JP2002371974A - Hermetically sealed type rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetically sealed type rotary compressor preventing a shortage of oil in a cylinder, poor lubrication between a sliding member and a cylindrical hole portion, and an intake air heat loss and an increase in the amount of discharged oil caused by feeding too much oil into the cylinder, even when an operating condition changes. SOLUTION: Pressure in a sealed container 6 is made to be lower than discharge pressure, an oil pocket 21 is formed on a main bearing 2 structuring a end plate of the cylinder 1 as a mechanism supplying the fixed amount of lubricating oil into a sucking chamber 11 formed by the cylinder 1. Grooves 2b, 3d are formed on the main bearing 2 and a sub bearing 3, which returns the lubricating oil leaking from a compressing chamber 10 formed by the cylinder 1 into clearances between a vane portion 8b and a sliding member 9, and between the main bearing 2 and the sub bearing 3 to the sucking chamber 11.

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 system, and more particularly to a hermetic rotary compressor and a refrigeration / air-conditioning system in which the pressure in an airtight container is lower than a discharge pressure. Things.

[0002]

2. Description of the Related Art Conventionally, as a rotary compressor used in a refrigeration / air conditioning system, an electric element having a stator and a rotor and a compression element driven by the electric element are housed in a closed container. The roller, which is rotatably fitted to the eccentric portion of the drive shaft, rotates eccentrically in the cylinder by the rotation of the drive shaft, and the inside of the cylinder is sucked and compressed by the vane pressed by the roller. By compressing the refrigerant gas sucked into the suction chamber from the suction pipe in the compression chamber, the compressed refrigerant gas is compressed in the closed vessel for the purpose of increasing the back pressure of the vane section pressed against the roller to a high pressure. Is discharged to an external refrigeration cycle through a discharge pipe (prior art 1).

As a conventional rotary compressor in which the suction pressure is set in the closed container, there is a rotary compressor described in Japanese Patent Application Laid-Open No. 2-286892 (prior art 2). This rotary compressor is of a low-pressure container type in which the pressure in the closed container is substantially the same as the low-pressure side of the compressor. The cylinder is rotated by the eccentric rotation of the rolling piston while the rotation shaft rotates one revolution on the inner surface of the bearing plate. An oil sump recess having a position and a size is formed of three sections: a section entirely communicating with the low-pressure chamber inside the section, a section closed by the end plate of the rolling piston, and a section completely communicating with the inside of the rolling piston. are doing. In this compressor, the amount of lubricating oil determined by the volume of the oil reservoir is supplied to the low-pressure chamber per one rotation of the rotating shaft due to the operation of the compressor, and a constant amount of lubricating oil is constantly supplied to the low-pressure chamber per one rotation of the rotating shaft. It is possible to supply a large amount of lubricating oil to the outside of the machine at the time of starting or the like. In this compressor, the lubricating oil supplied by the oil sump recess is moved into the gap between the rolling piston and the bearing plate and the gap between the vane and the bearing plate by the differential pressure between the compression chamber and the low pressure side in the closed vessel. Leaks lubricate and seal these parts.

[0004]

However, according to the prior art 1, the oil leaking from the high pressure side of the inner surface of the roller into the suction chamber due to the differential pressure becomes excessive, which causes a decrease in the performance of the compressor due to a heat loss and the like, and also causes the compressor to be compressed. In addition, there is a problem that the high-temperature gas discharged from the closed container causes a decrease in reliability due to a rise in coil temperature of the electric element. When the compressor is operated intermittently, when the compressor is stopped, the high-temperature and high-pressure gas in the closed vessel flows back into the evaporator of the refrigeration cycle, raising the temperature of the evaporator and improving the performance of the refrigeration / air-conditioning system. There was also a problem of causing intermittent loss to decrease. Furthermore, when a natural refrigerant having flammability is used from the viewpoint of preventing global warming, the amount of refrigerant used in equipment tends to be limited. When the pressure in the closed vessel is high, the amount of the refrigerant used increases, and there is a problem that it is difficult to apply a natural refrigerant.

On the other hand, in the prior art 2, when the pressure condition of the compressor changes, the amount of lubricating oil leaking from the compression chamber to the gap between the rolling piston and the bearing plate or the gap between the vane and the bearing plate due to the differential pressure changes. On the other hand, the amount of the lubricating oil supplied to the low-pressure chamber by the oil reservoir recess is constant regardless of the pressure condition. For example, when the pressure discharged from the compression chamber increases, the amount of lubricating oil leaking into each gap increases, but the amount of lubricating oil supplied to the low-pressure chamber is constant. Also, when the rotation speed changes, the amount of lubricating oil leaking from the compression chamber into each gap per hour changes in inverse proportion to the speed, but the amount of lubricating oil supplied to the low-pressure chamber by the oil sump recess decreases. Increase in proportion. Therefore, if the volume of the oil reservoir recess is set so that the oil supply amount is optimal under conditions of low pressure difference and high speed with a small amount of leakage, the oil reservoir concave portion will fill the low pressure chamber under conditions of high pressure difference and low speed with a large amount of leakage. There is a problem that the amount of lubricating oil to be supplied is insufficient, the leakage of compressed gas from each gap increases, and the compression performance decreases. In addition, if the volume of the oil reservoir recess is set so that the oil supply amount is optimal under conditions of high pressure difference or low speed where the amount of leakage is large, the oil reservoir recess can be used to reduce the amount of oil in the low pressure chamber under the condition of low pressure difference or high speed where the amount of leakage is small. The amount of lubricating oil to be supplied becomes excessive and the intake heating loss and the amount of oil discharged to the outside of the compressor increase, which causes a problem that the compressor performance and the cycle performance decrease.

An object of the present invention is to guide lubricating oil leaked from the compression chamber into each clearance inside the compression mechanism into the suction chamber even when the pressure in the closed vessel is lower than the discharge pressure. Even if the amount of oil leakage changes, always ensure that the optimal amount of lubricating oil is interposed in the cylinder, increasing the leakage of refrigerant gas due to insufficient oil in the cylinder, poor lubrication between the sliding member and the cylindrical hole, and the cylinder. It is an object of the present invention to provide a high-performance and highly reliable hermetic type rotary compressor capable of preventing an intake heating loss and an increase in a discharge oil amount due to an excessive oil supply amount.

[0007]

In order to achieve the above object, a hermetic rotary compressor according to the present invention comprises a cylinder having a cylindrical inner peripheral surface, and both ends of the cylindrical inner peripheral surface of the cylinder being closed. A plurality of end plates, and a cylindrical outer peripheral surface revolves while always maintaining a small gap with the cylindrical inner peripheral surface of the cylinder in a space surrounded by the cylinder and the plurality of end plates. A roller portion, a drive mechanism for giving a revolving motion to the roller portion, and a plate-shaped vane portion integrally projecting radially from a cylindrical outer peripheral surface of the roller portion to partition the cylinder into a suction chamber and a compression chamber. A cylindrical hole formed outside the cylindrical inner peripheral surface of the cylinder and having a central axis parallel to the central axis of the cylindrical inner peripheral surface, into which the vane portion is inserted, and the cylindrical hole portion on both sides of the vane portion. The cylinder is installed in two spaces formed between the cylinder and the cylinder. A hermetic type rotary compressor having two sliding members having a cylindrical surface portion slidably in contact with a portion and a flat portion slidably in contact with the flat portion of the vane portion in a closed container; A pressure lower than the discharge pressure, and a mechanism for supplying a certain amount of lubricating oil to the suction chamber, and the lubricating oil leaked from the compression chamber into the gap between the vane and the sliding member and the end plate. It is provided with a groove for returning to the suction chamber.

In order to achieve the above object, a hermetic rotary compressor according to the present invention comprises a cylinder having a cylindrical inner peripheral surface, and a plurality of end plates for closing both ends of the cylindrical inner peripheral surface of the cylinder. ,
A roller section that revolves while a cylindrical outer peripheral surface always keeps a minute gap with the cylindrical inner peripheral surface of the cylinder in a space surrounded by the cylinder and the plurality of end plates; A driving mechanism that gives revolving motion to the plate, a plate-shaped vane portion that projects in the radial direction integrally from the cylindrical outer peripheral surface of the roller portion to partition the inside of the cylinder into a suction chamber and a compression chamber,
A cylindrical hole formed outside the cylindrical inner peripheral surface of the cylinder with a central axis parallel to the central axis of the cylindrical inner peripheral surface, into which the vane portion is inserted, and the cylinder on both sides of the vane portion The two sliding members having a cylindrical surface portion slidably in contact with the cylindrical hole portion and a flat surface portion slidably in contact with the flat surface portion of the vane portion are hermetically sealed. In the hermetic rotary compressor provided in the container, the pressure in the hermetic container is lower than the discharge pressure, and a mechanism for supplying a certain amount of lubricating oil to the suction chamber is provided. It is provided with a groove for returning the lubricating oil leaked into the gap with the plate to the suction chamber.

[0009]

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 will be omitted, and redundant description will be omitted.

First, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a horizontal type swinging piston type compressor according to a first embodiment of the present invention, and FIG.
1 is an AA sectional view of FIG. 1, FIG. 3 is an explanatory view of the operation of the compression element of FIG. 1, FIG. 4 is an explanatory view of a main part of the compressor of FIG. 1, and FIG. 5 is a BB sectional view 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 the electric element and the compression element are arranged in a closed vessel 6, and a suction pressure lower than a discharge pressure is applied to the inside of the closed vessel 6. And The electric element is the 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 and a swinging piston 8 rotatably disposed in the cylinder 1.
And a main bearing 2 and a sub-bearing 3 for closing the openings at both ends of the cylinder 1. The oil supply mechanism includes the hole 1c of the cylinder 1, the vane 8b, the suction fluid diode 17, the discharge fluid diode 18, the oil supply pipe 19, the spiral groove 20, the oil pocket 21, and the like.

The cylinder 1 has a cylindrical inner peripheral surface 1a at the center.
The main bearing 2 and the sub-bearing 3
And is closed. The main bearing 2 and the sub bearing 3 constitute an end plate for the cylinder 1. The main bearing 2 and the sub-bearing 3 are formed with bearing portions 2a, 3a at the center, respectively.
The drive shaft 4 is rotatably supported. The main bearing 2 and the sub-bearing 3 are fixed to the cylinder 1 so as to coincide with the central axis of the cylindrical inner peripheral surface 1a of the cylinder 1 of the drive shaft 4 which is a rotating shaft. Further, a rotor 5 of an electric element is fixed to the drive shaft 4. Further, an outer peripheral portion of the main bearing 2 is fixed to a closed container 6, and a stator 7 of an electric element is fixed to the closed container 6.

An eccentric portion 4a is formed on the drive shaft 4 at a portion located within the cylindrical inner peripheral surface 1a of the cylinder 1. The cylindrical inner peripheral surface of the roller portion 8a of the swing piston 8 is rotatably fitted to the cylindrical outer peripheral surface of the eccentric portion 4a, and the cylindrical outer peripheral surface of the roller portion 8a and the cylindrical inner peripheral surface 1a of the cylinder 1 are fitted. The dimensions of each part are determined so that the gap between them is very small. Further, a vane portion 8b is integrally formed on the cylindrical outer peripheral surface of the roller portion 8a. Outside the cylindrical inner peripheral surface 1a of the cylinder 1, a cylindrical hole 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a is formed. The opposite side communicates with the cylindrical inner peripheral surface 1a of the cylinder 1 and another hole 1c provided outside the cylindrical hole 1b. The vane portion 8b extends so as to be inserted into the cylindrical hole portion 1b and the hole portion 1c. However, between the vane portion 8b and the cylindrical hole portion 1b, the vane portion 8b slidably abuts on the plane portion of the vane portion 8b. Flat part and cylindrical hole part 1
A sliding member 9 having a cylindrical surface portion slidably in contact with the cylindrical surface portion b is incorporated with the vane portion 8b interposed therebetween. As a result, the vane portion 8b moves forward and backward toward the central axis of the cylindrical hole portion 1b. And a rocking motion around the central axis. The tip of the vane 8b moves in the hole 1c, and the cylinder 1
Do not interfere with.

With the above configuration, when the drive shaft 4 is rotated by the electric element, the oscillating piston 8
A revolving motion accompanied with swinging is performed in the cylinder 1 together with a.
FIG. 3 is a diagram showing the movement of the swing piston 8 when the drive shaft 4 rotates by 60 degrees. As is apparent from FIG. 3, the center of the roller portion 8a while performing a swinging motion at 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. Make an orbital motion. The vane portion 8b performs a reciprocating motion toward the central axis of the cylindrical hole portion 1b and a swinging motion around the central axis. The sealing of the gap between the vane portion 8b and the cylindrical hole portion 1b is maintained by inserting the sliding member 9. Therefore, the compression chamber 10 (the hatched portion in FIG. 3) which is a closed space and the suction chamber 11 which is a suction space are formed by the cylinder 1, the oscillating piston 8, the main bearing 2, the sub-bearing 3, and the sliding member 9, and the electric element is provided. The rotation of the drive shaft 4 causes the volume to increase and decrease as shown in FIG.

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. Secondary bearing 3
Is discharged from the discharge port 3b formed into the discharge chamber 3c formed by the auxiliary bearing 3 and the discharge cover 14. Thereafter, the liquid is discharged from the discharge pipe 15 to the outside of the closed container 6.

As described above, in this embodiment, in particular, 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 is at a suction pressure.
By setting the inside of the closed container 6 to the suction pressure, there are 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, and the motor efficiency is improved and the performance is improved. I can do it. (2) Since the suction pressure is applied to the inner surface of the roller portion 8a, excessive supply of oil due to the pressure difference from the inner surface of the roller portion 8a to the suction chamber 11 is eliminated, and the performance of the compressor can be improved. (3) Refrigerant compatible with oil such as chlorofluorocarbon has a low pressure, so the proportion of refrigerant gas dissolved in oil is reduced, and it is difficult for foaming phenomenon of refrigerant gas to occur in bearings and the like, improving reliability. can do. In addition, the amount of the refrigerant used is reduced, and the safety can be enhanced when a flammable natural refrigerant (such as isobutane and propane) is used. (4) The pressure resistance of the sealed container 6 can be reduced, and the thickness and weight of the sealed container 6 can be reduced.

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

Next, the oil supply mechanism of the compression mechanism will be described. In FIG. 1, the rotation of the drive shaft 4 causes the vane portion 8b to move 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 suction fluid diode 17 by the pumping action due to this volume change (hereinafter, referred to as a vane oil pump).
The auxiliary bearing 3, the eccentric portion 4a, and the main bearing 2 are lubricated through the discharge fluid diode 18, the oil supply pipe 19, the pumping shaft 4, and the spiral groove 20 provided on the outer periphery of the driving shaft 4, and then hermetically sealed again. Return to the inside of the container 6.

A portion of the lubricating oil 16 that has lubricated the eccentric portion 4a flows out into the inner surface of the roller portion 8a, and is provided in an oil pocket 21 provided on the end surface of the main bearing 2 which alternately moves between the suction chamber 11 and the inner surface of the roller portion 8a. As a result, the air is supplied to the suction chamber 11 as shown by the solid arrow in FIG. In the refueling by the oil pocket 21, an appropriate amount of lubricating oil can be supplied to the suction chamber by the action of the positive displacement pump without depending on the differential pressure, so that intake heating loss due to excessive refueling can be reduced. Here, the same effect can be obtained even if the oil pocket 21 is provided on the end face side of the sub bearing 3 and the spiral groove 20 is provided on the main bearing 2 and the sub bearing 3 side.

The lubricating oil 16 passing through the spiral groove 20
The high-pressure refrigerant gas leaked from the compression chamber 10 into the inner surface of the roller portion 8a passes through the communication hole 4e, and the gas discharged from the drive shaft 4 is discharged through the gas vent hole 4b. It is discharged into the closed container 6 through the hole 4c.

4 and 5 inside the compression mechanism.
As shown by arrows, the refrigerant gas and the lubricating oil 16 for the internal seal leak from the compression chamber 10 into the vane portion 8b and the minute gap between the sliding member 9 and the main bearing 2 and the sub bearing 3, and the main bearing 2 On the side, the oil passes through the hole 1e communicating with the oil return groove 2b formed in the main bearing 2 and the suction port 1d, and on the sub bearing 3 side, the oil flows from the suction port 1d through the oil return groove 3d formed in the sub bearing 3. After flowing into the chamber 11, the lubricating oil 16 is again used for the internal seal.

With the above configuration, the compression chamber 10
The lubricating oil 16 that has leaked from the vane portion 8b and the minute gap between the sliding member 9 and the main bearing 2 and the sub bearing 3 from the suction chamber 11
Can be used again for the inner seal,
Even when the amount of leakage inside the compression mechanism changes due to operating conditions, an optimal amount of lubricating oil 16 always intervenes in the cylinder 1, and internal leakage due to lack of oil in the cylinder 1 and the sliding member 9 and the cylindrical hole It is possible to provide a high-performance and highly reliable hermetic rotary compressor capable of preventing intake heating loss and discharge oil amount increase due to poor lubrication with the portion 1b and excessive oil supply to the cylinder 1.

Further, if the volume of the oil pocket 21 is set to an optimum oil supply amount for performing internal sealing under a low pressure difference and a high speed condition with a small amount of leakage, the intake heating loss due to excessive oil supply to the suction chamber 11 and the heat loss can be reduced. While avoiding a decrease in cycle performance due to an increase in the amount of oil discharged to the outside of the compressor, internal leakage due to a shortage of oil in the cylinder 1 and a sliding member 9 and a cylindrical hole even under conditions of high pressure difference and low speed with a large amount of leakage. Poor lubrication with the part 1b can be prevented, and the performance of the inverter-driven refrigeration / air-conditioning system can be improved over a wide range of operating conditions of the compressor.

Further, since the refrigerant gas is also guided to the suction port 1d by the oil return grooves 2b and 3d, the leakage of the refrigerant gas into the hole 1c can be suppressed, and the capacity of the vane refueling pump due to the mixture of the refrigerant gas into the hole 1c can be reduced. Since lowering can be prevented, stable lubrication of the shaft sliding portion can be achieved.

Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is an explanatory view of a main part of a swinging piston type compressor according to a second embodiment of the present invention.

In the oscillating piston type compressor in which the suction pressure is set in the closed container 6, a load acts on the sliding member 9 on the discharge port 3b side in the direction of the thick arrow, and the sliding member 9 is moved in the cylindrical hole portion 1b. As a result, a gap 9a is formed between the sliding member 9 and the cylindrical hole 1b, which communicates with the compression chamber 10 and increases as it approaches the compression chamber 10. Normally, in consideration of the assemblability of the sliding member 9, it is desirable that the gap 9a between the sliding member 9 and the cylindrical hole 1b is larger than the gap between the sliding member 9 and the main bearing 2 and the sub bearing 3. In such a case, if the oil return grooves 2b and 3d communicate with each other at a location where the gap 9a is large, the refrigerant gas flows from the compression chamber 10 through the oil return grooves 2b and 3d through the gap 9a and into the suction chamber 1.
It is conceivable that the oil may excessively flow out to 1 and degrade the compressor performance.

Therefore, in the present embodiment, the oil return grooves 2b and 3d formed in the main bearing 2 and the sub bearing 3 are provided so as to pass near the position where the gap 9a between the sliding member 9 and the cylindrical hole 1b is minimized. Therefore, the refrigerant gas flowing out of the compression chamber 10 into the oil return grooves 2b and 3d via the gap 9a can be throttled at a place where the gap 9a between the sliding member 9 and the cylindrical hole 1b is minimized. Excessive leakage of the refrigerant gas into the chamber 11 can be suppressed.

Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 7 is a vertical sectional view of a vertically mounted swinging piston type compressor according to a third embodiment of the present invention.
7 is a sectional view taken along the line CC of FIG. 7, and FIG. 9 is an explanatory view of a main part of the compressor of FIG. 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 shown in FIGS. The lubrication structure before pumping 16 to the drive shaft 4 is different.

7 and 8, the lubrication piece 4d
Is mounted on the lower end of the drive shaft 4 and is immersed in the lubricating oil 16 in the sealed container 6. The lubricating oil 16 stored at the bottom of the sealed container 6 is sucked from the lubrication piece 4d by the centrifugal pump action by the rotation of the drive shaft 4 to lubricate each sliding portion,
Each sliding portion is lubricated through a spiral groove 20 formed in the drive shaft 4. The refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 passes through the gas vent hole 4b, and the high-pressure refrigerant gas leaked from the compression chamber 10 into the inner surface of the roller portion 8a passes through the communication hole 4e, and The gas is discharged to the closed container 6 through the gas discharge hole 4c formed inside the container.

On the other hand, inside the compression mechanism, as shown by an arrow in FIG. 9, the refrigerant gas and the lubricating oil 16 for internal sealing are supplied from the compression chamber 10 to the roller portion 8a, the vane portion 8b, the sliding member 9 and the main bearing 2 as shown in FIG. Leaks into a minute gap with the auxiliary bearing 3. The vane portion 8b, the sliding member 9, and the main bearing 2
Refrigerant gas and lubricating oil 16 that have leaked into the gap between
As described in the first embodiment, the suction chamber 1 is formed from oil return grooves 2b and 3d formed in the main bearing 2 and the sub-bearing 3.
Returned to 1. Further, the refrigerant gas and the lubricating oil 16 leaking into the minute gaps between the roller portion 8a and the main bearing 2 and the sub-bearing 3
Is discharged to the suction chamber 11 through a communication groove 8c formed on both sides of the roller portion 8a on the main bearing 2 side and the sub bearing 3 side and communicating with the suction chamber 11. The lubricating oil 16 thus returned to the suction chamber 11 is again used for the above-mentioned internal seal.
The communication groove 8c does not communicate with the oil pocket 21 and the discharge port 3b, so that the refrigerant gas does not leak from the compression chamber 10 excessively. Is formed near the inner surface of the roller portion 8a in order to ensure the sealing performance of a minute gap between the roller portion 8a and the roller portion 8a. Further, in the present embodiment, the seal portion is formed from the seal point in the latter half of the compression stroke in which the pressure difference between the roller portion 8a and the compression chamber 10 becomes large.

With the above configuration, the compression chamber 10
In addition to the lubricating oil leaked into the minute gap between the vane portion 8b and the sliding member 9 and the main bearing 2 and the sub bearing 3, the lubricating oil leaked into the gap between the roller portion 8a and the main bearing 2 and the sub bearing 3 Can be guided to the suction chamber 11 and used again for the internal seal. Therefore, even when the leakage amount inside the compression mechanism changes depending on the operating conditions, the optimal amount of lubricating oil always intervenes in the cylinder 1. In addition, it is possible to more effectively prevent internal leakage due to an insufficient amount of oil in the cylinder 1, poor lubrication between the sliding member 9 and the cylindrical hole portion 1b, and intake air heating loss and discharge oil amount increase due to excessive oil supply into the cylinder 1. A hermetic rotary compressor with high performance and high reliability can be provided.

Further, if the volume of the oil pocket 21 is set to an optimum oil supply amount for performing the internal sealing under a low pressure difference or a high speed condition with a small amount of leakage, the intake heating loss due to the excessive oil supply to the suction chamber 11 is reduced. While avoiding a decrease in cycle performance due to an increase in the amount of oil discharged to the outside of the compressor, internal leakage due to a shortage of oil in the cylinder 1 can be more effectively suppressed even under conditions of high pressure difference and low speed where the amount of leakage is large. In addition, it is possible to improve the performance of the inverter-driven refrigeration and air conditioning system in which the operating conditions of the compressor are wide.

Next, a fourth embodiment of the present invention will be described with reference to FIGS. FIG. 10 is a longitudinal sectional view of a horizontal type swinging piston type two-stage compressor according to a fourth embodiment of the present invention, and FIG. 11 is a sectional view taken along line DD of FIG.

In FIG. 10 and FIG.
Reference numeral 2 denotes a low pressure compression element 22a and a high pressure compression element 22b, and a main bearing 24, a sub bearing 25 and a partition plate 26, which also serve as a shaft support for a drive shaft 23, and a cylinder 2 of each compression element.
Openings at both ends of 7, 28 are closed. This main bearing 2
4 and the auxiliary bearing 25 and the partition plate 26
8 constitute an end plate. The compression operation of the oscillating piston type compressor of the present embodiment is the same as that of the oscillating piston type compressor of the first embodiment, but the flow of the refrigerant gas is greatly different.

The refrigerant gas enters the low-pressure cylinder 27 through the low-pressure suction pipe 29 attached to the closed vessel 6, and is compressed by the low-pressure compression element 22a. The compressed refrigerant gas passes through a low-pressure discharge port 24 a formed in the main bearing 24 and is discharged into the closed casing 6 through the discharge silencer 30. The refrigerant gas discharged into the closed container 6 is discharged from the low-pressure discharge pipe 31 to the outside, is radiated and cooled by the intercooler 32, and then enters the high-pressure cylinder 28 through the high-pressure suction pipe 33. It is compressed by the high-pressure compression element 22b. The compressed refrigerant gas enters the discharge chamber 34 through the high-pressure discharge port 25a provided in the sub-bearing 25, from which the high-pressure discharge pipe 3
It flows out through 5. Therefore, the inside of the sealed container 6 has an intermediate pressure (a discharge pressure of the low-pressure compression element and a suction pressure of the high-pressure compression element) lower than the discharge pressure of the high-pressure compression element 22b and higher than the suction pressure of the low-pressure compression element 22b. ing.

Next, an oil supply mechanism of the compression mechanism will be described. 10 and 11, the rotation of the drive shaft 23 causes the vane portion 36b of the high-pressure swing piston 36 to rotate.
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 37 by the pump action due to the volume change, is pumped up to the drive shaft 23 through the oil supply pipe 19, and is further pumped to the outer periphery of the drive shaft 23. The auxiliary bearing 25, the eccentric parts 23a, 23 pass through the spiral groove 20 provided.
b) Lubricate the main bearing 24 and return to the closed container again. Part of the lubricating oil 16 that has lubricated the low-pressure eccentric portion 23a of the low-pressure compression element 22a is supplied to the roller portion 3 of the low-pressure oscillating piston 38.
The suction chamber 11 is supplied to the suction chamber 11 by a differential pressure between the inner surface of the suction chamber 8a and the suction chamber. The high-pressure eccentric part 23b of the high-pressure compression element 22b
Is supplied to the suction chamber 11 in the same manner as in the oil pocket system described in the first embodiment.

Then, the lubricating oil 1 passing through the spiral groove 20
The high-pressure refrigerant gas leaked into the inner surface of the high-pressure roller portion 36a from the gas vent hole 23c and from the compression chamber 10 of the high-pressure compression element 22b passes through the communication hole 23d.
Through the gas discharge hole 4 formed inside the drive shaft 23.
It is discharged to the closed container 6 by c.

Here, in the horizontal type swinging piston type two-stage compressor, the first to third embodiments of the present invention are applied to a high-pressure compression element 22b in which the pressure in the compression chamber is higher than the pressure in the closed vessel 1. Oil return grooves 2b, 3d shown in any of
Alternatively, a communication groove 8c is provided. As a result, even when the amount of leakage inside the compression mechanism of the high-pressure compression element 22b changes due to operating conditions, an optimal amount of lubricating oil always intervenes in the cylinder 28, and the amount of oil in the cylinder 28 becomes insufficient. High-performance and highly reliable swinging piston type two-stage that can prevent internal leakage due to oil, poor lubrication between the sliding member 9 and the cylindrical hole portion 1b, and intake heat loss and discharge oil amount increase due to excessive oil supply into the cylinder 28. A compressor can be provided.

Also, if the volume of the oil pocket 21 (see FIG. 3) is set to an optimum oil supply amount for performing internal sealing under a condition of a low pressure difference and a high speed with a small amount of leakage, excessive oil supply to the suction chamber 11 can be achieved. In addition to avoiding deterioration of cycle performance due to intake heating loss due to oil leakage and increase in the amount of oil discharged to the outside of the compressor, internal leakage and sliding members due to lack of oil in the cylinder even under conditions of high pressure difference and low speed where leakage is large. 9 and the poor lubrication between the cylindrical hole 1b can be suppressed.

Next, a fifth embodiment of the present invention will be described with reference to FIG. FIG. 12 is a configuration diagram of a refrigeration cycle of a refrigeration system according to a fifth embodiment of the present invention. This refrigeration cycle is a refrigeration cycle dedicated to refrigeration (cooling). In FIG. 12, 39 is a condenser, 39a is a condenser fan,
40 is an expansion valve, 41 is an evaporator, 41a is an evaporator fan,
Reference numeral 42 denotes a hermetic rotary compressor according to the first to third embodiments described above.

The high-temperature and high-pressure working gas compressed by activating the hermetic rotary compressor 42 of the present invention flows into the condenser 39 from the discharge pipe 15 as shown by a solid line arrow, and the blowing action of the fan 39a. Radiates and liquefies with the expansion valve 4
0, adiabatic expansion and low temperature / low pressure.
After the heat is absorbed and gasified in step 1, it is sucked into the hermetic rotary compressor 42 via the suction pipe 12. Here, since the refrigeration system shown in FIG. 12 is equipped with the hermetic rotary compressor of the present invention, a refrigeration system excellent in energy efficiency can be obtained. In particular, the closed rotary compressor 42 of the present invention is
Pressure is lower than the discharge pressure.
The amount of high-pressure refrigerant flowing into the evaporator can be reduced, and intermittent energy loss can be reduced.

Although the present embodiment has been described using a single-stage compressor, a two-stage compressor can also be mounted, and is applicable not only to a refrigeration system but also to an air conditioning system.

[0043]

As described above in detail, according to the present invention, even if the pressure in the closed container is lower than the discharge pressure, the lubricating oil leaked from the compression chamber into the respective gaps inside the compression mechanism is sucked into the suction chamber. Even if the amount of leakage inside the compression mechanism changes due to operating conditions, the optimal amount of lubricating oil is always interposed in the cylinder, increasing the leakage of refrigerant gas due to insufficient oil in the cylinder and the sliding member. It is possible to provide a high-performance and highly reliable hermetic rotary compressor capable of preventing intake heating loss and discharge oil amount increase due to poor lubrication between the cylinder and the cylindrical hole and excessive oil supply into the cylinder.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a horizontally mounted 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 an operation explanatory diagram of the compression element of FIG. 1;

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

FIG. 5 is a sectional view taken along line BB of FIG. 4;

FIG. 6 is an explanatory view of a main part of a swinging piston type compressor according to a second embodiment of the present invention.

FIG. 7 is a longitudinal sectional view of a vertically mounted swinging piston type compressor according to a third embodiment of the present invention.

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

FIG. 9 is an explanatory view of a main part of the compressor of FIG. 7;

FIG. 10 is a longitudinal sectional view of a horizontal type swinging piston type two-stage compressor according to a fourth embodiment of the present invention.

FIG. 11 is a sectional view taken along the line DD in FIG. 10;

FIG. 12 is a configuration diagram of a refrigeration cycle of a refrigeration system according to a fifth embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cylinder, 1a ... Cylindrical inner peripheral surface, 1b ... Cylindrical hole part,
1c: hole, 1d: suction port, 1e: hole, 2: main bearing, 2a: bearing, 2b: oil return groove, 3: sub-bearing, 3a
... bearing part, 3b ... discharge port, 3c ... discharge chamber, 3d ... oil return groove, 4 ... drive shaft, 4a ... eccentric part, 4b ... gas vent hole, 4c ... gas discharge hole, 4d ... oil supply piece, 4e ... communication Hole 5 Rotor 6 Closed container 7 Stator 8 Swing piston 8a Roller part 8b Vane part 8c Communication groove 9 Sliding member 9a Gap 10 Compression Room, 11
... Suction chamber, 12 ... 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, 22 ... compression element, 22a ... low-pressure compression element, 22b
... high-pressure compression element, 23 ... drive shaft, 23a ... low-pressure eccentric part, 23b ... high-pressure eccentric part, 23c ... gas vent hole, 23
d: communication hole, 24: main bearing, 24a: low pressure discharge port, 25: sub bearing, 25a: high pressure discharge port, 26:
Partition plate, 27: Low pressure cylinder, 28: High pressure cylinder, 29: Low pressure suction pipe, 30: Discharge silencer,
31: low pressure discharge pipe, 32: intercooler, 33: high pressure suction pipe, 34: discharge chamber, 35: high pressure discharge pipe, 36: high pressure swing piston, 36a: high pressure roller part, 36b: high pressure Vane part, 37 ... fluid diode,
38: Low pressure swing piston, 38a: Low pressure roller section,
39: condenser, 39a: condenser fan, 40: expansion valve, 41: evaporator, 41a: evaporator fan, 42: hermetic rotary compressor.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kazuhiro Endo 502, Kunitachi-cho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratory, Hitachi, Ltd. (72) Inventor Akihiko Ishiyama 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Hitachi, Ltd. 3H029 AA04 AA15 AA21 AB03 BB01 BB03 BB05 BB12 BB44 CC04 CC06 CC09 CC25 CC32 CC33 CC48 CC66

Claims (11)

[Claims] 1. A cylinder having a cylindrical inner peripheral surface, a plurality of end plates for closing both ends of the cylindrical inner peripheral surface of the cylinder, and a space surrounded by the cylinder and the plurality of end plates. A roller part that revolves around the cylindrical outer peripheral surface while always maintaining a small gap with the cylindrical inner peripheral surface of the cylinder, a drive mechanism that gives the roller part a revolving motion, and a cylindrical part of the roller part. A plate-shaped vane portion integrally projecting radially from the outer peripheral surface to partition the inside of the cylinder into a suction chamber and a compression chamber, and a central axis of the cylindrical inner peripheral surface outside the cylindrical inner peripheral surface of the cylinder. A cylindrical hole formed with a parallel central axis and into which the vane is inserted, and incorporated into two spaces formed between the cylindrical holes on both sides of the vane so as to be slidable in the cylindrical hole. Slidably abuts the cylindrical surface that comes into contact with the flat surface of the vane. A hermetic rotary compressor provided with two sliding members having a flat surface portion in a closed container, a mechanism for supplying a fixed amount of lubricating oil to the suction chamber by setting the inside of the closed container to a pressure lower than a discharge pressure. And a groove for returning the lubricating oil leaked from the compression chamber into the gap between the vane portion and the sliding member and the end plate to the suction chamber. 2. A cylinder having a cylindrical inner peripheral surface and a suction port, a plurality of end plates closing both ends of the cylindrical inner peripheral surface of the cylinder, and the cylinder and the plurality of end plates. A roller portion that makes a revolving motion while maintaining a small gap between the cylindrical outer circumferential surface and the cylindrical inner circumferential surface of the cylinder in the space, and a drive mechanism that gives the roller portion a revolving motion,
A plate-like vane portion integrally projecting radially from a cylindrical outer peripheral surface of the roller portion to partition the inside of the cylinder into a suction chamber and a compression chamber; and a cylindrical inner portion provided outside the cylindrical inner peripheral surface of the cylinder. The cylinder is installed in two spaces formed between a cylindrical hole formed with a central axis parallel to the central axis of the peripheral surface and into which the vane is inserted, and the cylindrical holes on both sides of the vane. A hermetically sealed rotary compressor including two sliding members having a cylindrical surface portion slidably in contact with a hole portion and a flat portion slidably in contact with a flat portion of the vane portion in a closed container; A pressure lower than the discharge pressure, a mechanism for supplying a certain amount of lubricating oil to the suction chamber, and a communication between the suction port and the gap between the vane and the sliding member and the end plates on both sides. Grooves are formed on both end plates A hermetic rotary compressor characterized by the fact that it is formed. 3. The hermetic rotary compressor according to claim 1, wherein the pressure inside the hermetic container is set to a suction pressure. 4. The hermetic rotary compressor according to claim 2, wherein a groove formed in said one end plate is formed to open to a hole communicating with said suction port. Hermetic rotary compressor. 5. The hermetic rotary compressor according to claim 2, wherein said groove is formed so as to straddle said sliding member and said vane portion. 6. The hermetic rotary compressor according to claim 2, wherein the sliding member located on the compressor side with respect to the vane portion is moved in the load direction within the cylindrical hole portion by a load applied to the sliding member. Wherein the groove of the end plate is formed so as to pass through the vicinity where the gap between the sliding member and the cylindrical hole at the time of the sliding is minimized. 7. A cylinder having a cylindrical inner peripheral surface, a plurality of end plates for closing both ends of the cylindrical inner peripheral surface of the cylinder, and a space surrounded by the cylinder and the plurality of end plates. A roller part that revolves around the cylindrical outer peripheral surface while always maintaining a small gap with the cylindrical inner peripheral surface of the cylinder, a drive mechanism that gives the roller part a revolving motion, and a cylindrical part of the roller part. A plate-shaped vane portion integrally projecting radially from the outer peripheral surface to partition the inside of the cylinder into a suction chamber and a compression chamber, and a central axis of the cylindrical inner peripheral surface outside the cylindrical inner peripheral surface of the cylinder. A cylindrical hole formed with a parallel central axis and into which the vane is inserted, and incorporated into two spaces formed between the cylindrical holes on both sides of the vane so as to be slidable in the cylindrical hole. Slidably abuts the cylindrical surface that comes into contact with the flat surface of the vane. A hermetic rotary compressor provided with two sliding members having a flat surface portion in a closed container, a mechanism for supplying a fixed amount of lubricating oil to the suction chamber by setting the inside of the closed container to a pressure lower than a discharge pressure. And a groove for returning the lubricating oil leaked from the compression chamber into the gap between the roller portion and the end plate to the suction chamber. 8. A cylinder having a cylindrical inner peripheral surface, a plurality of end plates for closing both ends of the cylindrical inner peripheral surface of the cylinder, and a space surrounded by the cylinder and the plurality of end plates. A roller portion that revolves around while the cylindrical outer peripheral surface always keeps a minute gap with the cylindrical inner peripheral surface of the cylinder, a drive mechanism that gives revolving motion to the roller portion, and a cylindrical shape of the roller portion. A plate-shaped vane portion integrally projecting radially from an outer peripheral surface to partition the inside of the cylinder into a suction chamber and a compression chamber, and a central axis of the cylindrical inner peripheral surface outside the cylindrical inner peripheral surface of the cylinder. A cylindrical hole formed with a parallel central axis, into which the vane is inserted, and two spaces formed between the cylindrical holes on both sides of the vane are slidable into the cylindrical hole. Slidably abuts the cylindrical surface that comes into contact with the flat surface of the vane. A hermetic rotary compressor provided with two sliding members having a flat surface portion in a hermetic container, wherein the inside of the hermetic container is set at a pressure lower than a discharge pressure and a fixed amount of lubricating oil is supplied to the suction chamber. A hermetic rotary compressor, wherein a groove communicating the gap between the roller section and the end plate and the suction chamber is formed in the roller section. 9. The hermetic rotary compressor according to claim 8, wherein the groove is formed such that a distance from an inner surface of the roller portion is shorter than a distance from the compression chamber. Hermetic rotary compressor. 10. A hermetic two-stage rotary compressor provided with a groove according to claim 1. 11. A refrigeration / air conditioning system equipped with the hermetic rotary compressor according to any one of claims 1 to 10.