JP2001254688A - Swinging piston type compressor and freezer using it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce cost, miniaturize the size, and improve the performance and the reliability in a swinging piston type compressor and freezer. SOLUTION: A compression element 1 having a low-pressure compression element 4 and a high-pressure compression element 5 is arranged in a sealed vessel 3, swinging pistons 4b and 5b integrally formed with rollers 4b1 and 5b1 and vanes 4b2 and 5b2 are used, the inside of the sealed vessel 3 is held at a pressure lower than a discharge pressure of the high-pressure compression element 5, and an oil feeding mechanism intermittently feeding lubricating oil 20 via an oil pocket 21 intermittently communicated with an operation chamber side and an oil feed side of the high-pressure compression element 5 is provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oscillating piston type compressor and a refrigeration system using the same, and more particularly to an oscillating piston type compressor having a low-pressure compression element and a high-pressure compression element, a refrigerator, and an air conditioner. It is suitable for a refrigerating apparatus having a refrigerating cycle such as a refrigerator.

[0002]

2. Description of the Related Art Conventional hermetic two-stage rotary compressors include:
There is one described in JP-A-50-72205 (prior art 1).

In the prior art 1, the rotor and the vane are separate bodies, and the pressure in the closed vessel is maintained at an intermediate pressure between the condensing pressure and the evaporating pressure of the refrigerant. The upper end of the pipe is opened in the suction pipe of the high-pressure compression mechanism, and by utilizing the negative pressure in the housing due to the rotation of the rotor of the high-pressure compression mechanism, the refrigerant gas is sucked and the lubricating oil is pulled up from the oil suction pipe and the high-pressure compression mechanism Is to lead to.

A conventional rotary compressor is disclosed in Japanese Patent Application Laid-Open No. 7-301190 (prior art 2).

[0005] In the prior art 2, even in the case of using a chlorofluorocarbon alternative which is strictly lubricated, in order to solve the problem of friction and abrasion at the contact portion between the vane and the roller, a stator and a rotating member are provided in a closed container. A crankshaft driven by the motor element, a roller rotatably fitted to an eccentric portion of the crankshaft, a reciprocating motion in contact with a tip of the roller, and a suction chamber in the cylinder. A vane partitioning into a compression chamber, and a compression element formed by a main bearing and an auxiliary bearing having an end plate that supports the crankshaft and closes both end openings of the cylinder are housed, and the vane is most outwardly of the cylinder. When it is moved to 0
In the vicinity of the rotation angle of 90 °, oil supply means for supplying the lubricating oil accumulated in the closed container into the suction chamber of the cylinder toward the contact portion between the vane and the roller is provided. The discharge pressure is compressed by the compression element, and the vane is pressed by the discharge pressure and the spring to come into contact with the roller.

[0006]

However, the prior art 1 has a problem in that the oil supply to the high-pressure compression mechanism lacks stability of the oil supply amount because the driving force is a small pressure difference in the piping path. . If the oil is excessively supplied to the high-pressure compression mechanism, the oil may flow out during the refrigeration cycle, causing a decrease in the heat transfer performance of the heat exchanger and a poor lubrication due to a shortage of the oil in the sealed container of the compressor. is there.

Further, the prior art 1 has a problem that the contact portion between the vane and the roller cannot be eliminated at all, since the separate vane and the roller come into contact with each other. Since the spring is used to press the vane against the fin, the cost is increased.

On the other hand, in the prior art 2, since the separate vane and the roller are in contact with each other, even if oil supply means for supplying oil is provided in this portion, the contact between the vane and the roller can be prevented. There is a problem that the wear of the part cannot be eliminated at all.

The prior art 2 has the following problem because the inside of the closed container is set to a high temperature and a high discharge pressure in order to press the vane against the roller. That is, when the electric element is heated at a high temperature, the temperature of the coil rises, the reliability decreases, and it is difficult to increase the motor efficiency. Also, the leakage oil due to the differential pressure from the inner surface of the high-pressure roller into the low-pressure suction chamber is likely to be excessive, and the performance of the compressor may be reduced. And, since the refrigerant is easily dissolved in the oil under high pressure, a large amount of the refrigerant is required, which leads to an increase in cost, and in particular, when a flammable hydrocarbon-based refrigerant is used, the amount of leakage at the time of this leakage increases and In addition, the lubrication performance is reduced due to the foaming of the refrigerant from the oil supplied to the bearing portion, which may cause a reduction in reliability. Further, in order to increase the pressure resistance of the closed container, the use of a thick closed container causes an increase in weight and an increase in cost.

Further, in the case of the prior art 2, since the compression is one-stage, the compression performance is large under the condition that the compression ratio is large, for example, under the condition of refrigeration (for the air conditioner or the like) under the condition that the compression ratio is small. There's a problem.

An object of the present invention is to provide a swinging piston type compressor and a refrigeration system which can be reduced in cost, and which are small, high-performance and highly reliable.

[0012]

A first feature of the present invention to achieve the above object is that an electric element and a compression element are connected to each other via a drive shaft in a closed container, and the compression element Has a low-pressure compression element and a high-pressure compression element, each of the compression elements has a cylinder whose both end faces are closed, and a swing piston in which rollers and vanes are integrated, and the swing piston is inside the cylinder. The vane divides the working chamber in the cylinder into a suction chamber side and a compression chamber side, and the inside of the closed vessel is set to a pressure lower than the discharge pressure of the high-pressure compression element. While holding and compressing to a pressure higher than the pressure in the closed container, from the oil supply side to the operation chamber side via an oil storage part intermittently communicating with the oil supply side and the operation chamber side of the compression element. An oil supply mechanism for intermittently supplying lubricating oil Located in.

A second feature of the present invention is that the inside of the closed container is set at an intermediate pressure between the suction pressure and the discharge pressure of the compression element, and the suction chamber side and the oil supply side in the cylinder of the high pressure compression element are connected. And an oil supply mechanism for intermittently supplying lubricating oil from the oil supply side to the suction chamber side via an oil storage section intermittently connected to the oil supply section.

A third feature of the present invention resides in that an electric element and a compression element are horizontally connected via a drive shaft in a horizontally long closed container, and the compression element is composed of a low-pressure compression element and a high-pressure compression element. A compression element, and each of the compression elements is arranged side by side with the drive shaft, and intermittently communicates with the suction chamber side in the cylinder of the high pressure compression element and the lubricating oil side at the bottom of the sealed container. An oil supply mechanism is provided in which an oil pocket is formed in the vane and the lubricating oil is intermittently supplied to the suction chamber side.

A fourth feature of the present invention is that a corner cutout is formed in the vane so as to intermittently communicate with the suction chamber side in the cylinder of the high-pressure compression element and the lubricating oil side at the bottom of the closed vessel. An oil supply mechanism for intermittently supplying the lubricating oil to the suction chamber.

A fifth feature of the present invention is that an electric element and a compression element are connected to each other via a drive shaft in a closed container, and the compression element has a low-pressure compression element and a high-pressure compression element. Each of the compression elements has a cylinder whose both end faces are closed, a roller and a vane, and a swinging piston integrated with the swinging piston. The swinging piston is arranged in the cylinder so as to be able to revolve with swinging, and the vane is The inside of the cylinder is partitioned into a suction chamber and a compression chamber together with the rollers, and the inside of the closed container is maintained at a pressure lower than the discharge pressure of the high-pressure compressor, and the high-pressure compressor is discharged from a discharge part of the low-pressure compression element. That is, a flow path connecting the suction portions of the compression elements is provided.

A sixth feature of the present invention is that the inside of the closed container is set to the discharge pressure of the low-pressure compression element, and the flow path connects the discharge part of the low-pressure compression element to the suction part of the high-pressure compression element. The oil separation mechanism was provided in the middle of the process.

A seventh feature of the present invention is that a compressor, a condenser,
The decompression mechanism and the evaporator are connected by piping to form a refrigeration cycle, and the compressor is arranged in a closed vessel by connecting an electric element and a compression element via a drive shaft, and the compression element is used for low pressure. A compression element and a high-pressure compression element, wherein each of the compression elements has a cylinder whose both end faces are closed, and a swing piston in which rollers and vanes are integrated, and the swing piston swings into the cylinder. The vane divides the working chamber in the cylinder into a suction chamber side and a compression chamber side, and holds the inside of the closed vessel at a pressure lower than the discharge pressure of the high-pressure compressor. And an oil supply mechanism for intermittently supplying lubricating oil from the oil supply side to the operation chamber side via an oil storage portion intermittently communicating with the operation chamber side and the oil supply side of the high-pressure compression element. It is in.

An eighth feature of the present invention is that the oil supply side intermittently communicates with the oil supply side in the cylinder of the high-pressure compression element from the oil supply side. The lubricating oil is intermittently supplied to the refrigeration cycle so that the oil circulation rate in the refrigeration cycle is 0.1% by weight to 1.0% by weight.

A ninth feature of the present invention is that a compressor, a condenser,
The decompression mechanism and the evaporator are connected by a pipe to form a refrigeration cycle, and the compressor is configured such that an electric element and a compression element are laterally connected via a drive shaft in a horizontally long closed container, and the compression is performed. The element has a low-pressure compression element and a high-pressure compression element, and these compression elements are juxtaposed side by side with the drive shaft, and the suction chamber side in the cylinder of the high-pressure compression element and the bottom of the closed container are provided. The lubricating oil is intermittently supplied from the lubricating oil side at the bottom to the suction chamber side via an oil pocket intermittently communicating with the lubricating oil side, so that the oil circulation rate in the refrigeration cycle is reduced to 0.
That is, an oil supply mechanism for adjusting the weight to 1% to 1.0% by weight is provided.

A tenth feature of the present invention is that a compressor, a condenser, a decompression mechanism for a refrigerator, an evaporator for a refrigerator, a decompression mechanism for a freezer and an evaporator for a freezer are connected by piping to form a refrigeration cycle. The compressor is configured such that, from an oil pocket intermittently communicating with a suction chamber side in a cylinder of the high-pressure compression element and a lubricating oil side of a bottom of the closed vessel, the compressor is arranged from the lubricating oil side of the bottom part. An oil supply mechanism is provided intermittently to supply lubricating oil to the suction chamber so that the oil circulation rate in the refrigeration cycle is 0.1% by weight to 1.0% by weight. The refrigerating room pressure reducing mechanism and the refrigerating room evaporator are connected in series and provided between an outlet side of the condenser and a suction side of the high-pressure compression element, and communicate with a discharge side. The pressure reducing mechanism and the freezer evaporator are connected in series, and the outlet side of the condenser and the low pressure In that provided between the suction side of the compression element.

[0022]

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

First, a swinging piston type compressor according to a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a swinging piston type compressor according to a first embodiment of the present invention,
2 is a sectional view taken along the line AA in FIG. 1, FIG. 3 is a sectional view taken along the line BB in FIG. 1, FIG. 4 is an explanatory view of the operation of the lubrication mechanism of the oscillating piston type compressor in FIG. FIG. 6 is a perspective view showing a modified example of the oscillating piston provided with an oil pocket used in the oscillating piston type compressor. FIG.
FIG. 9 is a performance characteristic diagram showing a relationship between OPs.

As is apparent from FIG. 1, the closed container 3 is formed in a horizontally long cylindrical shape, and comprises a main body cylindrical portion and lid portions on both sides thereof. In the closed container 3, the compression element 1, the electric element 2, the drive shaft 6, and the like are housed. As described above, by making the closed container 3 into a horizontally long tubular shape, it is possible to improve the storability when the compressor is arranged in the rear machine room of the refrigerator. The electric element 2 includes a stator 2
a and a rotor 2b, the stator 2a is fixed to the closed casing 3, and the rotor 2b is rotatably arranged in the stator 2a. The compression element 1 includes a low-pressure compression element 4 and a high-pressure compression element 5, and includes a closed vessel 3 through a main bearing 9.
It is stuck to.

Each of the compression elements 4, 5 has a cylinder 4a, 5a having a cylindrical inner peripheral surface, and oscillating pistons 4b, 5b revolving with oscillation along the cylinder inner peripheral surface. Both end surfaces of the cylinders 4a and 5a are closed by a main bearing 9 and a sub bearing 10 which also serve as a shaft support for the drive shaft 6 with a partition plate 8 interposed therebetween.

The oscillating pistons 4b, 5b are formed by integrally forming cylindrical rollers 4b1, 5b1 and plate-like vanes 4b2, 5b2, respectively, and have an eccentric shaft 6a of a drive shaft 6 extending from the electric element 2. 6b. Thus, the rollers 4b1, 5b1 and the vanes 4b2, 5b2
Are formed integrally, it is possible to eliminate the wear of the contact portions between the rollers 4b1 and 5b1 and the vanes 4b2 and 5b2 as in the related art, and at the same time, the rollers 4b1 and 5b1
There is no need to press the back of the container with high pressure, and it is possible to eliminate the need to keep the inside of the sealed container 3 under high pressure. The vanes 4b2, 5b2 divide the inside of the cylinders 4a, 5a into a suction chamber side and a discharge chamber side.

The electric element 2 and the compression element 1 are connected via a drive shaft 6. In the drive shaft 6, the phase of the eccentric shaft 6a of the low-pressure compression element 4 and the phase of the eccentric shaft 6b of the high-pressure compression element 5 are shifted by 180 °. The low-pressure compression element 4 and the high-pressure compression element 5 are provided side by side in the axial direction such that the low-pressure compression element 4 is on the electric element 2 side. in this way,
Since the low-pressure compression element 4 and the high-pressure compression element 5 are provided side by side in the axial direction, the partition plate 8 can also be used, and the compressor can be made smaller.

Outer and lower sides of the cylindrical inner peripheral surfaces of the cylinders 4a and 5a, first cylindrical holes 4a1 and 5a1 having a central axis parallel to the central axis of the cylindrical inner peripheral surface communicate with each other. Is formed. The vanes 4b2 and 5b2 are cylindrical holes 4a.
1, 5a1 and the cylindrical holes 4a1, 5a1
Both sides are supported via a sliding member 7 so as to swing and advance / retreat about the central axis of the center.

Outside and below the first cylindrical holes 4a1, 5a1, second cylindrical holes 4a2, 5a2 having central axes parallel to the central axes of the cylindrical holes 4a1, 5a1 communicate with each other. Is provided. The tips of the vanes 4b2, 5b2 are inserted into the cylindrical holes 4a2, 5a2, and swing and move forward and backward. The cylindrical holes 4a2 and 5a2 are located at the bottom of the closed container 3, and are filled with the lubricating oil 20. In addition, the front-end | tip part of the vanes 4b2 and 5b2 is the hole 4a.
It moves in 2, 5a2 and does not interfere with the cylinders 4a, 5a.

The discharge valve device 11 is disposed on an end face of the main bearing 9 and opens and closes a discharge port (not shown) of the low-pressure compression element 4 formed in the main bearing 9. The discharge muffler 12 is disposed on the discharge side so as to cover the discharge valve device 11 so as to function as a discharge silencer for the low-pressure compression element 4, and has a discharge port communicating with the closed container 3. Thereby, the inside of the sealed container 3 is maintained at the intermediate pressure. The discharge valve device 13 is
The discharge port (not shown) of the high-pressure compression element 5 formed on the end face of the sub-bearing 10 and formed on the sub-bearing 10 is opened and closed. A discharge space for the high-pressure compression element 5 is defined by the auxiliary bearing 10 and the discharge cover 14. This discharge space communicates with the discharge pipe 18.

A space 10 b is formed at the bottom of the auxiliary bearing 10 for supplying the lubricating oil 20 to the sliding portion of the drive shaft 6 and the like. The space 10b communicates with the inside of the sealed container 3 via the fluid diode 10a, and one side has a cylindrical hole 4a2, 5a.
2 and the other side is connected to a path to a sliding portion of the drive shaft 6. The fluid diode 10a is formed such that the lubricating oil 20 easily flows into the fluid diode 10a from the space side in the sealed container 3 and hardly flows out in the opposite direction. Further, the cylindrical hole 5a2 forms a closed space in which one side is closed by the partition plate 8 and the other side is communicated with the space 10b. The oil supply cover 14a is mounted outside the discharge cover 14 to form an oil supply passage. One side of the oil supply passage communicates with the space 10 b through the communication passage of the discharge cover 14, and the other side communicates with the oil supply hole of the drive shaft 6 through the communication passage of the discharge cover 14.

The volume of the lubricating oil 20 in the sealed container 3 is changed by the vane 5b2 of the high-pressure compression element 5 moving forward and backward in the cylindrical hole 5a2, and the volume of the lubricating oil 20 is changed via the fluid diode 10a. Sucked into the space 10b
Drive shaft 6 through an oil supply passage formed by oil supply cover 14a
And supplied to a sliding portion of the drive shaft 6 (see dotted arrows in FIG. 1). As described above, the lubricating oil 20 can be supplied to the sliding portion of the drive shaft 6 or the like with a simple configuration by using the forward / backward movement of the vane 5b2 and the fluid diode 10a.

The suction pipe 15 of the low-pressure compression element 4 penetrates through the bottom of the closed vessel 3 and communicates with the suction side of the low-pressure compression element 4. Further, the discharge pipe 16 communicates with the inside of the sealed container 3 at an intermediate pressure, extends outward from the sealed container 3, and is connected to the intercooler 19. The suction pipe 17 of the high-pressure compression element 5 has one side connected to the intercooler 19 and the other side communicating with the suction side of the high-pressure compression element 5. As described above, the intercooler 19 is disposed between the discharge pipe 16 of the low-pressure compression element 4 and the suction pipe 17 of the high-pressure compression element 5. The discharge pipe 18 of the high-pressure compression element 5 is
The gas passes through the closed vessel 3 and communicates with the condenser of the refrigeration cycle.

The oil pocket 21 forming the oil storage portion is provided with a vane 5b on the suction side of the swing piston 5b for intermittently supplying the lubricating oil 20 into the working chamber of the high-pressure compression element 5.
2 is formed on the side surface. The details of this refueling mechanism will be described later.

In the above configuration, when the drive shaft 6 is rotated by the electric element 2, the oscillating pistons 4b, 5b revolve by the eccentric shaft portions 6a, 6b. As is clear from FIGS. 2 and 3, the rollers 4b of the swing pistons 4b, 5b
1, 5b1 revolves around the center while swinging so that the integrated vanes 4b2, 5b2 always face the center of the eccentric shafts 6a, 6b. As a result, the vanes 4b2, 5b2 are formed in the cylindrical holes 4a of the cylinders 4a, 5a.
The advancing / retreating motions toward the central axis of the first and fifth a1 and the swinging motion around the central axis are performed. The seal between the vanes 4b2 and 5b2 and the cylindrical holes 4a1 and 5a1 of the cylinders 4a and 5a is formed by a sliding member. 7 is maintained by being inserted.

Accordingly, the cylinders 4a and 5a of the low-pressure compression element 4 and the high-pressure compression element 5, the oscillating pistons 4b and 5b,
A compression chamber, which is an operating space, is formed by the sliding member 7 and the partition plate 8, which closes both end openings of the cylinder, the main bearing 9, and the sub-bearing 10, and the reciprocating motion of the oscillating pistons 4b, 5b performs a compressing action of the working fluid. Will be The working gas enters the cylinder 4a of the low-pressure compression element 4 through the suction pipe 15 as shown by the arrow in FIG. 1, and the rotation of the drive shaft 6 causes the swing piston 4b to swing with a substantially constant radius. It is compressed by the orbital motion, passes through a discharge valve device 11 disposed on the end plate of the main bearing 9, passes through a discharge muffler 12, and is discharged into the closed container 3. The working gas discharged into the closed vessel 3 goes out of the discharge pipe 16 to be radiated and cooled by the intercooler 19, and then enters the cylinder 5 a of the high-pressure compression element 5 through the suction pipe 17. Then, the swinging piston 5b makes a revolving motion accompanied by swinging, and is further compressed, passes through a discharge valve device 13 disposed on the end plate of the sub bearing 10, and enters a discharge space which is hermetically partitioned by a discharge cover 14. From there, it flows out to the refrigeration cycle outside the closed vessel 3 through the discharge pipe 18.

Next, the lubrication mechanism of the compressor according to the present invention will be described. When the drive shaft 6 is rotated by the electric element 2, the compression operation of the working gas is performed by the low-pressure compression element 4 and the high-pressure compression element 5 as described above, and the pressure in the closed vessel 3 is intermediate between the discharge pressure and the suction pressure. , The discharge pressure of the low-pressure compression element 4 in this embodiment.

The lubrication (external lubrication) of the sliding portion of the drive shaft 6 of the compressor will be described. Swing piston 5 of high-pressure compression element 5
b vane 5b2 moves forward and backward, and lubricating oil 2
This is based on an oil supply pump operation utilizing a change in the volume of the back space (space of the hole 5a2) of the vane 5b2 immersed in the water. That is, the flow path shape of the fluid diode 10a is tapered so that the cross-sectional area decreases from the oil storage portion of the lubricating oil 20 toward the back space direction of the vane 5b2, and the passage resistance of the flow (forward flow) entering from the oil storage portion. Thus, the passage resistance of the flow (backflow) going out to the oil storage section is increased. Therefore, when the volume of the back space is increased by the reciprocating motion of the vane 5b2, the fluid diode 10a
When the volume of the back space is reduced, the amount of the lubricating oil that returns to the oil storage unit through the fluid diode 10a is smaller than the amount of the lubricating oil that flows into the space from the oil storage unit through the oil storage unit. The amount of oil supplied to the center of the drive shaft 6 through the oil supply passage of the cover 14a. The oil that has reached the center of the drive shaft 6 passes through an oil supply hole (shown by a broken line) formed inside the drive shaft 6, and has a sub bearing 10, a main bearing 9, and an eccentric shaft 6a.
6b is supplied to each bearing sliding portion.

The internal lubrication, which is the lubrication in the compression element working chamber, will be described. In the internal lubrication of the low-pressure compression element 4, the amount of oil supplied into the working chamber becomes an amount leaked due to a differential pressure between the intermediate pressure in the closed vessel 3 and the pressure on the suction chamber side of the working chamber, and the driving force of the leak Is smaller than the case where the pressure in the closed container is the discharge pressure, so that the amount of oil leaking into the working chamber through the gap such as the end face of the oscillating piston 4b can be reduced, and the performance is improved. Can be achieved.

The internal lubrication of the high-pressure compression element 5 is performed by the vane 5b on the suction side of the oscillating piston 5b regardless of the differential pressure.
The oil is intermittently supplied by the positive displacement pumping action of the oil pocket 21 formed on the side face of the second. The oil supply operation of the oil pocket 21 will be described with reference to FIG. FIG. 4 shows the movement of the oscillating piston 5b of the high-pressure compression element 5 when the drive shaft 6 rotates by 90 °.

FIG. 4A shows the vane 5 of the oscillating piston 5b.
In a state where b2 projects most outside the cylinder 5a, this state is defined as a rotation angle (crank angle) θ = 0 ° of the drive shaft 6. In this state, the oil pocket 21 formed on the side surface of the vane 5b2 is opened in the lubricating oil 20 in the hole 5a2, and the space in the oil pocket 21 is filled with the lubricating oil 20. FIG. 4B shows the state in which the drive shaft 6 is rotated clockwise by 90 ° from this point, and in FIG.
The opening of the oil pocket 21 into which the oil pocket 21 has been taken is closed by the sliding member 7. Further 90 ° rotation (θ = 180
FIG. 4 (c) shows that the oil pocket 21 opens into the suction chamber in the cylinder 5a, and the lubricating oil 20 in the oil pocket 21 gushes out into the suction chamber due to the density difference between gas and liquid. Is replaced by A further 90 ° rotation from here (θ =
270 °) in the state shown in FIG. 4D. The opening of the oil pocket 21 in which the working gas has been taken in is closed by the sliding member 7. 4A, the working gas in the oil pocket 21 is replaced with the lubricating oil 20 and the space in the oil pocket 21 is filled with the lubricating oil 20 again. By repeating the above operation, it is possible to reliably supply a predetermined amount of the lubricating oil 20 into the working chamber of the high-pressure compression element 5.

The supply amount of the lubricating oil 20 in the internal lubrication of the high-pressure compression element 5 can be easily changed by changing the volume of the oil pocket 21, whereby the optimum oil amount of each compression element is controlled. Performance and reliability can be improved. In FIG. 5A, the oval oil pocket 21 is formed at the center of the side surface of the vane 5b2. However, the shape and position of the oil pocket 21 are not limited to this. As shown in FIG. 5 (b), the corner of the end face may be partially cut out. With such a shape, the oil pocket 21a can be integrally incorporated and formed when the swing piston 5b is formed by powder metallurgy or the like, so that the machining is simplified and the high-pressure compression element 5 is assembled. This makes it possible to prevent an error in assembling the swing piston 5b, such as mounting the oil pocket in the opposite direction. Here, the formation position of the oil pocket 21 is changed to the vane 5 of the swing piston 5b.
Although the b2 is a side portion on the side of the suction working chamber, the present invention is not limited to this. The lubricating oil storage section in the closed container and the high-pressure compression element in the suction working chamber of the high-pressure compression element 5 are provided. It does not depend on the position and shape of the oil pocket as long as it is an oil pocket that alternates between the suction working chamber. As a result, an oil supply mechanism that appropriately supplies the lubricating oil necessary for the seal of the working chamber by intermittent operation without depending on the differential pressure is realized.

With the above-described structure, the pressure in the closed vessel 3 can be made lower than the discharge pressure, and the inside of the closed vessel 3 is kept at a low temperature and a low pressure. Things. That is, the temperature of the electric element can be lowered, and the reliability and the motor efficiency can be improved. Further, the amount of oil supplied to the high-pressure compression element 4 can be easily set to an appropriate amount, and the performance of the compressor can be improved. At low pressure, the refrigerant hardly dissolves in the oil, and the amount of refrigerant can be reduced to reduce the cost. Particularly, when a flammable hydrocarbon-based refrigerant is used, the amount of refrigerant leakage at the time of leakage is reduced. It is possible to improve safety by reducing the amount of lubrication, and it is possible to suppress a decrease in lubrication performance due to foaming of the refrigerant from the oil supplied to the bearing portion, thereby improving reliability. Further, the pressure resistance of the closed container 3 is reduced, and the weight and cost can be reduced by using the thin closed container 3.

In this embodiment, the closed container 3
Although the inside is configured to be at the discharge pressure of the low-pressure compression element 4, it may be configured to be at the suction pressure of the low-pressure compression element 4. For lubrication, an oil supply mechanism similar to the internal lubrication of the high-pressure compression element 5 may be formed, and the performance and reliability can be improved by further reducing the pressure in the closed vessel 3.

By the way, the cylindrical roller 4b
Oscillating pistons 4b, 5b in which plate vanes 4b2, 5b2 are integrated with plate-shaped vanes 4b2, 5b2.
The optimal amount of internal lubricating oil supply for the performance of the oscillating piston type rotary compression mechanism that compresses the working gas by making a revolving motion with oscillating with a substantially constant radius in a and 5a has not been clarified. . In order to clarify this, the present inventors supply oil into the working chamber by the intermittent oil supply method using the oil pocket 21 described with reference to FIG. 4 in a state where the pressure in the closed container is equal to the suction pressure. The relationship with the compressor performance was experimentally investigated by varying the volume of the oil pocket. FIG. 6 shows an example of the experimental result.

FIG. 6 shows the oil circulation rate in the refrigerating cycle (mass ratio of oil in the refrigerant, measured by the method described in Annex D of JIS B8606) and the coefficient of performance COP (= refrigeration) of the compressor. FIG. 4 is a performance characteristic diagram showing a relationship of (capacity / power consumption). Here, the refrigerant is R134a, and the experimental condition is the suction pressure Ps-= corresponding to the normal operation state of the refrigerator.
0.095 MPa, discharge pressure Pd = 1.043 MPa,
The rotation speed n is 3000 min ^-1 . The coefficient of performance COP of the compressor is 1.0 (shown by a dashed line) when the pressure in the closed vessel 3 is the discharge pressure and the internal lubrication is performed by the oil supplied by the pressure difference between the discharge pressure and the suction pressure. It is expressed by the ratio when the time is done.

As is apparent from FIG. 6, when the oil circulation rate is less than 0.1% by weight, the amount of internal lubrication supplied is insufficient and the sealing performance of the working chamber is reduced. The performance is lower than in the case of internal lubrication, and the performance can be improved more than in the case of internal lubrication by the differential pressure between the discharge pressure and the suction pressure by securing the oil supply rate of 0.1% by weight or more of the oil circulation rate. On the other hand, the upper limit of the oil circulation rate is determined within a range in which the heat transfer performance such as the heat transfer coefficient in the pipe of the heat exchanger and the pressure loss does not deteriorate in the refrigeration cycle characteristics. Usually, the upper limit is 1.0% by weight. When the oil circulation rate increases beyond 1.0%, in the case of a refrigerator, the evaporating temperature of the cooler increases and the cooling performance starts to decrease.

As described above, the oil amount of the internal lubrication suitable for the performance of the oscillating piston type rotary compressor is in the range of 0.1% by weight to 1.0% by weight in terms of the oil circulation rate of the refrigeration cycle. Was revealed. Accordingly, an oil supply mechanism for intermittently supplying the lubricating oil into the working chamber of the high-pressure compression element 5 by the oil pocket 21 that alternately moves between the lubricating oil reservoir in the closed vessel 3 and the working chamber of the high-pressure compression element 5. Is provided, an appropriate amount of oil can be reliably supplied by the operation of the positive displacement pump without depending on the differential pressure, so that the performance and reliability can be improved. Further, the oil supply amount is adjusted by this oil supply mechanism so that the oil circulation rate (mass ratio of oil in the refrigerant) in the refrigeration cycle is in the range of 0.1% by weight to 1.0% by weight at which the performance of the compressor is optimum. The heat transfer performance of the heat exchanger can be improved, and the reliability of the compressor can be ensured. Can be.

Next, a second embodiment of the present invention will be described with reference to FIGS.
This will be described with reference to FIG. FIG. 7 is a longitudinal sectional view of a swinging piston type compressor according to a second embodiment of the present invention, and FIG. 8 is an enlarged view of a main part of FIG.

In the second embodiment, the oil supply amount for the internal lubrication of the high-pressure compression element 5 is set to a value that is equal to the oil circulation rate of the refrigeration cycle.
As a method of maintaining the pressure within the range of 1% to 1.0%, oil used for internal lubrication of the low-pressure compression element 4 is used. That is, lubricating oil is supplied to the low-pressure compression element 4 for internal lubrication by a differential pressure between the intermediate pressure in the closed vessel 3 and the pressure in the working chamber, and the lubricating oil is discharged together with the refrigerant. Is guided to the suction side of the high-pressure compression element 5 and is used for internal lubrication of the high-pressure compression element 5.

In the case of the first embodiment described above, the working gas compressed by the low-pressure compression element 4 is discharged into the closed vessel 3 and is supplied to the internal lubrication of the low-pressure compression element 4 to be supplied to the working gas. The lubricating oil discharged together with the oil is separated from the working gas by a rapid decrease in the flow velocity in the space inside the closed container 3, and the oil contained in the suction gas of the high-pressure compression element 5 almost disappears. . Therefore, in the second embodiment, the oil required for internal lubrication is included in the suction gas of the high-pressure compression element 5 by lowering the separation efficiency of the lubricating oil in the discharge gas of the low-pressure compression element 4, thereby reducing the pressure of the high-pressure compression element 5. Compression element 5
The oil supply mechanism for internal lubrication is omitted. Specifically, the discharge pipe 16 of the low-pressure compression element 4 does not directly open into the closed casing 3, but communicates with the discharge space in the discharge muffler 12 through the discharge passage 9 a formed in the main bearing 9. An oil return hole 12 a communicating with the inside of the closed container 3 is provided below the discharge muffler 12. Therefore, the oil separation efficiency can be changed mainly by changing the internal volume of the discharge muffler 12, so that the oil circulation rate of the refrigeration cycle required for internal lubrication of the high-pressure compression element 5 is 0.1%. To 1.0%. Moreover, if more oil than necessary for internal lubrication of the high-pressure compression element 5 is discharged from the low-pressure compression element 4,
This extra oil is separated in the discharge muffler 12 and returned to the reservoir of the lubricating oil 20 in the sealed container 3 from the oil return hole 12a.

The oil separation mechanism provided in the middle of the flow path connecting the discharge section of the low-pressure compression element 4 and the suction section of the high-pressure compression element 5 described above, and the lubricating oil storage section described in the first embodiment. It is also possible to simultaneously use two oil supply mechanisms that intermittently supply oil to the working chamber of the high-pressure compression element 5 by means of an oil pocket that alternates between the working chamber of the high-pressure compression element and the working chamber of the high-pressure compression element.

In the above-described embodiment, the horizontal oscillating piston type compressor has been described as an example. However, the present invention is not limited to this. In addition, the present invention can be applied to a vertically mounted oscillating piston compressor in which the compression element 1 is disposed below the closed vessel 3. In the case of the vertical type, since the lower end of the drive shaft 6 is immersed in the lubricating oil 20, the centrifugal pump action by the rotation of the drive shaft can be used as the external lubrication of the compressor, and the lubrication utilizing the forward / backward movement of the vane 5b2. It is possible to make the structure simpler than the mechanism.

Although the displacement volume (theoretical suction volume) of the low-pressure compression element and the high-pressure compression element of the oscillating piston type compressor is not particularly mentioned, generally, when the discharge pressure Pd and the suction pressure Ps are used. It is known that the intermediate pressure Pm at which the compression power is minimized becomes Pm = √ (Ps × Pd) from the condition that the pressure ratio of each stage becomes equal,
It is desirable to determine the displacement of the low-pressure compression element and the high-pressure compression element so that they can be set substantially equal to the intermediate pressure Pm.

Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 9 is a configuration diagram of a refrigeration apparatus according to a third embodiment of the present invention. This third embodiment is an example applied to a home refrigerator.

The refrigerating cycle of this refrigerating apparatus includes the compressor 30 of the present invention described in the first embodiment, the condenser 31 for radiating heat, the dryer 32 for adsorbing moisture remaining in the cycle, and the capillary. Refrigerator decompression mechanism 35 composed of tubes, etc., Refrigerator evaporator 3 for cooling the inside of the refrigerator
3. Header 3, which is a tank for temporarily storing liquid refrigerant
7. A freezing compartment decompression mechanism 36 composed of a capillary tube and the like, a freezing compartment evaporator 34, and a header 38 serving as a tank for temporarily storing liquid refrigerant are communicated by piping. In this refrigeration cycle, the refrigerator decompression mechanism 35, the refrigerator evaporator 33, and the header 37 are connected in series, one side is connected to the condenser 31 side, and the other side is a high-pressure compressor of a swinging piston type compressor. It is connected to the suction side of element 5. The decompression mechanism 36 for the freezer compartment, the evaporator 34 for the freezer compartment, and the header 38 are connected in series, one side is connected to the condenser 31 side, and the other side is connected to the low-pressure compression element 4 of the oscillating piston compressor. Connected to the suction side. Fan 31a
Is for forcibly exchanging the heat of the condenser 31a with the outside air, the fan 33a is for forcibly exchanging the heat of the evaporator 33 for the refrigerator compartment with the air of the refrigerator compartment, and the fan 34a is for the evaporator 34 for the freezer compartment. Is forcibly exchanged heat with the freezing room air. Note that a broken line 39 indicates a refrigeration room and 40 indicates a freezer room.

By activating the compressor 30, the working fluid is compressed between the cylinders of the compression elements 4, 5 and the oscillating piston. The compressed high-temperature and high-pressure working gas is supplied to the high-pressure compression element 5 as indicated by a solid arrow.
Flows into the condenser 31 from the discharge pipe 18 of the fan 31
The heat is radiated and liquefied by the blowing action of a, and the pressure reducing mechanism 35,
At 36, the heat is adiabatically expanded to a low temperature and low pressure, and the heat in the refrigerator compartment 39 is absorbed by the refrigerator evaporator 33 and the fan 33a, and the heat in the refrigerator compartment 40 is cooled by the freezer evaporator 34 and the fan 34a. After the heat is absorbed and gasified, each header 37, 38
, The working gas exiting the refrigerator compartment evaporator 33 is sucked from the suction pipe 17 of the high-pressure compression element 5, and the working gas exiting the freezer compartment evaporator 34 is sucked from the suction pipe 15 of the low-pressure compression element 4. I will. In addition, an elongated copper tube usually called a capillary tube is used as the pressure reducing mechanisms 35 and 36.
In order to effectively utilize the cooling power of the suction gas and prevent dew on the surface of the suction pipe, heat is exchanged with the suction pipe in each suction path.

Generally, the temperature in the freezer compartment of a refrigerator is -1.
The temperature in the refrigerator is kept at 8 ° C. and the temperature in the refrigerator compartment is kept at 3 ° C. However, since the evaporators corresponding to the respective temperatures in the refrigerator are used, it has two evaporation temperature levels, that is, suction pressure levels. By combining the compressor 30, the low-pressure compression element 4 sucks the working gas from the freezer evaporator 34 having a low suction pressure level and compresses it to the evaporator pressure level (intermediate pressure) of the refrigerator compartment evaporator 33. And then the high-pressure compression element 5
The working gas from the refrigerating compartment evaporator 33 is also added to compress the gas to the discharge pressure (condensing pressure). The cycle can be improved by about 30% compared to the cycle of the evaporation temperature, and since the compressor 30 of the present invention is mounted, a refrigeration system having excellent energy efficiency and high reliability can be obtained. The method of controlling the cooling power in the refrigerator mainly includes the electric element 2 and the evaporator fans 33a, 3b.
This is realized by controlling the rotation speed of the motor 4a by inverter control or the like.

Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 10 is a configuration diagram of a refrigeration apparatus according to a fourth embodiment of the present invention. The fourth embodiment is an example applied to an air conditioner.

The refrigerating cycle of this refrigerating apparatus is a heat pump cycle capable of performing a cooling and heating operation. The refrigerating cycle includes the compressor 30, the outdoor heat exchanger 41, and the expansion valve 42 for performing two-stage expansion described with reference to FIG. And 43, a gas-liquid separator 44 disposed between the two expansion valves 42 and 43, a gas extraction pipe 44a for taking out only gas refrigerant from the gas-liquid separator 44, expansion valves 42, 43, and a gas-liquid separator 44. Check valves 45a, 45b, 45c, 45 arranged so as to surround
d, the indoor heat exchanger 46, the four-way valve 47, and the suction accumulator 48 are connected by piping. The fan 41a forcibly exchanges heat between the outdoor heat exchanger 41 and the outside air, and the fan 46a forcibly exchanges heat between the indoor heat exchanger 46 and the indoor air. Note that a dashed line 49 indicates an outdoor unit, and 50 indicates an indoor unit.

When the hermetic two-stage rotary compressor 30 is started, the working gas (for example, R407)
C, R410A, R290, etc.).

In the cooling operation, the high-temperature and high-pressure working gas compressed by the high-pressure compression element 5 is expressed as
From the discharge pipe 18 through the four-way valve 47, the outdoor heat exchanger 4
1 and radiates and liquefies by the blowing action of the fan 41a,
After passing through the check valve 45a, it is throttled by the first-stage expansion valve 42 to have a medium temperature / medium pressure and enters the gas-liquid separator 44, where it is divided into a gas refrigerant and a liquid refrigerant, and the gas refrigerant is subjected to gas extraction. Tube 44
a is sucked into the suction pipe 17 of the high-pressure compression element 5. On the other hand, the liquid refrigerant is throttled again by the second-stage expansion valve 43 and becomes low temperature and low pressure, passes through the check valve 45b, absorbs indoor heat with the indoor heat exchanger 46 and the fan 46a, and gasifies. It is sucked into the suction pipe 15 of the low-pressure compression element 4 through the four-way valve 47 and the suction accumulator 48.

In the case of the heating operation, the four-way valve 47 is switched, so that it flows in the opposite direction to the cooling operation as indicated by the solid line arrow, and the high-temperature and high-pressure operation compressed by the high-pressure compression element 5 is performed. The gas flows from the discharge pipe 18 through the four-way valve 47 into the indoor heat exchanger 46, radiates and liquefies the room by the blowing action of the fan 46a, and passes through the check valve 45c to the first-stage expansion valve 42. The gas refrigerant enters the gas-liquid separator 44 at a medium temperature and a medium pressure and is separated into a gas refrigerant and a liquid refrigerant. The gas refrigerant is sucked into the suction pipe 17 of the high-pressure compression element 5 from the gas extraction pipe 44a. The liquid refrigerant is throttled again by the second-stage expansion valve 43 and becomes low temperature and low pressure, passes through the check valve 45d, absorbs outdoor heat with the outdoor heat exchanger 41 and the fan 41a, and gasifies. Through the one-way valve 47 and the suction accumulator 48 It sucked into the suction pipe 15 of the element 4.

In this refrigeration cycle, a gas-liquid separator 44 is provided in the middle of the expansion process, and the gas refrigerant that does not contribute to the cooling power is sucked into the high-pressure compression element 5 through the gas extraction pipe 44a without needless expansion and compression. As a result, the coefficient of performance COP of the refrigeration cycle is improved, and the compressor of the present invention is mounted. And a highly reliable air conditioning system can be obtained.

The present invention is not limited to the refrigerating apparatus shown in FIGS. 9 and 10, but simply uses a two-stage compressor of the present invention instead of a conventional single-stage hermetic compressor. It is also possible. In this case as well, the two-stage compression mechanism equipped with an internal lubrication mechanism that steadily and properly supplies oil to the working chamber of the high-pressure compression element by setting the internal pressure of the closed vessel to the intermediate pressure, and achieves high performance and high reliability of the compressor And the energy efficiency of the system can be improved. In addition, it becomes feasible to use CFC-free.

[0066]

According to the present invention, the cost can be reduced,
In addition, it is possible to obtain a small and high-performance and highly reliable swinging piston type compressor and refrigeration apparatus.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a 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 sectional view taken along line BB of FIG. 1;

FIG. 4 is an operation explanatory view of an oil supply mechanism of the swinging piston type compressor of FIG. 1;

FIG. 5 is a perspective view showing another modified example of the oscillating piston provided with an oil pocket used in the oscillating piston type compressor of FIG. 1;

FIG. 6 is a performance characteristic diagram showing a relationship between an oil circulation rate of a refrigeration cycle and a coefficient of performance COP.

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

FIG. 8 is an enlarged view of a main part of FIG. 7;

FIG. 9 is a configuration diagram of a refrigeration apparatus according to a third embodiment of the present invention.

FIG. 10 is a configuration diagram of a refrigeration apparatus according to a fourth embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Compression element, 2 ... Electric element, 3 ... Airtight container, 4 ... Low pressure compression element, 4a ... Cylinder, 4a1 ... Cylindrical hole part, 4a
2 ... Cylindrical hole, 4b ... Swinging piston, 4b1 ... Roller,
4b2: Vane, 5: High-pressure compression element, 5a: Cylinder, 5a1: Cylindrical hole, 5a2: Cylindrical hole, 5b: Swing piston, 5b1: Roller, 5b ": Vane, 6: Drive shaft, 6a, 6b ... Eccentric shaft portion, 7 ... Sliding member, 8 ... Partition plate, 9 ... Main bearing, 10 ... Sub bearing, 10a ... Fluid diode, 11 ... Discharge valve device, 12 ... Discharge muffler, 13 ... Discharge valve device, 14 ... Discharge Cover, 14a ... oiling cover, 1
5 suction pipe, 16 discharge pipe, 17 suction pipe, 18 discharge pipe, 19 intercooler, 20 lubricating oil, 21 oil pocket, 30 closed two-stage rotary compressor,
31 ... condenser, 32 ... dryer, 33 ... refrigerator evaporator, 34 ... freezer compartment evaporator, 35, 36 ... decompression mechanism, 3
7, 38: header, 39: refrigerator compartment, 40: freezer compartment, 41
... outdoor heat exchanger, 42, 43 ... expansion valve, 44 ... gas-liquid separator, 45a, 45b, 45c, 45d ... check valve, 46 ...
Indoor heat exchanger, 47: 4-way valve, 48: Suction accumulator, 49: Outdoor unit, 50: Indoor unit.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Kenichi Oshima 800, Tomita, Ohira-machi, Ohira-machi, Shimotsuga-gun, Tochigi Prefecture Inside the Cooling and Refrigerating Business Dept., Hitachi, Ltd. (72) Inventor Shigeya Kawanan 800, Tomita, Oda-machi, Ohira-cho, Shimotsuga-gun, Tochigi Stock (72) Inventor Takeshi Kono 502-Kandate-cho, Tsuchiura-shi, Ibaraki F-term (Mechanical Research Laboratory) 3H029 AA04 AA15 AA21 AB03 AB08 BB06 BB10 BB38 BB42 BB44 CC06 CC23 CC58

Claims (10)

[Claims] An electric element and a compression element are connected and arranged in a closed container via a drive shaft, wherein the compression element has a low-pressure compression element and a high-pressure compression element, and each of the compression elements is A cylinder whose both end surfaces are closed, a roller and a vane have an integral swinging piston, and the swinging piston is arranged in the cylinder so as to be able to revolve with swinging, and the vane is a working chamber in the cylinder. Is divided into a suction chamber side and a compression chamber side,
The inside of the closed container is maintained at a pressure lower than the discharge pressure of the high-pressure compression element, and the oil supply is performed via an oil storage unit that intermittently communicates with the working chamber side and the oil supply side of the high-pressure compression element. An oscillating piston type compressor provided with an oil supply mechanism for intermittently supplying lubricating oil from the side to the working chamber side. 2. A motor-driven element and a compression element are connected to each other via a drive shaft in a closed container, and the compression element has a low-pressure compression element and a high-pressure compression element. A cylinder closed at both ends, a roller and a vane have an integral swing piston, and the swing piston is arranged so as to be able to revolve with oscillation in the cylinder, and the vane moves inside the cylinder together with the roller. It is divided into a suction chamber and a compression chamber, and the inside of the closed container is set at an intermediate pressure between the suction pressure and the discharge pressure of the compression element, and the pressure chamber is intermittently interposed between the suction chamber side and the oil supply side in the cylinder of the high pressure compression element. A swing piston type compressor provided with an oil supply mechanism for intermittently supplying lubricating oil from the oil supply side to the suction chamber side via an oil storage section which is in fluid communication. 3. An electrically driven element and a compression element are disposed in a horizontally long sealed container by being laterally connected via a drive shaft, wherein the compression element has a low-pressure compression element and a high-pressure compression element, Each of the compression elements is provided side by side with the drive shaft, and each of the compression elements has a cylinder whose both end surfaces are closed, and a swing piston in which rollers and vanes are integrated, and the swing piston is provided in the cylinder. The vane is arranged so as to be able to revolve with swinging, the vane partitions the working chamber in the cylinder into a suction chamber side and a compression chamber side, and the inside of the closed vessel is maintained at a pressure lower than the discharge pressure of the high-pressure compressor. In addition, an oil pocket intermittently communicating with the suction chamber side in the cylinder of the high-pressure compression element and the lubricating oil side at the bottom of the hermetic container is formed in the vane so that the lubricating oil is formed on the suction chamber side. That an intermittent oil supply mechanism was provided. Oscillating piston type compressor. 4. A motor-driven element and a compression element are laterally connected via a drive shaft in a horizontally long closed container, and the compression element has a low-pressure compression element and a high-pressure compression element. Each of the compression elements is provided side by side with the drive shaft, and each of the compression elements has a cylinder whose both end surfaces are closed, and a swing piston in which rollers and vanes are integrated, and the swing piston is provided in the cylinder. The vane is arranged so as to be able to revolve with swinging, the vane partitions the working chamber in the cylinder into a suction chamber side and a compression chamber side, and the inside of the closed vessel is maintained at a pressure lower than the discharge pressure of the high-pressure compressor. In addition, a corner cutout is formed in the vane so as to intermittently communicate with the suction chamber side in the cylinder of the high-pressure compression element and the lubricating oil side at the bottom of the hermetic container, and the lubricating oil is supplied to the suction chamber side. That a refueling mechanism is provided intermittently Oscillating piston type compressor. 5. An electric element and a compression element are connected and arranged via a drive shaft in a closed container, wherein the compression element has a low-pressure compression element and a high-pressure compression element, and each of the compression elements is A cylinder closed at both ends, a roller and a vane have an integral swing piston, and the swing piston is arranged so as to be able to revolve with oscillation in the cylinder, and the vane moves inside the cylinder together with the roller. It is partitioned into a suction chamber and a compression chamber, and the inside of the closed container is maintained at a pressure lower than the discharge pressure of the high-pressure compressor, and connects the discharge part of the low-pressure compression element to the suction part of the high-pressure compression element. An oscillating piston type compressor having a flow path. 6. A motor-driven element and a compression element are connected and arranged in a closed container via a drive shaft, wherein the compression element has a low-pressure compression element and a high-pressure compression element, and each of the compression elements is A cylinder closed at both ends, a roller and a vane have an integral swing piston, and the swing piston is arranged so as to be able to revolve with oscillation in the cylinder, and the vane moves inside the cylinder together with the roller. The suction chamber and the compression chamber are partitioned, and the inside of the closed container is set to the discharge pressure of the low-pressure compression element, and in the middle of a flow path connecting the discharge part of the low-pressure compression element to the suction part of the high-pressure compression element. An oscillating piston compressor characterized by having an oil separation mechanism provided in the compressor. 7. A refrigeration cycle is configured by connecting a compressor, a condenser, a decompression mechanism, and an evaporator with piping, and the piston-type compressor includes a motor-driven element and a compression element in a closed vessel via a drive shaft. The compression elements have a low-pressure compression element and a high-pressure compression element, and each compression element has a cylinder whose both end faces are closed, and a swinging piston in which rollers and vanes are integrated. The swing piston is arranged so as to be able to revolve with swing in the cylinder, the vane divides a working chamber in the cylinder into a suction chamber side and a compression chamber side, and the high pressure From the oil supply side to the working chamber side via an oil storage part intermittently communicating with the working chamber side and the oil supply side of the high-pressure compression element while maintaining the pressure at a pressure lower than the discharge pressure of the compressor for working. That an oil supply mechanism for intermittently supplying lubricating oil Characterized refrigeration equipment. 8. A refrigeration cycle is configured by connecting a compressor, a condenser, a pressure reducing mechanism, and an evaporator with piping, wherein the compressor comprises:
An electric element and a compression element are connected and arranged in a closed container via a drive shaft, and the compression element has a low-pressure compression element and a high-pressure compression element, and each of the compression elements has both end faces closed. The cylinder, the roller and the vane have an integral swing piston, the swing piston is arranged so as to be able to revolve with the swing in the cylinder, and the vane connects the working chamber in the cylinder to the suction chamber side. And the pressure in the closed vessel is maintained at a pressure lower than the discharge pressure of the high-pressure compressor, and intermittently between the suction chamber and the oil supply side in the cylinder of the high-pressure compression element. Lubricating oil is intermittently supplied from the oil supply side to the suction chamber side through the communicating oil storage portion to make the oil circulation rate in the refrigeration cycle 0.1 to 1.0% by weight. A refrigeration apparatus comprising a mechanism. 9. A refrigeration cycle is configured by connecting a compressor, a condenser, a decompression mechanism, and an evaporator with piping, wherein the compressor comprises:
An electric element and a compression element are connected and arranged in a closed container via a drive shaft, and the compression element has a low-pressure compression element and a high-pressure compression element, and each of the compression elements has both end faces closed. The cylinder, the roller and the vane have an integral swing piston, and the swing piston is arranged in the cylinder so as to be able to revolve with the swing, and the vane moves in the cylinder together with the roller in the suction chamber and the compression chamber. And the inside of the closed container is maintained at a pressure lower than the discharge pressure of the high-pressure compressor, and the oil circulation rate in the refrigeration cycle is set to 0.1% by weight to 1.0% by weight. A refrigerating apparatus, wherein a flow path is provided from a discharge part of the low-pressure compression element to a suction part of the high-pressure compression element. 10. A compressor, a condenser, a decompression mechanism for a refrigerator,
The refrigerating compartment evaporator, the freezing compartment decompression mechanism and the freezing compartment evaporator are connected by piping to constitute a refrigerating cycle, and the compressor has a drive shaft including an electric element and a compression element in a horizontally long closed container. The compression elements include a low-pressure compression element and a high-pressure compression element, and each of the compression elements is provided side by side with the drive shaft, and each of the compression elements has an end face. The cylinder and the roller and the vane, which are closed, have an integral swing piston, and the swing piston is arranged so as to be able to revolve with oscillation in the cylinder, and the vane sucks the working chamber in the cylinder. Partitioned into a chamber side and a compression chamber side,
The inside of the closed container is set at the discharge pressure of the low-pressure compression element, and an oil pocket intermittently communicating with the suction chamber side in the cylinder of the high-pressure compression element and the lubricating oil side at the bottom of the closed container. And an oil supply mechanism for intermittently supplying lubricating oil from the lubricating oil side at the bottom to the suction chamber side so that an oil circulation rate in the refrigeration cycle is 0.1% by weight to 1.0% by weight. The condenser communicates with the discharge side of the high-pressure compression element, and the refrigerating-room depressurizing mechanism and the refrigerating-room evaporator are connected in series, and the outlet side of the condenser and the suction side of the high-pressure compression element are connected. Wherein the decompression mechanism for the freezing room and the evaporator for the freezing room are connected in series and provided between the outlet side of the condenser and the suction side of the low-pressure compression element. Refrigeration equipment.