KR102199140B1 - Rotary compressor - Google Patents

Abstract

The vane rotary compressor according to the present invention is provided on a rotary shaft, one end of the rotary shaft, a cylinder formed in an annular shape, supports the rotary shaft in a radial direction, and is coupled to cover one surface and the other surface of the cylinder, respectively, and compressed together with the cylinder. The main bearing and the sub-bearing forming a space, a roller provided in the compression space, forming a contact point forming a predetermined gap with the cylinder, and being coupled to the rotation shaft to compress the refrigerant according to rotation, so as to be slidable on the roller It is inserted, at least one vane provided to each contact the inner circumferential surface of the cylinder to separate the compression space into a plurality of regions, and formed to couple the cylinder to the main bearing so that the contact point is formed at a preset position It may include a contact point forming portion.

Description

Vane rotary compressor {ROTARY COMPRESSOR}

The present invention relates to a compressor, and to a vane rotary compressor in which a vane protrudes from a rotating roller and contacts an inner circumferential surface of a cylinder to form a compression chamber.

Rotary compressors can be classified into a method in which a vane is slidably inserted into a cylinder to contact a roller, and a method in which a vane is slidably inserted into a roller to contact a cylinder. In general, the former is called a rotary compressor, and the latter is classified as a vane rotary compressor.

In a rotary compressor, a vane inserted into a cylinder is drawn out toward a roller by an elastic force or a back pressure to contact the outer peripheral 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 out by centrifugal force and back pressure to contact the inner peripheral surface of the cylinder.

Rotary compressors independently form 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, the vane rotary compressor continuously forms as many compression chambers as the number of vanes per rotation of the roller, so that each compression chamber sequentially performs suction, compression, and discharge strokes.

Such a vane rotary compressor generally slides while a plurality of vanes rotate together with a roller and the front end surface of the vane is in contact with the inner circumferential surface of the cylinder, so that friction loss increases compared to a general rotary compressor.

In addition, the vane rotary compressor has an inner circumferential surface of the cylinder formed in a circular shape, but recently, the inner circumferential surface of the cylinder is formed in an ellipse or a combination of an ellipse and a circle, thereby reducing friction loss and improving compression efficiency. A vane rotary compressor (hereinafter, a hybrid rotary compressor) has been introduced.

In such a hybrid rotary compressor, due to the characteristic that the inner circumferential surface of the cylinder is formed in an asymmetrical shape, the location where the contact point is formed that separates the region where the refrigerant is introduced and the region where the compression stroke is started and the region where the compressed refrigerant discharge stroke is performed is determined by It will have a great impact.

In particular, in a structure in which the suction port and the discharge port are sequentially formed adjacent to each other in a direction opposite to the rotational direction of the roller in order to achieve a high compression ratio by increasing the compression path as much as possible, the location of the contact point greatly affects the efficiency of the compressor.

However, when assembling the compressor, there is a problem that the efficiency of the compressor is deteriorated as the contact point is not formed at the designed position due to assembly tolerances. Due to this, the deviation of the efficiency of the manufactured compressor became large.

It is an object of the present invention to provide a structure of a rotary compressor in which a contact point between a roller and a cylinder can be easily formed at a designed position by limiting the movement of the cylinder when assembling the compressor.

Further, an object of the present invention is to provide a structure of a rotary compressor capable of forming a contact point between a roller and a cylinder having a certain gap at a designed position.

Further, an object of the present invention is to provide a structure of a rotary compressor capable of preventing the efficiency of the compressor from being changed due to assembly tolerances by forming a contact point between the roller and the cylinder at a certain position.

Further, an object of the present invention is to provide a structure of a rotary compressor in which a contact point between a roller and a cylinder can be easily formed in a vane rotary compressor in which a compression space is formed by a main bearing, a cylinder and a sub bearing.

The rotary compressor according to the present invention is provided on a rotary shaft, one end of the rotary shaft, a cylinder formed in an annular shape, supports the rotary shaft in a radial direction, and is coupled to cover one surface and the other surface of the cylinder, respectively, thereby forming a compression space with the cylinder. The main bearing and the sub-bearing to be formed, a roller provided in the compression space, forming a contact point forming a predetermined gap with the cylinder, and being coupled to the rotation shaft to compress the refrigerant according to rotation, and slidably inserted into the roller, , At least one vane provided to each contact the inner circumferential surface of the cylinder to separate the compression space into a plurality of regions, and a contact point formed to couple the cylinder to the main bearing so that the contact point is formed at a preset position May contain wealth.

In other words, the contact point forming part may couple the cylinder to the main bearing so that the contact point is formed at a preset position.

Here, the contact point may mean a point where the gap between the outer peripheral surface of the roller and the inner peripheral surface of the cylinder is the smallest.

In addition, according to the present invention, the preset gap may be included in the range of 20 μm to 30 μm.

Here, the cylinder includes a suction port formed to suck the refrigerant into a region of the compression space, and a discharge port provided at a position spaced apart from the suction port in a direction opposite to the rotation direction of the compressor, and configured to discharge the compressed refrigerant It may include. Here, the contact point may be provided at a predetermined position between the suction port and the discharge port.

In addition, according to the present invention, the discharge port may include a first discharge port and a second discharge port that are sequentially formed along a rotation direction. Here, the contact point may be formed between the second discharge port and the suction port which are closer to the suction port than the first discharge port.

In addition, according to an embodiment of the present invention, the contact point forming unit may include a pin that is provided to pass through the cylinder in an axial direction, and at least one end thereof is coupled to the main bearing or the sub bearing.

Here, the contact point forming part is formed to be recessed in one surface of the main bearing facing the cylinder to receive at least a part of the pin by passing through the first groove and the cylinder in the axial direction to receive one end of the pin It may include a pin receiving hole. In this case, the pin receiving hole may be formed to overlap the first groove in an axial direction while the cylinder and the main bearing are aligned so that the contact point is formed.

In addition, the contact point forming part may further include a second groove formed to be recessed in one surface of the sub-bearing facing the cylinder to receive the other end of the pin. In this case, the pin receiving hole may be formed to overlap the second groove in an axial direction while the cylinder and the main bearing are aligned so that the contact point is formed.

In addition, according to a modified example of an embodiment of the present invention, the contact point forming part is in a state in which the cylinder and the main bearing are aligned so that the contact point and a protrusion protruding from one surface of the main bearing facing the cylinder are formed. It may include a protrusion receiving groove formed to overlap the protrusion in the axial direction to receive the protrusion.

Here, the protrusion and the protrusion receiving groove may be provided in at least two or more.

In addition, according to another modified example of an embodiment of the present invention, the contact point forming unit accommodates a cylinder formed in the main bearing to accommodate at least a portion of the cylinder in a state in which the cylinder and the main bearing are aligned so that the contact point is formed. May contain wealth.

Here, the cylinder may be coupled to the male bearing as it is fitted into the cylinder receiving portion.

Further, the cylinder receiving portion may be formed by at least two protruding protrusions protruding from one surface of the main bearing facing the cylinder.

A rotary compressor according to another embodiment of the present invention includes a rotating shaft, a cylinder provided at one end of the rotating shaft, formed in an annular shape, and supporting the rotating shaft in a radial direction, and are coupled to cover one surface and the other surface of the cylinder. A main bearing and a sub-bearing forming a compression space together with, a roller provided in the compression space, forming a contact point forming a predetermined gap with the cylinder, and being coupled to the rotation shaft to compress the refrigerant according to rotation, and the roller It may include at least one vane that is slidably inserted and is provided to separate the compression space into a plurality of regions by contacting the inner circumferential surface of the cylinder. Here, the main bearing may include a contact point forming portion formed integrally with the cylinder, and configured to form the contact point at a preset position when the sub bearing and the cylinder are coupled.

Furthermore, the main bearing may include a first shaft receiving part that receives at least a portion of the rotation shaft and supports the rotation shaft in a radial direction. In addition, the sub-bearing may include a second bearing unit that receives at least a portion of the rotation shaft and supports the rotation shaft in a radial direction.

Here, the first shaft and the second shaft may position the rotation shaft so that the roller forms the contact point at a preset position.

According to the present invention, since the radial movement of the cylinder is limited when the compressor is assembled by the contact point forming part, it is possible to prevent the relative position with respect to the main bearing from being changed. Accordingly, the contact point between the roller and the cylinder can be easily formed.

Further, by the contact point forming portion, the relative position in the direction perpendicular to the axial direction of the cylinder and the main bearing is adjusted, so that the contact point P1 can be formed at the designed position.

Further, according to the present invention, since the gap between the roller and the cylinder can be uniformly formed at the position where the contact point between the roller and the cylinder is designed by the contact point forming part, the gap is formed too small to cause frictional wear between the roller and the cylinder. It is possible to prevent a decrease in volume efficiency due to leakage of the refrigerant through the contact point due to occurrence of or the gap being formed too large.

In addition, according to the present invention, since the contact point between the roller and the cylinder can be formed at the designed position, the decrease in efficiency that may occur due to the contact point not being formed at the designed position can be prevented. Further, it is possible to prevent the efficiency of the compressor from varying due to assembly tolerances as the contact point between the roller and the cylinder is formed at a certain position for each manufactured compressor. Due to this, the deviation of the efficiency of the compressor due to the assembly tolerance may be reduced, so that the efficiency of the manufactured compressor may be leveled upward.

Due to the structural complexity, when assembling a vane rotary compressor in which a compression space is formed by a main bearing, a cylinder and a sub bearing made of separate members, the contact point between the roller and the cylinder can be easily formed, so that productivity can be increased. .

1 is a view showing a longitudinal sectional view of a rotary compressor according to the present invention.
2 is a cross-sectional view of a compression unit according to AA in the vane rotary compressor shown in FIG. 1.
3A to 3D are cross-sectional views illustrating a process in which the refrigerant is sucked, compressed, and discharged from the cylinder according to the present embodiment.
4 is an exploded perspective view of a compression mechanism of a rotary compressor according to an embodiment of the present invention.
5 is a view showing a vertical cross-sectional view of the compression mechanism of FIG. 4.
6A is a perspective view as viewed from below of a coupling relationship between a main bearing and a cylinder according to a modified example of an embodiment.
6B is a cross-sectional view showing a combined state of the main bearing and the cylinder shown in FIG. 6A.
7A is a perspective view as viewed from below of a coupling relationship between a main bearing and a cylinder according to another modification of the embodiment.
7B is a cross-sectional view showing a combined state of the main bearing and the cylinder shown in FIG. 7A.
8A is a perspective view as viewed from below of a formation relationship between a main bearing and a cylinder according to another embodiment of the present invention.
8B is a cross-sectional view showing a combined state of the main bearing and the cylinder shown in FIG. 8A.

Hereinafter, a vane rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

1 is a longitudinal cross-sectional view of a vane rotary compressor according to the present invention, and FIG. 2 is a cross-sectional view of a compression unit according to A-A in the vane rotary compressor shown in FIG. 1.

Referring to Figure 1, the vane rotary compressor according to the present invention, a drive motor 120 is installed inside the casing 110, one side of the drive motor 120 is mechanically connected by a rotating shaft 123 The compression unit 130 is installed.

The casing 110 may be divided into a vertical type or a horizontal type according to the installation mode of the compressor. The vertical type is a structure in which the driving motor and the compression unit are disposed on both sides of the upper and lower sides along the axial direction, and the horizontal type is a structure in which the driving motor and the compression unit are disposed on both left and right sides.

The drive motor 120 serves to provide power to compress the refrigerant. The drive 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 mounted on the inner circumferential surface of the cylindrical casing 110 by a method such as shrink fit. For example, the stator 121 may be fixedly installed on the inner peripheral surface of the intermediate shell 110b.

The rotor 122 is disposed to be spaced apart from the stator 121 and is located inside the stator 121. The rotation shaft 123 is pressed into the center of the rotor 122 to be coupled. When power is applied to the stator 121, the rotor 122 rotates according to the magnetic interaction between the stator 121 and the rotor 122. Accordingly, the rotation shaft 123 coupled to the rotor 122 performs concentric rotation with the rotor 122.

An oil passage 125 is formed in the axial direction at the center of the rotation shaft 123, and oil through holes 126a and 126b are formed in the middle of the oil passage 125 toward the outer circumferential surface of the rotation shaft 123. The oil through holes 126a and 126b are composed of a first oil through hole 126a belonging to the range of the first shaft receiving part 1311 and a second oil through hole 126b belonging to the range of the second shaft receiving part 1321. One first oil through hole 126a and one second oil through hole 126b may be formed, respectively, or may be formed in plurality.

An oil feeder 150 is installed in the middle or bottom of the oil passage 125. Accordingly, when the rotation shaft 123 rotates, the oil filled in the lower portion of the casing is pumped by the oil feeder 150 to be sucked up along the oil passage 125 and then through the second oil through hole 126b. It is supplied to the main bearing surface 1311a through the first oil through hole 126b of the sub-bearing surface 1321a.

The first oil through hole 126a is preferably formed to overlap with the first oil groove 1311b and the second oil through hole 126b with the second oil groove 1321b. Through this, oil supplied to the bearing surface of the main bearing 131 and the bearing surfaces 1311a and 1321a of the sub-bearing 132 through the first oil through hole 126a and the second oil through hole 126b will be described later. It can be quickly introduced into the second main pocket 1313b and the second sub-side pocket 1323b.

The compression unit 130 includes a cylinder 133 in which a compression space 410 is formed by a main bearing 131 and a sub bearing 132 installed on both sides in the axial direction.

1 and 2, the main bearing 131 and the sub bearing 132 are fixedly installed on the casing 110 and are installed to be spaced apart from each other along the rotation shaft 123. The main bearing 131 and the sub bearing 132 support the rotating shaft 123 in the radial direction and at the same time serve to support the cylinder 133 and the roller 134 in the axial direction. Accordingly, the main bearing 131 and the sub bearing 132 are provided with a bearing part 1311 and 1321 for radially supporting the rotating shaft 123, and a plan extending in the radial direction from the bearing part 1311 and 1321. Each of the branches 1312 and 1322 may be formed. For convenience, the bearing portion of the main bearing 131 is the first bearing portion 1311 and the flange portion as the first flange portion 1312, and the bearing portion of the sub bearing 132 is the second bearing portion 1321 and the second flange portion. It is defined as (1322).

The first bearing portion 1311 and the second bearing portion 1321 are formed in a bush shape, respectively, and the first flange portion and the second flange portion are formed in a disk shape. A radial bearing surface (hereinafter, abbreviated as a bearing surface or first bearing surface) 1311a, which is an inner circumferential surface of the first bearing portion 1311, has a first oil groove 1311b, and an inner peripheral surface of the second bearing portion 1321 In the radial bearing surface (hereinafter, abbreviated as a bearing surface or a second bearing surface) 1321a, second oil grooves 1321b are respectively formed. The first oil groove 1311b is formed in a straight line or oblique line between the upper and lower ends of the first shaft receiving portion 1311, and the second oil groove 1321b is a straight or oblique line between the upper and lower ends of the second shaft receiving portion 1321. Is formed by

A first communication channel 1315 to be described later is formed in the first oil groove 1311b, and a second communication channel 1325 to be described later is formed in the second oil groove 1321b. The first communication channel 1315 and the second communication channel 1325 are for guiding the oil flowing into the respective bearing surfaces 1311a and 1321a to the main side back pressure pocket 1313 and the sub side back pressure pocket 1323. will be.

The first flange portion 1312 is formed with a main back pressure pocket 1313, and the second flange portion 1322 is formed with a sub-side back pressure pocket 1323, respectively. The main back pressure pocket 1313 is a first main pocket 1313a and a second main pocket 1313b, and the sub-side back pressure pocket 1323 is a first sub-side pocket 1323a and a second sub-side pocket ( 1323b).

The first main pocket 1313a and the second main pocket 1313b are formed at a predetermined interval along the circumferential direction, and the first sub-side pocket 1323a and the second sub-side pocket 1323b are in the circumferential direction. It is formed along a predetermined interval.

The first main pocket 1313a forms a lower pressure than the second main pocket 1313b, for example, an intermediate pressure between the suction pressure and the discharge pressure, and the sub-side first pocket 1323a is A lower pressure than the two pockets 1323b, for example, an intermediate pressure substantially equal to that of the main first pocket 1313a is formed. The first main pocket 1313a is a micro-passage between the first bearing protrusion 1314a on the main side and the upper surface 134a of the roller 134, which will be described later, and the first sub-side pocket 1323a is a sub-side, which will be described later. 1 Oil passes through the micro-passage between the bearing protrusion 1314a and the lower surface 134b of the roller 134, respectively, and flows into the first pockets 1313a and 1323a on the main side and the sub side, thereby reducing pressure to form an intermediate pressure. do. However, the main-side second pocket 1313b and the sub-side second pocket 1323b are provided with the main bearing surface 1311a and the sub-bearing surface 1321a through the first oil through hole 126a and the second oil through hole 126b. Since the oil flowing into the main and sub-side second pockets 1313b and 1323b through the first communication channel 1315 and the second communication channel 1325 to be described later, the discharge pressure or pressure at almost the discharge pressure state Will be maintained.

The cylinder 133 has an elliptical inner circumferential surface forming the compression space (V). The inner circumferential surface of the cylinder 133 may be formed in a symmetrical oval shape having a pair of long and short axes. However, in this embodiment, the inner circumferential surface of the cylinder 133 is formed in an asymmetrical elliptical shape having several pairs of long and short axes. This asymmetrical elliptical cylinder 133 is referred to as a conventional hybrid cylinder, and this embodiment describes a vane rotary compressor to which a hybrid cylinder is applied. However, the present invention may be applied not only to a hybrid cylinder, but also to a cylinder having a symmetrical ellipse shape.

As shown in FIG. 2, the hybrid cylinder (hereinafter, abbreviated as a cylinder) 133 according to the present embodiment may have a circular shape, but is fixed to the inner peripheral surface of the casing 110 even if it is non-circular. This can be enough. Of course, the main bearing 131 or the sub bearing 132 is fixed to the inner circumferential surface of the casing 110, and the cylinder 133 is bolted to the main bearing 131 or the sub bearing 132 fixed to the casing 110. It can also be fastened.

In addition, an empty space portion is formed in the central portion of the cylinder 133 to form a compression space (V) including an inner peripheral surface. This empty space is sealed by the main bearing 131 and the sub bearing 132 to form a compression space (V). A roller 134 having a circular outer peripheral surface to be described later is rotatably coupled to the compression space V.

In the inner circumferential surface 133a of the cylinder 133, the suction ports on both sides of the circumferential direction are respectively centered at the first point P1 where the inner circumferential surface 133a of the cylinder 133 and the outer circumferential surface 134c of the roller 134 are in close contact with each other. 1331 and discharge ports 1332a and 1332b are formed.

That is, the suction port 1331 may be formed on the current side based on the compression path (rotation direction), and the discharge ports 1332a and 1332b may be formed on the rest side in the direction in which the refrigerant is compressed. In other words, the suction port 1331 may be formed to be spaced apart by a predetermined interval in the counterclockwise direction from the location where the discharge ports 1332a and 1332b are formed. It may be located between the suction port 1331 and the discharge port 1332a on the inner peripheral surface (133a) of the cylinder 133.

The suction port 1331 is directly connected to the suction pipe 113 penetrating the casing 110, and the discharge ports 1332a and 1332b communicate with the inner space S of the casing 110 to penetrate the casing 110 It is indirectly connected to the discharge pipe 114 to be combined. Accordingly, the refrigerant is directly sucked into the compression space (V) through the suction port (1331), while the compressed refrigerant is discharged into the inner space (S) of the casing 110 through the discharge ports (1332a) (1332b) and then discharged. It is discharged to the pipe 114. Accordingly, the inner space (S) of the casing 110 is maintained in a high-pressure state forming the discharge pressure.

More specifically, the high-pressure refrigerants discharged from the discharge ports 1332a and 1332b stay in the internal space S adjacent to the compression unit 130. Meanwhile, since the main bearing 131 is fixed to the inner circumferential surface of the casing 110, the upper and lower sides of the inner space S of the casing 110 are bordered. In this case, the high-pressure refrigerants staying in the inner space S adjacent to the compression unit 130 rises through the discharge passage 1316, and goes out through the discharge pipe 114 provided on the upper side of the casing 110. Can be discharged.

The discharge passage 1316 may be formed by penetrating the flange portion 1312 of the main bearing 131 in the axial direction, and a sufficient passage area may be secured so as not to generate passage resistance. More specifically, the discharge passage 1316 may be formed to extend along the circumferential direction in a region that does not overlap with the cylinder 133 in the axial direction. That is, the discharge passage 1316 may be formed to form an arc shape.

In addition, the discharge passage 1316 may be formed of a plurality of holes spaced apart in the circumferential direction. As such, as the maximum flow path area is secured, flow resistance may be reduced when the high-pressure refrigerant moves to the discharge pipe 114 provided on the upper side of the casing 110.

In addition, a separate suction valve is not installed at the suction port 1331, while discharge valves 1335a and 1335b for opening and closing the discharge ports 1332a and 1332b are provided at the discharge ports 1332a and 1332b. 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, the discharge valves 1335a and 1335b may be variously applied as necessary, such as a piston valve, in addition to a reed valve.

In addition, when the discharge valves 1335a and 1335b are reed valves, valve grooves 1336a and 1336b are formed on the outer peripheral surface of the cylinder 133 so that the discharge valves 1335a and 1335b can be mounted. Accordingly, the lengths of the discharge ports 1332a and 1332b are reduced to a minimum, thereby reducing the dead volume. The valve grooves 1336a and 1336b 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 1332a and 1332b may be provided along a compression path (compression progress direction). For convenience, the plurality of discharge ports 1332a and 1332b include the discharge ports located on the upstream side with respect to the compression path as the secondary discharge ports (or the second discharge ports) 1332b, and the discharge ports located on the downstream side are the main discharge ports (or 1 discharge port) 1332a.

Referring to the above-described first point P, the first outlet 1332a is formed adjacent to the first point P1, and the second outlet 1332b is counterclockwise from the first outlet 1332a. It is formed in a spaced position.

However, the sub-discharge port 1332b is not necessarily a necessary configuration, and may be selectively formed as necessary. For example, as in the present embodiment, if the inner circumferential surface 133a of the cylinder 133 forms a long compression period as described later to appropriately reduce the overcompression of the refrigerant, the secondary discharge port may not be formed. However, in order to reduce the overcompression amount of the compressed refrigerant to a minimum, a secondary discharge port 1332a as in the prior art should be formed in front of the main discharge port 1332b, that is, upstream of the main discharge port 1332b based on the compression progress direction. I can.

Meanwhile, the roller 134 described above is rotatably provided in the compression space V of the cylinder 133. The roller 134 has an outer circumferential surface 134c formed in a circular shape, and a rotation shaft 123 is integrally coupled to the center of the roller 134. Accordingly, the roller 134 has a center (Or) that matches the axis center (Os) of the rotation shaft 123, and performs concentric rotation with the rotation shaft 123 around the center (Or) of the roller 134. Is done.

Hereinafter, the first point P1 is referred to as a contact point for convenience. The center (Or) of the roller 134 is eccentric with respect to the center (Oc) of the cylinder 133, that is, the center (Oc) of the inner space of the cylinder 133, so that one side of the outer peripheral surface (134c) of the roller 134 is a cylinder It almost comes into contact with the inner peripheral surface 133a of 133.

The outer circumferential surface 134c of the roller 134 does not actually contact the inner circumferential surface 133a of the cylinder 133, but the outer circumferential surface 134c of the roller 134 and the inner circumferential surface 133a of the cylinder 133 are spaced apart and friction Even if no damage occurs, the high-pressure refrigerant in the discharge pressure region through the outer circumferential surface 134c of the roller 134 and the inner circumferential surface 133a of the cylinder 133 is close enough to be restricted from leaking into the suction pressure region. Since it is necessary, for convenience, the first point P1 will be referred to as the contact point P1 and described.

When the point of the cylinder 133 at which one side of the roller 134 almost contacts is referred to as the contact point P1, the center line passing through the contact point P1 and the center of the cylinder 133 is the inner peripheral surface 133a of the cylinder 133 It can be a position corresponding to the short axis of the elliptic curve forming the.

The roller 134 has a vane slot 342 formed at an appropriate location along the circumferential direction on its outer circumferential surface, and the vanes 1351, 1352, and 1353 are slidably coupled to each of the vane slots 1333a, 1333b, and 1333c. The vane slots 1333a, 1333b, and 1333c may be formed in a radial direction based on the center of the roller 134, but in this case, it is difficult to sufficiently secure the length of the vane. Therefore, it may be preferable that the vane slots 1333a, 1333b, and 1333c are formed to be inclined by a predetermined inclination angle with respect to the radial direction to sufficiently secure the length of the vane.

Here, the direction in which the vanes 1351,1352,1353 are inclined is a direction opposite to the rotational direction of the roller 134, that is, the front end surface of the vanes 1351,1352,1353 in contact with the inner circumferential surface 133a of the cylinder 133 Inclination toward the rotational direction of the roller 134 may be desirable because the compression start angle can be pulled toward the rotational direction of the roller 134 so that compression can start quickly.

In addition, oil (or refrigerant) flows into the rear side of the vanes 1351,1352,1353 at the inner ends of the vanes 1333a, 1333b, 1333c, so that the vanes 1351, 1352, and 1353 are inserted into the cylinder 133. Back pressure chambers 1334a, 1334b, and 1334c that can be added in the direction of the inner circumferential surface are formed. The back pressure chambers 1334a, 1334b and 1334c are sealed by the main bearing 131 and the sub bearing 132. These back pressure chambers 1334a, 1334b, and 1334c may each independently communicate with the back pressure pockets 1313 and 1323, but a plurality of back pressure chambers 1334a, 1334b and 1334c are provided by the back pressure pockets 1313 and 1323. It may be formed to communicate with each other.

The back pressure pockets 1313 and 1323 may be formed on the main bearing 131 and the sub bearing 132, respectively, as shown in FIG. 1. However, in some cases, only one of the main bearing 131 and the sub bearing 132 may be formed. This embodiment describes an example in which the back pressure pockets 1313 and 1323 are formed in both the main bearing 131 and the sub bearing 132. For convenience, a back pressure pocket formed on the main bearing 131 is defined as a main back pressure pocket 1313 and a back pressure pocket formed on the sub bearing 132 is defined as a sub-side back pressure pocket 1323.

As described above, the main back pressure pocket 1313 is again the main first pocket 1313a and the main second pocket 1313b, and the sub-side back pressure pocket 1323 is the sub-side first pocket 1323a and It consists of a second sub-side pocket 1323b. Further, both the main side and the sub side have a higher pressure in the second pocket than in the first pocket. Accordingly, the main first pocket 1313a and the sub-side first pocket 1323a communicate with the vane chamber to which the vane located relatively upstream (from the suction stroke to the discharge stroke) belongs, and the main second pocket 1323a The pocket 1313b and the sub-side second pocket 1323b may communicate with the vane chamber to which the vane is located relatively downstream (from the discharge stroke to the suction stroke) among the vanes.

As for the vanes 1351,1352,1353, the vane closest to the contact point P is referred to as the first vane 1351, followed by the second vane 1352 and the third vane 1352. , Between the first vane (1351) and the second vane (1352), between the second vane (1352) and the third vane (1353), between the third vane (1353) and the first vane (1351) are all They are separated by the same circumferential angle.

Therefore, the compression chamber formed by the first vane 1351 and the second vane 1352 is the first compression chamber V1, and the compression chamber formed by the second vane 1352 and the third vane 1352 is a second compression chamber. (V2), when the compression chamber formed by the third vane 1353 and the first vane 1351 is referred to as the third compression chamber V3, all compression chambers V1, V2, V3 have the same volume at the same crank angle. Will have. Here, the first compression chamber (V1) may be referred to as a suction chamber (V1), and the third compression chamber (V3) may be referred to as a discharge chamber (V3).

The vanes 1351,1352,1353 are formed in a substantially rectangular parallelepiped shape. Here, among both ends of the vane in the longitudinal direction, the surface in contact with the inner circumferential surface 133a of the cylinder 133 is referred to as the front end surface of the vane, and the surface facing the back pressure chambers 1334a, 1334b, 1334c is defined as the rear end surface.

The front end surfaces of the vanes 1351,1352,1353 are formed in a curved shape so as to be in line contact with the inner circumferential surface 133a of the cylinder 133, and the rear end surfaces of the vanes 1351,1352,1353 are back pressure chambers 1334a, 1334b, 1334c) may be inserted into a flat shape to receive back pressure evenly.

In the drawings, reference numeral 110a denotes an upper shell, and 110c denotes a lower shell. The upper shell 110a and the lower shell 110c form the exterior of the compressor 100 together with the intermediate shell 110c, and may seal the inner space S from the outside.

In the vane rotary compressor equipped with the hybrid cylinder as described above, power is applied to the drive motor 120 so that the rotor 122 of the drive motor 120 and the rotation shaft 123 coupled to the rotor 122 are When it rotates, the roller 134 rotates together with the rotation shaft 123.

Then, the centrifugal force generated by the rotation of the rollers 134 of the vanes 1351,1352,1353 and the back pressure of the back pressure chambers 1334a, 1334b, 1334c provided at the rear side of the vanes 1351,1352,1353 As a result, the vane slots 1333a, 1333b, and 1333c are drawn out, so that the front end surfaces of the vanes 1351, 1352, and 1353 come in contact with the inner peripheral surface 133a of the cylinder 133.

Then, the compression space (V) of the cylinder 133 is compressed by a plurality of vanes (1351, 1352, 1352) as many as the number of the vanes (1351, 1352, 1352) (including the suction chamber or the discharge chamber) (V1 , V2, V3 are formed, and each compression chamber (V1, V2, V3) moves along the rotation of the roller 134 by the shape of the inner peripheral surface 133a of the cylinder 133 and the eccentricity of the roller 134. The volume is variable, and the refrigerant filled in each of the compression chambers V1, V2, and V3 moves along the rollers 134 and vanes 1351, 1352, and 1353 to suck, compress and discharge the refrigerant.

Looking at this in more detail as follows. 3A to 3D are cross-sectional views illustrating a process in which a refrigerant is sucked, compressed, and discharged from the cylinder according to the present embodiment. A cross-sectional view showing a process in which refrigerant is sucked, compressed, and discharged from the cylinder according to the present embodiment. In FIGS. 3A to 3D, the main bearing is projected and shown, and the sub-bearing not shown in the drawing is the same as the main bearing.

As shown in (a) of FIG. 3, the volume of the first compression chamber V1 continuously increases until the first vane 1351 passes through the suction port 1331 and the second vane 1352 reaches the completion point of suction. As a result, the refrigerant continuously flows into the first compression chamber V1 from the suction port 1331.

At this time, the first back pressure chamber 1334a provided on the rear side of the first vane 1351 is provided in the first pocket 1313a of the main back pressure pocket 1313 and on the rear side of the second vane 1352. The second back pressure chamber 137b is exposed to the second pocket 1313b of the main back pressure pocket 1313, respectively. Accordingly, an intermediate pressure is formed in the first back pressure chamber 1334a, and a discharge pressure or a pressure close to the discharge pressure (hereinafter, defined as discharge pressure) is formed in the second back pressure chamber 1334a, and the first vane 1351 is intermediate By pressure, the second vanes 1352 are each pressurized by a discharge pressure and are in close contact with the inner circumferential surface of the cylinder 133.

As shown in (b) of FIG. 3, when the second vane 1352 proceeds to the compression stroke past the suction completion point (or compression start time), the first compression chamber V1 is sealed and the roller 134 And moves in the direction of the discharge port. During this process, the volume of the first compression chamber V1 is continuously decreased, and the refrigerant in the first compression chamber V1 is gradually compressed.

At this time, when the refrigerant pressure in the first compression chamber V1 increases, the first vane 1351 may be pushed toward the first back pressure chamber 1334a, and accordingly, the third compression chamber V1 precedes the third compression chamber. Refrigerant leakage may occur while communicating with the chamber V3. Therefore, in order to prevent leakage of the refrigerant, a higher back pressure must be formed in the first back pressure chamber 1334a.

Referring to the drawing, the back pressure chamber 1334a of the first vane 1351 is positioned at a stage before entering the second main pocket 1313b through the first main pocket 1313a. Accordingly, the back pressure formed in the first back pressure chamber 1334a of the first vane 1351 is soon raised from the intermediate pressure to the discharge pressure. Accordingly, as the back pressure of the first back pressure chamber 1334a increases, it is possible to prevent the first vane 1351 from being pushed backward.

As shown in (c) of FIG. 3, when the first vane 1351 passes through the first discharge port 1332a and the second vane 1352 does not reach the first discharge port 1332a, the first compression chamber As V1 communicates with the first discharge port 1332a, the first discharge port 1332a is opened by the pressure of the first compression chamber V1. Then, a part of the refrigerant in the first compression chamber V1 is discharged to the inner space of the casing 110 through the first discharge port 1332a, so that the pressure in the first compression chamber V1 is lowered to a predetermined pressure. Of course, when there is no first discharge port 1332a, the refrigerant in the first compression chamber V1 is not discharged and moves further toward the second discharge port 1332b, which is the main discharge port.

At this time, the volume of the first compression chamber V1 is further reduced, so that the refrigerant in the first compression chamber V1 is further compressed. However, the first back pressure chamber 1334a in which the first vane 1351 is accommodated is in a state in which it is completely in communication with the second main pocket 1313b, so that the first back pressure chamber 1334a almost forms a discharge pressure. Then, the first vane 1351 is prevented from being pushed out by the back pressure of the first back pressure chamber 1334a, and leakage between the compression chambers can be suppressed.

As shown in (d) of FIG. 3, when the first vane 1351 passes through the second discharge port 1332b and the second vane 1352 reaches the discharge start time, the refrigerant pressure in the first compression chamber V1 As the second discharge port 1332b is opened, the refrigerant in the first compression chamber V1 is discharged into the inner space of the casing 110 through the second discharge port 1332b.

At this time, the back pressure chamber 1334a of the first vane 1351 passes through the main second pocket 1313b, which is a discharge pressure region, and is just before entering the main first pocket 1313a, which is an intermediate pressure region. Accordingly, the back pressure formed in the back pressure chamber 1334a of the first vane 1351 is soon lowered from the discharge pressure to the intermediate pressure.

On the other hand, the back pressure chamber 1334b of the second vane 1352 is located in the main second pocket 1313b, which is a discharge pressure region, and a back pressure corresponding to the discharge pressure is formed in the second back pressure chamber 1334b.

Accordingly, the intermediate pressure Pm between the suction pressure and the discharge pressure is at the rear end of the first vane 1351 located in the first pocket 1313a on the main side, and the second pocket 1313b is located in the second pocket 1313b. A discharge pressure Pd (actually a pressure slightly lower than the discharge pressure) is formed at the rear end of the vane 1352. In particular, the second main pocket 1313b communicates directly with the oil passage 125 through the first oil through hole 126a and the first communication passage 1315, thereby communicating with the main second pocket 1313b. It is possible to prevent the pressure of the second back pressure chamber 1334b from rising above the discharge pressure Pd. Accordingly, an intermediate pressure Pm, which is significantly lower than the discharge pressure Pd, is formed in the first pocket 1313a on the main side, thereby increasing the mechanical efficiency between the cylinder 133 and the vane 135, and In the pocket 1313b2, as a pressure slightly lower than the discharge pressure Pd or the discharge pressure Pd is formed, the vanes are properly adhered to the cylinder, thereby suppressing leakage between the compression chambers and improving mechanical efficiency.

On the other hand, in the vane rotary compressor having a hybrid cylinder as in the present invention, since the inner peripheral surface 133a of the cylinder 133 is formed in an asymmetrical shape, the efficiency of the compressor varies depending on the position of the contact point P1. Hereinafter, a structure that can be assembled so that the contact point P1 is formed at a predetermined position will be described.

4 is a view showing an exploded perspective view of a compression mechanism of a rotary compressor according to an embodiment of the present invention, and FIG. 5 is a view showing a vertical cross-sectional view of the compression mechanism of FIG. 4.

The electric compressor according to the present invention includes a contact point forming part 140 formed to assemble the contact point P1 to be formed at a predetermined position when assembling the compressor. The contact point forming part 140 regulates the relative position of the cylinder 133 with respect to the main bearing 131 when assembling the compressor, and after the assembly is completed, the outer peripheral surface 134c of the roller 134 and the inner peripheral surface of the cylinder 133 ( A contact point P1 between 133a) may be formed.

More specifically, the contact point forming part 140 may include a pin 141, a pin receiving hole 142b, a first groove 142a, and a second groove 142c.

The pin 141 may be provided through the cylinder 133 in the axial direction. More specifically, the pin 141 may be formed in a cylindrical shape having a predetermined diameter and length. The pin 141 may be inserted into the cylinder 133 parallel to the axial direction.

A pin receiving hole 142b may be formed in one area of the cylinder 133 into which the pin 141 is inserted. The pin receiving hole 142b may be formed by penetrating the cylinder 133 in the axial direction. Also, the pin receiving hole 142b may be formed in a region that does not interfere with the first and second discharge ports 1332a and 1322b, the suction port 1331, and the like.

In addition, the pin receiving hole 142b may be formed to have a circular cross section so as to correspond to the shape of the outer peripheral surface of the pin 141. Here, the inner diameter of the pin receiving hole 142b and the outer diameter of the pin 141 may be formed to have substantially the same size. Accordingly, the pin 141 may be coupled to be fitted into the pin receiving hole 142b.

Meanwhile, one end of at least one of one end or the other end of the pin 141 may be coupled to the main bearing 131 or the sub bearing 132. The pin 141 may be formed to extend longer than the length of the cylinder 133 in the axial direction. In this case, since the pin 141 is inserted into the cylinder 133 in parallel with the axial direction, at least one of one end or the other end is provided to protrude from the cylinder 133.

Here, the protruding portion of the pin 141 may be inserted into the first groove 142a formed in the main bearing 131 or the second groove 142b formed in the sub bearing 132.

The first groove 142a may be formed to be recessed in one surface of the main bearing 131 facing the cylinder 133. Like the pin receiving hole 142b, the first groove 142a may be formed to have a circular cross section corresponding to the outer peripheral surface of the pin 141. The inner diameter of the first groove 142a may also be formed substantially the same as the outer diameter of the pin 141 like the pin receiving hole 142b.

The roller 134 is coupled to the rotation shaft 123, and the rotation shaft 123 is supported in the radial direction by the first number of shaft portions 1311 provided in the main bearing 131, so that the main bearing 131 and the cylinder 133 ), the location of the contact point P1 is different.

Therefore, the first groove 142a in the state in which the cylinder 133 and the main bearing 131 are aligned so that the contact point P1 between the outer peripheral surface 134c of the roller 134 and the inner peripheral surface 133a of the cylinder 133 is formed. ) And the pin receiving hole 142b may be formed to overlap in the axial direction.

On the other hand, in the structure in which the compression space V is formed by the main bearing 131, the cylinder 133, and the sub bearing 132, the rotation shaft 123 is provided in the sub bearing 132 and the second shaft receiving part 1321 It can also be supported in the radial direction by. Therefore, since the formation position of the contact point P1 is also different depending on the relative position between the sub bearing 132 and the cylinder 133, in order to form the contact point P1 at a certain position, the main bearing 131 and the cylinder ( It becomes relatively important to regulate the relative position between the 133 and the sub bearings 132.

Accordingly, the pin 141 may be inserted into and coupled to the sub bearing 132 as well as the main bearing 131. In this case, the pin 141 may be provided not only to protrude from one surface toward the main bearing 131 from the cylinder 133, but also to protrude from the other surface opposite to the one surface. That is, the pin 141 may be provided so as to protrude from the cylinder 133 toward the sub bearing 132 from the other surface.

A portion of the pin 141 protruding from the other surface of the cylinder 133 may be inserted into the second groove 142c of the sub bearing 132. The second groove 142c may be formed to be recessed in one surface of the main bearing 131 facing the cylinder 133.

In addition, the second groove 142c may be formed to have a circular cross-section corresponding to the outer peripheral surface of the pin 141, similar to the pin receiving hole 142b. The inner diameter of the second groove 142c may also be formed substantially the same as the outer diameter of the pin 141 like the pin receiving hole 142b. In addition, the second groove 142c and the pin receiving hole 142b may be formed to overlap in the axial direction while the cylinder 133 and the sub-bearing 132 are aligned so that the contact point P1 is formed.

That is, the first groove 142a, the pin receiving hole 142b, and the second groove 142c form a continuous cylindrical space, and the pin 141 is inserted into the cylindrical space, and the roller 134 at the designed position A contact point P1 between the outer circumferential surface 134c and the inner circumferential surface 133a of the cylinder 133 may be formed.

Meanwhile, as described above, the gap between the outer circumferential surface 134c of the roller 134 and the inner circumferential surface 133a of the cylinder 133 at the contact point P1 is spaced so as not to cause friction, but the refrigerant is removed through the gap. They should be close enough to prevent leakage. From this point of view, a gap between the outer peripheral surface 134c of the roller 134 and the inner peripheral surface 133a of the cylinder 133 required at the contact point P1 may be in the range of 20 μm to 30 μm.

In order to form a gap in the above-described range while the contact point P1 is formed at the set position, according to the present invention, a plurality of contact point forming portions 140 may be provided. For example, when two contact point forming portions 140 are provided, the contact point P1 may be formed to be positioned between the contact point forming portions 140. More specifically, the contact point P1 and the contact point forming part 140 may be provided to be positioned on a virtual straight line.

Meanwhile, FIG. 6A is a perspective view showing a coupling relationship between a main bearing and a cylinder according to a modified example of an embodiment, and FIG. 6B is a cross-sectional view showing a combined state of the main bearing and the cylinder shown in FIG. 6A.

In this embodiment, the contact point forming part 240 may include a protrusion 241 and a protrusion receiving groove 242 in which the protrusion 241 is accommodated. More specifically, the protrusion 241 may be formed to protrude from one surface of the main bearing 131 facing the cylinder 133. Meanwhile, the protrusion receiving groove 242 in which the protrusion 241 is accommodated may be formed to be recessed in one surface of the cylinder 133 facing the main bearing 131.

The protrusion 241 may be formed to have a cylindrical shape having an approximately predetermined diameter, and the protrusion accommodating groove 242 may be formed of a cylindrical space corresponding to the shape of the protrusion 241. In addition, the outer diameter of the protrusion 241 and the inner diameter of the protrusion receiving groove 242 are formed to be substantially the same, so that the protrusion 241 may be fitted and coupled to the protrusion receiving groove 242.

Meanwhile, the protrusion receiving groove 242 is formed to overlap the protrusion 241 in the axial direction while the cylinder 133 and the main bearing 131 are aligned so that the contact point P1 is formed to accommodate the protrusion 241. I can.

On the other hand, as in the above-described embodiment, when the compression space (V) is a structure formed by the main bearing 131, the cylinder 133, and the sub bearing 132, the contact point forming part 240 faces the cylinder. A protrusion protruding from one surface of the sub bearing 132 may be further included. In this case, as shown, the protrusion receiving groove 242 may be formed to extend in the axial direction to form a hole.

The protrusion of the sub-bearing 132 is inserted into the protrusion receiving groove 242 formed to extend in the axial direction, and a contact point between the roller 134 and the cylinder 133 together with the main bearing 131 and the cylinder 133 ( P1) can be formed.

FIG. 7A is a perspective view showing a coupling relationship between a main bearing and a cylinder according to another modified example of an embodiment, and FIG. 7B is a cross-sectional view showing a combined state of the main bearing and the cylinder shown in FIG. 7A.

Meanwhile, according to the present embodiment, the contact point forming part 340 may include a cylinder receiving part 341a formed to accommodate at least a part of the cylinder 133 in the main bearing 131. The cylinder receiving portion 341a may be formed by a plurality of protruding protrusions 341 protruding from one surface of the main bearing 131 facing the cylinder 133.

The plurality of protruding protrusions 341 may be formed of at least two or more protrusions, and when the cylinder 133 is coupled to the main bearing 131, it may contact the outer peripheral surface of the cylinder 133. In other words, the cylinder 133 may be coupled to fit into the plurality of protrusions 341 protruding from the main bearing 131.

In other words, the plurality of protruding protrusions 341 may be formed so that the cylinders 133 surround at least a portion of the outer peripheral surface of the cylinder 133.

By such a plurality of protrusions 341, the relative position in the direction perpendicular to the axial direction of the cylinder 133 and the main bearing 132 is adjusted, so that the contact point P1 is formed at the designed position. I can.

Meanwhile, although not shown, one surface of the plurality of protruding protrusions 341 in contact with the cylinder 133 may be formed to form a specific shape. In addition, a portion of the outer peripheral surface of the cylinder 133 in contact with the plurality of protrusions 341 may be formed to correspond to the shape of one surface of the plurality of protrusions 341. In this case, it is possible to easily adjust the designed relative position of the main bearing 131 and the cylinder 133 in the circumferential or rotational direction.

Meanwhile, the plurality of protrusions 341 may be formed at the same position in the radial direction from the center of the axis of the discharge passage 1316 and the rotation shaft 123. That is, the discharge passage 1316 comprising a plurality of protruding protrusions 341 and a plurality of holes may be formed alternately along the circumferential direction at a position spaced from the center of the axis of the rotation shaft 123 by the same distance in the radial direction.

In addition, in this embodiment, as in the above-described embodiment, when the compression space V is formed by the main bearing 131, the cylinder 133, and the sub bearing 132, the plurality of protrusions 341 are It may be formed to protrude from one surface of the sub bearing 132 facing the cylinder 133.

FIG. 8A is a perspective view showing a formation relationship between a main bearing and a cylinder according to another embodiment of the present invention, and FIG. 8B is a cross-sectional view showing a combined state of the main bearing and the cylinder shown in FIG. 8A.

As shown, the main bearing 231 and the cylinder 233 may be integrally formed. In this embodiment, since the main bearing 231 and the cylinder 233 are integrally formed, it is possible to omit the adjustment of the relative position between the main bearing 231 and the cylinder 233.

In the same structure as in this embodiment, when assembling the compressor, the sub-bearing 232 should be made of a separate member from the main bearing 231 and the cylinder 233 so that the roller 233 is provided in the compression space (V). Therefore, in the present embodiment, as to adjust the relative position of the sub-bearing 232 and the cylinder 233 supporting the rotation shaft 123 in the radial direction, the contact point P1 between the roller 234 and the cylinder 233 Can be formed.

In this case, when the sub-bearing 233 and the cylinder 233 described in the above-described embodiments are coupled, the contact point forming portions 140, 240, and 340 configured to form an existing contact point at a preset position may be included.

What has been described above are merely examples for implementing the rotary compressor according to the present invention, and the present invention is not limited to the above embodiments, and as claimed in the claims below, the scope does not depart from the gist of the present invention. Within the scope, anyone of ordinary skill in the field to which the present invention pertains will have the technical idea of the present invention to the extent that various modifications can be implemented.

Claims (12)

A cylinder formed in an annular shape and having an asymmetrical inner circumferential surface;
A main bearing and a sub bearing that are coupled to cover one surface and the other surface of the cylinder to form a compression space together with the cylinder;
A roller provided on a rotating shaft and rotating in the compression space while forming at least one contact point whose outer circumferential surface is close to the inner circumferential surface of the cylinder;
At least one vane slidably inserted into the roller and provided to separate the compression space into a plurality of regions by contacting each of the inner circumferential surfaces of the cylinder; And
Includes; a cylinder position fixing part for fixing a position in which the cylinder is aligned with respect to the main bearing or the sub bearing,
The cylinder position fixing part,
It includes a plurality of protruding protrusions formed in an arc shape so as to protrude in the axial direction from the main bearing or the sub-bearing to surround the outer peripheral surface of the cylinder and support it in a radial direction,
An inner circumferential surface of the plurality of protruding protrusions is formed to correspond to an outer circumferential surface of the cylinder at a portion facing each of the protruding protrusions. delete The method of claim 1,
A gap between the inner circumferential surface of the cylinder and the outer circumferential surface of the roller at the contact point is 20 μm to 30 μm. delete delete delete delete delete delete The method according to claim 1 or 3,
The protruding protrusion extends in an axial direction from one side of the main bearing or the sub-bearing facing the cylinder in the axial direction and is formed at the same radius at the center of the rotation shaft along the circumferential direction. Rotating shaft;
A cylinder provided at one end of the rotation shaft and formed in an annular shape;
A main bearing and a sub bearing that support the rotation shaft in a radial direction and are coupled to cover one surface and the other surface of the cylinder to form a compression space together with the cylinder;
A roller provided in the compression space, forming a contact point forming a predetermined gap with the cylinder, and being coupled to the rotation shaft to compress a refrigerant according to rotation; And
At least one vane slidably inserted into the roller, each contacting the inner circumferential surface of the cylinder to separate the compression space into a plurality of regions; and
A vane rotary compressor, characterized in that the cylinder is integrally extended on one side of the main bearing in the axial direction to fix a position in which the cylinder is aligned with the main bearing. delete

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