KR20140095702A

KR20140095702A - Scroll compressor

Info

Publication number: KR20140095702A
Application number: KR1020130008383A
Authority: KR
Inventors: 황인국; 문치명
Original assignee: 한라비스테온공조 주식회사
Priority date: 2013-01-25
Filing date: 2013-01-25
Publication date: 2014-08-04

Abstract

The present invention relates to a scroll compressor wherein the compression of a refrigerant enclosed in a compression chamber is conducted by the reduction of the compression chamber volume due to relative rotations of a fixated scroll and a rotation scroll. Provided is a scroll compressor wherein a noise reduction member for reducing a crashing sound is placed between the outer circumferential surface of a rotation shaft and the inner surface of an eccentric portion, which strikes the rotation shaft when the compressor stops operating.

Description

[0001] SCROLL COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of reducing an impact sound that may be generated by contact between an eccentric portion and a rotating shaft when the compressor is stopped.

Generally, compressors that serve to compress refrigerant in automotive cooling systems have been developed in various forms. Such a compressor includes a reciprocating type in which compression is performed while a refrigerant is compressed and a rotary type in which compression is performed while rotating.

Here, the reciprocating type includes a crank type in which the driving force of the driving source is transmitted by a crank to a plurality of pistons, a swash plate type in which the swash plate is transmitted, and a wobble plate type in which a wobble plate is used. And a vane rotating seat type using a vane, and a scroll type using a revolving scroll and a fixed scroll.

The scroll compressor is provided with a drive unit, a compression unit, and a control unit inside a housing that forms an appearance, and the inner space of the housing is divided into a suction chamber, a compression chamber, a discharge chamber, and a back pressure chamber.

In this case, the driving unit includes a stator and a rotor mounted coaxially inside the housing, and a rotating shaft installed through the stator, and the control unit includes various driving circuits and elements such as a PCB mounted on the inside of the housing. do.

The suction chamber is a space in which the refrigerant sucked from the outside of the housing is stored. The compression chamber is a space in which the refrigerant sucked into the suction chamber is compressed. The discharge chamber is a space in which compressed refrigerant is discharged from the compression chamber. In the fixed scroll direction.

1 shows an example of a scroll compressor compression unit shown in Japanese Unexamined Patent Application Publication No. 2012-67602 (Patent Document 1). As shown in Fig. 1, a compression unit is fixed to one side of a housing A scroll 10 and an orbiting scroll 11 which forms a compression chamber 15 by engaging with the fixed scroll 10 while being eccentrically rotated by a driving portion.

At this time, the orbiting scroll 11 is eccentrically coupled to the eccentric shaft 8a of the rotary shaft 8 by the bush 12 and the bearing 13, and between the bush 12 and the rotary shaft 8, A balance weight 19 is integrally formed with the bush 12 to balance the eccentric rotation.

In order to prevent breakage of the orbiting scroll 11 due to the liquid refrigerant compression during the initial operation of the orbiting scroll 11, a constant rotation tolerance is provided between the inner peripheral surface of the balance weight 19 and the outer peripheral surface of the rotary shaft 8, So that the rotational motion of the bush 8 is transmitted immediately to the bush 12 in a buffered manner according to the designed rotational tolerance.

When the compressor is stopped, the inner edge portion of the balance weight 19 strongly hits the outer circumferential surface of the rotary shaft 8, And there is a need to reduce such an impact sound in order to improve the sensitivity quality.

Patent Document 1: Japanese Unexamined Patent Application Publication No. 2012-67602 (published Apr. 05, 2012)

SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll compressor capable of reducing an impact noise that can be generated as an inner surface of a weight portion strikes an outer circumferential surface of a rotating shaft when a compressor stops operating.

The scroll compressor according to an embodiment of the present invention includes a fixed scroll that is fixedly disposed, a revolving motion, and a volume of the compression chamber formed between the fixed scroll and the compression scroll is changed according to the idle motion so that the refrigerant in the compression chamber is compressed The orbiting scroll includes an orbiting scroll, a rotating shaft for transmitting a rotational force to orbital motion of the orbiting scroll, a rotating shaft interposed between the rotating shaft and the orbiting scroll such that a rotational force of the rotating shaft is transmitted to the orbiting scroll, A weight portion formed on one side of the eccentric portion to offset a centrifugal force caused by revolution of the orbiting scroll; and a noise portion interposed between the inner surface of the weight portion facing each other and the outer peripheral surface of the rotary shaft to reduce an impact sound And a reduction member.

In the scroll compressor according to the embodiment of the present invention, the noise reducing member may be in the shape of a ring formed along the circumferential direction of the outer circumferential surface of the rotating shaft.

In the scroll compressor according to the embodiment of the present invention, a groove may be formed along the circumferential direction on the outer circumferential surface of the rotary shaft, and the noise reducing member may be coupled to the groove.

In the scroll compressor according to the embodiment of the present invention, the noise reducing member may be cap-shaped and may be overlapped with and coupled to the upper end of the rotary shaft, and between the lower surface of the eccentric portion facing each other and the upper surface of the rotary shaft, And the outer peripheral portion of the noise reduction member can be interposed between the inner surface of the weight portion facing each other and the outer peripheral surface of the rotation shaft.

In the scroll compressor according to the embodiment of the present invention, the noise reducing member may include PTFE (Polytetrafluoroethylene) or a plastic material.

BRIEF DESCRIPTION OF THE DRAWINGS The above features of the present invention will become more apparent from the following detailed description based on the accompanying drawings.

According to the present invention, the inner side surface of the weight portion does not come into direct contact with the outer peripheral surface of the rotating shaft by the noise reducing member interposed between the weight portion and the rotating shaft, but comes in contact with the noise reducing member, The noise is reduced.

In addition, when the noise reducing member is formed in a cap shape and overlapped with the upper end of the rotary shaft, the upper end of the noise reducing member is interposed between the lower surface of the eccentric portion and the upper surface of the rotary shaft. Therefore, friction between the eccentric portion and the rotary shaft So that the noise that can be generated between the lower surface of the eccentric portion and the upper surface of the rotary shaft is also reduced.

1 is a cross-sectional view schematically showing a compression section of a conventional scroll compressor;
2 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention.
3 is a perspective view showing the eccentric portion shown in Fig.
4 is a perspective view showing the eccentric portion and the rotation shaft shown in FIG.
Fig. 5 is a front view and an enlarged cross-sectional view of the eccentric portion and the rotating shaft shown in Fig. 4;
FIG. 6 is a front view and an enlarged cross-sectional view showing another example of the noise reducing member shown in FIGS. 4 and 5; FIG.

Hereinafter, a scroll compressor according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

2 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention.

A scroll compressor 100 according to an embodiment of the present invention includes a fixed scroll 300 fixedly disposed therein and a fixed scroll 300 disposed between the fixed scroll 300 and the fixed scroll 300 An orbiting scroll 600 for compressing the refrigerant in the compression chamber 700 while changing the volume of the compression chamber 700 to be formed and a rotary shaft 421 for transmitting a rotary force for orbiting the orbiting scroll 600, 421 are interposed between the rotary shaft 421 and the orbiting scroll 600 so that the rotary force of the rotary shaft 421 is transmitted to the orbiting scroll 600 and the orbiting scroll 600 is eccentric from the axial center of the rotary shaft 421, A weight portion 530 formed on one side of the eccentric portion 500 to counterbalance the centrifugal force caused by revolution of the orbiting scroll 600 and an inner side surface of the weight portion 530 facing each other, A noise reducing member 900 interposed between the outer circumferential surface It should.

The above-described configurations can be disposed inside the housing 200. The housing 200 has a drive housing 210 which forms an outer appearance of the compressor 100 and in which a drive motor 400 is mounted and a suction port (not shown) is formed on one side of the outer circumference, And a discharge port (not shown) coupled to the rear of the drive housing 210 and discharging compressed refrigerant to one side of the head housing 220, And a cover housing 230 provided with a cover (not shown).

At this time, the shape of the driving unit housing 210, the head housing 220, and the cover housing 230 can be variously modified, and the entire housing 200 can have various configurations.

For example, as shown in FIG. 2, the driving unit housing 210 may include two parts: a front housing 211 and a rear housing 212 that are opposed to each other. Alternatively, the driving unit housing 210 may include a front housing 211, The drive housing 210 and the cover housing 230 or the drive housing 210 and the head housing 220 may be formed integrally with each other.

A space portion is formed inside the driving unit housing 210, and a driving motor 400 can be mounted in the space portion. The driving motor 400 may include a stator 410 and a rotor 420. The stator 410 may include a stator 410 fixed to the inner circumferential surface of the driving unit housing 210 by press- A core 411 and a bundle of coils 412 wound on the stator core 411.

The rotor 420 is rotatably mounted on the inner side of the stator 410 and is rotatably driven. The rotary shaft 421 is rotatably inserted into the central through hole of the stator core 411 and is disposed along the center axis. And a permanent magnet 422 attached to the outer circumferential surface of the rotary shaft 421.

A magnetic field is formed in the stator coil 412 when a current flows through the coil 412 wound on the stator core 411 and the magnetic field is generated by the interaction between the stator 410 and the permanent magnet 422 The rotating shaft 421 is rotated. The rotational force of the rotary shaft 421 is transmitted to the orbiting scroll 600, which will be described later, and acts as an external force for causing the orbiting scroll 600 to revolve.

A first bearing receiving portion 214 may be formed on the bottom surface of the front housing 211 so that the first bearing 213 is fixed to the bottom surface of the front housing 211. A second bearing 215 may be provided on the bottom surface of the rear housing 212 The second bearing receiving portion 216 may be formed to be fixed and fixed to the second bearing 213. The rotation shaft 421 of the driving motor 400 is rotatably supported by the first bearing 213 at the front end, (Not shown).

Although not shown, a suction port may be formed on one side of the outer circumferential surface of the drive housing 210 so that the refrigerant sucked into the space in the drive housing 210 through the suction port is compressed And is compressed to a high pressure in the chamber 700 and can be supplied to the outside through the discharge port.

The head housing 220 may be coupled to the front of the driving unit housing 210 and may include an inverter 221 for converting DC power to AC power. And the rotation speed of the rotor. The rotational speed of the drive motor 400 is controlled by the inverter 221, so that the amount of compression of the refrigerant is controlled, and the interior of the vehicle can be kept constant at a desired temperature.

The cover housing 230 can be coupled to the rear of the driving housing 210 and the discharge port can be installed on one side of the outer circumference of the cover housing 230. The fixed scroll 300 and the orbiting scroll 600 are disposed inside the cover housing 230 .

The fixed scroll 300 may be fixed to one side of the cover housing 230 and the orbiting scroll 600 may be disposed on the other side of the cover housing 230 so as to face the fixed scroll 300 .

The orbiting scroll 600 may be connected to the rotary shaft 421 via the eccentric portion 500 and may be eccentrically connected to the axial center of the rotary shaft 421 by the eccentric portion 500. The connected orbiting scroll 600 revolves with respect to the fixed scroll 300 when the rotary shaft 421 rotates.

The fixed scroll 300 may include a fixed end plate 310 in the form of a disk and a fixed lap 320 protruding from the one side of the fixed end plate 310 so as to converge toward the center, May include a round plate 610 in the form of a disk and a orbiting wrap 620 protruding in a wavy line so as to converge toward the center to face the stationary lap 320 on one side of the orbiting end plate 610.

At this time, the space between the stationary wrap 320 and the orbiting wrap 620 can be divided into a plurality of compression chambers 700 as the stationary wrap 320 and the orbiting wrap 620 come into contact with each other at a plurality of points.

The refrigerant sucked through the outer periphery of the fixed lap 320 and the orbiting lap 620 is confined in the compression chamber 700. The compression chamber 700 moves toward the center while revolving in accordance with revolution of the orbiting scroll 600. Since the volume is reduced during movement, the refrigerant in the compression chamber 700 is compressed to a high pressure in this process.

The compressed refrigerant can be discharged to the high pressure chamber 231 in the cover housing 230 through the discharge port 311 formed at the center of the fixed scroll 300. The refrigerant in the high pressure chamber 231 is discharged to the oil separator (Not shown) and can be supplied to the outside through the discharge port.

A back pressure chamber 800 may be formed between one side of the orbiting end plate 610 facing the rotating shaft 421 and one end of the rotating shaft 421 on the back side of the orbiting scroll 600, The orbiting scroll 500 can be formed over the joining portion between the eccentric portion 500 and the turning end plate 610 and the rotational space of the eccentric portion 500. The orbiting scroll 600 can be formed by the pressure of the back pressure chamber 800, ).

The lubricating oil, which may be contained in the refrigerant compressed at the high pressure in the compression chamber (700), may be recovered while passing through the oil separator before being supplied to the outside through the discharge port. The recovered oil can be guided to the drive motor 400 through an oil passage (not shown) through a pressure reducing device (not shown) to lubricate the second bearing 215. The fixed scroll 300 and the orbiting scroll 600 can be lubricated with the refrigerant as they enter the compression chamber 700 and a part of the refrigerant can be introduced into the back pressure chamber 800 while passing through the compression chamber 700 So that the internal components of the back pressure chamber 800 can be lubricated.

FIG. 3 is a perspective view showing the eccentric portion shown in FIG. 2, FIG. 4 is a perspective view showing a state where the bush and the rotary shaft shown in FIG. 2 are coupled to each other, FIG. 5 is a front view And Fig.

3, the eccentric part 500 includes a coupling part 510 in the form of a circular plate coupled to one end of the rotary shaft 421, and an orbiting part 510 protruding from one surface of the coupling part 510, And a bush 520 in the form of a cylinder eccentrically coupled to one side of the bush 520.

The weight portion 530 may be formed in a semicylindrical shape so as to surround the outer circumferential surface of the rotary shaft 421 from the other surface of the coupling portion 510. At this time, both sides of the coupling portion 510 may be connected to the weight portion 530 in a round manner.

The above-described joint portion 510, the bush 520, and the weight portion 530 that the eccentric portion 500 may include may be integrally formed of the same material or have a structure that is mutually coupled with a separate member . In the illustrated example, an example of the eccentric part 500 integrally formed is shown.

When the eccentric part 500 and the orbiting scroll 600 are engaged, the bush 520 can be supported by the support bearing 521 (see FIG. 2). An eccentric hole 522 spaced from the center of the rotary shaft 421 may be formed through the bush 520 and the coupling part 510. An eccentric hole 522 may be formed in the eccentric hole 522 extending from one side of the orbiting scroll 600, An axis (not shown) may be inserted into the rotation shaft 421 through the eccentric hole 522.

The weight portion 530 can perform a function of offsetting the centrifugal force accompanying the revolution of the orbiting scroll 600. The inner surface of the weight portion 530 may be formed as a curved surface 531 having a semicircular shape and the curved surface 531 may cover a part of the outer circumferential surface of the rotating shaft 421 as shown in FIG.

A rotation tolerance may be formed between the curved surface 531 of the weight portion 530 and the outer peripheral surface of the rotary shaft 421 to prevent breakage of the orbiting scroll 600 due to the liquid refrigerant compression during the initial driving of the compressor 100 have.

In this case, one corner portion of the curved surface 531 of the weight portion 530 is connected to the rotation axis 421 of the rotation axis 421 because the rotation axis 421 is suddenly braked from 0 rpm to several rpm at the time of stopping the operation of the compressor 100. [ An impact sound may be generated by strongly hitting the outer peripheral surface.

4 and 5, in order to reduce such an impact sound, noise is reduced between the inner surface (curved surface 531) of the weight portion 530 facing each other and the outer peripheral surface of the rotary shaft 421, Member 900 is interposed.

Since the rotary shaft 421 and the eccentric part 500 are generally made of steel material, noise due to friction during the relative movement due to the rotation tolerance may be caused. Also, the curved surface 531 of the weight part 530 may be curved, The impact sound when the one corner portion strikes the outer circumferential surface of the rotary shaft 421 is large.

The noise reducing member 900 may include a material capable of reducing such noise, for example, PTFE (Polytetrafluoroethylene) or a plastic material. The noise reducing member 900 can reduce the noise that may be generated due to the corner portion of the curved surface 531 hitting the outer peripheral surface of the rotation shaft 421 by including such a material.

The noise reducing member 900 may be formed in a ring shape as an example. The noise reducing member 900 having such a shape is formed along the circumferential direction on the outer circumferential surface of the rotary shaft 421. At this time, the rotary shaft 421 may be formed with a groove 421a to which the noise reducing member 900 is coupled. The groove 421a may be formed along the circumferential direction on the outer circumferential surface of the rotating shaft 421 and the ring-shaped noise attenuating member 900 may be coupled to the groove 421a to maintain its position on the outer circumferential surface of the rotating shaft 421 have.

On the other hand, the clearance between the curved surface 531 of the weight portion 530 and the noise reduction member 900 becomes the aforementioned rotation tolerance d1. This rotation tolerance d1 is smaller than the clearance d2 between the curved surface 531 and the outer peripheral surface of the rotary shaft 421 so that the edge of the curved surface 531 at the time of stopping the compressor 100 is in direct contact with the outer peripheral surface of the rotary shaft 421 The noise reduction member 900 is brought into contact with the noise reduction member 900 and the noise that may be generated during contact due to the characteristics of the noise reduction member 900 can be reduced.

6 is a front view and an enlarged cross-sectional view showing another example of the noise reducing member shown in Figs. 4 and 5. Fig.

The noise reducing member 900 'of another example shown is formed in a cap shape. The noise reducing member 900 'having such a shape can be put on and coupled to the upper end of the rotation shaft 421.

The noise reduction member 900 'may have a through hole that communicates with the eccentric hole 522 in an upper end portion 901' in the form of a disk. The outer peripheral portion 903 'of the cylindrical noise-reducing member 900' has an axial length that can be interposed between the inner surface of the weight portion 530 and the outer peripheral surface of the rotary shaft 421. At this time, the clearance between the outer peripheral surface of the outer peripheral portion 903 'and the inner surface of the weight portion 530 becomes the rotation tolerance d1.

The noise reducing member 900 'of this example is interposed between the lower surface of the eccentric portion 500 where the upper end portions 901' face each other, specifically, the lower surface of the coupling portion 510 and the upper surface of the rotary shaft 421. Therefore, the friction that may be generated in the relative movement due to the rotation tolerance d1 'between the eccentric portion 500 and the rotary shaft 421 can be reduced, thereby reducing the noise.

The outer peripheral portion 903 'of the noise reducing member 900' is interposed between the inner surface of the weight portion 530 facing each other and the outer peripheral surface of the rotary shaft 421, The same function is performed.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, It is obvious that the modification or the modification is possible by the person.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.

100: Scroll compressor
200: Housing
300: Fixed scroll
400: drive motor
421:
500: Eccentric portion
530:
600: Turning scroll
700: compression chamber
800: back pressure chamber
900,900 ': Noise reduction member

Claims

A fixed scroll (300) fixedly disposed;
A revolving scroll 600 that causes the volume of the compression chamber 700 formed between the fixed scroll 300 and the revolving scroll 300 to change while the refrigerant in the compression chamber 700 is compressed according to the idle motion;
A rotary shaft (421) for transmitting rotational force to orbiting the orbiting scroll (600);
And an eccentric portion that is interposed between the rotary shaft 421 and the orbiting scroll 600 so that the rotary force of the rotary shaft 421 is transmitted to the orbiting scroll 600, and the orbiting scroll is eccentric from the axial center of the rotary shaft 500);
A weight portion 530 formed on one side of the eccentric portion 500 to offset a centrifugal force caused by revolution of the orbiting scroll 600; And
And a noise reduction member (900, 900 ') interposed between the inner surface of the weight portion (530) facing each other and the outer peripheral surface of the rotary shaft (421) to reduce impact noise.

The method according to claim 1,
Wherein the noise reducing member (900) has a ring shape formed along the circumferential direction of the outer peripheral surface of the rotating shaft (421).

The method of claim 2,
A groove 421a is formed along the circumferential direction on the outer peripheral surface of the rotary shaft 421,
Wherein the noise reduction member (900) is coupled to the groove (421a).

The method according to claim 1,
The noise reduction member 900 'is cap-shaped and covers the upper end of the rotation shaft 421. The noise reduction member 900' is disposed between the lower surface of the eccentric part 500 facing each other and the upper surface of the rotation shaft 421, The outer peripheral portion 903 'of the noise reduction member 900' is interposed between the inner side surface of the weight portion 530 facing each other and the outer peripheral surface of the rotation shaft 421 with the upper end portion 901 ' Is interposed between the scroll compressor and the scroll compressor.

The method according to claim 1,
Wherein the noise reduction member (900,900 ') comprises PTFE (Polytetrafluoroethylene) or a plastic material.