KR20140086482A

KR20140086482A - Compressor

Info

Publication number: KR20140086482A
Application number: KR1020120157040A
Authority: KR
Inventors: 설세석; 조국현; 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. According to the present invention, a cylinder comprises an outer cylinder part, an inner cylinder part, and a vane part to connect the outer cylinder part and the inner cylinder part and, is fixed to a casing. Furthermore, a rolling piston is connected to slide in the vane part and rotated between the outer cylinder part and the inner cylinder part to form an outer compression space and an inner compression space. The refrigerant leakage can be reduced as the power loss in comparison with same cooling capacity is small by reducing the weight of a rotator and a bearing area is small. The volume of a cylinder is easily changed to be enlarged. Furthermore, vibration noise of a compressor can be reduced as a refrigerant is discharged to the opposite side in the compression space. The refrigerant leakage which may occur as the rolling piston is transformed is prevented by appropriately setting an inner diameter of an inlet of the rolling piston. An appropriate suction amount of the refrigerant can be secured.

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 drawing, reference numerals 43a and 44a denote side inlet ports.

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, if the inner diameters of the suction ports 41a, 43a and 44a are too large, the member having the suction port may be deformed to allow the refrigerant to leak, while the suction ports 41a and 43a 44a is too small, the suction amount of the refrigerant may be reduced and the performance of the compressor may be deteriorated.

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 a refrigerant leakage due to deformation of a member and a reduction in refrigerant suction amount by setting an appropriate standard of the suction port.

In order to accomplish the object of the present invention, there is provided an air conditioner comprising: a casing to which a suction pipe is connected; 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 fixedly coupled between the bearing plates and connected to the outer cylinder portion and the inner cylinder portion by 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, And a second suction port communicating with the first suction port and the inner compression space is formed in the outer surface of the rolling piston, the outer piston having a first suction port penetrating from the outer circumferential surface to an inner circumferential surface and coupled to the suction pipe, Is provided.

A cylinder having an annular outer cylinder part and an inner cylinder part formed at a predetermined interval in the radial direction and a vane part connecting the outer cylinder part and the inner cylinder part in a radial direction; And a piston portion slidably coupled to the vane portion between the outer cylinder portion and the inner cylinder portion to separate the compression space between the outer cylinder portion and the inner cylinder portion into an outer compression space and an inner compression space, And a drive transmission portion extending from the crankshaft and eccentrically coupled to the center of the axis of the crankshaft; And a rolling bush which is rotatably inserted into the rolling piston and is slidably coupled to both sides of the vane portion, wherein a suction port for guiding the refrigerant to the inner compression space is formed in the piston portion of the rolling piston from an outer circumferential surface to an inner circumferential surface A compressor is provided.

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, by appropriately setting the inner diameter of the suction port provided in the rolling piston, the inner diameter of the suction port is too large to prevent the refrigerant from leaking due to deformation of the rolling piston, and the inner diameter of the suction port is too small to prevent the suction amount of the refrigerant from being reduced This can improve compressor performance.

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,
Fig. 8 is a cross-sectional view taken along the line "IV-IV" in Fig. 6, and is a longitudinal sectional view for explaining the specifications of the suction port of the rolling piston in the compressor of Fig.
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. Fig. 8 is a cross-sectional view taken along the line IV-IV in Fig. 6. In the compressor according to Fig. 4, the rolling piston FIG. 3 is a longitudinal sectional view for explaining the specifications of the suction port of FIG.

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 >

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 volume of the second compression space V2 is smaller than the volume of the first compression space V1 so that the sectional area D4 of the second suction port 141a 1) inlet port 131b (hereinafter, referred to as a diameter) D3. 6, the first suction port 131b is connected to the second suction port 141a in parallel with the vane portion 133, and the second suction port 141a may be formed in a straight line with the first suction port 131b. May be formed in the radial direction.

That is, the diameter D41 of the second intake port 141a is not greater than the inner circumference height H2 of the rolling piston 140 to maintain the strength of the rolling piston 140 relative to the compression force And it is also possible to prevent the refrigerant from leaking due to the deformation of the rolling piston 140, which may be preferable.

The diameter D41 of the second suction port 141a is smaller than the diameter D41 of the second suction port 141a of the rolling piston 140. The diameter D41 of the second suction port 141a is larger than the diameter D41 of the second suction hole 141a, The thickness t of the drive transmitting portion 142 is multiplied by 1.5 at a height of the inner peripheral surface of the rolling piston 140 (i.e., a height of the second vane portion) The refrigerant can be sucked into the second compression space V2 smoothly.

The second intake port 141a may have the same diameter as the inlet and the outlet. However, as shown in FIG. 8, the inner circumferential height H2 may be smaller than the outer circumferential height H1 of the rolling piston 140, The outlet-side diameter D42 is smaller than the inlet-side diameter D41, that is, the refrigerant can flow into the second compression space V2 more smoothly. In this case, the inlet-side diameter D41 of the second suction port 141a is larger than the inner circumferential surface height (i.e., the height of the second vane portion) H2 of the rolling piston 140, But may be larger than a height obtained by subtracting the thickness t of the drive transmission portion 142 from the inner circumferential surface height H2 of the rolling piston 140. [

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 coupled 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 145. [

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 132 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.

In this embodiment, the inner diameter of the second suction port 141a formed in the rolling piston 140 is appropriately set so that the inner diameter of the second suction port 141a is too large to allow the refrigerant to leak as the rolling piston 140 is deformed And the inner diameter of the second suction port 141a is too small to reduce the suction amount of the refrigerant, thereby improving the performance of the compressor.

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 133a: Stepped portion
140: Rolling piston 141: Piston part
141a: second suction port 142: drive transmission portion
D3: first inlet diameter D41, D42: second inlet diameter
V1, V2: outer side, inner side compression space

Claims

A casing to which the suction pipe is connected;
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 connected to the annular outer cylinder portion and the inner cylinder portion by a vane portion fixedly coupled between the bearing plates 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,
Wherein the outer cylinder portion is formed with a first suction port penetrating from an outer circumferential surface to an inner circumferential surface and coupled with the suction pipe,
Wherein the rolling piston has a second suction port penetrating from an outer circumferential surface to an inner circumferential surface to communicate the first suction port and the inner compression space.

The method according to claim 1,
The rolling piston may include:
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 second suction port is formed so that its diameter is not larger than the inner peripheral surface height of the piston portion.

3. The method of claim 2,
And the diameter of the second suction port is formed to be larger than a height obtained by subtracting the height multiplied by 1.5 from the thickness of the drive transmission portion at the inner peripheral surface height of the piston portion.

The method according to claim 1,
Sectional area of the second suction port is smaller than a cross-sectional area of the first suction port.

5. The method according to any one of claims 1 to 4,
In the vane portion,
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,
And the height of the first vane portion is different from the height of the second vane portion.

A cylinder having an outer cylinder portion and an inner cylinder portion formed in an annular shape and formed at predetermined intervals in a radial direction and a vane portion connecting the outer cylinder portion and the inner cylinder portion in a radial direction; And
A piston portion slidably coupled to the vane portion between the outer cylinder portion and the inner cylinder portion and separating a compression space between the outer cylinder portion and the inner cylinder portion into an outer compression space and an inner compression space; A rolling piston having a drive transmitting portion extending and eccentrically coupled with respect to an axial center of the crankshaft; And
And a rolling bush rotatably inserted into the rolling piston and slidably coupled to both sides of the vane portion,
The piston portion of the rolling piston is formed with a suction port for guiding the refrigerant to the inner compression space from the outer circumferential surface to the inner circumferential surface,
Wherein the inlet side diameter of the inlet is larger than the outlet side diameter.

The method according to claim 6,
A slidable surface is formed on the upper surface of the vane portion so that the driving transmission portion of the rolling piston is slidably inserted in the radial direction,
Wherein the inlet side diameter of the inlet port is larger than the height from the bottom surface of the vane portion to the sliding surface and the outlet side diameter of the inlet port is smaller than the height from the bottom surface to the sliding surface of the vane portion.

8. The method of claim 7,
Wherein a diameter of an outlet of the suction port is formed to be greater than a height from a bottom surface of the vane portion to a slid surface minus a thickness of the drive transmission portion.