WO2017073019A1

WO2017073019A1 - Rotary compressor

Info

Publication number: WO2017073019A1
Application number: PCT/JP2016/004503
Authority: WO
Inventors: 俊輔薬師寺; 小川　真
Original assignee: 三菱重工業株式会社
Priority date: 2015-10-27
Filing date: 2016-10-06
Publication date: 2017-05-04
Also published as: JP2017082632A; CN107614881B; EP3369932A4; EP3369932A1; EP3369932B1; JP6625864B2; CN107614881A

Abstract

Provided is a rotary compressor with which it is possible to reduce pulsation based on an acoustic inherent value of a two-layer structured muffler. This rotary compressor 10 is characterized in that: an upper muffler 50 has a first muffler 50A provided to the inner side, and a second muffler 50B provided to the outer side of the first muffler 50A and covering the first muffler 50A; the acoustic inherent value of the pre-specified frequency F is excited in the first muffler 50A; and the second muffler 50B absorbs sound waves of a frequency F that pass through the first muffler 50A. The gaps L2 between second discharge ports 56B1, 56B2, 56B3 of the second muffler 50B are 1/2 the gap L1 between first discharge ports 56A1 and 56A2 of the first muffler 50A, which is the most effective configuration for achieving the effects of the present invention.

Description

Rotary compressor

The present invention relates to a rotary compressor used in a refrigeration apparatus.

As shown in FIG. 7, the rotary compressor used in the refrigeration apparatus includes a cylinder 2 having a cylindrical inner wall surface and a piston provided eccentrically with respect to the center of the cylinder 2. And a rotor 3. 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 in FIG. 7 is a two-cylinder type compressor that includes two pairs of a cylinder 2 and a piston rotor 3 at the top and bottom.
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 compressed refrigerant is discharged from a discharge port (not shown) to the upper muffler 7A and the lower muffler 7B, and then reaches the sealed container 1. The rotary compressor separates the refrigerant from gas and liquid by the accumulator 8 and then sucks and compresses the refrigerant.

It is known that if the upper muffler has an inner and outer two-layer structure, the silencing effect can be improved by performing in two steps. Among them, in Patent Document 1, the upper cover (corresponding to a muffler) has a two-layer structure of an inner first cover and an outer second cover, and the lower cover has a single-layer structure of a third cover. The refrigerant discharged from the third cover is caused to flow into the upper second cover (outside the first cover). By doing so, the first cover and the third cover share the second cover, and in addition to the two-stage silencing by the flow path connecting the first cover to the second cover, the third cover is connected to the second cover. Two stages of noise reduction are realized by the flow path.

JP 2001-280241 A

The pulsation generated by the compression operation of the rotary compression mechanism consisting of the cylinder and piston rotor excites acoustic eigenvalues and structural eigenvalues while passing through the refrigerant discharge flow path, inducing vibration of the rotary compressor and causing noise. Become.
By making the muffler into a two-layer structure including Patent Document 1, it is possible to reduce the pulsation accompanying the compression operation, but the pulsation based on the acoustic eigenvalue of the muffler itself cannot be reduced, and this pulsation leaks from the muffler. End up.
Accordingly, an object of the present invention is to provide a rotary compressor that can reduce pulsation based on the acoustic eigenvalue of the muffler itself by using a muffler having a two-layer structure.

A rotary compressor according to the present invention is rotatable in 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 is supported and penetrates the rotary compression mechanism, an electric motor that rotates the main shaft around its central axis, and a refrigerant discharged from the rotary compression mechanism flows into the interior through a discharge port provided in the upper bearing. And a muffler to be stored in a sealed container.
The muffler of the rotary compressor of the present invention has a first muffler provided inside, and a second muffler that is outside the first muffler and covers the first muffler, and the first muffler is specified in advance. The acoustic characteristic value of the frequency F is excited, and the second muffler absorbs the sound wave of the frequency F that passes through the first muffler.

In the rotary compressor of the present invention, the first muffler includes a plurality of first discharge ports that discharge the refrigerant that has flowed into the second muffler, and the second muffler passes through the first discharge port to the inside. A plurality of second discharge ports are provided for discharging the flowed refrigerant into the sealed container, and the interval between the plurality of second discharge ports is based on ½ of the interval between the plurality of first discharge ports. Can be determined.

In the rotary compressor of the present invention, the interval between the first discharge ports can be set to the interval passing the side where the discharge port is not provided.
And the mutual space | interval of a 1st discharge outlet can be specified so that the frequency of an acoustic eigenvalue may be excited.

In the rotary compressor according to the present invention, the first muffler may have two first discharge ports, and the second muffler may have three or more second discharge ports.

In the rotary compressor of the present invention, the plurality of first discharge ports can be arranged on the same circumference.
A plurality of second discharge ports can be arranged on the same circumference.
Further, the plurality of first discharge ports and the plurality of second discharge ports can be arranged on the same circumference. In this case, at least one second discharge port can be adjacent to the first discharge port on both sides in the circumferential direction.

In the rotary compressor of the present invention, the first discharge port and the plurality of second discharge ports can be arranged radially inward from the discharge port.

In the rotary compressor of the present invention, the first muffler includes a single first discharge port that discharges the flowing refrigerant into the second muffler, and the second muffler passes through the first discharge port to the inside. A plurality of second discharge ports are provided to discharge the refrigerant flowing into the closed container, and the interval between the plurality of second discharge ports is ½ of the interval between the first discharge port and the discharge port. It can be determined by reference.

In the rotary compressor of the present invention, a plurality of second discharge ports can be arranged on the same circumference. Moreover, a single first discharge port and a plurality of second discharge ports can be arranged on the same circumference.

In the rotary compressor of the present invention, the position where the single or plural first discharge ports are provided overlaps with the position where the plural second discharge ports are provided in plan view of the first muffler and the second muffler. It is preferable that it has shifted | deviated without.

According to the rotary compressor of the present invention, the rotary compressor includes a two-layered muffler having a first muffler provided inside, and a second muffler that is outside the first muffler and covers the first muffler, It is assumed that one muffler is excited with an acoustic eigenvalue of a frequency F specified in advance, and that the second muffler absorbs a sound wave having a frequency F that passes through the first muffler, so that the muffler itself has an acoustic eigenvalue. The pulsation based can be reduced.

It is a longitudinal section showing a schematic structure of a rotary type compressor concerning an embodiment of the present invention. It is the elements on larger scale of FIG. The muffler of the rotary compressor of FIG. 1 is shown, (a) is a top view of a 1st muffler, (b) is a top view of a 2nd muffler. (A) is a top view which shows typically the muffler by which arrangement | positioning of the 1st discharge port of a 1st muffler and the 2nd discharge port of a 2nd muffler was shown, (b) is a figure which shows the principle of the muffling by this embodiment. It is. It is a schematic diagram which shows the other example of arrangement | positioning of the 1st discharge port of a 1st muffler, and the 2nd discharge port of a 2nd muffler. It is a schematic diagram which shows the other example of arrangement | positioning of the 1st discharge port of a 1st muffler, and the 2nd discharge port of a 2nd muffler. It is a longitudinal cross-sectional view which shows schematic structure of the conventional rotary compressor.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
The compressor 10 according to the present embodiment includes a rotary compression mechanism, and an upper muffler 50 to be described later has a two-layer structure, and the arrangement of refrigerant discharge ports in each layer is specified, whereby the upper muffler 50 is identified. Suppresses pulsation based on its own acoustic eigenvalue.
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 rotary compressor in which disk-shaped cylinders 20 A and 20 B provided in two upper and lower stages are accommodated in a cylindrical sealed container 11. is there. 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. As a result, spaces having a crescent-shaped opening cross section are formed between the cylinder inner wall surface 20S of the

cylinders

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

piston rotors

21A and 21B in plan view.
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 disc-shaped partition plate 24 is provided between the upper cylinder 20A and the lower cylinder 20B. The partition plate 24 partitions the space of the upper cylinder 20A and the space of 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 by an insertion groove formed extending in the radial direction of the

cylinders

20A and 20B so as to be able to advance and retreat in a direction toward and away from the

piston rotors

21A and 21B.
Further, the

cylinders

20A and 20B each have a discharge port (not shown) for discharging the refrigerant at a predetermined position, and the discharge port is provided with a reed valve (not shown). When the pressure of the compressed refrigerant reaches a predetermined value, the refrigerant is discharged to the outside of the

cylinders

20A and 20B by pushing the reed valve open.

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 upper bearing 29A and the lower bearing 29B are provided with a rotary compression mechanism interposed therebetween.
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, that is, are shifted in position. The

eccentric shaft portions

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

piston rotors

21A and 21B. Thereby, 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 in the

cylinders

20A and 20B. At this time, the blades described above are always pressed against the

piston rotors

21A and 21B while the tips thereof advance and retreat following the movements of 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 facing the outer peripheral portion of the rotor 37 is fixed to the inner peripheral surface of the sealed container 11.

As shown in FIGS. 1 and 2, 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 for supporting the main shaft 23 is formed around the axial center. In the upper bearing 29A, the outer peripheral surface of the base portion 291A is fixed to the inner peripheral surface of the sealed container 11 at a plurality of fixing points. This fixing is performed by, for example, welding or fastening with a bolt.
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 291A and the base 291B face each other. The upper bearing 29A supports the main shaft 23 between the cylinder 20A and the electric motor 36, and the lower bearing 29B supports the main shaft 23 at a portion protruding downward from the cylinder 20B.
The upper bearing 29A is provided with a discharge port 294A (see FIG. 3A) communicating with a discharge port (not shown) formed in the cylinder 20A, and the refrigerant passing through the cylinder 20A passes through the discharge port 294A. It is discharged into the upper muffler 50 described later. Similarly, the lower bearing 29B includes a discharge port (not shown) communicating with a discharge port (not shown) formed in the cylinder 20B, and the refrigerant passing through the cylinder 20B passes through the discharge port and passes through the lower muffler 60. It is discharged into the inside of.

Compressor 10 has upper muffler 50 mounted on upper bearing 29A and lower muffler 60 mounted on lower bearing 29B. When the refrigerant that has passed through the upper bearing 29A and the lower bearing 29B flows into the upper muffler 50 and the lower muffler 60, respectively, the pulsating component is removed. The refrigerant from which the pulsating component has been removed flows toward the upper side of the sealed container 11 through the first discharge port 56A formed in the upper muffler 50 and the second discharge port 56B formed in the lower muffler 60. Details of the upper muffler 50 will be described later.

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.

Prior to supplying the compressor 10 to the compressor 10, an accumulator 14 for gas-liquid separation of the refrigerant is fixed to the sealed 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 pass through the

openings

12A and 12B and are connected to the

suction ports

30A and 30B.

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 the gas phase is sucked into the

cylinders

20A and 20B from the

suction pipes

16A and 16B. The gas is supplied to compression chambers R1 and R2 that are internal spaces of the

cylinders

20A and 20B via the

ports

30A and 30B.
Then, by eccentrically rolling the

piston rotors

21A and 21B, the volumes of the compression chambers R1 and R2 are gradually reduced, and the refrigerant is compressed. The compressed refrigerant passes through the upper bearing 29A and the upper muffler 50 on the cylinder 20A side, and passes through the lower bearing 29B and the lower muffler 60 on the cylinder 20B side. It is discharged to the outside of the upper muffler 50 and the lower muffler 60 inside. After passing through the electric motor 36, the refrigerant is discharged to the piping constituting the refrigeration cycle via the discharge port 42 provided at the top.

Next, the upper muffler 50 that is a feature of the present embodiment will be described.
As shown in FIGS. 2 and 3, the upper muffler 50 is a two-layer structure including a first muffler 50A provided inside and a second muffler 50B outside the first muffler 50A and covering the first muffler 50A. Each has a structure and is fixed to the upper bearing 29A by a plurality of bolts B.
2 and 3, the first muffler 50A includes a flange 51A and a cup 52A that rises from the flange 51A. In the first muffler 50A, a flange 51A and a cup 52A are integrally formed by subjecting a flat metal plate such as an aluminum alloy plate to sheet metal processing.
The flange 51A is a portion provided to fix the upper muffler 50 to the upper bearing 29A, and is a flat member whose outer shape is circular in plan view. The flange 51A is abutted against the upper surface of the upper bearing 29A without any gap, and is fixed to the upper bearing 29A at a plurality of locations, in this embodiment, at five locations by a plurality of bolts B penetrating the flange 51A. In addition, the site | part to which the volt | bolt B of the flange 51A is fixed is provided in the aperture_diaphragm | restriction in which the side wall 54A of the cup 52A is dented toward the center of radial direction.

The cup 52A includes a hollow cylindrical side wall 54A and a top plate 55A that covers the opening at the upper end of the side wall 54A. The top plate 55A has a ring shape having an outer periphery and an inner periphery, the outer periphery is connected to the side wall 54A, and the inner periphery is abutted against the sleeve 292A of the upper bearing 29A.

Since the basic structure of the second muffler 50B is the same as that of the first muffler 50A, the same elements as those of the first muffler 50A are denoted by the reference numerals in which A is changed to B in FIGS. The description is omitted.

The upper muffler 50 passes through a refrigerant path through which compressed refrigerant discharged from

discharge ports

294A and 294B (FIG. 3A) provided in the upper bearing 29A passes in order of the first muffler 50A and the second muffler 50B. The air is discharged inside the sealed container 11 and outside the upper muffler 50 and the lower muffler 60. The discharge port 294B is for the compressed refrigerant once discharged to the lower muffler 60 to be discharged to the first muffler 50A through the lower bearing 29B and further through the upper bearing 29A.
In order to form this refrigerant path, as shown in FIG. 3, the first muffler 50A has two first discharge ports 56A1 and 56A2 formed through the front and back of the top plate 55A. 50B has three 2nd discharge outlets 56B1, 56B2, and 56B3 formed through the front and back of the top plate 55B. That is, the compressed refrigerant is the

discharge ports

294A and 294B of the upper bearing 29A, the internal space of the first muffler 50A, the first discharge ports 56A1 and 56A2 of the first muffler 50A, and the space between the second muffler 50B and the first muffler 50A. And the second outlets 56B1, 56B2, and 56B3 of the second muffler 50B pass in this order. The first discharge ports 56A1 and 56A2 and the second discharge ports 56B1, 56B2, and 56B3 are formed so as not to overlap with each other in plan view of the first muffler 50A and the second muffler 50B. The compressed refrigerant is prevented from passing directly through the second discharge port 56B1 from the discharge port 56A1.

The positions of the first discharge ports 56A1, 56A2 of the first muffler 50A and the second discharge ports 56B1, 56B2, 56B3 of the second muffler 50B are specified as follows.
In the first muffler 50A, the positions of the first outlets 56A1 and 56A2 are specified so that the acoustic eigenvalue of the frequency F to be silenced by the first muffler 50A is excited most strongly. Specifically, as shown in FIG. 4A, the acoustic eigenvalue is specified by the mutual interval L1 along the circumferential direction of the first discharge port 56A1 and the discharge port 56A2. By adopting the arrangement of the first discharge ports 56A1 and 56A2, the first muffler 50A can be actively expanded and contracted at the frequency F to be silenced, and pulsation energy can be converted into heat energy to suppress pulsation. The first discharge port 56A1 and the first discharge port 56A2 can have two mutual intervals along the circumferential direction, but the interval L1 here passes through the side where the

discharge ports

294A and 294B are not provided. And In this embodiment, the interval L1 is set to pass through the side where the

discharge ports

294A and 294B are not provided, but the

discharge ports

294A and 294B are provided depending on the interval between the discharge port 294A and the discharge port 294B. The direction passing the side can also be set as the interval L1.
The second muffler 50B absorbs the sound wave having the frequency F that passes through the first muffler 50A, and suppresses the transmission of pulsation to the outside of the second muffler 50B. Therefore, the second discharge ports 56B1, 56B2, and 56B3 of the second muffler 50B are arranged such that the interval L2 between adjacent discharge ports including the first discharge ports 56A1 and 56A2 is the interval between the first discharge ports 56A1 and 56A2. It is set to be 1/2 of L1. In FIG. 4A, for example, the interval L2 between the second discharge port 56B1 and the discharge port 56B3 is 1 / 2L1, the interval L2 between the discharge port 56B3 and the discharge port 56A2 is 1 / 2L1, and the second discharge port 56B2 and the first discharge port. The distance L2 between the outlets 56A1 is 1 / 2L1. As a result, the second muffler 50B resonates at half the wavelength of the sound wave that resonates with the first muffler 50A, and therefore can absorb the sound wave transmitted through the first muffler 50A.
The above is schematically shown in FIG. In addition, the interval L2 here is 1 / 2L1, which is the most preferable form, but the effect of the present invention can be enjoyed even if the interval L2 is slightly shifted from 1 / 2L2. That is, according to the present invention, the interval L2 can be determined with reference to 1 / 2L1.

[Operation and effect of compressor 10]
The operation and effect of the compressor 10 according to this embodiment will be described.
In the compressor 10, the upper muffler 50 has a two-layer structure of the first muffler 50A and the second muffler 50B, and the frequency F to be silenced by the first muffler 50A can be specified. Therefore, the pulsation of the targeted frequency can be reliably reduced.
In the rotary compressor, the pulsation caused by the refrigerant immediately after being discharged from the compression chamber has a strong frequency component determined by the dimensions of the compression chamber, and if the pulsation of this frequency can be reduced by this embodiment, the problem of noise caused by the pulsation is reduced. It can be almost solved. In particular, in the present embodiment, it is sufficient to adjust the mutual distance L1 between the first discharge ports 56A1 and 56A2 and the mutual distance L2 between the second discharge ports 56B1, 56B2, and 56B3, so that pulsation can be reduced at low cost.

In addition to the above, as long as the gist of the present invention is not deviated, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate.
In the above embodiment, the example in which the two first discharge ports 56A1 and 56A2 of the first muffler 50A are provided has been shown. However, as shown in FIG. 5A, the first muffler 50A has a single first discharge port. The present invention can also be applied when 56A1 is provided. In this case, based on the interval L1 or interval L3 between the discharge port 294A and the first discharge port 56A1 shown in FIG. 5A, as shown in FIG. 5B, the second discharge ports 56B1, 56B2, and 56B3. Determine the interval.
In the above-described embodiment, the discharge port 294A is not considered in specifying the interval L1 (interval L2), but this is because the interval between the discharge port 294A and the first discharge port 56A1 is extremely narrow, and the corresponding frequency is high. This is because it has been determined that there is no need for mute.
Further, as shown in FIGS. 6A and 6B, the present invention can also be applied when three or more first discharge ports 56A1, 56A2, and 56A3 are provided in the first muffler 50A. In this case, the second muffler 50B is provided with second discharge ports 56B1, 56B2, and 56B3.

In the above embodiment, the upper muffler 50 of the two-cylinder type rotary compressor is taken as an example, but the present invention can also be applied to the muffler of the one-cylinder type rotary compressor.

10 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

292A,

292B Sleeve

293A,

293B Receiving surface

294A,

294B Discharge port

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

Stator

40A, 40B Eccentric shaft portion 42 Discharge port 50 Upper muffler

50A First muffler

50B Second muffler

51A,

51B Flange

52A,

52B Cup

54A,

54B Side wall

55A, 55B Top plate 56A1, 56A2, 56A3 First discharge port 56B1, 56B2, 56B3 Second discharge port 60 Lower muff 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 in which the refrigerant discharged from the rotary compression mechanism flows into the inside through a discharge port provided in the upper bearing;
Is a rotary compressor accommodated in an airtight container,
The muffler is
A first muffler provided inside;
A second muffler on the outside of the first muffler and covering the first muffler,
In the first muffler, an acoustic eigenvalue of a frequency F specified in advance is excited,
The second muffler absorbs sound waves having a frequency F that passes through the first muffler.
A rotary compressor characterized by that.
The first muffler is
A plurality of first outlets for discharging the refrigerant that has flowed into the second muffler;
The second muffler is
A plurality of second discharge ports for discharging the refrigerant flowing into the inside through the first discharge port into the sealed container;
The interval between the plurality of second discharge ports is determined with reference to ½ of the interval between the plurality of first discharge ports.
The rotary compressor according to claim 1.
The rotary compressor according to claim 2, wherein the interval between the plurality of first discharge ports is an interval passing through a side where the discharge port is not provided.
The interval between the plurality of first discharge ports is specified so that the frequency of the acoustic eigenvalue is excited.
The rotary compressor of Claim 2 or Claim 3.
The first muffler includes two first discharge ports,
The second muffler includes three or more second discharge ports.
The rotary compressor according to any one of claims 2 to 4.
The plurality of first discharge ports are arranged on the same circumference,
The rotary compressor according to any one of claims 2 to 5.
The plurality of second discharge ports are arranged on the same circumference,
The rotary compressor according to any one of claims 2 to 6.
The plurality of first discharge ports and the plurality of second discharge ports are arranged on the same circumference,
The rotary compressor according to any one of claims 2 to 5.
At least one second outlet is adjacent to the first outlet on both sides in the circumferential direction;
The rotary compressor according to claim 8.
The rotary compression according to any one of claims 2 to 9, wherein the plurality of first discharge ports and the plurality of second discharge ports are disposed radially inward from the discharge port. Machine.
The first muffler is
A single first discharge port for discharging the refrigerant flowing into the second muffler;
The second muffler is
A plurality of second discharge ports for discharging the refrigerant flowing into the inside through the first discharge port into the sealed container;
The interval between the plurality of second discharge ports is determined with reference to 1/2 of the interval between the first discharge port and the discharge port.
The rotary compressor according to claim 1.
The plurality of second discharge ports are arranged on the same circumference,
The rotary compressor according to claim 11.
The first discharge port and the plurality of second discharge ports are arranged on the same circumference,
The rotary compressor according to claim 11.
The position where the single or plural first discharge ports are provided and the position where the plurality of second discharge ports are provided are shifted without overlapping in plan view of the first muffler and the second muffler. ,
The rotary compressor according to any one of claims 2 to 13.