CN109154296B

CN109154296B - Hermetic rotary compressor and refrigerating and air-conditioning apparatus

Info

Publication number: CN109154296B
Application number: CN201780032185.6A
Authority: CN
Inventors: 香曾我部弘胜; 坪野勇; 岸康弘; 土屋直洋; 竹泽谦治
Original assignee: Hitachi Johnson Controls Air Conditioning Inc
Current assignee: Hitachi Johnson Controls Air Conditioning Inc
Priority date: 2016-07-19
Filing date: 2017-07-10
Publication date: 2020-09-01
Anticipated expiration: 2037-07-10
Also published as: JP2018013042A; CN109154296A; JP6363134B2; WO2018016364A1

Abstract

A hermetic rotary compressor of the present invention includes a hermetic container, a motor, two rotary compression elements driven by the motor, and a partition plate partitioning the two rotary compression elements, each rotary compression element having a cylinder, a drum eccentrically and rotatably accommodated in the cylinder chamber, a vane partitioning the cylinder chamber into a suction chamber and a compression chamber, and a blow-off valve device discharging a working fluid compressed in the cylinder chamber into the hermetic container, wherein the rotary compression element on the lower side has a cylinder deactivation mechanism for deactivating a compression operation, and a cylinder oil flow passage for sucking up a lubricating oil intruding into the cylinder chamber, and a partition plate oil flow passage for communicating the suction chamber of the rotary compression element on the lower side with the suction chamber of the rotary compression element on the upper side is disposed in the partition plate.

Description

Hermetic rotary compressor and refrigerating and air-conditioning apparatus

Technical Field

The present invention relates to a hermetic rotary compressor used in, for example, an air conditioner, a refrigerator, or the like, and a refrigerating and air-conditioning apparatus equipped with the hermetic rotary compressor to constitute a refrigeration cycle.

Background

In recent years, as the range of application capacity expands, the hermetic rotary compressor is standardized as a double cylinder type rotary compressor having two sets of cylinder bores as rotary compression elements. Among such compressors, there is known a rotary compressor capable of performing an operation in which two cylinder chambers perform a compression action and a mechanical displacement variable operation (cylinder deactivation operation) in which a cylinder capable of switching between compression and stop according to a load is provided. In recent years, from the viewpoint of preventing global warming, attention has been paid to an R32 refrigerant having a small global warming potential as a refrigerant of a refrigeration and air-conditioning system, instead of the conventional R410A refrigerant.

In the conventional rotary compressor of patent document 1, there is disclosed a hermetic rotary compressor in which an increase in man-hours caused to limit return of lubricating oil from a cylinder deactivation operation cylinder to an accumulator (suction tank) at the time of cylinder deactivation operation is avoided, thereby achieving cost reduction.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2014-40812

Disclosure of Invention

Problems to be solved by the invention

The compression mechanism of the hermetic rotary compressor of patent document 1 is described as follows: the rotary compression mechanism includes a cylinder having a cylinder chamber communicating with a suction passage, a drum accommodated in the cylinder chamber in an eccentrically movable manner, a movable vane (vane) having a tip end abutting against a circumferential wall of the drum and dividing the cylinder chamber into a suction chamber and a compression chamber, and a purge valve device for discharging gas compressed in the cylinder chamber into a sealed casing, and further includes a cylinder deactivation mechanism for guiding suction pressure to the cylinder chamber via the suction passage and causing a tip end edge of the movable vane to be separated from the circumferential wall of the drum to stop a compression operation, and a communication passage 36 for communicating suction chambers formed in the cylinder chambers of the compression mechanism and the other compression mechanisms is provided in an intermediate partition plate 6.

In patent document 1, for example, in paragraphs 0032, 0048, and 0049, there is disclosed a two-cylinder rotary compressor in which an upper cylinder chamber having a cylinder deactivation mechanism and a lower cylinder chamber having no cylinder deactivation mechanism are communicated with each other via a communication passage, and lubricating oil that has intruded into the upper cylinder chamber is guided from the communication passage to the lower cylinder chamber and is not guided to an accumulator, so that return of lubricating oil during cylinder deactivation operation from the first cylinder chamber to the accumulator is restricted, and a large amount of lubricating oil is prevented from accumulating in the accumulator, and further, shortage of lubricating oil in a sealed casing can be prevented.

In this rotary compressor, the first cylinder chamber having the cylinder deactivation mechanism is disposed close to the main bearing, and the second cylinder chamber is disposed on the lower side via an intermediate partition plate, and during the mechanical displacement variable operation (cylinder deactivation operation), since the compression operation is performed in the second cylinder chamber separated from the main bearing, there is a problem as follows: the sub bearing close to the second cylinder chamber has a larger bearing load than the main bearing, and thus tends to cause an increase in mechanical loss and a decrease in reliability of the bearing.

Further, in the case where the cylinder chamber having the cylinder deactivation mechanism is disposed below the intermediate partition plate, the lubricating oil that has intruded into the first cylinder chamber is not sufficiently guided to the operating cylinder chamber located above through the communication hole provided in the intermediate partition plate because the lubricating oil is retained below the cylinder chamber, and there is a problem that the lubricating oil remains in the cylinder deactivation chamber and the stirring loss of the oil is increased by the eccentrically rotating drum, and there is a problem that the compressor performance is lowered in the mechanical displacement variable operation (cylinder deactivation operation).

The purpose of the present invention is to obtain a hermetic rotary compressor that has a cylinder tube capable of switching compression and stop according to load and that can improve the performance and reliability during mechanical variable displacement operation (cylinder deactivation operation), and to obtain a refrigerating and air-conditioning apparatus using the hermetic rotary compressor.

Means for solving the problems

In order to achieve the above object, a hermetic rotary compressor according to the present invention includes: a closed container provided with a discharge pipe and two suction pipes; a motor provided in the closed container and rotating a rotating shaft; two rotary compression elements provided below the motor and driven by rotation of the rotary shaft; and a partition plate that partitions the two rotary compression elements, each rotary compression element having: a cylinder having a cylinder chamber communicating with the suction pipe via a suction passage; a drum which is eccentrically and rotatably accommodated in the cylinder chamber; a vane for dividing the cylinder chamber into a suction chamber and a compression chamber; and a relief valve device for discharging the working fluid compressed in the cylinder chamber into the closed casing, wherein the lower rotary compression element has a cylinder deactivation mechanism for deactivating a compression operation and a cylinder oil flow passage for sucking the lubricating oil that has entered the cylinder chamber, and the partition plate has a partition plate oil flow passage for communicating a suction chamber of the lower rotary compression element with a suction chamber of the upper rotary compression element.

The effects of the invention are as follows.

According to the present invention, there are effects that a hermetic rotary compressor capable of improving performance and reliability in mechanical displacement variable operation (cylinder deactivation operation) and a refrigerating and air-conditioning apparatus using the hermetic rotary compressor and having excellent energy efficiency throughout the year can be obtained.

Drawings

Fig. 1 is a longitudinal sectional view of the hermetic rotary compressor of embodiment 1.

Fig. 2 is a cross-sectional view a-a of fig. 1.

FIG. 3 is a cross-sectional view B1-B2 of FIG. 2.

Fig. 4 is an enlarged sectional view of a main portion of fig. 3 showing an operating state of the double cylinder.

Fig. 5 is an enlarged cross-sectional view of a main portion of fig. 3 showing a single-cylinder deactivation operating state.

Fig. 6 is a cross-sectional view C-B2 of fig. 2 showing an oil flow passage configuration that is a feature of embodiment 1.

Fig. 7 is a cross-sectional view taken along line D-D of fig. 6.

Fig. 8 is a perspective view of the inner wall surface of the cylinder tube in the vicinity of the vane as viewed from the center of the cylinder tube.

Fig. 9 is a cross-sectional view a-a of fig. 1 in embodiment 2.

Fig. 10 is an enlarged sectional view of a main portion of fig. 9.

Fig. 11 is a perspective view of the inner wall surface of the cylinder tube in the vicinity of the vane as viewed from the center of the cylinder tube in fig. 9.

Fig. 12 is a schematic diagram of a refrigeration cycle of a refrigerating and air-conditioning apparatus including a hermetic rotary compressor according to the present invention.

Detailed Description

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The same reference numerals in the drawings of the respective embodiments show the same components or equivalent components.

Example 1

The hermetic rotary compressor of embodiment 1 will be described with reference to fig. 1 to 8. Fig. 1 is a longitudinal sectional view of a double cylinder type hermetic rotary compressor, fig. 2 is a cross sectional view a-a of fig. 1, fig. 3 is a cross sectional view B1-B2 of fig. 2, fig. 4 is an enlarged sectional view of a main portion of fig. 3 showing an operating state of double cylinders, fig. 5 is an enlarged sectional view of a main portion of fig. 3 showing an operating state of single cylinder deactivation, fig. 6 is an enlarged sectional view of a main portion C-B2 of fig. 2 showing an oil flow passage configuration of embodiment 1, fig. 7 is a cross sectional view D-D of fig. 6, and fig. 8 is a perspective view of an inner wall surface of the cylinder in the vicinity of a vane as viewed from the center of.

In fig. 1 to 3, reference numeral 1 denotes a closed container provided with one discharge pipe and two suction pipes, two rotary compression element parts 2 are housed in a lower part of the closed container 1, a motor part 3 for driving the two rotary compression element parts 2 is housed in an upper part, and the motor part 3 and the rotary compression element parts 2 are connected via a rotation shaft 4 disposed vertically. The motor unit 3 includes a stator 3a fixed to the inner surface of the sealed container 1 and a rotor 3b arranged inside the stator 3a with a predetermined gap therebetween and fixed to the rotating shaft 4. The motor unit 3 is electrically connected to an inverter (not shown) for controlling the operating frequency.

The rotary compression element 2 includes a first rotary compression element 2A and a second rotary compression element 2B disposed above and below the partition plate 5. The upper first rotary compression element part 2A includes a first cylinder 6A, and the lower second rotary compression element part 2B includes a second cylinder 6B. The first cylinder 6A is overlapped with the lower surface of a main bearing 7 fixed to the inner surface of the hermetic container 1, and a sub bearing 8 is attached to the lower surface of the second cylinder 6B. The rotary shaft 4 is rotatably supported by a main bearing 7 and a sub bearing 8, and integrally includes two eccentric portions 4a and 4B at positions inside the first cylinder 6A and the second cylinder 6B with a phase difference of about 180 °.

Rollers

9a and 9b are rotatably fitted around the outer peripheries of the

eccentric portions

4a and 4 b. The first cylinder 6A and the second cylinder 6B are divided into upper and lower surfaces by the partition plate 5, the main bearing 7, and the sub bearing 8, and a first cylinder chamber 10a is formed in the first cylinder 6A and a second cylinder chamber 10B is formed in the second cylinder 6B.

A discharge cover 7a forming a discharge space for the compressed working fluid is attached to the main bearing 7, and the discharge cover 7a covers a relief valve device 7b attached to an end plate of the main bearing 7. A discharge cover 8a is also attached to the sub-bearing 8, and the discharge cover 8a covers a relief valve device 8b attached to an end plate of the sub-bearing 8. The relief valve device 7b of the main bearing 7 communicates with the first cylinder chamber 10a, opens when the pressure in the cylinder chamber 10a rises to a predetermined pressure due to a compression action, and discharges the compressed working fluid into the discharge cover 7 a. The relief valve device 8a of the sub-bearing 8 communicates with the second cylinder chamber 10b, opens when the pressure in the cylinder chamber 10b rises to a predetermined pressure due to the compression action, and discharges the compressed working fluid into the discharge cover 8 a.

Vanes 11a and 11B disposed in respective cylinder chambers 10a and 10B so as to be capable of reciprocating are housed in the first cylinder 6A and the second cylinder 6B, vane springs 12a and 12B are housed in rear end portions of the respective vanes, and the vane springs 12a and 12B abut the respective vane tip portions with elastic force and act on outer peripheries of the rollers 9a and 9B. The lower end of the rotating shaft 4 is exposed below the sub-bearing 8 and is immersed in the lubricating oil 19 stored in the bottom of the closed casing 1. An oil feed pump is attached to the lower end surface of the rotary shaft 4, and lubricating oil is supplied from this oil feed pump to the sliding portions of the members constituting the second rotary compression element part 2B and the first rotary compression element part 2A via oil feed passages.

An intake pipe 14 through which the working fluid flows from an external refrigeration circuit is connected to an upper portion of an intake tank 15 having a gas-liquid separation function, and a first intake pipe 16a and a second intake pipe 16b for the compressor are connected to a bottom portion of the intake tank 15. The first intake pipe 16A communicates with the inside of the first cylinder chamber 10a via an intake passage 17a formed in the first cylinder 6A, and the second intake pipe 16B communicates with the inside of the second cylinder chamber 10B via an intake passage 17B formed in the second cylinder 6B.

Reference numeral 18 denotes a discharge pipe for discharging the high-pressure working fluid in the sealed container 1 to the external refrigeration circuit. Further, reference numeral 28 denotes a fixing bolt for assembling the compression element, and 29 denotes a discharge passage for guiding the working fluid discharged into the lower discharge cover 8a into the upper discharge cover 7 a.

As a method for achieving a mechanical displacement variable operation (cylinder deactivation operation) of a hermetic rotary compressor, a method is known in patent document 1 in which a tip end portion and a rear end portion of a movable blade (vane) are made to have the same pressure without applying a differential pressure and the movable blade is attracted by a permanent magnet so as not to protrude into a cylinder tube, thereby restricting the movable blade.

Reference numeral 20 denotes a solenoid for controlling the movement of the blade 11b, and is electrically connected to a power switch circuit (not shown) of the compressor. Reference numeral 20a denotes a movable iron core of the solenoid 20, 20B denotes a mounting member for fixing the solenoid 20 to the

second cylinder

6B, and 21 denotes a slide pin disposed to be reciprocatingly movable on an end plate of the sub-bearing 8, and one end of the slide pin abuts against the movable iron core 20 a. Reference numeral 22 denotes a return spring for releasing the regulation of the slide pin 21 on the vane when the solenoid 20 is turned off, and 23 denotes a groove formed in the lower end surface of the vane 11b and engaged with the end portion of the slide pin 21 having the inclined surface.

The full displacement operation and the mechanical displacement variable operation (cylinder deactivation operation) of the present embodiment will be described with reference to fig. 4 and 5.

Fig. 4 shows a full displacement (double cylinder) operating state in which both the first cylinder chamber 10a and the second cylinder chamber 10b perform a compression action. In the full displacement operation, since the solenoid 20 is not energized, the magnetic attraction force does not act on the movable iron core 20a, the slide pin 21 is moved downward by the elastic force of the return spring 22, the movable iron core 20a is also in a state of abutting against the stopper portion at the lower end, and any mechanical restriction that restricts the movement of the vane 11b is not applied. Therefore, when the motor is energized to rotate the rotary shaft 4, the first and

second drums

9a and 9b are eccentrically moved in the first and second

cylindrical chambers

10a and 10b, and the

vanes

11a and 11b are urged by the vane springs 12a and 12b to contact the outer peripheries of the first and

second drums

9a and 9b, so that a normal compression action is exerted in the double

cylindrical chambers

10a and 10b, and the high-pressure working fluid is discharged into the sealed container 1 through the discharge covers 7a and 8a, and flows out to the outside of the refrigeration cycle through the discharge pipe 18 at the upper portion of the sealed container 1.

Fig. 5 shows a mechanical displacement variable operation (single cylinder deactivation operation) in which the first cylinder chamber 10a performs a normal compression operation and the second cylinder chamber 10b performs a cylinder deactivation operation. In the displacement halving operation, the solenoid 20 is energized to apply a magnetic attractive force to the movable iron core 20a, so that the slide pin 21 moves upward against the elastic force of the return spring 22 and enters the groove 23 formed in the lower end surface of the vane 11 b. When the slide pin 21 enters the groove 23 of the vane 11b, the vane 11b does not return into the cylinder chamber 10b even if it is pressed by the vane spring 12 b. Therefore, even if the motor is energized to rotate the rotary shaft 4, the first and

second rollers

9a and 9b are eccentrically moved in the first and

second cylinder chambers

10a and 10b, and the second cylinder chamber 10b is not partitioned by the vane 11b, so that the volume in the cylinder chamber 10b is not changed and the compression action is not exerted. On the other hand, in the first cylindrical chamber 10a, the vane 11a is brought into contact with the outer periphery of the first drum 9a by the vane spring 12a and acts on the outer periphery thereof, so that a normal compression action is exerted in the cylindrical chamber 10a, and the high-pressure working fluid is discharged into the sealed container 1 through the discharge cover 7a and flows out to the outside of the refrigeration cycle through the discharge pipe 18 at the upper portion of the sealed container 1. Further, the sliding pin 21 is merely used to stop the movement of the vane 11b, and the compression action can be eliminated, but the two members collide with each other near the top dead center position of the vane 11b, which is likely to cause noise and increase in mechanical loss.

In order to solve this problem, in the present embodiment, the end portion contact surface of the slide pin 21 that engages with the groove 23 formed in the lower end surface of the vane 11b is made to be an inclined surface, and the vane 11b is attracted by the magnetic attraction force of the solenoid 20 until the tip portion of the vane 11b is positioned at a position retreated from the inner wall of the second cylinder chamber 10b by a dimension.

Next, an oil flow passage for eliminating the remaining lubricant oil in the cylinder tube provided with the cylinder deactivation mechanism, which is a characteristic feature of the present embodiment, will be described with reference to fig. 6 to 8. In the drawing, reference numeral 24 denotes a cylinder oil flow passage formed in the second cylinder 6B for performing the cylinder deactivation operation, and is formed so as to penetrate the cylinder 6B in the axial direction at a position between the vane 11B and the suction passage 17B. Reference numeral 24a denotes a cylinder bore notch which opens the lower end of the cylinder oil flow passage 24 into the cylinder bore

chamber

10b, and 25 denotes a partition plate oil flow passage which is formed in the partition plate 5 and communicates with the cylinder oil flow passage 24, and the diameter thereof is made larger than the diameter of the cylinder oil flow passage 24 in consideration of assembly variation. Reference numeral 26 denotes a cylinder cut on the operating cylinder 6A side where the upper end of the partition plate oil flow passage 25 opens into the cylinder chamber 10 a. Further, 7b 'is a discharge port engaged with a discharge port of the relief valve device 7b of the

main bearing

7, and 8 b' is a discharge port engaged with a discharge port of the relief valve device 8b of the sub-bearing 8.

As described above, during the displacement halving operation, the low pressure state continues in the second cylinder chamber 10b due to the suction pipe 16b connected to the suction tank 15 and the suction passage 17b communicating with the suction pipe 16 b. On the other hand, since the normal compression operation is performed in the first cylinder chamber 10a, the high-pressure working fluid is discharged into the sealed container 1, and the inside of the sealed container 1 is in a high-pressure state. Therefore, the lubricant oil 19 stored in the bottom portion of the closed casing 1 enters the second cylinder chamber 10B through the gaps between the respective components constituting the second rotary compression element part 2B. The lubricant oil after the entry is retained below the second cylinder chamber 10b by the action of gravity. The accumulated lubricating oil is sucked up to the first rotary compression element part 2A through the cylinder oil flow passage 24 and the partition oil flow passage 25 as indicated by arrows in fig. 8. That is, since the compression action is exerted in the first cylinder chamber 10a, the pressure on the partition plate oil flow passage 25 side opened by the cylinder cut 26 becomes a negative pressure lower than the suction pressure (the pressure in the suction tank 15). On the other hand, since the pressure in the second cylinder chamber 10B is maintained at the suction pressure, the lubricating oil that has intruded into the second cylinder chamber 10B due to the pressure difference between the two is sucked up from the cylinder cut 24a that opens at the lower end of the second cylinder 6B and is guided into the first cylinder chamber 10a through the cylinder cut 26 via the cylinder oil flow passage 24 and the partition oil flow passage 25, and therefore the lubricating oil remaining in the lower cylinder chamber 10B provided with the cylinder deactivation mechanism is eliminated, and the loss due to oil agitation can be suppressed. Further, by supplying the lubricating oil guided through the cylinder oil flow passage 24 and the partition oil flow passage 25, the oil-tightness of the first rotary compression element part 2A on the operating cylinder side can be improved to improve the performance, and thus a hermetic rotary compressor having excellent performance and reliability can be realized.

In the present embodiment, the cylinder oil flow passage 24 and the partition plate oil flow passage 25 are each formed to have a passage area sufficiently smaller than the passage areas of the first intake passage 17a and the second intake passage 17b connecting the cylinder chamber and the intake pipe. Thus, during the full displacement operation, the cylinder oil flow passage 24 and the partition plate oil flow passage 25 are prevented from interfering with the suction action of the working fluid in the first rotary compression element part 2A and the second rotary compression element part 2B, and the respective compression efficiencies are not impaired.

In the present embodiment, the second rotary compression element portion 2B provided with the cylinder deactivation mechanism is provided on the side of the sub bearing 8, and the first rotary compression element portion 2A not deactivating the cylinder is provided on the side of the main bearing 7. Accordingly, even in the mechanical displacement variable operation (cylinder deactivation operation), since most of the bearing load can be shared by the main bearing 7, an increase in mechanical loss and a reduction in reliability of the bearing can be suppressed as compared with a structure in which the two rotary compression elements are vertically replaced.

Next, a specific example of a refrigerating and air-conditioning apparatus incorporating the hermetic rotary compressor of the present embodiment will be described with reference to a refrigerating cycle configuration diagram shown in fig. 12. Fig. 12 is a schematic diagram of a refrigeration cycle including hermetic rotary compressor 30 of the present embodiment. Here, a refrigeration cycle using R32 refrigerant as a working fluid will be described as an example. The Global Warming Potential (GWP) of R32 is smaller than that of refrigerant R410A conventionally used in a refrigeration and air-conditioning system, and is a refrigerant that has received attention in recent years from the viewpoint of preventing global warming.

In fig. 12, the same reference numerals as those in fig. 1 denote the same components and perform the same functions, and a refrigeration cycle 31 including a hermetic rotary compressor 30 of the present embodiment is shown. Further, a condenser 32, an expansion valve 33, and an evaporator 34 are connected in this order by a refrigerant pipe 35, thereby constituting a refrigeration cycle.

Next, the flow of the refrigerant in fig. 12 will be described. The high-temperature and high-pressure refrigerant discharged from hermetic rotary compressor 30 enters condenser 32 and radiates heat, thereby decreasing the temperature. The refrigerant flowing out of the condenser 32 enters an expansion valve 33, turns into a low-temperature, low-pressure gas-liquid two-phase refrigerant, and is discharged. The two-phase gas-liquid refrigerant flowing out of the expansion valve 33 enters the evaporator 34, absorbs heat, is gasified, returns to the hermetic rotary compressor 30, is compressed again, and thereafter repeats the same cycle. Thus, in the case of the refrigeration apparatus, the evaporator 34 cools the object to be cooled. In the case of an air conditioner, the evaporator 34 performs a cooling operation by cooling the indoor air, or the condenser 32 performs a heating operation by heating the indoor air. As described above, by providing the hermetic rotary compressor 30 of the present embodiment, it is possible to provide a hermetic rotary compressor excellent in performance and reliability at the time of the mechanical displacement variable operation (cylinder deactivation operation), and to improve the performance and reliability of the refrigerating and air-conditioning system.

According to the configuration of embodiment 1 described above, it is possible to improve the performance by reducing the oil agitation loss of the cylinder deactivation cylinder and improving the oil tightness of the operating cylinder, and thus it is possible to realize a hermetic rotary compressor excellent in performance and reliability. In addition, the performance and reliability of the refrigerating and air-conditioning system provided with the compressor can be improved.

In embodiment 1, the description has been given of the application to the compression element of the double cylinder type, but the present invention is not limited to this, and can be applied to a rotary compressor including a compression element of the three cylinder type. In addition, in the rotary compression element unit without the cylinder deactivation mechanism, the same effect is obtained not only in a structure in which the vane elastically presses the drum but also in a swing type rotary compressor in which the drum and the vane are integrated.

Example 2

Fig. 9 is a transverse sectional view (corresponding to the section a-a in fig. 1) of the hermetic rotary compressor according to embodiment 2, fig. 10 is an enlarged sectional view of a main portion of fig. 9, and fig. 11 is a perspective view of an inner wall surface of the cylinder tube in the vicinity of the vane as viewed from the center of the cylinder tube in fig. 9. In the drawings, the same reference numerals as those in fig. 1 denote the same members and perform the same functions.

In the present embodiment, the suction chamber is formed in the cylinder chamber of the rotary compression element provided with the cylinder deactivation mechanism, the suction passage connects the cylinder chamber of the other rotary compression element and the suction pipe, and the oil flow passage communicating the suction chamber and the suction passage is provided, whereby the pressure difference between the spaces on both sides of the opening of the oil flow passage can be more effectively utilized to guide the lubricating oil having intruded into the cylinder chamber provided with the cylinder deactivation mechanism into the operating cylinder through the oil flow passage.

In fig. 9 to 11, 25a is a partition plate oil flow groove communicating with the partition plate oil flow passage 25 and guiding the oil flow direction to the lower portion of the

intake passage

17a, and 27 is a cylinder oil flow passage communicating the partition plate oil flow groove 25a and the intake passage 17 a.

The pressure in the suction passage 17a, which opens to the cylinder oil flow passage 27 on the operation cylinder side, has a lower negative pressure than the pressure in the first cylinder chamber 10a, which exerts a dynamic pressure effect due to the flow of the working fluid. Since the pressure in the second cylinder chamber 10B, which is the cylinder deactivation cylinder, is maintained at the suction pressure, the lubricating oil that has intruded into the second cylinder chamber 10B due to the pressure difference between the two is sucked up from the cylinder cut 24a that opens at the lower end portion of the second cylinder 6B as shown by the arrow in fig. 11, and is guided into the suction passage 17a from the cylinder oil passage 27 through the cylinder oil passage 24, the partition oil passage 25, and the partition oil through groove 25a, whereby the lubricating oil that has intruded into the cylinder deactivation cylinder can be more effectively guided to the operating cylinder side. In this embodiment, as in embodiment 1, the remaining of the lubricant oil in the cylinder tube provided with the cylinder deactivation mechanism can be eliminated to improve the performance and reliability of the hermetic rotary compressor.

Description of the symbols

1-a closed container, 2-a rotary compression element part, 2A-a first rotary compression element part, 2B-a second rotary compression element part, 3-a motor part, 3 a-a stator, 3B-a rotor, 4-a rotary shaft, 4a, 4B-an eccentric part, 5-a partition plate, 6A-a first cylinder, 6B-a second cylinder, 7-a main bearing, 7 a-a discharge cover, 7B-a discharge valve device, 8-a sub-bearing, 8 a-a discharge cover, 8B-a discharge valve device, 9a, 9B-a roller, 10 a-a first cylinder chamber, 10B-a second cylinder chamber, 11a, 11B-a blade, 12A, 12B-a blade spring, 14-a suction pipe, 15-a suction tank, 16A, 16B-a suction pipe, 17a, 17B-a suction passage, 18-a discharge pipe, 19-a lubricating oil, 20-a solenoid, 20 a-a movable iron core, 20B-a mounting piece, 21-slide pin, 22-return spring, 23-groove, 24-cylinder oil flow path, 24 a-cylinder cut, 25-partition plate oil flow path, 25 a-partition plate oil flow groove, 26-cylinder cut, 27-cylinder oil flow path, 28-fixing bolt, 29-discharge path, 30-hermetic rotary compressor, 31-refrigeration cycle, 32-condenser, 33-expansion valve, 34-evaporator, 35-refrigerant piping.

Claims

1. A hermetic rotary compressor is provided with:

a closed container provided with a discharge pipe and two suction pipes;

a motor provided in the closed container and rotating a rotating shaft;

two rotary compression elements provided below the motor and driven by rotation of the rotary shaft; and

a partition plate which partitions the two rotary compression elements,

the above-mentioned hermetic rotary compressor is characterized in that,

each rotary compression element has: a cylinder having a cylinder chamber communicating with the suction pipe via a suction passage; a drum which is eccentrically and rotatably accommodated in the cylinder chamber; a vane for dividing the cylinder chamber into a suction chamber and a compression chamber; and a relief valve device for discharging the working fluid compressed in the cylinder chamber into the closed casing,

the lower rotary compression element has a cylinder deactivation mechanism for stopping the compression operation and a cylinder oil flow passage for sucking up the lubricating oil entering the cylinder chamber of the lower rotary compression element,

a partition plate oil flow passage is disposed in the partition plate to communicate the suction chamber of the lower rotary compression element with the suction chamber of the upper rotary compression element,

the cylinder oil flow passage is open at a lower end of the cylinder of the lower rotary compression element.

2. A hermetic rotary compressor is provided with:

a closed container provided with a discharge pipe and two suction pipes;

a motor provided in the closed container and rotating a rotating shaft;

a partition plate which partitions the two rotary compression elements,

the above-mentioned hermetic rotary compressor is characterized in that,

a partition plate oil flow passage is disposed in the partition plate to communicate the suction chamber of the lower rotary compression element with the suction passage of the upper rotary compression element,

3. The hermetic rotary compressor according to claim 1 or 2,

the rotary compression element on the lower side is a rotary compression element as follows: performing a compression operation in a state where a tip end portion of the vane is elastically pressed against an outer periphery of the drum, performing a cylinder deactivation operation in a state where the tip end portion of the vane is separated from the outer periphery of the drum,

the upper rotary compression element is a rotary compression element that performs a compression operation in a state where the tip end of the vane is elastically pressed against the outer periphery of the drum or a swing compression element that performs a compression operation using the drum integrally formed with the vane.

4. The hermetic rotary compressor according to claim 1 or 2,

in the partition plate oil flow passage, the lubricating oil flows from the lower rotary compression element to the upper rotary compression element.

5. The hermetic rotary compressor according to claim 1 or 2,

the partition plate oil flow passage is formed to have a passage area smaller than that of the suction passage of the upper rotary compression element and that of the suction passage of the lower rotary compression element.

6. The hermetic rotary compressor according to claim 1 or 2,

the working fluid is R32.

7. A refrigerating and air-conditioning apparatus having a refrigerating cycle in which a hermetic rotary compressor, a condenser, an expansion device, and an evaporator are connected by refrigerant piping, characterized in that,

the above-mentioned hermetic rotary compressor is the hermetic rotary compressor recited in any one of claims 1 to 4.