KR100425720B1 - Muffler of compressor - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor silencer. The present invention relates to a compressor silencer provided at the suction side or the discharge side of a compressor to attenuate noise generated during operation. An extension cylinder in which both the leading side and the outlet side of the narrow channel flow tube communicate with each other is formed as an elliptic rotor formed by rotating the elliptic curve 360 ° about the long axis of the two-dimensional ellipse, While the introduction end of the outlet side narrow flow channel is disposed at one focal position, a resonance ball or sound absorbing material is mounted at the other focal position, and a sound absorbing material is attached to the inner circumferential surface of the expansion tube, thereby forming the narrow side flow channel. The noise frequencies of each band transmitted through are all attenuated in the sound absorbing material of the expansion barrel through the resonance hole at the second focal point, or Sikkim according to attenuate the noise of all frequencies to ensure that the attenuation by the sound-absorbing material attached to the second focus position can be significantly reduced the overall noise of the compressor. In addition, this can simplify the flow path of the suction silencer, thereby minimizing the suction loss of the refrigerant gas, thereby improving the compressor performance.

Description

Silencer for Compressor {MUFFLER OF COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor silencer, and more particularly, to a compressor silencer capable of reducing noise in all frequency bands.

In general, a silencer applied to the compressor is installed on the suction side or the discharge side of the fluid to attenuate the suction noise generated when the fluid is sucked or to attenuate the discharge noise generated when the fluid is discharged. A silencer is called a suction silencer and a silencer installed on the discharge side is called a discharge silencer.

The suction silencer and the discharge silencer attenuate the periodic pulsation phenomenon caused by the repeated suction and discharge of the fluid so that the fluid suctioned or discharged into the compressed space can be smoothly introduced and discharged, and also generated during the suction and discharge of the fluid. The noise of the valve and the flow noise of the fluid are blocked from being transmitted to the outside of the compression mechanism to reduce the compressor noise. Hereinafter, a look at the suction silencer applied to the reciprocating compressor.

1 is a longitudinal sectional view showing an example of a conventional hermetic reciprocating compressor.

As shown in the drawing, a conventional reciprocating compressor includes a casing 1 filled with a predetermined amount of oil, an electric mechanism part installed at an inner lower side of the casing 1 to generate a driving force by a power supplied from the outside, and It is installed on the upper portion of the transmission mechanism is configured to include a compression mechanism for receiving and compressing the gas by receiving the driving force of the transmission.

The compression mechanism is a frame (2) fixed to the inside of the casing (1) in the transverse direction, the cylinder (3) fixed to one side of the frame (2), and the transmission mechanism through the center of the frame (2) A drive shaft 5 press-fitted to the rotor 4B, a connecting rod 6 coupled to an upper eccentric portion of the drive shaft 5 to convert rotational motion into a reciprocating motion, and coupled to the connecting rod 6 And a piston (7) reciprocating in the cylinder (3), a valve assembly (8) coupled to the cylinder (3) to limit suction and discharge of refrigerant gas, and a valve assembly (8) thereof. And a head cover 9 having a constant discharge space DS, a suction silencer 10 coupled to one side of the head cover 9 so as to communicate with the suction side of the valve assembly 8, and the valve assembly 8 And a discharge silencer DM mounted to the cylinder 3 so as to communicate with the discharge side.

As shown in FIG. 2, the suction silencer 10 has an inlet 11 directly communicating with the refrigerant suction pipe SP passing through the casing 1 or inside the casing 1, and the inlet 11 thereof. The outlet port 12 communicates with the suction side of the valve assembly 8 to guide the refrigerant gas introduced through the into the compression space of the cylinder 3, and between the inlet port 11 and the outlet port 12 The first partition plate 13 and the second partition plate 14, which divide the internal volume into the first, second, and third expansion spaces S1, S2, and S3, and the first partition plate 13, A first narrow channel passage 15 through which the first expansion space S1 and the second expansion space S2 communicate vertically, and the first partition plate 13 and the second partition plate 14; The second narrow passage flow path 16 through which all of the second expansion space S2 is directly communicated with the outlet port 12, and formed through the middle circumferential wall of the second narrow passage flow path 16, thereby expanding the third expansion space. Helmholtz Resrvo with Space (S3) It consists of a resonance hole 17 for communicating the third expansion space (S3) to the outlet (12) to achieve ir).

In the figure, 4A is a stator, 18 is an oil drain hole, C is a support spring, O is an oil feeder, and SP is a compressor suction pipe.

The conventional hermetic reciprocating compressor configured as described above operates as follows.

First, when the power is applied to the electric drive unit and the rotor 4B is rotated by the interaction force between the stator 4A and the rotor 4B, the drive shaft 5 rotates together with the rotor 4B. The rotational motion of the drive shaft 5 is converted into a linear reciprocating motion by the connecting rod 6 coupled to the eccentric portion of the drive shaft 5 and transmitted to the piston 7, and the piston 7 The reciprocating motion of the inside of the cylinder 3 causes the refrigerant gas to be sucked and compressed and discharged. The pulsation pressure or noise generated in this process flows in a direction opposite to the flow direction of the refrigerant gas and is attenuated by the suction silencer 10.

Looking at this in more detail as follows.

That is, in the intake stroke in which the piston 7 moves from the top dead center to the bottom dead center, the refrigerant gas filled in the second expansion space S2 opens the intake valve (unsigned) and opens the cylinder 3 through the outlet port 12. At the same time, the new refrigerant gas is introduced into the second expansion space S2 through the introduction port 11, the first expansion space S1, and the first narrow flow channel 15. On the other hand, in the compression stroke in which the piston 7 moves from the bottom dead center to the top dead center, the inlet valve (unsigned) is closed and the discharge valve (unsigned) is opened, and the compressed gas is discharged through the discharge valve 9. Is discharged to the discharge space DS.

At this time, the repetitive pulsation pressure is continuously generated in the suction silencer 10 and the discharge cover 9 in the process of repeating the suction and discharge of the refrigerant gas, the pulsation pressure has a phase difference and each of the suction silencer 10 It propagates through the flow path, but is gradually attenuated and extinguished through the second narrow passage channel 16, the second expansion space S2, the first narrow passage channel 15, and the first expansion space S1. On the sphere 11 side, the pulsation pressure was largely dissipated and the refrigerant gas smoothly flowed in.

On the other hand, the noise generated when the refrigerant gas is inhaled is converted into thermal energy by a diffusion and dissipation through the narrow channel passages 15 and 16 and the expansion spaces S1 and S2 and attenuated at the same time. Helmholtz's effect in the Helmholtz resonance consisting of the resonance hole 17 of the tube 16 and the third expansion space S3 reduced the overall noise.

However, in the conventional inhalation silencer as described above, the size, length or volume of each narrow channel 15, 16, resonance hole 17 and expansion spaces S1, S2, S3 as described above are changed. By attenuating only the specific frequency noise of the band that is greatly uncomfortable using, there is a problem that the overall compressor noise still exist because it has no effect on the noise other than the specific frequency.

In particular, in the case of the suction silencer, if the diameter of each narrow channel 15 (16) is expanded to more than a certain limit in consideration of the suction amount of the refrigerant gas, the noise becomes louder, so it should always be manufactured within a certain limit. Compressor performance is limited, but in consideration of this, instead of increasing the diameter of the narrow channel 15 and 16, the flow path may be complicated, but this also limits the compressor performance by increasing the suction loss of the refrigerant gas. There was this.

SUMMARY OF THE INVENTION The present invention has been made in view of the problems of the conventional suction silencer, and an object of the present invention is to provide a silencer for attenuating the noise frequency of the entire band generated when the compressor is driven.

In addition, an object of the present invention is to provide a compressor silencer that can improve the compressor performance by preventing noise from increasing even when the diameter of the narrow channel is increased.

1 is a longitudinal sectional view showing an example of a conventional reciprocating compressor.

Figure 2 is a longitudinal sectional view showing an example of a suction silencer applied to a conventional reciprocating compressor.

Figure 3 is a perspective view showing an example of the silencer for the present invention compressor.

Figure 4 is a longitudinal cross-sectional view showing the effect of the silencer for the present invention compressor.

5 is a perspective view showing a modification of the silencer for the present invention compressor.

Figure 6 is a perspective view showing another modification of the silencer for the present invention compressor.

Figure 7 is a longitudinal cross-sectional view showing an example of the utilization of the silencer for the present invention compressor.

Figure 8a and Figure 8b is a schematic view for explaining the manufacturing principle of the silencer for the present invention. Figure 9 is a graph showing the transmission loss of the present invention elliptical silencer and conventional pipe-type silencer. ** For the main part of the figure Explanation of Codes **

110,210,310: first narrow channel Euro 120,220,320: second narrow channel

130,230,330: expansion tube 131: blocking plate

133,134,231,232,331,332,333: Sound absorbing material 132: Resonance ball

321,322: Inlet pipe S1, S2: First and second resonance space

F1, F2: First and second focus positions

In order to achieve the object of the present invention, in the compressor silencer provided on the suction side or discharge side of the compressor to attenuate the noise generated during operation, the inlet side and the outlet side of the inlet side narrow passage tube based on the suction direction of the fluid A silencer for a compressor is provided, wherein an expansion cylinder in which all the introduction sides of the side narrow flow channel communicate with each other is formed of an elliptic rotation body formed by rotating an elliptic curve 360 ° about a long axis of a two-dimensional ellipse.

Hereinafter, the compressor silencer according to the present invention will be described in detail based on the embodiment shown in the accompanying drawings.

Figure 3 is a perspective view showing an example of the silencer for the present invention, Figure 4 is a longitudinal cross-sectional view showing the operation and effect of the silencer for the present invention.

As shown in FIG. 2, the suction silencer according to the present invention includes a first narrow flow channel 110 connected to a refrigerant suction pipe (not shown) extending from the system, and a refrigerant sucked through the first narrow channel flow path 110. A second narrow flow channel 120 communicating with the suction side of the valve assembly (not shown) to guide the gas into the compression space of the cylinder (not shown), and an outlet side and a second side of the first narrow flow channel 110. The expansion channel 130 is formed between the inlet side of the narrow channel flow pipe 120 to communicate the two narrow channel pipes 110, 120.

The expansion cylinder 130 is formed of an elliptic rotating body having a three-dimensional shape by rotating the elliptic curve 360 ° about the long axis of the two-dimensional plane ellipse.

The blocking plate 131 for dividing the expansion cylinder 130 into the first resonance space (S1) and the second resonance space (S2) is disposed in the transverse direction at positions where both the focal points of the elliptic rotor are positioned, The outlet end of the second narrow flow channel 110 is disposed at the first focal position F1 among the above-described both focal points, and the inlet end of the first narrow flow channel 120 excludes the second focal position F2. It is preferable to be formed in the corner part of the 1st resonance space S1 which is the furthest position from the 1st focal position F1.

The blocking plate 131 is formed of a sound absorbing material, and the inlet end of the second narrow flow channel 120 is penetrated through the first focusing position F1 as described above, whereas the blocking plate 131 is formed at the second focusing position F2. Resonance ball 132 is formed so that the sound wave transmitted to the first resonance space (S1) through the second narrow channel flow path 120 is reflected to the inner circumferential surface and transmitted to the second resonance space (S2).

As shown in FIG. 3, the inlet end of the second narrow channel tube 120 is preferably coupled to the top of the blocking plate 131 at the same height.

The first sound absorbing material 133 is attached to the inner circumferential surface of the second resonance space S2 of the expansion cylinder 130, and the hemispherical second sound absorbing material 134 is disposed at the first focal position F1 as described above. It penetrates through the second narrow channel 120 and protrudes toward the second resonance space (S2). In addition, a sound absorbing material (not shown) may be attached to the inner circumferential surface of the first resonance space S1.

In the drawings, the same reference numerals are given to the same parts as in the prior art.

Inhalation silencer according to the present invention as described above has the following effects.

That is, during the suction stroke of the compressor, the refrigerant gas passes through the first narrow passage channel 110 through the first resonance space S1 and the second narrow channel tube 120 of the expansion cylinder 130. After the suction to the compressor (not shown) is repeated in the compression stroke of the compressor is repeated a series of processes to be discharged to the system.

At this time, when the suction stroke and the compression stroke of the compressor is opened and closed the suction valve (not shown) disposed at the outlet end of the second narrow flow path pipe 120, the valve sound is generated while the 'reverse pressure is formed when the suction valve is closed Pulsation noise is generated between the refrigerant gas flowing back by the gradient and the refrigerant gas sucked, and is transmitted to the inlet end of the second narrow channel 120 with various frequency bands as described above. Noise is reflected on the inner circumferential surface of the first resonance space (S1) of the expansion barrel 130 is transmitted to the second resonance space (S2) through the resonance hole 132, while the resonance in the second resonance space (S2) It is attenuated by the first sound absorbing material 133 and the second sound absorbing material 134 provided at the first focal position F1 on the inner circumferential surface.

To describe this in more detail, the characteristics of the ellipse are as follows.

First, as shown in FIG. 8A, a two-dimensional plane ellipse is a trace of a point where the sum of distances from two different focal points is the same, and the length of the long axis is a and the length of the short axis is b. It can be expressed by the coordinate of F = ± (a ² -b ² ) ^1/3 , 0). In addition, the two-dimensional plane ellipse is an arbitrary straight line from one focal point (convenience, first focus) (-F) is reflected from the elliptic curve to become a straight line passing through the other focal point (conventional, second focus) (F). . That is, the straight line connecting the elliptical point at the first focal point -F and the second focal point F has the same incident angle and reflection angle at the tangent at the point.

The two-dimensional characteristics of the ellipse are the same in the three-dimensional space, that is, as shown in Figure 8b is rotated 360 ° around the long axis of the ellipse to form an ellipse rotating body, the elliptic rotating body is cut perpendicular to the long axis In this case, the cross-section is always a circle so that any straight line from the first focal point (-F) of the long axis reflects from which of the three-dimensional curved surface the reflected straight line always passes the second focal point (F).

Based on this, referring to the first embodiment of the present invention, the sound wave (noise) transmitted from the first focal position F1 to the first resonance space S1 is always the first regardless of the frequency of the sound wave. After hitting and reflecting on the inner circumferential surface of the resonance space S1, all are transmitted to the second resonance space S2 through the resonance hole 132 located at the second focal position F2, and in each of the second resonance spaces S2, Sound waves of frequency are resonated and attenuated. In this case, when the first flaw material 133 is provided on the inner circumferential surface of the second resonance space S2, each sound wave transmitted to the resonance hole 132 impinges on the inner circumferential surface of the second resonance space S2, and the first Absorbed and attenuated by the flaw material 134, some of the sound waves are reflected back to the first focusing position (F1), but the second hemispherical second sound absorbing material 134 is provided at the first focusing position (F1) again It will be attenuated once.

Here, when another sound absorbing material (not shown) is mounted on the inner circumferential surface of the first resonant space (S1), the sound wave is a second narrow channel flow path by the sound absorbing material (not shown) of the first resonant space (S1) The sound wave transmitted through the inlet end of 120 may be partially attenuated before being transmitted to the second resonance space S2.

On the other hand, when there is a modification according to the present invention is as follows.

That is, in the above-described example, the expansion cylinder 130 is partitioned into the first resonance space S1 and the second resonance space S2 by the blocking plate 131, and the second expansion position F2 is defined in the second focal position F2. A resonance hole 132 for communicating the first resonance space S1 and the second resonance space S2 is provided, but in the present modified example, the first sound absorbing material having the spherical first sound absorbing material ( The sound wave transmitted from the first focusing position is reflected by the inner peripheral surface of the expansion barrel 230 and collected at the second focusing position so as to be absorbed and attenuated by the first sound absorbing material 231. At this time, when the sound absorbing material (not shown) is attached to the entire inner circumferential surface of the expansion barrel 230, the sound wave transmitted to the expansion cylinder 230 through the inlet end of the second narrow flow path tube 220 is the expansion cylinder 230 After being partially attenuated while being reflected on the inner circumferential surface of the first sound absorbing material 231 at the second focal position, the attenuation is once again attenuated.

Also in this case, it is preferable to mount the hemispherical second sound absorbing material 232 at the inlet end of the second narrow flow path tube 220. In the drawing, reference numeral 210 denotes a first narrow channel.

Another variation of the invention is as follows.

That is, the inlet end of the second narrow flow passage 320 inserted into the expansion cylinder 330 is bisected and the first introduction end 321 is disposed at the first focal position, and the second introduction end 322 is provided. Is arranged at the second focal position, and the hemispherical first sound absorbing material 331 and the second sound absorbing material 332 are respectively provided at the respective focal positions.

Here, the third sound absorbing material 333 may be attached to the inner circumferential surface of the expansion cylinder 330, and the length L1 of the first introduction end 321 and the length L2 of the second introduction end 322. It may be formed by different or different diameters. In the drawing, reference numeral 310 denotes a first narrow channel.

In this case, the sound waves transmitted through the first introduction end 321 and the second introduction end 322 are partially attenuated by the third sound absorbing material 333 provided on the inner circumferential surface of the expansion tube 330, and thus different introduction ends. 321 and 322 are reflected to each focus position where the second sound absorbing material 332 and the first sound absorbing material 331 provided at the respective focus positions are attenuated.

This series of suction silencers not only has the same effect when applied to the reciprocating compressor as well as other compressors as in the present embodiment, but can also have the same effect when the above principle is applied to the discharge silencer.

In particular, in the case of the suction silencer as shown in FIG. 7, if the suction silencer 100 of the present invention is mounted between the outlet side of the existing suction silencer 10 and the cylinder (not shown) of the compression mechanism, the existing suction silencer 10 ) Can be used to attenuate only the pulsation and the attenuation silencer 100 can be used to attenuate various noises, thereby simplifying the structure of the existing suction silencer 10, thereby reducing the diameter of the narrow channel of the existing suction silencer 10. It may be sufficiently large to facilitate the improvement of the compressor performance. For reference, FIG. 9 is a graph showing the transmission loss of the elliptical silencer of the present invention and the conventional pipe silencer. 'Negative pressure force ratio' at the inlet and outlet of the muffler physically decreases the sound pressure at the inlet as it exits through the silencer's resonance space and exits. The larger the transmission loss, the better the sound pressure attenuation effect of the silencer. Experimental results show that the elliptical silencer has an average 30 dB attenuation effect at about 3.0 kHz or less than the conventional pipe silencer as shown in FIG. It became.

Compressor silencer according to the present invention is an elliptic curve centered on the long axis of the two-dimensional ellipse is an expansion cylinder in which both the inlet side of the inlet narrow channel and the inlet side of the outlet narrow channel flows in communication with the suction direction of the fluid Is formed into an elliptic rotating body rotated by 360 °, and the inlet end of the outlet narrow channel is placed at either of the focal positions of the elliptic rotating bodies, while the resonance hole or sound absorbing material is located at the other focal position. By attaching the sound absorbing material to the inner peripheral surface of the expansion cylinder, the noise frequency of each band transmitted through the outlet side narrow channel is all attenuated in the sound absorbing material of the expansion cylinder through the resonance hole of the second focal position Or attenuated by the sound absorbing material mounted at its second focal point, thereby attenuating the noise at all frequencies, thereby significantly reducing the overall noise of the compressor. Can be reduced.

In addition, this can simplify the flow path of the suction silencer, thereby minimizing the suction loss of the refrigerant gas, thereby improving the compressor performance.

Claims (12)

In the compressor silencer provided on the suction side or discharge side of the compressor to attenuate the noise generated during operation, An elliptic rotator formed by rotating an elliptic curve 360 ° around the long axis of a two-dimensional ellipse in an extension tube in which both the inlet side of the inlet narrow channel and the inlet side of the outlet narrow channel flow in relation to the suction direction of the fluid. Silencer for the compressor, characterized in that formed by. The inlet end of the outlet narrowing channel is disposed at a first focal point of the ellipse, and the leading end of the inlet narrowing channel is disposed at a position other than the second focal point of the ellipse. Silencer for compressor. According to claim 2, wherein the blocking plate for dividing the expansion cylinder into the first resonance space and the second resonance space at the position between the two focal points of the ellipse is installed so as to be disposed transverse to the direction of travel of the outlet side narrow passage pipe, In the blocking plate in which the second focal point is located, a resonance hole is formed so that the sound waves transmitted to the first resonance space through the outlet side narrow passageway are reflected on the inner circumferential surface thereof and then transmitted to the second resonance space. Silencer for compressor. The compressor silencer according to claim 3, wherein a sound absorbing material is provided on an inner circumferential surface of the second resonance space. The compressor silencer according to claim 4, wherein a sound absorbing material is provided on an inner circumferential surface of the first resonance space. The compressor silencer according to claim 3, wherein a sound absorbing material is provided at the first focal position. The compressor silencer of claim 2, wherein a sound absorbing material is provided at the second focal position. The compressor silencer according to claim 7, wherein a sound absorbing material is added to the entire inner circumferential surface of the expansion tube and the introduction end of the outlet narrow channel. The compressor silencer according to claim 1, wherein each inlet end of the outlet-side narrow flow channel connected to the first focal point and the second focal point of the ellipse is disposed, and sound absorbing material is provided at each focal point. 10. The compressor silencer of claim 9, wherein a sound absorbing material is provided on an inner circumferential surface of the expansion cylinder. The silencer for a compressor according to claim 9, wherein the lengths of both outlet side narrow passages arranged at the respective focal points are different from each other. The silencer for a compressor according to claim 9, wherein the diameters of the introduction ends of both outlet side narrow passages arranged at the respective foci are different from each other.