KR20040007976A - Muffler of rotary compressor - Google Patents

Abstract

PURPOSE: A muffler of a rotary compressor is provided to reduce discharge of oil by improving structure of the muffler, and reduce noise generated during discharge of the compressor. CONSTITUTION: A muffler comprises a first chamber(304), a second chamber(305) and a third chamber(306) partitioned by three coupling parts(301) and a rotary shaft when the rotary shaft is inserted to a rotary shaft insertion port(303). The first chamber, the second chamber and the third chamber are connected with narrow channels formed by the rotary shaft and the coupling parts, respectively. The first chamber is directly connected with a discharge hole formed on an upper flange. The second chamber and the third chamber are symmetrically formed to be separated from the discharge hole. A plurality of discharge small holes(302a) are formed on the second chamber and the third chamber to form an arc line together with each other, and as near as possible to the rotary shaft insertion port. Noise is reduced thereby as pulsating noise generated during discharge of refrigerant and noise generated in a valve is cut off, and phase of discharge noise wave is variously changed to cause offset due to interference between noise waves.

Description

Muffler of rotary compressor {MUFFLER of ROTARY COMPRESSOR}

The present invention relates to a rotary compressor, and more particularly, to a structure of a muffler for reducing noise generated in a cylinder of a rotary compressor and at the same time reducing the amount of oil.

1 and 2, a schematic configuration and operation of a conventional rotary compressor will be described. In general, a rotary compressor is generally compressed with a driving unit 10 inside a cylindrical casing 100 and the casing 100. The part 11 has a structure included. At the center of the drive unit 10 is a rotating shaft 101 having an eccentric portion 101a and a rotor 102 fixedly coupled to the rotating shaft 101 to generate rotational power by a magnetic field and to transmit the rotating shaft 101 to the rotating shaft 101. It is provided and is spaced apart from the rotor 102 by a predetermined interval is composed of a stator 103 is fixed to the casing 100 surrounding the outer periphery of the rotor (102). Meanwhile, the compression unit 11 has a cylinder 106 in which the eccentric portion 101a and the roller piston 110 are integrally formed, and the upper and lower surfaces of the cylinder 106 support the rotating shaft 101. The upper flange 107 and the lower flange 108 are in close contact with each other. The upper flange 107 has a discharge hole 107a through which the high-pressure refrigerant compressed in the compression chamber is discharged, and the discharge hole 107a. ) And a valve stop plate 112a for preventing elastic deformation due to excessive opening of the discharge valve 112 is inevitably configured. In addition, a muffler 111 is provided on the upper flange to reduce the noise generated during the discharge operation.

In general, the operation of the compressor is such that the low pressure refrigerant introduced into the cylinder from the accumulator 104 through the suction port 105 is caused by the rotation of the rotary piston 101 including the eccentric portion 101a. The high pressure is applied by the compression action of 110 and is discharged from the compression chamber of the cylinder through the discharge hole 107a of the upper flange 107, and the discharge valve 112 is opened during this discharge action. And the upper flange 107 are introduced into a space (hereinafter referred to as a noise space). The refrigerant is discharged into the casing 100 through the discharge hole 111a to exit the compressor through the spaced interval between the rotor 102 and the stator 103 and the discharge port 109. At this time, the pulsation noise generated by the periodic discharge action of the high pressure refrigerant in accordance with the periodic rotation of the rotary shaft 101 and the noise for reducing the noise generated between the valve 112 and the valve stop plate 112a As shown in FIG. 2, a muffler 111 is provided.

In general, the muffler has a rotary shaft insertion hole 202 to be inserted into the rotary shaft 101 in the form of a large disc in the center, the coupling portion 201 for coupling with the upper flange 107 is provided. A pair of discharge holes 111a are provided spaced apart from the discharge holes 107a formed in the upper flange 107 by a predetermined distance, and the discharge holes 111a flow into the noise space from the discharge holes 107a. The high-pressure refrigerant is discharged into the casing 100, and the noise generated by the discharge action as described above is reduced by the change in the acoustic impedance of the muffler.

However, the muffler of the rotary compressor as described above has a structure in which the refrigerant discharged into the noise space is discharged through a pair of large discharge holes formed in the muffler, thereby reducing the pulsation noise of the refrigerant and the impact noise of the valve. In addition, there was a problem in that the oil is mixed with a high-pressure refrigerant in the noise space is discharged through the discharge hole as it is discharged through the compressor as it is discharged from the oil, there is a problem that the efficiency of the compressor is lowered.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to provide a muffler for improving the structure of the muffler to reduce the oil amount of oil and further reduce the noise generated during the discharge action of the compressor.

1 is a side cross-sectional view showing a cross section of a conventional rotary compressor.

2 is a top view showing a conventional muffler.

3A, 3B, 3C, and 3D are top views illustrating a muffler according to an embodiment of the present invention.

Figure 4 is a graph of a comparative experiment of the present invention and the prior art.

* Description of the symbols for the main parts of the drawings *

301: coupling portion 302a, 302b, 302c, 302d: discharge pore

303: rotary shaft insertion hole 304: the first chamber

305: second chamber 306: third chamber

401: discharge hole

The present invention for achieving the above object is a main feature of the muffler for reducing the noise generated from the cylinder of the rotary compressor, characterized in that a plurality of discharge pores are formed near the rotation shaft insertion hole of the muffler.

Hereinafter, preferred embodiments of the present invention will be described in more detail with reference to FIGS. 3A, 3B, 3C, and 3D. The same reference numerals are used for the same components, and overlapping operations and descriptions according to embodiments will be omitted as much as possible.

As shown in FIG. 3A, the muffler according to the present invention has three spaces (hereinafter, referred to as chambers) partitioned by three coupling parts 301 and the rotary shaft when the rotary shaft is inserted into the rotary shaft insertion hole 303 formed therein. The three chambers are communicated through narrow passages formed by the rotating shaft and the coupling part 301, respectively. The chamber may include a first chamber 304 in direct communication with the discharge hole 401 formed in the upper flange, and a second chamber 305 and a third chamber 306 spaced apart from the discharge hole 401 by a predetermined distance. Can be divided into As shown in FIG. 3A, the second chamber 305 and the third chamber 306 are configured symmetrically with each other. At this time, the second chamber 305 and the third chamber 306 are formed in a plurality of discharge holes 302a in an arc shape as close as possible to the rotation shaft insertion hole 303. Referring to the operation of the muffler having such a structure, first, the discharge valve is opened by the fluid force of the refrigerant compressed to high pressure in the cylinder of the rotary compressor, and the high-pressure refrigerant is discharged to the upper flange at a high speed (401). It is introduced into the first chamber 304 through the). Since the refrigerant moves through a narrow flow path formed between the first chamber 304, the second chamber 305, and the third chamber 306, the second chamber 305 and the third chamber ( It is moved to 306 and is discharged into the casing through a plurality of discharge holes 302a formed in the second chamber 305 and the third chamber 306, which is discharged into the plurality of discharge holes (302a) The refrigerant is sequentially discharged in the order of the discharge pore closest to the discharge hole 401, and the pulsation noise and the noise generated by the valve are also discharged through the path. In this case, the noise generated by the muffler is directly cut off, and the pulsation noise and the noise generated from the valve are noises depending on the positions of the plurality of discharge pores 302a while being exited through the plurality of discharge pores 302a. The phases of the waves vary, causing cancellation by interference, which reduces noise. In addition, the high-speed refrigerant is moved to the side wall of the muffler (not shown, see Fig. 1 of the prior art) by the moving inertia when moving from the first chamber to the second chamber. Due to this large amount of adhesion to the side wall of the muffler increases, the muffler also has the function of recovering the oil of the refrigerant.

3B is another embodiment of the present invention, similar to the configuration of FIG. 3A as shown in FIG. 3B, but having a different configuration in which the size of the discharge pore 302b becomes larger as the distance from the discharge hole 401 increases. Has

This configuration is more preferable in terms of reducing the discharge oil than in the muffler described in Fig. 3A. Usually, since the discharge pore formed in the muffler according to the embodiment of the present invention shown in FIG. 3A or less is formed to be as close as possible to the rotation shaft insertion opening, the high pressure refrigerant moving in the first chamber moves straight through the moving inertia. The discharge pore closest to the hole, that is, the discharge pore located in the narrow passageway formed between the first chamber, the second chamber, and the third chamber may directly discharge the high-pressure refrigerant, but is formed subsequent to the arc. The discharge pore farther away from the discharge hole, the more difficult the direct discharge of the high-pressure refrigerant moving directly from the discharge hole 401 due to the movement inertia of the refrigerant and oil, and the movement direction is bent by hitting the side wall of the muffler or the like. This allows indirect discharge of the high pressure refrigerant. In this case, the high pressure refrigerant collides with the side wall of the muffler, and the oil contained in the high pressure refrigerant sticks to the side wall of the muffler because of viscosity and particle size. In view of this phenomenon, when comparing the embodiment of Fig. 3A and the embodiment of Fig. 3B, the discharge pore 302b of Fig. 3B is configured to increase in size as it moves away from the discharge hole 401. That is, the size of the discharge pore closest to the rotation shaft insertion hole 303 of the plurality of discharge pore 302b and closest to the moving passage line of the high-pressure refrigerant is configured to be the smallest. Therefore, the refrigerant flowing from the first chamber 304 and the oil included in the refrigerant are first formed in the second chamber 305 or the third chamber 306 on the way of the moving direction of the refrigerant and the oil included in the refrigerant. The amount of the high-pressure refrigerant flowing directly into the casing through the smallest discharge pore closest to the discharge hole 401, that is, the discharge hole 401 is relatively small, and the content of oil is reduced due to the side wall of the muffler. Since the amount of indirect discharge of the refrigerant is increased, the effect of reducing the amount of oil due to the moving inertia of the oil is increased as described above.

Figure 3c is an embodiment having a different configuration from the above embodiment, the alternative configuration is similar to the above embodiment, but the discharge pore 302c and the arrangement according to the size is different from the above embodiment have. That is, the size of the discharge pore 302c closest to the discharge hole 401 is the smallest, and the size of the discharge pore 302c gradually increases and becomes smaller as the number of the discharge pore 302c moves away from the discharge hole 401. The discharge pore 302c farthest from 302c has a symmetrical configuration that becomes smaller by the size of the discharge pore 302c closest to the discharge hole 401. Referring to Figure 4 analyzing the experimental data compared to the conventional technology according to this configuration Figure 4 is a graph comparing the experimental data according to the invention represented in Figure 3c with the prior art as shown in Figure 4 the noise of the rotary compressor The reduction effect shows a marked improvement over the prior art. That is, in Fig. 4, the Y axis represents dB (decibels) and the X axis represents the rotation frequency, or frequency, of the rotary compressor, and the unit is Hz. Here, it can be seen that the technology of the present invention significantly reduces the noise measured in decibels on the basis of the prior art.

3d illustrates that the discharge holes 302d are arranged in a plurality of rows in an arc shape around the rotation shaft insertion hole 303. This configuration also shows another embodiment according to the technical idea of the present invention.

Therefore, in addition to those described above, those skilled in the art to which the present invention pertains may easily implement other forms of the present invention within the same scope as described above only by the description of the present invention.

According to the present invention, the pulsation noise generated at the time of discharge of the refrigerant and the noise generated from the valve are blocked and at the same time, due to various phase changes of the discharge noise wave, an offset phenomenon occurs due to the interference between the sound waves, thereby obtaining an excellent noise reduction effect. In addition, the oil amount of the oil is reduced, and the discharge of the refrigerant is relatively increased, thereby improving the efficiency of the compressor.

Claims (7)

In the muffler for reducing the noise generated from the cylinder of the rotary compressor, A muffler of a rotary compressor, characterized in that a plurality of discharge holes are formed in the vicinity of the rotary shaft insertion hole of the muffler. The method of claim 1, The plurality of discharge pores are formed in a circular line around the rotation shaft insertion hole muffler of the rotary compressor. The method according to claim 1 or 2, The muffler is divided into a first chamber which is in direct communication with the discharge hole, and a second chamber and a third chamber spaced apart from the discharge hole by a predetermined distance, wherein each chamber is in communication with a narrow passage. The method of claim 3, The muffler of the rotary compressor, wherein the plurality of discharge holes are formed in the second and third chambers excluding the first chamber. The method of claim 4, wherein The plurality of discharge pores formed in the second chamber and the third chamber, respectively, the discharge pore on the side close to the discharge hole is small and larger as the distance away from the discharge hole muffler of the rotary compressor. The method of claim 4, wherein The plurality of discharge holes formed in the second chamber and the third chamber, respectively, the discharge holes in the side close to the discharge hole is small and gradually larger and larger and smaller again from the discharge hole, the rotary compressor characterized in that Muffler. The method of claim 2, The discharge pore formed in the circular line is a muffler of the rotary compressor, characterized in that formed in a plurality of rows.