KR102024792B1

KR102024792B1 - Scroll compressor

Info

Publication number: KR102024792B1
Application number: KR1020130057326A
Authority: KR
Inventors: 최용규; 김학영; 원인호
Original assignee: 엘지전자 주식회사
Priority date: 2013-05-21
Filing date: 2013-05-21
Publication date: 2019-09-24
Also published as: KR20140136801A

Abstract

The scroll compressor according to the present invention is supported by the pin part of the crankshaft or the inner circumferential surface of the crankshaft by inserting a bush in which the surface receiving centrifugal force, gas force, and gas repulsion force is planar and inserting a surface contact or line contact with the pin part. As the protrusion is formed, the bush is in linear contact with the supporting protrusion, so that even if the pin of the crankshaft is bent, the bush is always in contact with the supporting protrusion, and similar to the reinforced stiffness without increasing the actual shaft diameter of the crankshaft. An effect can be obtained and it can prevent that the swing scroll behavior becomes unstable.

Description

Scroll Compressor {SCROLL COMPRESSOR}

The present invention relates to a scroll compressor, and more particularly to a scroll compressor having a tilting portion in the pin portion of the crankshaft.

The scroll compressor has two fixed chambers in which a fixed scroll is fixed to the inner space of the sealed container and the rotating scroll is engaged with the fixed scroll to move continuously between the fixed scroll of the fixed scroll and the rotating wrap of the rotating scroll. To form a compressor.

Scroll compressors are widely used for refrigerant compression in air conditioners and the like because they have a relatively high compression ratio compared to other types of compressors, and the suction, compression, and discharge strokes of the refrigerant are smooth and stable torque can be obtained.

In addition, the scroll compressor may be classified into a fixed radius type in which the turning scroll always pivots on the same trajectory regardless of the change in the compression condition, and a variable radius type in which the turning scroll may retreat in the radial direction according to the compression condition.

1 is a longitudinal sectional view showing an example of a conventional fixed radius scroll compressor.

As shown in the drawing, the conventional scroll compressor includes a sealed container 1 divided into a suction space 11 having a low pressure part and a discharge space 12 having a high pressure part, and a suction space 11 of the sealed container 1. A drive motor (2) installed at the upper surface of the main frame (3) and the main frame (3) fixedly installed between the suction space (11) and the discharge space (12) of the sealed container (1) and generating rotational force. A fixed scroll (4) fixedly installed in the main frame (3) and the fixed scroll (4) and is installed eccentrically coupled to the crankshaft (23) of the drive motor (2) continuously with the fixed scroll (4) Slewing scroll (5) forming a pair of two moving chamber (P) to move, and the old dam ring is installed between the fixed scroll (4) and the swinging scroll (5) to prevent the rotational movement of the swinging scroll (5) It includes (6).

The main frame 3 has a bearing hole 31 formed therethrough, and a pocket 32 is formed at the upper end of the bearing hole 31 so that the boss portion 53 of the pivoting scroll 5, which will be described later, is pivotally inserted. It is.

A fixing wrap 42 is formed at the bottom of the hard plate portion 41 of the fixed scroll 4, and a suction groove 43 is formed at one side of the hard plate portion 41 of the fixed scroll 4, and a discharge port 44 is formed at the center thereof. Formed.

On the upper surface of the hard plate portion 51 of the turning scroll (5), the turning wrap (52) is formed to engage with the fixed wrap (42) of the fixed scroll (4) to form the compression chamber (P), and the hard plate of the turning scroll (5). The boss portion 53 is formed at the bottom of the portion 51 to be coupled to the crankshaft 23. A bearing 54 is provided on the inner circumferential surface of the boss portion 53 so as to be engaged with the pin portion 23b of the crankshaft 23 to be described later. The bearing 54 has a bush bearing inserted therein or a bearing surface coated.

The crank shaft 23 is eccentrically formed so that the pin portion 23b is eccentrically coupled to the boss portion 53 of the swinging scroll 5 at the upper end of the shaft portion 23a that is pressed into the rotor 22 of the drive motor 2. have.

In the drawings, reference numeral 7 denotes a high and low pressure separator, 13 a suction pipe, 14 a discharge pipe, 21 a stator, and 45 a check valve.

In the conventional scroll compressor as described above, when the power is applied to the drive motor 2, the rotational force is generated, the rotating scroll (5) by the crank shaft 23 coupled to the rotor 22 of the drive motor (2) The two pairs of compression chambers (P) are formed while pivoting about the fixed scroll (4) to suck, compress, and discharge the refrigerant. At this time, the swing scroll 5 may be unstable because the centrifugal force generated during the pivoting motion and the gas force generated while compressing the refrigerant, and the gas repulsion force in the opposite direction of the centrifugal force. However, the swinging scroll 5 is supported by the main frame 3 to continue the swinging movement while being properly adjusted by back pressure or the like.

However, in the conventional scroll compressor as described above, when the compressor is operated under an overload condition, the turning scroll 5 receives a higher gas force, and thus the behavior of the turning scroll 5 becomes unstable. As well as the increase in the axial leakage, as shown in FIG. 2, the pin 23b of the crankshaft 23 is bent and the pin 23b is provided in the boss portion 53 of the turning scroll 5 ( 54) and local friction could cause bearing burnout.

In view of this, the diameter of the crankshaft 23 is increased to increase the axial rigidity, so that the behavior of the turning scroll 5 can be stabilized. In this case, as the diameter of the crankshaft 23 increases, the bearing 54 and In addition to the increase in frictional loss of the compressor, when applied to the shaft-through scroll compressor, there is a problem that the compression efficiency is reduced by reducing the volume of the compression chamber while increasing the inner diameter of the boss portion coupled to the crankshaft.

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor capable of stabilizing the swing scroll behavior without increasing the diameter of the crankshaft, thereby preventing axial leakage and preventing the bearing from being burned out by the crankshaft. I'm trying to.

In order to achieve the object of the present invention, a crank shaft for transmitting a rotational force of the drive motor; A fixed scroll on which a fixed wrap is formed; A pivot scroll formed with a boss portion eccentrically coupled to the crankshaft to make pivot movement, and a pivot wrap formed to engage the fixed wrap to form a compression chamber continuously moving; A bearing provided on an inner circumferential surface of the boss; And a bush provided between the bearing and the crankshaft, wherein at least one first plane is formed on one of an inner circumferential surface of the bush and an outer circumferential surface of the crankshaft, and the other side faces the first plane. A scroll compressor may be provided in which at least two or more second planes are formed.

In addition, the pin portion is formed eccentrically on the upper end of the crankshaft; A boss portion formed in the turning scroll to engage the crank shaft; A bearing provided at the boss portion; And a bush coupled to the pin part and inserted into the bearing, wherein the direction in which the centrifugal force acts and the direction in which gas repulsive force acts are opposed to each other are formed in the plane so as to face each other. The scroll compressor may be provided in which the gas force of the refrigerant to be compressed acts in one of the bushes and the fins, and the other in the plane.

1 is a longitudinal sectional view showing an example of a conventional scroll compressor;
Figure 2 is a longitudinal sectional view showing the instability of the swing scroll in the scroll compressor according to FIG.
3 is a longitudinal sectional view showing one embodiment of the present invention scroll compressor;
4 is an exploded perspective view of the compression unit in the scroll compressor according to FIG. 3;
5 is a longitudinal sectional view showing a compression unit in the scroll compressor according to FIG. 3;
6 is a sectional view taken along the line "II" in FIG. 5;
7 is a longitudinal cross-sectional view showing an unstable state of the turning scroll in the scroll compressor according to FIG.
Figure 8 is a longitudinal cross-sectional view showing an example of applying the bush and the support protrusion to the shaft through scroll compressor according to the present invention.

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

Figure 3 is a longitudinal sectional view showing an embodiment of the scroll compressor of the present invention, Figure 4 is a perspective view showing the compression unit in the scroll compressor according to Figure 3, Figure 5 is a longitudinal sectional view showing a compression section in the scroll compressor according to FIG. 6 is a sectional view taken along the line “II” in FIG. 5.

As shown in the drawing, the scroll compressor of the present embodiment is divided into a suction space 11 having a low pressure part and a discharge space 12 having a high pressure part, and an suction space of the sealed container 1 having an inner space of the sealed container 1. A drive motor 2 for generating a rotational force is installed at 11 and the main frame 3 is fixedly installed between the suction space 11 and the discharge space 12 of the sealed container 1. The fixed scroll 4 is fixedly installed on the upper surface of the main frame 3, and the fixed scroll 4 is eccentrically coupled to the crankshaft 100 of the drive motor 2 between the main frame 3 and the fixed scroll 4. The rotating scroll 5 which forms two pairs of compression chambers P which continuously move together with () may be rotatably installed. In addition, an old dam ring 6 may be installed between the fixed scroll 4 and the revolving scroll 5 to prevent the revolving movement of the revolving scroll 5.

The inner space of the sealed container (1) is fixed to the upper surface of the fixed scroll (4) to the suction space (11) and the discharge space (12) by the high and low pressure separator (7) in close contact with the inner peripheral surface of the sealed container (1) The suction pipe 13 may be coupled to the suction space 11, and the discharge pipe 14 may be coupled to the discharge space 12.

Although not shown in the drawing, the sealed container 1 is provided with a predetermined discharge space sealed and is divided into a suction space, which is a low pressure part, and a discharge space, which is a high pressure part, by a discharge plenum (not shown) fixedly coupled to the fixed scroll 4. May be

The fixed scroll (4) is projected on the bottom surface of the hard plate portion 41 and the fixed wrap (42) is formed to form a compression chamber (P) together with the turning wrap (52) of the turning scroll (5) to be described later, the fixed scroll The suction port 43 may be formed on the outer circumferential surface of the hard plate portion 41 of (4) so that the suction space 11 and the compression chamber P of the sealed container 1 communicate with each other.

A discharge port 44 is formed in the center of the hard plate portion 41 of the fixed scroll 4 so that the compression chamber P and the discharge space 12 of the sealed container 1 communicate with each other. In the normal operation of the compressor, the discharge port 44 is opened, while in the stop of the compressor, the discharge port 44 is closed to prevent the discharged refrigerant from flowing back into the compression chamber P through the discharge port 44. ) Can be installed.

The swinging scroll 5 is projected on the upper surface of the hard plate portion 51 and engaged with the fixed wrap 42 of the fixed scroll 4 to form the two pairs of compression chambers P. The boss part 53 may be formed on the bottom surface of the hard plate part 51 of the turning scroll 5 so that the pin part 120 of the crankshaft 100 may be inserted to receive the rotational force. The bearing 54 may be inserted or coated on the inner circumferential surface of the boss 53. The inner circumferential surface of the bearing 54 may be formed in a circular shape.

The crankshaft 100 is axially coupled to the rotor 22 of the drive motor 2 and protruded eccentrically to the upper end of the shaft portion 100 to the boss portion 53 of the turning scroll (5) It may be made of a pin portion 120 to be coupled.

4 to 6, the pin portion 120 has a smaller cross-sectional area than the shaft portion 110, the direction in which the centrifugal force of the two sides, that is, the turning scroll (5) in the plane projection (hereinafter, centrifugal force direction) ( Fc) and the direction in which the gas repulsion force opposite to the direction of the centrifugal force acts (hereinafter, the gas repulsive force direction) Fr are planes parallel to each other (hereinafter, transversely) in a direction Fθ perpendicular to the centrifugal force and the gas repulsive force. Direction first plane) 121 and 122.

One end of the transverse first planes 121 and 122, that is, the direction in which the gas force acts (hereinafter, the gas force direction) Fθ may support the protrusion protruding toward the second longitudinal plane 213 which will be described later. 123 may be formed. The support protrusion 123 may be formed in a rectangular cross-sectional shape having a curved surface having a semi-circular cross section in front projection and having a length equal to or smaller than the length of the second longitudinal plane 213 in planar projection.

The crankshaft 100 is coupled to the turning scroll 5 between the inner circumferential surface of the boss portion 53, more precisely, between the inner circumferential surface of the bearing 54 and the outer circumferential surface of the crankshaft 100, and more precisely, the outer circumferential surface of the pin portion 120. By turning the scroll (5) can be coupled to the bush 200 to be able to rotate in a fixed radius type.

The outer circumferential surface of the bush 200 may be formed in a circular shape so as to correspond to the inner circumferential surface of the bearing 54, while the inner circumferential surface of the bush 200 may be formed in a shape having a plurality of planes similar to the outer circumferential surface of the pin part 120.

For example, the inner circumferential surface of the bush 200 is a plane (hereinafter referred to as a lateral second plane) parallel to each other toward the gas force direction Fθ which is a direction perpendicular to the centrifugal force direction Fc and the gas repulsive force direction Fr ( 2) can be formed. The transverse second planes 211 and 212 may be formed to be substantially in surface contact with the transverse first planes 121 and 122. In addition, the transverse second planes 211 and 212 may be formed longer than the length of the transverse first planes 121 and 122 by the length of the flow avoiding portion S to be described later.

At one end of the gas force direction Fθ in both ends of the lateral second planes 211 and 212, a plane (hereinafter, referred to as a centrifugal force direction Fc or a gas repulsive force direction Fr) is a direction perpendicular to the gas force. Second longitudinal plane) 213.

On the opposite side of the second longitudinal plane 213, the bushing scroll 5 is pushed in the gas force direction Fθ when the turning scroll 5 receives a high compression chamber pressure (ie, gas force) under an overload condition. When the second longitudinal plane 213 of () is added to the support protrusion 123 of the pin portion 120, the flow avoiding portion (S), which is a space where the pin portion 120 can be bent in the gas force direction (Fθ) Can be formed. Flow avoiding portion (S) may be made at a predetermined interval formed between the inner circumferential surface of the bush 200 and the outer circumferential surface of the pin portion 120. In addition, the inner circumferential surface of the bush 200 and the outer circumferential surface of the fin part 120 forming the flow avoiding part S may be formed in a curved shape facing each other.

Although not shown in the drawings, the support protrusion 123 and the second longitudinal second plane 213 may be formed on the inner circumferential surface of the bush 200 and the outer circumferential surface of the fin part 120, respectively, in contrast to the above-described embodiment. However, even in this case, it may be preferable that the support protrusion protrudes in a direction opposite to the gas force direction Fθ.

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

The scroll compressor according to the present embodiment as described above has the following effects.

That is, when a power is applied to the drive motor 2 and a rotational force is generated, the turning scroll 5 eccentrically coupled to the crankshaft 100 of the driving motor 2 performs the turning movement and the fixed scroll 4 therebetween. Two pairs of compression chambers P are formed in succession. In the compression chamber P, the compression chamber P whose volume gradually decreases from the suction port (or suction chamber) 43 toward the discharge port (or discharge chamber) 44 is formed in successive steps.

Then, the refrigerant provided from the outside of the sealed container 1 flows into the suction space 11, which is the low pressure portion of the sealed container 1, through the suction pipe 13, and the low pressure refrigerant of the suction space 11 is fixed scroll 4. Of the sealed container (1) through the outlet (44) of the fixed scroll (4) in the final compression chamber in the compressed compression while flowing through the suction port 43 of the A series of processes to be discharged to the discharge space 12 is repeated.

Here, the swing scroll 5 may be unstable in response to centrifugal force, gas force, and gas repulsion force in different directions, but at least three surfaces on the pin portion 120 of the crankshaft 100 as in the present embodiment. That is, as the surface receiving the centrifugal force and the gas force and the gas repulsion force form a plane and the bush 200 which is in surface contact or line contact with the pin 120 is inserted, the turning scroll 5 is prevented from being pushed by the gas force. You can do a pivoting movement with a fixed radius. Accordingly, even if the pin portion 120 of the crankshaft 100 is bent by gas force as shown in FIG. 7, the pin portion 120 is positioned as the bush 200 is positioned between the bearing 54 and the pin portion 120. It is possible to prevent the bearing 54 from being burned out by preventing direct friction with the bearing 54.

In addition, when the support protrusion 123 is formed in the pin portion 120 of the crankshaft 100, the second longitudinal plane 213 of the bush 200 is in line contact with the support protrusion 123, and the crank shaft Even if the pin portion 120 of the 100 is bent by a predetermined angle α, the state in which the bush 200 is always in contact with the support protrusion 123 is maintained, thereby changing the actual shaft diameter of the crankshaft 100. A similar effect to that in which the stiffness is reinforced can be achieved without increasing, thereby preventing the swing scroll 5 from becoming unstable, thereby reducing the frictional loss or axial leakage of the swing scroll 5, thereby increasing the compression efficiency.

Meanwhile, in the above-described embodiment, the boss portion is formed to protrude to the rear surface of the turning wrap of the turning scroll by a predetermined height. However, as shown in FIG. 8, the boss portion 53 is the turning wrap 52 of the turning scroll 5. The same applies to a structure overlapping with a), i.e., a shaft-through scroll compressor.

Even in this case, since the basic configuration of the boss portion 53 and the pin portion 120 and the effects thereof are similar to those of the above-described embodiment, a detailed description thereof will be omitted. However, in the present embodiment, the diameter of the boss portion 53 is closely related to the volume of the compression chamber P due to the characteristics of the shaft through which the boss portion 53 is formed at the height overlapping the turning wrap 52. Therefore, when the bush 200 is inserted into the pin portion 120 and coupled to the boss portion 53 like the above-described embodiment without expanding the inner diameter of the boss portion 53 as in the present embodiment, the boss portion 53 is formed. It is possible to stabilize the behavior of the turning scroll 5 without increasing the inner diameter of the. Accordingly, the volume of the compression chamber P can be prevented from being reduced due to the expansion of the inner diameter of the boss portion 53 in the axial through scroll compressor, and the rotational scroll to compensate the volume of the compression chamber P can be prevented. By increasing the outer diameter of (5), it is possible to prevent the compressor from becoming oversized.

4: fixed scroll 41: hard plate portion of fixed scroll
42: fixed wrap 44: discharge port
5: turning scroll 52: turning wrap
53: boss 54: bearing
100: crankshaft 110: shaft portion
120: pin part 121,122: transverse first plane
123: support protrusion 200: bush
211,212: transverse second plane 213: longitudinal second plane
S: flow space part

Claims

A crank shaft which transmits the rotational force of the driving motor and is formed to be eccentric with respect to the axial center of the pin portion protruding in the axial direction at one end thereof;
A fixed scroll on which a fixed wrap is formed;
A swing scroll having a boss portion coupled to the pin portion of the crankshaft to make a swing movement, and a swing wrap being formed to form a compression chamber continuously engaged with the fixed wrap;
A bearing provided on an inner circumferential surface of the boss; And
And a bush provided between the bearing and the crankshaft.
One of an inner circumferential surface of the bush and an outer circumferential surface of the pin portion of the crankshaft is provided with a support protrusion protruding toward the outer circumferential surface of the pin portion or the inner circumferential surface of the bush, which is opposite to each other.
The axial length of the support protrusion is formed to be shorter than the axial length of the pin portion is provided with the end of the pin portion or the end of the bush facing the same.

The method of claim 1,
And the boss portion is formed to protrude to the opposite side of the pivoting wrap so as not to overlap the pivoting wrap in the axial direction.

The method of claim 1,
The boss portion is formed so as to overlap the pivot wrap in the axial direction so that the pin portion is coupled through the hard plate portion of the swing scroll.

delete

The method of claim 1,
The support protrusion is a scroll compressor that is formed to face the direction in which the gas force acts.

The method of claim 1,
And a flow avoiding part is formed at regular intervals between an inner circumferential surface of the bush and an outer circumferential surface of the fin part on the opposite side of the support protrusion.

The method of claim 1,
The support protrusion is a scroll compressor that is formed in a curved shape during front projection.

The method of claim 8,
The axial length of the support protrusion is formed to be 1/2 or less than the axial length of the pin portion.

The method according to any one of claims 1 to 3, 6 to 9,
Among the inner circumferential surface of the bush and the outer circumferential surface of the fin part, the direction in which the centrifugal force acts and the direction in which the gas repulsive force acts are formed in a plane so as to face each other, and the direction in which the gas force of the refrigerant to be compressed is applied is in the bush or the fin part. Scroll compressor, one of which is curved and the other is flat.