JPH08170595A - Hermetic compressor - Google Patents

Abstract

PURPOSE: To prevent lowering of oil sealing ability of a roller end surface, to restrain abrasion of the roller end surface, the end surface of a first bearing and the end surface of a second bearing, and to improve reliability of a sliding part by preventing an increase in the relative speed of the roller end surface and a set of the first bearing end surface and the second bearing end surface in a high speed rotating operation by an inverter or the like. CONSTITUTION: A closed compressor comprises a main bearing 26 and an auxiliary bearing 27 which are provided with circular grooves on the cylinder 4 side end surfaces fixed to both ends of a cylinder 4, a shaft sliding in rotation in the main bearing 26 and the auxiliary bearing 27, and bearing washers 19a, 19b stored in the circular grooves of the main bearing 26 and the auxiliary bearing 27 in such a manner as to freely rotate.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic compressor used in a refrigerator, an air conditioner, etc., and has a remarkable effect in improving efficiency and reliability particularly when operating an inverter. .

[0002]

2. Description of the Related Art As a conventional hermetic compressor, Japanese Patent Application Laid-Open No. 62-62
There is one disclosed in Japanese Patent Publication No. 199990. The conventional hermetic compressor will be described below with reference to the drawings.

A conventional configuration is shown in FIGS. 7 and 8. FIG.
FIG. 8 is a vertical sectional view of a conventional hermetic compressor, and FIG. 8 is a sectional view taken along the line AA of FIG.

In FIGS. 7 and 8, 1 is a closed casing, 1a is a refrigerant gas space, 2 is an electric motor part, and a cylinder 4, a roller 5, a vane 6 and a first shaft 3 are provided via a shaft 3.
It is connected to a machine unit body 9 composed of the bearing 7 and the second bearing 8. The shaft 3 includes a main shaft 3a, a sub shaft 3b, and a crank 3c.

Further, the main shaft 3a of the shaft 3, the sub shaft 3b,
The crank 3c is provided with oil passages 3d, 3e and 3f, respectively. Reference numeral 10 is a spring provided between the rear surface of the vane 6 and the cylinder 4. In the cylinder 4, 11a and 11b are rollers 5, vanes 6, first bearings 7,
The suction chamber and the compression chamber are formed by the second bearing 8. 1
Reference numeral 2 denotes an oil supply mechanism formed by a coil spring 12a fixed to the sub shaft 3b and a guide tube 12b fixed to the second bearing 8 and communicating with the oil passages 3e, 3f, 3d. Reference numeral 14 denotes a suction pipe, and the suction passage 15 of the second bearing 8 and the cylinder 4
Through the suction chamber 11a. Reference numeral 16 denotes a discharge part, which communicates with the inside of the closed casing 1 via a discharge valve (not shown). A discharge port 17 is open to the inside of the closed casing 1. Reference numeral 18 is a lubricating oil in the closed casing 1.

Next, the mechanism of the hermetic compressor will be described. Refrigerant gas from a cooling system (not shown) is introduced from a suction pipe 14 and a suction passage 15 into the suction chamber 1 in the cylinder 4.
1a. The refrigerant gas reaching the suction chamber 11a is rotatably housed in the crank 3c of the shaft 3 by the roller 5
In the compression chamber 11b partitioned by the vanes 6, the shaft 3 is gradually compressed by the rotational movement of the shaft 3 accompanying the rotation of the electric motor unit 2. The compressed refrigerant gas is once discharged into the closed casing 1 through the discharge unit 16 and a discharge valve (not shown), and then discharged through the discharge port 17 into the cooling system.

The lubricating oil 18 accumulated in the lower portion of the closed casing 1 is rotated by the coil spring 12a fixed to the sub shaft 3b of the oil supply mechanism 12, and is passed through the coil spring 12a in the guide tube 12b to the sub shaft 3b. To the oil passage 3e,
The sliding portion is lubricated through 3f and 3d, and a part of the lubricating oil flows out of the oil drain port 13 of the first bearing 7 on the electric motor 2 side and directly returns to the lower portion of the closed casing 1. A part of the gas enters the compression chamber 11b and is discharged into the closed casing 1 together with the refrigerant gas, and returns to the lower part of the closed casing 1.

Further, between the vane 6 and the cylinder 4, when the vane 6 reciprocates, it is immersed in the lubricating oil 18 stored in the closed casing 1 to supply oil to the vane 6 and the vane 6 and the cylinder 4. Lubrication between sliding parts,
It is sealed.

[0009]

However, in the above-mentioned conventional structure, when the hermetic compressor is rotated at a high speed by the inverter or the like, the roller 5 which is in contact with the crank 3C of the shaft 3 is rotated at a high speed, Both end surfaces 5
The relative speeds of the sliding portions of the end faces of the first bearing 7 and the second bearing 8 become faster. Therefore, the sliding heat generated at the sliding surface of the end surface of the roller 5 increases, the viscosity of the lubricating oil on the end surface of the roller 5 decreases, and the sealing performance deteriorates. There was a problem of reduced efficiency such as flowing into the chamber 11a and the compression chamber 11b. Further, there is a problem that the sliding distance between the end surfaces of the first bearing 7 and the second bearing 8 and the end surfaces of the roller 5 becomes long, causing abnormal wear.

The present invention solves the conventional problems, and suppresses an increase in the relative speed between the roller both end surfaces and the first bearing end surface and the second bearing end surface when the compressor rotates at a high speed by an inverter or the like. However, by suppressing an increase in sliding heat generation on the roller end surface, it is possible to prevent a decrease in sealing performance and a decrease in volumetric efficiency due to a decrease in the viscosity of the lubricating oil on the roller end surface, and to suppress the wear of the sliding portion. The purpose is to improve the reliability of the moving part.

Further, in the above-mentioned conventional structure, the heat generation of the hermetic compressor at a high speed increases the sliding heat generation at the sliding parts such as the bearings 7, 8 and the shaft 3, thus forming the compression chamber 11b. The temperature of the cylinder 4, the first bearing 7, and the second bearing 8 that rise are increased. Therefore, the refrigerant gas flowing into the compression chamber 11b is overheated, which causes a problem that volume efficiency is reduced.

Another object of the present invention is to cool a cylinder side wall having a large area facing the compression chamber even if the temperature of each sliding portion such as a bearing and a shaft rises because the compressor rotates at a high speed. To reduce the heating of the intake gas and improve the volumetric efficiency.

[0013]

In order to achieve this object, a hermetic compressor according to the present invention includes a hermetic casing having a refrigerant gas space, lubricating oil stored in a lower portion of the hermetic casing, and a hermetically sealed casing. Cylinder, a roller that eccentrically rotates inside the cylinder, a vane that reciprocates in the groove of the cylinder and abuts against the roller to divide the inside of the cylinder into a suction chamber and a compression chamber, and the cylinder side fixed to both ends of the cylinder. A main bearing and a sub-bearing each having a circular groove on the end surface of the
The bearing washer is rotatably housed in the circular grooves of the main bearing and the sub bearing.

Further, it comprises a communication hole having one end communicating with the bottom surface of the circular groove, and a communication pipe having one end joined to the other end of the communication hole and the other end communicating with the lubricating oil stored in the closed casing. Has been done.

Further, one end is connected with a communication hole which communicates with the bottom surface of the circular groove, and the other end is connected with a communication pipe which communicates with the lubricating oil accumulated in the closed casing, and at least 90 ° from the vane in the anti-compression direction. It is composed of the above communication path in the cylinder side wall.

A plurality of oil reservoirs are provided on at least one of the end surface of the bearing washer on the side opposite to the cylinder or the bottom surface of the circular groove provided on the main bearing and the sub bearing.

[0017]

The hermetic compressor of the present invention prevents the oil sealability of the roller end surface from increasing by preventing the relative speed between the roller end surface and the first bearing end surface and the second bearing end surface from increasing during high speed rotation operation by an inverter or the like. The decrease can be prevented, and the wear of the roller end surface, the first bearing end surface, and the second bearing end surface is suppressed, and the reliability of the sliding portion is improved.

Further, in the high-speed rotation operation of the compressor, even if the temperature of each sliding portion such as the bearing and the shaft rises, the heating of the intake gas can be reduced by cooling the cylinder constituting the compression chamber with oil. Volume efficiency is improved.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the hermetic compressor according to the present invention will be described below with reference to the drawings. It should be noted that the same components as those of the related art will be denoted by the same reference numerals and detailed description thereof will be omitted.

FIG. 1 is a vertical cross-sectional view of a hermetic compressor according to a first embodiment of the present invention, FIG. 2 is a cross-sectional view of a main part of the same embodiment, and FIG.
FIG. 3 is a sectional view taken along line BB of FIG.

In FIGS. 1, 2 and 3, 19a and 19 are shown.
b is a bearing washer, 26 is a main bearing, 27 is a sub bearing, and the main bearing 26 and the sub bearing 27 are fixed to the cylinder 4. Circular grooves 25a and 25b are provided on the end surfaces of the main bearing 26 and the sub bearing 27 on the cylinder 4 side, respectively, and the bearing washers 19a and 19a, respectively.
b is stored rotatably.

The operation of the hermetic compressor constructed as described above will be described below. End surface 5 of roller 5
Although a and 5b slide with bearing washers 19a and 19b rotatably housed in the circular grooves 25a and 25b, the movement of the roller 5 is complicated by the rotational movement with respect to the fixed coordinate system and the rotational movement with respect to the crank 3c. Entangled in. However, considering the relative speeds of the end surfaces 5a and 5b of the roller 5 and the sliding portions of the bearing washers 19a and 19b, it is largely due to the turning motion. Therefore, when the bearing washers 19a and 19b do not rotate, the bearing washers 19a and 19b and the end surface 5 of the roller 5 may be changed by increasing or decreasing the number of rotations of the shaft 3 and the crank 3c.
The relative speed of the sliding portions of a and 5b will increase or decrease.

By the way, the sliding portions of the end surfaces 5a and 5b of the roller 5 and the bearing washers 19a and 19b are supplied with lubricating oil from the inner peripheral portion of the roller 5 for lubrication, and at the same time, the inner peripheral portion of the roller 5 of high temperature and high pressure is sucked. Chamber 11a, compression chamber 1
1b is sealed.

Therefore, the crank 3c rotates, and the end surfaces 5a and 5b of the roller 5 and the bearing washers 19a and 1a.
When the movement mainly of the rotational movement of the shaft 3 in the rotational direction of the shaft 3 occurs between the sliding portions of the shaft 9b, the bearing washers 19a and 19b rotate in the rotational direction of the shaft 3 due to the viscous friction of the lubricating oil interposed in the sliding portions. Since the viscous friction of the lubricating oil increases / decreases as the relative speed increases / decreases, the shaft 3
The rotation of the bearing washer also increases / decreases with the increase / decrease in the number of rotations of the roller 5, that is, the increase / decrease in the rotation of the main body of the turning motion of the roller 5.

Therefore, if the rotation speed of the shaft 3 becomes faster, the rotation of the bearing washers 19a, 19b in the shaft rotation direction becomes faster, and the increase in the relative speed between the end surfaces 5a, 5b of the roller 5 and the bearing washers 19a, 19b is suppressed. can do.

Therefore, even if the shaft 3 is rotated at a high speed by an inverter or the like, it is possible to suppress an increase in relative speed between the end surfaces 5a and 5b of the roller 5 and the sliding portions of the bearing washers 19a and 19b, and suppress an increase in sliding heat generation. . Therefore, it is possible to prevent the sealing property between the inner circumference of the roller 5 and the suction 11a and the compression chamber 11b from being lowered due to the decrease in the viscosity of the lubricating oil on the end surfaces 5a and 5b of the roller 5, and to increase the relative speed of the sliding portion. It is possible to suppress and prevent increase in wear.

As described above, the hermetic compressor of this embodiment is
A roller 5 that eccentrically rotates in the cylinder 4, and a cylinder 4
Vanes 6 that divide the inside of the cylinder 4 into a suction chamber 11a and a compression chamber 11b by reciprocating in the groove of the cylinder 5 and contacting the rollers 5, and a cylinder 4 fixed to both ends of the cylinder 4.
Bearing 26 and sub bearing 27 having circular grooves on the side end surface
And a bearing washer 19a, 19b rotatably housed in the circular grooves of the main bearing 26 and the auxiliary bearing 27. Can suppress an increase in relative speed between the end surfaces 5a and 5b of the roller 5 and the sliding portions of the bearing washers 19a and 19b even when rotated at a high speed by an inverter or the like, and suppress an increase in sliding heat generation.

Therefore, the inner circumference of the roller 5 and the suction 11a due to the decrease in the viscosity of the lubricating oil on the end surfaces 5a, 5b of the roller 5,
It is possible to prevent a decrease in the sealing property between the compression chambers 11b, suppress an increase in the relative speed of the sliding portion, and prevent an increase in wear.

Next, a second embodiment of the hermetic compressor according to the present invention will be described with reference to the drawings. The same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.

FIG. 4 is a sectional view of the essential parts of a hermetic compressor according to the second embodiment of the present invention. In FIG. 4, 20, 2
Reference numeral 1 is a communication hole provided in the main bearing 26 and the sub bearing 27, respectively, and one ends 20a and 20b of the communication holes communicate with the circular grooves 25a and 25b, respectively. Reference numerals 22 and 23 denote communication holes having one ends 22a and 23a communicating with the lubricating oil 18 in the closed casing 1, and the other ends 22b and 23, respectively.
b is connected to the other ends 20b and 21b of the communication holes, respectively.

The operation of the hermetic compressor constructed as above will be described below. First, when the compressor operates, the pressure in the suction chamber 11a decreases, and the pressure in the closed casing 1 from which the compressed refrigerant is discharged rises. The bearing washers 19a and 19b are attached to the suction chamber 11
Since it faces a, the gap between the circular grooves 25a and 25b of the main bearing 26 and the sub bearing 27, and the end surfaces 5a and 5 of the roller 5
The pressure in the gap with b also decreases.

Therefore, due to the pressure difference from the high pressure inside the closed casing 1, the lubricating oil 18 inside the closed casing 1
Flows into the circular grooves 25a and 25b through the communication pipes 22 and 23 and the communication holes 20 and 21, and the circular grooves 25a and 25b.
Is supplied to the sliding parts between the bearing washers 19a and 19b and the circular grooves 25a and 25b, and the sliding parts between the bearing washers 19a and 19b can be sufficiently lubricated, and the rollers can be smoothly rotated by the bearing washers 19a and 19b. It is possible to reduce the relative speed to the end surface of the circular groove 5, and to prevent abrasion of the circular grooves 25a and 25b and the bearing washers 19a and 19b. In addition, the bearing washers 19a and 19b and the main bearing 2
6, the gap between the auxiliary bearing 27 and the end surfaces 5a, 5b of the roller 5 can be oil-sealed, and the lubricating oil 18 flows into the suction chamber 11b or the like, thereby reducing the volumetric efficiency and increasing the input efficiency. Can be prevented.

In this embodiment, the lubrication mechanism for the circular groove utilizing the differential pressure using the communication hole and the communication pipe is used, but it goes without saying that the same effect can be obtained with other lubrication mechanisms. Yes.

As described above, the circular grooves 25a, 25
Communication holes 20 and 21 communicating with the bottom surface of b, and communication pipes 22 and 23 having one end joined to the other ends of the communication holes 20 and 21 and the other end communicating with the lubricating oil 18 stored in the closed casing 1. The bearing washer 19a,
The relative speed with the end surface of the roller 5 can be reduced by the smooth rotation of 19b, and the circular grooves 25a and 25b, the bearing washers 19a and 19b, and the end surfaces 5a and 5 of the roller 5 can be reduced.
Wear of b can be prevented.

Further, the main bearing 26, the sub bearing 27, the bearing washers 19a and 19b, the end surface 5a of the roller 5,
It is possible to prevent the lubricating oil 18 from flowing into the suction chamber 11b or the like via 5b or the like, and prevent a decrease in volume efficiency or an increase in input.

Next, a third embodiment of the hermetic compressor according to the present invention will be described with reference to the drawings. The same components as those in the first and second embodiments are designated by the same reference numerals and detailed description thereof will be omitted.

FIG. 5 is a sectional view of the essential parts of a hermetic compressor according to the third embodiment of the present invention. In FIG. 5, 28, 2
Reference numeral 9 denotes a communication passage in the cylinder side wall provided in the cylinder 4, which is provided at least 90 ° or more in the anti-compression direction from the vane 6. And the communication passage 2 in the cylinder side wall
8, 29 have one end communicating with the communication holes 20, 21 and the other end communicating with the communication pipe. Therefore, the circular grooves 25a and 25b
Communicate with each other through the connecting pipes 22 and 23, the communication passages 28 and 29 in the cylinder side wall, and the connecting holes 20 and 21, respectively.

The operation of the hermetic compressor constructed as described above will be described below. First, when the compressor operates, the communication pipes 22 and 23, the communication passages 28 and 2 in the cylinder side wall
The lubricating oil in the closed casing 1 flows into the circular grooves 25a and 25b by the differential pressure through the communication holes 20 and 21. Further, the cylinder 4 constituting the suction chamber 11a and the compression chamber 11b is heated by the heat generated by compressing the refrigerant and the sliding heat, and especially the temperature from the vane 6 in the anti-compression direction becomes high.

However, since the lubricating oil flows in the communication passage in the cylinder side wall provided in the range of at least 90 ° or more in the anti-compression direction from the vane 6 which is a particularly high temperature portion,
The cylinder 4 can be cooled. Therefore, the cold refrigerant sucked into the suction chamber 11a can be prevented from being overheated from the cylinder 4, and the volumetric efficiency of the compressor can be improved.

In this embodiment, the connecting hole and connecting pipe are used, but it goes without saying that the same effect can be obtained with other configurations.

As described above, in the hermetic compressor of this embodiment, one end has a communicating hole communicating with the bottom surfaces of the circular grooves 25a and 25b, and the other end has the lubricating oil 18 stored in the hermetic casing 1.
From the communication holes 20 and 21 that communicate with each other, the other end of the communication holes 20 and 21 and the communication pipes 22 and 23, and the communication path in the cylinder side wall at least 90 ° or more in the anti-compression direction from the vane Since it is configured, the cylinder 4 can be cooled, overheating of the refrigerant by the cylinder 4 can be reduced, and the volumetric efficiency of the compressor can be improved.

Next, a fourth embodiment of the hermetic compressor according to the present invention will be described with reference to the drawings. The same components as those in the first, second and third embodiments are designated by the same reference numerals and detailed description thereof will be omitted.

FIG. 6 is a front view of the bearing washers 19a and 19b of the hermetic compressor according to the fourth embodiment of the present invention.

In FIG. 6, 19c is a circular groove 25a, 2
An end surface on the counter cylinder side opposite to the bottom surface of 5b, and 24 is an oil reservoir provided on the end surface 19c on the counter cylinder side of the bearing washers 19a and 19b.

The operation of the hermetic compressor constructed as above will be described below. First, when the compressor is operated, the lubricating oil 18 in the closed casing 1 becomes circular groove 25.
It flows into a and 25b. Then, the circular grooves 25a, 25
The lubricating oil 18 that has flowed into b is the bearing washer 1
By the rotation of 9a and 19b and the oil sump 24, the circular groove 25
It is supplied to the entire sliding portion between the a and 25b and the bearing washers 19a and 19b. Therefore, local wear of the sliding portion can be prevented.

Also, while the compressor is stopped, the oil sump 24
Since the lubricating oil can be stored inside, the sliding parts of the bearing washers 19a and 19b and the circular grooves 25a and 25b can be lubricated immediately after the compressor is started, and the reliability of the sliding parts is improved. .

As described above, in the hermetic compressor of this embodiment, a plurality of oils are provided on at least one of the end faces of the bearing washers 19a and 19b on the side opposite to the cylinder side or the bottom faces of the circular grooves provided on the main bearing 26 and the sub bearing 27. Since the reservoir 24 is provided, it is possible to supply lubricating oil to the entire sliding portion of the bearing washers 19a and 19b and the circular grooves 25a and 25b, and to lubricate the sliding portion immediately after starting the compressor. The reliability of the sliding part is improved.

[0048]

As described above, according to the present invention, the roller that eccentrically rotates in the cylinder, and the vane that reciprocates in the groove of the cylinder and contacts the roller to divide the inside of the cylinder into the suction chamber and the compression chamber. A main bearing and a sub-bearing each having a circular groove on an end surface on the cylinder side fixed to both ends of the cylinder, and a shaft that rotationally slides in the main bearing and the sub-bearing,
As the bearing washer is rotatably housed in the circular groove of the main bearing and the sub bearing, even if the shaft rotates at high speed by an inverter, etc. The rise can be suppressed, and the increase in sliding heat generation can be suppressed. Therefore, it is possible to prevent a decrease in the sealing property between the inner circumference of the roller and the suction chamber and the compression chamber due to a decrease in the viscosity of the lubricating oil on the end surface of the roller, and prevent a decrease in volume efficiency due to a leak from the end surface of the roller. By suppressing an increase in the relative speed of the moving part, it is possible to prevent an increase in wear of the sliding parts of the roller and the bearing washer.

Further, it comprises a communication hole having one end communicating with the bottom surface of the circular groove, and a communication pipe having one end joined to the other end of the communication hole and the other end communicating with the lubricating oil stored in the closed casing. Therefore, the relative speed with the end surface of the roller can be reduced by smooth rotation of the bearing washer, and the circular groove,
It is possible to prevent wear on the end faces of the bearing washer and roller. Further, it is possible to prevent the lubricating oil from flowing into the suction chamber or the like through the main bearing, the sub bearing, the bearing washer, the end surface of the roller, etc., and prevent the volumetric efficiency from decreasing and the input from increasing.

In the hermetic compressor of this embodiment, one end is connected with a communication hole communicating with the bottom surface of the circular groove, and the other end is connected with a communication pipe communicating with the lubricating oil accumulated in the hermetic casing. Since it is composed of the communication path in the cylinder side wall at least 90 ° or more in the anti-compression direction from the vane, the cylinder can be cooled, the overheating of the refrigerant by the cylinder can be reduced, and the volume efficiency of the compressor can be improved. it can.

Since the hermetic compressor of this embodiment is constituted by a plurality of oil reservoirs on at least one of the end surface of the bearing washer on the side opposite to the cylinder side and the bottom surface of the circular groove provided in the main bearing and the sub bearing, Lubricating oil can be supplied to the entire sliding part of the bearing washer and the circular groove, and local wear of the sliding part can be prevented,
The sliding part can be lubricated immediately after the compressor is started, and the reliability of the sliding part is improved.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a first embodiment of a hermetic compressor according to the present invention.

FIG. 2 is a cross-sectional view of the main part of the embodiment.

FIG. 3 is a sectional view taken along line BB of FIG.

FIG. 4 is a sectional view of the essential parts of a second embodiment of the hermetic compressor according to the present invention.

FIG. 5 is a sectional view of the essential parts of a third embodiment of the hermetic compressor according to the present invention.

FIG. 6 is a front view of a fourth embodiment of the hermetic compressor according to the present invention.

FIG. 7 is a vertical sectional view of a conventional hermetic compressor.

8 is a sectional view taken along line AA of FIG. 7;

[Explanation of symbols]

 1 Airtight casing 1a Refrigerant gas space 3 Shaft 4 Cylinder 4a Cylinder groove 5 Roller 6 Vane 11a Suction chamber 11b Compression chamber 18 Lubricating oil 19a, 19b Bearing washer 20, 21 Contact hole 22, 23 Contact pipe 24 Oil sump 25a, 25b Circular Groove 26 Main bearing 27 Sub bearing 28, 29 Cylinder side wall communication passage

Claims (4)

[Claims] 1. A hermetic casing having a refrigerant gas space, and lubricating oil stored in a lower portion of the hermetic casing,
A cylinder housed in the closed casing, a roller that eccentrically rotates in the cylinder, and a vane that reciprocates in a groove of the cylinder and contacts the roller to divide the cylinder into an intake chamber and a compression chamber. A main bearing and a sub-bearing fixed to both ends of the cylinder and provided with circular grooves on the end face on the cylinder side, a shaft that rotationally slides in the main bearing and the sub-bearing, and a circular shape of the main bearing and the sub-bearing. Hermetic compressor with bearing washer rotatably housed in the groove. 2. A communication hole having one end communicating with the bottom surface of the circular groove, and a communication pipe having one end joined with the other end of the communication hole and the other end communicating with the lubricating oil stored in the closed casing. The hermetic compressor according to claim 1. 3. A communication hole, one end of which communicates with the bottom surface of the circular groove, and the other end of which is connected with a communication pipe which communicates with the lubricating oil stored in the closed casing, and at least 90 ° in the anti-compression direction from the vane. The hermetic compressor according to claim 1, comprising the communication passage in the cylinder side wall. 4. The hermetic compressor according to claim 1, wherein a plurality of oil reservoirs are provided on at least one of the end surface of the bearing washer on the side opposite to the cylinder or the bottom surface of the circular groove provided in the main bearing and the sub bearing.