WO2022169117A1

WO2022169117A1 - Rotary compressor

Info

Publication number: WO2022169117A1
Application number: PCT/KR2022/000227
Authority: WO
Inventors: 사범동; 설세석; 강승민
Original assignee: 엘지전자 주식회사
Priority date: 2021-02-04
Filing date: 2022-01-06
Publication date: 2022-08-11
Also published as: CN116848322A; KR20220112531A; EP4290078A1; KR102499761B1

Abstract

A rotary compressor according to the present embodiment comprises: a main bearing and a sub-bearing which are respectively provided on both sides of a cylinder in the axial direction and each provided with a guide groove; a roller which is accommodated in the cylinder and rotated along with a rotary shaft; at least one vane which is slidably inserted in the roller, and on which a guide protrusion that is slidably inserted in the guide groove in the circumferential direction is extended in the axial direction; and a bearing member which is provided between the guide groove of at least one bearing between the main bearing and the sub-bearing and the guide protrusion of the vane. As such, the frictional loss between the vane or the roller and the main bearing or the sub-bearing facing same can be reduced to improve the compressor efficiency.

Description

rotary compressor

The present invention relates to a vane type rotary compressor in which a vane is coupled to a rotating roller.

The rotary compressor can be divided into a method in which a vane is slidably inserted into a cylinder and contacted with the roller, and a method in which a vane is slidably inserted into the roller and contacted with the cylinder. In general, the former is called a roller eccentric rotary compressor (hereinafter referred to as a rotary compressor), and the latter is classified as a vane concentric rotary compressor (hereinafter, a vane rotary compressor).

In the rotary compressor, the vane inserted into the cylinder is drawn toward the roller by elastic force or back pressure, and comes into contact with the outer circumferential surface of the roller. On the other hand, in the vane rotary compressor, the vane inserted into the roller rotates together with the roller, and is drawn toward the cylinder by centrifugal force and back pressure, and comes into contact with the inner circumferential surface of the cylinder.

The rotary compressor independently forms as many compression chambers as the number of vanes per rotation of the roller, so that each compression chamber simultaneously performs suction, compression, and discharge strokes. On the other hand, in the vane rotary compressor, as many compression chambers as the number of vanes per rotation of the roller are continuously formed, each compression chamber sequentially performs suction, compression, and discharge strokes. Therefore, the vane rotary compressor forms a higher compression ratio than the rotary compressor. Accordingly, the vane rotary compressor is more suitable for using high-pressure refrigerants with low ozone depletion potential (ODP) and global warming potential (GWP), such as R32, R410a, and CO ₂ .

In such a vane rotary compressor, as a plurality of vanes rotate together with the rollers, the vane slides while the sealing surface of the vane is in contact with the inner circumferential surface of the cylinder.

The vane rotary compressor is disclosed in Patent Document 1 (US Patent Publication: US2015-0064042 A1). The vane rotary compressor disclosed in Patent Document 1 is a low-pressure method in which the inner space of the motor chamber is filled with suction refrigerant, but a structure in which a plurality of vanes are slidably inserted into the rotating roller discloses the characteristics of the vane rotary compressor.

In the vane rotary compressor disclosed in Patent Document 1, an inner circumferential surface of a cylinder constituting a compression space has a plurality of curves. For example, the inner peripheral surface of the cylinder disclosed in Patent Document 1 may be formed in an asymmetric elliptical shape eccentric with respect to the axial center of the rotation shaft. Accordingly, the inner peripheral surface of the cylinder is provided with a proximal portion closest to the axial center and a remote portion located farthest from the axial center, and between the proximal portion is connected by curved surfaces having different lengths and ends. .

On the other hand, the roller is formed in a circular shape with a constant curvature of the outer circumferential surface and is disposed concentrically with respect to the axial center of the rotation shaft, and the roller has a plurality of vane slots that are divided and recessed by a predetermined depth from the outer circumferential surface at equal intervals along the outer circumferential surface of the roller. is formed with

In the vane rotary compressor as described above, the mechanical friction loss between the cylinder and the vane increases as the inner circumferential surface of the cylinder and the tip end (ie, the sealing surface) of the vane are always in contact or move relative to each other with an oil film between them. can do.

Accordingly, as in Patent Document 2 (Korean Patent Application Laid-Open No. 10-2011-0095155), there is known a structure for suppressing mechanical friction loss between the vane and the cylinder by regulating the radial motion of the vane. That is, in Patent Document 2, a ring is provided on a main bearing or a sub-bearing, and the vane is provided with a pin sliding in the circumferential direction along the ring. Through this, the vane only rotates along the roller, but the radial motion toward the cylinder is restricted. This ensures that the vanes are always in position relative to the cylinder, thereby suppressing friction between the cylinder and the vanes.

In the vane rotary compressor as described above, since the position of the vanes is determined by the ring, when a machining error or an assembly error is large, the vane and the cylinder may be excessively closely adhered or conversely excessively spaced apart. Also, friction loss between the axial side of the roller and the axial side of the bearing facing it may still occur.

Accordingly, as in Patent Document 3 (Japanese Patent Application Laid-Open No. 2012-167578), the tip portion (sealing surface) of the vane is non-contact with respect to the cylinder, but a structure that enables radial movement is known. That is, Patent Document 3 has a circular vane guide groove eccentric to the bearing, and a semicircular vane guide is applied to this groove to rotate along the vane guide groove. Then, while the vane moves in a radial direction with respect to the inner circumferential surface of the cylinder, it is possible to maintain a non-contact state with the inner circumferential surface of the cylinder. Through this, it is possible to reduce the mechanical friction loss between the cylinder and the vane by reducing the contact section between the cylinder and the vane.

However, in the conventional vane rotary compressor as described above, as the vane guide slides along the inner circumferential surface of the vane guide groove, mechanical friction loss may occur between the vane guide and the vane guide groove.

In addition, in the conventional vane rotary compressor, mechanical friction loss may occur between the axial side of the roller and the axial side of the main bearing or sub-bearing facing the same.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotary compressor capable of reducing mechanical friction loss caused by rotation of a vane.

Further, an object of the present invention is to provide a rotary compressor capable of restricting the withdrawal of vanes using a main bearing and/or sub-bearing, but reducing mechanical friction loss between the main bearing and/or sub-bearing and the vane. .

Furthermore, an object of the present invention is to provide a rotary compressor capable of reducing mechanical friction loss between the main bearing and/or sub-bearing and the vane by providing a bearing member between the main bearing and/or sub-bearing and the vane. .

Another object of the present invention is to provide a rotary compressor capable of reducing mechanical friction loss caused by the rotation of the roller.

Furthermore, an object of the present invention is to provide a rotary compressor capable of reducing mechanical friction loss between a main bearing and/or a sub bearing and a roller facing the same.

Furthermore, an object of the present invention is to provide a rotary compressor capable of reducing mechanical friction loss between the main bearing and/or sub-bearing and the roller by providing a bearing member between the main bearing and/or sub-bearing and the roller. .

In order to achieve the object of the present invention, a guide groove is formed on a surface facing the axial side of the roller in at least one of the main bearing and the sub-bearing, and in the axial direction of the vane facing the guide groove. A guide projection having a contact surface inserted into the guide groove and sliding along the inner peripheral surface of the guide groove extends in the axial direction at the end, and the bearing member is disposed between the inner peripheral surface of the guide groove and the contact surface of the guide projection facing it. A provided rotary compressor may be provided. Through this, it is possible to reduce the radial mechanical friction loss between the vane and the main bearing or sub-bearing supporting it.

In addition, in order to achieve the object of the present invention, guide grooves are formed in the main bearing and the sub bearing supporting the rotation shaft, and the vanes slidably inserted into the rollers are slidably inserted into the guide grooves and are radially constrained by guide projections. is formed, and a ball bearing may be provided between the guide groove and the guide projection. Through this, it is possible to easily install the bearing member between the vane and the main bearing or sub bearing supporting the same.

For example, the inner ring constituting the ball bearing may further include a rotating plate portion extending between the main bearing and the roller and between the sub bearing and the roller. Through this, it is possible to reduce the axial mechanical friction loss between the roller and the main bearing or sub-bearing facing it.

As another example, the rotating plate portion may be rotatably inserted into the inner circumferential surface of the cylinder. In this way, it is possible to more effectively reduce the axial mechanical friction loss between the roller and the main bearing or sub bearing facing it.

In addition, in order to achieve the object of the present invention, guide grooves are formed in the main bearing and the sub bearing supporting the rotation shaft, and the vanes slidably inserted into the rollers are slidably inserted into the guide grooves and are radially constrained by guide projections. is formed, a first bearing part is provided between the guide groove and the guide protrusion, and a second bearing part is provided between the main bearing and the roller and/or between the sub bearing and the roller, the first bearing part and the A rotary compressor in which the second bearing part is integrally formed may be provided. In this way, it is possible to reduce the radial friction loss between the vane and the main or sub-bearing and the axial friction loss between the roller and the main or sub-bearing.

For example, the first bearing part and the second bearing part may be integrally formed. Through this, it is possible to easily manufacture a bearing member capable of reducing frictional losses in the radial and axial directions.

As another example, the outer peripheral surface of the second bearing part may be provided to face the inner peripheral surface of the cylinder, and a sealing part may be formed on the outer peripheral surface of the second bearing part. Through this, while the second bearing part rotates in the cylinder, it is possible to effectively suppress refrigerant leakage in the compression space.

In addition, in order to achieve the object of the present invention, the cylinder may be formed in an annular inner peripheral surface. The main bearing and the sub-bearing respectively provided on both sides of the axial direction of the cylinder may form a compression space together with the cylinder, and guide grooves may be provided on the side surface forming the compression space. The roller accommodated in the cylinder may be provided to rotate together with a rotation shaft. At least one vane slidably inserted into the roller may have a guide protrusion inserted into the guide groove to slide along a circumferential direction in an axial direction. A bearing member may be provided between the guide groove of at least one of the main bearing and the sub-bearing and the guide protrusion of the vane. Through this, it is possible to increase compressor efficiency by reducing friction loss between the vane and the main bearing or sub bearing supporting the same.

Specifically, the bearing member may include an outer ring inserted into the inner circumferential surface of the guide groove; an inner ring provided on the inner side of the outer ring, the inner circumferential surface of which is slidably in contact with the contact surface of the guide protrusion; and a sliding member provided between the outer ring and the inner ring to allow the outer ring and the inner ring to perform relative motion. Through this, the mechanical friction loss between the vane and the main bearing or sub-bearing supporting the vane can be more effectively reduced, and the bearing member can be easily installed.

For example, any one of the outer ring and the inner ring may further include a rotating plate portion extending between the roller and the main bearing and the sub bearing facing them. In this way, it is possible to more effectively reduce the axial mechanical friction loss between the roller and the main bearing or sub bearing facing it.

For example, the bearing member may include: a first bearing part provided between at least one of the main bearing and the sub-bearing and the vane facing the same in a radial direction; and a second bearing part provided between at least one of the main bearing and the sub-bearing and the roller facing the same in the axial direction. In this way, it is possible to reduce the radial friction loss between the vane and the main or sub-bearing and the axial friction loss between the roller and the main or sub-bearing.

As another example, the first bearing part and the second bearing part may be formed as a single body. Through this, it is possible to easily manufacture a bearing member capable of reducing frictional losses in the radial and axial directions.

As another example, the second bearing part may be thicker than the first bearing part. Through this, the sealing area between the cylinder and the bearing member can be secured, and the sealing part can be easily formed on the outer peripheral surface of the second bearing part.

As another example, the first bearing part may be formed in a ring shape, and the second bearing part may be formed in a disk shape.

As another example, the first bearing unit may include: an outer ring inserted into a guide groove of at least one of the main bearing and the sub bearing; an inner ring provided on the inner side of the outer ring, the inner circumferential surface of which is slidably in contact with the guide projection of the vane; and a sliding member provided between the outer ring and the inner ring to allow the outer ring and the inner ring to perform relative motion. The second bearing part extends radially from one end of the inner ring or one end of the outer ring of the first bearing part and is provided on the axial side of the main bearing and the sub bearing facing the axial side of the roller can be In this way, it is possible to reduce the radial friction loss between the vane and the main or sub-bearing and the axial friction loss between the roller and the main or sub-bearing.

As another example, the axial side of the second bearing part may be spaced apart from the axial side of the main bearing or the sub-bearing facing it. Through this, it is possible to effectively reduce the friction loss by suppressing the contact of the second bearing part with the main bearing or the sub-bearing.

As another example, the second bearing part may be inserted into the cylinder such that its outer circumferential surface faces the inner circumferential surface of the cylinder. Through this, a sealing surface is formed between the second bearing part and the inner circumferential surface of the cylinder, thereby effectively reducing refrigerant leakage in the compression space.

As another example, a sealing part may be provided between the outer peripheral surface of the second bearing part and the inner peripheral surface of the cylinder. Through this, it is possible to more effectively suppress refrigerant leakage in the compression space while the second bearing part is spaced apart from the cylinder.

As another example, an outer circumferential surface of the second bearing part may be formed in the same shape as an inner circumferential surface of the cylinder. Through this, the second bearing part rotates inside the cylinder, thereby suppressing the relative motion between the roller and the second bearing part.

For example, the bearing member may be provided between at least one of the main bearing and the sub-bearing and the vane facing the same in a radial direction. An axial side surface of the roller may be in sliding contact with an axial side surface of the main bearing and an axial side surface of the sub bearing facing them. Through this, the mechanical friction loss between the second bearing part and the roller can be suppressed.

As another example, the inner peripheral surface of the cylinder may be formed in a circular or elliptical shape. A discharge port may be formed in at least one of an axial side surface of the main bearing and an axial side surface of the sub bearing. Through this, the shape of the inner circumferential surface of the cylinder can be formed in various ways, and overcompression can be suppressed by forming a long compression cycle.

For example, a bush groove may be formed in the roller, and a pair of swing bushes may be rotatably inserted into the bush groove, and the vane may be slidably inserted between the swing bushes. Through this, the front end of the vane can be formed to have the same curvature as the inner circumferential surface of the cylinder, thereby securing a sealing area between the cylinder and the vane.

In the rotary compressor according to the present embodiment, a bearing member may be provided between the guide grooves provided in the main bearing and the sub bearing and the guide projections of the vanes facing them. Through this, it is possible to increase compressor efficiency by reducing friction loss between the vane and the main bearing or sub bearing supporting the same.

In addition, in the rotary compressor according to the present embodiment, a ball bearing made of an outer ring, an inner ring, and a sliding member may be installed between the inner circumferential surface of the guide groove and the guide projection facing the same. Through this, the mechanical friction loss between the vane and the main bearing or sub-bearing supporting the vane can be more effectively reduced, and the bearing member can be easily installed.

In addition, the rotary compressor according to the present embodiment may further include a rotary plate portion extending between the roller and the main bearing and the sub bearing facing the outer ring or the upper inner ring constituting the ball bearing. In this way, it is possible to more effectively reduce the axial mechanical friction loss between the roller and the main bearing or sub bearing facing it.

In addition, the rotary compressor according to the present embodiment, the first bearing portion provided between the main bearing and the sub-bearing and the vanes facing them in the radial direction, the main bearing and the sub-bearing and the roller facing it in the axial direction. It may include a second bearing unit provided. In this way, it is possible to reduce the radial friction loss between the vane and the main or sub-bearing and the axial friction loss between the roller and the main or sub-bearing.

In addition, in the rotary compressor according to the present embodiment, the first bearing part and the second bearing part may be formed as a single body. Through this, it is possible to easily manufacture a bearing member capable of reducing frictional losses in the radial and axial directions.

In addition, in the rotary compressor according to the present embodiment, the second bearing part may be formed to be thicker than the first bearing part. Through this, the sealing area between the cylinder and the bearing member can be secured, and the sealing part can be easily formed on the outer peripheral surface of the second bearing part.

In addition, in the rotary compressor according to the present embodiment, the second bearing part may be spaced apart from the axial side surface of the main bearing or the sub bearing facing the second bearing part in the axial direction. Through this, it is possible to effectively reduce the friction loss by suppressing the contact of the second bearing part with the main bearing or the sub-bearing.

In addition, in the rotary compressor according to the present embodiment, the second bearing part may be inserted into the cylinder so that the outer circumferential surface faces the inner circumferential surface of the cylinder. Through this, a sealing surface is formed between the second bearing part and the inner circumferential surface of the cylinder, thereby effectively reducing refrigerant leakage in the compression space.

In addition, in the rotary compressor according to the present embodiment, a sealing part may be provided between the outer peripheral surface of the second bearing part and the inner peripheral surface of the cylinder. Through this, it is possible to more effectively suppress refrigerant leakage in the compression space while the second bearing part is spaced apart from the cylinder.

In addition, in the rotary compressor according to the present embodiment, the inner circumferential surface of the cylinder is formed in a circular or elliptical shape, and the discharge port may be formed in at least one of the axial side surface of the main bearing and the axial side surface of the sub bearing. Through this, the shape of the inner circumferential surface of the cylinder can be formed in various ways, and overcompression can be suppressed by forming a long compression cycle.

In addition, in the rotary compressor according to the present embodiment, a bush groove is formed in the roller, two pair of swing bushes are rotatably inserted into the bush groove, and the vane may be slidably inserted between the swing bushes. Through this, the front end of the vane can be formed to have the same curvature as the inner circumferential surface of the cylinder, thereby securing a sealing area between the cylinder and the vane.

1 is a cross-sectional view showing an example of a vane rotary compressor according to the present invention in a longitudinal section;

2 is an exploded perspective view of the compression unit in FIG. 1;

3 is a perspective view showing the compression part of FIG. 2 assembled;

Fig. 4 is a plan view of Fig. 3;

5 is an enlarged cross-sectional view of the compression unit in FIG. 1;

6 is a perspective view showing the vane bearing in FIG.

7 is a cross-sectional view showing a state in which the vane bearing of FIG. 6 is mounted on the main bearing;

8 and 9 are cross-sectional views showing other embodiments of the sealing part of the vane bearing in FIG. 5;

10 is a cross-sectional view showing another embodiment of the vane bearing;

11 is a cross-sectional view showing another embodiment of the vane bearing.

Hereinafter, a vane rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. For reference, the vane slot of the roller according to the present invention can be equally applied to the vane rotary compressor in which the vane is slidably inserted into the roller. For example, the same can be applied to the example in which the vane slot is formed in the radial direction as well as the example in which the vane slot is formed to be inclined as in the present embodiment.

1 is a longitudinal cross-sectional view showing an example of a vane rotary compressor according to the present invention, FIG. 2 is an exploded perspective view of the compression part in FIG. 1, FIG. 3 is a perspective view showing the compression part of FIG. 2 assembled, and FIG. 3 is a plan view.

Referring to FIG. 1 , the vane rotary compressor according to the present embodiment includes a casing 110 , a driving motor 120 , and a compression unit 130 . The drive motor 120 is installed in the upper inner space 110a of the casing 110, the compression unit 130 is installed in the lower inner space 110a of the casing 110, respectively, and the drive motor 120 and the compression unit ( 130 is connected to the rotation shaft 123 .

The casing 110 is a portion forming the exterior of the compressor, and may be divided into a vertical or horizontal type depending on an installation aspect of the compressor. The vertical type has a structure in which the driving motor 120 and the compression unit 130 are disposed on both upper and lower sides along the axial direction, and the horizontal type has a structure in which the driving motor 120 and the compression unit 130 are disposed on both left and right sides. The casing according to the present embodiment may be formed in a bell shape.

The casing 110 includes an intermediate shell 111 formed in a cylindrical shape, a lower shell 112 covering the lower end of the intermediate shell 111 , and an upper shell 113 covering the upper end of the intermediate shell 111 . The driving motor 120 and the compression unit 130 are inserted into the intermediate shell 111 to be fixedly coupled, and the suction pipe 115 may be penetrated to be directly connected to the compression unit 130 .

The lower shell 112 is sealingly coupled to the lower end of the intermediate shell 111 , and a storage oil space 110b in which oil to be supplied to the compression unit 130 is stored may be formed below the compression unit 130 . The upper shell 113 is sealingly coupled to the upper end of the intermediate shell 111 , and an oil separation space 110c may be formed above the driving motor 120 to separate oil from the refrigerant discharged from the compression unit 130 . have.

The driving motor 120 is a part constituting the electric part, and provides power to drive the compression part 130 . The driving motor 120 includes a stator 121 , a rotor 122 , and a rotation shaft 123 .

The stator 121 is fixedly installed inside the casing 110 , and may be press-fitted to the inner circumferential surface of the cylindrical casing 110 by shrink fit or the like. For example, the stator 121 may be fixed by being press-fitted to the inner circumferential surface of the intermediate shell 110a.

The rotor 122 is rotatably inserted into the stator 121 , and the rotation shaft 123 is press-fitted to the center of the rotor 122 . Accordingly, the rotating shaft 123 rotates concentrically with the rotor 122 .

In the center of the rotation shaft 123, the oil passage 125 is formed in the shape of a hollow hole, and in the middle of the oil passage 125, oil through

holes

126a and 126b may be formed to penetrate toward the outer circumferential surface of the rotation shaft 123. . The oil through-

holes

126a and 126b include a first oil through-hole 126a belonging to the range of the main bearing unit 1312 to be described later and a second oil through-hole 126b belonging to the range of the second bearing unit 1322 . Each of the first oil through-hole 126a and the second oil through-hole 126b may be formed one by one, or a plurality of first oil through-holes 126b may be formed. This embodiment shows an example in which a plurality of pieces are formed.

An oil pickup 127 may be installed in the middle or lower end of the oil passage 125 . The oil pickup 127 may be a gear pump, a viscous pump, a centrifugal pump, or the like. This embodiment shows an example to which a centrifugal pump is applied. Accordingly, when the rotating shaft 123 rotates, the oil filled in the oil storage space 110b of the casing 110 is pumped by the oil pickup 127, and this oil is sucked along the oil passage 125 and then the second oil through hole. It may be supplied to the sub-bearing surface 1322a with the sub-bearing unit 1322 through the 126b, and to the main bearing surface 1311a of the main bearing unit 1312 through the first oil through hole 126a. This will be explained again later.

The compression unit 130 includes a main bearing 131 , a sub bearing 132 , a cylinder 133 , a roller 134 , and a plurality of

vanes

1351 , 1352 , and 1353 . The main bearing 131 and the sub bearing 132 are respectively provided on upper and lower sides of the cylinder 133 to form a compression space V together with the cylinder 133, and the roller 134 rotates in the compression space V Installed as possible, the

vanes

1351, 1352 and 1353 are slidably inserted into the roller 134 to divide the compression space V into a plurality of compression chambers.

1 and 2 , the main bearing 131 may be fixedly installed on the intermediate shell 111 of the casing 110 . For example, the main bearing 131 may be inserted into the intermediate shell 111 and welded.

The main bearing 131 may be closely coupled to the upper end of the cylinder 133 . Accordingly, the main bearing 131 forms the upper surface of the compression space V, supports the upper surface of the roller 134 in the axial direction, and at the same time supports the upper half of the rotary shaft 123 in the radial direction.

The main bearing 131 may include a main plate part 1311 and a main bearing part 1312 . The main plate part 1311 covers the upper side of the cylinder 133 and is coupled to the cylinder 133 , and the main bearing part 1312 moves from the center of the main plate part 1311 toward the driving motor 120 in the axial direction. It extends to support the upper half of the rotation shaft 123 .

The main plate part 1311 may be formed in a disk shape, and the outer peripheral surface of the main plate part 1311 may be fixed in close contact with the inner peripheral surface of the intermediate shell 111 . A main guide groove 1311a may be formed on a lower surface of the main plate portion 1311 , that is, an axial lower surface facing the axial upper surface of the roller 134 to receive a guide protrusion 1351d to be described later.

The main guide groove 1311a accommodates a main bearing hole 1312a, which will be described later, and is formed eccentrically with respect to the bearing hole center (axial center or roller rotation center) (unsigned) forming the center of the main bearing hole 1312a. can be For example, the center Og formed by the inner circumferential surface 1311a1 of the main guide groove 1311a is formed to be located on the same axis as the center Ov of the compression space V formed by the inner circumferential surface 1331 of the cylinder 133. can be Accordingly, the center Og of the main guide groove 1311a and the center Ov of the compression space V may be formed eccentrically with respect to the rotation center Or of the roller 134 .

In other words, when the first bearing part 1365 and the second bearing part 1366 rotate together in the

vane bearings

136 and 137 to be described later as in the present embodiment, as described above, the main guide groove 1311a) The center Og and the center Ov of the compression space V may be formed eccentrically with respect to the rotation center Or of the roller 134 while being formed to be located on the same axis.

However, when the second bearing part 1366 is excluded or the second bearing part 1366 is fixed, the center Og of the main guide groove 1311a and the center Ov of the compression space V are eccentric to each other. It may also be formed.

The main guide groove 1311a may be formed to have substantially the same depth as a whole, and may communicate with the oil passage 125 provided in the rotation shaft 123 . For example, the main guide groove 1311a is formed in a stepped shape at the inner peripheral edge of the main plate part 1311 or at the lower edge of the main bearing 1312, the first oil through hole 126a of the rotating shaft 123 and It may be formed at a position where it communicates directly in the radial direction, or it may be formed to communicate through the main bearing surface 1312a1 formed by the inner circumferential surface of the main bearing hole 1312a. Accordingly, a discharge pressure or an oil equivalent thereto may be introduced into the main guide groove 1311a.

The inner circumferential surface of the main guide groove 1311a is a position not communicating with the compression space V, for example, the inner circumferential surface 1311a1 of the main guide groove 1311a is the main bearing surface 1312a1 formed by the inner circumferential surface of the main bearing hole 1312a. ) and the outer peripheral surface 1341 of the roller 134 may be formed to be located. Accordingly, a sealing distance is secured between the main bearing 131 and the roller 134, and even if a discharge pressure or an oil equivalent thereto is introduced into the inside of the main guide groove 1311a, the oil flows into the compression space V. can be restrained

The inner circumferential surface 1311a1 of the main guide groove 1311a may be formed in the same shape as the outer circumferential surface 1341 of the roller 134 to be described later. For example, the inner peripheral surface 1311a1 of the main guide groove 1311a may be formed in the same circular shape as the outer peripheral surface 1341 of the roller 134 to be described later. Accordingly, the sealing surface (or sealing distance) between the main guide groove 1311a and the outer peripheral surface of the roller may be uniformly formed along the circumferential direction.

The main bearing part 1312 is formed in a bush shape through which the main bearing hole 1312a penetrates in the axial direction to form a hollow, and an oil groove (not shown) is provided on the main bearing surface 1312a1, which is the inner peripheral surface of the main bearing hole 1312a. can be formed.

1 and 2 , the sub-bearing 132 may be closely coupled to the lower end of the cylinder 133 . Accordingly, the sub-bearing 132 forms the lower surface of the compression space V, supports the lower surface of the roller 134 in the axial direction and at the same time supports the lower half of the rotation shaft 123 in the radial direction.

The sub bearing 132 may be formed similarly to the main bearing 131 described above. For example, the sub-bearing 132 according to the present embodiment may include a sub-plate part 1321 and a sub-bearing part 1322 .

The sub-plate part 1321 covers the lower side of the cylinder 133 and is coupled to the cylinder 133 , and the sub-bearing part 1322 axially moves from the center of the sub-plate part 1321 toward the lower shell 112 . It extends to support the lower half of the rotation shaft 123 .

The sub-plate part 1321 may be formed in a disk shape similar to the main plate part 1311 , and may be formed to be substantially the same as the outer diameter of the cylinder 133 . Accordingly, the outer circumferential surface of the sub-plate portion 1321 may be spaced apart from the inner circumferential surface of the intermediate shell 111 .

A sub-guide groove 1321a may be formed on the upper surface of the sub-plate part 1321 in the axial direction. Since the sub guide groove 1321a is formed symmetrically with the main guide groove 1311a described above centering on the roller 134, the description of the sub guide groove 1321a is replaced with the description of the main guide groove 1312a. .

The sub-bearing part 1322 is formed in a bush shape through which the sub-bearing hole 1322a penetrates in the axial direction to form a hollow, and an oil groove (not shown) on the sub-bearing surface 1322a1, which is the inner peripheral surface of the sub-bearing hole 1322a. can be formed.

1 to 3 , the cylinder 133 according to the present embodiment may be in close contact with the lower surface of the main bearing 131 and may be bolted to the main bearing 131 together with the sub bearing 132 . Accordingly, the cylinder 133 may be fixedly coupled to the casing 110 by the main bearing 131 .

The cylinder 133 may be formed in an annular shape having a compression space V in the center. For example, the inner circumferential surface 1331 of the cylinder 133 constituting the compression space V is formed in a circular shape having the same inner diameter along the circumferential direction, and the center (shown in FIG. 4) Ov of the compression space V is It may be formed to be eccentric with respect to the rotation center (shown in FIG. 4) Or of the roller 134 constituting the axial center (shown in FIG. 4) Os. Accordingly, the inner peripheral surface 1331 of the cylinder 133 is formed eccentrically with respect to the outer peripheral surface 1341 of the roller 134, and between the inner peripheral surface 1331 of the cylinder 133 and the outer peripheral surface 1341 of the roller 134, the A proximity point (or contact point) P at which the inner circumferential surface 1331 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134 are almost in contact may be formed.

The cylinder 133 may have suction ports 1332 and

discharge ports

1333a and 1333b formed on both sides of the circumferential direction with respect to the proximity point P, respectively. Accordingly, the suction port 1332 and the

discharge ports

1333a and 1333b may be separated from each other by the proximity point P.

The suction port 1332 is directly connected to the suction pipe 115 penetrating the casing 110 , and the

discharge ports

1333a and 1333b communicate toward the inner space 110a of the casing 110 , and are coupled through the casing 110 . It may be indirectly connected to the discharge pipe 116 that is. Accordingly, the refrigerant is directly sucked into the compression space V through the suction port 1332 , while the compressed refrigerant is discharged into the inner space 110a of the casing 110 through the

discharge ports

1333a and 1333b and then discharged through the discharge pipe. (116) can be discharged. Accordingly, the inner space 110a of the casing 110 may be maintained in a high pressure state constituting the discharge pressure.

In addition, while a separate suction valve is not installed at the suction port 1332 ,

discharge valves

1335a and 1335b for opening and closing the

respective discharge ports

1333a and 1333b are installed in each of the

discharge ports

1333a and 1333b, respectively. can Each of the

discharge valves

1335a and 1335b may be formed of a reed valve having one end fixed and the other end forming a free end. However, each of the

discharge valves

1335a and 1335b may be variously applied as needed, such as a piston valve in addition to a reed type valve.

In addition, when each of the

discharge valves

1335a and 1335b is a reed type valve, the

valve accommodating grooves

1334a and 1334b are respectively provided on the outer peripheral surface of the cylinder 133 so that the

respective discharge valves

1335a and 1335b can be mounted. can be formed. Accordingly, the length of the

discharge ports

1333a and 1333b is reduced to a minimum, thereby reducing the body volume. The valve

accommodating grooves

1334a and 1334b may be formed in a triangular shape to secure a flat valve seat surface as shown in FIG. 2 .

Meanwhile, a plurality of

discharge ports

1333a and 1333b may be formed along the compression path (compression progress direction). For convenience, the plurality of

outlets

1333a and 1333b will be described by defining the outlet positioned on the upstream side as the first outlet port 1333a and the outlet positioned on the downstream side as the second outlet port 1333b based on the compression path.

However, the discharge port may not be configured in plurality. For example, if the inner peripheral surface of the cylinder 133 forms a long compression cycle to appropriately reduce overcompression of the refrigerant, only one discharge port may be formed.

Meanwhile, referring to FIG. 4 , the roller 134 described above may be rotatably provided in the compression space V of the cylinder 133 . The roller 134 may be formed such that its rotational center Or is positioned on the same axis as the axial center Os of the rotational shaft 123 . The roller 134 may be integrally formed or assembled with the rotation shaft 123 to be integrally coupled. Accordingly, the roller 134 rotates with the rotation shaft 123 about the axis center Os.

The roller 134 has an outer peripheral surface 1341 formed in a circular shape, and a plurality of bush grooves 1342 may be formed on the outer peripheral surface 1341 of the roller 134 at predetermined intervals along the circumferential direction. The bush groove 1342 is defined as a first bush groove (unsigned), a second bush groove (unsigned), and a third bush groove (unsigned) along the compression progress direction (rotational direction of the roller), and the first bush The groove, the second bush groove, and the third bush groove may be formed to be identical to each other.

A swing bush 1343 forming a kind of vane slot may be rotatably coupled to each bush groove 1342 . In the swing bush 1343 , two bushes formed in a substantially semicircular shape may be inserted into the bush groove 1342 at intervals of the thickness of each

vane

1351 , 1352 , and 1353 to be coupled thereto. Accordingly, the

vanes

1351 , 1352 , and 1353 coupled to the swing bush 1343 may rotate while moving along the inner circumferential surface 1331 of the cylinder 133 using the swing bush 1343 as a hinge point.

As described above, when the

vanes

1351 , 1352 , and 1353 are rotatably supported with respect to the roller 134 by each swing bush 1343 , the rotation center Or of the roller 134 is the compression space V Even if the roller 134 rotates in a state eccentrically positioned with respect to the center Ov, the

vanes

1351, 1352, and 1353 may always face the center Ov of the compression space V. Then, the

vane tip portions

1351b, 1352b, and 1353b forming the front surfaces of the

vanes

1351,1352,1363 to be described later have the same curvature as the inner circumferential surface 1331 of the cylinder 133, so that each

vane

1351,1352,1363) It is possible to secure a sealing area between the and the cylinder (133).

Meanwhile, a back pressure chamber 1344 may be formed inside the bush groove 1342 , that is, between the bush groove 1342 and the rotation center Or of the roller 134 . The back pressure chamber 1344 may radially communicate with each bush groove 1342 and may communicate with the above-described main guide groove 1311a and/or sub guide groove 1321a in the axial direction. Accordingly, each

vane

1351,1352,1353 is connected to the inner circumferential surface 1331 of the cylinder 133 by using the pressure of high-pressure oil (or refrigerant) flowing into the main guide groove 1311a or/and the sub-guide groove 1321a. ) in the direction of

Each back pressure chamber 1344 is sealed by the main bearing 131 and the sub-bearing 132, as described above, the main guide groove 1311a and/or the sub-guide groove 1321a can be axially communicated with each other. have. The back pressure chamber 1344 may communicate with the main guide groove 1311a and/or the sub guide groove 1321a.

2 to 4, a plurality of

vanes

1351, 1352, and 1353 according to this embodiment are vane

bodies

1351a, 1352a, and 1353a, the vane front end (or front surface) 1351b, 1352b, 1353b, It may include vane rear end (or rear surface) 1351c, 1352c, 1353c, and guide

projections

1351d, 1352d and 1353d. The

vane tip portions

1351b, 1352b, and 1353b are surfaces in contact with the inner circumferential surface 1331 of the cylinder 133, and the vane rear ends 1351c, 1352c, and 1353c are understood as surfaces facing the back pressure chambers 1343a, 13343b, and 1343c. can be

Each of the

vane bodies

1351a, 1352a, and 1353a may be formed in a substantially rectangular parallelepiped shape. Accordingly, each of the

vane bodies

1351a , 1352a , and 1353a can slide smoothly along the longitudinal direction between the respective swing bushes 1343 .

The

vane tip portions

1351b, 1352b, and 1353b are formed in a curved shape to be in line contact with the inner circumferential surface 1331 of the cylinder 133, and the sealing surface forming the front surface of each

vane tip portion

1351b, 1352b, 1353b is the cylinder 133 ) may be formed to have substantially the same curvature as the inner circumferential surface 1331 . Accordingly, even if each of the

vane tip parts

1351b, 1352b, and 1353b is slightly spaced apart from the inner circumferential surface 1331 of the cylinder 133, the sealing area between the

vane tip parts

1351b, 1352b, and 1353b and the cylinder is secured to secure the compression chamber. Hepatic leakage can be suppressed.

The rear ends of the

vanes

1351c, 1352c, and 1353c may be formed to be flat. Accordingly, the pressure receiving surface constituting the rear surface of each of the rear ends of the

vanes

1351c, 1352c, and 1353c receives the back pressure of each back pressure chamber 1344 evenly, and each

vane

1351, 1352, and 1353 moves toward the cylinder 133. While moving quickly, the behavior of the

vanes

1351 , 1352 , and 1353 can be stabilized.

The

guide projections

1351d, 1352d, and 1353d extend in the axial direction from both sides in the rear axial direction of the

vane body

1351a, 1352a, 1353a forming the vane

rear end portions

1351c, 1352c, 1353c. can be formed. For example, the guide protrusions 1351d, 1352d, and 1353d are upper guide protrusions (hereinafter, first guide protrusions) 1351d1 (not shown) extending upward in the axial direction toward the main guide groove 1311a (not shown). ) and a lower guide protrusion (hereinafter, a second guide protrusion) 1351d2 (not shown) (not shown) extending in the axial direction downward toward the sub-guide groove 1321a.

The first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) may have the same shape and the same size and be formed on the same axis. However, in some cases, the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) may be formed in different shapes and different sizes, and in the axial direction. They may be formed at positions eccentric to each other. Hereinafter, the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) have the same shape and the same size and are formed on the same axis. Explain.

The first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) are formed to have the same width as the

vane bodies

1351a, 1352a, and 1353a. can be However, in some cases, the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) are greater than the width of the vane body 1351a (1352ad) (1353a). It may be formed large or small. For example, the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) are both sides or one of the vane body 1351a (1352ad) (1353a). It may be formed extending in the circumferential direction from the side. In this case, the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) are the inner peripheral surfaces 1311a1 of each

guide groove

1311a, 1321a ( 1321a1), it may be preferable to be formed in an arc shape. Also, in this case, the first guide protrusions 1351d1, 1352d1, 1353d1 and the second guide protrusions 1351d2, 1352d2, 1353d2 may be identically formed in the circumferential direction, respectively, but may be formed differently in the circumferential direction. may be

The first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) may each have a flat outer circumferential surface. However, the inner peripheral surface (1311a1) (1321a1) of the

guide grooves

1311a and 1321a in which the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) face each other. ) is formed in a circular curved surface, so the outer peripheral surfaces of the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) are

guide grooves

1311a and 1321a, respectively. ) of the inner peripheral surface (1311a1) (1321a1), more precisely, it may be preferably formed in a circular curved surface to correspond to the inner peripheral surface (1365a) of the first bearing portion 1365 of the inner ring 1362 to be described later.

Meanwhile, referring to FIGS. 1 to 4 , the outer peripheral surfaces of the first guide protrusions 1351d1, 1352d1, 1353d1 and the second guide protrusions 1351d2, 1352d2, 1353d2 and the main guide groove 1311a facing them. And

vane bearings

136 and 137 may be provided between the inner peripheral surfaces 1311a1 and 1321a1 of the sub-guide groove 1321a. The

vane bearings

136 and 137 may be variously applied to ball bearings, roller bearings, bush bearings, foil bearings, and the like. In the present embodiment, the example of the

vane bearings

136 and 137 made of ball bearings will be mainly described, but the

vane bearings

136 and 137 will be described again later.

The vane rotary compressor as described above operates as follows.

That is, when power is applied to the drive motor 120 , the rotor 122 of the drive motor 120 and the rotary shaft 123 coupled to the rotor 122 rotate, and are coupled to the rotary shaft 123 or The integrally formed roller 134 rotates together with the rotating shaft 123 .

Then, the plurality of

vanes

1351,1352,1353 slidably inserted into the swing bush 1343 of the roller 134 serving as the vane slot are centrifugal force generated by the rotation of the roller 134 and the

vanes

1351 , 1352 and 1353 are drawn out or drawn in from the roller 134 by the back pressure of the back pressure chamber 1343 provided on the rear side, and the

vane tip portions

1351b, 1352b, and 1353b of each of the

vanes

1351, 1352 and 1353. ) is in contact with the inner circumferential surface 1332 of the cylinder 133 .

Then, the compression space (V) of the cylinder 133 is formed by a plurality of vanes (1351,1352,1353) by the number of the plurality of vanes (1351,1352,1353) as many compression chambers (including a suction chamber or a discharge chamber) It is partitioned by (V1, V2, V3), and each compression chamber (V1, V2, V3) moves along the rotation of the roller 134 while moving along the inner peripheral surface 1332 shape of the cylinder 133 and the eccentricity of the roller 134 The volume is changed by , and the refrigerant sucked into each compression chamber (V1, V2, V3) is compressed while moving along the rollers 134 and the

vanes

1351, 1352, and 1353, and this refrigerant is compressed in the cylinder 133. A series of processes of being discharged into the inner space 110a of the casing 110 through the

discharge ports

1333a and 1333b provided on the inner circumferential surface 1331 of the is repeated.

At this time, the plurality of

vanes

1351, 1352, and 1353 are drawn out from the roller 134, respectively, and the vane tip ends 1351b, 1352b, and 1353b forming the front surface of the

vanes

1351,1352, and 1353b are of the cylinder 133. In contact with the inner peripheral surface 1332 is separated between the compression chamber.

However, when the

vane tip portions

1351b, 1352b, and 1353b of each of the

vanes

1351, 1352 and 1353 slide and move while always in contact with the inner circumferential surface 1331 of the cylinder 133, the cylinder 133 and Mechanical loss (or friction loss) due to friction between the

vanes

1351 , 1352 and 1353 may be greatly increased. On the other hand, when the back pressure for each

vane

1351,1352,1353 is lowered in consideration of this, the vane tip ends 1351b, 1352b, and 1353b of each

vane

1351,1352b, and 1353b are the inner peripheral surfaces 1331 of the cylinder 133. Refrigerant leakage may occur between the compression chambers as they are spaced apart from each other. In particular, in the process of performing the compression stroke, as the pressure in the corresponding compression chamber increases, the

vanes

1351 , 1352 , and 1353 may be pushed out from the cylinder 133 by receiving the gas force of the compression chamber. Then, the cylinder 133 and the vanes (1351,1352,1353) are further spaced apart, the refrigerant leakage can be increased.

Accordingly, by appropriately lowering the back pressure acting on the rear ends of the

vanes

1351c, 1352c, and 1353c, the refrigerant does not leak between the inner circumferential surface 1331 of the cylinder 133 and the front surfaces of the

vanes

1351,1352c, and 1353c. In the cylinder 133 and the vanes (1351,1352,1353) can be made to move relative to the spaced apart state. Through this, it is desirable to reduce the mechanical friction loss between the cylinder 133 and the

vanes

1351,1352,1353 and at the same time secure the back pressure acting on the

vanes

1351,1352,1353 to suppress refrigerant leakage. do.

Accordingly, in this embodiment, as described above, a main guide groove 1311a is formed in the main plate portion 1311 and a sub guide groove 1321a is formed in the sub-plate portion 1321, respectively, and these main guide grooves 1311a are formed. and a first guide protrusion 1351d1 (not shown) (not shown) at the upper end in the axial direction of the

vane body

1351a, 1352a, 1353a facing the sub guide groove 1321a, and a second guide protrusion at the lower end in the axial direction ( 1351d2) (not shown) (not shown) may be formed, respectively. Accordingly, the first guide protrusion 1351d1 (not shown) (not shown) and the second guide protrusion 1351d2 (not shown) (not shown) are caught by the main guide groove 1311a and the sub guide groove 1321a and are cut off. The amount of protrusion is limited, thereby reducing the mechanical friction loss between the cylinder 133 and the

vanes

1351,1352,1353, and at the same time securing the back pressure acting on the

vanes

1351,1352,1353 to suppress refrigerant leakage. have.

Even when the

guide grooves

1311a, 1321a and the

guide projections

1351d, 1352d, and 1353d are formed as described above, friction loss occurs between the

guide grooves

1311a and 1321a and the

guide projections

1351d, 1352d, and 1353d. can be Accordingly, in this embodiment, the

vane bearings

136 and 137 described above are provided between the

guide grooves

1311a and 1321a and the

guide projections

1351d, 1352d, and 1353d, respectively, so that the

guide grooves

1311a and 1321a and the guide projections are provided. The friction loss between (1351d,1352d,1353d) can be reduced.

FIG. 5 is an enlarged cross-sectional view of the compression part in FIG. 1 , FIG. 6 is a perspective view showing the vane bearing in FIG. 5 after being broken, and FIG. 7 is a cross-sectional view showing the state in which the vane bearing of FIG. 6 is mounted to the main bearing.

5 to 7 , between the main guide groove 1311a and the first guide protrusion 1351d1 (not shown) (not shown) inserted therein and/or the sub guide groove 1321a according to the present embodiment Each of the

vane bearings

136 and 137 may be provided between the second guide protrusion 1351d2 (not shown) (not shown) inserted therein.

As described above, the

vane bearings

136 and 137 may be variously applied to ball bearings, roller bearings, bush bearings, foil bearings, etc., but in this embodiment, the

vane bearings

136 and 137 made of ball bearings will be mainly described. .

In addition, the

vane bearings

136 and 137 may extend between the roller 134 and the main bearing 131 and the sub bearing 132 facing them. In this embodiment,

vane bearings

136 and 137 are provided between the

guide grooves

1311a and 1321a and the

guide projections

1351d, 1352d, and 1353d and between the roller 134 and the

bearings

131 and 132, respectively. It will be explained based on examples.

In addition, the

vane bearings

136 and 137 are installed between the main guide groove 1311a and the first guide projection 1351d1 (not shown) (not shown) as the main side vane bearing 136, and the sub guide groove What is installed between the 1321a and the second guide protrusion 1351d2 (not shown) (not shown) is defined as the sub-side vane bearing 137, respectively, and hereinafter, the main-side vane bearing will be described as a representative example.

The vane bearing 136 according to the present embodiment may include an outer ring 1361 , an inner ring 1362 , and a plurality of balls 1363 .

The outer ring 1361 may be formed in an annular shape so that the center Oob of the outer ring 1361 is positioned on the same axis as the center Og of the main guide groove 1311a. In other words, the center Oob of the outer ring 1361 may be provided eccentrically with respect to the rotation center Or of the roller 134 .

In addition, the outer diameter of the outer ring 1361 may be formed to be substantially the same as the inner diameter of the main guide groove 1311a, or may be formed to be slightly smaller. For example, when the outer diameter of the outer ring 1361 is formed to be substantially the same as the inner diameter of the main guide groove 1311a, the outer ring 1361 is press-fitted into the main guide groove 1311a and fixed, and the outer diameter of the outer ring 1361 is When the inner diameter of the main guide groove 1311a is substantially the same, the outer ring 1361 can freely rotate in the main guide groove 1311a. In this embodiment, the outer diameter of the outer ring 1361 is formed to be substantially equal to the inner diameter of the main guide groove 1311a, and the outer ring 1361 is press-fitted to the inner circumferential surface of the main guide groove 1311a.

The inner ring 1362 may include a first bearing part 1365 and a second bearing part 1366 . The first bearing part 1365 may be formed in an annular shape, and the second bearing part 1366 may be formed in a disk shape with an empty central part.

The outer diameter of the first bearing part 1365 may be smaller than the outer ring 1361 and the inner diameter may be larger than the inner diameter of the main bearing hole 1312a. The center Ob1 of the first bearing part 1365 is located on the same axis as the center Oob of the outer ring 1361 , that is, the center Ob1 of the first bearing part 1365 is the roller 134 . It may be formed eccentric with respect to the rotation center (Or). Accordingly, the inner ring 1362 including the first bearing part 1365 may be rotatably inserted inside the outer ring 1361 .

The second bearing unit 1366 may extend in a flange shape from the lower end of the first bearing unit 1365 or an outer peripheral surface around the lower end. The second bearing unit 1366 may be formed to extend as a single body with the first bearing unit 1365 , or may be formed separately and then assembled.

For example, when the second bearing part 1366 is formed as a single body on the first bearing part 1365, the manufacturing cost can be reduced by excluding the assembly process of the entire inner ring, and the second bearing part 1366 is the second bearing part 1366. When assembled to the first bearing part 1365, the thickness t2 of the second bearing part 1366 is formed to be thicker than the thickness t1 of the first bearing part 1365, and the sealing parts 1367 and 1377 to be described later. can be easily formed.

However, even when the first bearing part 1365 and the second bearing part 1366 are formed as a single body, the thickness t2 of the second bearing part 1366 is greater than the thickness t1 of the first bearing part 1365 . The thickness t2 of the second bearing part 1366 may be thicker than the thickness t1 of the first bearing part 1365 even when a separate sealing part 1367 is not formed. . Through this, it is possible to secure a sealing area between the outer peripheral surface 1366a of the second bearing part 1366 and the inner peripheral surface 1331 of the cylinder 133 .

The inner diameter D1 of the second bearing part 1366 is smaller than the degree to which the back pressure chamber 1344 can communicate with the main guide groove 1311a, for example, the inner diameter D2 of the main guide groove 1311a. The diameter D3 of the virtual circle connecting the inner ends of the back pressure chamber 1344 may be larger than the diameter D3. Accordingly, the high-pressure oil flowing into the main guide groove 1311a may be smoothly introduced into each back pressure chamber 1344 without being blocked by the second bearing unit 1366 .

The outer diameter D12 of the second bearing part 1366 may be substantially the same as or slightly smaller than the inner circumferential surface 1331 of the cylinder 133 , that is, the inner diameter D4 of the compression space V. Accordingly, the second bearing part 1366 is rotatably inserted into the inner space of the cylinder 133 , that is, the compression space V, and the center of rotation Or of the roller 134 together with the first bearing part 1365 . can be rotated around the center. Therefore, the first bearing 1365 may be defined as a rotating ring part, and the second bearing part 1366 may be defined as a rotating plate part.

In this case, the second bearing part 1366 may be formed to be spaced apart by a predetermined distance t3 from the lower surface of the main plate part 1311 or the upper surface of the sub-plate part 1321 with one axial side surface facing it. have. For example, the lower end of the second bearing unit 1366 is slightly longer than the lower end of the first bearing unit 1365 , so that the second bearing unit 1366 moves from the main plate unit 1311 or the sub-plate unit 1321 to the shaft. It may be formed to be spaced apart in the direction. Accordingly, when the second bearing part rotates, it is possible to reduce the mechanical friction loss by suppressing contact with the main plate part 1311 or the sub-plate part 1321 .

In addition, the second bearing part 1366 of the vane bearing 136 provided on both sides in the axial direction of the roller seals both sides of the compression space V constituting the inner space of the cylinder 133 in the axial direction to form a substantial compression space ( V) is formed. Accordingly, a sealing part 1367 for sealing the compression space V may be further provided between the outer peripheral surface of the second bearing part 1366 and the inner peripheral surface 1331 of the cylinder 133 facing it.

The sealing part 1367 may be formed of at least one or more sealing grooves provided in an annular shape along the circumferential direction on the outer circumferential surface of the second bearing part 1366 . 8 and 9 are cross-sectional views showing other embodiments of the sealing part of the vane bearing in FIG. 5 .

For example, the sealing part 1367 may be formed of a single sealing groove as shown in FIG. 5 , or may include a plurality of sealing grooves arranged to be spaced apart by a predetermined interval along the axial direction as shown in FIG. 8 . Accordingly, the sealing part 1367 may be filled with oil or a refrigerant to seal between the compression chambers.

Alternatively, as shown in FIG. 9 , the sealing part 1367 forms a sealing groove 1367a on the outer circumferential surface of the second bearing part 1366, and an annular sealing member 1367b may be inserted into the sealing groove 1367a. have. In this case, the sealing member 1367b may be made of a Teflon material having lubricity.

6 and 7 , a plurality of balls 1363 may be inserted to be positioned between the inner circumferential surface of the outer ring 1361 and the outer circumferential surface of the inner ring 1362 . Accordingly, the inner ring 1362 in contact with the first guide protrusion 1351d1 (not shown) (not shown) of the

vanes

1351 , 1352 and 1353 may perform a relative motion with respect to the outer ring 1361 .

Meanwhile, referring to FIG. 5 , the sub-guide groove 1321a of the sub-bearing 132 and the second guide protrusion 1351d2 (not shown) (not shown) of the

vanes

1351 , 1352 and 1353 are also described above. The side vane bearing 137 may be equally applied. The sub-side vane bearing 137 is composed of an outer ring 1371 , an inner ring 1372 , and a plurality of balls 1373 like the main side vane bearing, and for this, the description of the main side vane bearing 136 is replaced.

Although not shown in the drawings, the sub-side vane bearing 137 may be formed in a shape different from that of the main-side vane bearing 136 . For example, the main side vane bearing 136 may be formed of a ball bearing, and the sub-side vane bearing 137 may be formed of a roller bearing or a bush bearing.

As described above, between the main guide groove 1311a and the first guide protrusion 1351d1 (not shown) (not shown), the sub guide groove 1321a and the second guide protrusion 1351d (not shown) (not shown) As the

vane bearings

136 and 137 made of ball bearings are respectively installed between the The

inner rings

1362 and 1372 of the

vane bearings

136, 137 in contact with the

guide projections

1351d, 1352d, and 1353d of the

vanes

1351,1352,1353 are connected to the outer ring 1361 by a plurality of balls 1363. relative to the Accordingly, while each of the

vanes

1351, 1352, and 1353 has

guide projections

1351d, 1352d, and 1353d, the

guide projections

1351d, 1352d, and 1353d and the

guide grooves

1311a and 1321a can be generated between the The radial friction loss can be significantly reduced.

At the same time, the inner ring 1362 according to the present embodiment includes the

first bearing portions

1365 and 1375 between the

guide projections

1351d, 1352d, and 1353d and the

guide grooves

1311a and 1321a as well as the main plate portion ( 1311) and

second bearing parts

1366 and 1376 extending between the upper surface of the roller 134 and between the sub-plate part 1321 and the lower surface of the roller 134 are provided, and a second bearing part 1366 is provided. 1376 may rotate with roller 134 . Accordingly, the axial friction loss generated between the main bearing 131 and the roller 134 and between the sub bearing 132 and the roller 134 can be significantly reduced.

In this way, while suppressing the friction loss between the vane tip and the cylinder by limiting the protrusion of the vane, the radial friction loss between the guide projection and the guide groove and the axial direction between the main bearing and the roller and between the sub bearing and the roller Friction loss can be significantly reduced. Through this, it is possible to increase the compressor efficiency by reducing the mechanical friction loss in the compression part.

On the other hand, the case of another embodiment of the vane bearing is as follows.

That is, in the above-described embodiment, the inner ring is formed of the first bearing portion and the second bearing portion, but in some cases, the outer ring of the vane bearing may be formed of the first bearing portion and the second bearing portion. For convenience, hereinafter, the main-side vane bearing will be mainly described, and the sub-side vane bearing will be replaced with the description of the main-side vane bearing.

10 is a cross-sectional view showing another embodiment of the vane bearing.

Referring to FIG. 10 , the main side vane bearing 136 according to the present embodiment may include an outer ring 1361 , an inner ring 1362 , and a plurality of balls 1363 . Since the outer ring 1361, the inner ring 1362, and the plurality of balls 1363 are similar to the above-described embodiments, a detailed description thereof is replaced with the description of the above-described embodiment.

However, in this embodiment, the outer ring 1361 may be formed of a first bearing portion 1365 and a second bearing portion 1366, and the inner ring 1362 may be formed in an annular shape. Even in this case, the second bearing part 1366 may be inserted into the compression space V of the cylinder 133 to form an upper surface of the compression space V.

The outer circumferential surface 1365a of the first bearing part 1365 of the outer ring 1361 according to the present embodiment is press-fitted to the inner circumferential surface 1311a1 of the main guide groove 1311a as in the above-described embodiment and may be fixed, or the main guide It may be rotatably inserted with respect to the inner peripheral surface (1311a1) of the groove (1311a).

For example, when the outer ring 1361 is fixed by being press-fitted into the main guide groove 1311a as in the above-described embodiment of the first bearing part 1365, the second bearing part 1366 is also the main plate part 1311. can be fixed to Accordingly, it is possible to more effectively suppress the leakage of the compression space (V) by close contact between the outer peripheral surface (1366a) of the second bearing part (1366) and the inner peripheral surface (1331) of the cylinder (133). In addition, as the second bearing part 1366 is fixed, the inner peripheral surface of the cylinder 133 may be formed in various ways such as a symmetrical oval or an asymmetrical ellipse in which a plurality of ellipses are combined in addition to a circular shape to increase the compression efficiency.

On the other hand, when the outer ring 1361 is rotatably inserted with the first bearing part 1365 with respect to the inner circumferential surface 1311a1 of the main guide groove 1311a, the second bearing part 1366 is the roller as in the above-described embodiment. It can be rotated with (134). Then, not only the radial friction loss in the first bearing part 1365 but also the axial friction loss in the second bearing part 1366 can be suppressed, so that the compressor efficiency can be improved.

On the other hand, another embodiment of the vane bearing is as follows.

That is, in the above-described embodiments, the inner ring or outer ring of the vane bearing is formed of the first bearing portion and the second bearing portion, but in some cases, the inner ring or outer ring of the vane bearing may be formed of only the first bearing portion. For convenience, hereinafter, the main-side vane bearing will be mainly described, and the sub-side vane bearing will be replaced with the description of the main-side vane bearing.

11 is a cross-sectional view showing another embodiment of the vane bearing.

Referring to FIG. 11 , the vane bearing 136 according to the present embodiment may include an outer ring 1361 , an inner ring 1362 , and a plurality of balls 1363 . Since the outer ring 1361, the inner ring 1362, and the plurality of balls 1363 are similar to the above-described embodiments, a detailed description thereof is replaced with the description of the above-described embodiment.

However, in this embodiment, the outer ring 1361 and the inner ring 1362 may be formed of only the first bearing part 1365 , respectively. For example, the inner ring 1362 consists only of a ring-shaped first bearing part 1365 only between the inner circumferential surface 1311a1 of the main guide groove 1311a and the first guide protrusion 1351d1 (not shown) (not shown). can be provided. The shape and size of the first bearing unit 1365 may be the same as the shape and size of the first bearing unit 1365 in the above-described embodiments.

As described above, when the outer ring 1361 and the inner ring 1362 are formed of only the first bearing part 1365 , the inner circumferential surface 1311a1 of the main guide groove 1311a and the first guide protrusion 1351d1 (not shown) (not shown) It is possible to suppress the radial friction loss that occurs between the

In addition, when the second bearing part 1366 is excluded as in the present embodiment, the inner peripheral surface 1331 of the cylinder 133 may be formed in various ways. For example, the inner circumferential surface 1331 of the cylinder 133 may be formed in a symmetrical oval or asymmetrical oval shape in which a plurality of ellipses are combined in addition to a circular shape. Through this, the inner circumferential surface 1331 of the cylinder 133 can be formed so that the compression cycle in the compression space V becomes longer, thereby reducing compression loss due to overcompression.

In addition, when the second bearing part 1366 is excluded as in the present embodiment, a discharge port (not shown) may be formed in the main plate part 1311 or the sub-plate part 1321 . Accordingly, when the discharge port (not shown) is formed on the inner peripheral surface 1331 of the cylinder 133, it is possible to suppress the lack of surface pressure on the

vane tip portions

1351b, 1352b, and 1353b, which may occur. Through this, partial damage to the

vane tip portions

1351b, 1352b, and 1353b or the inner circumferential surface 1331 of the cylinder 133 facing the same can be suppressed, thereby preventing leakage between compression chambers and a decrease in compression efficiency resulting therefrom in advance.

On the other hand, in the above-described embodiments, all of the examples in which the swing bush is provided on the roller have been mainly examined, but the swing bush is not necessarily provided. For example, at least one vane slot is formed on the outer circumferential surface of the roller like a conventional vane rotary compressor, and the same may be applied when the vane is slidably inserted into the vane slot.

Claims

a cylinder having an inner circumferential surface formed in an annular shape;

a main bearing and a sub-bearing respectively provided on both sides of the cylinder in the axial direction to form a compression space together with the cylinder, and a guide groove provided on a side surface forming the compression space;

a roller accommodated in the cylinder and rotating together with the rotating shaft;

at least one vane slidably inserted into the roller and extending in the axial direction with a guide protrusion inserted into the guide groove to slide along the circumferential direction; and

and a bearing member provided between a guide groove of at least one of the main bearing and the sub-bearing and a guide protrusion of the vane.
According to claim 1,

The bearing member is

an outer ring inserted into the inner circumferential surface of the guide groove;

an inner ring provided on the inner side of the outer ring, the inner circumferential surface of which is slidably in contact with the contact surface of the guide protrusion; and

and a sliding member provided between the outer ring and the inner ring to allow the outer ring and the inner ring to move relative to each other.
3. The method of claim 2,

One of the outer ring and the inner ring is further provided with a rotating plate portion extending between the roller and the main bearing and the sub bearing facing them.
According to claim 1,

The bearing member is

a first bearing part provided between at least one of the main bearing and the sub-bearing and the vane facing the same in a radial direction; and

and a second bearing part provided between at least one of the main bearing and the sub-bearing and the roller facing the same in the axial direction.
5. The method of claim 4,

The first bearing part and the second bearing part are formed as a single body.
5. The method of claim 4,

The second bearing part is formed to be thicker than the first bearing part.
5. The method of claim 4,

The first bearing portion is formed in a ring shape, and the second bearing portion is formed in a disk shape.
5. The method of claim 4,

The first bearing part,

an outer ring inserted into a guide groove of at least one of the main bearing and the sub bearing;

an inner ring provided on the inner side of the outer ring, the inner circumferential surface of which is slidably in contact with the guide projection of the vane; and

a sliding member provided between the outer ring and the inner ring to allow the outer ring and the inner ring to perform relative motion;

The second bearing part,

A rotary compressor extending radially from one end of the inner ring or one end of the outer ring of the first bearing part and provided on the axial side of the roller and the axial side of the main bearing and the sub bearing facing the same.
5. The method of claim 4,

The second bearing portion is a rotary compressor in which an axial side thereof is spaced apart from an axial side of the main bearing or the sub-bearing facing it.
5. The method of claim 4,

The second bearing part is inserted into the cylinder so that the outer circumferential surface faces the inner circumferential surface of the cylinder.
11. The method of claim 10,

A sealing part is provided between an outer peripheral surface of the second bearing part and an inner peripheral surface of the cylinder.
11. The method of claim 10,

The second bearing portion has an outer peripheral surface formed in the same shape as an inner peripheral surface of the cylinder.
According to claim 1,

The bearing member is

It is provided between at least one of the main bearing and the sub-bearing and the vane facing the same in the radial direction,

The axial side of the roller is in sliding contact with the axial side of the main bearing and the axial side of the sub bearing facing them.
14. The method of claim 13,

The inner peripheral surface of the cylinder is formed in a circular or oval shape,

A rotary compressor in which a discharge port is formed in at least one of an axial side surface of the main bearing and an axial side surface of the sub bearing.
15. The method according to any one of claims 1 to 14,

A bush groove is formed in the roller, two and a pair of swing bushes are rotatably inserted into the bush groove, and the vane is slidably inserted between the swing bushes.