KR20020029707A - Structure for reducing noise in hermetic compressor - Google Patents

Abstract

The present invention relates to a hermetic compressor. The present invention relates to an eccentric portion of a rotating shaft which is rotated by receiving a driving force of a power mechanism, and a rolling piston inserted into the eccentric portion, whereby gas is sucked and compressed by the revolution of the rolling piston. The inner space of the cylinder is provided with an upper bearing and a lower bearing for sealing the inner space of the cylinder and supporting the rotating shaft, respectively, which are coupled to contact the upper and lower surfaces of the cylinder with the inner space discharged. The gas suction hole penetrates the inner circumferential surface and the cylinder outer surface of the inner space of the cylinder so that the gas is sucked in, and a pulsation reducing groove having a predetermined space is formed in the inner circumferential wall of the gas suction hole to reduce the pulsation of the gas. As the rotary shaft rotates by receiving the driving force of the electric mechanism unit The rolling piston inserted into the eccentric portion of the rotating shaft rotates in the inner space of the cylinder while reducing the pressure pulsation of the gas generated in the process of inhaling, compressing and discharging the refrigerant gas due to the volume change of the partitioned inner space. It is to increase the reliability by suppressing the vibration noise generated by the pulsation.

Description

Vibration noise reduction structure of hermetic compressor {STRUCTURE FOR REDUCING NOISE IN HERMETIC COMPRESSOR}

The present invention relates to a hermetic compressor, and more particularly, to a vibration noise reduction structure of a hermetic compressor to minimize vibration noise caused by pressure pulsation generated during a process of inhaling, compressing, and discharging gas into a cylinder.

Generally, a hermetic compressor is a device for compressing a fluid. Such a compressor is composed of an electric mechanism part which is mounted in a sealed container and generates a driving force, and a compressor mechanism that compresses gas by receiving the driving force of the electric mechanism part. The compressor may be of various types, such as a rotary compressor, a reciprocating compressor, a scroll compressor, and a scroll compressor.

1 and 2 illustrate the compression mechanism of the rotary compressor as a center, and as shown in FIG. 1, the compression mechanism is provided with an eccentric portion 11 at one side thereof, connected to an electric shaft, and a rotary shaft 10. A cylinder 20 into which the inner space P is sucked and compressed is installed inside the sealed container 1, and the eccentric portion 11 of the rotating shaft is inserted into the inner space P, and the cylinder. Upper and lower bearings 40 and 50 are coupled to the upper and lower portions of the cylinder 20 to seal the inner space P of the cylinder 20 by fastening the bolts 30, respectively, and to support the rotating shaft 10. And a rolling piston 60 inserted into the eccentric portion 11 of the rotation shaft and positioned in the internal space P of the cylinder 20 to revolve as the rotation shaft 10 rotates, and one side of the cylinder 20. Radially linear reciprocating motion is inserted into the end of the rolling piece A vane for linearly contacting the outer circumferential surface of the 60 to convert the space formed by the inner circumferential surface of the inner space P of the cylinder 20 and the outer circumferential surface of the rolling piston 60 into the suction zone a and the compression zone b. 70).

The cylinder 20 has an inner space P formed therein so as to have a predetermined inner diameter among the cylinder bodies 21 formed in a predetermined shape, and gas is sucked into the inner space P on one side of the cylinder body 21. A through suction part 22 is formed, and a discharge port 23 through which gas is discharged is formed at a side of the suction part 22, and the vane 70 is disposed between the suction part 22 and the discharge port 23. This inserted vane slot 24 is formed.

The cylinder 20 has an eccentric portion 11 and a rolling piston 60 of the rotating shaft located in the inner space P thereof, and the vane 70 is inserted into the vane slot 24 and the suction portion 22 thereof. ) Is coupled to the suction pipe 80 through which the refrigerant gas is introduced, and the upper bearing 40 and the lower bearing 50 are coupled to the upper and lower surfaces of the cylinder body 21, so that the inner space P is sealed. At this time, the discharge port 23 of the cylinder 20 is in communication with the discharge hole 41 formed in the upper bearing 40.

Reference numeral 81 is a discharge means, 82 is a silencer, 83 is a spring supporting the vane.

Compressor mechanism operation of the hermetic compressor as described above, first, the driving force of the electric mechanism is transmitted to the rotary shaft 10, when the rotary shaft 10 is rotated, the eccentric portion 11 of the rotary shaft 10 by the rotation of the rotary shaft 10 In the state in which the rolling piston 60 coupled to the vane 70 is in contact with the vane 70, the rolling piston 60 revolves about the axis center in the cylinder internal space P. Due to 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 60 due to the orbital rotation of the rolling piston 60, the refrigerant gas of low temperature and low pressure is introduced into the suction pipe 11 and the suction portion ( 22) for the suction part space of the cylinder 20 is compressed to a state of high temperature and high pressure that the refrigerant gas of the compressed high-temperature and high-pressure is Saturday output port 23 and the discharge hole (41 with the motion of the discharge valve 81 through) It is discharged through.

Meanwhile, the suction part 22 of the cylinder guiding the refrigerant gas to be sucked into the inner space P of the cylinder is implemented in various forms so that the suction of the refrigerant gas into the cylinder inner space P can be performed smoothly. 3 is an example of a conventional structure for the cylinder suction part 22, which is disclosed in US 5,829,960. As shown in the drawing, the cylinder suction part 22 has a small inner diameter on one side of the cylinder body 21 inwardly. And a multi-stage through hole 22a having a relatively large inner diameter to the outside is formed, and the suction tube 80 is inserted into the multi-stage through hole 22a with a larger inner diameter, wherein the inner diameter of the suction tube 80 is increased. And the small inner diameter of the through hole 22a are equal, and the inner diameter of the entire gas flow path is constant. In addition, an opening groove 22b is formed at an inner edge of the cylinder inner space P, including the through hole 22a in a vertical direction of the through hole 22a, and the opening groove 22b is formed in the inner space ( It is formed in a curved shape with a large width toward the P) side.

In another modification, as shown in FIG. 4, a hemispherical expansion groove 22c is formed on the inner circumferential wall of the cylinder internal space P so as to extend the end of the through hole 22a.

However, as described above, the structures in which the end of the through-hole 22a is extended toward the inner space P of the cylinder are driven by the idle operation of the rolling piston 60 located in the inner space P of the cylinder. While the refrigerant gas is sucked into the cylinder space P by the volume change of the cylinder space P partitioned by the vanes 70, the amount of suction gas is increased to improve the compression performance. There was a disadvantage that the vibration noise generated by the pulsation of the gas is not reduced.

The object of the present invention devised in view of the above point is a vibration noise reduction structure of a hermetic compressor to minimize vibration noise caused by pressure pulsation generated in the process of inhaling, compressing and discharging gas into the cylinder inner space. In providing.

1,2 is a front sectional view and a plan sectional view showing a general hermetic rotary compressor;

3 and 4 are perspective views each showing an example of the conventional closed rotary compressor noise reduction structure,

5, 6 is a front and plan sectional view of a hermetic compressor equipped with a vibration noise reduction structure of the present invention,

7 is a perspective view of a vibration noise reduction structure of the hermetic compressor of the present invention;

8, 9, 10, and 11 are plan views illustrating embodiments of the hermetic compressor vibration noise reduction structure according to the present invention.

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

10; Axis of rotation 11; Eccentric

20; Cylinder 25; Gas suction hole

26; Pulsation reducing groove 26a; Penetration

40; Upper bearing 50; Lower bearing

A; Cylinder upper surface B; Cylinder

P; Cylinder inner space

In order to achieve the object of the present invention as described above, the eccentric portion of the rotating shaft and the rolling piston inserted into the eccentric portion are rotated in response to the driving force of the electric mechanism, so that the gas is sucked and compressed by the revolution of the rolling piston. In the hermetic compressor having an inner space to be discharged and the upper and lower surfaces of the cylinder are in contact with each other to seal the inner space of the cylinder and to support the rotating shaft, respectively. A gas suction hole penetrating the inner circumferential surface of the cylinder inner space and the cylinder outer surface is formed so that gas is sucked into the inner space of the cylinder, and a pulsation reducing groove having a predetermined space is provided in the inner circumferential wall of the gas suction hole to reduce the pulsation of the gas. Vibration noise reduction structure of the hermetic compressor characterized in that formed Is provided.

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

5 and 6 illustrate an example of the vibration noise reduction structure of the hermetic compressor of the present invention. As shown in the drawing, first, the compression mechanism of the hermetic rotary compressor has an eccentric portion 11 at one side thereof, The rotating shaft 10 is connected, and the inner space P is sucked and compressed is provided inside the sealed container 1 and the eccentric portion 11 of the rotating shaft is inserted into the inner space P. The upper and lower portions of the cylinder 20 and the upper and lower portions of the cylinder 20 are coupled to each other by fastening the bolts 30 to seal the inner space P of the cylinder, and support the rotating shaft 10. A rolling piston (60) inserted into the lower bearing (40) and the eccentric portion (11) of the rotary shaft and positioned in the inner space (P) of the cylinder to revolve as the rotary shaft (10) rotates; One side of the cylinder 20 is inserted to enable linear reciprocating motion in the radial direction In addition, the end portion thereof is in line with the outer circumferential surface of the rolling piston 60 to form a space portion formed by the inner circumferential surface of the inner space P of the cylinder and the outer circumferential surface of the rolling piston 60 as the suction region a and the compression region b. It is comprised including the vane 70 to convert.

The cylinder 20 is formed to have a predetermined thickness and area, and is fixed at the center of the cylinder body 21 in which the upper bearing 40 and the lower bearing 50 are in contact with both sides thereof, that is, the upper and lower surfaces A and B, respectively. An inner space P penetrated to have an inner diameter is formed, and a vane slot 24 into which the vanes 70 are inserted is formed in the cylinder body 21, and a discharge port 23 is formed at a side of the vane slot 24. Is formed and the other side of the vane slot 24 is provided with a gas suction hole 25 for the gas is sucked into the inner space (P).

A pulsation reduction groove 26 having a predetermined space is formed in the inner circumferential wall of the gas suction hole 25 to reduce the pulsation of the gas. As shown in FIG. 7, the pulsation reducing groove 26 is formed in the inner circumferential wall of the gas suction hole 25 so as to penetrate the upper surface A of the cylinder body 21 in contact with the upper bearing 40. It consists of the through part 26a formed and the contact surface 42 of the said upper bearing 40 which blocks the said through part 26a.

In another embodiment of the pulsation reducing groove 26 and the through portion (26a) formed in the inner circumferential wall of the gas suction hole 25 to penetrate the lower surface of the cylinder body 21 in contact with the lower bearing 40 and It consists of the contact surface 51 of the said lower bearing 50 which blocks the through part 26a.

The through portion 26a of the pulsation reducing groove 26 is formed in an area including a rim D forming the cylinder inner space P to form the same space as the cylinder inner space P, but the gas suction hole It is formed in a circular shape having its center point on the center line of (25). The circular shape of the through part 26a is formed in a circular shape having an inner diameter corresponding to the inner diameter of the gas suction hole 25, and the circular shape is formed in a hemispherical shape overlapping with the inner space P. The distance k of the point where the inner space P forming the circle and the penetrating portion 26a overlap, that is, the width at which the inner space P and the penetrating portion 26a communicate with each other is defined by the width of the penetrating portion 26a. It is formed to correspond to the inner diameter.

As a modification of the penetrating portion 26a of the pulsation reducing groove, as shown in FIG. 8, the edge D forming the cylinder inner space P is formed to form the same space as the cylinder inner space P. As shown in FIG. It is formed in the area including a circular shape having a center point on the center line of the gas suction hole (25). A circular shape of the through part 26a is formed in a circular shape having an inner diameter smaller than that of the gas suction hole 25, and the circular shape overlaps the inner space P to form a hemispherical shape. The distance k of the point where the inner space P forming the circle and the penetrating portion 26a overlap, that is, the width at which the inner space P and the penetrating portion 26a communicate with each other is defined by the width of the penetrating portion 26a. It is formed to correspond to the inner diameter.

In another modified example of the penetrating portion 26a of the pulsation reducing groove, as shown in FIG. 9, the frame includes an edge forming the cylinder inner space P to form the same space as the cylinder inner space P. FIG. It is formed in the region and is formed in the form of two overlapping circles having its center point on the center line of the gas suction hole (25). The two overlapping circle shapes are formed in a circular shape having an inner diameter smaller than the inner diameter of the gas suction hole 25, and a circle on one side thereof overlaps the inner space P to form a hemisphere. The distance k of the point where the circular inner space P and the penetrating portion 26a overlap is formed to correspond to the inner diameter of the penetrating portion 26a.

In another modified example of the penetrating portion 26a of the pulsation reducing groove, as shown in FIG. 10, the edge D forming the cylinder inner space P to form the same space as the cylinder inner space P is shown. Is formed in an area including a but is formed in a circular shape having a center point on the center line of the gas suction hole (25). The penetrating portion 26a may have a circular shape having an inner diameter smaller than the inner diameter of the gas suction hole 25, but the circular shape may not overlap with the inner space P to become a complete circle. The distance k at which the circular inner space P and the penetrating portion 26a overlap, that is, the width k at which the inner space P and the penetrating portion 26a communicate with each other, is defined as that of the penetrating portion 26a. It is formed smaller than the inner diameter.

In another modified example of the penetrating portion 26a of the pulsation reducing groove, as shown in FIG. 11, the edge D forming the cylinder inner space P to form the same space as the cylinder inner space P is illustrated. Is formed in an area including a but is formed in a circular shape having its center point in a portion that does not coincide with the center line of the gas suction hole (25). The penetrating portion 26a may have a circular shape having an inner diameter smaller than the inner diameter of the gas suction hole 25, but the circular shape may not overlap with the inner space P to become a complete circle. The circular through portion 26a is formed such that its center is located on the opposite side where the vane slot 24 is formed on the center line of the gas suction hole 25 and forms the circular inner space P and the through portion ( The distance k at which the points 26a overlap, that is, the width at which the inner space P and the penetrating portion 26a communicate with each other, is smaller than the inner diameter of the penetrating portion 26a.

On the other hand, the suction pipe 80 through which the refrigerant gas flows into the gas suction hole 25 of the cylinder 20 is coupled, and the cylinder discharge port 23 communicates with the discharge hole 41 formed in the upper bearing 40. .

Reference numeral 81 is a discharge means, 82 is a silencer, 83 is a spring supporting the vane.

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

First, the operation of the hermetic compressor is a driving piston is transmitted to the rotating shaft 10, when the rotating shaft 10 is rotated, the rolling piston 60 is coupled to the eccentric portion 11 of the rotating shaft by the rotation of the rotating shaft 10 In the state of contact with the vane (70) is to revolve around the axis center in the cylinder inner space (P). Due to 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 60 due to the orbital rotation of the rolling piston 60, the refrigerant gas enters the suction pipe 11 and the gas suction hole 25. the suction part space of the cylinder 20 is compressed to conditions of high temperature and high pressure and the refrigerant gas in the compressed high-temperature and pressure via the SAT output port 23 and discharge hole 41 with the motion of the discharge valve 81 through the Discharged.

In the above process, the refrigerant gas is continuously sucked, compressed and discharged by the volume change of the cylinder internal space P, that is, the volume of the space in which the internal space P is partitioned, and the pressure pulsation of the refrigerant gas is generated. The generated pulsation is reduced by the pulsation reducing groove 26 formed in the gas suction hole 25 so as to be located at the inner space P side of the cylinder. The pulsation reducing groove 26 reduces pulsation in a specific frequency band by changing its internal volume.

As described above, the vibration noise reduction structure of the hermetic compressor according to the present invention is divided into a rolling piston inserted into an eccentric portion of the rotating shaft while the driving shaft is rotated in response to the driving force of the electric mechanism. It is possible to reduce the pressure pulsation of the gas generated in the process of inhaling, compressing and discharging the refrigerant gas by changing the volume of the internal space, thereby suppressing the vibration noise generated by the pressure pulsation of the gas, thereby improving the reliability of the compressor. have.

Claims (8)

A cylinder having an eccentric portion of a rotating shaft which is rotated by the driving force of the electric mechanism part and a rolling piston inserted into the eccentric portion is provided with an inner space in which gas is sucked, compressed and discharged by the revolution of the rolling piston. A hermetic compressor having an upper bearing and a lower bearing respectively coupled to the upper and lower surfaces to be in contact with each other to seal the inner space of the cylinder and supporting the rotating shaft, wherein the inner space of the cylinder is configured to suck gas into the inner space of the cylinder. And a gas suction hole penetrating the inner circumferential surface and the outer surface of the cylinder and a pulsation reducing groove having a predetermined space is formed in the inner circumferential wall of the gas suction hole to reduce the pulsation of the gas. . According to claim 1, wherein the pulsation reducing groove is formed of a through portion formed to penetrate the upper or lower surface of the cylinder in which the upper bearing or the lower bearing and the contact surface or the lower bearing contact surface of the upper bearing blocking the through portion. Vibration noise reduction structure of hermetic compressor. According to claim 2, wherein the through portion is formed in a circular shape having a center point on the center line of the gas suction hole is formed in the region including the rim forming the inner space of the cylinder so as to make the same space as the cylinder inner space. Vibration noise reduction structure of hermetic compressor. According to claim 2, The penetrating portion is formed in a region including the rim forming the inner space of the cylinder so as to make the same space as the inner cylinder space, the circular having a center point at a position that does not coincide with the center line of the gas suction hole Vibration noise reduction structure of the hermetic compressor, characterized in that formed in the form. According to claim 2, wherein the through portion is formed in a circular shape including a border forming the inner space of the cylinder to form the same space as the cylinder inner space, the width of the area where the through-hole and the inner space of the circular shape meets the through Vibration noise reduction structure of the hermetic compressor, characterized in that formed smaller than the inner diameter of the negative. According to claim 2, wherein the through portion is formed in a circular shape including a border forming the inner space of the cylinder to form the same space as the cylinder inner space, the width of the area where the through-hole and the inner space of the circular shape meets the through Vibration noise reduction structure of the hermetic compressor, characterized in that formed larger than the inner diameter of the negative. The vibration noise reduction structure of a hermetic compressor of claim 2, wherein the inner diameter of the through part is formed to be the same as the inner diameter of the gas suction hole. The vibration noise reduction structure of a hermetic compressor of claim 2, wherein an inner diameter of the through part is smaller than an inner diameter of the gas suction hole.