KR102317529B1 - Rotary compressor - Google Patents

Abstract

A rotary compressor according to the present invention includes a rotary shaft; a bearing plate supporting the rotation shaft; a cylinder coupled to the bearing plate and having a suction port and a vane slot at a predetermined interval along the circumferential direction; a roller coupled to the rotation shaft, provided inside the cylinder, forming a compression space together with the bearing plate and the cylinder, and having a hinge groove formed on an outer circumferential surface; and a vane having one end slidably coupled to the vane slot of the cylinder, and the other end being rotatably coupled to the hinge groove of the roller, wherein at least one suction guide is recessed in the outer circumferential surface of the roller. have. Through this, the volumetric efficiency of the compressor may be improved and the performance of the compressor may be improved by reducing the input of the motor.

Description

Rotary Compressor

The present invention relates to a compressor, and more particularly to a rotary compressor in which a roller and a vane are coupled.

A rotary compressor is a method of compressing a refrigerant using a roller rotating in the compression space of a cylinder and a vane that is in contact with the outer circumferential surface of the roller and divides the compression space of the cylinder into a plurality of spaces.

The rotary compressor may be divided into a rolling piston type and a hinged vane type depending on whether the rollers and the vanes are coupled. The rolling piston method is a method in which the vanes are detachably coupled from the rollers so that the vanes are in close contact with the rollers, and the hinged vane method is a method in which the vanes are hinged to the rollers. Compared to the rolling piston method, the hinge vane method can reduce the axial leakage by stabilizing the motion of the vane.

In general, the rotary compressor can reduce the suction loss by reducing the vortex and reaction force of the suction refrigerant depending on the shape of the suction passage. In addition, in the rotary compressor, the larger the space of the compression chamber, the greater the volumetric efficiency. The technique is known.

Japanese Laid-Open Patent Publication No. 2012-154235 (2012.08.16)

It is an object of the present invention to provide a rotary compressor capable of improving the volumetric efficiency by increasing the volume of the compression chamber.

Furthermore, an object of the present invention is to provide a rotary compressor that increases the suction amount of the refrigerant by reducing the suction reaction force of the refrigerant sucked into the compression chamber while increasing the volume of the compression chamber.

Furthermore, an object of the present invention is to provide a rotary compressor capable of increasing the motor efficiency by reducing the weight of the driving unit while increasing the volume of the compression chamber.

In order to achieve the object of the present invention, in a rotary compressor in which a vane is hinged to a roller, a rotary compressor in which a groove is formed on an outer circumferential surface of the roller may be provided.

Here, the cylinder may have a suction port, and the groove may be formed on a surface facing the suction port.

A length between both ends of the groove in the circumferential direction may be the same as the inner diameter of the suction port.

In addition, the groove may be formed in the middle of the outer peripheral surface of the roller.

In addition, the groove may be formed through the axial direction of the roller.

In addition, in order to achieve the object of the present invention, the annular member and the plate-shaped member are provided hingedly coupled to the inside of the cylinder, the annular member is rotatably coupled to the eccentric portion of the rotating shaft, and the plate-shaped member slides on the cylinder A space forming a suction pressure is formed on one side in the circumferential direction around the plate-shaped member, and a space forming a discharge pressure is formed on the other side in the circumferential direction. A rotary compressor in which a suction guide groove is formed may be provided.

Here, at least a portion of the inner circumferential surface of the suction guide groove may be formed in a curved surface.

And, the inner peripheral surface of the suction guide groove may be formed symmetrically with respect to the circumferential center of the suction guide groove.

And, the inner circumferential surface of the suction guide groove is formed asymmetrically with respect to the center in the circumferential direction of the suction guide groove, and the suction guide groove is formed to be longer than the length in the direction away from the vane in the direction of approach. can

In addition, in order to achieve the object of the present invention, the rotating shaft; a bearing plate supporting the rotation shaft; a cylinder coupled to the bearing plate and having a suction port and a vane slot at a predetermined interval along the circumferential direction; a roller coupled to the rotation shaft, provided inside the cylinder, forming a compression space together with the bearing plate and the cylinder, and having a hinge groove formed on an outer circumferential surface; and a vane having one end slidably coupled to the vane slot of the cylinder, and the other end being rotatably coupled to the hinge groove of the roller, wherein at least one suction guide is recessed in the outer circumferential surface of the roller. A compressor may be provided.

Here, the suction guide may be formed on a surface facing the suction port, and at least a portion of the suction guide and the suction port may overlap in a radial direction when the hinge groove contacts the inner circumferential surface of the cylinder.

Here, the suction guide portion may be formed at a position spaced apart from at least one end face of the roller by a predetermined axial height among both end faces in the axial direction.

In addition, the suction guide portion may be formed at a position spaced apart from both ends of the roller in the axial direction by a predetermined axial height, respectively.

Here, the suction guide portion may be formed through both end surfaces of the roller in the axial direction.

Here, the suction guide portion may be spaced apart by a first interval that is the shortest length from the hinge groove, and the first interval may be formed to be less than or equal to a radial thickness of the roller.

In addition, the first interval may be formed to be less than or equal to the second interval, which is the interval between the inner circumferential surface of the roller and the hinge groove.

Here, an allowable distance is provided between the inner circumferential surface of the cylinder and the outer circumferential surface of the roller, the allowable distance has a maximum allowable distance and a minimum allowable distance along the circumferential direction, and the suction guide part has an end farther from the hinge groove. It may be formed within the range where the allowable interval is located.

In addition, the suction guide portion may be located within a range where the end far from the hinge groove is suctioned out of the compression space.

The shortest length between both ends of the suction guide in the circumferential direction may be smaller than or equal to the inner diameter of the suction port.

Here, at least a portion of the inner surface of the suction guide portion may be formed in a curved surface.

In addition, the suction guide portion may have an inner surface formed in an arc shape.

Here, at least a portion of the inner surface of the suction guide portion may be formed as a straight surface.

In addition, the suction guide portion may be formed as an inclined surface in which at least a portion of the inner surface intersects each other.

Here, the suction guide portion may be formed symmetrically with respect to the circumferential center of the suction guide portion.

Here, the suction guide portion may be formed asymmetrically with respect to the circumferential center of the suction guide portion.

Here, the plurality of suction guides may be formed along the circumferential direction, and the plurality of suction guides may be spaced apart from each other by a predetermined third interval along the circumferential direction.

In addition, the sum of the shortest lengths connecting both ends of each of the suction guides in the circumferential direction may be formed to be larger than the inner diameter of the suction port.

In the rotary compressor according to the present invention, the volume of the compression chamber is increased as at least one suction guide is recessed on the outer circumferential surface of the roller in the hinge vane type, and thus the volumetric efficiency of the compressor can be improved.

In addition, in the present invention, a suction guide is formed on the outer circumferential surface of the roller in the hinge vane method, and as the suction guide is formed to be depressed on the surface facing the suction port, the volume of the compression chamber is expanded while the suction reaction force of the refrigerant sucked into the compression chamber is reduced. can be reduced Through this, when the refrigerant is sucked, the amount of refrigerant sucked can be improved by colliding with the outer circumferential surface of the roller and suppressing the formation of a reverse flow or a vortex.

In addition, the present invention can reduce the weight of the roller while expanding the volume of the compression chamber as the suction guide is recessed on the outer circumferential surface of the roller in the hinge vane method, thereby increasing the motor efficiency by lowering the input of the motor. .

In addition, in the present invention, as the suction guide part is formed within the range from the hinge groove to the maximum allowable interval position in the hinge vane method, the refrigerant leakage between the compression chambers due to the suction guide part is minimized to realize the improvement of the volumetric efficiency due to the suction guide part. can

In addition, in the present invention, in the hinge vane method, as the suction guide part is formed in the range from the hinge groove to the suction completion point or the discharge completion point, the suction guide part is depressed on the outer peripheral surface of the roller, and refrigerant leakage between the compression chambers is prevented in advance. can do. Through this, the volumetric efficiency of the compressor may be improved.

In addition, in the present invention, since the suction reaction force may increase when a high-pressure refrigerant such as R32 is used, the suction guide unit described above can be usefully applied to the hinge vane type rotary compressor to which the high-pressure refrigerant is applied.

1 is a longitudinal sectional view showing a rotary compressor according to the present invention;
2 is a cross-sectional view showing a compression part in the rotary compressor according to FIG. 1;
3 is a schematic view showing a change in the position of the vane roller with respect to the rotation angle of the rotating shaft in the rotary compressor according to the present embodiment;
4 is a perspective view showing the compression part in FIG. 1 broken;
5 is a perspective view showing the vane roller in FIG. 4;
6 is a front view showing the vane roller in FIG. 5 compared to the suction port;
7 is a "V-V" front sectional view of FIG. 5;
8 is an enlarged cross-sectional view of the compression unit in FIG. 1;
9 is a schematic view shown to explain the specifications of the suction guide;
10 is a graph showing a comparison of the refrigerant discharge amount according to the processing angle of the suction guide part;
11 is a schematic view showing a process in which the refrigerant is sucked through the suction guide;
12 is a graph showing a comparison of changes in input torque for each turning angle of the roller;
13 and 14 are plan views showing other embodiments of the suction guide in a broken manner;
15 is a plan view showing another embodiment of the suction guide part in a break;
16 is a perspective view showing another embodiment of the suction guide unit;
17 is a perspective view showing another embodiment of the suction guide unit;
18A and 18B are plan views illustrating the operation of the suction guide unit according to FIG. 17;

Hereinafter, a rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. The rotary compressor according to the present invention may be classified into a single rotary compressor or a double rotary compressor according to the number of cylinders. The present invention relates to an axial side shape of a roller or a plate facing the roller in a hinged vane type rotary compressor in which a roller and a vane are combined. Therefore, it can be applied to both a single rotary compressor and a double rotary compressor. Hereinafter, a single rotary compressor will be described as an example, but the same may be applied to a double rotary compressor.

1 is a longitudinal cross-sectional view showing the rotary compressor according to the present embodiment, and FIG. 2 is a cross-sectional view showing the compression unit in the rotary compressor according to FIG. 1 .

1 and 2, in the rotary compressor according to this embodiment, the electric part 20 is installed in the inner space 11 of the casing 10, and the rotating shaft 30 is located below the electric part 20. The compression unit 100 mechanically connected by the is installed in the inner space 11 of the casing 10 .

The casing 10 is formed in a cylindrical shape and disposed in the longitudinal direction. However, in some cases, the casing 10 may be disposed in the transverse direction.

The electric part 20 includes a stator 21 press-fitted to the inner circumferential surface of the casing 10 and fixed, and a rotor 22 rotatably inserted into the stator 21 . A rotating shaft 30 is press-fitted to the rotor 22 . An eccentric portion 35 is formed on the rotating shaft 30 to be eccentric with respect to the shaft portion 31 , and a roller 141 of a vane roller 140 to be described later is slidably coupled to the eccentric portion 35 .

The compression unit 100 includes a main bearing plate (hereinafter, a main bearing) 110 , a sub bearing plate (hereinafter, a sub bearing) 120 , a cylinder 130 , and a vane roller 140 . The main bearing plate 110 and the sub bearing plate 120 are provided on both sides in the axial direction with the cylinder 130 interposed therebetween to form a compression space V inside the cylinder 130 .

In addition, the main bearing 110 and the sub bearing 120 radially support the rotation shaft 30 penetrating the cylinder 130 . The vane roller 140 is coupled to the eccentric portion 35 of the rotating shaft 30 and compresses the refrigerant while rotating in the cylinder 130 .

In the main bearing 110 , the main plate part 111 is formed in a disk shape, and an annular side wall part 111a is formed at the edge of the main plate part 111 to be shrink-fitted or welded to the inner circumferential surface of the casing 10 . In the center of the main plate part 111, the main bearing part 112 is formed to protrude upward toward the transmission part, and the main bearing part 112 has a main bearing hole 112a through which the rotation shaft 30 is inserted and supported. do.

In the sub bearing 120 , the sub plate part 121 is formed in a disk shape and may be bolted to the main bearing 110 together with the cylinder 130 . Of course, when the cylinder 130 is fixed to the casing 10 , the main bearing 110 may be bolted to the cylinder 130 together with the sub bearing 120 , respectively, and the sub bearing 120 is the casing 10 . ), the cylinder 130 and the main bearing 110 may be fastened to the sub bearing 120 with bolts.

In the center of the sub-plate part 121, a sub bearing part 122 is formed to protrude downward toward the bottom surface of the casing 10, and the sub bearing part 122 has a sub bearing hole 122a and a main bearing hole 112a. It is formed through and on the same axis. The lower end of the rotation shaft 30 is supported in the sub shaft hole 122a.

The cylinder 130 is formed in an annular shape. The inner circumferential surface of the cylinder 130 is formed in a perfect circle shape having the same inner diameter. The inner diameter of the cylinder 130 is formed larger than the outer diameter of the roller 141 . Accordingly, a compression space V is formed between the inner circumferential surface of the cylinder 130 and the outer circumferential surface of the roller 141 .

For example, the inner circumferential surface of the cylinder 130 is the outer wall surface of the compression space (V), the outer circumferential surface of the roller 141 is the inner wall surface of the compression space (V), and the vane 145 is the side of the compression space (V). Each wall can be formed. Therefore, as the roller 141 rotates, the outer wall surface of the compression space V forms a fixed wall, while the inner wall surface and the side wall surface of the compression space V form a variable wall whose position is variable. have.

A suction port 131 is formed in the cylinder 130 , and a vane slot 132 is formed on one side in the circumferential direction of the suction port 131 , and a discharge guide groove is formed on the opposite side of the suction port 131 with the vane slot 132 interposed therebetween. (133) is formed.

The suction port 131 is formed to pass through the inner circumferential surface in a radial direction from the outer circumferential surface of the cylinder 130 , and the suction pipe 12 penetrating the casing 10 is connected to the outer circumferential side of the suction port 131 . Accordingly, the refrigerant is sucked into the compression space V of the cylinder 130 through the suction pipe 12 and the suction port 131 .

In addition, the suction port 131 is generally formed in a circular cross-sectional shape, but in some cases may be formed in an oval cross-sectional shape or may be formed in an angular shape. In this embodiment, an example in which the suction port 131 is formed in a circular cross-sectional shape will be mainly described. Therefore, the inner diameter of the suction port 131 in this embodiment is constant.

The vane slot 132 is elongated in a direction toward the outer circumferential surface on the inner circumferential surface of the cylinder 130 . The inner circumferential side of the vane slot 132 is opened, and the outer circumferential side is formed to be blocked or blocked by the inner circumferential surface of the casing 10 .

The vane slot 132 is formed to have a width approximately similar to the thickness or width of the vane 145 so that the vane 145 of the vane roller 140, which will be described later, slides. Accordingly, both side surfaces of the vane 145 are supported by both inner wall surfaces of the vane slot 132 and slide approximately in a straight line.

The discharge guide groove 133 is formed by chamfering the inner edge of the cylinder 130 in a hemispherical shape. The discharge guide groove 133 serves to guide the refrigerant compressed in the compression space V of the cylinder 130 to the discharge port 114 of the main bearing 110 . Accordingly, the discharge guide groove 133 is formed at a position overlapping the discharge port 114 when projected in the axial direction so as to communicate with the discharge port 114 .

However, since the discharge guide groove 133 generates a dead volume, it is preferable not to form the discharge guide groove 133 as much as possible, and even if the discharge guide groove 133 is formed, it may be preferably formed so that the volume thereof is minimized. .

Meanwhile, the vane roller 140 includes a roller 141 and a vane 145 as described above. The roller 141 and the vane 145 may be formed as a single body, or may be combined to perform a relative motion. Hereinafter, the present embodiment will be mainly described with respect to an example in which the roller and the vane are rotatably coupled.

The roller 141 is formed in a cylindrical shape. The roller 141 may be formed in a perfect circle shape having an inner peripheral surface and an outer peripheral surface having the same center, or may be formed in a perfect circle shape in which the inner peripheral surface and the outer peripheral surface of the roller 141 have different centers in some cases.

In addition, the axial height of the roller 141 is formed to be substantially equal to the height of the inner peripheral surface of the cylinder 130 . However, since the roller 141 must slide with respect to the main bearing 110 and the sub bearing 120 , the axial height of the roller 141 may be formed to be slightly smaller than the height of the inner circumferential surface of the cylinder 130 .

In addition, the inner peripheral height and the outer peripheral height of the roller 141 is formed to be substantially the same. Accordingly, both axial end surfaces connecting between the inner peripheral surface and the outer peripheral surface of the roller 141 form a sealing surface, respectively. These sealing surfaces are formed at right angles to the inner circumferential surface or the outer circumferential surface of the roller 141, respectively. However, the edge between the inner peripheral surface of the roller 141 and each sealing surface or the edge between the outer peripheral surface and each sealing surface of the roller 141 may be formed to be slightly inclined or curved.

In addition, the roller 141 is rotatably inserted and coupled to the eccentric portion 35 of the rotating shaft 30 , and the vane 145 is slidably coupled to the vane slot 132 of the cylinder 130 to the roller 141 . is hinged to the outer circumferential surface of the Accordingly, when the rotating shaft 30 rotates, the roller 141 rotates inside the cylinder 130 by the eccentric part 35 , and the vane reciprocates while being coupled to the roller 141 .

However, the rollers 141 may be aligned to be positioned at the same center with respect to the cylinder 130 , but may be aligned slightly eccentrically in some cases. For example, when the center of the roller 141 and the center of the cylinder 130 coincide, the gap (hereinafter, allowable distance) between the inner circumferential surface of the cylinder 130 and the outer circumferential surface of the roller 141 is approximately in the circumferential direction. kept constant Then, the compression stroke is started when the contact point between the inner peripheral surface of the cylinder 130 and the outer peripheral surface of the roller 131 that is closest reaches the circumferential end 131a of the suction port 131, and this compression stroke continues until the discharge stroke. persists evenly.

However, when the center of the roller 141 and the center of the cylinder 130 coincide, the pressure in the compression chamber gradually rises to reach the discharge stroke, and refrigerant leakage due to the pressure difference between the preceding compression chamber and the following compression chamber occurs. can occur.

Accordingly, the center of the roller 141 and the center of the cylinder 130 may be aligned to be eccentric. For example, the cylinder 130 is aligned so that the center O' of the roller 141 is eccentric in a direction close to the discharge port 114 with respect to the center (concentric with the axial center) O of the cylinder 130 . can do it Accordingly, the allowable distance from the side where the suction port 131 is located around the imaginary line connecting the center (O ") and the axial center (O) of the hinge groove 145 is widely arranged at a maximum of about 40-50 μm, and , the allowable distance from the side where the outlet 114 opposite to that is located is arranged as narrow as 10 to 20 μm at most.

Then, in the initial compression stroke, even if the allowable interval is wide, the pressure difference between the preceding compression chamber (V1) and the subsequent compression chamber (V2) is not large, so that refrigerant leakage between both compression chambers (V1) and (V2) is not large. . On the other hand, even if the pressure difference between the preceding compression chamber (V1) and the following compression chamber (V2) increases while the pressure in the preceding compression chamber (V1) gradually rises to reach the discharge stroke, the allowable interval is relatively narrow. The refrigerant leakage between (V1) and (V2) can be suppressed. This will be described later together with the suction guide.

In addition, the roller 141 is formed in an annular shape so that the inner circumferential surface has an inner diameter sufficient to be in sliding contact with the outer circumferential surface of the eccentric portion 35 of the rotation shaft 30 . The radial width (thickness) of the roller 141 is formed to a thickness sufficient to secure a sealing distance from the hinge groove 1411 to be described later.

In addition, the thickness of the roller 141 may be uniformly formed along the circumferential direction, or may be formed differently in some cases. For example, the inner peripheral surface of the roller 141 may be formed in an elliptical shape.

However, in order to minimize the load during rotation of the rotating shaft 30, the inner and outer peripheral surfaces of the roller 141 are formed in a perfect circle shape having the same center, and the radial thickness t1 of the roller 141 is constant along the circumferential direction. It may be desirable to form

In addition, one hinge groove 1411 is formed on the outer peripheral surface of the roller 141 so that the hinge protrusion 1452 of the vane 145 to be described later is inserted and rotated. The hinge groove 1411 is formed in an arc shape with an open outer circumferential surface.

The inner diameter of the hinge groove 1411 is formed to be larger than the outer diameter of the hinge protrusion 1452, and is formed to a size sufficient to slide without falling out while the hinge protrusion 1452 is inserted.

In addition, a suction guide portion 1415 is formed on one side of the hinge groove 1411 , that is, in the rotation direction of the rotation shaft 30 . The suction guide will be described again later while explaining the vane roller.

Meanwhile, the vane 145 includes a sliding portion 1451 and a hinge protrusion 1452 .

The sliding part 1451 is a part constituting the vane body, and is formed in a flat plate shape having a predetermined length and thickness. For example, the sliding part 1451 is formed in a rectangular hexahedral shape as a whole. In addition, the sliding portion 1451 is formed with a length such that the vane 145 remains in the vane slot 132 even when the roller 141 is completely moved to the opposite side of the vane slot 132 .

The hinge protrusion 1452 is formed to extend to the front end of the sliding part 1451 facing the roller 141 . The hinge protrusion 1452 is inserted into the hinge groove 1411 and is formed to have a rotatable cross-sectional area. The hinge protrusion 1452 may be formed in a semi-circular shape or a substantially circular cross-sectional shape excluding the connecting portion to correspond to the hinge groove 1411 .

In the drawings, unexplained reference numeral 13 denotes a discharge pipe, 150 denotes a discharge valve, and 160 denotes a discharge muffler.

The rotary compressor according to the present embodiment as described above operates as follows.

That is, when power is applied to the electric part 20, the rotor 22 of the electric part 20 rotates and the rotating shaft 30 rotates. Then, while the roller 141 of the vane roller 140 coupled to the eccentric portion 35 of the rotation shaft 30 rotates, the refrigerant is sucked into the compression space V of the cylinder 130 .

This refrigerant is compressed by the rollers 141 and the vanes 145 of the vane roller 140 , the discharge valve 150 provided in the main bearing plate 110 is opened, and the muffler 160 through the discharge port 114 is It is discharged into the inner space, and a series of processes of being discharged into the inner space 11 of the casing 10 are repeated.

At this time, the position of the roller 141 and the vane 145 is moved according to the rotation angle of the rotation shaft 30 . 3 is a schematic view showing a change in the position of the vane roller with respect to the rotation angle of the rotating shaft in the rotary compressor according to the present embodiment.

First, in this figure, the eccentric portion 35 of the rotating shaft 30 faces the vane slot 132, the axial center of the rotating shaft 30 (the same as the cylinder axial center) (O) and the hinge groove ( The position of the virtual line passing through the center (O ") of 1411 is 0°. This corresponds to Fig. 3 (a). In this case, the hinge groove 1411 of the roller 141 is on the inner peripheral surface of the cylinder 130. Almost in contact with the vane 145 is drawn into the inside of the vane slot (132).

Next, (b) and (c) of Figure 3 is a state in which the rotation shaft is rotated by about 60° and 120°. 3 (a) to 3 (b), (c) in the state of the hinge groove 1411 of the roller 141 is spaced apart from the inner peripheral surface of the cylinder 130, a part of the vane 145 is a vane slot (132) will be withdrawn. At this time, the refrigerant flows into the subsequent compression chamber V2 through the suction port 131 while forming the suction chamber in the subsequent compression chamber V2. On the other hand, the preceding compression chamber V1 compresses the refrigerant filled in the preceding compression chamber V1 while forming the compression chamber. Since the refrigerant accommodated in the preceding compression chamber V1 has not yet reached the discharge pressure, gas force or vane reaction force is not generated in the preceding compression chamber V1 or is negligible even if it is generated.

Next, in (d) of FIG. 3 is a state in which the rotation shaft is rotated by about 180°. 3 (c) to 3 (d) state, the hinge groove 1411 of the roller 141 is maximally spaced from the inner peripheral surface of the cylinder 130, the vane 145 is from the vane slot (132) will be maximally drawn out. The preceding compression chamber (V1) is in a state in which the compression process has progressed considerably, so that the refrigerant accommodated in the preceding compression chamber (V1) is in a state close to the discharge pressure.

Next, (e) of FIG. 3 is a state in which the rotating shaft is rotated by about 240°. In this state, the hinge groove 1411 of the roller 145 moves toward the inner peripheral surface of the cylinder 130 again, and the vane 145 is partially introduced into the vane slot 132 . At this time, the refrigerant accommodated in the preceding compression chamber V1 reaches the discharge pressure and starts discharging or almost reaching the discharging start time. Therefore, in this state, since the pressure difference between the pressure in the preceding compression chamber V1 and the pressure in the following compression chamber V2 reaches the highest or almost the highest, as described above, between the cylinder 130 and the roller 141 of the allowable gap is almost minimized.

Next, (f) of FIG. 3 is a state in which the rotating shaft is rotated by about 300°. This is a state in which the refrigerant in the preceding compression chamber V1 is almost completely discharged, the hinge groove 1411 of the roller 141 is almost in contact with the inner circumferential surface of the cylinder 130 , and the vane 145 is almost in the vane slot 132 . is in the state of being brought in. In this state, the pressure difference between the preceding compression chamber V1 and the following compression chamber V2 is reduced, and the allowable gap between the cylinder 130 and the roller 141 is gradually increased.

As described above, in the rotary compressor, the volumetric efficiency is determined according to the volume of the compression chamber due to the characteristics thereof, and the vortex and reaction force of the refrigerant sucked in are increased or decreased according to the shape of the suction passage. Accordingly, when the volume of the compression chamber is increased, the volumetric efficiency of the compressor can be improved, and when the suction flow path is formed in the forward direction of the refrigerant, the vortex and reaction force of the refrigerant can be reduced.

Accordingly, in the present embodiment, a suction guide portion (or a suction guide groove) may be formed on at least one of the inner circumferential surface of the cylinder constituting the compression chamber and the outer circumferential surface of the roller. The suction guide portion may be formed by being depressed in the inner peripheral surface of the cylinder and/or in the outer peripheral surface of the roller so that the volume of the compression chamber can be enlarged.

However, when the suction guide portion is formed on the inner circumferential surface of the cylinder, the compression start time may be delayed depending on the shape of the suction guide portion, and the weight of the roller may not decrease, so that it may not be possible to reduce the input of the motor. On the other hand, when the suction guide portion is formed on the outer circumferential surface of the roller, it is possible to prevent the compression start point from being delayed depending on the shape of the suction guide portion, and the weight of the roller is reduced to reduce the input of the motor, thereby improving the motor efficiency.

Therefore, the following description will be focused on an example in which the suction guide is formed on the outer circumferential surface of the roller. However, the suction guide portion is not necessarily limited to being formed only on the outer peripheral surface of the roller. That is, the suction guide portion may be formed on the outer peripheral surface of the roller, the inner peripheral surface of the cylinder, or the inner peripheral surface of the cylinder.

FIG. 4 is a perspective view showing the compression part in FIG. 1 by breaking it, FIG. 5 is a perspective view showing the vane roller in FIG. 4, FIG. 6 is a front view showing the vane roller in FIG. 5 compared to the suction port, and FIG. "V-V" is a cross-sectional view.

4 to 7 , the roller 141 forming a part of the vane roller 140 may be formed in a cylindrical shape having a predetermined thickness and height, as described above. A hinge groove 1411 into which the vane 145 is rotatably inserted is formed on one side of the outer circumferential surface of the roller 141, and a suction guide 1415 is formed on one circumferential side (right side in the drawing) of the hinge groove 1411. can be

The suction guide 1415 may be formed to be depressed by a predetermined depth from the outer circumferential surface of the roller 141 toward the center O' of the roller 141 . Therefore, the suction guide portion 1415 may be mixed with the suction guide groove.

The suction guide portion 1415 may be formed on the side of the rotational direction of the rotation shaft 30 with the hinge groove 1411 as the center (O″), that is, on the side facing the suction port 131. However, the roller 141 is a cylinder Since the relative motion with respect to 130, the suction guide 1415 may be out of the range of the suction port depending on the turning position (moved position) of the roller 141.

Accordingly, the suction guide 1415 is at least a portion of the suction guide 1415 based on the point when the turning position of the roller 141 is 0 degrees (that is, the point when the hinge groove of the roller is closest to the inner circumferential surface of the cylinder). It may be formed at a position overlapping the suction port 131 in the radial direction. This will be explained again later.

In addition, the suction guide portion 1415 may be formed at an axial intermediate position among the outer peripheral surface of the roller 141 , or may be formed through both sides of the roller 141 in the axial direction or through one side of the roller 141 . 4 to 7 show an example in which the suction guide is formed in the middle of the roller in the axial direction. An embodiment in which the suction guide portion 1415 is formed through the axial side surface of the roller 141 will be described later.

5 to 7 , the suction guide portion 1415 may be formed to be spaced apart from each other by a predetermined distance from both end surfaces of the roller 141 in the axial direction. Accordingly, the suction guide 1415 is located approximately in the middle of the outer circumferential surface of the roller 141 , and axial sealing surfaces 141a and 141b may be formed on both sides of the suction guide 1415 in the axial direction, respectively.

Here, the axial sealing surfaces 141a and 141b are defined as the interval between the axial side surface of the roller 141 and the axial side surface of the suction guide 1415, and the axial sealing surfaces 141a and 141b are connected The side adjacent to the transmission part 20 may be defined as an upper axial sealing surface (first axial sealing surface) 141a, and the opposite side may be defined as a lower axial sealing surface (second axial sealing surface) 141b. have

The circumferential length of the first axial sealing surface 141a and the circumferential length of the second axial sealing surface 141b may be the same as or different from each other. In addition, the axial length of the first axial direction sealing surface 141a and the axial length of the second axial direction sealing surface 141b may be formed to be the same or different from each other. 4 shows an example in which the circumferential length and the axial length of both axial sealing surfaces 141a and 141b are the same.

For example, when the circumferential length and the axial length of the first axial sealing surface 141a and the second axial sealing surface 141b are the same, the first axial sealing surface 141a and the second axis The direction sealing surface 141b can be easily formed. In addition, since the center of gravity of the roller 141 with respect to the eccentric part 35 of the rotating shaft 30 is located at the axial center of the eccentric part 35, the behavior of the roller 141 can be maintained constant.

However, the circumferential length or axial length of the first axial sealing surface 141a may be greater than the circumferential length or axial length of the second axial sealing surface 141b. This is because the discharge port 114 is formed in the main bearing 110 located on the upper side in the axial direction of the roller 141, so that the refrigerant in the preceding compression chamber V1 constituting the discharge chamber is further driven upward, and the refrigerant is It is possible to effectively suppress the inflow toward the trailing compression chamber V2 forming the suction chamber riding on the upper surface of the vane 145 or the upper surface of the roller 141 .

In addition, the suction guide portion 1415 is preferably formed to be spaced apart from the hinge groove 1411 of the roller 141 by a predetermined distance. That is, the suction guide portion 1415 is similar to forming a kind of slimming portion around the hinge groove 1411 of the roller 141 . Therefore, since the gap between the suction guide 1415 and the hinge groove 1411 becomes thinner, the suction guide 1415 is positioned as far from the hinge groove 1411 as possible in order to suppress the damage of the roller 141. .

However, on the contrary, since the suction guide 1415 is a space for accommodating the refrigerant flowing into the compression chamber constituting the suction chamber through the suction port 131, it is advantageous to secure the suction volume to be formed as close to the hinge groove 1411 as possible. .

For example, the shortest distance (first gap) L1 between the suction guide 1415 and the hinge groove 1411 may be formed to be less than or equal to the radial thickness t1 of the roller 141 . More precisely, the first gap L1 may be formed to be less than or equal to the shortest distance (second gap) L2 from the inner circumferential surface of the roller 141 to the hinge groove 1411 . That is, the first interval L1 may be formed to be 0.7 to 0.9 times larger than the second interval L2. The second gap L2 may be usually about 2 mm.

In addition, the suction guide portion 1415 is preferably formed to be spaced apart from the inner peripheral surface of the roller 141 by a predetermined distance in the radial direction. That is, since the thickness of the roller 141 is reduced in the portion where the suction guide portion 1415 is formed, the roller 141 may be deformed by receiving a force from the eccentric portion 35 when the rotation shaft 30 rotates. Therefore, an appropriate gap must be secured between the inner surface of the suction guide 1415 and the inner peripheral surface of the roller 141 .

However, since the roller 141 is coupled to the eccentric portion 35 of the rotation shaft 30 to allow relative motion, it receives less force than the hinge groove 1411 . Accordingly, the shortest interval (third interval) L3 between the inner surface of the suction guide 1415 and the inner circumferential surface of the roller 141 is approximately equal to or smaller than the first interval L1 or the second interval L2. can

On the other hand, in order for the suction guide portion 1415 to be formed as deep as possible in the radial direction, it is advantageous for the inner diameter of the roller 141 to be formed as small as possible. However, the inner diameter of the roller 141 is limited by the outer diameter of the rotating shaft 30, the inner diameter of the main bearing hole (112a), or the inner diameter of the sub bearing hole (122a).

FIG. 8 is an enlarged cross-sectional view of the compression unit in FIG. 1 . For example, in the case of the sub bearing 120 , a chamfer 123 is formed at a corner where the sub plate part 121 and the sub bearing hole 122a meet. Therefore, the inner circumferential surface of the chamfer 123 and the roller 141 should be radially interfered by a preset interference distance (fourth interval) L4 while the roller 141 rotates. The fourth interval L4 may be formed to be approximately half of the first interval L1.

On the other hand, the suction guide 1415 serves to expand the volume of the compression space (V) by forming a groove on the outer peripheral surface of the roller 141 as described above. Therefore, it may be advantageous to improve the volumetric efficiency to form the suction guide 1415 as long as possible in the circumferential direction.

However, the suction guide portion 1415 is spaced apart from the inner circumferential surface of the cylinder 130 even when the outer circumferential surface of the roller 141 is in contact with the inner circumferential surface of the cylinder 130 . Accordingly, the suction guide 1415 may act as a kind of refrigerant leakage path while the preceding compression chamber V1 and the following compression chamber V2 communicate with each other through the suction guide 1415 .

In consideration of this, the suction guide portion 1415 according to the present embodiment is preferably formed to be located within a range where refrigerant leakage does not occur or can be minimized along the circumferential direction. Hereinafter, the circumferential end of the suction guide 1415 adjacent to the hinge groove 1411 will be defined as the first end 1415a and the opposite end will be defined as the second end 1415b.

9 is a schematic diagram showing the specifications of the suction guide.

Referring to FIG. 9 , the suction guide 1415 according to the present embodiment may be formed within a range from the end 1411a of the hinge groove 1411 to the maximum clearance point P1 . That is, the first end 1415a of the suction guide 1415 is formed to be positioned as close to the end 1411a of the hinge groove 1411 as possible, and the second end 1415b of the suction guide 1415 is the maximum allowable. It may be formed to be positioned as close as possible to the gap position P1.

The end 1411a of the hinge groove 1411 is defined as the end of the suction port 131 side among both ends of the hinge groove 1411, and the maximum allowable spacing position P1 is between the inner peripheral surface of the cylinder 130 and the outer peripheral surface of the roller 141. It can be defined as the largest point among the allowable intervals of

As described above, as the inner peripheral surface of the cylinder 130 and the outer peripheral surface of the roller 141 are each formed in a circular shape, when the center (O') of the roller 141 coincides with the center (O) of the cylinder 130, the roller The allowable clearance between 141 and the cylinder 130 becomes uniform along the circumferential direction.

However, in general, as the center (O') of the roller 141 is eccentrically aligned from the center (O) of the cylinder 130, the allowable distance between the inner peripheral surface of the cylinder 130 and the outer peripheral surface of the roller 141 is It is formed differently along the circumferential direction. That is, referring to FIG. 9 , the maximum allowable gap position P1 and the minimum allowable gap position P2 are formed on opposite sides with a phase difference of 180 degrees.

Therefore, the allowable distance gradually increases from the minimum allowable distance position (P2) where the allowable distance (t22) is the minimum to the maximum allowable distance position (P1) where the allowable distance (t21) becomes the maximum, and the maximum allowable distance position (P1) The allowable distance gradually decreases up to the position of the minimum allowable gap (P2), which is 180 degrees opposite from .

In general, when the point at which the hinge groove 1411 is closest to the inner circumferential surface of the cylinder 130 is 0 degrees, the minimum allowable spacing position P2 is formed in the vicinity of approximately 260 degrees around the discharge start angle. Accordingly, the maximum allowable gap position P1 is formed in the vicinity of 80 degrees with a phase difference of 180 degrees from the minimum allowable gap position P2. Of course, this may vary depending on the size of the compressor.

Accordingly, the second end 1415b of the suction guide 1415 according to the present embodiment is at a point smaller than or equal to the maximum allowable spacing position P2, that is, the hinge groove 1411 is closest to the inner circumferential surface of the cylinder 130. It may be formed within a range of 80 degrees based on the rotation direction of the rotation shaft 30 at 0 degrees, which is a close point.

If the suction guide portion 1415 is formed to exceed the maximum allowable interval position (P1), the refrigerant in the preceding compression chamber (V1) is excessively leaked into the subsequent compression chamber (V2). Then, a compression loss in the preceding compression chamber V1 may occur, thereby substantially reducing the volumetric efficiency. Therefore, the second end 1415b of the suction guide 1415, that is, the maximum machining angle θ of the suction guide 1415 may be preferably formed within the maximum allowable spacing position P1 as described above. .

However, even if the suction guide 1415 is formed in a range where the second end 1415b is smaller than the maximum allowable gap position P1, a difference may occur in the refrigerant discharge amount. That is, as the entire outer circumferential surface of the roller 141 rotates while contacting the entire inner circumferential surface of the cylinder 130 in turn, the suction guide 1415 also circumferentially extends from the first end 1415a to the second end 1415b. It faces the inner peripheral surface of the cylinder 130 in the radial direction in turn along the direction.

Accordingly, depending on the position (or angle) of the suction guide portion 1415 facing the inner circumferential surface of the cylinder 130, both compression chambers (V1) and (V2) are communicated or separated while substantially in the preceding compression chamber (V1). The compression start time (or the refrigerant leakage amount between the compression chambers) may vary.

For example, if the suction guide 1415 is formed up to 80 degrees, which is the maximum processing angle θ, the preceding compression chamber V1 and the following compression chamber V2 are suction guides even when the suction port 131 is closed. They are communicated with each other through the portion 1415 . Then, a portion of the refrigerant accommodated in the preceding compression chamber V1 flows back into the subsequent compression chamber V2, and eventually, the amount of refrigerant discharged to the preceding compression chamber V1 is reduced to a certain extent.

However, when the suction guide portion 1415 is formed from 0 degrees to the suction completion point (or compression start time), the preceding compression chamber V1 becomes the subsequent compression chamber V2 at the suction completion point of the preceding compression chamber V1. It is possible to suppress the refrigerant leakage between the compression chambers through the suction guide 1415 while being separated from the. Through this, it is possible to suppress a decrease in the amount of refrigerant discharged to the preceding compression chamber V1. 10 is a graph showing a comparison of the refrigerant discharge amount according to the processing angle of the suction guide part.

Referring to FIG. 10 , when the maximum processing angle θ for the second end of the suction guide 1415 exceeds 80 degrees, which is an angle corresponding to the maximum allowable spacing position P1 of the suction guide 1415 , , it can be seen that the refrigerant discharge amount rapidly decreases. Therefore, the final machining angle of the suction guide portion 1415 may be advantageously formed within the range from 0 degrees to 80 degrees, which is the angle of the maximum allowable gap position P1.

However, it can be seen that the refrigerant discharge amount gradually decreases as the position of the suction guide 1415 moves from the maximum allowable interval position P1 toward the suction port 131 . And the position of the suction guide 1415 (ie, the second end of the suction guide) is the same as the circumferential end (the vane slot side is defined as the start end) of the suction port 131 up to the same point (D = L5), the refrigerant It can be seen that the intake amount is kept constant.

This is because the point at which the outer circumferential surface of the roller 141 contacts the circumferential end 131a of the suction port 131 is the suction completion point for the preceding compression chamber V1 described above, so the suction completion time of the preceding compression chamber V1 This is because the refrigerant leakage between the compression chambers through the suction guide 1415 is suppressed while the preceding compression chamber V1 is separated from the subsequent compression chamber V2 in the .

Accordingly, the second end 1415b of the suction guide portion 1415 is a portion where the outer peripheral surface of the roller 141 is in contact with the end 131a of the suction port 131, that is, the suction completion point (or compression start point). It may be desirable to form up to This is a position corresponding to the circumferential end 131a of the suction port 131 , and this angle is a position in which the hinge groove 1411 is rotated by about 15 to 20 degrees based on the angle in contact with the cylinder 130 . Of course, this may vary slightly depending on the size of the compressor.

Referring back to FIGS. 6 and 7 , the shortest circumferential length L3 of the suction guide 1415 may be formed to be substantially the same as the inner diameter D of the suction port 131 . The shortest length L5 in the circumferential direction of the suction guide 1415 is a straight line distance connecting the first end 1415a and the second end 1415b of the suction guide 1415 . Hereinafter, the shortest circumferential length L5 of the suction guide 1415 is defined as the shortest length of the suction guide 1415 .

On the other hand, the shortest length (L5) of the suction guide portion 1415 may be formed smaller than the inner diameter (circumferential inner diameter) (D) of the suction port. However, in this case, since the suction port 131 faces the outer circumferential surface of the roller 141 around the suction guide 1415 in close proximity to the position, the refrigerant sucked through the suction port 131 is absorbed by the suction guide 1415 around and around the suction guide 1415. They can collide to form vortices or create reaction forces. Accordingly, the shortest length L5 of the suction guide 1415 may be advantageously formed to be equal to or larger than the inner diameter D of the suction port 131 in terms of increasing the suction volume.

In addition, the axial length L6 of the suction guide 1415 may be formed to be greater than or equal to the inner diameter (axial length) D of the suction port 131 . More preferably, the axial length (shown in FIG. 6) (L6) of the suction guide portion 1415 is formed to be larger than the inner diameter (D) of the suction port 131 may be advantageous to increase the suction volume.

In addition, the suction guide portion 1415 may have an inner surface formed in various shapes. However, it is preferable that the inner surface of the suction guide 1415 be formed so that the refrigerant sucked through the suction port 131 can smoothly move along the turning direction of the roller 141 .

11 is a schematic diagram illustrating a process in which a refrigerant is sucked through a suction guide. Referring to FIG. 11 , the suction guide 1415 according to the present embodiment is recessed by a predetermined depth from the outer peripheral surface of the roller 141 , and the inner surface may be formed as a curved surface. In this case, the entire inner surface of the suction guide 1415 may be formed as a curved surface, or may be partially formed as a curved surface.

In addition, in the suction guide 1415 according to the present embodiment, the first inner surface 1415c constituting the inner circumferential surface when projected in the axial direction may be formed in a semicircle or arc shape. In this case, the curvature of the first inner surface 1415c of the suction guide 1415 may be set according to the standard of the compressor, but may be approximately equal to or greater than the curvature of the outer peripheral surface of the roller 141 .

The first inner surface 1415c of the suction guide 1415 is the center line of the suction port 131 in a state where the circumferential center P3 of the first inner surface 1415c coincides with the center line CL of the suction port 131 Both sides of the circumferential direction may be symmetrically formed with respect to (CL). Accordingly, not only the processing of the suction guide 1415 is easy, but the entire refrigerant flowing through the suction port 131 moves smoothly in the suction guide 1415, thereby reducing flow resistance.

In addition, among the inner surfaces of the suction guide 1415 , the second inner surface 1415d forming the upper inner surface and the third inner surface 1415e forming the lower inner surface may be formed in a flat surface, respectively. Accordingly, while the suction guide 1415 is formed in the middle of the outer peripheral surface of the roller 141, the volume of the suction guide 1415 can be formed as large as possible.

The suction guide according to the present embodiment as described above has the following effects.

That is, the refrigerant is sucked into the compression space V through the suction port 131 . The suction port 131 is formed in a direction substantially normal to the outer circumferential surface of the roller 141 . Accordingly, the direction in which the refrigerant is sucked is a direction normal to the outer circumferential surface of the roller 141 , and the interval between the outer circumferential surface of the roller 141 and the inner circumferential surface of the cylinder 130 is very narrow.

Accordingly, if the suction guide 1415 is not formed on the outer circumferential surface of the roller 141, the refrigerant sucked into the compression space V constituting the suction chamber through the suction port 131 is rotated at a high speed. A vortex may be formed by colliding with the outer circumferential surface of the tube, or a tendency to flow backward toward the suction port may occur due to the suction reaction force.

However, as in this embodiment, when the suction guide 1415 is recessed by a predetermined depth on the outer circumferential surface of the roller 141 , the suction guide 1415 causes the outer circumferential surface of the roller 141 and the cylinder 130 . The actual gap between the inner periphery is widened. That is, the suction guide 1415 acts as a kind of buffer space for the suctioned refrigerant.

Then, the refrigerant sucked into the compression space V constituting the suction chamber through the suction port 131 flows into the suction guide unit 1415 facing the suction port 131 , and the refrigerant is absorbed into the suction guide unit 1415 . As the shock caused by the collision is buffered in the , it smoothly moves along the roller 141 .

Accordingly, it is possible not only to suppress the vortex phenomenon of the refrigerant sucked into the compression space V constituting the suction chamber, but also to reduce the suction reaction force of the refrigerant. Then, the refrigerant is smoothly sucked into the compression space V constituting the suction chamber, so that the suction amount of the refrigerant is increased and the compressor efficiency can be improved.

In addition, since the suction guide 1415 serves as a kind of slimming part, the weight of the roller 141 can be reduced by the volume of the suction guide 1415, and as the weight of the roller 141 decreases, the overall motor input can be reduced to improve compressor efficiency. 12 is a graph showing a comparison of changes in input torque for each turning angle of a roller. Conventionally, it is an example in which the suction guide is not applied to the roller, and this embodiment shows an example in which the suction guide is applied to the outer peripheral surface of the roller.

Looking at this, it can be seen that the input torque in this embodiment is reduced compared to the related art. This means that if the suction guide is not applied to the roller as in the prior art, the weight of the roller increases and the input torque of the motor increases. It can be seen that the weight of 141) decreases and the input torque decreases.

On the other hand, another example of the suction guide unit is as follows.

That is, in the above-described embodiment, the inner surface of the suction guide portion is formed in an arc shape, but in some cases, the inner surface of the suction guide portion 1415 may be formed in a straight surface or a straight surface and a curved surface.

13 and 14 are plan views showing other embodiments of the suction guide part in a cutaway view.

Referring to FIG. 13 , a portion of the first inner surface 1415c of the suction guide 1415 according to the present embodiment may be formed in a wedge cross-sectional shape. For example, the outer peripheral side of the first inner surface 1415c of the suction guide 1415 is formed as a straight line parallel to the longitudinal direction of the suction port 131, and the inner peripheral side is formed in a wedge cross-sectional shape that becomes narrower toward the center. can

Accordingly, the shortest outer circumferential length L5 of the suction guide 1415 may be the same as or larger than the inner diameter D of the suction port 131 . In addition, the shortest outer circumferential length L5 of the suction guide portion 1415 may be formed smaller than the inner diameter D of the suction port 131 .

Even when the inner surface of the suction guide 1415 has a wedge cross-sectional shape as described above, the basic configuration of the suction guide 1415 and the effect thereof are similar to those of the above-described embodiment. Therefore, a detailed description thereof will be omitted.

However, as in the present embodiment, as the first inner surface 1415c of the suction guide 1415 is formed in a wedge cross-sectional shape, the suction guide 1415 may be formed as a straight surface as a whole. Accordingly, in the present embodiment, the inner surface of the suction guide 1415 can be easily processed compared to the arc shape.

In addition, if the shortest length of the suction guide 1415 is the same, the volume of the suction guide 1415 is that the inner surface of the suction guide 1415 is formed in a wedge cross-sectional shape as in this embodiment. It can be increased compared to being formed in an arc shape, such as

Accordingly, in the roller 141 in the suction guide 1415 according to the present embodiment, the weight of the roller 141 is reduced compared to the above-described embodiment, and the present embodiment has a motor compared to the above-described embodiment. can be lowered.

Furthermore, as in this embodiment, when the first inner surface 1415c of the suction guide 1415 is formed in a wedge cross-sectional shape, the refrigerant sucked into the compression space V constituting the suction chamber through the suction port 131 is suction guide. Since it moves relatively smoothly inside the part 1415 , the vortex and reaction force of the refrigerant can also be effectively reduced.

Meanwhile, referring to FIG. 14 , the first inner surface 1415c of the suction guide 1415 according to the present embodiment may be formed in a rectangular cross-sectional shape as a whole. For example, the outer peripheral side of the first inner surface 1415c of the suction guide 1415 is formed as a straight line parallel to the longitudinal direction of the suction port 131 , and the inner peripheral side is a straight line orthogonal to the longitudinal direction of the suction port 131 . It may be formed of cotton.

Accordingly, the outer periphery shortest length L51 and the inner periphery shortest length L52 of the suction guide portion 1415 are formed to be the same as each other, and may be formed equal to or larger than the inner diameter D of the suction port 131 . have. Of course, the shortest outer periphery length L51 of the suction guide 1415 may be slightly larger than the inner periphery shortest length L52.

Even when the inner surface of the suction guide 1415 has a rectangular cross-sectional shape as described above, the basic configuration of the suction guide 1415 and the effect thereof are similar to those of the above-described embodiment. Therefore, a detailed description thereof will be omitted.

However, as the first inner surface of the suction guide 1415 is formed in a rectangular cross-sectional shape as in the present embodiment, the suction guide 1415 may be formed as a straight surface as a whole. Accordingly, in the present embodiment, the inner surface of the suction guide 1415 can be easily processed compared to that formed in an arc shape or a wedge shape.

In addition, if the shortest length of the suction guide 1415 is the same, the volume of the suction guide 1415 is that the first inner surface 1415c of the suction guide 1415 is formed in a rectangular cross-sectional shape as in this embodiment. This can be increased compared to that formed in an arc shape or a rectangular cross-sectional shape as in the above-described embodiment.

Accordingly, in the roller 141 in the suction guide 1415 according to the present embodiment, the weight of the roller 141 is further reduced compared to the above-described embodiment. can be further lowered.

Furthermore, as in this embodiment, when the first inner surface 1415c of the suction guide 1415 is formed in a rectangular cross-sectional shape, the refrigerant sucked into the compression space V constituting the suction chamber through the suction port 131 is suction guide. It is buffered inside the part 1415, and the vortex and reaction force of the refrigerant can also be effectively reduced.

Although not shown in the drawings, the inner circumferential side of the suction guide 1415 may be formed to be curved along the inner circumferential surface of the roller 141 . In this case, the volume of the suction guide 1415 may be increased by that much.

On the other hand, there is another embodiment of the suction guide unit as follows.

That is, in the above-described embodiments, both sides of the suction guide 1415 in the circumferential direction are formed symmetrically with each other around an imaginary line extending from the center line CL of the suction port 131 , but in some cases, the above virtual It may be formed so that both sides of the circumferential direction are asymmetric with respect to the line.

15 is a cutaway plan view of another embodiment of the suction guide. Referring to FIG. 15 , one side of the suction guide 1415 in the circumferential direction of the first inner surface 1415c may be formed in a closed shape, while the other side in the circumferential direction may be formed in an open shape. For example, among the first inner surfaces 1415c of the suction guide 1415 , the first inner surface 1415c on the side of the first end 1415a adjacent to the hinge groove 1411 is formed along the longitudinal direction of the suction port 131 . It is formed in parallel to a set depth, and the first inner surface 1415c on the second end 1415b side opposite to the first end 1415a is in the longitudinal direction of the suction port 131 from the first inner surface 1415c on the first end side. It may be formed to be orthogonal.

Accordingly, the suction guide portion 1415 is formed in a 'L' shape as a whole so that the first end side adjacent to the vane 145 is formed in a closed shape, while the second end side away from the vane 145 is formed in an open shape. can be

Even when the inner surface of the suction guide 1415 has an asymmetrical shape as described above, the basic configuration of the suction guide 1415 and the effect thereof are similar to those of the above-described embodiment. Therefore, a detailed description thereof will be omitted.

However, as in the present embodiment, as the first inner surface 1415c of the suction guide 1415 is formed in a shape adjacent to the vane 145 is blocked and the side far from the vane 145 is opened, the above-described embodiment The suction guide portion 1415 can be more easily processed as compared to being formed in a symmetrical shape in which both ends in the circumferential direction are blocked.

In addition, as the circumferential end of the suction guide 1415 is formed in an open shape, the suction guide 1415 is compared to the suction guide 1415 of the above-described embodiments in which both ends in the circumferential direction are blocked and formed in a symmetrical shape. may increase in volume.

Accordingly, in the roller 141 in the suction guide 1415 according to the present embodiment, the weight of the roller 141 is further reduced compared to the roller of the above-described embodiment, and the present embodiment is compared with the above-described embodiment. The input of the motor can be further lowered.

Furthermore, as in the present embodiment, when the circumferential end of the suction guide 1415 is formed in an open shape, the refrigerant sucked into the compression space V constituting the suction chamber through the suction port 131 is of the roller 141 . Since it can move quickly in the rotational direction, the vortex and reaction force of the refrigerant can also be effectively reduced.

On the other hand, there is another embodiment of the suction guide unit as follows.

That is, in the above-described embodiments, the suction guide 1415 is formed by being depressed to a predetermined depth in the middle of the outer circumferential surface of the roller 141 , but in some cases, the suction guide 1415 is the axis of the roller 141 . It may be formed through either side of both sides in the direction, or may be formed through both side surfaces. Hereinafter, an example in which the suction guide 1415 penetrates both sides of the roller in the axial direction will be mainly described.

16 is a perspective view showing another embodiment of the suction guide unit.

Referring to FIG. 16 , the suction guide 1415 according to the present embodiment may be formed to penetrate from the upper surface of the roller 141 in the axial direction to the lower surface in the axial direction. In this case, the axial sealing surfaces are excluded from both sides of the suction guide 1415 in the axial direction.

In addition, the suction guide portion 1415 may be formed in the same cross-sectional shape along the axial direction. Of course, the suction guide 1415 may be formed in a different cross-sectional shape along the axial direction, but it may be preferable to have the same cross-sectional shape along the axial direction in consideration of the processing aspect.

In addition, the suction guide 1415 may be formed in various ways in the above-described embodiments, for example, an arc cross-sectional shape, a wedge cross-sectional shape, a square cross-sectional shape, an asymmetric cross-sectional shape, and the like. Hereinafter, a circular arc cross-sectional shape will be described as a representative example.

The suction guide 1415 according to the present embodiment may be formed to have a circular arc cross-sectional shape as in the embodiment of FIG. 5 and to be recessed by a predetermined depth from the outer peripheral surface of the roller 141 .

In addition, the first end 1415a of the suction guide 1415 is formed to be spaced apart from the hinge groove 1411 by a predetermined first interval L1, and the suction guide 1415 has the second end 1415b It may be formed within the range from the contact point (more precisely, the end of the suction port) to the suction completion point or compression start point. Specifically, referring to FIGS. 6 to 9 , the second end 1415b of the suction guide 1415 is preferably formed up to the outer peripheral surface of the roller 141 in contact with the end 131a of the suction port 131 . can Of course, the suction guide portion 1415 may be formed up to the maximum allowable interval position (P1).

In addition, as described above, the shortest length L5 of the suction guide 1415 may be the same as or larger than the inner diameter D of the suction port 131 . Of course, the shortest length L5 of the suction guide 1415 may be formed smaller than the inner diameter D of the suction port 131 .

The suction guide 1415 according to the present embodiment is similar to the suction guide 1415 of the above-described embodiments in basic structure and effect. However, in this embodiment, as the suction guide portion 1415 is formed through both sides in the axial direction including the outer peripheral surface of the roller 141, unlike the embodiment shown in FIG. 5 , the first axial sealing surface and A second axial sealing surface may be excluded.

Accordingly, the suction guide 1415 can be processed more easily, and the volume of the suction guide 1415 can be increased. In addition, compared to the roller 141 of the embodiment shown in FIG. 5, the weight of the roller 141 is further reduced, so that the input of the motor can be further lowered.

On the other hand, there is another embodiment of the suction guide unit as follows.

That is, in the above-described embodiment, only one suction guide portion is formed along the circumferential direction on the outer circumferential surface of the roller, but in some cases, a plurality of suction guide portions 1415 may be formed along the circumferential direction.

17 is a perspective view showing another embodiment of the suction guide, and FIGS. 18A and 18B are plan views illustrating the operation of the suction guide according to FIG. 17 .

Referring to FIG. 17 , the suction guide 1415 according to the present embodiment may include a first guide 1416 and a second guide 1417 . A circumferential sealing surface 141c may be formed between the first guide 1416 and the second guide 1417 with a predetermined interval (fifth interval) L7 along the circumferential direction.

Although not shown in the drawings, the suction guide portion 1415 has a third guide portion, a fourth guide portion, etc. in addition to the first and second guide portions 1416 and 1417 in the circumferential direction respectively along the circumferential sealing surface (L7). It may be formed successively with interposed therebetween. For convenience, the following description is limited to the first guide part and the second guide part.

In addition, the first guide portion 1416 and the second guide portion 1417 may be formed in the same shape or may be formed in different shapes. For convenience, hereinafter, an example in which the first guide part 1416 and the second guide part 1417 are formed to have the same shape will be mainly described.

The first end of the first guide portion 1416 is formed with a first interval L1 from the hinge groove 1411 as in the other embodiments described above, and the second end 1416b of the first guide portion 1417 is formed. ) may be formed within the range from the contact point (more precisely, the end of the suction port) to the suction completion point or compression start point. Specifically, as described above, the second end 1416b of the first guide portion 1416 may be preferably formed up to the outer peripheral surface of the roller 141 in contact with the end 131a of the suction port 131 .

The shortest distance L5' of the first guide part 1416 and the shortest distance L5" of the second guide part 1417 may be formed to be equal to or larger than the inner diameter of the suction port 131, respectively. The total shortest distance L5 for the suction guide 1415, which is the sum of the shortest distance L5' of the first guide 1416 and the shortest distance L5" of the second guide 1417, is the It may be formed to be approximately twice or more larger than the inner diameter (D).

As described above, even in the case of this embodiment in which the suction guide 1415 includes a plurality of guides L5' and L5", the basic configuration of the suction guide 1415 and its operational effects are similar to those of the suction guide 1415. ) is similar to the above-described embodiments in which one is, therefore, a detailed description thereof will be omitted.

However, in this embodiment, as a plurality of suction guides 1415 are formed with a circumferential sealing surface 141c therebetween along the circumferential direction, the entire circumferential direction of the suction guide 1415 compared to the above-described embodiment. The length (hereinafter, the arc length of the suction guide or the shortest interval of the suction guide) L5 may be increased.

At this time, as the arc length of the suction guide 1415 increases, the volume of the compression chamber increases, so that the volumetric efficiency can be improved. However, when the arc length of the suction guide 1415 increases, the compression chamber is moved to the preceding compression chamber V1 through the suction guide 1415 before the compression chamber reaches the suction completion point (approximately 80°). can be communicated. Then, a portion of the refrigerant compressed in the compression chamber may leak through the suction guide 1415 into the compression chamber constituting the suction chamber, thereby reducing the discharge amount.

Accordingly, the suction guide 1415 according to the present embodiment is divided into a first guide 1416 and a second guide 1417 , and between the first guide 1416 and the second guide 1417 . The circumferential sealing surface 141c of the fifth interval L7 may be formed. Accordingly, it is possible to suppress the reverse flow of the refrigerant compressed in the preceding compression chamber (V1) to the subsequent compression chamber (V2) through the suction guide (1415).

As shown in FIG. 18A, in the position where the roller 141 is 0 degrees, a portion of the first guide 1416 and the second guide 1417 of the suction guide 1415 form a suction chamber V1 preceding compression chamber. is included in At this time, the volume of the preceding compression chamber V1 is the total volume of the first guide 1416 and the second guide 1417 included in the preceding compression chamber V1 in addition to the volume of the corresponding compression chamber. . Accordingly, the suction volume of the compression chamber constituting the suction chamber is increased compared to the case in which the suction guide 1415 is formed of one as in the above-described embodiment.

As shown in FIG. 18b , when the roller 141 turns about 20 degrees, the first guide 1416 is in the following compression chamber V2 communicating with the suction port 131 , and the preceding compression chamber V1 is in The second guide portions 1417 are respectively positioned. At this time, as the circumferential sealing surface 141c spaced apart by the fifth interval L7 is formed between the first guide 1416 and the second guide 1417, the first guide 1416 and the second guide 1416 are formed. The guide portion 1417 is circumferentially separated. Accordingly, it is possible to suppress the reverse flow of the refrigerant of the preceding compression chamber V1 including the second guide portion 1417 to the subsequent compression chamber V2 including the first guide portion 1416 . Through this, the actual discharge amount may be increased.

In addition, as the volume of the suction guide 1415 increases, the weight of the roller 141 may decrease, thereby lowering the input of the motor, thereby improving the compressor efficiency.

Meanwhile, although not shown in the drawings, the first guide part and the second guide part may be formed in different shapes. For example, the first guide part may have a shape penetrating both surfaces in the axial direction of the roller 141 , and the second guide part may be formed in a shape recessed in the middle of the outer circumferential surface of the roller 141 . Also, the first guide 1416 may have a large volume and the second guide 1417 may have a small volume. In addition, the first guide portion 1416 may be formed in a curved surface, and the second guide portion 1417 may be formed in a straight surface. Of course, the opposite shape is also possible.

On the other hand, in the present invention, since the suction reaction force may increase when a high-pressure refrigerant such as R32 is used, the suction guide according to the present embodiment may be usefully applied to a hinge vane type rotary compressor to which such a high-pressure refrigerant is applied.

10: casing 11: inner space
12: suction pipe 13: discharge pipe
20: electric part 21: stator
22: rotor 30: rotation shaft
35: eccentric part 100: compression part
110: main bearing plate 111: main plate part
111a: annular side wall part 112: main bearing part
112a: main shaft hole 114: discharge port
120: sub bearing plate 121: sub plate portion
122: sub bearing part 122a: sub bearing hole
123: chamfer 130: cylinder
131: inlet 131a: end of the inlet
132: vane slot 133: discharge guide groove
140: vane roller 141: roller
141a: first axial sealing surface 141b: second axial sealing surface
141c: circumferential sealing surface 1411: hinge groove
1411a: end of the hinge groove 1415: suction guide
1415a: the first end of the suction guide 1415b: the second end of the suction guide
1415c: first inner surface 1415d: second inner surface
1415e: third inner side 145: vane
1451: sliding part 1452: hinge protrusion
150: discharge valve 160: discharge muffler
CL: center line of intake port t1: radial thickness of roller
t21: Maximum allowable distance t22: Minimum allowable distance
D: the inner diameter of the inlet
L1: The shortest distance between the suction guide and the hinge groove (the first gap)
L2: The shortest distance from the inner peripheral surface of the roller to the hinge groove (second gap)
L3: The shortest distance between the inner circumferential surface of the suction guide and the inner circumferential surface of the roller (third gap)
L4: Interference distance between chamfer and roller (4th interval)
L5: The shortest length in the circumferential direction of the suction guide
L51: The shortest length in the circumferential direction on the outer periphery of the suction guide
L52: The shortest length in the circumferential direction of the inner periphery of the suction guide
L5': the shortest length in the circumferential direction of the first guide
L5": the shortest circumferential length of the second guide part
L6: axial length of the suction guide
L7: a circumferential distance between the first guide part and the second guide part (fifth gap)
P1: Position of the maximum alignment interval P2: Position of the minimum alignment interval
P3: circumferential center of suction guide θ: maximum cutting angle
O: Shaft center (center of cylinder) O': Center of roller
O": Center of hinge groove V: Compression space
V1: leading compression chamber V2: trailing compression chamber

Claims (17)

axis of rotation;
a bearing plate supporting the rotation shaft;
a cylinder coupled to the bearing plate and having a suction port and a vane slot at a predetermined interval along the circumferential direction;
a roller coupled to the rotation shaft, provided inside the cylinder, forming a compression space together with the bearing plate and the cylinder, and having a hinge groove formed on an outer circumferential surface thereof; and
One end is slidably coupled to the vane slot of the cylinder, and the other end is a vane rotatably coupled to the hinge groove of the roller;
At least one suction guide portion is recessed in the outer peripheral surface of the roller,
On both sides of the axial direction of the suction guide,
A rotary compressor in which a first axial sealing surface and a second axial sealing surface are respectively formed so that the suction guide portions are spaced apart from each other by a predetermined axial height from both end surfaces of the roller in the axial direction. According to claim 1,
The suction guide is formed on a surface facing the suction port,
A rotary compressor in which at least a portion of the suction guide and the suction port overlap in a radial direction when the hinge groove contacts the inner circumferential surface of the cylinder. According to claim 1,
The first axial sealing surface and the second axial sealing surface are formed to have the same circumferential length and the same axial length. According to claim 1,
Among the inner surfaces of the suction guide, one inner surface in the axial direction and the other inner surface in the axial direction are formed in planes parallel to each other. According to claim 1,
The suction guide portion is spaced apart by a first interval that is the shortest length from the hinge groove,
The first interval is less than or equal to the radial thickness of the roller. 6. The method of claim 5,
The first interval is less than or equal to a second interval, which is a interval between the inner peripheral surface of the roller and the hinge groove. According to claim 1,
An allowable distance is provided between the inner peripheral surface of the cylinder and the outer peripheral surface of the roller, and the allowable distance has a maximum allowable distance and a minimum allowable distance along the circumferential direction,
The suction guide portion is a rotary compressor in which an end far from the hinge groove is formed within a range where the maximum allowable distance is located. 8. The method of claim 7,
The suction guide portion is a rotary compressor in which an end far from the hinge groove is located within a range where the suction of the compression space is completed. 9. The method of claim 8,
The shortest length between both ends of the suction guide in the circumferential direction is smaller than or equal to the inner diameter of the suction port. According to claim 1,
The suction guide portion is a rotary compressor in which at least a portion of the inner surface is formed in a curved surface. 11. The method of claim 10,
The suction guide portion is a rotary compressor whose inner surface is formed in an arc shape. According to claim 1,
The suction guide portion is a rotary compressor in which at least a part of the inner surface is formed as a straight surface. 13. The method of claim 12,
The suction guide portion is a rotary compressor in which at least a portion of the inner surface is formed as an inclined surface that crosses each other. According to claim 1,
The suction guide portion is a rotary compressor that is formed symmetrically with respect to the circumferential center of the suction guide portion. According to claim 1,
The suction guide portion is a rotary compressor formed asymmetrically with respect to the circumferential center of the suction guide portion. 16. The method according to any one of claims 1 to 3, 5 to 15,
A plurality of suction guides are formed along the circumferential direction, and the plurality of suction guides are spaced apart from each other by a third predetermined interval along the circumferential direction. 17. The method of claim 16,
In the plurality of suction guides, the sum of the shortest lengths connecting both ends of each of the suction guides in the circumferential direction is formed to be larger than the inner diameter of the suction port.

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