WO2018186357A1

WO2018186357A1 - Closed-type compressor and refrigeration cycle device

Info

Publication number: WO2018186357A1
Application number: PCT/JP2018/014139
Authority: WO
Inventors: 勝吾志田; 青木　俊公; 昌宏畑山
Original assignee: 東芝キヤリア株式会社
Priority date: 2017-04-07
Filing date: 2018-04-02
Publication date: 2018-10-11
Also published as: JP2018178793A; CN110520625B; KR20190119647A; CN110520625A; KR102222539B1; JP6927731B2

Abstract

Provided are a closed-type compressor and a refrigeration cycle device equipped with the same, the closed-type compressor being capable of ensuring a sufficient flow passage area of a discharge flow passage for discharging a gas refrigerant from a partitioning plate discharge space, suppressing a degradation in the stiffness of a partitioning plate, and achieving improvements in compression performance and reliability. The partitioning plate is provided with a partitioning plate space. A compression mechanism part is provided with a merging passage which merges a working fluid in a muffler chamber on a sub bearing side and a working fluid in the partitioning plate space and guides the fluids to a muffler chamber on a main bearing side. The partitioning plate space has a connection flow passage connected to the merging passage. The dimension of the connection flow passage in a direction perpendicular to an axis of a rotary shaft is greater than the dimension of the connection flow passage in the axial direction.

Description

Hermetic compressor and refrigeration cycle apparatus

Embodiments of the present invention relate to a hermetic compressor having two cylinder chambers and a refrigeration cycle apparatus that includes this hermetic compressor and constitutes a refrigeration cycle.

Conventionally, a hermetic compressor in which an electric motor part and a compression mechanism part connected via a rotating shaft are accommodated in a sealed container, and the compression mechanism part includes two cylinder chambers via an intermediate partition plate is often used. The rollers are eccentrically moved in the respective cylinder chambers to compress the gas refrigerant as the working fluid, and the compressed gas refrigerant is discharged into the sealed container through a bearing muffler attached to the cylinder. .

In Patent Document 1, an intermediate partition plate interposed between two cylinders is divided into two along the axial direction to form a partition plate space in which the two intermediate partition plates communicate with each other in the sealed container. Patent Document 1 discloses a technology that can cope with an increase in capacity by discharging a gas refrigerant compressed in a cylinder chamber into a bearing muffler chamber and a partition plate space of an intermediate partition plate divided into two.

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 sealed container, it is necessary to secure a discharge flow path that connects the partition plate space and the sealed container. In the technique of Patent Document 1, the discharge gas refrigerant is merged into one discharge flow path from the partition plate discharge space and the bearing muffler chamber and guided to the bearing muffler.

In order to improve the compression performance of the compressor, it is required to increase the flow path area of the discharge flow path for discharging the gas refrigerant from the partition plate discharge space. However, if the discharge path area of the gas refrigerant from the partition plate discharge space is increased, the thickness of the partition plate is partially reduced. If it does so, there exists a possibility that the rigidity of a partition plate may fall and the reliability as a compressor may be impaired.

Also, if the thickness of the partition plate is increased in order to prevent a decrease in the rigidity of the partition plate, the distance between the main bearing and the sub-bearing increases. If it does so, it will become easy to bend a rotating shaft, and there exists a possibility that the reliability as a compressor may be impaired after all.

Therefore, the present invention provides a hermetic seal that can secure a sufficient flow channel area of the discharge flow channel for discharging the gas refrigerant from the partition plate discharge space, while suppressing a decrease in rigidity of the partition plate and improving compression performance and reliability. A mold compressor and a refrigeration cycle apparatus including the hermetic compressor are provided.

In order to achieve the above object, a hermetic compressor of the present embodiment includes a hermetic container, and an electric motor unit and a compression mechanism unit that are housed in the hermetic container and connected via a rotating shaft, The compression mechanism section includes a first muffler, a main bearing, a first cylinder having a first cylinder chamber, a first partition plate, which form a first muffler chamber provided in order along the rotation axis. A second partition plate that forms a partition plate space with the first partition plate, a second cylinder having a second cylinder chamber, a secondary bearing, and a second muffler that forms a second muffler chamber are provided. The compression mechanism section is provided in the main bearing, and discharges the working fluid compressed in the first cylinder chamber into the first muffler chamber; and the first bearing discharge mechanism. Provided in the partition plate and compressed in the first cylinder chamber. A first partition plate discharge valve mechanism that discharges the working fluid into the partition plate space, and a working fluid that is provided in the auxiliary bearing and compressed in the second cylinder chamber is discharged into the second muffler chamber. A second partition plate that is provided with the sub-bearing and the second partition plate, and discharges the working fluid compressed in the second cylinder chamber to the partition plate space. A discharge valve mechanism; and a merging passage that joins the working fluid in the second muffler chamber and the working fluid in the partition plate space to lead to the first muffler chamber, the merging passage in the partition plate space The dimension in the direction orthogonal to the axis of the rotation axis of the connection flow path connected to is larger than the dimension along the axial direction of the rotation axis of the connection flow path.

The cross-sectional shape of the connection flow path of the hermetic compressor according to the present embodiment is preferably a square shape.

The hermetic compressor of the present embodiment includes an independent partition plate fluid passage that guides the working fluid discharged to the partition plate space to the first muffler chamber, and the partition plate fluid passage is formed from the junction passage. Is preferably provided at a position near the discharge port of the first partition plate discharge valve mechanism.

In addition, the hermetic compressor of the present embodiment preferably includes an independent muffler chamber fluid passage that guides the working fluid discharged to the second muffler chamber to the first muffler chamber.

In the hermetic compressor of the present embodiment, 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 from the second cylinder chamber to the first cylinder chamber. The discharge flow rate is preferably larger than the discharge flow rate discharged to the second muffler chamber.

Further, in the hermetic compressor of the present embodiment, the flow passage area of the connection flow passage is larger than the flow passage area of the confluence passage on the second muffler chamber side.

To achieve the above object, the refrigeration cycle apparatus of the present embodiment includes the hermetic compressor, a radiator connected to the hermetic compressor, an expansion device connected to the radiator, and the expansion. And a heat absorber connected between the device and the hermetic compressor.

The longitudinal cross-sectional view of the hermetic compressor by 1st Embodiment, and the refrigerating-cycle block diagram of a refrigerating-cycle apparatus. (A) is a top view of the 1st partition plate by the same embodiment, (B) is explanatory drawing which shows the flow of the refrigerant | coolant of a compression mechanism part. The figure which shows the cross section of the connection channel | path of the partition plate by the same embodiment. (A) is a top view of the 1st partition plate by 2nd Embodiment, (B) is a top view of a 2nd partition plate, (C) is explanatory drawing which shows the flow of the refrigerant | coolant of a compression mechanism part.

Hereinafter, embodiments for carrying out the invention will be described.

(First embodiment)
The present embodiment will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view of a hermetic compressor 1 according to a first embodiment and a refrigeration cycle configuration diagram of a refrigeration cycle apparatus R that is an air conditioner, for example.
As shown in FIG. 1, a hermetic compressor 1 (hereinafter simply referred to as “compressor 1”) is connected to a refrigeration cycle apparatus R.

A refrigerant pipe P is connected to the compressor 1. A condenser 2 that is a radiator, an expansion valve (expansion device) 3, an evaporator 4 that is a heat absorber, and an accumulator 5 are sequentially connected to the refrigerant pipe P. Further, the refrigerant pipe P is branched into two from the accumulator 5 and connected to the side portion of the compressor 1. The compressor 1, the condenser 2, the expansion valve 3, the evaporator 4, the accumulator 5, and the refrigerant pipe P constitute a refrigeration cycle of the refrigeration cycle apparatus R.

Next, the compressor 1 will be described.

The compressor 1 includes a sealed container 10. An electric motor unit 11 is accommodated on the upper side in the sealed container 10, and a compression mechanism unit 12 is accommodated on the lower side. The electric motor unit 11 and the compression mechanism unit 12 are connected via a rotating shaft 13. Lubricating oil is stored in the inner bottom portion of the sealed container 10. The remaining part (other part) of the internal space of the sealed container 10 is filled with a high-pressure gas refrigerant that is a working fluid compressed by the compression mechanism unit 12.

A discharge pipe 1 a is provided on the upper surface of the sealed container 10. A refrigerant pipe P communicating with the condenser 2 is connected to the discharge pipe 1a. Further, two

suction pipes

1 b and 1 b are provided on the lower peripheral wall of the sealed container 10. The

suction pipes

1b and 1b communicate with the accumulator 5.

The electric motor unit 11 has a rotor (rotor) 15 fixed by being fitted to the rotary shaft 13, and an inner peripheral surface facing the outer peripheral surface of the rotor 15 with a narrow gap. And a stator (stator) 16 that is fixed by being fitted to the inner peripheral wall.

The rotary shaft 13 is provided with two columnar eccentric portions a and b projecting toward the outer peripheral side of the rotary shaft 13 (direction orthogonal to the shaft center). These eccentric portions a and b are provided at positions spaced apart by a predetermined dimension along the axial direction of the rotating shaft 13 and displaced by 180 ° along the rotating direction of the rotating shaft 13. These eccentric portions a and b are provided eccentric to the axis center of the rotating shaft 13. A portion between the eccentric portions a and b in the rotating shaft 13 is referred to as an intermediate shaft portion c.

The compression mechanism unit 12 includes a main bearing 17, a first cylinder 18, an intermediate partition plate 20, a second cylinder 22, and a sub-bearing 23 provided in order along the axial direction of the rotary shaft 13. I have. Each of the main bearing 17 and the sub bearing 23 has a boss portion that rotatably supports the rotating shaft 13.

The flange part of the main bearing 17 is attached with a first muffler 25 which is a hollow case surrounding the periphery. A first muffler chamber 25 a is formed inside the first muffler 25. Further, the first muffler 25 is provided with a plurality of communication holes that allow the inside of the muffler chamber 25a and the space in the sealed container 10 to communicate with each other.

A second muffler 26 that is a hollow case surrounding the periphery is attached to the flange portion of the auxiliary bearing 23. Inside the second muffler 26, a second muffler chamber 26a is formed.

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

The upper end portion of the inner diameter hole of the first cylinder 18 is closed by the main bearing 17, and the lower end side of the inner diameter hole of the first cylinder 18 is closed by the first partition plate 20 a of the intermediate partition plate 20. A first cylinder chamber 18A is formed by the inner diameter hole of the first cylinder 18 closed by the main bearing 17 and the first partition plate 20a.
The upper end side of the inner diameter hole of the second cylinder 22 is closed by the second partition plate 20 b of the intermediate partition plate 20, and the lower end side of the inner diameter hole of the second cylinder 22 is closed by the auxiliary bearing 23. A second cylinder chamber 22 </ b> A is formed by the inner diameter hole of the second cylinder 22 closed by the second partition plate 20 b and the auxiliary bearing 23.

Rotating shaft 13 is inserted through first cylinder chamber 18A and second cylinder chamber 22A. One eccentric portion a formed on the rotating shaft 13 is located in the first cylinder chamber 18A, and the other eccentric portion b formed on the rotating shaft 13 is located in the second cylinder chamber 22A.

The roller 27 is fitted to one eccentric part a, and the roller 28 is fitted to the other eccentric part b. The roller 27 rolls while a part of the outer peripheral wall is in contact with the inner peripheral wall of the first cylinder chamber 18A as the rotary shaft 13 rotates. The roller 28 rolls while a part of the outer peripheral wall is in contact with the inner peripheral wall of the second cylinder chamber 22A as the rotary shaft 13 rotates.

A blade (not shown) is slidably provided in each of the first cylinder chamber 18A and the second cylinder chamber 22A. The tips of the blades are in contact with the outer peripheral walls of the

rollers

27 and 28 by a force acting from an elastic body such as a spring.

A part of the outer peripheral wall of the roller 27 is in contact with a part of the inner peripheral wall of the first cylinder chamber 18A, and the tip of the blade is elastically in contact with the outer peripheral wall of the roller 27, whereby the inside of the first cylinder chamber 18A is The roller 27 is partitioned into two spaces whose volume varies as the roller 27 rolls. A part of the outer peripheral wall of the roller 28 is in contact with a part of the inner peripheral wall of the second cylinder chamber 22A, and the tip of the blade is elastically in contact with the outer peripheral wall of the roller 28, whereby the inside of the second cylinder chamber 22A is The roller 28 is partitioned into two spaces whose volume varies as the roller 28 rolls.

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

FIG. 2A is a plan view of the first partition plate 20a, and FIG. 2B is an explanatory view showing the flow of refrigerant in the compression mechanism section 12. FIG.

In FIG. 2A, a mark with cross hatching in a circle is a bolt hole d. The first cylinder 18, the divided intermediate partition plate 20, the second cylinder 22, and the auxiliary bearing 23 are connected to the main bearing. A bolt that is fastened to 17 is inserted.

As schematically shown in FIGS. 2A and 2B in addition to FIG. 1, a discharge port for discharging the gas refrigerant compressed by the eccentric motion of the roller 27 from the first cylinder chamber 18 </ b> A is provided in the flange portion of the main bearing 17. There is provided a first bearing discharge valve mechanism 30 including 30a, a reed valve 30b that opens and closes the discharge port 30a with a predetermined pressure, and a valve pressing plate 30c that regulates the maximum opening of the reed valve 30b. Yes.

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

The flange portion of the sub-bearing 23 has a discharge port 31a for discharging the gas refrigerant compressed by the eccentric motion of the roller 28 from the second cylinder chamber 22A, and a reed valve 31b for opening and closing the discharge port 31a with a predetermined pressure. A second bearing discharge valve mechanism 31 including a valve pressing plate 31c that regulates the maximum opening of the reed valve 31b is provided.

When the reed valve 31b of the second bearing discharge valve mechanism 31 is opened and the discharge port 31a is opened and closed, the second cylinder chamber 22A and the muffler chamber 26a in the second bearing muffler 26 attached to the sub bearing 23 are provided. And communicate with each other.

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

The first partition plate 20a includes a discharge port 33a for discharging the gas refrigerant compressed by the eccentric motion of the roller 27 from the first cylinder chamber 18A, and a reed valve 33b for opening and closing the discharge port 33a with a predetermined pressure. A first partition plate discharge valve mechanism 33 provided with a valve pressing plate 33c that regulates the maximum opening of the reed valve 33b is provided.

The second partition plate 20b includes a discharge port 34a for discharging the gas refrigerant compressed by the eccentric motion of the roller 28 from the second cylinder chamber 22A, and a reed valve 34b for opening and closing the discharge port 34a with a predetermined pressure. A second partition plate discharge valve mechanism 34 including a valve pressing plate 34c that restricts the maximum opening of the reed 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 inner diameters of the

discharge ports

30a, 31a, 33a and 34a are set so as to increase, and the spring constants of the

reed valves

30b, 31b, 33b and 34b are set.

The compressed gas refrigerant discharged from the first partition plate discharge valve mechanism 33 and the second partition plate discharge valve mechanism 34 is guided along a later-described flow path shown in FIGS. It has come to be.

The first partition plate 20a and the second partition plate 20b include a partition plate space 35 that receives the compressed gas refrigerant discharged from the first partition plate discharge valve mechanism 33 and the second partition plate discharge valve mechanism 34. Is partitioned. The partition plate space 35 has a partition plate discharge space 35a and a connection flow path 35b. A first partition plate discharge valve mechanism 33 and a second partition plate discharge valve mechanism 34 are provided in the partition plate discharge space 35a. The connection flow path 35b is a long space continuously extending along the plane of the partition plate 20 from the partition plate discharge space 35a. Moreover, the height of the partition plate discharge space 35a is larger than the height of the connection flow path 35b.

FIG. 3 is an AA cross section of FIG. 2, and is an enlarged cross sectional view along the axial direction of the rotary shaft 13 of the connection flow path 35b formed in the intermediate partition plate 20. FIG.

For example, the first partition plate 20a and the second partition plate 20b each have a thickness of 10 mm. That is, the first partition plate 20a and the second partition plate 20b form an intermediate partition plate 20 having a thickness of 20 mm. The connection flow path 35b is formed by a groove having a depth of 5 mm and a width of 12 mm provided in the first partition plate 20a and the second partition plate 20b. That is, the connection flow path 35b has a rectangular shape in which the axial length (height) t of the rotary shaft 13 is 10 mm and the length (width) h in the direction orthogonal to the axial direction of the rotary shaft 13 is 12 mm. The width h dimension of the connection channel 35b is formed larger than the height t dimension.

In addition, a passage S that guides the gas refrigerant discharged from the second cylinder chamber 22A to the second muffler chamber 26a in the second muffler 26 to the first muffler chamber 25a in the first muffler 25 is provided as a subsidiary. The bearing 23, the second cylinder 22, the second partition plate 20 b, the first partition plate 20 a, the first cylinder 18, and the flange portion of the main bearing 17 are provided on the respective members. This passage S is a merging passage S that communicates with the connection flow path 35b in the second partition plate 20b and the first partition plate 20a. Regarding the discharge flow rate of the gas refrigerant discharged from the second cylinder chamber 22A, the discharge flow rate of the gas refrigerant discharged from the second cylinder chamber 22A to the partition plate space 35 is the second flow rate from the second cylinder chamber 22A. More than the discharge flow rate of the gas refrigerant discharged into the muffler chamber 26a. Therefore, the flow passage area of the connection flow passage 35b provided in the intermediate partition plate 20 is set to be larger than the flow passage area of the merge passage S on the second muffler chamber 26a side. Therefore, the gas refrigerant in the partition plate space 35 easily flows into the merge passage S.

In such a configuration, when the electric motor unit 11 is energized, the rotary shaft 13 rotates and the compression mechanism unit 12 is driven. As a result, the suction chamber, which is one space in the first cylinder chamber 18A partitioned by the blades, and the suction chamber, which is one space in the second cylinder chamber 22A, become negative pressure, and the gas that is the working fluid The refrigerant flows into each suction chamber.

Rollers

27 and 28 provided with a phase difference of 180 ° roll as the rotary shaft 13 rotates. The gas refrigerant flowing into the first cylinder chamber 18A and the gas refrigerant flowing into the second cylinder chamber 22A are compressed by gradually reducing the volume of the discharge chamber, which is the other space partitioned by the blades. Is done.

When compressed to a predetermined pressure, the reed valve 30b of the first bearing discharge valve mechanism 30 is opened and the discharge port 30a is released. The compressed gas refrigerant is discharged from the first cylinder chamber 18A to the first muffler chamber 25a of the first muffler 25.

At the same time, the reed valve 33b of the first partition plate discharge valve mechanism 33 is opened and the discharge port 33a is released. The compressed gas refrigerant is discharged into the partition plate space 35 from the first cylinder chamber 18A.

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

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

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

The gas refrigerant discharged from the first partition plate discharge valve mechanism 33 and the second partition plate discharge valve mechanism 34 into the partition plate space 35 passes through the connection flow path 35b and flows into the first cylinder 18 and the main bearing 17. It is guided to the first muffler chamber 25a of the first muffler 25 through a merge passage S provided continuously in the flange portion.

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 sealed container 10 Is released inside.

The inside of the sealed container 10 is filled with high-temperature and high-pressure gas refrigerant, and flows into the refrigerant pipe P connected to the discharge pipe 1a and led to the condenser 2. The refrigerant is condensed and liquefied by the condenser 2, decompressed by the expansion valve 3, and evaporated by the evaporator 4. The ambient air is cooled by the evaporation of the refrigerant, and the refrigeration cycle apparatus R exhibits the refrigeration (cooling) capability.

The refrigerant exiting the evaporator 4 is separated into gas and liquid by the accumulator 5 and is introduced into the first cylinder chamber 18A and the second cylinder chamber 22A through the

suction pipes

1b and 1b of the compressor 1 and 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 to the partition plate space 35, and compressed in the second cylinder chamber 22A, is supplied to the second cylinder chamber 22A. 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 through the common flow path S.

By making the cross section of the connection flow path 35b of the partition plate space 35 into a square shape and making its width h dimension larger than the height t dimension, the flow area of the connection flow path 35b without increasing the thickness of the intermediate partition plate 20 Can be secured greatly. Therefore, the distance between the main bearing 17 and the auxiliary bearing 23 is prevented from increasing, and the reliability as a compressor is increased.

Also, the flow resistance of the connection flow path 39a is reduced, and the pressure loss is improved.

Further, by adjusting the size of the inner diameter of the

discharge ports

30a, 31a, 33a and 34a, the spring constant of the

reed valves

30b, 31b, 33b and 34c, etc., the discharge of the gas refrigerant discharged into the partition plate space 35 The flow rate was made larger than the discharge flow rate of the gas refrigerant discharged into the second muffler chamber 26a. Therefore, noise is reduced by the sound insulation effect of the intermediate partition plate 20.

(Second Embodiment)
A second embodiment will be described with reference to FIG. Elements that are the same as or similar to those in the first embodiment are assigned the same reference numerals, and redundant descriptions are omitted as appropriate.

FIG. 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. FIG. 4C is a diagram showing the refrigerant flow in the compression mechanism section 12.

The compressor 1A of the second embodiment includes a partition plate fluid passage 36 and a muffler chamber fluid passage 38 at positions different from the joining passage S in addition to the joining passage S.

The partition plate fluid passage 36 allows the gas refrigerant discharged from the first cylinder chamber 18 </ b> A and the second cylinder chamber 22 </ b> A to the partition plate space 35 to pass through the first cylinder 18 and the flange portion of the main bearing 17. The muffler 25 is led to the muffler chamber 25a. The partition plate fluid passage 36 is provided in each member of the first cylinder 18 and the main bearing 17.

The muffler chamber fluid passage 38 allows the gas refrigerant discharged from the second cylinder chamber 22A to the second muffler chamber 26a of the second muffler 26 to pass through the auxiliary bearing 23, the second cylinder 22, and the second partition plate 20b. The first partition plate 20 a, the first cylinder 18, and the flange portion of the main bearing 17 are led to the first muffler chamber 25 a of the first muffler 25. The muffler chamber fluid passage 38 is provided in each member of the auxiliary bearing 23, the second cylinder 22, the second partition plate 20 b, the first partition plate 20 a, the first cylinder 18, and the main bearing 17.

Thus, by forming the partition plate fluid passage 36 and the muffler chamber fluid passage 38, the discharge passage area for discharging the gas refrigerant compressed in the first cylinder chamber 18A and the second cylinder chamber 22A is expanded. Therefore, pressure loss is reduced and compression efficiency is 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 junction passage S.

Thus, the pressure loss of the gas refrigerant discharged from the partition plate fluid passage 36 and unnecessary heat exchange are reduced, and the highly efficient compressor 1 can be provided.

According to the hermetic compressor 1 of at least one embodiment described above, the flow resistance of the connection flow path 35b is reduced by making the width h dimension larger than the height t dimension, and the flow of the connection flow path 35b is reduced. A road area can be secured large without thickening the intermediate partition plate 20, and a highly efficient and reliable compressor can be provided.

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 spaces are different. The height of each space may be the same, but by reducing the height of the connection flow path 35b, the partition without partitioning the amount of gas refrigerant discharged to the partition plate space 35. The rigidity of the plate can be increased.

Further, a space having an intermediate height may be provided between the partition plate discharge space 35a and the connection flow path 35b with respect to the partition plate discharge space 35a and the connection flow path 35b. In this case, the partition plate fluid passage 36 may communicate with the connection channel 35b having the smallest space height, or may communicate with the intermediate height space. Thereby, the discharge amount of the gas refrigerant discharged to the partition plate space 35 can be increased.

Although several 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 forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. This embodiment and its modifications are included in the invention described in the claims and their equivalents, as well as included in the scope and gist of the invention.

DESCRIPTION OF SYMBOLS 1 ... Sealed compressor (compressor), 2 ... Condenser (radiator), 3 ... Expansion valve (expansion device), 4 ... Evaporator (heat absorber), 10 ... Sealed container, 13 ... Rotating shaft, 11 ... Electric motor part, 12 ... compression mechanism part, 17 ... main bearing, 18A ... first cylinder chamber, 18 ... first cylinder, 20a ... first partition plate, 20b ... second partition plate, 22A ... second Cylinder chamber, 22 ... second cylinder, 23 ... sub-bearing, 25 ... first muffler, 25a ... first muffler chamber, 26 ... second muffler, 26a ... second muffler chamber, 30 ... first Discharge valve mechanism, 31 ... second discharge valve mechanism, 33 ... first partition plate discharge valve mechanism, 33a ... discharge port (of the first partition plate discharge valve mechanism), 34 ... second partition plate discharge valve mechanism 35 ... Partition space, 35b ... Connection flow path, 36 ... Partition fluid passage, 38 ... Muffler chamber fluid communication , S ... merge path, h ... connecting channel width, t ... connecting channel height, R ... refrigeration cycle

Claims

A sealed container;
An electric motor unit and a compression mechanism unit housed in the sealed container and coupled via a rotating shaft;
The compression mechanism section includes a first muffler, a main bearing, a first cylinder having a first cylinder chamber, a first partition plate, which form a first muffler chamber provided in order along the rotation axis. A second partition plate that forms a partition plate space with the first partition plate, a second cylinder having a second cylinder chamber, a secondary bearing, and a second muffler that forms a second muffler chamber are provided. ,
The compression mechanism is
A first bearing discharge valve mechanism that is provided in the main bearing and discharges the working fluid compressed in the first cylinder chamber to the first muffler chamber;
A first partition plate discharge valve mechanism that is provided on the first partition plate and discharges the working fluid compressed in the first cylinder chamber to the partition plate space;
A second bearing discharge valve mechanism provided in the sub-bearing for discharging the working fluid compressed in the second cylinder chamber into the second muffler chamber;
A second partition plate discharge valve mechanism that is provided in the second partition plate and discharges the working fluid compressed in the second cylinder chamber to the partition plate space;
A merging passage that joins the working fluid of the second muffler chamber and the working fluid of the partition plate space to lead to the first muffler chamber,
The hermetic compressor, wherein a dimension of a connection channel that is connected to the junction passage in the partition space in a direction perpendicular to the axis of the rotation axis is larger than a dimension of the connection channel along the axis of the rotation axis.
The hermetic compressor according to claim 1, wherein a cross-sectional shape of the connection channel is a quadrangle.
An independent partition plate fluid passage that guides the working fluid discharged into the partition space to the first muffler chamber;
The hermetic compressor according to claim 1, wherein the partition plate fluid passage is provided at a position closer to a discharge port of the first partition plate discharge valve mechanism than the merging passage.
The hermetic compressor according to any one of claims 1 to 3, further comprising an independent muffler chamber fluid passage that guides the working fluid discharged to the second muffler chamber to the first muffler chamber.
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 discharge flow rate discharged from the second cylinder chamber to the second muffler chamber. The hermetic compressor according to any one of claims 1 to 4, wherein the hermetic compressor is larger than the hermetic compressor.
The hermetic compressor according to claim 5, wherein a flow passage area of the connection flow passage is larger than a flow passage area on the second muffler chamber side of the merging passage.
A hermetic compressor according to any one of claims 1 to 6,
A radiator connected to the hermetic compressor;
An expansion device connected to the radiator;
A refrigeration cycle apparatus comprising: a heat absorber connected between the expansion device and the hermetic compressor.