JP6927731B2 - Closed compressor and refrigeration cycle equipment - Google Patents

Description

An embodiment of the present invention relates to a closed compressor having two cylinder chambers and a refrigerating cycle apparatus including the closed compressor to form a refrigerating cycle.

Conventionally, a closed compressor is often used in which an electric motor unit and a compression mechanism unit connected via a rotating shaft are housed in a closed container, and the compression mechanism unit is provided with two cylinder chambers via an intermediate partition plate. Then, the rollers eccentrically move in each cylinder chamber to compress the gas refrigerant which is the working fluid and discharge it into the closed container via the bearing muffler attached to the cylinder.

In Patent Document 1, the intermediate partition plate interposed between the two cylinders is divided into two along the axial direction, and the two intermediate partition plates form a partition plate space communicating with the inside of the closed container. Further, there is disclosed a technique capable of increasing the capacity by discharging the gas refrigerant compressed in the cylinder chamber to the partition plate space of the intermediate partition plate divided into two together with the bearing muffler chamber.

Japanese Patent No. 2013-83245

By the way, in order to guide the gas refrigerant discharged into the partition plate space of the intermediate partition plate divided into two into the closed container, it is necessary to secure a discharge flow path. In the technique of Patent Document 1, the discharged gas refrigerant from the partition plate discharge space and the bearing muffler chamber is merged into one discharge flow path and guided to the bearing muffler.

In order to improve the compression performance of the compressor, it is required to increase the area of the gas refrigerant discharge flow path from the partition plate discharge space. However, if the area of the gas refrigerant discharge flow path from the partition plate discharge space is increased, the wall thickness of the partition plate is partially reduced, which may reduce the rigidity of the partition plate and impair the reliability of the compressor. ..
Further, if the thickness of the partition plate is increased in order to prevent the rigidity of the partition plate from being lowered, the distance between the main bearing and the sub-bearing becomes large, so that the rotating shaft tends to bend, and eventually the reliability as a compressor is impaired. There is a risk.

The problem to be solved by the present invention is a closed type that can suppress a decrease in the rigidity of the partition plate while sufficiently securing a discharge flow path area of the gas refrigerant from the partition plate discharge space, and can improve the compression performance and reliability. It is to provide a compressor and a refrigeration cycle apparatus equipped with this closed type compressor.

In order to achieve the above object, the closed compressor of the embodiment accommodates an electric motor unit and a compression mechanism unit connected via a rotating shaft in a closed container. The compression mechanism unit includes a first muffler provided in order along the rotation axis, a main bearing, a first cylinder having a first cylinder chamber, a first partition plate, and a first partition plate. A second partition plate for forming a partition plate space, a second cylinder having a second cylinder chamber, an auxiliary bearing, and a second muffler are provided.
A first discharge valve mechanism for discharging the working fluid compressed by the first cylinder to the first muffler is provided in the main bearing, and the working fluid compressed in the first cylinder chamber is discharged to the partition plate space. A first sluice plate discharge valve mechanism is provided on the first sluice plate. A second discharge valve mechanism for discharging the working fluid compressed in the second cylinder chamber to the second muffler is provided in the auxiliary bearing, and the working fluid compressed in the second cylinder chamber is discharged into the partition plate space. A second partition plate discharge valve mechanism is provided on the second partition plate.
A confluence passage is provided to merge the working fluid of the second muffler chamber and the working fluid of the partition plate space and lead to the first muffler chamber, and the axis of the rotation axis of the connecting flow path connected to the confluence passage of the partition plate space. Make the dimensions in the orthogonal direction larger than the dimensions along the axial direction.
An independent partition plate fluid passage that guides the working fluid discharged into the partition plate space to the first muffler chamber, or an independent muffler chamber that guides the working fluid discharged into the second muffler chamber to the first muffler chamber. It has a fluid passage.

The vertical sectional view of the closed type compressor and the refrigerating cycle block diagram of the refrigerating cycle apparatus according to 1st Embodiment. A plan view (A) of the first partition plate according to the same embodiment and an explanatory view (B) showing the flow of the refrigerant in the compression mechanism section. The figure which shows the cross section of the connection passage of the partition plate by the same embodiment. 2 is a plan view (A) of the first partition plate, a plan view (B) of the second partition plate, and an explanatory view (C) showing the flow of the refrigerant in the compression mechanism portion according to the second embodiment.

Hereinafter, embodiments for carrying out the invention will be described.
(First Embodiment)
This embodiment will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the sealed compressor 1 of the first embodiment and a refrigerating cycle configuration diagram of a refrigerating cycle device R which is, for example, an air conditioner.
In the figure, reference numeral 1 denotes a closed type compressor (hereinafter, simply referred to as a “compressor”), and the compressor 1 will be described later.

A refrigerant pipe P is connected to the compressor 1, and a condenser 2 which is a radiator, an expansion valve (expansion device) 3, an evaporator 4 which is a heat absorber, and an accumulator 5 are sequentially provided in the refrigerant pipe P. Further, the refrigerant pipe P is branched from the accumulator 5 into two and connected to the side portion of the compressor 1, and the refrigerating cycle of the refrigerating cycle device R is formed by these.

Next, the compressor 1 will be described.
The compressor 1 includes a closed container 10, an electric motor unit 11 is housed on the upper side of the closed container 10, a compression mechanism part 12 is housed on the lower side, and the motor part 11 and the compression mechanism part 12 rotate. It is connected via a shaft 13. Lubricating oil is stored in the inner bottom portion of the closed container 10, and the remaining internal space is filled with a high-pressure gas refrigerant which is a working fluid compressed by the compression mechanism portion 12.

A discharge pipe 1a is provided on the upper surface of the closed container 10, and a refrigerant pipe P communicating with the condenser 2 is connected to the discharge pipe 1a. Further, two suction pipes 1b and 1b are provided on the lower peripheral wall of the closed container 10, and the suction pipes 1b and 1b communicate with the accumulator 5.

In the motor unit 11, the rotor 15 to which the rotating shaft 13 is fitted and fixed and the outer peripheral surface of the rotor 15 and the inner peripheral surface face each other through a narrow gap, and the inner peripheral wall of the closed container 10 is opposed to each other. It is composed of a stator (stator) 16 that is fitted and fixed to.

The rotating shaft 13 is formed with two columnar eccentric portions a and b protruding toward the outer peripheral side. These eccentric portions a and b are provided at positions separated by a predetermined dimension along the axial direction of the rotating shaft 13 and eccentric in a direction displaced by 180 ° along the rotating direction of the rotating shaft 13. The portion between the eccentric portions a and b with respect to the rotating shaft 13 is referred to as an intermediate shaft portion c.

The compression mechanism portion 12 includes a main bearing 17, a first cylinder 18, an intermediate partition plate 20, a second cylinder 22, and an auxiliary bearing 23 along the axial direction of the rotating shaft 13. The main bearing 17 and the sub-bearing 23 rotatably support the rotating shaft 13 at their respective boss portions.

A first muffler 25, which is a hollow case surrounding the flange portion of the main bearing 17, is attached to the flange portion, and a first muffler chamber 25a is formed inside. Further, the first muffler 25 is provided with a plurality of communication holes for communicating the inside of the muffler chamber 25a and the space inside the closed container 10.
A second muffler 26, which is a hollow case surrounding the flange portion of the auxiliary bearing 23, is attached to the flange portion, and a second muffler chamber 26a is formed inside.

The intermediate partition plate 20 is interposed between the first cylinder 18 and the second cylinder 22, and surrounds the intermediate shaft portion c formed between the two eccentric portions a and b of the rotating shaft 23. surround. The intermediate partition plate 20 is divided into a first partition plate 20a and a second partition plate 20b along the axial direction of the rotating shaft 13.

The inner diameter hole of the first cylinder 18 is closed at the upper end by the main bearing 17 and at the lower end by the first partition plate 20a constituting the intermediate partition plate 20 to form the first cylinder chamber 18A. NS.
The inner diameter hole of the second cylinder 22 is closed on the upper end side by the second partition plate 20b constituting the intermediate partition plate 20, and the lower end side is closed by the auxiliary bearing 23 to form the second cylinder chamber 22A.

A rotary shaft 13 is inserted into the first and second cylinder chambers 18A and 22A, and one eccentric portion a formed on the rotary shaft 13 is located in the first cylinder chamber 18A and is formed on the rotary shaft 13. The other eccentric portion b is located in the second cylinder chamber 22A.
A roller 27 is fitted to one eccentric portion a, and a roller 28 is fitted to the other eccentric portion b. The rollers 27 and 28 roll while a part of the outer peripheral wall of the rotating shaft 13 abuts on the inner peripheral walls of the first and second cylinder chambers 18A and 22A.

Blades (not shown) are slidably provided in the first and second cylinder chambers 18A and 22A, respectively, and are urged by an elastic body such as a spring so that the tip of the blade is attached to the outer peripheral walls of the rollers 27 and 28. Contact.
A part of the outer peripheral walls of the rollers 27 and 28 abuts on a part of the inner peripheral walls of the first and second cylinder chambers 18A and 22A, and the tip of the blade elastically abuts on the outer peripheral walls of the rollers 27 and 28. As a result, the inside of the first and second cylinder chambers 18A and 22A is divided into two spaces whose volumes change with the rolling of the rollers 27 and 28.

The suction pipe 1b for sucking the low-pressure gas refrigerant into the first cylinder chamber 18A is connected to the first cylinder 18. The suction pipe 1b for sucking the low-pressure gas refrigerant into the second cylinder chamber 22A is connected to the second cylinder 22.

As schematically shown in FIG. 2 (B), the flange portion of the main bearing 17 has a discharge port 30a for discharging the gas refrigerant compressed by the eccentric movement of the roller 27 from the first cylinder chamber 18A, and the discharge port 30a. A first bearing discharge valve mechanism 30 is provided, which includes a lead valve 30b that opens and closes the port 30a at a predetermined pressure, and a valve holding plate 30c that regulates the maximum opening degree of the lead valve 30b.

When the lead valve 30b of the first bearing discharge valve mechanism 30 is opened and the discharge port 30a is released, the first cylinder chamber 18A and the first muffler in the first muffler 25 attached to the main bearing 17 are opened. It communicates with the room 25a.

The flange portion of the auxiliary bearing 23 includes a discharge port 31a for discharging the gas refrigerant compressed by the eccentric movement of the roller 28 from the second cylinder chamber 22A, and a lead valve 31b for opening and closing the discharge port 31a at a predetermined pressure. A second bearing discharge valve mechanism 31 including a valve holding plate 31c that regulates the maximum opening degree of the lead valve 31b is provided.
The reed valve 31b of the second bearing discharge valve mechanism 31 opens, and the discharge port 31a is opened and closed, so that the second cylinder chamber 22A and the muffler chamber 26a in the second bearing muffler 26 attached to the auxiliary bearing 23 are opened. And are in communication.

The gas refrigerant discharged to the second muffler chamber 26a is guided to the first muffler chamber 25a via the merging passage S described later.

The first partition plate 20a includes a discharge port 33a that discharges a gas refrigerant compressed by the eccentric movement of the roller 27 from the first cylinder chamber 18A, and a lead valve 33b that opens and closes the discharge port 33a at a predetermined pressure. A first sluice plate discharge valve mechanism 33 including a valve holding plate 33c that regulates the maximum opening degree of the lead valve 33b is provided.

The second partition plate 20b includes a discharge port 34a for discharging the gas refrigerant compressed by the eccentric movement of the roller 28 from the second cylinder chamber 22A, and a lead valve 34b for opening and closing the discharge port 34a at a predetermined pressure. A second sluice plate discharge valve mechanism 34 including a valve holding plate 34c that regulates the maximum opening degree of the lead valve 34b is provided.
The total discharge flow rate of the gas refrigerant discharged from the first partition plate discharge valve mechanism 33 and the second partition plate discharge valve mechanism 34 is larger than the discharge flow rate of the gas refrigerant discharged from the second bearing discharge valve mechanism 31. The size of the inner diameters of the discharge ports 30a, 31a, 33a and 34a and the spring constants of the lead valves 30b, 31b, 33b and 34b are set for each member so as to be large.

The compressed gas refrigerant discharged from the first sluice plate discharge valve mechanism 33 and the second sluice plate discharge valve mechanism 34 is guided along the flow paths shown in FIGS. 2 (A) and 2 (B), which will be described later. It is designed to be used.

FIG. 2A is a plan view of the first partition plate 20a, and FIG. 2B is an explanatory view showing the flow of the refrigerant in the compression mechanism unit 12.
The mark in which cross-hatching is added to the circle shown in FIG. 2 (A) is a bolt hole d, and the main bearing 17 has an intermediate partition plate 20 divided into two with a first cylinder 18 and a second cylinder 22. It is for inserting a bolt that together with the auxiliary bearing 23.

A partition plate space 35 in which the first partition plate 20a and the second partition plate 20b receive the compressed gas refrigerant discharged from the first partition plate discharge valve mechanism 33 and the second partition plate discharge valve mechanism 34. Is forming. The partition plate space 35 includes a partition plate discharge space 35a and a connection flow path 35b. The partition plate discharge space 35a is a space of a portion where the first and second partition plate discharge valve mechanisms 33 and 34 are provided. The connection flow path 35b is a long space that continuously extends from the partition plate discharge space 35a along the plane of the partition plate 20. Further, the height of the partition plate discharge space 35a is provided to be larger than the height of the connection flow path 35b.

FIG. 3 is a cross-sectional view taken along the line AA of FIG. 2, which is an enlarged cross-sectional view taken along the axial direction of the rotating shaft 13 of the connecting flow path 35b formed in the intermediate partition plate 20. In this case, the first and second partition plates 20a and 20b each have a thickness of 10 mm, and form an intermediate partition plate 20 having a thickness of 20 mm. The connecting flow path 35b is formed by grooves having a depth of 5 mm and a width of 12 mm provided on the first and second partition plates 20a and 20b, and the length (height) t of the rotating shaft 13 in the axial direction is 10 mm. The length (width) h in the direction orthogonal to the axial direction of the rotating shaft 13 is a square shape of 12 mm, and the width h dimension of the flow path is formed larger than the height t dimension.

Further, the gas refrigerant discharged from the second cylinder chamber 22A to the second muffler chamber 26a formed in the second muffler 26 is supplied to the auxiliary bearing 23, the second cylinder 22, the second partition plate 20b, and the like. Each member is provided with a passage indicated by S in the drawing leading to the first muffler chamber 25a in the first muffler 25 via the flange portion of the first partition plate 20a, the first cylinder 18, and the main bearing 17. Be done. This passage is a merging passage S that communicates with the connecting flow path 35b of the partition plate space 35 in the second and first partition plates 20b and 20a. As for the discharge flow rate of the gas refrigerant from the second cylinder chamber 22A, since the partition plate space 35 is larger than the second muffler chamber 26a, the flow path area of the connection flow path 35b provided in the intermediate partition plate 20 is combined with the flow path area. The area of the flow path on the second muffler chamber 26a side of S is made larger so that the gas refrigerant can easily flow into the merging passage S from the partition plate space 35.

In such a configuration, when the electric motor unit 11 is energized, the rotating shaft 13 rotates and the compression mechanism unit 12 is driven, so that the first cylinder chamber 18A and the second cylinder chamber 22A partitioned by the blades are used. The suction chamber, which is one of the spaces, is negatively pressured, and the gas refrigerant, which is the working fluid, flows in.
The rollers 27 and 28 provided with a phase difference of 180 ° roll with the rotation of the rotating shaft 13, and the gas refrigerant flowing into the first cylinder chamber 18A and the second cylinder chamber 22A is partitioned by a blade. It is compressed by gradually reducing the volume of the discharge chamber, which is the other space.

When compressed to a predetermined pressure, the reed valve 30b of the first bearing discharge valve mechanism 30 opens, the discharge port 30a is released, and the compressed gas refrigerant is transferred from the first cylinder chamber 18A to the first muffler 25. It is discharged to the first muffler chamber 25a.
At the same time, the reed valve 33b of the first partition plate discharge valve mechanism 33 is opened, the discharge port 33a is released, and the compressed gas refrigerant is discharged from the first cylinder chamber 18A into the partition plate space 35.

The reed valve 31b of the second bearing discharge valve mechanism 31 is opened with a phase difference of 180 °, the discharge port 31a is released, and the compressed gas refrigerant is transferred from the second cylinder chamber 22A to the second muffler 26. Discharged to muffler chamber 26a

The gas refrigerant in the second muffler chamber 26a passes through the auxiliary bearing 23 and the second cylinder 22 via the merging passage S, and the second partition plate 20b constituting the intermediate partition plate 20 and the first partition. When passing through the plate 20a, it merges with the gas refrigerant flowing in through the connecting flow path 35b of the partition plate space 35, and passes through the first cylinder 18 and the merging passage S continuously provided in the main bearing 17. It is guided to 25a to the muffler chamber in the muffler 25 of 1.

At the same time, the reed valve 34b of the second partition plate discharge valve mechanism 34 is opened, the discharge port 34a is released, and the compressed gas refrigerant is discharged into the partition plate space 35.

The gas refrigerant discharged from the first sluice plate discharge valve mechanism 33 and the second sluice plate discharge valve mechanism 34 into the sluice plate space 35 passes through the connection flow path 35b to the first cylinder 18 and the main bearing 17. It is guided to the merging passage S provided along the first muffler chamber 25a of the first muffler 25 through the flange portion of the first muffler 25.
Eventually, the gas refrigerant compressed in the first cylinder chamber 18A and the gas refrigerant compressed in the second cylinder chamber 22A merge in the first muffler chamber 25a of the first muffler 25, and the closed container 10 It is released inside.

The closed container 10 is filled with a high-temperature and high-pressure gas refrigerant, circulates in the refrigerant pipe P connected to the discharge pipe 1a, and is guided to the condenser 2. Here, it is condensed and depressurized by the expansion valve 3 and evaporated by the evaporator 4. The ambient air is cooled by this evaporation, and the freezing (cooling) ability is exhibited as the freezing cycle device R.

The refrigerant leaving the evaporator 4 is gas-liquid separated by the accumulator 5, is guided to the first cylinder chamber 18A and the second cylinder chamber 22A via the suction pipes 1b and 1b of the compressor 1, and is compressed. Then, it is compressed again as described above and circulates in the above-mentioned path.

In this way, the gas refrigerant compressed in the first cylinder chamber 18A and discharged from the first partition plate discharge valve mechanism 33 into the partition plate space 35 and the second cylinder chamber 22A are compressed and second. The gas refrigerant discharged from the partition plate discharge valve mechanism 34 into the partition plate space 35 is guided to the muffler chamber 25a of the first muffler 25 via the common flow path S.

By making the cross section of the connecting flow path 35b of the partition plate space 35 square and making the width h dimension larger than the height t dimension, the connecting flow path 35b can be formed without increasing the thickness of the intermediate partition plate 20. The flow path area can be increased. Therefore, it is possible to prevent the distance between the main bearing 17 and the auxiliary bearing 23 from becoming large, and the reliability of the compressor is enhanced.
Further, the flow path resistance of the connection flow path 39a is reduced, and the pressure loss is improved.

Further, by adjusting the size of the inner diameters of the discharge ports 30a, 31a, 33a and 34a and the spring constants of the reed valves 30b, 31b, 33b and 34c, the discharge flow rate of the gas refrigerant to the partition plate space 35 can be adjusted to the second muffler. Since the flow rate is set to be larger than the discharge flow rate to the chamber 26a, noise can be reduced by the sound insulation effect of the intermediate partition plate 20.

(Second Embodiment)
The second embodiment will be described with reference to FIG. Elements that are the same as or similar to those in the first embodiment are designated by the same reference numerals, and duplicate description will be omitted as appropriate.
4A is a plan view of the first partition plate 20a according to the second embodiment, FIG. 4B is a plan view of the second partition plate 20b, and FIG. 4C is a plan view of the second partition plate 20b. It is a figure which shows the flow of the refrigerant of the compression mechanism part 12.

In the compressor of the second embodiment, in addition to the merging passage S, a partition plate fluid passage 36 and a muffler chamber fluid passage 38 are provided. The partition plate fluid passage 36 allows gas refrigerant discharged from the first and second cylinder chambers 18A and 22A to the partition plate space 35 to pass through the first cylinder 18 and the flange portion of the main bearing 17. Each member is provided so as to lead to the muffler chamber 25a formed in the muffler 25.
The muffler chamber fluid passage 38 supplies the gas refrigerant discharged from the second cylinder chamber 22A to the second muffler chamber 26a formed in the second muffler 26 by the auxiliary bearing 23, the second cylinder 22, and the second. Each member is provided so as to lead to the first muffler chamber 25a in the first muffler 25 via the partition plate 20b, the first partition plate 20a, the first cylinder 18, and the flange portion of the main bearing 17. Be done.

By forming the partition plate fluid passage 36 and the muffler chamber fluid passage 38 in this way, the area of the discharge passage for discharging the gas refrigerant compressed in the first and second cylinder chambers 18A and 22A is expanded, so that the pressure is increased. The loss can be reduced and the compression efficiency can be improved.

As shown in FIG. 4A, the partition plate fluid passage 36 is provided at a position closer to the discharge port 33a of the first partition plate discharge valve mechanism 33 than the merging passage S.
As a result, the pressure loss of the gas refrigerant discharged from the partition plate fluid passage 36 and unnecessary heat exchange can be reduced, and the compressor 1 with high efficiency can be provided.

According to the closed compressor of at least one embodiment described above, the width h dimension of the connection flow path 35b is larger than the height t dimension to reduce the flow path resistance, and the intermediate partition plate 20 is made thicker. It is possible to increase the flow path area of the connection flow path 35b without using it, and it is possible to provide a highly efficient and highly reliable compressor.
The partition plate space 35 described above includes a partition plate discharge space 35a and a connection flow path 35b, and the heights of the respective spaces are different. The height may be the same, but by reducing the height of the connection flow path 35b, the rigidity of the partition plate is increased without reducing the discharge amount to the partition plate space 35.
Further, a space having an intermediate height with respect to the two spaces may be provided between the partition plate discharge space 35a and the connection flow path 35b. In this case, the partition plate fluid passage 36 may be provided so as to communicate with the connection flow path 35b having the smallest space height, or may be provided so as to communicate with the space having an intermediate height. As a result, the amount of gas refrigerant discharged to the partition plate space 35 can be increased.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. This embodiment and its modifications are included in the scope and gist of the invention, as well as in the scope of the invention described in the claims and the equivalent scope thereof.

1 ... Sealed compressor (compressor), 10 ... Sealed container, 13 ... Rotating shaft, 11 ... Electric unit, 12 ... Compressing mechanism, 25a ... First muffler chamber, 25 ... First muffler, 17 ... Main Bearings, 18A ... 1st cylinder chamber, 18 ... 1st cylinder, 20a ... 1st partition plate, 20b ... 2nd partition plate, 22A ... 2nd cylinder chamber, 22 ... 2nd cylinder, 23 ... Auxiliary bearing, 26a ... 2nd muffler chamber, 26 ... 2nd muffler, 30 ... 1st discharge valve mechanism, 33 ... 1st sluice plate discharge valve mechanism, 31 ... 2nd discharge valve mechanism, 34 ... 2 partition plate discharge valve mechanism, 35 ... partition plate space, 35b ... connection flow path, 36 ... partition plate fluid passage, 38 ... muffler chamber fluid passage, S ... merging passage, 33a ... (1st partition plate discharge valve mechanism) ) Discharge port, h ... Connection flow path width, t ... Connection flow path height, 2 ... Condenser (radiator), 3 ... Expansion valve (expansion device), 4 ... Evaporator (heat absorber), R ... Refrigeration cycle

Claims (6)

A motor unit and a compression mechanism unit connected via a rotating shaft are housed in a closed container.
A first muffler, a main bearing, a first cylinder having a first cylinder chamber, and a first cylinder in which the compression mechanism portion forms a first muffler chamber provided in order along the rotation axis. A partition plate, a second partition plate that forms a partition plate space with the first partition plate, a second cylinder having a second cylinder chamber, an auxiliary bearing, and a second muffler chamber are formed. With a second muffler
A first bearing discharge valve mechanism for discharging the working fluid compressed in the first cylinder chamber to the first muffler chamber is provided in the main bearing, and the working fluid compressed in the first cylinder chamber is provided. A first partition plate discharge valve mechanism for discharging the fluid into the partition plate space is provided in the first partition plate.
A second bearing discharge valve mechanism for discharging the working fluid compressed in the second cylinder chamber to the second muffler chamber is provided in the auxiliary bearing, and the working fluid compressed in the second cylinder chamber is provided. In a closed compressor provided with a second partition plate discharge valve mechanism provided in the second partition plate.
A confluence passage is provided to merge the working fluid of the second muffler chamber and the working fluid of the partition plate space and lead to the first muffler chamber.
The dimension of the connecting flow path connected to the confluence passage in the partition plate space in the direction orthogonal to the axis of the rotation axis is larger than the dimension along the axial direction .
An independent partition plate fluid passage that guides the working fluid discharged into the partition plate space to the first muffler chamber, or
An independent muffler chamber fluid passage for guiding the working fluid discharged into the second muffler chamber to the first muffler chamber is provided.
A sealed compressor that features this. The cross-sectional shape of the connection flow path is made square.
The closed compressor according to claim 1. The first or second aspect of the present invention, wherein the partition plate fluid passage is provided at a position closer to the discharge port of the first partition plate discharge valve mechanism than the merging passage. Sealed compressor. In each discharge valve mechanism, the total discharge flow rate of the working fluid discharged from the first cylinder chamber and the second cylinder chamber to the partition plate space is the total discharge flow rate from the second cylinder chamber to the second muffler chamber. It is configured to be larger than the discharge flow rate discharged to
The sealed compressor according to claim 1 to 4. The flow path area of the connection flow path is larger than the flow path area of the merging passage on the second muffler chamber side.
The sealed compressor according to claim 5. The sealed compressor according to any one of claims 1 to 6, a radiator connected to the sealed compressor, an expansion device connected to the radiator, and the expansion device and the sealed type. Equipped with a heat absorber connected between the compressors
A refrigeration cycle device characterized by that.

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