WO2014141331A1

WO2014141331A1 - Rotary compressor

Info

Publication number: WO2014141331A1
Application number: PCT/JP2013/005732
Authority: WO
Inventors: 俊輔薬師寺
Original assignee: 三菱重工業株式会社
Priority date: 2013-03-12
Filing date: 2013-09-26
Publication date: 2014-09-18
Also published as: EP2942526B1; CN104937274B; JP2014173554A; EP2942526A1; CN104937274A; EP2942526A4; JP6161923B2

Abstract

A rotary compressor is provided with: an upper bearing (29A) and a lower bearing (29B), which are provided so as to sandwich a rotary compression mechanism; a main shaft (23) which is rotatably supported by both the upper bearing (29A) and the lower bearing (29B) and which penetrates through the rotary compression mechanism; an electric motor (36) which rotationally drives the main shaft (23) about the axis of the main shaft (23); and a muffler (50A) which is affixed to the upper bearing (29A) and into which a refrigerant discharged from the rotary compression mechanism flows. The muffler (50A) has formed thereon a rib (56) which extends along the radial line which connects the affixation point (F) at which the upper bearing (29A) is affixed to a hermetic container (11) and the center of the main shaft (23).

Description

Rotary compressor

The present invention relates to a rotary compressor that can suppress vibration of a shaft that rotates integrally with a rotor of a motor.

As shown in FIG. 6, the rotary compressor used in the refrigeration apparatus includes a cylinder 2 having a cylindrical inner wall surface and a piston rotor provided eccentrically with respect to the center of the cylinder 2. 3 is provided. The piston rotor 3 is provided on a main shaft 4 provided along the central axis of the cylinder 2. The main shaft 4 is provided so as to be rotatable around its central axis via an upper bearing 5A and a lower bearing 5B fixed to the cylinder 2. A rotor 6 A of a motor 6 is fixed to the main shaft 4. On the outer peripheral side of the rotor 6A, a stator 6B fixed to the inner peripheral surface of the hermetic container 1 is disposed. When the stator 6B is energized, the main shaft 4 is rotationally driven together with the rotor 6A, and the piston rotor 3 is Swivel inside.
The rotary compressor sucks the refrigerant into a compression chamber formed between the cylinder 2 and the piston rotor 3, and compresses the refrigerant by reducing the volume of the compression chamber by the rotation of the piston rotor 3. The rotary compressor gas-liquid separates the refrigerant by the accumulator 8 and then sucks and compresses the refrigerant.

In the rotary compressor, vibration is generated as the main shaft 4 rotates. For example, the vibration is transmitted to the sealed container 1 and the accumulator 8 in order, and noise may be generated. Therefore, various proposals have been made to reduce the vibration of the rotary compressor.
For example, Patent Document 1 proposes to reduce the vibration transmitted from the upper bearing to the sealed container by interposing a casting support member effective in vibration damping between the sealed container and the upper bearing. Yes.

Patent Documents

2 and 3 propose reducing vibration by forming ribs in the upper bearing.

JP-A-6-26478 JP 7-133781 A JP 59-182691 A

As described above, many proposals have been made so far, but since the cause of vibration is wide-ranging, the problem of vibration is not exhaustive. Increasing the rigidity of the components of the rotary compressor, particularly the upper and lower bearings that support the main shaft that is the main cause of vibration, is effective in reducing vibration. However, the rotary compressor, like many other devices and equipment, is required to be lighter. However, if the rigidity of the component is increased, the weight generally increases, so this requirement is satisfied. Is not easy.
Therefore, the present invention has been made based on such a problem, and an object thereof is to provide a rotary compressor capable of effectively reducing vibration while minimizing an increase in weight.

The rotary compressor of the present invention is rotatably supported by each of a rotary compression mechanism that compresses and discharges a supplied refrigerant, an upper bearing and a lower bearing provided across the rotary compression mechanism, and an upper bearing and a lower bearing. A main shaft that passes through the rotary compression mechanism, an electric motor that rotates the main shaft about its central axis, a muffler that is fixed to the upper bearing and into which refrigerant discharged from the rotary compression mechanism flows, and rotary compression A mechanism, an upper bearing, a lower bearing, a main shaft, an electric motor, and a sealed container that accommodates the muffler therein. At least one of the muffler and the upper bearing has a fixing point for fixing the upper bearing to the sealed container and the main shaft. A stiffening body extending along a radial line connecting the center is provided.
As will be described in detail later, in the upper bearing, a larger distortion occurs in the region from the fixed point toward the center of the main shaft than in other regions. Therefore, according to the present invention, a stiffening member is provided on at least one of the muffler and the upper bearing as a reinforcing member for the large strain region, thereby improving the rigidity of the main shaft and reducing the vibration of the main shaft. Moreover, since the present invention only needs to provide a stiffening body, an increase in the weight of the compressor can be minimized.
The stiffening body in the present invention includes all structural parts for increasing the moment of section of the muffler and the upper bearing and improving the rigidity against bending and torsion, and is typically a rib.

When providing a stiffening rib on the muffler, the stiffening rib can be formed integrally with the muffler, or the stiffening rib is formed separately from the muffler, and the separate stiffening rib is fixed to the muffler. You can also
When the stiffening body is formed integrally with the muffler, a refrigerant flow path (first refrigerant flow path) through which the refrigerant discharged from the inside of the muffler into the sealed container passes can be formed in the stiffening body. . This form has the advantage that the muffler can be integrally formed by sheet metal processing, including the stiffener and the refrigerant flow path.
Further, when the stiffening rib is formed separately from the muffler, the refrigerant flow path (second refrigerant flow path) through which the refrigerant discharged from the muffler into the sealed container passes is replaced with the stiffening body. Avoiding it can form a muffler. This configuration is effective when a stiffening body having a shape that cannot be formed integrally with the muffler is required.

According to the present invention, since only a stiffening body is provided on at least one of the muffler and the upper bearing corresponding to a large strain region, the rigidity with respect to the main shaft is improved while minimizing an increase in weight, The vibration of the main shaft can be reduced.

It is sectional drawing which shows the structure of the rotary compressor which concerns on 1st Embodiment of this invention. It is a longitudinal cross-sectional view which shows the vicinity of the rotary mechanism of the rotary compressor shown in FIG. It is a cross-sectional view which shows the vicinity of the rotary mechanism of the rotary compressor shown in FIG. The rotary compressor which concerns on 2nd Embodiment of this invention is shown, (a) is a cross-sectional view corresponding to FIG. 3, (b) is a longitudinal cross-sectional view corresponding to FIG. The rotary compressor which concerns on 3rd Embodiment of this invention is shown, (a) is a cross-sectional view corresponding to FIG. 3, (b) is a longitudinal cross-sectional view corresponding to FIG. It is sectional drawing which shows the structure of the conventional rotary compressor.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
[First Embodiment]
Hereinafter, the compressor 10 according to the first embodiment of the present invention will be described. The compressor 10 is characterized in that the vibration of the main shaft 23 is reduced by integrally forming a rib 56 corresponding to a stiffening body on a muffler 50A described later.
Hereinafter, the configuration of the compressor 10 will be described, and then the operation and effect of the compressor 10 will be described.

[Configuration of Compressor 10]
As shown in FIG. 1, the compressor 10 is a so-called two-cylinder type compressor in which disk-shaped cylinders 20 A and 20 B are provided in two upper and lower stages inside a cylindrical sealed container 11. A cylindrical cylinder inner wall surface 20S is formed in each of the

cylinders

20A and 20B.

Cylindrical piston rotors

21A and 21B each having an outer diameter smaller than the inner diameter of the cylinder inner wall surface 20S are arranged inside the

cylinders

20A and 20B. The

piston rotors

21A and 21B are inserted and fixed to the

eccentric shaft portions

40A and 40B of the main shaft 23 along the central axis of the sealed container 11, respectively. Thus, spaces R each having a crescent-shaped cross section are formed between the cylinder inner wall surfaces 20S of the

cylinders

20A and 20B and the outer peripheral surfaces of the

piston rotors

21A and 21B.
Here, the upper-stage piston rotor 21A and the lower-stage piston rotor 21B are provided so that their phases are different from each other by 180 °.
A disk-shaped partition plate 24 is provided between the upper and

lower cylinders

20A and 20B. The partition plate 24 partitions the space R in the upper cylinder 20A and the space R in the lower cylinder 20B into the compression chamber R1 and the compression chamber R2 without communicating with each other.

The upper and

lower cylinders

20A and 20B are provided with blades (not shown) for dividing the compression chambers R1 and R2 into two, respectively. The blade is held in an insertion groove formed extending in the radial direction of the

cylinders

20A and 20B so as to be able to advance and retract in a direction approaching and separating from the

piston rotors

21A and 21B.
Further, the

cylinders

20A and 20B are formed with discharge holes (not shown) for discharging the refrigerant at predetermined positions, and the discharge holes are provided with reed valves (not shown). When the pressure of the compressed refrigerant reaches a predetermined value, the reed valve is pushed open to discharge the refrigerant to the outside of the

cylinders

20A and 20B.

The main shaft 23 is rotatably supported around its central axis by an upper bearing 29A fixed to the cylinder 20A and a lower bearing 29B fixed to the cylinder 20B.
The main shaft 23 includes

eccentric shaft portions

40A and 40B that are offset in a direction orthogonal to the central axis of the main shaft 23. The

eccentric shaft portions

40A and 40B have outer diameters slightly smaller than the inner diameters of the

piston rotors

21A and 21B. Accordingly, when the main shaft 23 rotates, the

eccentric shaft portions

40A and 40B rotate around the central axis of the main shaft 23, and the upper and

lower piston rotors

21A and 21B roll eccentrically in the

cylinders

20A and 20B. At this time, the blade tip described above advances and retreats following the movement of the

piston rotors

21A and 21B, and is always pressed against the

piston rotors

21A and 21B.

The main shaft 23 protrudes and extends upward from the upper bearing 29A, and a rotor 37 of an electric motor 36 for rotating the main shaft 23 is integrally provided in the protruding portion. A stator 38 is fixed to the inner peripheral surface of the sealed container 11 so as to face the outer peripheral portion of the rotor 37.

2 and 3, the upper bearing 29A includes a base 291A and a sleeve 292A that rises vertically from the base 291A. The base portion 291A and the sleeve 292A are formed so that their axial centers coincide with each other, and a receiving surface 293A on which the main shaft 23 is supported is formed around the axial center. In the upper bearing 29A, the outer peripheral surface of the base 291A is fixed to the inner peripheral surface of the sealed container 11 at three fixing points F. Fixing is performed, for example, by welding or fastening with bolts.
The lower bearing 29B includes a base 291B and a sleeve 292B that rises vertically from the base 291B. The base 291 B and the sleeve 292 B are formed so that their axes coincide with each other, and a receiving surface 293 B for supporting the main shaft 23 is formed around the axis.
The upper bearing 29A and the lower bearing 29B are disposed so that the base portion 291A and the base portion 291B face each other, and the upper bearing 29A supports the main shaft 23 between the cylinder 20A and the electric motor 36. A portion of the main shaft 23 that protrudes downward from the cylinder 20B is supported by the lower bearing 29B.
The upper bearing 29A has a discharge hole (not shown) that communicates with a discharge hole formed in the cylinder 20A, and the refrigerant that has passed through the cylinder 20A is discharged into the later-described muffler 50A through the discharge hole. Is done. Similarly, the lower bearing 29B includes a discharge hole (not shown) that communicates with a discharge hole formed in the cylinder 20B, and the refrigerant that has passed through the cylinder 20B passes through the discharge hole to form a muffler 50B described later. It is discharged inside.

Compressor 10 has muffler 50A mounted on upper bearing 29A and muffler 50B mounted on lower bearing 29B. When the refrigerant that has passed through the upper bearing 29A and the lower bearing 29B flows into the muffler 50A and the muffler 50B, respectively, the pulsating component is removed. The refrigerant from which the pulsating component has been removed flows upward through the discharge path formed in the muffler 50A and the muffler 50B.

Openings

12A and 12B are formed on the side of the sealed container 11 at positions facing the outer peripheral surfaces of the

cylinders

20A and 20B. In the

cylinders

20A and 20B,

suction ports

30A and 30B are formed at positions facing the

openings

12A and 12B to communicate with a predetermined position on the cylinder inner wall surface 20S.

In the compressor 10, an accumulator 14 for gas-liquid separation of the refrigerant prior to supply to the compressor 10 is fixed to the hermetic container 11 via a stay 15.
The accumulator 14 is provided with

suction pipes

16A and 16B for letting the compressor 10 suck the refrigerant in the accumulator 14. The distal ends of the

suction pipes

16A and 16B are connected to the

suction ports

30A and 30B through the

openings

12A and 12B.

The compressor 10 takes in the refrigerant into the accumulator 14 from the suction port 14a of the accumulator 14, separates the refrigerant in the accumulator 14, and sucks the gas phase from the

suction pipes

16A and 16B into the

cylinders

20A and 20B. The gas is supplied to compression chambers R1 and R2 that are internal spaces of the

cylinders

20A and 20B through the

ports

30A and 30B.
Then, when the

piston rotors

21A and 21B roll eccentrically, the volumes of the compression chambers R1 and R2 gradually decrease and the refrigerant is compressed. The compressed refrigerant passes through the upper bearing 29A and the muffler 50A on the side of the cylinder 20A, and passes through the lower bearing 29B and the muffler 50B on the side of the cylinder 20B. It is discharged to the outside of the muffler 50A and the muffler 50B. The refrigerant passes through the electric motor 36 and is then discharged to the piping constituting the refrigeration cycle via the discharge port 42 provided in the upper part.

In this embodiment, the muffler 50A attached to the upper bearing 29A has a function of supporting the main shaft 23 in addition to the upper bearing 29A. The muffler 50 A has a support function for the main shaft 23, thereby reducing vibration of the main shaft 23. The muffler 50A has the following configuration in order to exhibit this function.

As shown in FIGS. 2 and 3, the muffler 50 A includes a flange 51, a cup 52 that rises from the flange 51, and a sleeve 53 that rises from the cup 52. In the muffler 50A, the flange 51, the cup 52, and the sleeve 53 can be integrally formed by subjecting a flat metal plate such as an aluminum alloy plate to sheet metal processing.
The flange 51 is a portion provided to fix the muffler 50A to the upper bearing 29A, and is a flat member having a circular outer shape. The flange 51 is abutted against the upper surface of the upper bearing 29 A without any gap, and is fixed to the upper bearing 29 A at three locations by bolts B penetrating the flange 51. The portion of the flange 51 where the bolt B is fixed corresponds to the diaphragm 59 in which the side wall 54 of the cup 52 is recessed toward the center in the radial direction.

The cup 52 includes a hollow cylindrical side wall 54 and a top plate 55 that covers an opening formed at the tip of the side wall 54.
The top plate 55 has a ring shape having an outer periphery and an inner periphery, and the outer peripheral side is connected to the side wall 54 and the inner peripheral side is connected to the sleeve 53.

The top plate 55 includes ribs 56 that are formed integrally with the top plate.
The rib 56 is provided along the radial direction of the top plate 55, and is formed in a U-shape by bending a part of the top plate 55 upward and turning it back. Therefore, the inside of the rib 56 communicates with the inside of the cup 52.
The ribs 56 are provided at three locations at intervals in the circumferential direction. When the end on the outer peripheral side of each rib 56 is extended outward in the radial direction, a fixed point F for fixing the upper bearing 29A to the sealed container 11 is reached. Further, when the inner peripheral end of each rib 56 is extended inward in the radial direction, the central axis of the main shaft 23 is reached. In other words, the rib 56 is provided corresponding to the line segment connecting the central axis of the main shaft 23 and the fixed point F (almost along the line segment).
The rib 56 is formed continuously from the top plate 55 to the lower end of the side wall 54, and is formed continuously from the top plate 55 to the upper end of the sleeve 53. That is, the rib 56 is provided from the lower end of the cup 52 to the upper end of the sleeve 53, and contributes to improving the rigidity of the cup 52 and the sleeve 53.

The sleeve 53 rises vertically from the inner periphery of the top plate 55, while its upper end is opened. An inner peripheral surface of the sleeve 53 is in contact with an outer peripheral surface of the sleeve 292A of the upper bearing 29A, and supports the sleeve 292A from the periphery. As described above, since the rib 56 is provided from the lower end to the upper end of the sleeve 53, the sleeve 53 has higher rigidity than the rib 56 is not provided.

[Operation and effect of compressor 10]
Next, the operation and effect of the compressor 10 according to the first embodiment will be described.
When the strain distribution of the compressor 10 during operation is confirmed by simulation, the upper bearing 29A has a larger strain in the radial direction from each fixed point F toward the central axis of the main shaft 23 than in other regions. It has been confirmed. This suggests that the large strain region has a greater degree of support for the main shaft 23 than the other regions. On the other hand, the compressor 10 supports the main shaft 23 via the upper bearing 29A with the muffler 50A provided with the ribs 56, and the rib 56 has three fixing points F of the upper bearing 29A and the center of the main shaft 23. It can be said that it is provided at the most effective position for vibration suppression. Therefore, the muffler 50A supports the main shaft 23 via the upper bearing 29A by the sleeve 53 while alleviating a large distortion in the region along the radial direction from the fixed point F to the central axis of the main shaft 23 that occurs in the upper bearing 29A. As a result, the swing of the main shaft 23 can be reduced. As a result, the compressor 10 can suppress the generation of noise due to vibration transmitted from the sealed container 11 to the accumulator 14 by increasing the rigidity of the muffler 50A with almost no increase in weight.
Further, since the muffler 50A supplements a part of the rigidity required for the upper bearing 29A, an effect of reducing the rigidity of the upper bearing 29A and reducing the weight of the upper bearing 29A can be expected.

In the muffler 50A, the inside of the rib 56 communicates with the inside of the muffler 50A. Therefore, the refrigerant that has passed through the cylinder 20A and has flowed into the muffler 50A flows through the refrigerant flow path (first refrigerant flow path) 61 inside the rib 56, and finally flows through the rib 56 of the sleeve 53. As a result, it is discharged from the upper end into the closed container 11.
Therefore, the refrigerant flowing into the muffler 50A is discharged in a smooth flow along the main shaft 23, and thus the pressure loss of the discharged refrigerant is small.
Further, since the refrigerant is discharged from the periphery of the main shaft 23, the space between the electric motor 36 and the stator 38 is separated in the radial direction, and the discharged refrigerant is less likely to vibrate the stator 38. This also allows the compressor 10 to reduce noise due to vibration.

[Modification of Compressor 10]
The compressor 10 according to the first embodiment includes the three ribs 56 corresponding to the three fixed points F, but the present invention is not limited to this, and is less than three, or four or more. It is allowed to provide a rib. For example, when there are three fixed points F and only the distortion in the region from the specific one fixed point F toward the inner periphery increases, ribs are provided only in the region corresponding to the fixed point F. This option is realistic.

The compressor 10 corresponds to an example in which each of the ribs 56 extends to a fixed point F, but the present invention is not limited to this. Even if the extension line of the rib is slightly deviated from the fixed point F, it is clear that the shaft rigidity of the main shaft 23 can be improved if even a part of the rib overlaps with a large strain region. The present invention defines that a part or all of the ribs overlap in a large strain area as being along a radial line segment connecting the fixed point F and the center, and a rib corresponding to this definition. Forming.

Next, in the compressor 10, the rib 56 is most preferably provided continuously from the lower end of the cup 52 to the upper end of the sleeve 53. However, this is only a preferable form. For example, ribs are provided on any part extending from the cup 52 to the sleeve 53, such as an example in which the sleeve 53 and the side wall 54 are provided only, or an example in which only the sleeve 53 and the top plate 55 are provided. Can be provided.

In the compressor 10, the sleeve 53 of the muffler 50 A is in contact with the upper bearing 29 A except for the gaps inside the ribs 56, but the present invention is not limited to this. For example, it is also possible to adopt a structure in which only the portion where the rib 56 is formed is supported in contact with the upper bearing 29A. In the present embodiment, since the rib 56 also serves as the refrigerant flow path 61 for discharging the refrigerant to the outside of the muffler 50A, it is not necessary to provide another discharge hole for discharging the refrigerant. Therefore, in order to increase the shaft rigidity of the main shaft 23, the space inside the ribs 56 is removed, and the upper shaft 29A is contacted.

[Second Embodiment]
In the first embodiment, the rib 56 is formed integrally with the muffler 50A. However, the compressor 110 of the second embodiment is manufactured by separately forming the rib 57 from the muffler 50A, as shown in FIG. Join to the muffler 50A. For joining, known means such as welding, brazing, and adhesion can be applied. In this case, since the inside of the rib 57 and the inside of the muffler 50A are partitioned by the top plate 55, the rib 57 does not function as a coolant passage. Therefore, as shown in FIG. 4, a discharge hole (second refrigerant flow path) 60 as a refrigerant passage is formed in the top plate 55. However, a gap corresponding to the discharge hole may be provided between the sleeve 53 and the sleeve 292A of the upper bearing 29A.

Since the compressor 110 includes the ribs 57, it is possible to suppress the generation of noise due to vibration transmitted from the sealed container 11 to the accumulator 14 as in the first embodiment.
When the rib 56 is formed integrally with the muffler 50A, the shape and size of the rib 56 may be restricted from the viewpoint of workability. For example, when the rib 56 has to be raised, integral molding may be difficult. However, the rib 57 manufactured as a separate body has almost no such restriction, and can accommodate various shapes and dimensions required.
In the form in which the rib and the top plate are manufactured separately, it is preferable that the rib extends to the flange 51 in order to improve rigidity.

[Third Embodiment]
In the first embodiment and the second embodiment, the ribs 56 and 57 are provided on the muffler 50A. However, the compressor 120 of the third embodiment is provided with the rib 58 on the upper bearing 29A as shown in FIG. The positions where the ribs 58 are provided are the same as those in the first embodiment and the second embodiment.
In addition, when the rib 58 of the upper bearing 29A interferes with the muffler 50A (not shown), processing for avoiding the interference is performed on the muffler 50A. Further, the muffler 50A is provided with a structure for discharging the refrigerant from the muffler 50A by providing the discharge hole 60 provided in the second embodiment.

Since the compressor 120 includes the rib 58, it is possible to suppress the generation of noise due to vibration transmitted from the sealed container 11 to the accumulator 14, as in the first embodiment. In particular, since the compressor 120 is provided with the rib 58 on the upper bearing 29A that is thicker than the muffler 50A, the degree to which the rigidity with respect to the main shaft is improved is increased, and vibration can be more effectively suppressed. Further, when the thickness of the upper bearing 29A is reduced in order to reduce the weight, it is effective to provide the ribs 58 in order to ensure the rigidity of the bearing itself.

As described above, the present invention has been described based on the embodiment. However, the configuration described in the above embodiment may be selected or changed to another configuration as long as it does not depart from the gist of the present invention.
For example, in the embodiment described above, a two-cylinder type compressor is taken as an example, but the present invention is not limited to this. For example, the present invention can be applied to a one-cylinder type compressor, a scroll compression mechanism, and a rotary The present invention can also be applied to a composite type compressor combined with a compression mechanism.
Moreover, in embodiment described above, the stiffening rib extended along the radial line segment which connects the fixing point which fixes an upper bearing to an airtight container, and the center of a main axis | shaft was shown. However, depending on the shape and deformation mode of the upper bearing, it is also effective to provide stiffening ribs along the circumferential direction when, for example, it is desired to suppress deformation of the bearing.

10, 110, 120 Compressor 11 Sealed

container

12A, 12B Opening 14 Accumulator 14a Suction port 15

Stay

16A,

16B Suction pipe

20A, 20B Cylinder 20S Cylinder

inner wall surface

21A, 21B Piston rotor 23 Main shaft 24 Partition plate 29A Upper bearing 29B Lower bearing 291A,

291B Base portion

292A,

292B Sleeve

293A,

293B Receiving surface

30A, 30B Suction port 36 Electric motor 37 Rotor 38

Stator

40A, 40B Eccentric shaft portion 42

Discharge port

50A, 50B Muffler 51 Flange 52 Cup 53 Sleeve 54 Side wall 55

Top plate

56 , 57, 58 Rib (stiffening body)
59 Restriction 60 Discharge hole (second refrigerant flow path)
61 Refrigerant flow path (first refrigerant flow path)
B Bolt F Fixed point R Space R1, R2 Compression chamber

Claims

A rotary compression mechanism for compressing and discharging the supplied refrigerant;
An upper bearing and a lower bearing provided across the rotary compression mechanism;
A main shaft that is rotatably supported by each of the upper bearing and the lower bearing and passes through the rotary compression mechanism;
An electric motor for rotating the main shaft around its central axis;
A muffler fixed to the upper bearing and into which the refrigerant discharged from the rotary compression mechanism flows;
A sealed container that houses the rotary compression mechanism, the upper bearing, the lower bearing, the main shaft, the electric motor, and the muffler;
With
At least one of the muffler and the upper bearing is provided with a stiffening body extending along a radial line segment connecting a fixing point for fixing the upper bearing to the sealed container and the center of the main shaft,
A rotary compressor characterized by that.
The stiffening body is provided on the muffler,
The rotary compressor according to claim 1.
The stiffening body is formed integrally with the muffler.
The rotary compressor according to claim 1 or 2.
The muffler is
The stiffening body formed integrally with the muffler;
A first refrigerant flow path formed in the stiffening body, through which the refrigerant discharged from the inside of the muffler to the inside of the sealed container passes,
The rotary compressor according to claim 1.
The muffler is
The stiffening rib formed separately from the muffler and fixed to the muffler;
A second refrigerant flow path through which the refrigerant discharged from the inside of the muffler passes into the sealed container.
The rotary compressor according to claim 1.
The inside of the rib 57 and the inside of the muffler are partitioned by a top plate,
The second refrigerant flow path is formed on the top plate.
The rotary compressor according to claim 5.
The stiffening body is provided on the upper bearing,
The rotary compressor according to claim 1.
The stiffener is a plurality of stiffener ribs;
The rotary compressor according to any one of claims 1 to 7.