GB2553712A

GB2553712A - Rotary compressor and vapor-compression refrigeration cycle device

Info

Publication number: GB2553712A
Application number: GB1716659.6A
Authority: GB
Inventors: Moroe Shogo; Yokoyama Tetsuhide; Takahashi Shinichi; Sugiura Kanichiro
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2015-05-08
Filing date: 2015-05-08
Publication date: 2018-03-14
Anticipated expiration: 2035-05-08
Also published as: JPWO2016181446A1; JP6391816B2; WO2016181446A1; GB2553712B; GB201716659D0

Abstract

The present invention has a valve mechanism (50) that blocks an oil-supply flow path during non-compression operation and opens same during compression operation, said oil-supply flow path guiding lubricating oil that is inside a sealed container (3), to a gap between a vane (24) and a vane groove (29), via a vane rear chamber (25).

Description

(56) Documents Cited:

EP 1806475 A1 JP 2010261347 A (58) Field of Search: INT CL F04C

F04C 23/00 (2006.01)

WO 2011/030809 A1 JP 2010116836 A (71) Applicant(s):

Mitsubishi Electric Corporation (Incorporated in Japan)

7-3 Marunouchi 2-chome, Chiyoda-ku, Tokyo 100-8310, Japan (72) Inventor(s):

Shogo Moroe Tetsuhide Yokoyama Shinichi Takahashi Kanichiro Sugiura (74) Agent and/or Address for Service:

Mewburn Ellis LLP

City Tower, 40 Basinghall Street, LONDON, Greater London, EC2V 5DE, United Kingdom (54) Title ofthe Invention: Rotary compressor and vapor-compression refrigeration cycle device Abstract Title: Rotary compressor and vapor-compression refrigeration cycle device (57) The present invention has a valve mechanism (50) that blocks an oil-supply flow path during non-compression operation and opens same during compression operation, said oil-supply flow path guiding lubricating oil that is inside a sealed container (3), to a gap between a vane (24) and a vane groove (29), via a vane rear chamber (25).

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FIG. 15

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DESCRIPTION

Title of Invention

ROTARY COMPRESSOR AND VAPOR COMPRESSION TYPE REFRIGERATION

CYCLE APPARATUS

Technical Field [0001]

The present invention relates to a rotary compressor used in a heat pump apparatus, and a vapor compression type refrigeration cycle apparatus provided with the rotary compressor. In particular, the present invention relates to a rotary compressor with improved energy saving performance in an operating condition close to an actual load, and a vapor compression type refrigeration cycle apparatus provided with such a rotary compressor.

Background Art [0002]

In a heat pump apparatus such as an air-conditioning apparatus or a water heater, a vapor compression type refrigeration cycle apparatus having a rotary compressor is typically employed. This means that a heat pump apparatus is equipped with a refrigeration cycle formed by connecting a rotary compressor, a condenser, a decompression unit, and an evaporator via pipes, and is configured to perform operation corresponding to the usage (air conditioning, water heating, or the like, for example).

[0003]

Meanwhile, energy saving regulations for air-conditioning apparatuses are strengthened in various countries in recent years, and the operation standard is being changed to that similar to an actual load. In Japan, an efficiency improvement has been shown by means of cooling and heating average COP conventionally. However, it was changed to Annual Performance Factor (APF) since 2011. Further, it is conceivable that energy saving performance standards for air-conditioning apparatuses and water heaters will be further changed to new standards close to an actual load.

For example, assuming that the rated heating capacity required at the time of startup of an air-conditioning apparatus is 100%, for example, constantly required heating capacity is about 10% to 50%. The efficiency in such a low load region affects the actual APF more than that of the rated capacity.

[0004]

Therefore, as a means of regulating the cooling and heating capacity, ON-OFF control has been used, conventionally. However, ON-OFF control involves a problem that a temperature control fluctuation range and vibration noises are increased, a problem that the energy saving performance is deteriorated, and the like. Accordingly, in order to improve the energy saving performance, inverter control that varies the rotation speed of a motor for driving a rotary compressor has been widespread in recent years.

[0005]

In recent years, an air-conditioning apparatus is required to shorten startup time and is required to be operated in a harder environment (low temperature or high temperature). As such, rated capacity of a certain level or higher is needed.

Meanwhile, as houses have higher heat insulating property, constantly required capacity is decreasing, and the capacity range at the time of operation is widened. Accordingly, a rotation speed variable range of a rotary compressor by the inverter is expanded, and a rotation speed range for which high efficiency of the rotary compressor is required tends to expand. Therefore, in a conventional air-conditioning apparatus, it is difficult to maintain high efficiency of a rotary compressor while continuously operating the rotary compressor with a low rotation speed under a low load capacity condition.

[0006]

In view of the above, a rotary compressor having a means capable of mechanically changing the displacement volume (mechanical capacity control unit) is attracting attention again. For example, Patent Literature 1 and Patent Literature 2 disclose a rotary compressor having two compression mechanisms namely a first compression mechanism and a second compression mechanism. In the case of a high load, both compression mechanisms perform compressing operation, while in the case of a low load, one of the compression mechanisms performs compressing operation and the other compression mechanism performs cylinder resting operation (noncompressing operation), whereby the refrigerant circulation flow rate is halved so that the capacity is halved.

[0007]

In the rotary compressor described in Patent Literature 1, a vane of the compression mechanism is accommodated in a vane groove reciprocatively, and a rear end portion of the vane locates in a vane back chamber communicating with the vane groove. The vane back chamber is configured to communicate with the inner space of a sealed container to receive the pressure (high pressure) of the inner space, and high pressure acts on the rear end portion of the vane.

[0008]

In the compressing operation, low-pressure refrigerant is guided to the cylinder chamber of the compression mechanism, whereby low to intermediate pressure acts on the vane front end. Further, high pressure acts on the rear end portion of the vane, as described above. Therefore, a pressure difference is caused between the front end and the rear end of the vane. Due to an effect of the pressure difference, the front end portion of the vane is pressed to be brought into contact with the piston. Thereby, normal compressing operation is performed.

[0009]

In the cylinder resting operation, by the switching mechanism, high-pressure refrigerant is guided to the cylinder chamber whereby high pressure acts on both the front end portion and the rear end portion of the vane to eliminate a pressure difference between the front end and the rear end of the vane. As there is no pressure difference, the front end portion of the vane is separated from the outer peripheral face of the piston, whereby compression action is not performed.

[0010]

Even in the case of a rotary compressor described in patent Literature 2, at the time of compressing operation, suction pressure (low pressure) acts on the front end portion of a vane, and discharge pressure (high pressure) acts on the rear end portion, like those described in Patent Literature 1. In Patent Literature 2, the vane back chamber has a permanent magnet therein. The permanent magnet generates attractive magnetic force that attracts the vane in a direction away from the piston. Accordingly, in Patent Literature 2, in addition to the pressing force in a direction of making the vane contact with the piston, attractive magnetic force in a direction of separating the vane from the piston also acts on the vane at the same time. When the pressing force is smaller than the attractive magnetic force, the vane is separated from the piston and cylinder resting operation is performed, while when the pressing force is larger than the attractive magnetic force, the vane is brought into contact with the piston, and compressing operation is performed.

[0011]

In either Patent Literature 1 or Patent Literature 2, at the time of low load, one of the compression mechanisms is operated in a cylinder resting operation (noncompressing operation) to halve the refrigerant circulation flow rate, whereby operation can be performed without reducing the rotation speed of the motor. Accordingly, compressor efficiency can be improved.

Citation List

Patent Literature [0012]

Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2005-171847

Patent Literature 2: International Publication No. WO 2014/175429 Summary of Invention Technical Problem [0013]

In Patent Literature 1 and Patent Literature 2, switching mechanisms for switching between the compressing operation and the cylinder resting operation are different. However, both Patent Literatures are intended to improve the compression efficiency by applying compressing operation at the time of high load and applying cylinder resting operation at the time of low load. Further, in both Patent Literatures, the vane back chamber is configured to communicate with the inner space of a sealed container to allow the high pressure to act on the vane back surface. In other words, the vane back chamber communicates with a lubricating oil storage unit in the sealed container. At the time of compressing operation, lubricating oil in the lubricating oil storage unit is guided to the gap between the vane and the vane groove via the vane back chamber to reduce the sliding resistance between them.

[0014]

At the time of cylinder resting operation, the vane moves to the vane back chamber side in the vane groove, and the rear end portion of the vane is positioned inside the vane back chamber. As such, the length of the portion of the vane inserted in the vane groove is shortened compared with that at the time of compressing operation. In other words, the length in the inserting direction (reciprocating direction) of the gap between the vane and the vane groove is shortened. Accordingly, the passage resistance of the passage from the lubricating oil storage unit to the vane back chamber, and further to the cylinder chamber via the vane and the vane groove is reduced. Therefore, high-temperature lubricating oil in the lubricating oil storage unit flows to the cylinder chamber through the vane back chamber and the gap.

[0015]

Here, when the lubricating oil flows into the cylinder chamber during the cylinder resting operation, the lubricating oil in the cylinder chamber stays therein because refrigerant does not move during the cylinder resting operation. As the inside of the cylinder chamber has a suction pressure, the pressure of the lubricating oil staying in the cylinder chamber and high-temperature refrigerant molted in the lubricating oil gradually drops. Along with a drop of the pressure, the refrigerant is separated from the lubricating oil and flows backward to the pipe of the suction side. In the case, the high-temperature refrigerant flowing backward and low-temperature refrigerant flowing from refrigerant circuit to the compression mechanism are mixed. As a result, there is a problem that the refrigerant flowing to the compression mechanism of the compressing operation side is heated and the temperature rises, whereby a loss increases.

[0016]

The present invention has been made to solve the problem described above.

An object of the present invention is to achieve a rotary compressor and a vapor compression type refrigeration cycle apparatus that performs switching between compressing operation and cylinder resting operation, and suppresses a backward flow of lubricating oil at the time of cylinder resting operation to improve the compressor efficiency.

Solution to Problem [0017]

A rotary compressor according to an embodiment of the present invention includes a sealed container that stores lubricating oil, and a plurality of compression mechanisms accommodated in the sealed container, each of the compression mechanisms being configured to compress refrigerant and discharge the refrigerant to an inner space of the sealed container. Each of the compression mechanisms includes a cylinder having a cylinder chamber, a piston that eccentrically rotates in the cylinder chamber, a vane configured such that a front end of the vane is brought into contact with the piston to divide the cylinder chamber into a plurality of spaces, a vane groove formed in the cylinder, the vane groove accommodating the vane to allow the vane to reciprocate, and a vane back chamber formed in the cylinder in communication with the vane groove on a side opposite to the vane groove with respect to the cylinder chamber, the vane back chamber accommodating a rear end portion of the vane. Any of the compression mechanisms has a switching mechanism to perform switching between compressing operation and non-compressing operation. The compressing operation is operation of compressing the refrigerant in a state where the front end of the vane is in contact with the piston when the piston rotates, and the non-compressing operation is operation in which the front end of the vane is separated from the piston and the refrigerant is not compressed. The rotary compressor has a valve mechanism that opens an oil supply passage for guiding the lubricating oil in the sealed container to a gap between the vane and the vane groove via the vane back chamber at the time of the compression operation, and blocks the oil supply passage at the time of the noncompression operation.

Advantageous Effects of Invention [0018]

According to the present invention, switching can be ensured between compressing operation and non-compressing operation, and a backward flow of lubricating oil can be suppressed at the time of cylinder resting operation. Accordingly, compressor efficiency can be improved.

Brief Description of Drawings [0019] [Fig. 1] Fig. 1 is a schematic vertical cross-sectional view illustrating a structure of a rotary compressor 100 according to Embodiment 1 of the present invention.

[Fig. 2] Fig. 2 is a schematic horizontal cross-sectional view illustrating a structure of the rotary compressor 100 according to Embodiment 1 of the present invention in which Fig. 2(a) is a schematic horizontal cross-sectional view of a first compression mechanism 10, and Fig. 2(b) is a schematic horizontal cross-sectional view of a second compression mechanism 20.

[Fig. 3] Fig. 3 is an operation explanatory diagram of a valve mechanism 50 of the rotary compressor 100 according to Embodiment 1 of the present invention, in which Fig. 3(a) is a schematic cross-sectional view around the valve mechanism 50 at the time of compression operation, and Fig. 3(b) is a schematic cross-sectional view around the valve mechanism 50 at the time of cylinder resting operation.

[Fig. 4] Fig. 4 is an operation explanatory diagram of the valve mechanism 50 of the rotary compressor 100 according to Embodiment 1 of the present invention, in which Fig. 4(a) is a schematic top view around the valve mechanism 50 at the time of compression operation, and Fig. 4(b) is a schematic top view around the valve mechanism 50 at the time of cylinder resting operation.

[Fig. 5] Fig. 5 is a perspective view of a yoke 52 of the rotary compressor 100 according to Embodiment 1 of the present invention.

[Fig. 6] Fig. 6 is a drawing illustrating modifications of the shape of a notch 52a formed in the yoke 52 of the rotary compressor 100 according to Embodiment 1 of the present invention.

[Fig. 7] Fig. 7 is a drawing illustrating a modification of a position of a notch 24c formed in a second vane 24 of the rotary compressor 100 according to Embodiment 1 of the present invention, that is a top view around the notch 24c.

[Fig. 8] Fig. 8 is a drawing illustrating modifications of the shape of the notch 24c formed in the second vane 24 of the rotary compressor 100 according to Embodiment 1 of the present invention.

[Fig. 9] Fig. 9 is a schematic vertical cross-sectional view illustrating a structure of a rotary compressor 100 according to Embodiment 2 of the present invention.

[Fig. 10] Fig. 10 is a schematic cross-sectional view around a valve mechanism 50A of a rotary compressor 100 according to Embodiment 3 of the present invention.

[Fig. 11] Fig. 11 is a perspective view of a yoke 52 of the rotary compressor 100 according to Embodiment 3 of the present invention.

[Fig. 12] Fig. 12 is a schematic cross-sectional view around the valve mechanism 50A of the rotary compressor 100 according to Embodiment 3 of the present invention.

[Fig. 13] Fig. 13 is a top view around a valve mechanism 50B at the time of cylinder resting operation of a rotary compressor 100 according to Embodiment 4 of the present invention.

[Fig. 14] Fig. 14 is a top view around the valve mechanism 50B in a state where an upper oil supply passage forming member 53a is removed from the second compression mechanism 20 of the rotary compressor 100 according to Embodiment 4 of the present invention, in which Fig. 14(a) illustrates a state at the time of compressing operation and Fig. 14(b) illustrates a state at the time of cylinder resting operation.

[Fig. 15] Fig. 15 is a perspective view of a second vane 24 of the rotary compressor 100, seen from the rear end portion 24b side, according to Embodiment 4 of the present invention.

[Fig. 16] Fig. 16 is a diagram illustrating a modification of an intermediate holding member 54 of the rotary compressor 100 according to Embodiment 4 of the present invention.

[Fig. 17] Fig. 17 is a drawing illustrating modifications of the second vane 24 of the rotary compressor 100 according to Embodiment 4 of the present invention.

[Fig. 18] Fig. 18 is a configuration diagram illustrating a vapor compression type refrigeration cycle apparatus 500 according to Embodiment 5 of the present invention. Description of Embodiments [0020]

An example of a rotary compressor 100 according to the present invention will be described below based on the drawings. It should be noted that a size correlation between constituent members may not be the same as actual one in the drawings described later. Further, in a vertical cross-sectional view and a horizontal crosssectional view, three-dimensional positional relations among discharge ports 18 and 28 and cylinder suction passages 17 and 27 do not necessarily match. In the drawings described below including Fig. 1, those denoted by the same reference numerals or reference characters are identical or equivalent that apply to the entire description of the embodiments provided below. Further, the forms of the constituent elements described in the entire description are provided for illustrative purposes, and are not limited to the forms described in the description. Furthermore, regarding high and low of temperature, pressure, and the like, high, low, and the like are not defined in a relationship with absolute values particularly. They are defined relatively according to the states, operation, and the like in the system, devices, and the like.

[0021]

Embodiment 1.

[Configuration of rotary compressor 100]

Fig. 1 is a schematic vertical cross-sectional view illustrating a structure of a rotary compressor 100 according to Embodiment 1 of the present invention. Fig. 2 is a schematic horizontal cross-sectional view illustrating the structure of the rotary compressor 100 according to Embodiment 1 of the present invention, in which Fig. 2(a) is a schematic horizontal cross-sectional view of a first compression mechanism 10, and Fig. 2(b) is a schematic horizontal cross-sectional view of a second compression mechanism 20. It should be noted that Figs. 1 and 2 illustrate the rotary compressor 100 in which the first compression mechanism 10 is in a compressing state and the second compression mechanism 20 is in a non-compressing state (cylinder resting state).

[0022]

The rotary compressor 100 is used as a constituent element of a refrigeration cycle adopted in a heat pump apparatus such as an air-conditioning apparatus or a water heater, for example. Further, the rotary compressor 100 has a function of sucking gaseous fluid, compressing it to be in a high-temperature and high-pressure state, and discharging it.

The rotary compressor 100 according to Embodiment 1 includes, in an inner space 7 of a sealed container 3, a compression mechanism 99 having the first compression mechanism 10 and the second compression mechanism 20, and a motor 8 that drives the first compression mechanism 10 and the second compression mechanism 20 via a drive shaft 5.

[0023]

The sealed container 3 is, for example, a cylindrical sealed container in which an upper end portion and a lower end portion are closed. A bottom portion of the sealed container 3 serves as a lubricating oil storage unit 3a for storing lubricating oil for lubricating the compression mechanism 99. In an upper portion of the sealed container 3, a compressor discharge pipe 2 is provided to communicate with the inner space 7 of the sealed container 3.

[0024]

The motor 8 is configured such that the rotation speed thereof is variable by the inverter control or the like, for example. The motor 8 includes a stator 8b and a rotor 8a. The stator 8b is formed to be in a substantially cylindrical shape, and the outer periphery is fixed to the sealed container 3 by shrink fit or the like, for example. On the stator 8b, a coil to which electric power is supplied from an outside power source is wound. The rotor 8a is in a substantially cylindrical shape and is disposed in an inner circumference portion of the stator 8b with a given space from the inner circumferential surface of the stator 8b. To the rotor 8a, the drive shaft 5 is fixed, whereby the motor 8 and the compression mechanism 99 are connected via the drive shaft 5. This means that when the motor 8 rotates, rotary power is transmitted to the compression mechanism 99 via the drive shaft 5.

[0025]

The drive shaft 5 includes a long shaft portion 5a constituting an upper portion of the drive shaft 5, a short shaft portion 5b constituting a lower portion of the drive shaft 5, eccentric pin shaft portions 5c and 5d and an intermediate shaft portion 5e formed between the long shaft portion 5a and the short shaft portion 5b. Here, the eccentric pin shaft portion 5c is formed such that the center axis thereof is eccentric by a predetermined distance from the center axis of the long shaft portion 5a and the short shaft portion 5b, and is disposed in a first cylinder chamber 12 of the first compression mechanism 10 described below. Further, the eccentric pin shaft portion 5d has a center axis that is eccentric by a predetermined distance from the center axis of the long shaft portion 5a and the short shaft portion 5b, and is disposed in a second cylinder chamber 22 of the second compression mechanism 20 described below.

[0026]

Further, the eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are disposed such that the phases thereof are shifted by 180 degrees. The eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are connected by the intermediate shaft portion 5e. It should be noted that the intermediate shaft portion 5e is disposed in a through hole of an intermediate partition plate 4 described below. In the drive shaft 5 configured in this manner, the long shaft portion 5a is rotatably supported by a bearing 60a of a first support member 60, and the short shaft portion 5b is rotatably supported by a bearing 70a of a second support member 70.

This means that the drive shaft 5 is configured such that the eccentric pin shaft portions 5c and 5d perform eccentric rotary motion in the first cylinder chamber 12 and the second cylinder chamber 22.

[0027]

The compression mechanism 99 includes the rotary type first compression mechanism 10 provided to an upper portion and the rotary type second compression mechanism 20 provided to a lower portion. The first compression mechanism 10 and the second compression mechanism 20 are disposed below the motor 8. The compression mechanism 99 is configured such that a first support member 60, a first cylinder 11 constituting the first compression mechanism 10, the intermediate partition plate 4, a second cylinder 21 constituting the second compression mechanism 20, and the second support member 70 are layered sequentially from the top side to the bottom side.

[0028]

The first compression mechanism 10 is configured of the first cylinder 11, a first piston 13, a first vane 14, and the like. The first cylinder 11 is a plate member in which a substantially cylindrical through hole, substantially concentric with the drive shaft 5 (in more detail, the long shaft portion 5a and the short shaft portion 5b) is formed to penetrate in the up and down direction. The through hole is configured such that one end portion (upper side end portion in Fig. 1) is closed with a flange 60b of the first support member 60, and the other end portion (lower side end portion of Fig. 1) is closed with the intermediate partition plate 4 to thereby form the first cylinder chamber 12.

[0029]

In the first cylinder chamber 12 of the first cylinder 11, the first piston 13 is provided. The first piston 13 is formed in a ring shape, and is slidably provided to the eccentric pin shaft portion 5c of the drive shaft 5. Further, the first cylinder 11 has a vane groove 19 communicating with the first cylinder chamber 12 and extending in the radial direction of the first cylinder chamber 12. The vane groove 19 is provided with the first vane 14 in a slidable manner. In other words, the vane groove 19 accommodates the first vane 14 in a manner allowing it to reciprocate. When the front end portion 14a of the first vane 14 is brought into contact with the outer periphery of the first piston 13, the first cylinder chamber 12 divides into a suction chamber 12a and a compression chamber 12b.

[0030]

Further, the first cylinder 11 has a vane back chamber 15 for accommodating a rear end portion 14b of the first vane 14, behind the vane groove 19, that is, behind the first vane 14. The vane back chamber 15 is provided to penetrate the first cylinder 11 vertically. Further, the upper opening port of the vane back chamber 15 is partially opened to the inner space 7 of the sealed container 3, and the lubricating oil stored in the lubricating oil storage unit 3a can flow into the vane back chamber 15. The lubricating oil flowing into the vane back chamber 15 flows between the vane groove 19 and the first vane 14 to reduce the slide resistance between the two. As described below, the rotary compressor 100 of Embodiment 1 is configured such that the refrigerant compressed by the compression mechanism 99 is discharged to the inner space 7 of the sealed container 3. Accordingly, the vane back chamber 15 becomes the same high-pressure atmosphere as that of the inner space 7 of the sealed container 3.

[0031]

The second compression mechanism 20 is configured of the second cylinder 21, the second piston 23, the second vane 24, and the like. The second cylinder 21 is a plate member in which a substantially cylindrical through hole, substantially concentric with the drive shaft 5 (in more detail, the long shaft portion 5a and the short shaft portion 5b), is formed to penetrate vertically. The through hole is configured such that one end portion (upper end portion in Fig. 1) is closed with the intermediate partition plate 4, and the other end portion (lower end portion in Fig. 1) is closed with a flange 70b of the second support member 70 to thereby form the second cylinder chamber 22.

[0032]

In the second cylinder chamber 22 of the second cylinder 21, the second piston 23 is provided. The second piston 23 is formed in a ring shape, and is provided slidably to the eccentric pin shaft portion 5d of the drive shaft 5. Further, the second cylinder 21 is provided with a vane groove 29 communicating with the second cylinder chamber 22 and extending in the radial direction of the second cylinder chamber 22.

In the vane groove 29, the second vane 24 is provided slidably. In other words, the vane groove 29 accommodates the second vane 24 in such a manner as to allow the second vane 24 to reciprocate. When the front end portion 24a of the second vane 24 is brought into contact with the outer periphery of the second piston 23, the second cylinder chamber 22 divides into a suction chamber and a compression chamber like the first cylinder chamber 12.

[0033]

Further, the second cylinder 21 has a vane back chamber 25 for accommodating a rear end portion 24b of the second vane 24, behind the vane groove 29, that is, behind the second vane 24. The vane back chamber 25 is provided to penetrate the second cylinder 21 vertically. Further, the vane back chamber 25 communicates with the inner space 7 of the sealed container 3 via a partial oil supply passage 55 formed in a pair of oil supply passage forming members 53a and 53b described below (see Fig.

3), whereby the lubricating oil in the lubricating oil storage unit 3a flows into the vane back chamber 25. Accordingly, the vane back chamber 25 becomes the same highpressure atmosphere as that of the inner space 7 of the sealed container 3. Further, the lubricating oil flowing into the vane back chamber 25 flows into the gap between the vane groove 29 and the second vane 24 to reduce the sliding resistance between the two.

[0034]

To the first cylinder 11 and the second cylinder 21, a suction muffler 6 is connected. The suction muffler 6 separates the refrigerant flowing from the evaporator of the refrigerant circuit outside the rotary compressor 100 into liquid refrigerant and gas refrigerant, and allows only the gas refrigerant to flow into the first cylinder chamber 12 and the second cylinder chamber 22.

[0035]

In detail, the suction muffler 6 includes a container 6b, an inflow pipe 6a, an outflow pipe 6c, and an outflow pipe 6d. The inflow pipe 6a guides the low-pressure refrigerant from the evaporator to the container 6b. The outflow pipe 6c guides the gas refrigerant, of the refrigerant stored in the container 6b, to the first cylinder chamber 12 of the first cylinder 11. The outflow pipe 6d guides the gas refrigerant, of the refrigerant stored in the container 6b, to the second cylinder chamber 22 of the second cylinder 21. The outflow pipe 6c of the suction muffler 6 is connected to the cylinder suction passage 17 (passage communicating with the first cylinder chamber 12) of the first cylinder 11. Further, the outflow pipe 6d of the suction muffler 6 is connected to the cylinder suction passage 27 (passage communicating with the second cylinder chamber 22) of the second cylinder 21.

[0036]

Further, the first cylinder 11 has a discharge port 18 for discharging the gas refrigerant compressed in the first cylinder chamber 12. The discharge port 18 communicates with the through hole formed in the flange 60b of the first support member 60. The through hole is provided with an open/close valve 18a that is opened when the inside of the first cylinder chamber 12 becomes a predetermined pressure or higher. Further, the first support member 60 has a discharge muffler 63 that is mounted to cover the open/close valve 18a (that is, through hole). Similarly, the second cylinder 21 has a discharge port 28 for discharging gas refrigerant compressed in the second cylinder chamber 22. The discharge port 28 communicates with a through hole formed in the flange 70b of the second support member 70. The through hole is provided with an open/close valve 28a that is opened when the inside of the second cylinder chamber 22 becomes a predetermined pressure or higher. Further, on the second support member 70, a discharge muffler 73 is mounted to cover the open/close valve 28a (that is, through hole).

[0037]

As described above, the basic configurations of the first compression mechanism 10 and the second compression mechanism 20 are almost the same. However, the detailed configurations of the first compression mechanism 10 and the second compression mechanism 20 differ from each other in the configurations described below.

[0038]

The cylinder chambers 12 and 22 always communicate with the suction pressure space, the vane back chambers 15 and 25 always communicate with the discharge pressure space, and in the vanes 14 and 24, the suction pressure and the discharge pressure act on the front end portions 14a and 24a and the rear end portions 14b and 24b, respectively. By the pressure difference acting on the front ends and the back ends of the vanes 14 and 24, force acts on the respective vanes 14 and 24 in the direction of bringing them into contact with the pistons 13 and 23. The force in the contact direction is defined as first force.

[0039]

In the vane back chamber 15 of the first compression mechanism 10, a compression spring 40 is disposed, and force is applied in a direction that the first vane 14 is brought into contact with the piston 13, so that the first force is applied even when the pressure difference is not caused.

[0040]

The second compression mechanism 20 includes a switching mechanism for performing switching between cylinder resting operation and compressing operation.

In Fig. 1, a portion surrounded by a square corresponds to the switching mechanism. The switching mechanism will be described below specifically.

[0041]

The switching mechanism has a holding member that holds the second vane 24 when the second vane 24 is separated from the outer peripheral wall of the second piston 23. The holding member includes a permanent magnet 51 and the yoke 52, and is disposed in the vane back chamber 25. The permanent magnet 51 and the yoke 52 constitute a magnetic body of the present invention. The magnetic body of the present invention may be configured solely of the permanent magnet 51.

[0042]

On the second vane 24, attractive magnetic force is acted in a direction apart from the second piston 23 by the permanent magnet 51. The attractive magnetic force has a characteristic that it increases as it comes closer to the permanent magnet 51.

In the below description, force acting in a direction of separating the second vane 24 from the second piston 23 is defined as second force.

[0043]

On the second vane 24, the first force and the second force are always acted, and with the magnitude correlation between the first force and the second force, a compression state where the front end portion 24a of the second vane 24 is brought into contact with the second piston 23 and a cylinder resting state where the front end portion 24a of the second vane 24 is separated from the second piston 23 are switched autonomously. This means that the state becomes a compression state when the first force is larger than the second force. On the other hand, when the second force is larger than the first force, the second vane 24 is separated from the second piston 23, whereby the second cylinder chamber 22 becomes a cylinder resting state where the compression chamber 12b is not formed. Once the second vane 24 is separated from the second piston 23, the second force acting on the second vane 24 increases as the second vane 24 approaches the permanent magnet 51.

[0044]

To switch the state to the compression state again, it is necessary that the first force larger than the second force is applied to the second vane 24. However, the second force when the second vane 24 is sucked and held by the yoke 52 is larger than the second force when the second vane 24 is separated from the second piston 23. Accordingly, the first force for allowing the cylinder resting state to be switched to the compression state is larger than the first force when the state is switched from the compression state to the cylinder resting state.

[0045] [Description of operation of rotary compressor 100]

Next, operation at the time of driving the rotary compressor 100 configured as described above will be described.

[0046] [Operation when compressing refrigerant by first compression mechanism 10 and second compression mechanism 20]

First, operation of compressing refrigerant by both the first compression mechanism 10 and the second compression mechanism 20 will be described. Such operation is the same as the operation of a normal rotary compressor 100 in which a compression mechanism does not become a cylinder resting state. The detail of the operation will be described below.

[0047]

When electric power is supplied to the motor 8, the drive shaft 5 is rotated by the motor 8 in counterclockwise seen from directly above (rotation phase θ with reference to the vane position as shown in Fig. 2). When the drive shaft 5 rotates, in the first cylinder chamber 12, the eccentric pin shaft portion 5c eccentrically rotates, and in the second cylinder chamber 22, the eccentric pin shaft portion 5d eccentrically rotates. It should be noted that the eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d eccentrically rotate in such a manner that the phases shift by 180 degrees from each other.

[0048]

Along with the eccentric rotary motion of the eccentric pin shaft portion 5c, in the first cylinder chamber 12, the first piston 13 eccentrically rotates, and the low-pressure gas refrigerant sucked into the first cylinder chamber 12 from the outflow pipe 6c of the suction muffler 6 via the cylinder suction passage 17 is compressed. Similarly, along with the eccentric rotary motion of the eccentric pin shaft portion 5d, in the second cylinder chamber 22, the second piston 23 eccentrically rotates, and the low-pressure gas refrigerant sucked into the second cylinder chamber 22 from the outflow pipe 6d of the suction muffler 6 via the cylinder suction passage 27 is compressed.

[0049]

The gas refrigerant compressed in the first cylinder chamber 12 is discharged from the discharge port 18 to the discharge muffler 63 when it becomes a predetermined pressure, and then is discharged from the discharge port of the discharge muffler 63 to the inner space 7 of the sealed container 3. Further, the gas refrigerant compressed in the second cylinder chamber 22 is discharged from the discharge port 28 into the discharge muffler 73 when it becomes a predetermined pressure, and then discharged from the discharge port of the discharge muffler 73 to the inner space 7 of the sealed container 3. Then, the high-pressure gas refrigerant discharged to the inner space 7 of the sealed container 3 is discharged from the compressor discharge pipe 2 to the outside of the sealed container 3.

When the refrigerant is compressed in the first compression mechanism 10 and the second compression mechanism 20, the refrigerant suction operation and the compression operation described above are repeated in the first compression mechanism 10 and the second compression mechanism 20.

[0050] [Operation when second compression mechanism 20 becomes cylinder resting state]

Hereinafter, operation of the second compression mechanism 20 when it becomes a cylinder resting state will be described. It should be noted that even during the operation, the first vane 14 of the first compression mechanism 10 is pressed by the compression spring 40 and is always in contact with the first piston 13, and performs the refrigerant compression operation as described above. Accordingly, operation of the second compression mechanism 20 when the second compression mechanism 20 becomes a cylinder resting state will be described.

[0051]

In the aforementioned state where the second compression mechanism 20 is compressing the refrigerant, the discharge pressure acts on the rear end portion 24b of the second vane 24 via the lubricating oil. Therefore, due to the pressure difference acting on the front end portion 24a and the rear end portion 24b of the second vane 24, the pressing force (first force) acting on the second vane 24 exceeds the attractive magnetic force (second force) of the permanent magnet 51, whereby the front end portion 24a of the second vane 24 is pressed against the outer peripheral wall of the second piston 23. Accordingly, in the second compression mechanism 20, refrigerant is compressed as the drive shaft 5 rotates.

[0052]

On the other hand, immediately after the start of operation of the rotary compressor 100, or in a state where the rotary compressor 100 is in a low load state, the pressure of the inner space 7 of the sealed container 3 is low. As such, the attractive magnetic force (second force) of the permanent magnet 51 exceeds the pressing force (first force) caused by the pressure difference acting on the front end portion 24a and the rear end portion 24b of the second vane 24. Thereby, in a state where the discharge pressure acts on the entire rear end portion 24b of the second vane 24 and the suction pressure acts on the entire front end portion 24a of the second vane 24, the second vane 24 is separated from the outer peripheral wall of the second piston 23 and the second compression mechanism 20 becomes a cylinder resting state. [0053]

Then, when the front end portion 24a of the second vane 24 is separated from the outer peripheral wall of the second piston 23 and the rear end portion 24b of the second vane 24 approaches the permanent magnet 51, the attractive magnetic force with respect to the second vane 24 increases. Thereby, the second vane 24 further moves to a direction apart from the outer peripheral wall of the second piston 23, and the rear end portion 24b of the second vane 24 is brought into contact with the yoke 52 and is sucked and held.

[0054] [Operation of releasing cylinder resting state of second compression mechanism 20]

Next, operation of releasing the cylinder resting state of the second compression mechanism 20 will be described. In a state where the rear end portion 24b of the second vane 24 is in contact with the yoke 52, a contact portion between the rear end portion 24b of the second vane 24 and the yoke 52 has a communication space 56 (see Fig. 4(b) described below) communicating with the inner space 7 of the sealed container 3. Thereby, the pressure of the inner space 7 acts on the rear end portion 24b of the second vane 24. Then, when the pressure of the inner space 7 of the sealed container 3 (that is, discharge pressure) increases in a state where the second vane 24 is in contact with the yoke 52 and sucked and held, pressing force caused by the pressure difference between the suction pressure acting on the entire front end portion 24a of the second vane 24 and the discharge pressure acting on the communication space 56 (see Fig. 4(b) described below) exceeds the attractive magnetic force applied by the permanent magnet 51. In that state, the second vane 24 is separated from the yoke 52 and the sucked and held state of the second vane 24 is released.

[0055]

Then, the lubricating oil is supplied to the entire rear end portion 24b of the second vane 24, the discharge pressure acts on the entire rear end portion 24b of the second vane 24, and the pressing force (first force) acting on the second vane 24 increases. Thereby, the second vane 24 further moves to the second piston 23 side, and the front end portion 24a of the second vane 24 is pressed against the outer peripheral wall of the second piston 23, and the second compression mechanism 20 starts the refrigerant compression operation.

[0056] [Characteristic configuration of compression mechanism 99]

The present invention includes the valve mechanism 50 that opens the partial oil supply passage 55, described below, for guiding the lubricating oil in the sealed container 3 to the gap between the second vane 24 and the vane groove 29 via the vane back chamber 25 at the time of compressing operation, and blocks it at the time of the non-compressing operation. Hereinafter, the valve mechanism 50 will be described with reference to Figs. 3 to 5.

[0057]

Fig. 3 is an operation explanatory diagram of the valve mechanism 50 of the rotary compressor 100 according to Embodiment 1 of the present invention, in which Fig. 3(a) is a schematic cross-sectional view around the valve mechanism 50 at the time of compressing operation, and Fig. 3(b) is a schematic cross-sectional view around the valve mechanism 50 at the time of cylinder resting operation. Fig. 4 is an operation explanatory diagram of a valve mechanism of the rotary compressor 100 according to Embodiment 1 of the present invention, in which Fig. 4(a) is a schematic top view around the valve mechanism 50 at the time of compressing operation, and Fig. 4(b) is a schematic top view around the valve mechanism 50 at the time of cylinder resting operation. Fig. 5 is a perspective view of the yoke 52 of the rotary compressor 100 according to Embodiment 1 of the present invention.

[0058]

The vane back chamber 25 is provided to penetrate the second cylinder 21 vertically as described above, and a pair of oil supply passage forming members 53a and 53b are fixed to the second cylinder 21 so as to sandwich the vane back chamber 25 from the top and the bottom in the axial direction, in other words, to close the upper and lower opening ports of the vane back chamber 25. In the below description, an oil supply passage forming member on the upper side is referred to as an upper oil supply passage forming member 53a, and an oil supply passage forming member on the lower side is referred to as a lower oil supply passage forming member 53b.

[0059]

The upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b are made of a nonmagnetic material. If the upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b are made of a magnetic material, the magnetic field from the permanent magnet 51 flows to the upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b, so that the second force acting on the second vane 24 decreases. In order to prevent this to happen, the upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b are made of a nonmagnetic material.

[0060]

In the upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b, the partial oil supply passage 55 for supplying lubricating oil in the lubricating oil storage unit 3a to the vane back chamber 25 is provided to penetrate in the axial direction. The partial oil supply passage 55 constitutes a part of the oil supply passage for guiding the lubricating oil in the sealed container 3 to the gap between the second vane 24 and the vane groove 29 via the vane back chamber 25.

In the below description, oil supply passage indicates the entire passage for guiding the lubricating oil in the sealed container 3 to the gap between the second vane 24 and the vane groove 29 via the vane back chamber 25, and partial oil supply passage indicates a passage that allows the inner space 7 of the sealed container and the vane back chamber 25 to communicate with each other to thereby guide the lubricating oil into the vane back chamber 25.

[0061]

As illustrated in Fig. 4(a), an opening port 55a to the vane back chamber 25 of the partial oil supply passage 55 is always closed partially by the yoke 52. Further, a width a of the partial oil supply passage 55 is formed to be smaller than a width b of the second vane 24.

[0062]

Then, at the time of compressing operation, as the second vane 24 is moved to the second piston 23 side, the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55 is opened and the partial oil supply passage 55 and the vane back chamber 25 are in a communicating state. On the other hand, at the time of cylinder resting operation, the second vane 24 moves to the vane back chamber 25 and the rear end portion 24b of the second vane 24 is in contact with the yoke 52. As such, the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55 is closed with both top and bottom end faces 24e of the second vane 24 (see Fig. 3(a)), whereby the communication between the inner space 7 of the sealed container 3 and the vane back chamber 25 is blocked. This means that in the partial oil supply passage 55, a space is separated from the vane groove 29 by the second vane 24 and the yoke 52.

With the aforementioned configuration, the valve mechanism 50 in which the oil supply passage is opened and closed by the reciprocating motion of the second vane 24 is configured.

[0063]

Further, as shown in Fig. 5, the yoke 52 has a notch 52a having a width smaller than the width b of the second vane 24 in a manner penetrating in the axial direction. The notch 52a forms the communication space 56 communicating with the inner space 7 of the sealed container 3, in a contact portion between the rear end portion 24b of the second vane 24 and the yoke 52 in a state where the rear end portion 24b of the second vane 24 is sucked by the yoke 52 at the time of cylinder resting operation. To the communication space 56, the pressure of the inner space 7 of the sealed container 3, that is, discharge pressure ofthe compression mechanism, is applied.

[0064]

Accordingly, even at the time of cylinder resting operation, the state can be in a state where the pressure of the inner space 7 of the sealed container 3 (discharge pressure of the first compression mechanism 10) acts on the rear end portion 24b of the second vane 24, like the time of compressing operation. Thereby, operation of autonomous switching from the cylinder resting operation to the compressing operation can be conducted. This means that when the difference pressure that is the first force (difference pressure between the pressure of the inner space 7 of the sealed container 3 (discharge pressure) and the pressure in the second cylinder chamber 22 (suction pressure)) becomes larger than the second force (attractive magnetic force), switching can be conducted autonomously from the cylinder resting operation to the compressing operation as described above.

[0065]

The aforementioned configuration ensures to prevent the lubricating oil from flowing into the cylinder chamber 22, and to perform switching operation autonomously between the cylinder resting operation and the compressing operation as conventional. [0066] [Flow of lubricating oil in second compression mechanism 20] (Compressing operation)

At the time of compressing operation, the second vane 24 is located at a position not closing the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55. As such, the lubricating oil in the lubricating oil storage unit 3a flows into the gap between the vane groove 29 and second vane 24 via the partial oil supply passage 55 and the vane back chamber 25, to thereby reduce the sliding resistance between the two.

[0067] (Cylinder resting operation)

At the time of cylinder resting operation, the second vane 24 is sucked and held by the yoke 52, the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55 is closed with the both top and bottom end faces 24e of the second vane 24 to thereby block communication between the inner space 7 of the sealed container 3 and the vane back chamber 25. Accordingly, the lubricating oil in the lubricating oil storage unit 3a does not flow into the gap between the vane groove 29 and the second vane 24, whereby it is possible to prevent the lubricating oil from flowing into the second cylinder chamber 22.

[0068] [Effect]

As described above, in the rotary compressor 100 configured as Embodiment 1, switching between the compressing operation and the cylinder resting operation can be conducted autonomously. Further, the valve mechanism 50 is provided to prevent the lubricating oil from flowing into the gap between the vane groove 29 and the second vane 24 during cylinder resting operation. Therefore, it is possible to prevent the lubricating oil in the lubricating oil storage unit 3a from flowing into the second cylinder chamber 22. Accordingly, a loss caused by the lubricating oil in the lubricating oil storage unit 3a flowing into the second cylinder chamber 22 can be reduced, whereby the compressor efficiency can be improved.

[0069]

Further, the partial oil supply passage 55 is configured such that only a through hole is provided in the upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b. Therefore, compared with a configuration in which through holes penetrating a plurality of members are assembled to communicate with each other to form a partial oil supply passage, for example, the configuration is simple and does not cause deterioration in the assembling workability.

[0070]

Further, the yoke 52 has the notch 52a, and the pressure ofthe inner space 7 of the sealed container 3 always acts on the rear end portion 24b of the second vane 24. Accordingly, when the difference pressure that is the first force becomes larger than the second force, switching is conducted from the cylinder resting operation to the compressing operation autonomously.

[0071]

The valve mechanism 50 is to open and close the passage running from the partial oil supply passage 55 to the vane groove 29 by the reciprocating motion ofthe second vane 24. This means that the second vane 24 also functions as a movable valve body. Accordingly, the configuration is simpler than the case where the valve mechanism 50 is configured of a valve body that is different from the second vane 24.

[0072]

Further, the valve mechanism 50 can be configured by forming the partial oil supply passage 55 to extend in the axial direction and opening and closing the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55 with the both top and bottom end faces 24e in the axial direction of the second vane 24.

[0073]

Further, by allowing the width a of the partial oil supply passage 55 and the width b of the second vane 24 to have a relation of b>a, opening and closing of the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55 can be conducted by the second vane 24.

[0074]

Further, as the oil supply passage forming members 53a and 53b are made of a nonmagnetic material, it is possible to solve the inconvenience of the case where the oil supply passage forming members 53a and 53b are made of a magnetic material. This means that it is possible to solve an inconvenience that the magnetic field from the permanent magnet 51 flows to the oil supply passage forming member made of a magnetic material so that the second force acting on the second vane 24 decreases. [0075]

While, in Embodiment 1, the second compression mechanism 20 that is in a cylinder resting state is disposed below the first compression mechanism 10, the second compression mechanism 20 that is in a cylinder resting state may be disposed above the first compression mechanism 10, of course.

[0076] [Modification]

In Embodiment 1, an example in which one notch 52a, penetrating axially, is formed in the yoke 52 has been described. However, the shape of the notch 52a and the position of the notch 52a are not limited to the structure illustrated in Fig. 5, and may be modified as described below. Even in the case where the notch 52a is formed like the modification described below, the same effect as that of the notch 52a described above can be achieved.

[0077] (Shape of notch 52a provided to yoke 52)

Fig. 6 illustrates modifications of the notch 52a provided to the yoke 52 of the rotary compressor 100 according to Embodiment 1 ofthe present invention.

Fig. 6(a) illustrates a configuration having two notches 52a. Fig. 6(b) illustrates a configuration in which one notch 52a is divided into two at the top and bottom of the axial direction. Even with the configurations of Figs. 6(a) and 6(b), the same effect as that of the configuration of Fig. 5 can be achieved. Further, the inner face shape of the notch 52a is not limited to a rectangle. As illustrated in Fig. 6(c), the notch 52a may have a curvature. While Fig. 6(c) illustrates an example in which the notch 52a of Fig. 6(b) has a curvature, this is also applicable to the notches 52a illustrated in Fig. 5 and Fig. 6(a).

[0078]

It should be noted that, in Embodiment 1, the permanent magnet 51 and the yoke 52 constitute a magnetic body, and the notch 52a is formed in the yoke 52. In the case where a magnetic body is solely made of the permanent magnet 51, the permanent magnet 51 may be directly notched. However, as the permanent magnet 51 is brittle, it is preferable to provide it in the yoke 52.

[0079] (Position of notch 52a: second vane 24)

Fig. 7 illustrates a modification of the position of the notch 24c provided in the second vane 24 of the rotary compressor 100 according to Embodiment 1 of the present invention that is a top view around the notch 24c.

In Embodiment 1, the notch 52a penetrating axially is formed in the yoke 52. However, as illustrated in Fig. 7, the notch 24c may be provided to the rear end portion 24b of the second vane 24. Further, notches may be provided to both the yoke 52 and the rear end portion 24b of the second vane 24.

[0080] (Shape of notch 24c provided to second vane 24)

Fig. 8 illustrates modifications of the shape of the notch 24c formed in the second vane 24 of the rotary compressor 100 according to Embodiment 1 of the present invention.

As shapes of the notch 24c in the case of forming the notch 24c in the rear end portion 24b of the second vane 24, the shapes of Fig. 8 can be adopted, for example. That is, Fig. 8(a) illustrates an example in which one notch 24c extending vertically is formed in the rear end portion 24b of the second vane 24. Fig. 8(b) illustrates a case where the inner face shape of the notch 24c of Fig. 8(a) has a curvature. Fig. 8(c) illustrates an example in which two notches 24c are formed in the rear end portion 24b of the second vane 24.

[0081]

Fig. 8(d) illustrates an example in which the notch 24c is divided into two at the top and bottom of the axial direction, in the rear end portion 24b of the second vane 24. Fig. 8(e) illustrates an example in which the notch 24c is formed only on the upper side of the rear end portion 24b of the second vane 24. Fig. 8(f) illustrates an example in which the notch 24c is formed only on the lower side of the rear end portion 24b of the second vane 24. Fig. 8(g) illustrates an example in which the notch 24c not penetrating the top and bottom end faces is formed in the rear end portion 24b of the second vane 24.

[0082]

It should be noted that while Embodiment 1 describes an example in which the upper oil supply passage forming member 53a and the lower oil supply passage forming member 53b, made of a nonmagnetic material, are provided to close the top and bottom opening ports of the vane back chamber 25, and the partial oil supply passage 55 is formed in these members, the following configuration is also acceptable besides this, for example. That is, the intermediate partition plate 4 and the flange 70b of the second support member 70 may be extended in a radial direction (direction orthogonal to the axial direction of the drive shaft 5 of the compression mechanism 99) to close the top and bottom opening ports of the vane back chamber 25, and the partial oil supply passage 55 may be formed in the extended portion. However, the intermediate partition plate 4 and the flange 70b of the second support member 70 are made of a magnetic material, and the attractive magnetic force of the permanent magnet 51 is reduced, as described above. Accordingly, it is preferable to use it when the attractive magnetic force of the permanent magnet 51 is sufficiently strong.

[0083]

Embodiment 2. (Other exemplary configuration of switching mechanism)

In Embodiment 1, description has been given on the switching mechanism for switching between cylinder resting operation and compressing operation by the pressure difference between the suction pressure acting on the front end portion 24a of the second vane 24 and the discharge pressure acting on the rear end portion 24b of the second vane 24, and by the magnitude correlation with the attractive magnetic force. To put it simply, the switching mechanism is configured such that when the inner pressure (discharge pressure) of the sealed container 3 decreases, the attractive magnetic force prevails, so that the compressing operation is switched to the cylinder resting operation autonomously. Embodiment 2 describes a switching mechanism for switching from the compressing operation to the cylinder resting operation forcibly, regardless of a change in the inner pressure (discharge pressure) of the sealed container 3. Even in the case of switching between the cylinder resting operation and the compressing operation by the switching mechanism of Embodiment 2, the compressor efficiency at the time of cylinder resting operation can be improved.

[0084]

Fig. 9 is a schematic vertical cross-sectional view illustrating a structure of a rotary compressor 100 according to Embodiment 2 of the present invention.

Hereinafter, a difference in Embodiment 2 from Embodiment 1 will be mainly described. It should be noted that the part of the configuration not particularly described in Embodiment 2 is the same as that of Embodiment 1.

[0085]

In Embodiment 2, the outflow pipe 6d of the suction muffler 6 is provided with a pressure selector valve 150. Further, the rotary compressor 100 of Embodiment 2 further includes a bypass pipe 160 connecting the pressure selector valve 150 and the compressor discharge pipe 2. The pressure selector valve 150 switches the connection destination of the cylinder suction passage 27 between the outflow pipe 6d and the bypass pipe 160. In Embodiment 2, by the switching conducted by the pressure selector valve 150, the connection destination of the cylinder suction passage 27 is switched whereby the pressure of the second cylinder chamber 22 is switched. Consequently, switching is conducted between the cylinder resting operation and the compressing operation.

[0086] [Operation of rotary compressor 100 and flow of lubricating oil] (Compressing operation)

In the compressing operation, the pressure selector valve 150 is switched to the solid line side of Fig. 9. Thereby, the cylinder suction passage 27 communicates with the outflow pipe 6d. To the second cylinder chamber 22, low-pressure refrigerant flowing from the suction muffler 6 is guided via the outflow pipe 6d and the cylinder suction passage 27, and the suction pressure acts on the front end portion 24a ofthe second vane 24. In a contact portion between the rear end portion 24b of the second vane 24 and the yoke 52, the communication space 56 is formed like Embodiment 1, and on the rear end portion 24b of the second vane 24, the pressure of the inner space 7 of the sealed container 3 is acted. As such, after the pressure selector valve 150 is switched to the solid line side of Fig. 9, when the difference pressure that is the first force (difference pressure between the pressure (discharge pressure) of the inner space 7 of the sealed container 3 and the pressure (suction pressure) in the second cylinder chamber 22)) becomes larger than the second force, switching is conducted autonomously from the cylinder resting operation to the compressing operation, whereby compressing operation is performed.

[0087]

At the time of compressing operation, the partial oil supply passage 55 communicates with the vane groove 29, and the lubricating oil flows between the vane groove 29 and the second vane 24, whereby oil supply is secured.

[0088] (Cylinder resting operation)

In the cylinder resting operation, the pressure selector valve 150 is switched to the dotted line of Fig. 9. Thereby, the cylinder suction passage 27 communicates with the bypass pipe 160, and high-pressure refrigerant discharged from the compressor discharge pipe 2 is guided to the second cylinder chamber 22 via the bypass pipe 160 and the cylinder suction passage 27. Accordingly, high pressure acts on both the front end portion 24a and the rear end portion 24b of the second vane 24, whereby no difference pressure is caused. Therefore, the second vane 24 is sucked and held by the permanent magnet 51, and the cylinder resting operation is performed.

[0089]

At the time of cylinder resting operation, as the oil supply passage is closed by the valve mechanism 50 as described above, lubricating oil does not flow into the gap between the vane groove 29 and the second vane 24. Thereby, at the time of cylinder resting operation, it is possible to prevent the lubricating oil from flowing into the second cylinder chamber 22.

[0090]

As described above, in the rotary compressor 100 configured as in Embodiment 2, the same effect as that of Embodiment 1 can be obtained. This means that switching can be conducted between the compressing operation and the cylinder resting operation, and it is possible to reduce a loss caused by inflow of the lubricating oil in the lubricating oil storage unit 3a to the second cylinder chamber 22 during the cylinder resting operation. Thereby, compressor efficiency can be improved.

[0091]

Embodiment 3. (Partial oil supply passage is arranged in radial direction)

In Embodiment 1, the partial oil supply passage 55 extends axially. In Embodiment 3, the partial oil supply passage 55 extends in a direction orthogonal to the axial direction (radial direction). Even in this case, the same effect as that of Embodiment 1 can be achieved.

[0092]

Fig. 10 is a schematic cross-sectional view around the valve mechanism 50Aof a rotary compressor 100 according to Embodiment 3 of the present invention, in which

Fig. 10(a) is a schematic cross-sectional view around the valve mechanism 50Aat the time of compressing operation, and Fig. 10(b) is a schematic cross-sectional view around the valve mechanism 50 at the time of cylinder resting operation. Fig. 11 is a perspective view of the yoke 52 of the rotary compressor 100 according to Embodiment 3 of the present invention. Hereinafter, a difference in Embodiment 3 from Embodiment 1 will be mainly described. The part of the configuration not particularly described in Embodiment 3 is the same as that of Embodiment 1.

[0093]

The rotary compressor 100 of Embodiment 3 includes a partial oil supply passage 55A extending radially, instead of the partial oil supply passage 55 extending axially.

The partial oil supply passage 55A is configured of the permanent magnet 51, the yoke 52, and a through hole radially penetrating the second cylinder 21 portion located outside them.

[0094]

A valve mechanism 50Aof Embodiment 3 opens and closes an opening port 55a to the vane back chamber 25 of the partial oil supply passage 55A in a back end surface 24d (surface opposite to the yoke 52) of the second vane 24.

[0095] [Flow of lubricating oil in second compression mechanism 20] (Compressing operation)

At the time of compressing operation, the second vane 24 locates at a position not closing the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55A, as illustrated in Fig. 10(a). As such, the lubricating oil in the lubricating oil storage unit 3a flows to the gap between the vane groove 29 and the second vane 24 via the partial oil supply passage 55A and the vane back chamber 25, as indicated by the arrow of Fig. 10(a), to reduce the sliding resistance between the two.

[0096] (Cylinder resting operation)

At the time of cylinder resting operation, as illustrated in Fig. 10(b), the second vane 24 is sucked and held by the yoke 52, and the opening port 55a to the vane back chamber 25 of the partial oil supply passage 55A is closed with the back end surface 24d (surface opposite to the yoke 52 of the second vane 24) of the second vane 24, whereby the communication between the inner space 7 of the sealed container 3 and the vane back chamber 25 is blocked. Accordingly, the lubricating oil in the lubricating oil storage unit 3a does not flow to the gap between the vane groove 29 and the second vane 24, whereby it is possible to prevent the lubricating oil from flowing into the second cylinder chamber 22.

[0097]

As described above, even in the rotary compressor 100 configured as Embodiment 3, the same effect at that of Embodiment 1 can be achieved. This means that switching between the compressing operation and the cylinder resting operation can be conducted autonomously, and a loss caused by inflow of the lubricating oil in the lubricating oil storage unit 3a to the second cylinder chamber 22 during the cylinder resting operation can be reduced. Thereby, the compressor efficiency can be improved.

[0098]

The partial oil supply passage allowing the inner space 7 of the sealed container 3 and the vane back chamber 25 to communicate with each other may be formed to extend axially as in Embodiment 1 and Embodiment 2, or may be formed to extend radially as in Embodiment 3. A specific configuration of the partial oil supply passage 55A extending radially can be realized by forming the partial oil supply passage 55A in a part of the magnetic body (permanent magnet 51 and yoke 52) and the second cylinder 21, as illustrated in Fig. 10. This means that it is realized by a configuration in which the magnetic body (the permanent magnet 51 and the yoke 52) and the second cylinder 21 serve as an oil supply passage forming member.

[0099] [Modification]

While one partial oil supply passage 55A is provided in Embodiment 3, the number of the partial oil supply passage 55A is not limited to this. A plurality of partial oil supply passages 55A may be provided as described in a modification described below.

[0100]

Fig. 12 is a schematic cross-sectional view around the valve mechanism 50Aof the rotary compressor 100 according to Embodiment 3 of the present invention.

Fig. 12 illustrates a configuration having a plurality of partial oil supply passages 55 extending radially. With a plurality of partial oil supply passages 55A, the pressure rising speed of the vane back chamber 25 becomes higher compared with the case of less partial oil supply passages 55A, whereby the responsiveness at the time of switching from the cylinder resting operation to the compressing operation is improved.

It should be noted that even when a plurality of partial oil supply passages 55 are provided, the notch 52a may be located in the yoke 52, or in the rear end portion 24b of the second vane 24. Regardless of the location of the notch, an effect by providing a plurality of partial oil supply passages 55 can be achieved.

[0101]

Embodiment 4. (Positions of closing oil supply passage are right and left side faces of vane)

In Embodiments 1 to 3, the oil supply passage is closed with both top and bottom end faces (both end faces in the axial direction) 24e ofthe second vane 24 (see Fig. 3). Meanwhile, in Embodiment 4, the oil supply passage is closed with right and left side faces (both end faces in the radial direction) 24d of the second vane 24, which is different from the cases of Embodiments 1 to 3. Further, in Embodiments 1 to 3, as the width a of the partial oil supply passage 55 is smaller than the width b of the second vane 24, it is possible to prevent the lubricating oil from flowing from the partial oil supply passage 55 to the second cylinder chamber 22 through the vane groove 29 at the time of cylinder resting operation. On the other hand, there is a restriction on the width a of the partial oil supply passage 55. In Embodiment 4, the restriction on the width a of the partial oil supply passage 55 can be removed to increase the width a of the partial oil supply passage 55, the amount of oil supply at the time of compressing operation can be secured, and the reliability can be improved.

[0102]

Fig. 13 is a top view around the valve mechanism 50B at the time of cylinder resting operation of the rotary compressor 100 according to Embodiment 4 of the present invention. Fig. 14 is a top view around the valve mechanism 50B in which the upper oil supply passage forming member 53a is removed in the second compression mechanism 20 of the rotary compressor 100 according to Embodiment 4 of the present invention, in which Fig. 14(a) illustrates a state at the time of compressing operation, and Fig. 14(b) illustrates a state at the time of cylinder resting operation. Hereinafter, a difference in Embodiment 4 from Embodiment 1 will be mainly described. The part of the configuration not particularly described in Embodiment 4 is the same as that of Embodiment 1.

[0103]

The rotary compressor 100 of Embodiment 4 includes a partial oil supply passage 55B in place of the partial oil supply passage 55 of Embodiment 1. As illustrated in Fig. 13, the partial oil supply passage 55B is configured such that the width a is formed to be longer than the vane width b, and the partial oil supply passage 55B and the vane back chamber 25 communicate with each other not only at the time of compressing operation but also at the time of cylinder resting operation. Further, in Embodiment 4, the vane back chamber 25 is also provided with an intermediate holding member 54, which is different from the cases of Embodiments 1 to 3.

[0104]

The intermediate holding member 54 has a through hole having an outer shape substantially following the inner shape of the vane back chamber 25 and penetrating in the radial direction. The through hole is configured of a first hole 54a, a second hole 54b, and a third hole 54c having three different cross-sectional areas in the radial direction, sequentially from the inside of the radial direction. The first hole 54a forms a vane back end sliding chamber 54a in which the rear end portion 24b of the second vane 24 slides at the time of compressing operation. The vane back end sliding chamber 54a is formed to have a size capable of supplying the oil sufficiently.

[0105]

The second hole 54b is a part serving as a valve hole for partially closing the communicating portion between the vane back chamber 25 and the vane groove 29 and opening and closing the oil supply passage from the lubricating oil storage unit 3a to the gap between the second vane 24 and the vane groove 29. The second hole 54b has an inner shape slightly larger than the outer shape of the second vane 24.

[0106]

At the time of compressing operation, the rear end portion 24b of the second vane 24 separates from the second hole 54b to open the oil supply passage as illustrated in Fig. 14(a), while at the time of cylinder resting operation, the rear end portion 24b of the second vane 24 is inserted into the second hole 54b to block the oil supply passage, as illustrated in Fig. 14(b). As described above, in Embodiment 2, the valve mechanism 50B in which the second vane 24 is inserted into and separated from the second hole 54b serving as the valve hole to thereby open and close the oil supply passage is configured. It is preferable that the gap between the second vane 24 and the second hole 54b is similar to or smaller than the gap between the second vane 24 and the vane groove 29 from the viewpoint of preventing inflow of the lubricating oil to the second cylinder chamber 22 at the time of cylinder resting operation by increasing the passage resistance.

[0107]

The third hole 54c forms a vane back chamber 25A that is newly formed by inserting the intermediate holding member 54 into the vane back chamber 25. In the vane back chamber 25A, the permanent magnet 51 and the yoke 52 are disposed. As illustrated in Fig. 13, the vane back chamber 25A communicates with the partial oil supply passage 55.

[0108] [Flow of lubricating oil in second compression mechanism 20] (Compressing operation)

At the time of compressing operation, the rear end portion 24b of the second vane 24 performs reciprocating motion inside of the vane back end sliding chamber

54a. In this state, the vane back chamber 25A and the vane back end sliding chamber

54a communicate with each other via the second hole 54b. As indicated by an arrow in Fig. 14(a), oil is sufficiently supplied from the vane back chamber 25 into the vane back end sliding chamber 54a via the second hole 54b.

[0109] (Cylinder resting operation)

At the time of cylinder resting operation, the rear end portion 24b of the second vane 24 is inserted into the second hole 54b as illustrated in Fig. 14(b), the vane back chamber 25 and the vane back end sliding chamber 54a are blocked, and the oil supply passage is blocked. Accordingly, it is possible to suppress inflow of the lubricating oil from the lubricating oil storage unit 3a into the second cylinder chamber 22 via the partial oil supply passage 55B, the vane back chamber 25A, the second hole 54b, and the vane back end sliding chamber 54a.

[0110] [Shape of rear end portion 24b of second vane 24]

Fig. 15 is a perspective view, seen from the rear end portion 24b side, of the second vane 24 of the rotary compressor 100 according to Embodiment 4 of the present invention.

The rear end portion 24b of the second vane 24 is applied with chamfering or bending processing. With such processing, the gap running from the second hole 54b to the first hole 54a is widened, compared with the case of not being processed. Accordingly, the lubricating oil easily flows from the vane back chamber 25 to the gap between the second vane 24 and the vane groove 29 during compressing operation. [0111]

Further, as the rear end portion 24b of the second vane 24 is applied with chamfering or bending processing, even in the state where the rear end portion 24b of the second vane 24 is in contact with the yoke 52 at the time of cylinder resting operation, the pressure of the inner space 7 of the sealed container 3 acts on the rear end portion 24b of the second vane 24. This means that the chamfered portion or the bent portion serves as the notch 24c of Embodiments 1 to 3. It should be noted that it is acceptable to provide the notch 24c illustrated in Fig. 8, for example, while performing chamfering or bending processing on the rear end portion 24b of the second vane 24.

[0112]

As described above, even in the rotary compressor 100 configured as in Embodiment 4, the same effect as that of Embodiment 1 can be achieved. This means that switching between the compressing operation and the cylinder resting operation can be conducted autonomously, and a loss caused by leakage of the lubricating oil in the lubricating oil storage unit 3a to the cylinder chamber during the cylinder resting operation can be reduced. Thereby, the compressor efficiency can be improved.

[0113]

Further, Embodiment 4 has the valve mechanism 50B in which the second vane 24 is inserted into and separated from a valve hole formed by partially closing the communicating portion between the vane back chamber 25 and the vane groove 29 to thereby open and close the oil supply passage. As such, there is no restriction on the width a of the partial oil supply passage 55, and the width can be set freely. Accordingly, in Embodiment 4, the width a of the partial oil supply passage 55 can be increased by releasing the restriction on the width a of the partial oil supply passage 55, the amount of oil supply at the time of compressing operation can be secured, and the reliability can be improved.

[0114] [Modification] (Intermediate holding member 54)

In Embodiment 4, description has been given on the configuration in which the first hole 54a and the second hole 54b of the intermediate holding member 54 have large and small two-stage cross-sectional areas in the radial direction. However, the present embodiment is not limited to this configuration. A configuration as described below is also acceptable.

[0115]

Fig. 16 illustrates a modification of the intermediate holding member 54 of the rotary compressor 100 according to Embodiment 4 of the present invention, in which

Fig. 16(a) illustrates a state at the time of compressing operation, and Fig. 16(b) illustrates a state at the time of cylinder resting operation.

In this example, the cross-sectional area in the radial direction of the first hole 54a of a hollow holding member is decreasing in a stepless manner toward the outside in the radial direction. Even with this configuration, oil is sufficiently supplied from the vane back chamber 25A into the vane back end sliding chamber 54a via the second hole 54b as shown by an arrow of Fig. 16(a).

[0116] (Form of rear end portion 24b of second vane 24)

In Embodiment 4, the rear end portion 24b ofthe second vane 24 is applied with chamfering or bending processing. Besides it, the following form may also be acceptable. The same effect can be achieved with the following form.

[0117]

Fig. 17 illustrates a modification of the second vane 24 of the rotary compressor 100 according to Embodiment 4 of the present invention.

Fig. 17(a) illustrates an example in which two corners formed of both top and bottom end faces 24e and the back end face 24d of the second vane 24 are chamfered, respectively. Fig. 17(b) illustrates an example in which the rear end portion 24b of the second vane 24 is formed to be in a convex shape. Fig. 17(c) illustrates an example in which the rear end portion 24b of the second vane 24 is formed to be in a concave shape.

[0118]

It should be noted that while the Embodiments 1 to 4 have been described as different modes, the rotary compressor 100 may be configured by appropriately combining the characteristic configurations and modifications of the respective embodiments. For example, the modification regarding the notch described in Embodiment 1 and the modification regarding the number of partial oil supply passages 55 described in Embodiment 3 may be combined. This means that in the configuration of the modification (having a plurality of oil supply passages) of Embodiment 3 illustrated in Fig. 12, the notch 24c may be formed in the rear end portion 24b of the second vane 24.

[0119]

Embodiment 5. (Refrigeration cycle apparatus)

The rotary compressor 100 described in Embodiments 1 to 4 may be used as a vapor compression type refrigeration cycle apparatus as described below, for example. [0120]

Fig. 18 is a configuration diagram illustrating a vapor compression type refrigeration cycle apparatus 500 according to Embodiment 5 of the present invention.

The vapor compression type refrigeration cycle apparatus 500 according to Embodiment 5 includes the rotary compressor 100 described in any of Embodiments 1 to 4, a radiator 300 that allows refrigerant to be compressed by the rotary compressor 100 to reject heat, an expansion mechanism 200 that expands the refrigerant flowing out of the radiator 300, and an evaporator 400 that allows the refrigerant flowing out of the expansion mechanism 200 to absorb heat.

[0121]

With the rotary compressor 100 as described in any of Embodiments 1 to 4 as in the vapor compression type refrigeration cycle apparatus 500 according to Embodiment 5, it is possible to improve the energy saving performance in the actual load operation. Reference Signs List [0122]

3a lubricating oil 5a long shaft portion compressor discharge pipe 3 sealed container storage unit 4 intermediate partition plate 5 drive shaft

5b short shaft portion 5c eccentric pin shaft portion 5d eccentric pin shaft portion 5e intermediate shaft portion 6 suction muffler 6a inflow pipe 6b container 6c outflow pipe 6d outflow pipe 7 inner space motor 8a rotor 8b stator 10 first compression mechanism first cylinder 12 first cylinder chamber 12a suction chamber 12b compression chamber 13 first piston 14 first vane 14a front end portion 14b rear end portion 15 vane back chamber 17 cylinder suction passage 18 discharge portl 8a open/close valve 19 vane groove 20 second compression mechanism 21 second cylinder 22 second cylinder chamber 23 second piston 24 second vane

24a front end portion 24b rear end portion 24c notch 24d back end surface

24e both top and bottom end faces 25 vane back chamber 25A vane back chamber 27 cylinder suction passage 28 discharge port28a open/close valve 29 vane groove 40 compression spring 50 valve mechanism 50A valve mechanism 50B valve mechanism 51 permanent magnet 52 yoke 52a notch 53a upper oil supply passage forming member 53b lower passage forming member 54 intermediate holding member 54a first hole (vane back end sliding chamber) 54b second hole 54c third hole

55A partial oil supply passage opening port56 communication space partial oil supply passage 55B partial oil supply passage 55a 60 first support member60a bearing

10	60b	flange	63	discharge muffler	70	second support member	70a
	bearing	70b	flange 73	discharge muffler	99	compression mechanism	100
	rotary compressor	150 pressure selector valve	160	bypass pipe 200 expansion
	mechanism	300	radiator	400 evaporator	500	vapor compression type

refrigeration cycle apparatus.

Claims

CLAIMS [Claim 1]

A rotary compressor comprising: a sealed container that stores lubricating oil; and a plurality of compression mechanisms accommodated in the sealed container, each of the compression mechanisms being configured to compress refrigerant and discharge the refrigerant to an inner space of the sealed container, wherein each of the compression mechanisms includes a cylinder having a cylinder chamber, a piston that eccentrically rotates in the cylinder chamber, a vane configured such that a front end of the vane is brought into contact with the piston to divide the cylinder chamber into a plurality of spaces, a vane groove formed in the cylinder, the vane groove accommodating the vane to allow the vane to reciprocate, and a vane back chamber formed in the cylinder in communication with the vane groove on a side opposite to the vane groove with respect to the cylinder chamber, the vane back chamber accommodating a rear end portion of the vane, wherein any of the compression mechanisms has a switching mechanism to conduct switching between a compressing operation and a non-compressing operation, the compressing operation being an operation of compressing the refrigerant in a state where the front end of the vane is in contact with the piston when the piston rotates, the non-compressing operation being an operation in which the front end of the vane is separated from the piston and the refrigerant is not compressed, and the rotary compressor has a valve mechanism that opens an oil supply passage for guiding the lubricating oil in the sealed container to a gap between the vane and the vane groove via the vane back chamber at time of the compression operation, and blocks the oil supply passage at time of the non-compression operation.
[Claim 2]

The rotary compressor of claim 1, wherein at the time of the non-compressing operation, the rear end portion of the vane is attracted toward the vane back chamber by magnetic force of a magnetic body provided to the vane back chamber whereby the rear end portion of the vane and the magnetic body are brought into contact with each other, and one or both of contact portions between the rear end portion of the vane and the magnetic body have a notch constantly communicating with the inner space of the sealed container.
[Claim 3]

The rotary compressor of claim 1 or 2, further comprising an oil supply passage forming member that allows the vane back chamber and the inner space of the sealed container to communicate with each other, and forms a partial oil supply passage constituting a part of the oil supply passage, wherein the valve mechanism opens and closes a passage from the partial oil supply passage to the vane groove by reciprocating motion of the vane.
[Claim 4]

The rotary compressor of claim 3, wherein the vane back chamber is formed to penetrate the cylinder in an axial direction of a drive shaft of the compression mechanism, a pair of the oil supply passage forming members is provided to sandwich the vane back chamber from both sides in the axial direction, and the partial oil supply passage is formed to extend in the axial direction, and the valve mechanism opens and closes an opening port of the partial oil supply passage, which is open to the vane back chamber with both end faces in the axial direction of the vane.
[Claim 5]

The rotary compressor of claim 4, wherein a relation of b>a is satisfied where “a” represents a width a of the partial oil supply passage and “b” represents a width b of the vane.
[Claim 6]

The rotary compressor of claim 3, wherein the width a of the partial oil supply passage is formed to be longer than the width b of the vane, and the partial oil supply passage and the vane back chamber constantly communicate with each other, and the valve mechanism opens or closes the oil supply passage when the vane is inserted into and separated from a valve hole formed to partially close a communicating portion between the vane back chamber and the vane groove.
[Claim 7]

The rotary compressor of any one of claims 3 to 6, wherein the oil supply passage forming member is made of a nonmagnetic material.
[Claim 8]

The rotary compressor of claim 3 as dependent on claim 2, wherein the magnetic body and a part of the cylinder serve as the oil supply passage forming member, the partial oil supply passage being formed in the oil supply passage forming member while extending in a direction orthogonal to an axial direction of a drive shaft of the compression mechanism, and the valve mechanism opens and closes an opening port of the partial oil supply passage, which is open to the vane back chamber with a face opposite to the magnetic body of the vane.
[Claim 9]

The rotary compressor of claim 8, wherein a plurality of the partial oil supply passages are provided.
[Claim 10]

The rotary compressor of any one of claims 1 to 9, wherein the switching mechanism has a pressure selector valve that introduces suction pressure or discharge pressure to the cylinder chamber of the compression mechanism. [Claim 11]

A vapor compression type refrigeration cycle apparatus comprising: the rotary compressor of any one of claims 1 to 10;

a radiator that allows the refrigerant compressed by the rotary compressor to reject heat;

an expansion mechanism that expands the refrigerant flowing out of the radiator; and an evaporator that evaporates the refrigerant flowing out of the expansion mechanism.