is formed to be located in the order of the discharge flow path 100 and the suction flow path (90) on the basis of the rotation direction of the.

The opening and closing means 110 may include a first bearing body 61 and a first opening and closing portion to open and close the discharge passage 100 communicating with the first space S1 and the discharge passage 100 communicating with the second space S2, respectively. 2 are respectively installed in the bearing body portion (71).

The first and second bearings 60 and 70 are preferably fixedly coupled to the hermetic container 30.

Preferably, a silencer 120 is installed in the first bearing 60 and the second bearing 70 to reduce the discharge noise of the refrigerant gas.

The oil supplied to the portion where the sliding contact of the compression mechanism portion and the electric mechanism portion occurs in the bottom surface of the sealed container 30 is filled. And an oil feeder 200 for pumping oil at the end of the rotary shaft 50 is installed.

On one side of the rotor 41 or the rotating shaft 50 constituting the electric mechanism unit, a balancer 300 for adjusting the rotational imbalance generated by the circular motion of the vane 80 is installed, the position of the rotor 41 It is preferably installed in.

On the other hand, the first space (S1) and the second space (S2) to form a structure to form a variety, as a modified example, as shown in Figure 9, the first, second space (S1) ( S2 is formed by the cylinder 150 to which the first and second bearings 130 and 140 and the first and second bearings 130 and 140 are coupled. That is, the first and second bearings 130 and 140 are formed with support portions 132 and 142 protruding at a predetermined height from the body portions 131 and 141 having a round bar shape, and the other sides have a predetermined height and Protruding portions 133 and 143 having outer diameters are formed, and shaft insertion holes 134 and 144 into which the rotation shaft 50 is inserted into the center of the body portions 131 and 141 are formed, and the protrusions 133 ( A sinusoidal wave surface 135 and 145 having a convex convex line H and a concave concave line L is formed at 143. The outer diameter of the protrusions 133 and 143 is formed to correspond to the outer diameter of the rotation shaft disc 52.

The cylinder 150 has an outer diameter and a predetermined thickness corresponding to the inner diameter of the sealed container 30 and a through hole 151 is formed to have an inner diameter corresponding to the outer diameter of the protrusions 133 and 143 therein.

Such a structure is rotated by being inserted and coupled so that the disc portion 52 is positioned in the through hole 151 of the cylinder 150 in a state where the vanes 80 are inserted into the disc portion 52 of the rotary shaft 50. 50 is coupled to the cylinder 150 and the first bearing 130 is the shaft insertion hole 134 is inserted into the long shaft portion 51 of the rotary shaft 50, the projection 133 is the cylinder 150 At the same time, the convex line H is coupled to the disc 52 of the rotating shaft 50 while being inserted into the through hole 151. The second bearing 140 has the shaft insertion hole 144 inserted into the short axis 53 of the rotary shaft 50 and the protrusion 143 is inserted into the through hole 151 of the cylinder 150. The convex line (H) is in contact with the disc portion 52 of the rotating shaft 50 to have a phase difference of 180 degrees with the convex line (H) of the first bearing 130 is coupled. At this time, the first space S1 is formed by one surface of the rotating shaft disc part 52, the sinusoidal wave surface 135 of the first bearing 130, the inner circumferential surface of the through hole 151 of the cylinder 150, and the outer circumferential surface of the rotating shaft 50. The second space is formed by the other surface of the rotating shaft disc portion 52, the sinusoidal wave surface 145 of the second bearing 140, the inner circumferential surface of the through hole 151 of the cylinder 150, and the outer circumferential surface of the rotating shaft 50. S2) is formed. Meanwhile, a disc connecting portion 57 having an outer diameter and a length larger than the outer diameter of the long and short shaft portions 51 and 53 is formed at a portion where the disc portion 52 is positioned in the rotation shaft 50, and the disc connecting portion ( The disc part 52 is extended in the outer peripheral surface of 57. As shown in FIG. In addition, grooves are formed in the first and second bearings 130 and 140 so that the disc connecting portions 57 of the rotating shaft 50 are inserted. The cylinder 150 is fixedly coupled to the hermetic container 30.

Hereinafter, the operational effects of the compressor of the present invention will be described.

First, when power is applied and the rotor 45 of the electric machine part M rotates, the rotary shaft 50 press-fitted to the rotor 45 rotates. The vane 80 coupled to the disc portion 52 of the rotor 45 by the rotation of the rotation shaft 50 moves in a circular motion about the rotation shaft 50, and thus, the first space S1 and the second space ( S2) is switched to the suction area a and the compression area b, respectively. By the circular motion of the vane 80, the first space S1 and the second space S2 are converted into the suction area a and the compression area b, respectively, while the suction passage 90 of the first space S1 is rotated. The refrigerant gas is sucked through the discharge and discharged through the discharge passage 100 while the refrigerant gas is sucked through the suction passage 90 in the second space S2 and compressed and discharged through the discharge passage 100. . At this time, the vane 80 inserted into the vane slot 55 of the rotation shaft disc part 52 moves up and down along the vane slot 55 by the rotation of the rotation shaft 50, and during the first rotation of the disc part 52. 1 round trip.

When the vane 80 is driven in a circular motion, the refrigerant gas is sucked, compressed and discharged in more detail. First, the positions of the vanes 80, that is, both ends of the vanes 80 are illustrated in FIGS. 10 and 11. As described above, when positioned in the convex line H of the first bearing 60 and the concave line L of the second bearing 70, the first space S1 compresses the sucked refrigerant gas and discharges the flow path ( As the discharge is completed through 100, the refrigerant gas is sucked into the first space S1, and at the same time, the second space S2 is in a state in which the refrigerant gas is sucked and the sucked refrigerant gas is compressed.

When the vane 80 is positioned at the position just past the suction flow path 90 of the first bearing 60 due to the rotation of the rotation shaft 50, the vane 80 is located in the first space S1. At the end of the refrigerant gas suction process, compression is performed, and at the same time, the second space S2 is in a state where suction and compression are further progressed at the same time. Then, the vanes 80 are angularly moved in the rotational direction by the rotation of the rotary shaft 50, and as shown in FIG. 13, both ends of the vanes 80 are formed with the concave line L of the first bearing 60. When it is located in the convex line H of the second bearing 70, the first space S1 compresses the refrigerant gas and the suction of the refrigerant gas proceeds, and at the same time, the second space S2 compresses the compressed refrigerant gas. Discharge is completed. When the vanes 80 are angularly moved by the rotation of the rotary shaft 50, and as shown in FIG. 14, the vane 80 is positioned at a position past the suction flow path 90 of the second bearing 70, the first space S1. The compression and suction of the refrigerant gas proceed a little more at the same time, and at the same time, the suction of the refrigerant gas is completed in the second space S2. Then, the vanes 80 are angularly moved by the rotation of the rotary shaft 50, so that both ends of the vanes 80 are convex line H and the second end of the first bearing 60, as shown in FIG. When it is located at the concave line (L) position of the bearing 70, the first space (S1) is completed to discharge the compressed refrigerant gas and at the same time the suction of the refrigerant gas is completed, and at the same time the second space (S2) Compression and suction of the refrigerant gas are simultaneously performed.

As described above, one rotation of the rotation shaft 50, that is, the vane 80 rotates one rotation, inhales, compresses, and discharges the refrigerant gas in the first and second spaces, respectively. As this process is repeated, the refrigerant gas is continuously compressed.

The refrigerant gas in the high temperature and high pressure state compressed and discharged in the first and second spaces S1 and S2 is discharged to the outside of the compressor through the inside of the sealed container 30 and the discharge tube 32.

In the compressor of the present invention, since the rotating body rotating by the driving force of the electric mechanism unit M is composed of the rotating shaft 50 and the vanes 80, the compressor is simpler than other compressors and has fewer components.

In terms of performance, the parts located in the internal space into which the refrigerant gas flows, that is, the portion of the rotating shaft 50 and the volume of the disc part 52 and the vane 80 are reduced to reduce the dead volume, so that the compression space is relatively large and compressed. The performance is excellent. That is, when comparing the compressor of the present invention with the rotary compressor, in the case of the rotary compressor, the rolling piston 5 inserted into the rotary shaft 3, the eccentric portion 3a and the eccentric portion 3a is formed in the inner space of the cylinder 4. Since the position is large, the compression volume is reduced because of the large volume, but the compressor of the present invention has a small volume since the portion of the rotating shaft 50 and the disc portion 52 and the vanes 80 are positioned in the internal space.

In addition, in terms of reliability, the eccentric mass, which forms a rotational imbalance when the rotating body rotates by receiving the driving force of the electric machine part M, is small to prevent the occurrence of vibration noise and to balance the minute rotational imbalance mass. Since the mass of the balance waiter used is also reduced, the overall torque is reduced and power consumption is reduced. Therefore, the electric machine unit M having a relatively small size is used.

As described above, the compressor according to the present invention has a simple structure, a relatively small number of parts, and an excellent compression performance, thereby reducing manufacturing cost and miniaturization. And it reduces the vibration noise during operation has the effect of increasing the reliability.

Claims (5)

An airtight container including a suction pipe and a discharge pipe through which the fluid is sucked and discharged; An electric mechanism part mounted in the sealed container to generate a driving force; A rotating shaft provided with a disc part having a predetermined thickness and an outer diameter and fixedly coupled to the rotor of the electric machine part; A first bearing inserted into the rotating shaft and fixedly coupled to the inner wall of the sealed container to support the rotating shaft, and having an intaglio space forming part for forming a first space together with one surface of the rotating shaft disc part; A second bearing inserted into the rotating shaft and fixedly coupled to the inner wall of the sealed container to support the rotating shaft, and having an intaglio space forming part for forming a second space together with the other surface of the rotating shaft disc part; The first and second spaces are inserted into the disc portions of the rotary shaft so as to partition the first space and the second space, and the first and second spaces are respectively absorbed and compressed in accordance with the rotation of the disc by rotation of the rotary shaft. Vanes for converting; A suction passage formed to suck refrigerant gas into the first and second spaces, respectively; A discharge passage formed to discharge the refrigerant gas compressed in the first and second spaces; And an opening and closing means for opening and closing the discharge passage. The compressor of claim 1, wherein a silencer is installed in the first bearing and the second bearing to reduce noise generated by the discharge gas discharged through the discharge passage. The compressor according to claim 1, wherein an oil feeder is formed in the bottom of the sealed container and an oil flow path is formed inside the rotating shaft, and an oil feeder is installed in the oil flow path to suck up the oil filled in the bottom of the sealed container. . 2. The compressor as set forth in claim 1, wherein a balancer is provided on the rotating shaft or the rotor of the electric motor unit to adjust the rotational imbalance caused by the circular motion of the vanes. The compressor of claim 1, wherein the bottom of the space forming portion of the first and second bearings is formed as a curved surface having a sine wave shape.