KR100332972B1 - Structure for reducing noise in rotary compressor - Google Patents

Abstract

The present invention relates to a noise reduction structure of a hermetic rotary compressor. The present invention relates to a rotary shaft which is provided with an eccentric portion and is rotated by receiving a driving force of an electric mechanism, a rolling piston inserted into an eccentric portion of the rotary shaft, and the rolling piston is inserted. A cylinder having a space formed between an inner circumferential surface thereof and an outer circumferential surface of the rolling piston; upper and lower bearings respectively coupled to the cylinder to seal the inner space and supporting the rotating shaft; Enclosed rotary compressor having a vane for coupling linearly reciprocating radially through the main wall and linear contact with the outer circumferential surface of the rolling piston and converting the space portion of the cylinder into a suction zone and a compression zone according to the rotation of the rotating shaft. Inner groove of the portion overlapping with the circumferential wall of the cylinder And an opening groove of a portion overlapping the inner space of the cylinder, and configured to form a surge groove having a distance from the inner wall of the cylinder to the end of the opening groove of 55% or less of the rolling piston thickness to suck, compress, and discharge the refrigerant gas. By reducing the noise caused by the pressure pulsation generated in the process to improve the reliability and to reduce the compression power required to compress the refrigerant gas.

Description

Noise reduction structure of hermetic rotary compressor {STRUCTURE FOR REDUCING NOISE IN ROTARY COMPRESSOR}

The present invention relates to a hermetic rotary compressor, and more particularly, to a noise reduction structure of a hermetic rotary compressor capable of reducing noise caused by pressure pulsation generated in the process of sucking, compressing and discharging gas.

In general, a compressor is a device for compressing a fluid, and there are various types of compressors such as a rotary compressor, a reciprocating compressor, and a scroll compressor according to a method of compressing a gas. Such a compressor is composed of a hermetically sealed container having a predetermined internal space, an electric mechanism part mounted in the hermetically sealed container to generate a driving force, and a compressor mechanism part that compresses gas by receiving a driving force of the electric mechanical part.

As an example of the compressor, in the hermetic rotary compressor, as illustrated in FIGS. 1A and 1B, an electric mechanism part is mounted on one side in the hermetic container 1 formed in a predetermined shape, and the compressor mechanism part is provided at a predetermined interval. Is mounted. The electric machine part includes a stator 2 fixedly coupled to the hermetic container 1 and a rotor 3 rotatably coupled to the stator 2.

And the compression mechanism is formed to have a predetermined length and the eccentric portion (4a) is formed on one side of the rotating shaft (4) is pressed into the inner diameter of the rotor 3, and the internal space (P) where the gas is sucked and compressed Is provided inside the sealed container 1 and seals the cylinder 5 into which the eccentric portion 4a of the rotating shaft is inserted into the inner space P and the inner space P of the cylinder. Upper and lower bearings 7 and 8 that are coupled to the upper and lower portions of the cylinder 5 by fastening the bolts 6 and support the rotating shaft 4, and the eccentric portions 4a of the rotating shaft. A rolling piston (9) inserted into the inner space (P) of the cylinder (5) and revolving in accordance with the rotation of the rotary shaft (4), and inserted into one side of the cylinder (5) so as to reciprocate in a radial direction. In addition, the end thereof is in line contact with the outer circumferential surface of the rolling piston (9), the inner hole of the cylinder (5) Is configured to include a space portion suction region (a) and the vanes (10) for converting the compression region (b) formed by the outer peripheral surface of the inner peripheral surface of the rolling piston (9).

A discharge port 5b is formed such that the inlet port 5a through which the gas is sucked into the cylinder 5 is located at the side of the vane 10, and the compressed gas is discharged from the compression zone b on the other side of the vane 10. Is formed and the suction port 5a, the vane 10 and the discharge port 5b are formed in the order of the discharge port 5b, the vane 10 and the suction port 5a according to the rotational direction of the rotation shaft 4. . Discharge holes 7a are formed in the upper bearing 7 or the lower bearing 8 coupled to the upper and lower portions of the cylinder 5 so as to communicate with the discharge port 5b (shown in the upper bearing in the drawing). ). The suction tube 11 and the discharge tube 12 into which the gas is sucked and discharged are coupled to the sealed container 1, and oil is filled in the bottom surface of the sealed container 1.

Reference numeral 13 is a discharge valve, 14 is a retainer, 15 is a silencer, and 16 is an accumulator.

Compressor as described above is a rolling piston (9) coupled to the eccentric portion (4a) of the rotary shaft by the rotation of the rotary shaft 4 when the rotor 3 rotates while the rotor (3) by the current applied ) Is orbited about the axis center in the cylinder internal space (P) in the state in contact with the vane (10). The low temperature and low pressure refrigerant gas is introduced into the suction pipe 11 and the suction port 5a by the volume change of the space portion formed by the inner circumferential surface of the cylinder internal space P and the outer circumferential surface of the rolling piston 9 due to the orbital rotation of the rolling piston 9. Through the outlet port 5b and the discharge hole 7a together with the operation of the discharge valve 13, the compressed refrigerant gas of the high temperature and high pressure is sucked into the space portion of the cylinder 5 through Discharged.

Referring to the process in which the refrigerant gas is sucked, compressed and discharged in accordance with the rotation of the rotary shaft 4 will be described in more detail. First, as shown in FIG. 2, the long diameter tip d of the eccentric portion 4a of the rotary shaft is vane ( When it comes into contact with 10), the discharge stroke ends and the suction stroke ends. The rotary shaft 4 rotates so that the tip d of the eccentric portion 4a passes through 90 ° with respect to the vane 10, and as shown in FIG. 3, at the position of the vane 10 and 180 °. In the area where the space P is converted into the suction area a and the compression area b by the vane 10, the refrigerant gas is sucked into the suction area a and the volume is reduced in the compression area b. As the gas is gradually compressed. When the rotating shaft 4 is rotated so that the long-diameter tip of the eccentric portion 4a passes 180 ° and is positioned at the discharge port 5b as shown in FIG. 4, the refrigerant gas suction amount into the suction region a is increased. At the same time as the pressure increases in the compression zone b while the pressure in the compression zone b becomes greater than the discharge gas, the discharge valve 13 opens, and the compressed gas discharges through the discharge port 5b and It discharges through the discharge hole 7a.

On the other hand, while the rotor 3 rotates during operation of the compressor, the noise caused by the pressure pulsation is generated in the process of continuously repeating the process of inhaling, compressing and discharging the refrigerant gas. In order to reduce the noise caused by the pressure pulsation by providing a resonance effect on the part, researches of various angles are being conducted.

As an example of the conventional structure for reducing the pressure pulsation, as shown in Figures 5a, 5b, having a predetermined inner diameter and depth between 150 ° ~ 270 ° in the direction of rotation of the rotation axis relative to the vane 10 The non-penetrating hole 12 is formed in each one or more places of an upper bearing or a lower bearing.

However, the conventional structure as described above is formed by the non-penetrating hole 12 in the form of a simple cylinder, so that the role of the effective resonator is insufficient, and the thickness of the rolling piston 9 when setting the internal volume of the non-penetrating hole 12 is insufficient. You will be limited. That is, when the size of the non-penetrating hole 12 is larger than the thickness of the rolling piston 9, the gas in the high pressure region leaks into the low pressure region in the process of compressing the refrigerant gas, causing re-expansion loss.

In addition, the setting range of the non-penetrating hole 12 may not be an appropriate range within an arbitrarily set range considering only the discharge side, and the aspect of compression efficiency may not be considered.

The object of the present invention devised in view of the above point is to minimize the noise generated by the pressure pulsation generated in the compression mechanism during operation of the compressor as well as to reduce the compression driving force required to compress the refrigerant gas. It is to provide a noise reduction structure of a hermetic rotary compressor.

1a, 1b is a front cross-sectional view and a planar cross-sectional view showing a general hermetic rotary compressor,

2, 3, and 4 are planar cross-sectional views illustrating an operation process of the hermetic rotary compressor, respectively.

5a and 5b are a front view and a plan view showing an example of a conventional closed rotary compressor noise reduction structure;

Figure 6a, 6b is a front cross-sectional view and planar cross-sectional view of the hermetic rotary compressor with a closed rotary compressor noise reduction structure of the present invention,

7, 8, 9a, 9b is a plan view and a front cross-sectional view showing a modification of the surge groove constituting the noise reduction structure of the hermetic rotary compressor of the present invention, respectively;

10, 11 and 12 are plan views showing the operating state of the closed rotary compressor noise reduction structure of the present invention, respectively;

13 is a degree of freedom modeled after the closed rotary compressor noise reduction structure of the present invention,

14 is a graph illustrating a noise state during operation of the hermetic rotary compressor and the conventional hermetic rotary compressor equipped with a noise reduction structure according to the present invention, respectively;

FIG. 15 is a graph illustrating a noise generation state according to each position of a surge groove constituting the noise reduction structure of the hermetic rotary compressor of the present invention; FIG.

(Explanation of symbols for the main parts of the drawing)

4 ; Axis of rotation 4a; Eccentric

5; Cylinder 7; Upper bearing

8 ; Lower bearing 9; Rolling piston

10; Vane 30; Surge Home

31; Inner groove portion 32; Opening groove

a; Suction chamber b; Compression chamber

P; Compressed space

In order to achieve the object of the present invention as described above, an eccentric part is provided, and a rotating shaft is rotated by receiving a driving force of the electric mechanism part, a rolling piston inserted into the eccentric part of the rotating shaft, and an inner space into which the rolling piston is inserted. And a cylinder having a space formed between the inner circumferential surface and the outer circumferential surface of the rolling piston, the upper and lower bearings respectively coupled to the cylinder to seal the inner space and supporting the rotating shaft, and penetrate the circumferential wall of the cylinder. In the hermetic rotary compressor having a vane which is coupled to the linear reciprocating motion in the direction and coupled to the outer circumferential surface of the rolling piston and the vane for converting the space of the cylinder into the suction zone and the compression zone in accordance with the rotation of the rotary shaft, the cylinder The inner groove of the portion overlapping with the main wall of the It made part opening groove in the region overlapping with the inner space the noise reducing structure being 55% or less, the hermetic rotary compressor, characterized in that the stand forms a groove in the distance the rolling piston thickness up to the end opening groove portion in the cylinder inner wall is provided.

Hereinafter, the noise reduction structure of the hermetic rotary compressor of the present invention will be described according to the embodiment shown in the accompanying drawings.

6A and 6B illustrate an example of a noise reduction structure of the hermetic rotary compressor of the present invention. Referring to this, first, the hermetic rotary compressor is configured to generate gas by receiving a driving force of the electric mechanism unit and the electric mechanism unit generating a driving force. Compression mechanism portion for compressing, the rotating shaft (4) constituting the compression mechanism portion has a predetermined length and the eccentric portion (4a) is formed on one side thereof and is pressed into the rotor (3) of the electric mechanism portion. The rolling piston 9 is inserted into the eccentric portion 4a of the rotation shaft 4, and the rolling piston 9 is coupled to be located in the inner space P of the cylinder 5. The rolling piston 9 is formed in an annular shape having an inner diameter and a predetermined thickness t corresponding to the outer diameter of the eccentric portion 4a. An inlet port 5a through which gas is sucked into the inner space P is formed in the cylinder 5, and a discharge port 5b through which the compressed gas is discharged from the inner space P is formed at the side thereof. The vane 10 is inserted into the cylinder 5 so as to be located between the discharge port 5b and the suction port 5a, and the end of the vane 10 is inserted into the rolling piston 9 located in the inner space P. Line is contacted. The vane 10 converts the space between the inner circumferential surface of the cylinder inner space P and the outer circumferential surface of the rolling piston 9 into the suction zone a and the compression zone b as the rotation shaft 4 rotates.

Upper and lower bearings 8 and 8 are respectively coupled to upper and lower surfaces of the cylinder 5 to seal the inner space P of the cylinder, and the rotary shaft 4 is upper and lower bearings 7 and 8. Are respectively inserted through to support the rotating shaft (4). A discharge hole 7a is formed in the upper bearing 7 or the lower bearing 8 so as to communicate with the discharge port 5b (shown in the upper bearing in the drawing), and the discharge hole opens and closes the discharge hole 7a. The valve 13 is mounted.

Then, the surge groove 30 is formed by the inner groove portion 31 of the portion overlapping with the circumferential wall 5c of the cylinder 5 and the opening groove portion 32 of the portion overlapping with the cylinder internal space P. The surge groove 30 is formed such that the distance L from the inner wall of the cylinder to the end of the opening groove 32 is 55% or less of the rolling piston thickness t. For example, the surge groove 30 is formed in a cylindrical shape having a predetermined inner diameter and a predetermined depth, and when coupled, the cylindrical surge groove 30 has an inner groove 31 at a portion overlapping the cylinder circumferential wall 5c. And it is divided into the opening groove 32 of the portion overlapping with the inner cylinder space (P).

As another modified example of the surge groove 30, as shown in FIG. 7, an elliptic cylinder shape having a predetermined depth and having an elliptical shape in cross section is combined and the surge groove 30 having an elliptic cylinder shape when coupled thereto. Is divided into an inner groove portion 31 overlapping the cylinder circumferential wall 5c and an opening groove portion 32 of a portion overlapping the cylinder inner space P.

In addition, as another modification of the surge groove 30, as shown in Figure 8, has a predetermined depth and the cross-section is formed in a polygonal cylinder shape having a square shape or more and the rectangular groove shape surge groove 30 ) Is divided into an inner groove portion 31 overlapping with the cylinder circumferential wall 5c and an opening groove portion 32 of a portion overlapping with the cylinder inner space P.

In addition, the surge groove 30 is preferably formed in a constant depth, and as a variant thereof, as shown in Figure 9a, 9b, it may be formed so that the depth is different. That is, the stepped in the form of a multi-stage or curved surface is formed so that the depth of the surge groove 30 is different.

The surge groove 30 is formed at one or more places on the sliding surface of the upper bearing 7 or the lower bearing 8. The surge groove 30 is preferably formed in the lower bearing 8 so as to be located between 80 ° ~ 90 ° in the rotational direction of the rotary shaft 4 with respect to the vane (10).

The surging volume of the surge groove 30 is formed to be 0.5% to 2% of the volume of the space portion, which is a space between the inner circumferential surface of the inner space P of the cylinder 5 and the outer circumferential surface of the rolling piston 9. That is, it is preferably formed so as to be 0.5% to 2% of the total gas intake volume.

Hereinafter, the operational effects of the hermetic rotary compressor noise reduction structure of the present invention will be described.

First, when power is applied to rotate the rotating shaft 4 while the rotor 3 constituting the electric mechanism rotates, the rolling coupled to the eccentric portion 4a of the rotating shaft 4 by the rotation of the rotating shaft 4. The piston 9 is idle in the cylinder internal space P while in contact with the vane 10.

The low temperature low pressure refrigerant gas is sucked into the cylinder internal space P through the suction pipe 11 and the suction port 5a by the volume change of the cylinder space portion partitioned by the vane 10 by the revolution of the rolling piston 9. The compressed high-temperature high-pressure refrigerant gas is discharged through the discharge port 5b and the discharge hole 7a together with the operation of the discharge valve 13. Referring to this process in more detail, first, as shown in Fig. 10, when the eccentric portion 4a of the long shaft tip d of the rotary shaft is in contact with the vane 10, the discharge stroke ends and the suction is performed. The administration ends. Then, as the rotary shaft 4 rotates so that the tip d of the eccentric portion 4a reaches the position past the surge groove 30, as shown in FIG. As a result, the refrigerant gas is sucked into the suction zone a while being converted into the suction zone a and the compression zone b, and the gas is gradually compressed due to a decrease in volume in the compression zone b. In this step, the compressive force acts by the surge groove 30 smaller than before. As shown in FIG. 12, in the process of the rotation shaft 4 rotating so that the long-diameter tip d of the eccentric portion 4a reaches the position of the discharge port 5b through the surge groove 30, When the suction amount of the refrigerant gas to a) increases and the pressure in the compression zone b increases while the pressure in the compression zone b becomes larger than the discharge gas, the discharge valve 13 opens and the compressed gas is opened. Is discharged through the discharge port 5b and the discharge hole 7a.

As the above process is repeated continuously, the gas is compressed, and the noise caused by the pressure pulsation generated in the process is reduced by the surge groove 30. As shown in FIG. 13, the surge groove 30 acts as a resonator to attenuate noise in a specific frequency band caused by pressure pulsation. FIG. 14 is a graph measuring pressure pulsations generated by operating a compressor in a state where the surge groove 30 is formed and the surge groove 30 is not formed. As shown in FIG. It can be seen that the noise is significantly reduced in the area where compression and suction are simultaneously performed.

FIG. 15 is a graph showing values of noise generated by operating the compressor at the positions of the surge grooves 30 at various angles, and as shown in FIG. 15, the surge grooves 30 are 80 °. When installed between ~ 90 °, the noise reduction effect is large. In addition, since the surge groove 30 is formed at a position of 80 ° to 90 ° from the vane, which is the area where the compression power gain is the largest, the compression power required to compress the gas can be reduced.

In addition, since the opening groove 32 of the surge groove 30 is formed at 55% or less of the rolling piston thickness t, pressure leakage may be prevented to the inside of the rolling piston 9.

As described above, the noise reduction structure of the hermetic rotary compressor according to the present invention forms a surge groove so as to communicate with the inner space of the cylinder in which the refrigerant gas is compressed, but the opening area in which the surge groove communicates with the inner space of the cylinder is rolled. Since it is formed to be 55% or less of the piston thickness, the noise caused by the pressure pulsation generated in the process of inhaling, compressing, and discharging the refrigerant gas can be reduced to increase reliability, and the compression power required to compress the refrigerant gas can be reduced. It has an effect.

Claims (5)

An eccentric part is provided, and a rotating shaft which is rotated by receiving a driving force of the electric mechanism part, a rolling piston inserted into the eccentric part of the rotating shaft, and an inner space into which the rolling piston is inserted is formed, and a space is formed between the inner circumferential surface and the outer circumferential surface of the rolling piston. A cylinder formed, an upper and lower bearing coupled to the cylinder to seal the inner space and supporting the rotating shaft, and coupled to allow a linear reciprocating motion in a radial direction through the main wall of the cylinder and the rolling In a hermetic rotary compressor having a vane coupled to the outer circumferential surface of the piston to convert the space portion of the cylinder into a suction zone and a compression zone according to the rotation of the rotary shaft, the inner groove of the portion overlapping with the main wall of the cylinder and the cylinder Consists of the opening groove of the part overlapping the internal space Noise reduction structure of the cylinder inner wall of the hermetic distance from the end opening in the groove portion, characterized in that the surge less than 55% of the thickness of the rolling piston rotary compressor form a groove. The noise reduction structure of a hermetic rotary compressor according to claim 1, wherein the surge groove has a surging volume corresponding to 0.5% to 2% of the total volume of the space part. The noise reduction structure of a closed rotary compressor according to claim 1 or 2, wherein a surge groove is formed between 80 ° and 90 ° in a rotational direction of the rotary shaft based on the vane. The noise reduction structure of a closed rotary compressor according to any one of claims 1 to 3, wherein at least one surge groove is formed in the lower bearing. The noise reduction structure of a hermetic rotary compressor according to claim 1 or 3, wherein the planar cross section of the surge groove is formed of a polygon in a circle, an ellipse, or a square or more, and its longitudinal section is formed of a curved jaw or an angular jaw of multiple stages. .