KR20140086606A

KR20140086606A - Compressor

Info

Publication number: KR20140086606A
Application number: KR1020120157301A
Authority: KR
Inventors: 용민철; 사범동; 이윤희
Original assignee: 엘지전자 주식회사
Priority date: 2012-12-28
Filing date: 2012-12-28
Publication date: 2014-07-08

Abstract

The present invention relates to a compressor. The compressor according to the present invention includes a cylinder which has an outer cylinder part, an inner cylinder part and a vane part for connecting the outer cylinder part and the inner cylinder part with each other and is fixed to a casing. Moreover, a rolling piston is connected to the vane part to be able to slide in order to form an outer compression space and an inner compression space while carrying out a turning motion between the outer cylinder part and the inner cylinder part. Therefore, the compressor can reduce power loss in comparison with the same cooling capacity by reducing weight of a rotor, can reduce refrigerant leak because a bearing area is narrow, and can easily expand and change capacity of the cylinder. Furthermore, the compressor can reduce vibration and noise because refrigerants in each of the compression spaces are discharged in the opposite directions. Additionally, the compressor can enhance reliability and enhance performance by reducing a dead capacity because a curved reinforcing part is formed at a part where the outer cylinder part and the vane part or the inner cylinder part and the vane part get in contact with each other.

Description

COMPRESSOR

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor, and more particularly to a one-cylinder-two compression chamber compressor in which two compression spaces are formed in one cylinder.

Generally, a compressor is applied to a vapor compression type refrigeration cycle such as a refrigerator or an air conditioner (hereinafter abbreviated as a refrigeration cycle). The refrigerant compressor has been introduced with a constant-speed compressor driven at a constant speed or an inverter-type compressor controlled in rotation speed.

The compressor is generally referred to as a closed compressor in the case where the compression section operated by the transmission section which is a motorized section and the compression section operated by the transmission section are provided together in the internal space of the closed casing and the case where the transmission section is separately provided outside the casing is referred to as an open compressor have. Most of the refrigeration appliances for home use or commercial use are hermetically sealed compressors.

A hermetic compressor can be classified into a single-type hermetic compressor and a double-hermetic type compressor according to the number of cylinders. In the hermetically sealed compressor, one cylinder having one compression space is provided inside the casing, while the double-hermetically sealed compressor has a plurality of cylinders having one compression space inside the casing.

Compressed air compressors can be divided into 1 suction-2 discharge system and 1 suction-1 discharge system depending on the method of compressing the refrigerant. In the one suction-1 discharge mode, the accumulator is connected to the first cylinder through the primary suction flow path, and the second cylinder is connected to the discharge side of the first cylinder connected to the accumulator through the secondary suction flow path, And then discharged into the inner space of the casing. On the other hand, the one suction-2 discharge system is a system in which a plurality of cylinders are branched and connected to one suction pipe, and refrigerant is respectively compressed in a plurality of cylinders and discharged into the inner space of the casing.

1 is a longitudinal sectional view showing a rotary compressor of a conventional 1 suction-2 discharge type. As shown in the figure, the rotary compressor of the conventional one-suction-two-discharge type has a transmission portion 2 in the casing 1 and a compression portion 3 on the lower side of the transmission portion 2 have. The transmission section (2) and the compression section (3) are mechanically connected by a crankshaft (23). 21 denotes a stator, and 22 denotes a rotor.

The compression section 3 is fixed to the casing 1 at a predetermined interval between the main bearing 31 and the sub bearing 32 so as to support the crankshaft 23 and the main bearing 31 and the sub bearing 32 A first cylinder 34 and a second cylinder 35 separated by an intermediate plate 33 are provided.

The intermediate plate 33 is provided with a suction port 33a to which the suction pipe 11 is connected and the compression space V1 of the first cylinder 34 and the compression chamber V2 A first suction groove 33b and a second suction groove 33c communicating with each other are formed.

The first eccentric portion 23a and the second eccentric portion 23b are formed in the crankshaft 23 along the axial direction at an interval of about 180 占 and the first eccentric portion 23a and the second eccentric portion 23b A first rolling piston 36 and a second rolling piston 37 for compressing the refrigerant are respectively coupled to the outer circumferential surface of the first rolling piston 36 and the second rolling piston 37. The first and second cylinders 34 and 35 are respectively pressed against the first and second rolling pistons 36 and 37 to form a first compression space V1 and a second compression space V2, A first vane (not shown) and a second vane (not shown) are coupled to the suction chamber and the compression chamber. Reference numeral 5 denotes an accumulator, reference numeral 12 denotes a discharge pipe, and reference numerals 31a and 31b denote discharge ports.

When the power source is applied to the electric motor 2 and the rotor 22 and the crankshaft 23 of the electric motor 2 are rotated, the conventional 1-intake- The rolling piston 36 and the second rolling piston 37 pivotally move the refrigerant into the first cylinder 34 and the second cylinder 35 alternately. The refrigerant is compressed by the first rolling piston 36, the first vane, the second rolling piston 37 and the second vane so that the discharge ports 31a provided in the main bearing 31 and the sub- And then discharged into the inner space of the casing 1 through the first opening 31b.

However, in the above-described conventional 1-intake-2 discharge type rotary compressor, the first eccentric portion 23a and the second eccentric portion 23b are arranged at a predetermined distance in the longitudinal direction of the crankshaft 23 The moment due to the eccentric load is increased, and the vibration and the friction loss of the compressor are increased. In addition, it is also possible to separate the suction chamber and the compression chamber from each other by the pressure of the respective vanes pressed against the respective rolling pistons 36, 37 and, depending on the operating conditions, the vanes and the respective rolling pistons 36, 37 are separated from each other, The efficiency of the compressor could be lowered.

In view of this, conventionally, as disclosed in Korean Patent No. 10-0812934, a 1-cylinder-2 compression chamber type rotary compressor having two compression spaces in one cylinder has been introduced. FIG. 2 is a longitudinal sectional view showing one embodiment of a conventional 1-cylinder-2 compression chamber rotary compressor, and FIG. 3 is a transverse sectional view showing a cylinder and a piston in a 1-cylinder-2 compression chamber type compressor according to FIG.

2, a conventional 1-cylinder-2 compression chamber type rotary compressor (hereinafter abbreviated as a 1-cylinder-2 compression chamber compressor) has a first compression space V1 And a second compression space V2 are formed. The cylinder 43 is coupled to the eccentric portion 23c of the crankshaft 23 and pivots about the piston 44 so that the piston 44 is engaged with the upper housing 41, And is slidably coupled between the upper housing 42 and the lower housing 42.

A suction port 41a having an elongated hole shape is formed at one side of the upper housing 41 so as to communicate with the respective suction chambers of the first compression space V1 and the second compression space V2. The first discharge port 41b and the second discharge port 41c are formed so as to communicate with the respective compression chambers of the first compression space V1 and the discharge space S2.

3, the cylinder 43 includes an outer cylinder portion 45 forming a first compression space V1, an inner cylinder portion 46 forming a second compression space V2, And a vane portion 47 connecting the cylinder portion 45 and the inner cylinder portion 46 to separate the suction chamber and the compression chamber. The outer cylinder portion 45 and the inner cylinder portion 46 are formed in an annular shape, and the vane portion 47 is formed in a vertically erected flat plate shape.

The inner diameter of the outer cylinder portion 45 is formed to be larger than the outer diameter of the piston 44 and the outer diameter of the inner cylinder portion 46 is formed to be smaller than the inner diameter of the piston 43, And the outer circumferential surface of the inner cylinder portion 46 contacts the inner circumferential surface of the piston 43 at one point to form the first compression space V1 and the second compression space V2, respectively.

The piston 44 is formed in an annular shape and a bush groove 44a is formed such that the vane portion 47 of the cylinder 43 is slidably inserted. A bush 48 is provided. The rolling bush 48 is disposed such that the semicircular suction side bush 48a and the discharge side bush 48b are in contact with the vane portion 47 on both sides of the vane portion 47. [

In the conventional one-cylinder-two compression seal compressor as described above, the cylinder 43 coupled to the crankshaft 23 pivots with respect to the piston 44 and compresses the refrigerant in the first compression space V1 and the second compression The refrigerant sucked into the space V2 is compressed by the outer cylinder portion 45 and the inner cylinder portion 46 and the vane portion 47 to be supplied to the first discharge port 41b and the second discharge port 41c, To the internal space of the casing 1 through the opening portion of the casing 1.

Thereby, the first compression space (V1) and the second compression space (V2) are disposed adjacent to each other on the same plane, and the moment and the friction loss can be reduced. In addition, since the vane portion 47 separating the suction chamber and the compression chamber is integrally coupled to the outer cylinder portion 45 and the inner cylinder portion 46, the sealing property of the compression space can be improved.

However, in the conventional one-cylinder-two compression seal compressor as described above, since the piston 44 is fixed and the cylinder 43 rotates, there is a large power loss compared to the same cooling power and a large bearing area, There was an increasing problem.

In order to change the volume of the cylinder 43 as a part of the outer circumferential surface of the cylinder 43 is closely contacted with the inner circumferential surface of the upper housing 41 to perform the orbiting motion, the conventional one- The size of the casing 1 itself must be enlarged and changed, which makes it difficult to adjust the volume of the compressor.

In the conventional one-cylinder-two compression chamber compressor, since the first discharge port 41b and the second discharge port 41c are formed in the same direction, the refrigerant discharged first causes a kind of pulsation phenomenon in the discharge space S2 The vibration noise of the compressor is increased.

In the conventional one-cylinder-two compression chamber compressor, the portion where the outer cylinder portion 43a and the vane portion 43c or the inner cylinder portion 43b and the vane portion 43c are in contact with each other is linearly contacted, There is a problem that the rigidity is lowered or broken while being subjected to concentrated load in the compression process, and a carcass occurs at a portion where the cylinder portions 43a, 43b and the vane portion 43c are in contact with each other.

It is an object of the present invention to provide a compressor capable of reducing the refrigerant leakage by reducing the weight of the rotating body and having a small power loss compared to the same cooling power and a small bearing area.

Another object of the present invention is to provide a compressor which can easily expand and change the volume of a cylinder.

Another object of the present invention is to provide a compressor capable of reducing vibration noise by buffering refrigerant discharged from each compression space.

Another object of the present invention is to provide a compressor capable of preventing the load from being concentrated or damaged at a portion where the cylinder portion and the vane portion are in contact with each other and reducing the dead volume.

In order to achieve the object of the present invention, A crankshaft for transmitting a rotational force of a driving portion provided in the casing; A plurality of bearing plates for supporting the crankshaft; A cylinder coupled between the bearing plates and having an outer cylinder portion and an inner cylinder portion connected to a vane portion to form a compression space; And a rolling piston slidably coupled to the vane portion between the outer cylinder portion and the inner cylinder portion and separating the compression space into an outer compression space and an inner compression space while pivotally moving by the crankshaft, A reinforcing portion is formed at a portion where the vane portion is in contact with the outer cylinder portion or the inner cylinder portion, and the reinforcing portion is formed of a first curved surface having a predetermined curvature radius.

The rotary compressor of the one-cylinder-two compression chamber type according to the present invention is characterized in that a cylinder having an outer cylinder portion and an inner cylinder portion is fixed and the rolling piston is swung in the cylinder, It is possible to reduce the possibility that the refrigerant leaks due to a small power loss compared to the same cooling power and a small bearing area.

In addition, since the cylinder is fixed and the rolling piston is pivotally moved, a protruding portion is formed on one side of the outer circumferential surface of the outer cylinder portion, so that a clearance space is formed between the inner circumferential surface of the casing and the outer circumferential surface of the cylinder, The diameter can be enlarged and the volume of the cylinder can easily be enlarged and changed.

Since the first discharge port communicating with the outer compression space and the second discharge port communicating with the inner compression space are formed in opposite directions to each other, the discharged refrigerant is buffered with respect to each other to reduce the pulsation phenomenon, thereby reducing the vibration noise of the compressor have.

In addition, since the curved reinforcing portion is formed at the portion where the outer cylinder portion and the vane portion or the inner cylinder portion and the vane portion are in contact with each other, it is possible to prevent a portion in contact therewith from being subjected to a concentrated load or being damaged during the compression process, The end of the bush groove opening or the rolling bushing of the cylinder bushing is curved so that the portion where the cylinder portion and the vane portion are in contact with each other is prevented from interfering with the rolling piston or the rolling bushing to improve the reliability of the compressor, .

1 is a longitudinal sectional view showing a rotary compressor of the conventional 1 suction-2 discharge system,
2 is a vertical cross-sectional view showing one embodiment of a conventional 1-cylinder-2 compression chamber type rotary compressor,
Fig. 3 is a cross-sectional view taken along the line "II" in Fig. 2,
4 is a longitudinal sectional view showing a rotary compressor of a one-cylinder-two compression chamber type according to the present invention,
FIG. 5 is a perspective view of the compression unit of FIG. 4,
Fig. 6 is a sectional view taken along line II-II in Fig. 4,
7 is a cross-sectional view taken along the line "III-III" in Fig. 6,
8 is a plan view showing an enlarged view of the portion "A" in Fig. 6,
9 is a cross-sectional view showing the compression process of the outer compression space and the inner compression space in FIG.

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

FIG. 4 is a longitudinal sectional view showing a rotary compressor of a one-cylinder-two compression chamber type according to the present invention, FIG. 5 is a perspective view showing decompression of a compression part in the compressor of FIG. 7 is a cross-sectional view taken along the line "III-III" in Fig. 6, and is a vertical sectional view showing a compressed portion, and Fig. 8 is a plan view showing an enlarged view of the portion "A"

As shown in the drawings, the rotary compressor of the one-cylinder-two compression chamber type according to the embodiment of the present invention is provided with a transmission portion 2 for generating a driving force in the internal space of the casing 1, A compression unit 100 having two compression spaces V1 and V2 can be installed in one cylinder.

The electromotive section 2 includes a stator 21 fixed to the inner circumferential surface of the casing 1, a rotor 22 rotatably inserted into the stator 21, And a crankshaft 23 coupled to transmit the rotational force to a rolling piston 140 to be described later.

The stator 21 can be formed by lamination of a ring-shaped steel sheet laminated on the casing 1 and then fixedly coupled to the casing 1, and the coil C is wound on the lamination.

The rotor 22 can be formed by inserting a permanent magnet (not shown) into a lamination in which a ring-shaped steel sheet is laminated.

The crankshaft 23 may be formed as a rod having a predetermined length and an eccentric portion 23a projecting radially and eccentrically from the lower end of the crankshaft 23 so that the rolling piston 140 is coupled eccentrically.

The compression unit 100 includes an upper bearing plate 110 and a lower bearing plate 120 which are disposed at predetermined intervals in the axial direction and support the crankshaft 23, A cylinder 130 which is provided between the upper bearing 110 and the lower bearing 120 to form a compression space V and a cylinder 130 which is coupled to the crankshaft 23 and rotates in the cylinder 130, V, which compresses the refrigerant.

The upper bearing 110 is tightly welded to the inner circumferential surface of the casing 1 and the lower bearing 120 can be bolted to the upper bearing 110 together with the cylinder 130.

The upper bearing 110 has a first discharge port 112a communicated with a first compression space V1 to be described later and a second discharge port 112a communicated with a second compression space V2 122a may be formed. A discharge cover 150 may be coupled to the upper bearing 110 to receive the first discharge port 112a and a lower chamber 160 may be coupled to the lower bearing 120 to receive the second discharge port 122a . A discharge passage F that sequentially passes through the lower bearing 120, the cylinder 130 and the upper bearing 110 is formed so that the inner space of the lower chamber 160 and the inner space of the discharge cover 150 can communicate with each other have.

The upper bearing 110 and the lower bearing 120 are formed in an annular shape so that bearing water portions 111 and 121 having shaft holes 111a and 121a are formed at the center, respectively.

The inner diameter D1 of the shaft hole 111 of the upper bearing 110 may be larger than the inner diameter D2 of the shaft hole 121 of the lower bearing 120. [ That is, since the crankshaft 23 is mainly supported by the upper bearing 110 near the center of the eccentric load, the diameter of the portion contacting the upper bearing 110 is larger than the diameter of the portion contacting the lower bearing 120 . Accordingly, it is preferable that the second discharge port 122a located relatively inward of the first discharge port 112a and the second discharge port 122a is formed in the lower bearing 120 because it does not invade the bearing portion of the bearing .

For example, if the second discharge port is formed in the upper bearing 110, the second discharge port must penetrate the bearing portion 111 of the upper bearing 110 having a relatively large outer diameter, so that the bearing strength may be reduced accordingly . Accordingly, in order to compensate for the bearing strength as much as the second discharge port is affected, the bearing portion 111 of the upper bearing 110 must be longer, and the compressor can be made larger. Therefore, it is preferable that the second discharge port 122a is formed in the lower bearing 120 having a relatively small outer diameter of the bearing water portion, because the second discharge port can be formed without invading the bearing water portion 121.

5 and 6, the cylinder 130 includes an outer cylinder part 131 formed in an annular shape and a plurality of protrusions 132 formed at a predetermined interval in the radial direction so as to form a compression space V inside the outer cylinder part 131 The first compression space V1 and the second compression space V2 are connected to each other in the suction direction and the second compression space V2 is connected to the inner cylinder part 132 in the radial direction, And a vane portion 133 for separating the chamber and the compression chamber. The vane portion 133 may be formed between the first suction port 131b and the first discharge port 112a, which will be described later.

4, the outer cylinder portion 131 may have an outer diameter smaller than the inner diameter of the casing 1, so that the outer cylinder portion 131 may have a smaller outer diameter than the inner diameter of the casing 1, It is preferable that the bolts B1 are fastened between the bearings 110 and the lower bearing 120 to prevent thermal deformation of the cylinder. A part of the outer cylinder part 131 is formed in an arc shape so as to be in close contact with the inner circumferential surface of the casing 1 and is radially penetrated into the projecting and retreating part 131a, The first suction port 131b communicating with the first suction port 131b may be formed. A refrigerant suction pipe 11 connected to the accumulator 5 may be inserted into the first suction port 131b.

The outer cylinder portion 131 is formed to have a height such that the upper surface and the lower surface thereof closely contact the upper bearing 110 and the lower bearing 120, and a plurality of fastening holes 131c are formed at predetermined intervals along the circumferential direction And a plurality of discharge guide holes 131d forming a discharge passage F may be formed between the fastening holes 131c.

The inner cylinder portion 132 may have a shaft hole 132a formed at its center so that the crank shaft 23 is rotatably coupled. The center of the shaft hole 132a of the inner cylinder portion 132 may be formed to coincide with the center of rotation of the crankshaft 23. [

The height H2 of the inner cylinder part 132 may be lower than the height H1 of the outer cylinder part 131. The lower surface of the inner cylinder part 132 is formed in the same plane as the lower surface of the outer cylinder part 131 so as to be in contact with the lower bearing 120 while the upper surface of the inner cylinder part 132 is connected to the drive transmission part 142 of the rolling piston 140, The upper bearing 110 can be inserted at a height that can be inserted between the upper bearing 110 and the upper bearing 110.

The cylinder 130 is coupled with the fastening hole 112b of the upper bearing 110 and the fastening hole 112b of the lower bearing 120 through the fastening hole 131c formed in the outer cylinder portion 131 of the cylinder 130. [ 122b with bolts B1.

5 to 7, the vane portion 133 has a predetermined thickness so as to connect between the inner circumferential surface of the outer cylinder portion 131 and the outer circumferential surface of the inner cylinder portion 132, .

A stepped portion 133a is formed on the upper surface of the vane portion 133 so that the drive transmission portion 142 of the rolling piston 140 to be described later overlaps the inner cylinder portion 132 and a part of the vane portion 133 . Therefore, when the first vane portion 135 is referred to as the first vane portion 135 from the outer connecting end 133b to the step 133a and the second vane portion 136 from the inner connecting end 133c to the step 133a, The axial height of the first vane portion 135 is the same as the axial height H1 of the outer cylinder portion 131 and the axial height of the second vane portion 136 is the axial height of the inner cylinder portion 132 H2. &Lt; / RTI >

The outer connecting end 133b and the inner connecting end 133c of the vane portion 133 may be provided with a reinforcing portion 137 for reinforcing the thickness of the connection end and reducing the concentrated load. As shown in FIG. 8, the reinforcing portion 137 is formed of a first curved surface 137a having a predetermined radius of curvature, which can reduce the concentrated load and can prevent interference with the rolling piston 140 and the rolling bush 170 Can be prevented.

The radius of curvature? Of the reinforcing portion 137 can be formed within a range of 0.03 x R??? 0.65 x R. Where R is the design radius of the rolling bush.

The minimum radius of curvature and the maximum radius of curvature of the reinforcing portion 137 are values set through a structural analysis result for the vane portion 133. That is, the minimum radius of curvature of the reinforcing portion 137 is determined by multiplying the design radius of the rolling bush 170 by 0.03. As a result of the structural analysis, the strength is reinforced by about 120% or more as compared with the case where the reinforcing portion 137 is not provided . Based on this, the minimum radius of curvature of the reinforcement portion was determined as described above.

The radius of curvature of the reinforcing portion 137 may be set to be within a range that can not be interfered with the rolling piston 140 or the rolling bush 170 Respectively. In this case, a second curved surface 145c is formed on the opening end 145a of the bush groove 145 of the rolling piston 140, and a third curved surface 171a (not shown) is provided on the end of the rolling bushing 170 The maximum radius of curvature of the reinforcing portion 137 is determined. In particular, when the rolling piston 140 reaches the top dead center or bottom dead center, it should not interfere with the reinforcement 137 of the third curved surface 171a (not shown) of the rolling bush 170, The radius of curvature c of the third curved surface 171a (not shown)

Lt; / RTI >

Here, t is the thickness of the vane portion.

5 to 7, the rolling piston 140 has a piston 141 disposed between the outer cylinder portion 131 and the inner cylinder portion 132, and a piston portion 141 extending from the upper inner peripheral surface of the piston portion 141, And a drive transmitting portion 142 coupled to the eccentric portion 23c of the shaft 23.

The outer diameter of the piston portion 141 is formed to be smaller than the inner diameter of the outer cylinder portion 131 so that the first piston portion 141 is formed on the outer side of the piston portion 141, The inner diameter of the piston portion 141 is formed to be larger than the outer diameter of the inner cylinder portion 132 so that the second compression space V2 can be formed on the inner side of the piston portion 141. [

A second suction port 141a penetrating from the outer circumferential surface of the piston portion 141 to the inner circumferential surface and communicating the first suction port 131b and the second compression space V2 is formed and one side of the second suction port 141a, Between the second suction port 141a and the second discharge port 122a formed in the lower bearing 120, the vane portion 133 is slidably inserted through the rolling bush 140, which will be described later, 145 may be formed.

The bush groove 145 has an approximately circular shape and an outer opening surface 145a which is a discontinuous surface in the outer peripheral surface and the inner peripheral surface of the piston portion 141 so that the vane portion 133 can be penetrated in the radial direction of the bush groove 145, And the inner opening surface 145b may be formed.

A vane portion 133 is inserted in a radial direction of the bush groove 145 and a suction side bush 171 and a discharge side bush 172 of the rolling bush 170 are inserted into both sides of the vane portion 133 And can be rotatably coupled. The rolling bushes 170 can be engaged such that the flat surfaces thereof slide on both sides of the vane portion 133 and the round surfaces slide on the main surface of the bush groove.

The drive transmitting portion 142 may be formed in the shape of an annular plate having an eccentric portion hole 142a such that the eccentric portion 23a of the crankshaft 23 is engaged. A predetermined depth is formed between the eccentric portion hole 142a of the drive transmission portion 142 and the upper surface of the drive transmission portion 142 so as to form a back pressure space between the upper surface of the drive transmission portion 142 and the bearing surface of the upper bearing 110 The stepped groove 142b having a width can be stepped. Although not shown in the drawings, the stepped groove may be formed on the axial bearing surface 112c of the upper bearing 110. [

In the drawing, reference numerals 181 and 182 denote first and second discharge valves, respectively.

The rotary compressor of the 1 cylinder-2 compression chamber type according to the present embodiment as described above is operated as follows

When the rotor 22 is rotated together with the crankshaft 23 by applying power to the coil C of the transmission portion 2, the rolling piston 23, which is coupled to the eccentric portion 23c of the crankshaft 23, The first cylinder 140 is supported by the upper bearing 110 and the lower bearing 120 and is guided by the vane portion 133 to pivotally move between the outer cylinder portion 131 and the inner cylinder portion 132, The space V1 and the second compression space V2 are alternately formed.

9 (a) and 9 (b), when the rolling piston 140 opens the first suction port 131b of the outer cylinder part 131, the refrigerant flows through the first suction port 131b Is sucked into the suction chamber of the first compression space (V1) and is compressed while moving toward the compression chamber of the first compression space (V1) by the swing motion of the rolling piston (140) the first discharge valve 181 is opened and discharged to the inner space of the discharge cover 150 through the first discharge port 112a as shown in FIG. At this time, although the upper surface of the vane portion 133 is formed to be stepped, the rolling chamber 170 blocks the suction chamber and the compression chamber of the second compression space V2, thereby preventing the refrigerant from leaking.

9 (c) and 9 (d), when the rolling piston 140 opens the second suction port 141a, the refrigerant flows through the first suction port 131b and the second suction port 141a, Is sucked into the suction chamber of the compression space V2 and is compressed by the rolling piston 140 while moving toward the compression chamber of the second compression space V2 and this refrigerant is compressed as shown in FIGS. 9A and 9B The second discharge valve 182 is opened and discharged to the lower chamber 160 through the second discharge port 122a and the refrigerant moves to the inner space of the discharge cover 150 through the discharge flow path F, 1) into the inner space of the inner tube.

In the rotary compressor of the 1 cylinder-2 compression chamber type according to the present embodiment as described above, since the cylinder 130 is fixed and the rolling piston 140 rotates inside the cylinder 130, Compared to the case of rotating the compressor, the power loss with respect to the same cooling power is small, and the bearing area is narrow, so that the possibility that the refrigerant leaks may be reduced.

In this embodiment, the cylinder 130 is fixed and the rolling piston swings, while a protrusion 131a is formed on one side of the outer circumferential surface of the outer cylinder part 131, so that the inner circumferential surface of the casing 1 and the cylinder 130 The diameter of the cylinder 130 can be enlarged by using the margin space S and the volume of the cylinder 130 can easily be enlarged and changed through the margin space S .

Also, in this embodiment, since the first discharge port 112a and the second discharge port 122a are formed in opposite directions, refrigerant discharged from the compressor is buffered to reduce the pulsation phenomenon, thereby reducing vibration noise of the compressor.

The reinforcing portion 137 having a predetermined radius of curvature is formed at a portion where the outer cylinder portion 131 or the inner cylinder portion 132 and the vane portion 133 are in contact with each other, The rolling load of the rolling piston 140 and the rolling bush 170 may be curved so that the rolling load applied to the rolling piston 140 is reduced. Or the rolling bush 170 is prevented from interfering with the reinforcement 137, thereby improving the reliability of the compressor and improving the performance of the compressor through the reduction of the carcass.

1: casing 2:
23: crank shaft 23c: eccentric portion
100: compression section 110: upper bearing
112a: First discharge port 120: Lower bearing
122a: second discharge port 130: cylinder
131: outer cylinder part 131a:
131b: first intake port 132: inner cylinder part
133: Vane portion 137a: First curved surface
140: Rolling piston 141: Piston part
142: drive transmitting portion 145: bush groove
145c: second curved surface 171,172: rolling bush
171a: third curved surface V1, V2: outer side, inner compression space

Claims

Casing;
A crankshaft for transmitting a rotational force of a driving portion provided in the casing;
A plurality of bearing plates for supporting the crankshaft;
A cylinder coupled between the bearing plates and having an outer cylinder portion and an inner cylinder portion connected to a vane portion to form a compression space; And
And a rolling piston slidably coupled to the vane portion between the outer cylinder portion and the inner cylinder portion and separating the compression space into an outer compression space and an inner compression space while pivotally moving by the crankshaft,
A reinforcing portion is formed at a portion where the vane portion is in contact with the outer cylinder portion or the inner cylinder portion,
Wherein the reinforcing portion is formed of a first curved surface having a predetermined curvature radius.

The method according to claim 1,
Wherein the rolling piston is formed with a bush groove having an opening so that the vane portion of the cylinder is slidably inserted, the bush groove is rotatably coupled to the rolling bush to induce the rolling motion of the rolling piston,
Wherein an opening end of the bush groove is formed of a second curved surface having a predetermined radius of curvature so as to correspond to a first curved surface of the reinforcing portion.

3. The method of claim 2,
Wherein the curvature radius of the first curved surface is larger than the curvature radius of the second curved surface.

The method according to claim 1,
Wherein the rolling piston is formed with a bush groove having an opening so that the vane portion of the cylinder is slidably inserted, the bush groove is rotatably coupled to the rolling bush to induce the rolling motion of the rolling piston,
Wherein the rolling bush is formed in a semicircular cross-sectional shape, and both ends of the flat surface are formed with a third curved surface having a predetermined radius of curvature so as to correspond to the first curved surface of the reinforcing portion.

5. The method of claim 4,
Wherein a radius of curvature of the first curved surface is formed larger than a radius of curvature of the third curved surface.

2. The apparatus according to claim 1,
A first vane portion connected to an inner circumferential surface of the outer cylinder portion; And
And a second vane portion connected to an outer circumferential surface of the inner cylinder portion,
Wherein the first vane portion and the second vane portion are connected to each other at different heights and a stepped portion is formed at a connecting point thereof.

The rolling piston according to claim 1,
A piston portion formed in an annular shape and disposed between the outer cylinder portion and the inner cylinder portion; And
And a drive transmission portion extending from the piston portion in a plate shape and coupled to an eccentric portion of the crankshaft,
And the bush grooves are formed in the piston portion.

8. The method according to any one of claims 1 to 7,
The curvature radius (?) Of the reinforcing portion
0.03 x R??? 0.65 x R.
Where R is the design radius of the rolling bush.

9. The method of claim 8,
The radius of curvature (c) of the end of the rolling bushing

Lt; RTI ID = 0.0 > of: < / RTI >
Here, t is the thickness of the vane portion.