JP2002250292A - Closed type rotary compressor and refrigeration/air- conditioning device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a closed type rotary compressor and a refrigeration/air- conditioning device with a high performance and a high reliability by making a pressure in a closed container to a lower pressure than a discharge pressure and discharging a refrigerant gas leaked from a compression chamber into the closed container without interfering it with a lubricating oil to certainly feeding the refrigerant gas to a bearing slide part. SOLUTION: The pressure in the closed container 6 is made to a lower pressure than a discharge pressure of a compression element and a refrigerant gas discharge passage 4c communicated with the inside of the closed container 6 is formed on a driving shaft 4. A refrigerant gas communication passage 4b radially outwardly extending from the refrigerant gas discharge passage 4c and communicating with a gap in a roller 8a is formed on an eccentric part 4a of the driving shaft 4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic rotary compressor and a refrigeration / air-conditioning apparatus, and more particularly to a hermetic rotary compressor and a refrigeration / air-conditioning apparatus in which the pressure in an airtight container is lower than the discharge pressure. Things.

[0002]

2. Description of the Related Art Conventionally, refrigerators such as refrigerators and refrigerators,
Rotary compressors used in refrigeration and air conditioning systems such as air conditioners such as room air conditioners and packaged air conditioners
An electric element having a stator and a rotor and a compression element driven by the electric element are housed in a sealed container, and a roller rotatably fitted to an eccentric portion of a drive shaft constituting the compression element is driven by a drive shaft. Rotation of the cylinder causes eccentric rotational movement in the cylinder, partitions the interior of the cylinder into a suction chamber and a compression chamber by the vane pressed by the roller, and the refrigerant gas sucked into the suction chamber from the suction pipe by the rotation of the roller in the compression chamber. The compressed and compressed refrigerant gas is discharged into a closed container, and further discharged from a discharge pipe to an external refrigeration cycle. In the rotary compressor configured as described above, the inside pressure of the sealed container is often set to the discharge pressure in order to increase the back pressure of the vane pressed against the roller (prior art 1).

Further, as a rotary compressor in which the suction pressure is set in a closed container, for example, a rotary compressor disclosed in Japanese Patent Application Laid-Open No. H8-247062 (prior art 2) has been proposed. Such a rotary compressor is of a low-pressure type that sucks intake gas into a closed case. The lubricating oil is sent out by a vane pump provided along the oil supply path at the lower end of the center of the shaft, and is supplied to each sliding portion such as a crank chamber, a main bearing, and a sub-bearing. The lubricating oil is supplied to the side by a communication passage communicating with the crank chamber. Further, the refrigerant gas foamed in the lubricating oil in the oil supply passage provided at the center of the shaft is discharged upward through a vent hole formed by extending from the oil supply passage. Further, the high-pressure refrigerant gas leaked into the roller from the compression chamber does not enter the sliding portion of the bearing,
The gas is discharged from a communication passage connecting the crank chamber and the suction side of the cylinder, or a gas discharge passage connecting the crank chamber and the inside of the closed container.

[0004]

However, in the rotary compressor of the prior art 1, since the inside of the sealed container is set to a high temperature and a high discharge pressure, the oil leaking from the inner surface of the roller into the suction chamber due to the differential pressure is excessive. This causes a decrease in compressor performance due to heating loss and the like, and a decrease in reliability and motor efficiency due to an increase in coil temperature of the electric element. In addition, when the compressor is operated intermittently, when the compressor is stopped, high-temperature, high-pressure gas in the closed vessel flows back into the evaporator, raising the temperature of the evaporator and reducing the performance of the refrigeration / air-conditioning system. Was invited. Furthermore, when using a natural refrigerant having flammability from the viewpoint of preventing global warming, it is desirable to reduce the amount of refrigerant used in the refrigeration cycle,
As the ambient pressure of the oil increases, the amount of refrigerant dissolved in the oil increases, so when the pressure inside the closed container is high, the amount of refrigerant used increases, and foaming phenomena occur in bearings and the like, and reliability increases. Was caused. In addition, since it is necessary to increase the pressure resistance of the closed container, it is necessary to increase the thickness of the closed container, which increases the weight.

On the other hand, in the rotary compressor of the prior art 2,
The high-pressure refrigerant gas leaked from the compression chamber into the crank chamber
When the oil is discharged from the communication passage connecting the crank chamber and the suction side of the cylinder, there is a problem that the oil is excessively supplied to the suction chamber because the crank chamber and the suction chamber are always in communication. Further, when the refrigerant gas is discharged from the gas discharge path communicating between the crank chamber and the inside of the closed container, when the refrigerant gas is discharged from the gas discharge path by centrifugal force, the lubricating oil in the crank chamber may be discharged together. There is. As a result, there is a possibility that the amount of lubrication to each sliding portion such as the crank chamber, the main bearing, and the sub-bearing may be insufficient, resulting in poor lubrication.

SUMMARY OF THE INVENTION It is an object of the present invention to make the pressure in the closed vessel lower than the discharge pressure, and to discharge the refrigerant gas leaking from the compression chamber into the closed vessel without interfering with the lubricating oil. It is an object of the present invention to provide a high-performance and highly reliable hermetic rotary compressor and a refrigerating / air-conditioning apparatus that can supply oil to a moving part.

Another object of the present invention is to make the pressure in the closed container lower than the discharge pressure, and to discharge the refrigerant gas leaking from the compression chamber to the inner surface of the roller into the closed container without interfering with the lubricating oil. In addition, the refrigerant gas generated in the lubrication groove formed in the bearing sliding part can be easily discharged by sharing the discharge path, and high performance and reliability that can reliably lubricate the bearing sliding part with a simple configuration An object of the present invention is to provide a high hermetic rotary compressor.

Another object of the present invention is to set the inside of the closed vessel at an intermediate pressure between the discharge pressure and the suction pressure and discharge the refrigerant gas leaking from the high-pressure compression chamber into the closed vessel without interfering with the lubricating oil. It is an object of the present invention to provide a hermetic type rotary compressor capable of performing a two-stage compression with high performance and high reliability, which can reliably lubricate a bearing sliding portion.

[0009]

In order to achieve the above object, a typical hermetic rotary compressor of the present invention includes an electric element in a closed container and a compression element connected to the electric element. A cylinder chamber is formed by closing both ends of the cylinder of the compression element with an end plate, and a drive shaft is supported by a main bearing and a sub bearing provided in the end plate, and is fitted to an eccentric portion formed on the drive shaft. A roller is disposed in the cylinder chamber, and the rotation of the drive shaft revolves the roller in the cylinder chamber to compress the refrigerant gas. In a hermetic rotary compressor that supplies lubricating oil accumulated in a bearing sliding portion of the drive shaft to a pressure lower than a discharge pressure of the compression element in the hermetic container, a refrigerant gas communicates with the hermetic container. And forming the drive shaft Detchi, in which the refrigerant gas communication passage communicating with the void of said roller extends radially outwardly from the refrigerant gas discharge passage formed in the eccentric portion.

In order to achieve the above object, a typical hermetic rotary compressor of the present invention includes an electric element in a closed container and a compression element connected to the electric element, and a cylinder of the compression element. The openings at both ends are closed by an end plate to form a cylinder chamber, the main shaft and the auxiliary bearings provided on the end plate support the drive shaft, and the roller fitted to the eccentric portion formed on the drive shaft is Lubrication that is disposed in a cylinder chamber, compresses refrigerant gas by revolving the rollers in the cylinder chamber by rotation of the drive shaft, and accumulates in the bottom of the sealed container by the action of an oil supply pump due to rotation of the drive shaft. In a hermetic rotary compressor having an oil supply groove for supplying oil to a bearing sliding portion of the drive shaft, a pressure inside the hermetic container is set lower than a discharge pressure of the compression element, and a refrigerant communicates with the hermetic container. A discharge passage is formed on the drive shaft, and extends radially outward from the refrigerant gas discharge passage to communicate with a gap between the eccentric portion and the end plate in the roller and from the refrigerant gas discharge passage. A refrigerant gas communication passage extending radially outward and communicating with the oil supply groove is formed in the eccentric portion.

In order to achieve the above-mentioned another object, an electric element and a compression element connected to the electric element are provided in a closed container, and this compression element is composed of two parts, a low-pressure compression element and a high-pressure compression element. Each compression element is constituted by a compression element, and both ends of the cylinder of each compression element are closed with an end plate to form a cylinder chamber of each compression element, and the drive shaft is axially supported by a main bearing and an auxiliary bearing provided on the end plate. By disposing rollers fitted to the eccentric portions of the compression elements formed on the drive shaft in the cylinder chambers of the compression elements, and by rotating the drive shaft, the rollers revolve in the cylinder chambers. Refrigerant gas 2
In the hermetic rotary compressor, which compresses the oil into a stage and lubricates the bearing sliding portion of the drive shaft with lubricating oil accumulated in the bottom of the hermetic container by the action of an oil supply pump due to the rotation of the drive shaft, An intermediate pressure between the discharge pressure and the suction pressure of the compression element, a refrigerant gas discharge path communicating with the inside of the closed container is formed on a drive shaft, and the refrigerant gas discharge path extends radially outward from the refrigerant gas discharge path and is And a refrigerant gas communication passage communicating with a gap in the roller of the compression element is formed at an eccentric portion of the high-pressure compression element.

[0012]

Embodiments of the present invention will be described below with reference to the drawings. In the second and subsequent embodiments, some of the components common to the first embodiment are omitted, and
A duplicate description will be omitted. The same reference numerals in the drawings of the respective embodiments indicate the same or corresponding components.

First, a first embodiment of the present invention will be described with reference to FIGS.
This will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of a horizontal type swinging piston type compressor according to a first embodiment of the present invention, FIG. 2 is a sectional view taken along line AA of FIG. 1, and FIG. FIG. 4 is an enlarged view of a main part of the compressor of FIG. 1, and FIG. 5 is a view of the drive shaft of FIG.

In the oscillating piston type compressor of the present invention, an electric element, a compression element, and a drive shaft 4 for connecting both the electric element and the compression element are arranged in a closed container 6, and a suction pressure lower than a discharge pressure in the closed container 6. And The electric element has a stator 7 and a rotor 5. The compression element has a compression mechanism and an oil supply mechanism. The compression mechanism includes a cylinder 1, a piston 8 rotatably arranged in the cylinder 1, a main bearing 2 and a sub-bearing 3 for closing both ends of the cylinder 1. The lubrication mechanism includes a hole 1c of the cylinder 1,
It comprises a vane portion 8b, a suction fluid diode 17, a discharge fluid diode 18, an oil supply pipe 19, a spiral groove 20, an oil pocket 21, and the like.

The cylinder 1 has a cylinder chamber having a cylindrical inner peripheral surface 1a at the center thereof. Openings at both ends are closed by a main bearing 2 and a sub-bearing 3 which constitute end plates. The main bearing 2 and the sub-bearing 3 have bearing portions 2a, 3a formed in the center, respectively, and rotatably support the drive shaft 4. The main bearing 2 and the sub-bearing 3 are arranged such that the rotating shaft of the driving shaft 4 which is supported is a cylindrical inner peripheral surface 1 a of the cylinder 1.
Is fixed to the cylinder 1 so as to coincide with the central axis of the cylinder 1. Further, the outer peripheral portion of the main bearing 2 is fixed to the closed container 6. In addition, since the thrust bearing portion 4h is formed on the main bearing side of the eccentric portion 4a, a gap is formed between the eccentric portion 4a and the main bearing 2 located radially outward. The oil pocket 21 is formed in the gap. The rotor 5 of the electric element is fixed to the drive shaft 4, and the stator 7 of the electric element is fixed to the closed casing 6 so as to be coaxial with the rotor 5.

The drive shaft 4 has an eccentric portion 4a formed in a portion located within the cylindrical inner peripheral surface 1a of the cylinder 1. The eccentric portion 4a is provided with the roller portion 8a of the swing piston 8.
Is rotatably fitted in the cylindrical inner peripheral surface of the first member. The roller portion 8a is rotatably housed in the cylindrical inner peripheral surface 1a of the cylinder 1, and its cylindrical outer peripheral surface and the cylinder 1
The dimensions of each part are determined so that the gap between the inner peripheral surface 1a and the inner peripheral surface 1a becomes very small.

The oscillating piston 8 has a roller portion 8a
A vane portion 8b is integrally formed so as to protrude radially from the cylindrical outer peripheral surface. That is, the cylinder 1 communicates with the outside of the cylindrical inner peripheral surface 1a to form a cylindrical hole 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a.
Another hole 1c having a central axis parallel to the central axis of the cylinder 1 and the inner peripheral surface 1a of the cylinder is formed in communication with the outside of the cylindrical hole 1b on the side opposite to the cylinder. The vane 8b is inserted across the cylindrical hole 1b and the hole 1c.

By using the oscillating piston 8 in which the roller portion 8a and the vane portion 8b are integrally formed, the roller portion and the vane portion are separately formed so as to slide while being in contact with each other. The problem of wear due to the contact between the two can be solved.

Between the vane portion 8b and the cylindrical hole portion 1b, a cylindrical portion slidably abutting on the flat surface portion of the vane portion 8b and a cylindrical member slidably abutting on the cylindrical surface portion of the cylindrical hole portion 1b. A sliding member 9 having a surface portion is incorporated so as to sandwich the vane portion 8b. Thereby, the vane portion 8b
Is supported by the cylinder 1 so as to perform a reciprocating motion toward the central axis of the cylindrical hole portion 1b and a swinging motion around the central axis.
The tip of the vane portion 8b moves forward and backward and swings in the hole 1c, and does not come into contact with the cylinder 1.

In the swinging piston type compressor having the above-described structure, when the drive shaft 4 is rotated by the electric element, the swinging piston 8 is rotated together with the rotation of the eccentric portion 4a of the drive shaft 4 as shown in FIG.
As shown in (a) to (f), a revolving motion with swinging is performed in the cylinder 1.

FIGS. 3A to 3F show that the drive shaft 4 is
FIG. 9 is a diagram showing the motion of the swing piston 8 when rotated by degrees. As is apparent from FIG. 3, the roller portion 8a swings by a slight angle around the center axis of the eccentric portion 4a so that the vane portion 8b always faces the center axis direction of the cylindrical hole portion 1b of the cylinder 1. The center revolves while performing. As a result, the vane portion 8b performs a reciprocating motion toward the central axis of the cylindrical hole portion 1b of the cylinder 1 and a oscillating motion around the central axis, but the vane portion 8b and the cylindrical hole portion 1b of the cylinder 1 The gap seal is maintained by the sliding member 9 being inserted. The cylinder 1, the oscillating piston 8, the main bearing 2, the sub-bearing 3, and the sliding member 9 form a compression chamber 10 (a hatched portion in FIG. 3) as a closed space and a suction chamber 11 as a suction space.
3 is formed as the drive shaft 4 is rotated by the electric element.
The increase and decrease of the volume are repeated as shown.

Returning to FIG. 1, a suction pipe 12 is opened through the side surface of the closed vessel 6 located on the compression element side. A suction passage 13 is provided at a position close to the suction pipe 12. The suction passage 13 is always in communication with the suction chamber 12. In addition, this suction passage 13
Is provided eccentrically with the opening of the suction pipe 12, and forms an oil separation mechanism.

With this configuration, the refrigerant gas is sucked into the closed vessel 6 from the suction pipe 12 attached to the closed vessel 6, passes through the suction passage 13, is sucked into the suction chamber 11, and has the capacity of the compression chamber 10. And is discharged simultaneously from the discharge port 3b formed in the sub bearing 3 to the discharge chamber 3c formed by the sub bearing 3 and the discharge cover 14. Thereafter, the compressed refrigerant gas is discharged from the discharge pipe 15 to the outside of the closed vessel 6.

As described above, in this embodiment, particularly, the structure is such that the refrigerant gas that has passed through the suction pipe 12 is once sucked into the closed vessel 6, and the inside of the closed vessel 6 has a suction pressure lower than the discharge pressure. The use of the suction pressure in the closed container 6 has the following advantages. (1) Since the electric element is hardly heated by the compressed high-temperature refrigerant gas and cooled by the low-temperature refrigerant gas, the temperatures of the rotor 5 and the stator 7 are reduced, reliability is improved, and motor efficiency is improved. To improve performance. (2) Since the inside of the roller portion 8a has a suction pressure, the suction chamber 1
2, the supply of excess oil due to the pressure difference to 2 is eliminated, and the heat loss and the like can be reduced, so that the performance of the compressor can be improved. (3) When a refrigerant compatible with oil such as chlorofluorocarbon is used, the pressure in the closed vessel 6 is low, so that the proportion of the refrigerant gas dissolved in the oil decreases, and the refrigerant gas foams in bearings and the like. Is less likely to occur, and the reliability can be improved. In the case of using a flammable natural refrigerant (eg, isobutane, propane, etc.), the amount of refrigerant used is reduced,
Safety can be improved. (4) The pressure resistance of the sealed container 6 can be reduced, and the thickness and weight can be reduced.

Further, in the swinging piston type compressor shown in this embodiment, since the roller portion 8a and the vane portion 8b are integrated, the roller and the vane are separated from each other. There is no need to apply a high back pressure to the vane in order to press the vane, and it is easy to apply to a structure in which the inside of the closed container 6 is set to the suction pressure.

The oil supply mechanism of the compression mechanism in this embodiment will be specifically described.

As shown in FIG. 3, the rotation of the drive shaft 4 causes the vane portion 8b to advance and retreat in the hole portion 1c.
The volume of c changes. The lubricating oil 16 stored at the bottom of the sealed container 6 by the pump action due to the volume change is
As shown in FIG.
As shown by a two-dot chain line arrow in FIGS. 1 and 4, the spiral is pumped up to one end of the drive shaft 4 through the discharge fluid diode 18 and the oil supply pipe 19, and further provided on the outer periphery of the drive shaft 4. Secondary bearing 3 and eccentric part 4 through groove 20
a, Lubricate the main bearing 2 and return to the closed container 6 again. Here, even if the spiral groove 20 is provided on the main bearing 2 and the sub-bearing 3 side, the same operation is obtained.

The lubricating oil 16 which lubricates the eccentric portion 4a
3 flows out into the roller portion 8a, and as shown in FIG. 3, flows into the suction chamber 11 by the oil pocket 21 provided on the end face of the main bearing 2 which alternately moves between the suction chamber 11 and the roller portion 8a. Supplied. That is, as shown by the solid arrows in FIGS. 3A and 3B, the lubricating oil is filled in the oil pocket 21 in a state where the oil pocket 21 is located in the roller portion 8a. The lubricating oil is supplied from the oil pocket 21 into the suction chamber 11 in a state where the oil pocket 21 is located in the suction chamber 11 as indicated by the solid arrow in ()). In this manner, an appropriate amount of lubricating oil can be supplied to the suction chamber 11 by the operation of the positive displacement pump without depending on the differential pressure, so that the heating loss and the like can be reduced. Here, the same action can be obtained even if the oil pocket 21 is provided on the end face side of the auxiliary bearing 3.

As shown by a solid arrow in FIG. 4, the refrigerant gas bubbled from the lubricating oil 16 passing through the spiral groove 20 and the high-pressure refrigerant gas leaked from the compression chamber 10 into the roller portion 8a are connected to the refrigerant gas passage. The gas is discharged into the closed container 6 through a gas discharge hole 4c formed inside the drive shaft 4 through a gas vent hole 4b constituting a passage. As a result, the amount of refrigerant gas in the bearing sliding portion of the drive shaft 4 can be reduced, and the reliability of the bearing sliding portion can be improved. In particular, since the discharge passages 4b and 4c for the refrigerant gas leaking into the roller portion 8a and the spiral groove 20 of the bearing sliding portion are configured independently, the discharge of the refrigerant gas and the lubricating oil of the bearing sliding portion are performed. The function can be ensured without interference with the supply. The gas discharge holes 4c constitute a refrigerant gas discharge path,
The drive shaft 4 extends from the center of the eccentric portion 4a along the axis of the drive shaft 4 and opens at the end face on the electric element side. The gas vent hole 4b is formed as an independent communication passage extending radially outward from the gas discharge hole 4c in the eccentric portion 4a and communicating with the gap in the roller portion 8a and the spiral groove 20.
In addition, the gas vent hole 4b is opened to a gap outside the thrust bearing portion 4h on the main bearing side of the eccentric portion 4a, and is opened to a space on the opposite side to communicate with each other.

Here, the inside of the roller portion 8a contains the refrigerant gas leaking from the compression chamber 10 and the lubricating oil 1 that lubricates the eccentric portion 4a.
6 coexist, and the difference in density between the lubricating oil and the refrigerant gas due to the centrifugal force caused by the rotation of the drive shaft 4 causes the high-density lubricating oil to be located outside and the low-density refrigerant gas to be located inside. Almost only the refrigerant gas can be discharged from the gas discharge hole 4c formed inside the drive shaft 4 through the gas vent hole 4b, so that the high-pressure refrigerant gas can be prevented from entering the bearing sliding portion. . In addition, when the refrigerant gas is discharged, oil supply to the suction chamber 11 required for the internal seal by the oil pocket 21 is not hindered by the refrigerant gas, and an appropriate lubricating oil supply into the cylinder 1 is realized. Internal leakage can be suppressed.

The gas vent hole 4b is formed so as to communicate with the gap between both sides of the eccentric portion 4a and the main bearing 2 and the sub bearing 3, so that the refrigerant gas leaking into the roller portion 8a is formed. Can be reliably and quickly discharged from both sides of the eccentric portion 4a.

Further, the gas vent hole 4b is formed so as to communicate with a gap between the eccentric portion 4a formed outside the thrust bearing 4h formed on one side of the eccentric portion 4a and the main bearing 2. Therefore, the refrigerant gas on the thrust bearing side leaked into the roller portion 8a can be reliably and quickly discharged.

Moreover, it extends radially outward from the gas discharge hole 4c, communicates with the gap between the eccentric portion 4a in the roller portion 8a and the main bearing 2 and the sub bearing 3, and extends radially outward from the gas discharge hole 4c. The gas vent hole 4b extending toward the spiral groove 20 and communicating with the spiral groove 20 is formed in the eccentric portion 4a.
The refrigerant gas leaked into the roller portion 8a and the refrigerant gas generated in the spiral groove 20 can be easily discharged through the common gas discharge hole 4c, and the bearing sliding portion can be reliably supplied with a simple configuration. .

A gas vent hole 4b extending radially outward from the gas discharge hole 4c and communicating with an eccentric portion 4a in the roller portion 8a, a gap between the main bearing 2 and the sub bearing 3, and a gas discharge hole 4c. Since the gas vent hole 4b extending radially outward and communicating with the spiral groove 20 is formed independently, the refrigerant gas on the inner surface of the roller portion 8a and the refrigerant gas foamed from the lubricating oil in the spiral groove 20 are separated. Can be pulled out to the gas discharge hole 4c without interference.

As described above, by adopting the structure of the present embodiment, the inside of the sealed container 6 is set to the suction pressure,
0, the discharge passages 4b and 4c for discharging the refrigerant gas leaked into the roller portion 8a into the closed container 6 and the spiral groove 20 for lubricating the bearing sliding portion can be separated, and the refrigerant gas and the lubricating oil interfere with each other. Therefore, reliable lubrication to each sliding portion is possible, and a high-performance and highly reliable swinging piston type compressor can be provided.

Next, a second embodiment of the present invention will be described with reference to FIGS.
This will be described with reference to FIG. FIG. 6 is a longitudinal sectional view of a main part of a horizontal type swinging piston type compressor according to a second embodiment of the present invention, and FIG. 7 is a view of the drive shaft section in FIG.

In the present embodiment, the refrigerant gas discharge passage is the same as that described in the first embodiment, but differs mainly in the oil supply passage. Hereinafter, the oil supply mechanism of the present embodiment will be described.

The lubricating oil 16 supplied through the oil supply pipe 19 by the same pumping action as described in the first embodiment is applied to the hole 4d formed inside the drive shaft 4 (the center of one end).
Through the oil outflow hole 4e formed to extend radially outward of the drive shaft 4 from the hole 4d.
The auxiliary bearing 3, the eccentric portion 4 a, and the main bearing 2 are lubricated by being guided to the groove 4 f formed on the side and passing through the spiral groove 20 formed on the side of the main bearing 2. Here, since the lubricating oil 16 passing through the oil outflow hole 4e is subjected to centrifugal force due to the rotation of the drive shaft 4, the amount of lubricating oil increases, and stable lubricating oil can be supplied to each sliding portion.

With the above arrangement, the discharge passages 4b, 4c for discharging the refrigerant gas leaking into the roller portion 8a from the compression chamber into the closed container by setting the inside of the closed container to the suction pressure.
And lubrication oil passages 4f and 20 for lubricating the bearing sliding portion and the like can be separated so that the refrigerant gas and the lubricating oil do not interfere with each other, and when the lubricating oil 16 passes through the oil outflow hole 4e, the drive shaft 4 Since the centrifugal force due to the rotation is given, the amount of lubrication increases, and the lubrication of each sliding part is made possible. Thus, a swinging piston type compressor with high performance and high reliability can be provided.

Next, a third embodiment of the present invention will be described with reference to FIGS.
Explanation will be made using 0. FIG. 8 is a longitudinal sectional view of a vertically mounted swinging piston type compressor according to a third embodiment of the present invention, and FIG.
FIG. 10 is an enlarged view of a main part of the compressor of FIG. 8.

The compression operation of the vertical oscillating piston type compressor of this embodiment is the same as that of the horizontal oscillating piston type compressor of the first embodiment, except that the lubricating oil stored in the lower portion of the closed vessel 6 The lubricating structure before pumping 16 to the drive shaft 4 is mainly different.

Refueling piece 4 mounted on lower end of drive shaft 4
g is immersed in the lubricating oil 16 in the closed container 6. As shown in FIG. 10, the lubricating oil 16 stored in the bottom of the sealed container 6 has a smaller diameter than the hole 4 d of the drive shaft 4 due to the centrifugal pump action by the rotation of the drive shaft 4. The oil is sucked from the oil supply piece 4g having an opening and is supplied to the oil outflow hole 4e and the spiral groove 20 formed in the drive shaft 4 to lubricate each sliding portion.

The lubricating oil 16 passing through the spiral groove 20
The high pressure refrigerant gas leaked into the roller portion 8a from the compression chamber 10 passes through the gas vent hole 4b to reach the gas discharge hole 4c formed inside the drive shaft 4, and this gas flows. It is discharged from the end of the drive shaft 4 into the closed container 6 through the discharge hole 4c.

In the case of a vertical compressor, the supply direction of the lubricating oil 16 to each sliding portion is opposite to the gravity, so that the lubricating amount is insufficient and lubrication failure is likely to occur. When the lubricating oil 16 passes through the oil outflow hole 4e, centrifugal force is given by the rotation of the drive shaft 4, so that the amount of lubrication increases, and the viscous pumping action of the spiral groove 20 causes the auxiliary bearing 3,
Since the eccentric portion 4a and the main bearing 2 are supplied, the lubricating oil 16 can be stably supplied to each sliding portion even in the case of a vertical compressor.

Next, a fourth embodiment of the present invention will be described with reference to FIGS. FIG. 11 is a vertical sectional view of a horizontal type two-cylinder rotary compressor according to a fourth embodiment of the present invention.
FIG. 12 is an enlarged view of a main part of the compressor of FIG. 11.

In this embodiment, the cylinders 22a,
2b has cylindrical inner peripheral surfaces 22c and 22d at the center, respectively.
Are formed, and the partition plate 23 is provided with the openings at both ends in the middle.
Are closed by the main bearing 24 and the sub-bearing 25. In addition, the partition plate 23, the main bearing 24, and the sub bearing 25
It constitutes an end plate for the cylinders 22a and 22b. The main bearing 24 and the sub-bearing 25 are formed with bearing portions 24a and 25a at the center, respectively.
6 is rotatably supported. The main bearing 24 and the sub-bearing 25 are configured such that the rotation shaft of the drive shaft 26 is a cylinder 22a,
They are fixed to the cylinders 22a and 22b, respectively, so as to coincide with the central axes of the cylindrical inner peripheral surfaces 22c and 22d of the cylinder 22b. The rotor 5 of the electric element is fixed to the drive shaft 26. The outer periphery of the main bearing 24 is fixed to the closed container 6, and the stator 7 of the electric element is fixed to the closed container 6.

The drive shaft 26 has cylinders 22a, 22b
The eccentric portion 2 is provided at the portion corresponding to the cylindrical inner peripheral surfaces 22c and 22d of
6a and 26b are formed. The eccentric portions 26a, 2
The cylindrical inner peripheral surfaces of the rollers 27a and 27b are rotatably fitted to the cylindrical outer peripheral surface of 6b. Rollers 27a, 2
The dimensions of each part are determined so that the gap between the cylindrical outer peripheral surface of 7b and the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b is very small. Also, rollers 27a, 27b
The vanes 28a and 28b have springs 29 on the cylindrical outer peripheral surface thereof.
a, 29b. Cylinder 22a,
A vane slot (not shown) is formed outside the cylindrical inner peripheral surfaces 22c and 22d of the vane 22b.
a and 28b are inserted into the vane slots. As a result, the vanes 28a and 28b move inside the vane slots in the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b.
Perform a forward / backward movement toward the central axis of.

With the above configuration, when the drive shaft 26 is rotated by the electric element, the rollers 27a and 27b revolve with the eccentric portions 26a and 26b. Due to this orbital movement, the refrigerant gas is sucked into the closed vessel 6 from the suction pipe 12 attached to the closed vessel 6, passes through the suction passage 13, and is sucked into the cylinders 22a and 22b, and the volume of the compression chamber decreases. At the same time, the refrigerant gas sucked into the cylinder 22a flows through the discharge port 30a formed in the main bearing 24 from the main bearing 24 and the discharge cover 31.
The refrigerant gas discharged to the discharge chamber 32a formed by the sub-a is discharged from the discharge port 30b formed in the sub-bearing 25 to the discharge chamber 32b formed by the sub-bearing 25 and the discharge cover 31b. Is discharged. Thereafter, the refrigerant gas discharged to both the discharge chambers 32a and 32b merges and is discharged to the outside of the compressor from the discharge pipe 15 attached to the closed container 6.

In the case of the rotary compressor in which the inside of the closed vessel 6 has a suction pressure in this embodiment, the vanes 28a and 28b are connected to the rollers 27a and 27b as in the case where the inside of the closed vessel 6 is set to a high pressure.
Since there is no back pressure for pressing the springs 29a,
It is necessary to increase the force for pressing the vane against the roller, for example, by increasing the spring force of 9b.

The oil supply mechanism of the compression mechanism of this embodiment will be described. 11 and 12, the drive shaft 26
, The vane 28b moves forward and backward in a vane slot (not shown), and the volume of the space 22e in which the spring 29b is mounted changes. The lubricating oil 16 stored at the bottom of the sealed container 6 by the pumping action due to the change in volume,
The main bearing 24, the sub bearing 25, and the eccentric portions 26a, 26b are sucked from the fluid diode 33, pumped up to the drive shaft 26 through the oil supply pipe 19, and passed through the spiral groove 20 provided on the outer periphery of the drive shaft 26. Lubricate and return to the closed container again. Lubricating oil 1 lubricating eccentric portions 26a, 26b
A part of 6 is supplied to the suction chamber in the same manner as in the oil pocket system described in the first embodiment. Here, the same action can be obtained regardless of whether the oil pocket is provided on the end face of the main bearing 24, the end face of the auxiliary bearing 25, or the end face of the partition plate 23.

The refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 and the high-pressure refrigerant gas leaked from the compression chamber to the inner surfaces of the rollers 27a and 27b are separated from the gas vent holes 34a and 3b.
The gas is discharged into the closed container 6 through the gas discharge hole 4c formed in the drive shaft 26 through the drive shaft 4b. Here, in the rollers 27a and 27b, the refrigerant gas leaked from the compression chamber 10 and the lubricating oil 16 that lubricates the eccentric portions 26a and 26b coexist, and the centrifugal force generated by the rotation of the drive shaft 26 causes the lubricating oil and the refrigerant to flow. Due to the gas density difference, the high-density lubricating oil is located outside and the low-density refrigerant gas is located inside. Therefore, almost only the refrigerant gas is formed inside the drive shaft 26 through the gas vent holes 34a and 34b. The gas can be discharged from the gas discharge hole 4c, and in this case, the internal leakage can be suppressed without obstructing the oil supply to the suction chamber required for the internal seal by the oil pocket.

With the above structure, the discharge passages 34a, 34b, 4c for discharging the refrigerant gas leaked from the compression chamber into the rollers 27a, 27b into the closed container 6 and the sliding parts such as bearings are lubricated. To provide a high-performance and highly reliable rotary compressor, because the spiral groove 20 can be separated from the groove and the refrigerant gas and the lubricating oil do not interfere with each other, so that each sliding portion can be reliably supplied with oil. Can be.

Next, a fifth embodiment of the present invention will be described with reference to FIGS. FIG. 13 is a longitudinal sectional view of a horizontal type swinging piston type two-stage compressor according to a fifth embodiment of the present invention.
FIG. 14 is an enlarged view of a main part of the compressor of FIG. 13.

In this embodiment, the compression element 35 comprises a low-pressure compression element 35a and a high-pressure compression element 35b. Openings at both ends of the cylinders 1 ′, 1 ″ of each of the compression elements 35 a, 35 b are connected to the main bearing 24
And the auxiliary bearing 25 and the partition plate 23.
The main bearing 24, the sub-bearing 25 and the partition plate 23 constitute an end plate for the cylinders 1 'and 1 ". The compression operation of the oscillating piston type compressor of this embodiment has been described in the first embodiment. Although it is basically the same as the case of the oscillating piston compressor, the flow of the refrigerant gas is different mainly.

The refrigerant gas enters the cylinder 1 'of the low-pressure compression element 35a through the suction pipe 36 attached to the closed vessel 6, and is compressed. The compressed refrigerant gas passes through a discharge port 30 a formed in the main bearing 24 and is discharged into the closed container 6 through a discharge silencer 41. The refrigerant gas discharged into the closed container 6 is discharged from the discharge pipe 37 to the outside, is radiated by the intercooler 38, is cooled, and then passes through the suction pipe 39 into the cylinder 1 ″ of the high-pressure compression element 35b. The compressed refrigerant gas enters the discharge chamber 32b through a discharge port 30b provided in the sub-bearing 25, and flows out of the compressor through a discharge pipe 40 therefrom.

The oil supply mechanism of the compression mechanism of this embodiment will be described. 13 and 14, the drive shaft 26
, The vane portion 8b ″ of the high-pressure compression element 35b
Moves forward and backward in the hole 1c, and the volume of the hole 1c changes. The lubricating oil 16 stored at the bottom of the sealed container 6 is sucked from the fluid diode 33 by the pump action due to the change in volume, pumped up to the drive shaft 26 through the oil supply pipe 19, and provided on the outer periphery of the drive shaft 26. The auxiliary bearing 25, the eccentric portions 26a and 26b, and the main bearing 24 are lubricated through the spiral groove 20 and returned into the closed container 6 again. Part of the lubricating oil 16 that has lubricated the eccentric portion 26a of the low-pressure compression element 35a is supplied to the suction chamber by the differential pressure between the roller portion 8a 'and the suction chamber, while the eccentric portion 26b of the high-pressure compression element 35b is removed. A part of the lubricating oil 16 is supplied to the suction chamber in the same manner as in the oil pocket system described in the first embodiment. here,
The same action can be obtained regardless of whether the oil pocket is provided on the end face of the auxiliary bearing 25 or the end face of the partition plate 23.

Refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 is guided to gas exhaust holes 4c formed inside the drive shaft 26 through gas vent holes 34a and 34b.
The high-pressure refrigerant gas leaked into the roller portion 8a ″ from the compression chamber of the high-pressure compression element 35b is guided to the gas discharge hole 4c through the gas vent hole 34b, and then these refrigerants pass through the gas discharge hole 4c. The drive shaft 26 is discharged from one end of the drive shaft 26 into the closed container 6.

Here, in the roller portion 8a ″ of the high-pressure compression element 35b, the refrigerant gas leaking from the compression chamber 10 and the lubricating oil 16 that lubricates the eccentric portion 26b coexist. Due to the centrifugal force caused by the density difference between the lubricating oil and the refrigerant gas, the high-density lubricating oil is positioned outside and the low-density refrigerant gas is positioned inside, so that almost only the refrigerant gas is driven through the vent hole 34b. It can be discharged from the gas discharge hole 4c formed inside the shaft 26, and can prevent high-pressure refrigerant gas from entering the bearing sliding portion. It is possible to realize an appropriate supply of lubricating oil into the cylinder and to suppress internal leakage without obstructing oil supply by an oil pocket to a suction chamber required for an internal seal.

With the above arrangement, the discharge passages 34b and 4c for discharging the refrigerant gas leaked from the compression chamber into the roller portion 8a "into the closed container 6 and the spiral groove for lubricating the bearing sliding portion. 20 can be separated from each other, and there is no interference between the refrigerant gas and the lubricating oil, so that reliable lubrication to each sliding part is possible, and a high performance and highly reliable horizontal swinging piston type two-stage compressor. Can be provided.

Next, a sixth embodiment of the present invention will be described with reference to FIG. FIG. 15 is a configuration diagram of a refrigeration cycle of a refrigeration apparatus according to a sixth embodiment of the present invention. This refrigeration cycle is an example of a cycle dedicated to refrigeration (cooling).

In FIG. 15, the refrigeration cycle is formed by connecting a hermetic rotary compressor 45, a condenser 42, an expansion valve 43 constituting a pressure reducing device, and an evaporator 44 by piping.
The condenser fan 42a forcibly blows air to the condenser 42, and the evaporator fan 44a forcibly blows air to the evaporator 44.

By starting the hermetic rotary compressor 45, the high-temperature and high-pressure working gas compressed by the hermetic rotary compressor 45 flows into the condenser 42 from the discharge pipe 15 as shown by a solid line arrow. Then, heat is radiated and liquefied by the blowing action of the condenser fan 42a, throttled by the expansion valve 43, adiabatically expanded to a low temperature and low pressure, and absorbed and gasified by the evaporator 44 by the blowing action of the evaporator fan 44a. , Suction pipe 12
, And is sucked into the hermetic rotary compressor 45. Then, the hermetic rotary compressor 45 is intermittently operated based on the operation command and the operation state detection signal.

Since such a refrigerating apparatus is equipped with the above-described hermetic rotary compressor 45 of the present invention, a refrigerating system excellent in energy efficiency can be obtained. In particular, since the hermetic rotary compressor 45 of the present invention keeps the inside of the hermetic container at a discharge pressure or lower, the amount of high-temperature and high-pressure refrigerant flowing into the evaporator during intermittent operation can be reduced, and intermittent energy loss can be reduced. .

Although a single-stage compressor has been described here, a two-stage compressor can also be mounted, and is applicable not only to a refrigeration system but also to an air conditioner.

[0065]

As described above, according to the present invention,
The pressure inside the closed vessel is lower than the discharge pressure, and the refrigerant gas leaked from the compression chamber can be discharged into the closed vessel without interfering with the lubricating oil. It is possible to provide a hermetic rotary compressor and a refrigeration / air-conditioning device having high performance.

Further, according to the present invention, the inside of the sealed container is set at a pressure lower than the discharge pressure, and the refrigerant gas leaked from the compression chamber to the inner surface of the roller can be discharged into the sealed container without interfering with the lubricating oil. In addition, the refrigerant gas generated in the lubrication groove formed in the bearing sliding part can be easily discharged by sharing the discharge path, and high performance and reliability that can reliably lubricate the bearing sliding part with a simple configuration A high hermetic rotary compressor can be provided.

Further, according to the present invention, the inside of the closed vessel is set at an intermediate pressure between the discharge pressure and the suction pressure, and the refrigerant gas leaking from the high-pressure compression chamber is discharged into the closed vessel without interfering with the lubricating oil. Thus, it is possible to provide a hermetic rotary compressor capable of performing two-stage compression with high performance and high reliability that can reliably lubricate the bearing sliding portion.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a horizontal type swinging piston type compressor according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a diagram illustrating the operation of the compression element of FIG. 2;

FIG. 4 is an enlarged view of a main part of the compressor of FIG. 1;

FIG. 5 is a view of the drive shaft portion in FIG.

FIG. 6 is a vertical sectional view of a main part of a horizontal swing type piston compressor according to a second embodiment of the present invention.

FIG. 7 is a view of the drive shaft section in FIG.

FIG. 8 is a longitudinal sectional view of a vertically mounted swinging piston type compressor according to a third embodiment of the present invention.

FIG. 9 is a sectional view taken along line DD of FIG. 8;

FIG. 10 is an enlarged view of a main part of the compressor of FIG.

FIG. 11 is a longitudinal sectional view of a horizontal type two-cylinder rotary compressor according to a fourth embodiment of the present invention.

FIG. 12 is an enlarged view of a main part of the compressor of FIG. 11;

FIG. 13 is a longitudinal sectional view of a horizontal type swinging piston type two-stage compressor according to a fifth embodiment of the present invention.

FIG. 14 is an enlarged view of a main part of the compressor of FIG.

FIG. 15 is a configuration diagram of a refrigeration cycle of a refrigeration apparatus according to a sixth embodiment of the present invention.

[Explanation of symbols]

1 ... cylinder, 1 '... cylinder, 1 "... cylinder, 1a
... cylindrical inner peripheral surface, 1b ... cylindrical hole, 1c ... hole, 2 ... main bearing, 2a ... bearing, 3 ... auxiliary bearing, 3a ... bearing, 3b
... discharge port, 3c discharge chamber, 4 drive shaft, 4a eccentric part, 4b gas vent hole, 4c gas exhaust hole, 4d hole
4e: oil outflow hole, 4f: groove, 4g: oil supply piece, 5: rotor, 6: sealed container, 7: stator, 8: swinging piston,
8a: Roller part, 8a '... Roller part, 8a "... Roller part, 8b ... Vane part, 8b' ... Vane part, 8b" ... Vane part, 9 ... Sliding member, 10 ... Compression chamber, 11 ... Suction chamber, 1
2 ... suction pipe, 13 ... suction passage, 14 ... discharge cover,
15 discharge pipe, 16 lubricating oil, 17 suction fluid diode, 18 discharge fluid diode, 19 oil supply pipe, 20 spiral groove, 21 oil pocket, 22a,
22b: cylinder, 22c, 22d: cylindrical inner peripheral surface, 2
2e: space, 23: partition plate, 24: main bearing, 24a:
Bearing part, 25 ... sub bearing, 25a ... bearing part, 26 ... drive shaft, 26a, 26b ... eccentric part, 27a, 27b ... roller, 28a, 28b ... vane, 29a, 29b ... spring,
30a, 30b: discharge port, 31a, 31b: discharge cover, 32a, 32b: discharge chamber, 33: fluid diode, 34a, 34b: gas vent hole, 35: compression element, 3
5a: compression element for low pressure, 35b: compression element for high pressure, 36
... Suction pipe, 37 ... Discharge pipe, 38 ... Intercooler,
39 ... suction pipe, 40 ... discharge pipe, 41 ... discharge silencer, 42 ... condenser, 42a ... condenser fan, 43 ...
Expansion valve, 44 ... evaporator, 44a ... evaporator fan, 45 ...
Hermetic rotary compressor.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification code FI Theme coat ゛ (Reference) F04C 29/02 311 F04C 29/02 311E F25B 1/00 387 F25B 1/00 387J 43/02 43/02 D (72) Inventor Isao Hayase 502, Kandachi-cho, Tsuchiura-shi, Ibaraki Pref., Machinery Research Laboratories, Hitachi, Ltd. 3H029 AA04 AA15 AB03 BB02 BB35 BB42 CC03 CC05 CC09 CC16 CC17 CC23 CC35

Claims (9)

[Claims] An electric element and a compression element connected to the electric element are provided in a closed vessel, and both ends of a cylinder of the compression element are closed with end plates to form a cylinder chamber, which is provided on the end plate. A drive shaft is supported by a main bearing and a sub bearing, and a roller fitted to an eccentric portion formed on the drive shaft is arranged in the cylinder chamber, and the rotation of the drive shaft causes the roller to revolve in the cylinder chamber. A compressor for compressing the refrigerant gas, and supplying lubricating oil accumulated in a bottom portion of the closed container to a bearing sliding portion of the drive shaft by an oil supply pump function by rotation of the drive shaft. The inside of the closed vessel is set to a pressure lower than the discharge pressure of the compression element, and a coolant gas discharge path communicating with the inside of the closed vessel is formed on a drive shaft, and extends radially outward from the coolant gas discharge path. Hermetic rotary compressor a refrigerant gas communication passage communicating with the air gap of the serial in rollers, characterized in that formed on the eccentric portion. 2. The hermetic rotary compressor according to claim 1, wherein the refrigerant gas communication passage is formed to communicate with a gap between both side surfaces of the eccentric portion and the end plates on both sides thereof. A hermetic rotary compressor. 3. The hermetic rotary compressor according to claim 1, wherein said refrigerant gas communication passage is formed between said eccentric portion and said end formed outside a thrust bearing formed on one side of said eccentric portion. A hermetic rotary compressor formed so as to communicate with a gap between the plate and the plate. 4. A closed chamber is provided with an electric element and a compression element connected to the electric element, wherein both ends of the cylinder of the compression element are closed with end plates to form a cylinder chamber, which is provided on the end plate. A drive shaft is supported by a main bearing and a sub bearing, and a roller fitted to an eccentric portion formed on the drive shaft is arranged in the cylinder chamber, and the rotation of the drive shaft causes the roller to revolve in the cylinder chamber. The closed type rotation that compresses the refrigerant gas and forms an oil supply groove for supplying the lubricating oil accumulated in the bottom of the closed container to the bearing sliding portion of the drive shaft by the operation of the oil supply pump by the rotation of the drive shaft. In the compressor, the inside of the closed container is set at a pressure lower than the discharge pressure of the compression element, and a refrigerant gas discharge passage communicating with the inside of the closed container is formed on a drive shaft, and a radius from the refrigerant gas discharge passage is formed. A refrigerant gas communication passage extending outwardly and communicating with a gap between the eccentric portion in the roller and the end plate and extending radially outward from the refrigerant gas discharge passage and communicating with the oil supply groove; A hermetic rotary compressor formed in the eccentric portion. 5. The hermetic rotary compressor according to claim 4, wherein the refrigerant gas communication passage extends radially outward from the refrigerant gas discharge passage, and the eccentric portion in the roller and the end plate. And a communication passage extending radially outward from the refrigerant gas discharge passage and communicating with the oil supply groove is formed independently of each other. . 6. A closed chamber is provided with an electric element and a compression element connected to the electric element, wherein both ends of a cylinder of the compression element are closed with end plates to form a cylinder chamber, which is provided on the end plate. A drive shaft is supported by a main bearing and a sub bearing, and a roller fitted to an eccentric portion formed on the drive shaft is arranged in the cylinder chamber, and the rotation of the drive shaft causes the roller to revolve in the cylinder chamber. The closed type rotation that compresses the refrigerant gas and forms an oil supply groove for supplying the lubricating oil accumulated in the bottom of the closed container to the bearing sliding portion of the drive shaft by the operation of the oil supply pump by the rotation of the drive shaft. In the compressor, the inside of the closed container is set at a pressure lower than the discharge pressure of the compression element, and a refrigerant gas discharge passage communicating with the inside of the closed container is formed on a drive shaft, and a radius from the refrigerant gas discharge passage is formed. A refrigerant gas communication passage extending outward and communicating with a gap in the roller is formed in the eccentric portion, and an oil supply groove formed in a bearing sliding portion of the drive shaft, the refrigerant gas discharge passage, and the refrigerant gas communication passage. And a closed rotary compressor formed independently. 7. A hermetic rotary compressor according to claim 6, further comprising a pump mechanism for supplying lubricating oil to one end of said drive shaft by means of a vane moving forward and backward with the revolving motion of said roller. An oil communication passage extending radially outward from a center portion of one end of the drive shaft so as to supply the supplied lubricating oil to the oil supply groove. . 8. A closed vessel comprising an electric element and a compression element connected to the electric element, wherein the compression element comprises two compression elements, a low-pressure compression element and a high-pressure compression element. Both ends of the cylinder of the compression element are closed by end plates to form cylinder chambers for the compression elements, and the drive shaft is supported by the main bearings and sub bearings on the end plates, and the drive shaft is formed on the drive shaft. Rollers fitted to the eccentric portions of the compression elements are arranged in the cylinder chambers of the compression elements, and the rotation of the drive shaft revolves the rollers in the cylinder chambers to compress the refrigerant gas into two stages. A hermetic rotary compressor that supplies lubricating oil accumulated in a bottom portion of the hermetic container to a bearing sliding portion of the drive shaft by an oil supply pump function by rotation of the drive shaft; Discharge pressure The pressure of the compression element for high pressure extends from the refrigerant gas discharge path radially outward while forming a refrigerant gas discharge path communicating with the closed container at a drive shaft. A hermetic rotary compressor, characterized in that a refrigerant gas communication passage communicating with an internal space is formed in an eccentric portion of the high-pressure compression element. 9. A refrigerating cycle is constituted by connecting a hermetic rotary compressor, a condenser, a decompression device, and an evaporator by piping, wherein the hermetic rotary compressor has an electric element and an electric element in a closed container. A compression element that is connected to the compressor, performs intermittent operation, and makes the inside of the closed vessel a pressure lower than the discharge pressure of the compression element.The compression element closes both end openings of the cylinder with end plates to close the cylinder chamber. The drive shaft is supported by a main bearing and a sub bearing provided on the end plate, and a roller fitted to an eccentric portion formed on the drive shaft is arranged in the cylinder chamber. Refrigerant gas is compressed by revolving the rollers in the cylinder chamber, and lubricating oil accumulated at the bottom of the closed container is supplied to the bearing sliding portion of the drive shaft by the operation of a refueling pump by rotation of the drive shaft. A refrigerant gas discharge passage communicating with the inside of the closed container is formed in the drive shaft, and a refrigerant gas communication passage extending radially outward from the refrigerant gas discharge passage and communicating with a gap in the roller is formed in the eccentric portion. Refrigeration characterized by
Air conditioner.