KR20180104871A - Rotary compressor - Google Patents

Abstract

The present invention relates to a rotary compressor. The rotary compressor according to one aspect of the present invention comprises: a shell forming an interior space; a driving motor arranged in the interior space of the shell; and a compression tool portion receiving power of the driving motor for operation and compressing a refrigerant. The compression tool portion comprises: a cylinder forming a chamber for refrigerant compression; a roller compressing the refrigerant within the chamber; a bearing coupled to the cylinder, and provided with a discharging port through which the refrigerant compressed in the chamber passes; a muffler coupled to the bearing and having the refrigerant passed through the discharging port drawn thereto; and a refrigerant guide pipe connected to the muffler so as to be extended to surround the outer circumference of the muffler, and guiding the refrigerant drawn to the muffler to a bottom space of the driving motor.

Description

[0001]

The present invention relates to a rotary compressor.

Generally, a compressor is a mechanical device that receives power from an electric motor such as an electric motor or a turbine and compresses air, refrigerant or various other operating gases to increase the pressure. The compressor is used for a household appliance such as a refrigerator and an air conditioner, It is widely used throughout.

These compressors are broadly classified into reciprocating compressors, rotary compressors, and scroll compressors.

The reciprocating compressor is a compressor that compresses a refrigerant while linearly reciprocating the piston in the cylinder so as to form a compression space in which a working gas is sucked and discharged between a piston and a cylinder.

The rotary compressor is a compressor in which a compression space is formed between an eccentrically rotated roller and a cylinder and an operating gas is sucked and discharged, and the roller is eccentrically rotated along the inner wall of the cylinder to compress the refrigerant.

The scroll compressor is a compressor in which a compression space in which an operating gas is sucked and discharged is formed between an orbiting scroll and a fixed scroll, and the orbiting scroll rotates along the fixed scroll to compress the refrigerant.

On the other hand, Korean Patent Laid-Open Publication No. 10-2005-0062995 (published Jun. 27, 2005) discloses a rotary twin compressor discharge device.

The twin compressor disclosed in the prior art includes a hermetically sealed container, a compression mechanism section, and a transmission mechanism section.

The compression mechanism section includes an upper bearing, a first cylinder, a second cylinder, a lower bearing, and an intermediate plate.

A first silencer for reducing discharge noises is mounted on the upper portion of the upper bearing, and a second silencer is mounted on the lower portion of the lower bearing for reducing discharge noise.

However, in the case of the twin compressor of the prior art, since the muffler is attached to each bearing, the noise of some frequencies can be reduced, but noise of various frequencies generated in the compressor can not be reduced.

An object of the present invention is to provide a rotary compressor in which the noise reduction effect is improved.

Another object of the present invention is to provide a rotary compressor capable of forming a noise reduction structure by a simple structure.

According to an aspect of the present invention, there is provided a rotary compressor including: a shell defining an inner space; A drive motor disposed in an inner space of the shell; And a compression mechanism for compressing the refrigerant by receiving the power of the driving motor.

The compression mechanism includes: a cylinder defining a chamber for refrigerant compression; A roller for compressing the refrigerant in the chamber; A bearing coupled to the cylinder and having a discharge port through which the refrigerant compressed in the chamber passes; A muffler coupled to the bearing and through which the refrigerant having passed through the discharge port is introduced; And a refrigerant guide pipe connected to the muffler and extending to surround the outer periphery of the muffler and guiding the refrigerant introduced into the muffler to a space below the driving motor.

The refrigerant guide pipe may be arranged to surround the muffler in a spiral shape or arc shape from the outside of the muffler.

The inlet of the refrigerant guide tube may be welded to the chamber forming part in a state where the inlet of the refrigerant guide pipe penetrates through the chamber forming part and is drawn into the chamber forming part.

The outlet of the refrigerant guide tube may be bent upward at an angle.

The inner diameter of the refrigerant guide tube is formed to be larger than the inner diameter of the discharge port so that a frequency lower than the frequency reduced by the muffler can be reduced, and the length of the refrigerant guide tube may be longer than the length of the discharge port. have.

According to the proposed invention, since the refrigerant guide pipe serves as an additional resonator in addition to the conventional muffler, the frequency band to be reduced is increased, and the noise reduction effect is improved.

Further, according to the present invention, the resonator can be formed by designing the length and the inner diameter of the refrigerant guide tube without changing the structure of other parts in the compressor, and then connecting the same to the muffler. Therefore, there is an advantage that a resonator for noise reduction can be formed without changing the existing structure.

In particular, since the inner space of the shell serves as a volume portion, a resonator can be formed by coupling the refrigerant guide tube to the upper muffler. Therefore, there is an advantage that a resonator can be formed by a simple structure.

1 is a sectional view showing a configuration of a rotary compressor according to an embodiment of the present invention;
2 is a perspective view of a compression mechanism according to an embodiment of the present invention;
3 is a plan view of an upper muffler in a state where a refrigerant guide tube is connected according to an embodiment of the present invention.
FIG. 4 is a bottom view of an upper muffler in a state where a refrigerant guide pipe is connected according to an embodiment of the present invention. FIG.
5 is a side view of the refrigerant guide tube.
6 is a view for explaining the principle of reducing noise by the upper muffler and the refrigerant guide tube of the present invention.
7 is a graph comparing the degree of noise reduction according to the presence or absence of the refrigerant guide tube of the present invention.

Hereinafter, the rotary compressor of the present invention will be described in detail with reference to the drawings.

Hereinafter, the rotary compressor of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a sectional view showing a configuration of a rotary compressor according to an embodiment of the present invention, and FIG. 2 is a perspective view of a compression mechanism according to an embodiment of the present invention.

1 and 2, a rotary compressor 1 according to an embodiment of the present invention includes a shell 10 forming an internal space, an upper cap (not shown) coupled to the upper side of the shell 10, 11 and a lower cap 12 coupled to the lower side of the shell 10.

The shell 10 may be formed in a cylindrical shape, for example. The shell 10 may include an upper opening and a lower opening.

A part of the upper cap 11 is formed in a cylindrical shape and can be inserted into the shell 10 through the upper opening of the shell 10.

A part of the lower cap 12 is formed in a cylindrical shape and can be inserted into the shell 10 through a lower opening of the shell 10.

A suction pipe 13 is connected to the shell 10 and a discharge pipe 14 is connected to the upper cap 11. However, in the present invention, the connecting position of the suction pipe 13 and the discharge pipe 14 is not limited thereto.

The rotary compressor 1 may further include a driving motor 20 installed inside the shell 10 and a compression mechanism 30 connected to the driving motor 20 and compressing the refrigerant.

The driving motor 20 may include a stator 21 for generating a magnetic force by an applied power source and a rotor 22 disposed inside the stator 21.

The stator 21 may be fixed to the inner circumferential surface of the shell 10. A portion of the stator 21 may be spaced apart from the inner circumferential surface of the shell 10 so that the stator 21 can move up and down the oil in the shell 10 through the stator 21.

The rotor 22 may be rotated by an induced electromotive force generated through interaction with the stator 21 in a state where the rotor 22 is positioned in the stator 21.

The compression mechanism (30) can receive the rotational force of the rotor (22) and compress the refrigerant. The compression mechanism 30 may be configured to compress the refrigerant in a single chamber or to compress the refrigerant in the plurality of chambers.

In Fig. 1, a compression mechanism 30 capable of performing compression in two chambers is shown as an example.

The compression mechanism 30 may include a rotation shaft 32 connected to the rotor 22 to transmit a rotational force.

The rotary shaft 32 may extend in the vertical direction within the shell 10. An oil passage 322 for flowing the oil is formed in the rotary shaft 32. The oil passage 322 is formed to pass through the rotation shaft 32 vertically.

Further, although not shown, a branch passage for supplying oil to the chambers of the respective cylinders, which will be described later, may be branched from the oil passage 322 on the rotary shaft 32.

The compression mechanism (30) may include an upper compression unit and a lower compression unit.

The upper compression unit and the lower compression unit may be connected to the rotary shaft 32, respectively. When the compression mechanism unit 30 performs compression in a single chamber as described above, the compression mechanism unit 30 will include a single compression unit.

The upper compression unit may include an upper cylinder 42 forming an upper chamber 420 and an upper roller 35 located in the upper chamber 420 and connected to the rotary shaft 32.

The upper roller 35 is eccentrically coupled to the rotary shaft 32 and may be rotated with a constant eccentric locus according to the rotation of the rotary shaft 32.

An upper vane slot 422 is formed in the upper cylinder 42 and an upper vane 43 can be received in the upper vane slot 422. The upper vane 43 reciprocates within the upper vane slot 422 to partition the upper chamber 420 into a suction chamber and a compression chamber.

The upper cylinder 42 is formed with an upper refrigerant inlet 421 through which the refrigerant flows. The upper refrigerant inlet 421 may extend obliquely from the lower surface of the upper cylinder 42 toward the upper chamber 420, though not limited thereto.

The upper compression unit may further include a main bearing 52 positioned on the upper side of the upper cylinder 42.

The main bearing 52 is fixed to the inner circumferential surface of the shell 10 and covers the upper side of the upper chamber 420. The main bearing 52 may be positioned below the driving motor 20. A discharge port 521 through which the refrigerant compressed in the upper chamber 420 is discharged is formed in the main bearing 52.

The rotation shaft 32 passes through the main bearing 52 and is connected to the rotor 22. The main bearing 52 guides the rotation so that the rotation shaft 32 is not eccentric but rotates stably.

An upper muffler 62 may be seated on the upper side of the main bearing 52.

The upper muffler 62 can reduce the noise generated during the discharge of the refrigerant compressed in the upper chamber 420.

The rotary shaft 32 may pass through the upper muffler 62. The upper muffler 62 may have a through hole 625 through which the rotating shaft 32 passes.

The lower compression unit may include a lower cylinder 46 forming a lower chamber 460 and a lower roller 37 located in the lower chamber 460 and connected to the rotary shaft 32.

The lower roller 37 may be eccentrically coupled to the rotary shaft 32 and may be rotated with a constant eccentric locus according to the rotation of the rotary shaft 32.

The lower cylinder 46 may include a lower vane slot 462 and the lower vane slot 462 may receive the lower vane 47.

The lower vane 47 reciprocates within the lower vane slot 462 to partition the lower chamber 460 into a suction chamber and a compression chamber.

The lower cylinder 46 is formed with a lower refrigerant inlet port 461 through which the refrigerant flows. The lower refrigerant inlet port 461 may extend obliquely from the upper surface of the lower cylinder 46 toward the lower chamber 460, though not limited thereto.

In addition, the lower cylinder 46 may further include a lower refrigerant discharge port (not shown) through which the compressed refrigerant is discharged.

The lower compression unit may further include a sub bearing 54 positioned below the lower cylinder 46.

The sub bearing 54 can support the lower cylinder 46. The sub bearing 54 may cover the lower side of the lower chamber 460.

The rotary shaft 32 may pass through the sub bearing 54. Therefore, the sub bearing 54 guides the rotation so that the rotation shaft 32 is not eccentrically but stably rotated.

The sub bearing 54 is provided with a discharge port 541 through which the refrigerant compressed in the lower chamber 460 passes.

A lower muffler 64 may be coupled to the sub bearing 54. The lower muffler 64 can reduce the noise generated during the discharge of the refrigerant compressed in the lower chamber 460.

An oil opening 640 through which the oil passes may be formed at the center of the lower muffler 64. The oil passage 322 of the rotary shaft 32 can communicate with the oil opening 640. Accordingly, the oil stored in the shell 10 can be supplied to the oil passage 322 of the rotary shaft 32 through the oil opening 640.

The compression mechanism 30 may further include an intermediate plate 50 positioned between the upper cylinder 42 and the lower cylinder 46.

The intermediate plate 50 may cover the lower side of the upper chamber 420 and the upper side of the lower chamber 460. The intermediate plate 50 prevents the upper roller 35 and the lower roller 37 from directly rubbing against each other during the rotation of the rotary shaft 32.

The intermediate plate 50 may include a branching portion 502 for branching the refrigerant sucked through the suction pipe 13. The branch portion 502 may communicate with the upper refrigerant inlet port 421 and the lower refrigerant inlet port 461.

The rotation axis 32 is arranged to pass through the intermediate plate 50.

On the other hand, the refrigerant compressed in the lower chamber 460 is discharged to the inner space of the lower muffler 64.

The refrigerant discharged to the inner space of the lower muffler 64 flows through the sub bearing 54, the lower cylinder 46, the intermediate plate 50, the upper cylinder 42, and the main bearing 52, And flows into the inner space of the upper muffler 62.

To this end, refrigerant passage openings 542, 464, 506, and 508 are formed in the sub bearing 54, the lower cylinder 46, the intermediate plate 50, the upper cylinder 42, and the main bearing 52, 426, 522 may be provided.

The compression mechanism unit 30 may further include a refrigerant guide pipe 65 for discharging the refrigerant drawn into the upper muffler 62 to the outside of the upper muffler 62.

The refrigerant guide pipe 65 is disposed outside the upper muffler 62 so that the refrigerant discharged from the upper muffler 62 flows into the shell 10 after flowing a predetermined distance along the refrigerant guide pipe 65. [ To be discharged.

At this time, the refrigerant flowing along the refrigerant guide pipe 65 flows into the space between the outer side of the upper muffler 62 and the lower surface space 70 of the driving motor 20 (see A region in FIG. 1) ). ≪ / RTI >

The refrigerant guide pipe (65) may be disposed to extend along the outer circumference of the upper muffler (62).

For example, the refrigerant guide pipe 65 may surround a part of the periphery of the upper muffler 62 while being connected to the upper muffler 62. Therefore, part or all of the refrigerant guide pipe 65 may be arranged in a helical form or in an arc form. In this case, interference between the refrigerant guide pipe (65) and the drive motor (20) can be prevented.

The upper muffler 62 includes a seating plate 620 that is seated on the upper bearing 52 and a chamber forming portion 622 that extends upward from the seating plate 620 and forms a predetermined space therein, . ≪ / RTI >

The seating plate 620 may be provided with a fastening hole 621 through which the screw passes for fastening the screw to the upper bearing 52.

The chamber forming part 622 may be a multi-stage chamber forming part. For example, the chamber forming part 622 includes a first chamber forming part 623 protruding upward from the seating plate 620, a second chamber forming part 623 protruding upward from the first chamber forming part 623, (624). ≪ / RTI >

At this time, the outer circumferential length of the first chamber forming portion 623 is shorter than the outer circumferential length of the seating plate 620, and the outer circumferential length of the second chamber forming portion 624 is shorter than the length of the second chamber forming portion 624, Is shorter than the outer circumferential length of the forming portion 623.

The rotation axis 32 may pass through the second chamber forming part 624. Therefore, the through hole 625 may be formed in the second chamber forming portion 624.

The refrigerant guide pipe (65) may be connected to the chamber forming part (622).

Hereinafter, the structure of the refrigerant guide pipe 65 and the coupling relationship between the refrigerant guide pipe 65 and the upper muffler 62 will be described.

FIG. 3 is a plan view of an upper muffler in a state where a refrigerant guide tube is connected according to an embodiment of the present invention, and FIG. 4 is a bottom view of an upper muffler in a state where a refrigerant guide tube is connected according to an embodiment of the present invention And Fig. 5 is a side view of the refrigerant guide tube.

6 is a view for explaining the principle of reducing noise by the upper muffler and the refrigerant guide tube of the present invention.

3 to 6, the inlet 66 of the refrigerant guide pipe 65 may be connected to the first chamber forming portion 623 of the upper muffler 62.

For example, the inlet 66 of the refrigerant guide pipe 65 may pass through the first chamber forming part 623 in the horizontal direction. The inlet 66 of the refrigerant guide pipe 65 may be inserted into the inner space of the upper muffler 62 through the first chamber forming part 623.

The inlet 66 of the refrigerant guide pipe 65 is inserted between the first chamber forming portion 624 and the inlet 66 of the refrigerant guide pipe 65 in a state in which the inlet 66 of the refrigerant guide pipe 65 is drawn into the inner space of the upper muffler 62 A predetermined space 626 is formed.

The space 626 serves to reduce noise inside the upper muffler 62.

At this time, the width of the space 626 increases from the inlet 66 toward the inside of the refrigerant guide pipe 65, and the space 626 serves as an additional muffler.

That is, in the space 626, the narrowest portion of the resonator may serve as the neck, and the remaining portion may serve as the chamber portion.

The inlet 66 of the refrigerant guide pipe 65 may be coupled to the upper muffler 62 by welding while the inlet 66 of the refrigerant guide pipe 65 penetrates the upper muffler 62. [ have.

The refrigerant guide pipe 65 extends around the upper muffler 62 while the inlet 66 of the refrigerant guide pipe 65 is welded to the upper muffler 62.

Referring to FIG. 4, a line passing through the center of the inlet 66 of the refrigerant guide pipe 65 from the center of the upper muffler 62 may be referred to as a first virtual line A1. A line connecting the end of the outlet 67 of the refrigerant guide pipe 65 from the center of the upper muffler 62 may be referred to as a second imaginary line A2.

At this time, the angle? Formed by the first imaginary line A1 and the second imaginary line A2 is not limited but may be 225 degrees or more. This is to ensure the length of the refrigerant guide pipe (65).

Specifically, the internal space (volume V1) of the discharge port 521 of the upper bearing 52 and the upper muffler 62 serves as a first resonator.

A space 70 (volume V2) formed by the outer surface of the upper muffler 62 and the lower surface of the drive motor 20 in the refrigerant guide pipe 65 and the shell 10 is connected to the second resonator resonator.

The inner space of the upper muffler 62 and the inner space 70 of the shell 10 serve as the volume of the resonator and the discharge port 521 and the refrigerant guide pipe 65 serve as the neck of the resonator, It plays a role.

In the present invention, the first resonator and the second resonator are designed to have different frequency bands.

The length of the refrigerant guide pipe (65) may be longer than the length of the discharge port (521).

The inner diameter of the refrigerant guide pipe 65 may be larger than the inner diameter of the discharge port 521 so that the refrigerant in the upper muffler 62 flows smoothly along the refrigerant guide pipe 65.

In general, the frequency reduced by the resonator is reduced as the length of the neck portion is longer, the volume of the volume portion is larger, and the cross-sectional area (diameter) of the neck portion is smaller.

The inner diameter of the refrigerant guide pipe 65 is larger than the inner diameter of the discharge port 521 but the length of the refrigerant guide pipe 65 is longer than the length of the discharge port 521, The volume V2 of the internal space 70 of the shell is formed to be larger than the volume V1 of the internal space of the muffler 62. [

The value obtained by dividing the flow path cross-sectional area of the refrigerant guide pipe 65 by the length of the refrigerant guide pipe 65 is equal to a value obtained by dividing the flow path cross-sectional area of the discharge port 521 by the length of the discharge port 521 Can be largely designed.

Therefore, the frequency band of the noise reduced by the second resonator is smaller than the frequency band reduced by the first resonator.

In the present invention, the frequency band reduced by the second resonator may be determined by the length and the inner diameter of the refrigerant guide pipe (65).

According to the present invention, the resonator can be formed by designing the length and the inner diameter of the refrigerant guide pipe (65) and then connecting the refrigerant guide pipe (65) to the upper muffler (62) without changing the structure of other parts in the conventional compressor. Therefore, according to the present invention, a resonator for noise reduction can be formed without changing the existing structure.

Particularly, since the internal space of the shell serves as a volume portion, a resonator can be formed by coupling the refrigerant guide tube to the upper muffler. Therefore, there is an advantage that a resonator can be formed by a simple structure.

On the other hand, oil can be stored in the shell 10. The oil level of the oil stored in the shell 10 may vary during the conveyance of the compressor 1 or during the operation of the compressor 1.

The outlet (67) of the refrigerant guide pipe (65) may be bent upward so that the oil does not enter the refrigerant guide pipe (65) when the oil level of the oil changes. For example, at least a part of the outlet 67 of the refrigerant guide pipe 65 may be positioned higher than the first chamber forming part 623. Therefore, the outlet 67 of the refrigerant guide pipe 65 is positioned higher than the inlet 66.

As shown in FIG. 5, the refrigerant guide pipe 65 may extend to round at the same height, and the outlet 67 may be bent upward.

FIG. 7 is a graph comparing the degree of noise reduction according to the presence or absence of the refrigerant guide tube of the present invention.

Referring to FIG. 7, it can be seen that the degree of noise reduction (TL) in the low frequency band of 1 KHz or less is large when the refrigerant guide tube is present compared to the case where the refrigerant guide tube is not present.

This can be achieved by coupling the refrigerant guide pipe 65 having a length greater than the length of the discharge port 521 to the upper muffler 62, as described above.

10: shell 52: upper bearing
62: upper muffler 65: refrigerant guide tube
521: Discharge port

Claims (9)

A shell forming an inner space;
A drive motor disposed in an inner space of the shell; And
And a compression mechanism for compressing the refrigerant by being operated by receiving the power of the driving motor,
The compression mechanism includes: a cylinder defining a chamber for refrigerant compression;
A rotating shaft connected to the driving motor;
A roller positioned in the chamber and connected to the rotary shaft to compress the refrigerant in the chamber while rotating;
A bearing coupled to the cylinder and having a discharge port through which the refrigerant compressed in the chamber passes;
A muffler coupled to the bearing and through which the refrigerant having passed through the discharge port is introduced; And
And a refrigerant guide tube connected to the muffler and extending to surround an outer periphery of the muffler and guiding the refrigerant introduced into the muffler into a space below the driving motor. The method according to claim 1,
Wherein the refrigerant guide tube surrounds the muffler in a spiral shape or arc shape from the outside of the muffler. The method according to claim 1,
Wherein the muffler includes: a seating plate that is seated on the bearing;
And a chamber forming part extending upward from the seating plate and forming a space therein,
And an inlet of the refrigerant guide tube is coupled to the chamber forming portion. The method of claim 3,
Wherein the inlet of the refrigerant guide tube is welded to the chamber forming part while being drawn into the chamber forming part through the chamber forming part. 5. The method of claim 4,
And a space for noise reduction is formed between the inlet of the refrigerant guide tube and the inside of the chamber forming portion, which are drawn into the chamber forming portion. The method of claim 3,
The chamber forming part includes a first chamber forming part extending upward from the seating plate,
And a second chamber forming part extending upward in the first chamber forming part and having a circumferential length shorter than a circumferential length of the first chamber forming part,
And an inlet of the refrigerant guide tube is coupled to the first chamber forming portion. The method of claim 3,
And the outlet of the refrigerant guide tube is bent upward at a predetermined angle. 8. The method of claim 7,
And the outlet of the refrigerant guide tube is located higher than the inlet of the refrigerant guide tube. The method according to claim 1,
Wherein an inner diameter of the refrigerant guide tube is larger than an inner diameter of the discharge port,
Wherein a length of the refrigerant guide pipe is longer than a length of the discharge port.

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