CN109154296B - Hermetic Rotary Compressor and Refrigeration Air Conditioning Device - Google Patents

Abstract

The hermetic rotary compressor of the present invention includes an airtight container, a motor, two rotary compression elements driven by the motor, and a partition plate separating the two rotary compression elements, wherein each rotary compression element has a cylinder, and is eccentrically rotatably accommodated in a The roller of the cylinder chamber, the vane that divides the cylinder chamber into the suction chamber and the compression chamber, and the relief valve device that discharges the working fluid compressed in the cylinder chamber into the airtight container, and the rotary compression element on the lower side has A cylinder deactivation mechanism for stopping the compression operation, and a cylinder oil flow passage for sucking the lubricating oil that has entered the cylinder chamber, the partition plate is provided with a suction chamber for the lower rotational compression element and the upper rotational compression element. The partition plate oil flow passage communicated with the suction chamber.

Description

Hermetic Rotary Compressor and Refrigeration Air Conditioning Device

technical field

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

Background technique

In recent years, the hermetic rotary compressor has been standardized as a two-cylinder type rotary compressor having two sets of cylinders as rotary compression elements as the range of application capacities has expanded. In addition, among such compressors, a rotary compressor capable of performing an operation in which a compression action is exerted by two cylinder chambers and a machine provided with a cylinder capable of switching between compression and stop according to a load are known. Variable displacement operation (cylinder deactivation operation). In addition, in recent years, from the viewpoint of preventing global warming, as a refrigerant for refrigeration and air-conditioning systems, instead of the conventional R410A refrigerant, the R32 refrigerant having a small global warming potential has been attracting attention.

In the conventional rotary compressor of Patent Document 1, there is disclosed a hermetic rotary compressor which avoids the occurrence of a problem of restricting the return of the lubricating oil from the cylinder deactivation cylinder to the accumulator (suction tank) during deactivation operation. The man-hours are increased, thereby realizing cost reduction.

prior art literature

Patent Literature

Patent Document 1: Japanese Patent Laid-Open No. 2014-40812

SUMMARY OF THE INVENTION

The problem to be solved by the invention

The compression mechanism portion of the hermetic rotary compressor of Patent Document 1 is described as being a rotary compression mechanism portion having a cylinder tube having a cylinder chamber communicating with a suction passage, and being eccentrically accommodated in the cylinder tube The drum of the chamber, the rotor blade (vane) that abuts the front end of the drum to the peripheral wall of the drum and divides the cylinder chamber into the suction chamber and the compression chamber, and the discharge valve that discharges the gas compressed in the cylinder chamber into the airtight case The device is provided with a cylinder deactivation mechanism that guides the suction pressure to the cylinder chamber through the intake passage and separates the front end edge of the rotor from the peripheral wall of the drum to stop the compression operation. A communication passage 36 through which the compression mechanism portion of the mechanism and the suction chambers of the cylinder chambers of the other compression mechanism portions communicate with each other.

For example, paragraphs 0032, 0048, 0049, etc. of Patent Document 1 discloses a two-cylinder type rotary compressor in which an upper cylinder chamber having a cylinder deactivation mechanism and a cylinder chamber not having a cylinder deactivation mechanism are connected via a communication passage. The suction chambers of the lower cylinder chamber are communicated with each other, and the lubricating oil that has penetrated into the upper cylinder chamber is guided from the communication passage to the lower cylinder chamber without being guided to the accumulator, so that the lubrication during the deactivation operation is achieved. The return of the oil from the first cylinder chamber to the accumulator is restricted, so that a large amount of lubricating oil is prevented from accumulating in the accumulator, thereby preventing a shortage of lubricating oil in the airtight case.

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

In addition, when the cylinder chamber having the cylinder deactivation mechanism is arranged on the lower side of the intermediate partition plate, since the lubricating oil intruded into the first cylinder chamber stays below the cylinder chamber, it does not pass through the chamber provided in the first cylinder chamber. The communication hole of the intermediate partition plate is sufficiently guided to the operating cylinder chamber located above, and there is a problem that lubricating oil remains in the deactivation cylinder chamber, and the agitation loss of the oil increases due to the eccentrically rotating drum, and there is a mechanical displacement. The problem of reducing compressor performance during variable operation (cylinder deactivation operation).

An object of the present invention is to obtain a hermetic rotary compressor and a refrigerating and air-conditioning apparatus using the hermetic rotary compressor capable of improving the mechanical properties of a hermetic rotary compressor provided with a cylinder capable of switching between compression and stop according to a load. performance and reliability during variable displacement operation (cylinder deactivation).

solutions to problems

In order to achieve the above object, the hermetic rotary compressor of the present invention includes: a closed container provided with one discharge pipe and two suction pipes; a motor provided in the closed container to rotate a rotating shaft; two rotary compression elements , which are provided below the electric motor and are driven by the rotation of the above-mentioned rotating shaft; and a partition plate that separates the two rotational compression elements, each rotational compression element having: a cylinder, which is provided with the above-mentioned suction passage through a suction passage. A cylinder chamber communicated with a pipe; a drum that is eccentrically rotatably accommodated in the cylinder chamber; a vane that divides the cylinder chamber into a suction chamber and a compression chamber; The working fluid compressed in the chamber is discharged into the airtight container, and the rotary compression element on the lower side has a cylinder stop mechanism for stopping the compression operation, and a cylinder oil flow passage for sucking the lubricating oil that has penetrated into the cylinder chamber. The separator is provided with a separator oil flow passage that communicates the suction chamber of the lower rotational compression element with the suction chamber of the upper rotational compression element.

The effects of the invention are as follows.

According to the present invention, it is possible to obtain a hermetic rotary compressor capable of improving performance and reliability during mechanical variable displacement operation (cylinder deactivation), and a refrigerating and air-conditioning apparatus using the hermetic rotary compressor and having excellent year-round energy efficiency Effect.

Description of drawings

FIG. 1 is a longitudinal sectional view of the hermetic rotary compressor according to the first embodiment.

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1 .

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

FIG. 4 is an enlarged cross-sectional view of a main part of FIG. 3 showing a twin-cylinder operation state.

FIG. 5 is an enlarged cross-sectional view of a main part of FIG. 3 showing a single-cylinder deactivation operation state.

FIG. 6 is a cross-sectional view taken along line C-B2 of FIG. 2 , showing the structure of the oil flow passage, which is a feature of the first embodiment.

FIG. 7 is a D-D cross-sectional view of FIG. 6 .

FIG. 8 is a perspective view of the inner wall surface of the cylinder tube near the vanes as viewed from the center of the cylinder tube.

9 is a cross-sectional view taken along line A-A of FIG. 1 in Example 2. FIG.

FIG. 10 is an enlarged cross-sectional view of a main part of FIG. 9 .

FIG. 11 is a perspective view of the inner wall surface of the cylinder bore near the vanes as viewed from the center of the cylinder bore in FIG. 9 .

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

Detailed ways

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The same symbols in the drawings of the respective embodiments indicate the same or equivalent parts.

Example 1

The hermetic rotary compressor of the first embodiment will be described with reference to FIGS. 1 to 8 . 1 is a longitudinal cross-sectional view of a double-cylinder type hermetic rotary compressor, FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1 , FIG. 3 is a cross-sectional view taken along line B1-B2 of FIG. 2 , and FIG. 4 is a view of FIG. FIG. 5 is an enlarged cross-sectional view of a main part of FIG. 3 showing a single-cylinder deactivation state, and FIG. 6 is an enlarged cross-sectional view of a main part taken along line C-B2 of FIG. FIG. 7 is a D-D cross-sectional view of FIG. 6 , and FIG. 8 is a perspective view of the inner wall surface of the cylinder tube near the vane viewed from the center of the cylinder tube.

In FIGS. 1 to 3 , reference numeral 1 denotes an airtight container provided with one discharge pipe and two suction pipes. The airtight container 1 houses two rotary compression element parts 2 in the lower part and two rotary compression elements for driving in the upper part. The motor part 3 of the part 2 is connected to the rotary compression element part 2 via a rotating shaft 4 arranged vertically. The motor unit 3 includes a stator 3 a fixed to the inner surface of the airtight container 1 , and a rotor 3 b arranged inside the stator 3 a with a predetermined gap and fixed to the rotating shaft 4 . In addition, the motor unit 3 is electrically connected to an inverter (not shown) that controls the operating frequency.

The rotational compression element part 2 is constituted by a first rotational compression element part 2A and a second rotational compression element part 2B which are arranged on the upper and lower sides of the partition plate 5 . The upper first rotational compression element 2A includes a first cylinder 6A, and the lower second rotational compression element 2B includes a second cylinder 6B. The first cylinder 6A overlaps the lower surface of the main bearing 7 fixed to the inner surface of the airtight container 1 , and the sub bearing 8 is attached to the lower surface of the second cylinder 6B. The rotary shaft 4 is rotatably supported by the main bearing 7 and the sub-bearing 8, and integrally includes two eccentric portions 4a, 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 to the outer periphery of each of the eccentric portions 4a and 4b. 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 first cylinder chamber 10a is formed in the second cylinder 6B The second cylinder chamber 10b is formed.

A discharge cover 7 a that forms a discharge space for the compressed working fluid is attached to the main bearing 7 , and the discharge cover 7 a covers a relief valve device 7 b attached to an end plate of the main bearing 7 . A discharge cover 8 a is also attached to the sub-bearing 8 , and the discharge cover 8 a covers the relief valve device 8 b attached to the 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 compression, and discharges the compressed working fluid into the discharge cover 7a. 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 compression, and discharges the compressed working fluid into the discharge cover 8a.

Vanes 11a and 11b which are reciprocally arranged in the respective cylinder chambers 10a and 10b are accommodated in the first cylinder 6A and the second cylinder 6B, and leaf springs 12a and 12b are accommodated at the rear end portions of the respective vanes. The leaf springs 12a and 12b act on the outer peripheries of the drums 9a and 9b by abutting the tip end portions of the respective leaves by elastic force. 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 airtight container 1 . An oil supply pump is attached to the lower end surface of the rotary shaft 4, and lubricating oil is supplied from here to each sliding portion of the members constituting the second rotary compression element portion 2B and the first rotary compression element portion 2A through an oil supply passage.

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

18 is a discharge pipe which makes the high-pressure working fluid in the airtight container 1 flow out to an external refrigeration circuit. Further, 28 is a fixing bolt for assembling the compression element, and 29 is a discharge passage for guiding the working fluid discharged into the lower discharge cover 8a to the upper discharge cover 7a.

As a method of realizing a mechanical variable displacement operation (cylinder deactivation operation) of a hermetic rotary compressor, it is known that the front end and rear end of a rotor blade (blade) are set to the same pressure without applying the same pressure as disclosed in Patent Document 1. Differential pressure, and the method of attracting and restraining the moving blades by the permanent magnets so that the moving blades do not protrude into the cylinder, but in this embodiment, the cylinder deactivation can be realized by a simpler structure, and the electromagnetic force is used. A method of mechanically restraining the blades will be described.

20 is a solenoid for controlling the movement of the vane 11b, and is electrically connected to a power switch circuit (not shown) of the compressor. 20a is a movable iron core of the solenoid 20, 20b is a mount for fixing the solenoid 20 to the second cylinder 6B, 21 is a sliding pin reciprocatingly arranged on the end plate of the sub-bearing 8, one end is Abuts against the movable iron core 20a. 22 is a return spring for releasing the restriction of the vane by the slide pin 21 when the power supply of the solenoid 20 is turned off, and 23 is a groove formed on the lower end surface of the vane 11b and engaged with the end portion of the slide pin 21 having an 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 FIGS. 4 and 5 .

FIG. 4 shows a full-displacement (two-cylinder) operation state in which both the first cylinder chamber 10a and the second cylinder chamber 10b exert a compressing effect. During 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, and the movable iron core 20a also comes into contact with the movable iron core 20a. In the state of the limiting portion at the lower end, no mechanical restriction is imposed on the blade 11b to restrict its movement. Therefore, when the electric motor is energized and the rotating shaft 4 is driven to rotate, the first and second rollers 9a and 9b are eccentrically moved in the first cylinder chamber 10a and the second cylinder chamber 10b, and the blades 11a and 11b are moved eccentrically. The leaf springs 12a and 12b are urged to abut against the outer peripheries of the first and second rollers 9a and 9b, so that a normal compression action is exerted in the double cylinder chambers 10a and 10b, and the high-pressure working fluid flows through the discharge covers 7a and 8a. The air is discharged from the airtight container 1 and flows out to the external refrigeration cycle through the discharge pipe 18 at the upper part of the airtight container 1 .

5 shows a mechanical variable displacement 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. During the operation of reducing the displacement by half, the solenoid 20 is energized, so that a magnetic attractive force acts on the movable iron core 20a, so that the slide pin 21 overcomes the elastic force of the return spring 22 and moves upward, and enters the lower part of the blade 11b. Slot 23 on the end face. When the slide pin 21 enters the groove 23 of the vane 11b, even if the vane 11b is pressed by the vane spring 12b, it will not return to the cylinder chamber 10b. Therefore, even if the electric motor is energized and the rotating shaft 4 is driven to rotate, the first and second rollers 9a and 9b are eccentrically moved in the first cylinder chamber 10a and the second cylinder chamber 10b, and the second cylinder chamber Since the inside of 10b is not partitioned by the vanes 11b, there is no change in the volume of the cylinder chamber 10b, and the compression effect is not exerted. On the other hand, in the first cylinder chamber 10a, since the vane 11a is in contact with the outer periphery of the first roller 9a by the leaf spring 12a, a normal compressing action is exerted in the cylinder chamber 10a, and the high-pressure working fluid passes through the The discharge hood 7 a is discharged into the airtight container 1 , and flows out to the outside refrigeration cycle through the discharge pipe 18 in the upper part of the airtight container 1 . In addition, simply using the slide pin 21 to stop the movement of the vane 11b can eliminate the compression effect, but the two collide near the top dead center of the roller 9b near the vane 11b, which tends to cause noise and increase in mechanical loss.

In order to solve this problem, in the present embodiment, the abutting surface of the end portion of the slide pin 21 engaging with the groove 23 formed in the lower end surface of the blade 11b is an inclined surface, and the magnetic attraction force of the solenoid 20 is used to The suction-pulling vane 11b is located at a position retreated by a dimension δ from the inner wall of the second cylinder chamber 10b until the front end portion of the vane 11b.

Next, referring to FIGS. 6 to 8 , a description will be given of the oil flow passage for eliminating the residual oil in the cylinder bore provided with the cylinder deactivation mechanism, which is a feature of the present embodiment. In the drawings, reference numeral 24 denotes a cylinder oil flow passage formed in the second cylinder 6B performing the cylinder deactivation, 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. 24a is a cylinder cutout for opening the lower end of the cylinder oil flow passage 24 to the cylinder chamber 10b, and 25 is a partition plate oil flow passage formed in the partition plate 5 and communicated with the cylinder oil flow passage 24, which is made in consideration of assembly deviation. The diameter is larger than the diameter of the cylinder oil flow passage 24 . 26 is a cylinder bore cutout on the side of the operating cylinder 6A where the upper end of the partition plate oil flow passage 25 is opened to the cylinder chamber 10a. In addition, 7b' is a discharge port engaged with the discharge port of the relief valve device 7b of the main bearing 7, and 8b' is a discharge port engaged with the discharge port of the relief valve device 8b of the sub-bearing 8.

As described above, in the displacement halving operation, the inside of the second cylinder chamber 10b continues to be in a low pressure state due to the suction pipe 16b connected to the suction tank 15 and the suction passage 17b communicating with the suction pipe 16b. On the other hand, since the normal compression operation is performed in the first cylinder chamber 10a, the high-pressure working fluid is discharged to the airtight container 1, and the airtight container 1 becomes a high-pressure state. Therefore, the lubricating oil 19 stored in the bottom of the airtight container 1 intrudes into the second cylinder chamber 10b from the gaps between the respective components constituting the second rotational compression element part 2B. The lubricating oil that has penetrated is retained under the second cylinder chamber 10b by the action of gravity. The accumulated lubricating oil is sucked up to the first rotary compression element portion 2A via the cylinder oil flow passage 24 and the partition plate oil flow passage 25 as indicated by the arrows in FIG. 8 . That is, since the compression action is exerted in the first cylinder chamber 10a, the pressure on the side of the partition plate oil flow passage 25 opened by the cylinder cutout 26 becomes a negative pressure lower than the suction pressure (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 opened from the lower end portion of the second cylinder 6B The cylinder bore cutout 24a is sucked up, and is guided into the first cylinder bore chamber 10a from the cylinder bore cutout 26 through the cylinder bore oil flow passage 24 and the partition plate oil flow passage 25, so that the cylinder on the lower side with the cylinder deactivation mechanism is eliminated. The lubricating oil remaining in the cylinder chamber 10b can suppress the loss due to oil agitation. In addition, by supplying lubricating oil guided through the cylinder oil flow passage 24 and the partition plate oil flow passage 25, the oil sealability of the first rotary compression element portion 2A on the operating cylinder side can be improved to improve performance, so that performance and reliability can be achieved. Hermetic rotary compressor with excellent performance.

In this embodiment, both the cylinder oil flow passage 24 and the partition plate oil flow passage 25 are formed so that the passage area is sufficiently smaller than the passage area of the first suction passage 17a and the second suction passage 17b connecting the cylinder chamber and the suction pipe. This prevents the cylinder oil flow passage 24 and the partition plate oil flow passage 25 from interfering with the working fluid suction action of the first rotary compression element portion 2A and the second rotary compression element portion 2B during the full displacement operation, thereby preventing damage the respective compression efficiency.

In addition, in the present embodiment, the second rotational compression element 2B provided with the cylinder deactivation mechanism is provided on the sub bearing 8 side, and the first rotational compression element 2A without non-cylinder is provided on the main bearing 7 side. As a result, most of the bearing load can be shared by the main bearing 7 even during the mechanical variable displacement operation (cylinder deactivation operation), and therefore, compared with the structure in which the arrangement of the two rotating compression element parts is replaced up and down, it is possible to An increase in mechanical loss and a decrease in the reliability of the bearing are suppressed.

Next, a specific example of a refrigerating and air-conditioning apparatus incorporating the hermetic rotary compressor of the present embodiment will be described based on the refrigerating cycle block diagram shown in FIG. 12 . FIG. 12 is a schematic diagram of a refrigeration cycle including the hermetic rotary compressor 30 of the present embodiment. Here, a refrigerating cycle using R32 refrigerant as a working fluid will be described as an example. R32 has a smaller global warming potential (GWP) than R410A, a refrigerant that has been conventionally used in refrigeration and air conditioning systems, and has been attracting attention in recent years from the viewpoint of preventing global warming.

In FIG. 12 , the components denoted by the same reference numerals as those in FIG. 1 are the same components and perform the same functions, and show the refrigeration cycle 31 including the hermetic rotary compressor 30 of the present embodiment. In addition, 32 is a condenser, 33 is an expansion valve, and 34 is an evaporator, and these components are sequentially connected by the refrigerant piping 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 the hermetic rotary compressor 30 enters the condenser 32 and radiates heat, thereby reducing the temperature. The refrigerant flowing out of the condenser 32 enters the expansion valve 33, becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant, and is discharged. The gas-liquid two-phase refrigerant flowing out of the expansion valve 33 enters the evaporator 34, absorbs heat, vaporizes, returns to the hermetic rotary compressor 30, is compressed again, and repeats the same cycle. Accordingly, in the case of a refrigeration apparatus, the above-mentioned evaporator 34 cools the object to be cooled. In the case of an air conditioner, cooling operation is performed by cooling indoor air by the evaporator 34 , or heating operation by heating indoor air by the condenser 32 . As described above, by including the hermetic rotary compressor 30 of the present embodiment, it is possible to provide a hermetic rotary compressor excellent in performance and reliability during the mechanical variable displacement operation (cylinder deactivation operation), and to realize the refrigerating and air-conditioning system. Performance and reliability improvements.

According to the structure of the first embodiment described above, the performance improvement due to the reduction of oil stirring loss in the deactivation cylinder and the improvement of the oil tightness of the running cylinder can be achieved, so that the closed rotary compression excellent in performance and reliability can be realized. machine. Furthermore, the performance and reliability of the refrigeration and air-conditioning system including the compressor can be improved.

In addition, in Embodiment 1, the application to the compression element of the twin-cylinder type has been described, but the present invention is not limited to this, and can also be applied to a rotary compressor provided with a compression element of the triple-cylinder type. In addition, the rotary compression element without the cylinder deactivation mechanism is not limited to the structure in which the vane elastically presses the drum, and the same effect is obtained, for example, in a swing type rotary compressor in which the drum and the vane are integrated.

Example 2

9 is a cross-sectional view (corresponding to the A-A section in FIG. 1 ) of the hermetic rotary compressor according to the second embodiment, FIG. 10 is an enlarged cross-sectional view of a main part of FIG. 9 , and FIG. 11 is a view of the vicinity of the vanes from the center of the cylinder in FIG. 9 . Perspective view of the inner wall of the cylinder. In the drawings, the components denoted by the same reference numerals as those in FIG. 1 are the same components and perform the same functions.

In the present embodiment, a suction chamber is formed in the cylinder chamber of the rotary compression element provided with the cylinder deactivation mechanism, and the suction passage connects the cylinder chamber of the other rotary compression element and the suction pipe, and the suction chamber and the suction pipe are arranged to communicate with each other. The oil flow passage of the passage can more effectively utilize the pressure difference between the spaces on both sides of the opening of the oil flow passage to guide the lubricating oil entering the cylinder chamber having the cylinder deactivation mechanism into the operating cylinder through the oil flow passage.

In FIGS. 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 part of the suction passage 17a, and 27 is a cylinder connecting the partition plate oil flow groove 25a and the suction passage 17a. oil flow path.

Compared with the pressure in the first cylinder chamber 10a, the pressure in the suction passage 17a opened by the cylinder oil flow passage 27 on the operating cylinder side has the effect of the dynamic pressure due to the flow of the working fluid and becomes a lower negative pressure. pressure. The pressure in the second cylinder chamber 10b, which is the deactivation cylinder, is maintained at the suction pressure, and thus the lubricating oil that has intruded into the second cylinder chamber 10b due to the pressure difference between the two flows from the The cylinder cutout 24a opened at the lower end of the second cylinder 6B sucks upward, and is guided to the suction passage 17a from the cylinder oil flow passage 27 through the cylinder oil flow passage 24, the partition plate oil flow passage 25, and the partition plate oil flow groove 25a. In this way, the lubricating oil that has penetrated into the deactivation cylinder can be more effectively guided to the operating cylinder side. In the present embodiment, the performance and reliability of the hermetic rotary compressor can be improved by eliminating the residual lubricating oil in the cylinder bore provided with the cylinder deactivation mechanism, as in the first embodiment.

Explanation of symbols

1—Airtight container, 2—Rotation compression element, 2A—First rotation compression element, 2B—Second rotation compression element, 3—Motor part, 3a—stator, 3b—rotor, 4—rotating shaft, 4a, 4b—eccentric part, 5—dividing plate, 6A—first cylinder, 6B—second cylinder, 7—main bearing, 7a—discharge cover, 7b—relief valve device, 8—auxiliary bearing, 8a—discharge Cover, 8b—drain valve device, 9a, 9b—roller, 10a—first cylinder chamber, 10b—second cylinder chamber, 11a, 11b—vanes, 12a, 12b—vane springs, 14—suction pipe, 15 - suction tank, 16a, 16b - suction pipe, 17a, 17b - suction passage, 18 - discharge pipe, 19 - lubricating oil, 20 - solenoid, 20a - movable iron core, 20b - mounting piece, 21 - sliding pin , 22—return spring, 23—groove, 24—cylinder oil flow passage, 24a—cylinder bore cutout, 25—separation plate oil flow passage, 25a—separation plate oil flow groove, 26—cylinder bore cutout, 27—cylinder bore oil Flow passage, 28—fixing bolt, 29—discharge passage, 30—hermetic rotary compressor, 31—refrigeration cycle, 32—condenser, 33—expansion valve, 34—evaporator, 35—refrigerant piping.

Claims (7)

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;

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 passage 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.

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.

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