KR102190063B1 - Vain rotary compressor - Google Patents

Abstract

A vane rotary compressor according to the present invention comprises: a cylinder provided with an inlet; A main bearing and a sub-bearing coupled to the cylinder to form a compression space together with the cylinder; A rotating shaft supported in a radial direction by the main bearing and the sub bearing; A roller eccentrically accommodated in the compression space to form a contact point with the inner circumferential surface of the cylinder, rotates together with the rotation shaft, and has a plurality of vane slots formed along the circumferential direction; And a plurality of vanes each slidably inserted into the vane slots of the rollers and protruding in a direction toward an inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers, wherein the suction port includes an inner circumferential surface of the cylinder and A first suction unit formed through between the outer circumferential surfaces; And a groove shape having a predetermined depth on the inner circumferential surface of the cylinder, communicated with the first suction unit on the opposite side of the contact point based on the first suction unit, and extend in the rotational direction of the rotation shaft from the inner circumferential surface of the cylinder A second suction unit formed; may be included. Through this, it is possible to suppress a pressure drop by increasing the suction flow rate of the refrigerant.

Description

Vane rotary compressor {VAIN 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. Therefore, the vane rotary compressor has a higher compression ratio than the rotary compressor. Accordingly, the vane rotary compressor is more suitable to use a refrigerant having a low ozone depletion index (ODP) and global warming index (GWP) such as R32, R410a, and CO ₂ .

In the vane rotary compressor, as one compression space is divided into a plurality of compression chambers, the compression stroke may be shortened and the coefficient of performance (COP) of the compressor may decrease. Accordingly, the vane rotary compressor disclosed in the patent document [Japanese Laid-Open Patent: JP2014-040797A, (Published: 2014.03.06)] has an asymmetrical shape on the inner circumferential surface of the cylinder so that the compression stroke (compression cycle) is increased.

However, in the conventional vane rotary compressor as described above, as the compression stroke (compression cycle) increases, the suction stroke (suction cycle) decreases on the contrary. Then, the suction flow rate of the refrigerant sucked into the compression chamber constituting the suction chamber decreases, and a pressure drop in the compression chamber may occur. Then, as the volumetric efficiency in the compression chamber is lowered, the performance coefficient of the compressor is lowered. This problem is a characteristic of the vane rotary compressor, which occurs in the same manner as when the inner circumferential surface of the cylinder has a circular or symmetrical ellipse shape as in the case of an asymmetrical ellipse shape. However, in the case of an asymmetric ellipse, the above-described problem may occur even more.

Further, in the conventional vane rotary compressor, as the suction port is formed by passing through the cylinder in the radial direction, the area of the suction port is limited by the height of the cylinder in the axial direction. Moreover, since sealing distances must be secured on both upper and lower sides of the suction port, the area of the suction port is further limited. Accordingly, there is a limit in expanding the area of the suction port, so that the suction flow rate of the refrigerant is reduced, and a pressure drop may occur.

In addition, in the conventional vane rotary compressor, when R32, which is an eco-friendly refrigerant, is applied, the above-described problem may occur more significantly. That is, R32 was developed as a refrigerant that replaces R410a, but the refrigerant has a smaller particle density than R410a, resulting in insufficient mass flow. Then, a pressure drop relative to the volume of the same compression chamber may occur, so that the above-described increase in the suction loss and the resulting decrease in the volume efficiency further increase, and the performance coefficient of the compressor may be further lowered. This may occur more significantly in a heating low temperature condition, a high pressure ratio condition (Pd/Ps ≥ 6), and a high speed operation condition (80 Hz or more).

Patent Document: Japanese Published Patent: JP2014-040797A, (Published: 2014.03.06)

An object of the present invention is to provide a vane rotary compressor capable of enhancing compressor performance by suppressing a pressure drop relative to the volume of the same compression chamber.

Further, an object of the present invention is to provide a vane rotary compressor capable of suppressing a pressure drop relative to the volume of the same compression chamber by increasing the suction cycle.

Furthermore, an object of the present invention is to provide a vane rotary compressor capable of appropriately maintaining a compression cycle while increasing a suction cycle.

Another object of the present invention is to provide a vane rotary compressor capable of increasing the suction flow rate of a refrigerant while the suction port is formed through the cylinder in the radial direction.

Furthermore, it is intended to provide a vane rotary compressor capable of expanding the suction area of the suction port while securing the sealing distance of the suction port.

Further, it is intended to provide a vane rotary compressor capable of increasing the suction period for the compression chamber while expanding the suction area of the suction port.

In addition, another object of the present invention is to provide a vane rotary compressor capable of increasing the coefficient of performance by lowering the pressure drop in the compression chamber and increasing the suction period of the refrigerant even when the eco-friendly refrigerant R32 is applied. I want to provide it.

In order to achieve the object of the present invention, it is intended to provide a vane rotary compressor, characterized in that the inlet has a circumferential length longer than an axial length.

Further, the present invention is to provide a vane rotary compressor, characterized in that the suction port is formed in a plurality of shapes in the circumferential direction.

Further, the present invention comprises a suction port formed at a position close to the contact point between the cylinder and the roller, and a suction guide groove communicated with the suction port and formed to be located farther from the contact point than the main suction port, and the suction guide groove It is intended to provide a vane rotary compressor, characterized in that the area of is formed smaller than the area of the suction port.

Here, the suction port may be formed in a circular cross-sectional shape, and the suction guide groove may be formed in a non-circular cross-sectional shape.

In addition, in order to achieve the object of the present invention, the cylinder is provided with a suction port; A main bearing and a sub-bearing coupled to the cylinder to form a compression space together with the cylinder; A rotating shaft supported in a radial direction by the main bearing and the sub bearing; A roller eccentrically accommodated in the compression space to form a contact point with the inner circumferential surface of the cylinder, rotates together with the rotation shaft, and has a plurality of vane slots formed along the circumferential direction; And a plurality of vanes each slidably inserted into the vane slots of the rollers and protruding in a direction toward an inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers, wherein the suction port includes an inner circumferential surface of the cylinder and A first suction unit formed through between the outer circumferential surfaces; And a groove shape having a predetermined depth on the inner circumferential surface of the cylinder, communicated with the first suction unit on the opposite side of the contact point based on the first suction unit, and extend in the rotational direction of the rotation shaft from the inner circumferential surface of the cylinder A vane rotary compressor comprising a; formed second suction unit may be provided.

Here, a line passing through the longitudinal center of the first suction unit is a first virtual line, a line passing through the center of the outer diameter of the cylinder and the contact point is a second imaginary line, and passing through the center of the outer diameter of the cylinder and the end of the second suction unit. When the line is referred to as a third virtual line, a first angle between the first virtual line and the second virtual line may be formed to form a range of 0.8 to 1.2 times a second angle between the first virtual line and the third virtual line. have.

In addition, the first and second angles may be the same.

In addition, the second suction unit may have an area larger than that of the second suction unit.

In addition, the cross-sectional area of the second suction unit may be formed equally in the rotation direction of the rotation shaft.

In addition, the cross-sectional area of the second suction unit may be formed to gradually decrease in the direction of rotation of the rotation shaft.

In addition, the height in the axial direction of the second suction unit may be smaller than the height in the axial direction of the first suction unit.

In addition, the height in the axial direction of the second suction unit may be formed equal to the height in the axial direction of the first suction unit.

Here, the second suction unit may be formed to have the same depth along the circumferential direction of the cylinder.

Here, the second suction unit may be formed to be inclined to become deeper as the first suction unit approaches.

In addition, the second suction part may have a space part formed in a straight line parallel to the first suction part from the inner circumferential surface of the cylinder to a predetermined depth.

Here, the suction port may have a length in the circumferential direction greater than a length in the axial direction.

And, at least one of the plurality of bearings is formed with a back pressure pocket communicating with the rear side of the vane slot, the back pressure pocket is formed of a plurality of pockets having different internal pressures separated along the circumferential direction, The plurality of pockets may be provided on an inner circumferential side facing the outer circumferential surface of the rotation shaft, and bearing protrusions forming a radial bearing surface with respect to the outer circumferential surface of the rotation shaft may be formed, respectively.

In addition, the plurality of pockets may include: a first pocket having a first pressure; And a second pocket having a pressure higher than the first pressure; wherein the bearing protrusion of the second pocket communicates the inner circumferential surface of the bearing protrusion facing the outer circumferential surface of the rotation shaft and an outer circumferential surface opposite to the outer circumferential surface thereof. Can be formed.

The vane rotary compressor according to the present invention moves the suction start angle of the suction port close to the contact point and at the same time delays the suction completion angle and the compression start angle as much as possible, thereby maintaining the compression cycle of the compression chamber and extending the suction cycle to inhale refrigerant. The flow rate can be increased. Through this, it is possible to increase the performance of the compressor by suppressing the pressure drop relative to the volume of the same compression chamber.

Further, in the vane rotary compressor according to the present invention, a plurality of suction ports communicating with each other are arranged in a circumferential direction, so that the suction area can be enlarged while securing a sealing distance of the suction ports formed through the radial direction. Through this, the suction period can be extended to increase the suction flow rate of the refrigerant.

Further, the vane rotary compressor according to the present invention increases the suction flow rate of the refrigerant by increasing the suction cycle while maintaining the compression cycle for the compression chamber, thereby lowering the pressure drop in the compression chamber even when the eco-friendly refrigerant R32 is applied. You can increase the coefficient.

In addition, the vane rotary compressor according to the present invention can enhance the above-described effect even in a heating low temperature condition, a high pressure ratio condition, and a high speed operation condition.

1 is a cross-sectional view showing an example of a vane rotary compressor according to the present invention,
2 and 3 are cross-sectional views of the compression unit applied to FIG. 1, and FIG. 2 is a cross-sectional view of "IV-IV" of FIG. 1, and FIG. 3 is a cross-sectional view of "V-V" of FIG.
4A to 4D are cross-sectional views showing a process in which a refrigerant is sucked, compressed, and discharged from the cylinder according to the present embodiment;
FIG. 5 is a cross-sectional view of a compression unit in longitudinal section to explain the back pressure of each back pressure chamber in the vane rotary compressor according to the present embodiment;
6 and 7 are a perspective view and a plan view showing a cylinder in the vane rotary compressor according to the present embodiment,
8 is a front view illustrating a first suction unit and a second suction unit according to the present embodiment;
9 is a schematic diagram showing a position of a suction port according to the present embodiment compared with a conventional suction port position;
10A to 10D are schematic diagrams illustrating a process of forming a compression chamber according to a position of a vane in the vane rotary compressor according to the present embodiment;
11 is a graph showing a comparison of the suction flow rate in the compression chamber and the suction area of the compression chamber with respect to the rotation angle of the roller in order to explain the effect according to the present embodiment.
12 to 14 are front views showing another embodiment of the suction port according to the present embodiment,
15 to 17 are perspective views and cross-sectional views showing other embodiments of the second suction unit according to the present embodiment.

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 showing an example of a vane rotary compressor according to the present invention, FIGS. 2 and 3 are cross-sectional views of the compression unit applied to FIG. 1, and FIG. 2 is a cross-sectional view of “IV-IV” of FIG. And FIG. 3 is a cross-sectional view taken along line "V-V" of FIG. 2.

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 driving motor 120 includes a stator 121, a rotor 122 and a rotation shaft 123.

The stator 121 is fixedly installed inside the casing 110 and may be 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 110a.

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. Accordingly, the rotation shaft 123 rotates concentrically with the rotor 120.

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 to be described later 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. This embodiment shows an example formed by a plurality of pieces.

An oil feeder 127 is installed in the middle or lower end of the oil passage 125. Accordingly, when the rotating shaft 123 rotates, the oil filled in the lower portion of the casing is pumped by the oil feeder 127 and sucked up along the oil passage 125, and then the second shaft receiving portion and the second shaft receiving portion 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.

It is preferable that the first oil through hole 126a is formed to overlap with the first oil groove 1311b to be described later, and the second oil through hole 126b is formed to overlap with the second oil groove 1321b. Through this, the oil supplied to the bearing surface of the main bearing 131 and the bearing surface 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. This will be described later.

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

Referring to FIGS. 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 rotation shaft 123 in the radial direction and at the same time support the cylinder 133 and the roller 134 in the axial direction. Accordingly, the main bearing 131 and the sub-bearing 132 have a shaft receiving portion 1311, 1321 supporting the rotating shaft 123 in a radial direction, and a plan extending in the radial direction from the receiving portion 1311, 1321 Each of the branches 1312 and 1322 may be formed. For convenience, the shaft receiving part of the main bearing 131 is the first shaft receiving part 1311 and the flange part as the first flange part 1312, and the shaft receiving part of the sub-bearing 132 is the second shaft receiving part 1321 and the second flange part. It is defined as (1322).

1 and 3, the first shaft portion 1311 and the second shaft 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. This will be described later together with the back pressure pocket.

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. This will be described later.

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 structure of the back pressure pocket according to the present invention can be equally applied to a vane rotary compressor having a symmetrical oval shape.

2 and 3, the hybrid cylinder (hereinafter, abbreviated as a cylinder) 133 according to the present embodiment may have a circular outer circumferential surface, but the inner circumferential surface of the casing 110 is non-circular It may be sufficient if it is a fixed shape. 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 to be described later is rotatably coupled to the compression space (V).

The inner circumferential surface 133a of the cylinder 133 has a suction port 1331 and a discharge port on both sides of the circumferential direction around the point at which 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. 1332a) 1332b are formed.

The suction port 1331 has a first suction part 1331a formed through from the inner circumferential surface of the cylinder 133 to the outer circumferential surface, and a second suction part 1331a extending along the circumferential direction from one end of the first suction part 1331a to form a groove shape. It may be made of a suction part 1331b. This will be described later.

The suction port 1331 is directly connected to the suction pipe 113 by a connection pipe (not shown) penetrating the casing 110, and the discharge ports 1332a and 1332b communicate toward the inner space 110 of the casing 110 And is indirectly connected to the discharge pipe 114 that is coupled through the casing 110. 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 (110) of the casing (110) through the discharge ports (1332a) (1332b) and then discharged. It is discharged to the pipe 114. Accordingly, the inner space 110 of the casing 110 is maintained in a high-pressure state forming a discharge pressure.

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 FIGS. 2 and 3.

Meanwhile, a plurality of discharge ports 1332a and 1332b are formed 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 based on the compression path as the secondary discharge ports (or the first discharge ports) 1332a, and the discharge ports located on the downstream side are the main discharge ports (or 2 discharge port) 1332b.

However, the secondary discharge port is not necessarily a necessary component, and can be selectively formed if 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, referring to FIGS. 2 and 3, 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.

The center (Or) of the roller 134 is eccentric with respect to the center (Oc) of the cylinder 133, that is, the center of the inner space of the cylinder 133 (hereinafter, defined as the center of the cylinder for convenience) (Oc). One side of the outer peripheral surface 134c of the roller 134 almost contacts the inner peripheral surface 133a of the cylinder 133. Here, when one side of the outer circumferential surface of the roller 134 is closest to the inner circumferential surface of the cylinder 133, and an arbitrary point of the cylinder 133 at which the roller 134 almost contacts the cylinder 133 is referred to as a contact point (P). , The center line passing through the contact point P and the center of the cylinder 133 may be a position corresponding to the short axis of the elliptic curve forming the inner peripheral surface 133a of the cylinder 133.

The roller 134 has a plurality of vane slots 1341a, 1341b, 1341c formed at appropriate places along the circumferential direction on its outer circumferential surface, and vanes 1351, 1352, 1353 at each vane slot (1341a, 1341b, 1341c) ) Are inserted and combined by sliding. The vane slots 1341a, 1341b, and 1341c 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 1341a, 1341b, and 1341c 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 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, and 1353 at the inner ends of the vane slots 1341a, 1341b, 1341c, 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. For convenience, the direction toward the cylinder based on the direction of movement of the vane is defined as front and the opposite side as rear.

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, 1334c may each independently communicate with the back pressure pockets 1313, 1323, but a plurality of back pressure chambers 1334a, 1334b, 1334c are provided by the back pressure pockets 1313, 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 or 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, the back pressure pocket formed in the main bearing 131 is defined as the main back pressure pocket 1313, and the back pressure pocket formed in the sub bearing 132 is defined as the 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 back pressure chamber to which the vanes located relatively upstream (from the suction stroke to the discharge stroke) belong to the vanes. The pocket 1313b and the sub-side second pocket 1323b may communicate with a back pressure 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.

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

The front 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 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 110b denotes an upper shell and 110c denotes a lower shell.

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 1341a, 1341b, and 1341c are drawn out, so that the front surfaces of the vanes 1351, 1352, and 1353 come in contact with the inner circumferential 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) is formed, and each compression chamber (V1, V2, V3) moves along the rotation of the roller 134, and the shape of the inner circumferential surface 133a of the cylinder 133 and the eccentricity of the roller 134 As a result, the volume is varied, 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 suction, compress and discharge the refrigerant.

Looking at this in more detail as follows. 4A to 4D are cross-sectional views illustrating a process in which a refrigerant is sucked, compressed, and discharged from the cylinder according to the present embodiment. In FIGS. 4A to 4D, 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. 4, 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 point of completion of the 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. 4, 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. 4, 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. 4, 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.

FIG. 5 is a cross-sectional view of a compression unit in longitudinal section to explain the back pressure of each back pressure chamber in the vane rotary compressor according to the present embodiment.

5, an intermediate pressure Pm between the suction pressure and the discharge pressure is located at the rear end of the first vane 1351 positioned in the first pocket 1313a on the main side, and is positioned 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 second vane 1352 to be performed. 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, the first pocket (1313a) and the second pocket (1313b) of the main side back pressure pocket (1313) according to the present embodiment communicates with the oil passage (125) through the first oil through hole (126a), the sub-side back pressure The first pocket 1323a and the second pocket 1323b of the pocket 1323 communicate with the oil passage 125 through the second oil through hole 126b.

Referring back to Figs. 2 and 3, the main side first pocket 1313a and the sub side first pocket 1323a are the main side and the sub side by the main side and the sub side first bearing protrusions 1314a and 1324a. The first pockets 1313a and 1323a are closed for each of the facing bearing surfaces 1311a and 1321a. Accordingly, the oil (refrigerant oil) of the main and sub-side first pockets 1313a and 1323a flows into the bearing surfaces 1311a and 1321a through the respective oil through holes 126a and 126b, and then the main The pressure is reduced while passing between the upper surface 134a or the lower surface 134b of the side and sub-side first bearing protrusions 1314a and 1324a and the facing roller 134 to form an intermediate pressure.

On the other hand, the main side second pocket 1313b and the sub side second pocket 1323b are the main and sub-side second pockets 1313b and 1323b by the main and sub-side second bearing protrusions 1314b and 1324b. ) Communicates with each of the bearing surfaces 1311a and 1321a facing each other. Accordingly, the oil (refrigerant oil) of the main and sub-side second pockets 1313b and 1323b flows into the bearing surfaces 1311a and 1321a through the respective oil through holes 126a and 126b, and then the main As it passes through the side and sub-side second bearing protrusions 1314b and 1324b and flows into each of the second pockets 1313b and 1323b, a discharge pressure or a pressure slightly lower than the discharge pressure is formed.

However, the main second pocket 1313b and the sub-side second pocket 1323b according to the present exemplary embodiment have bearing surfaces 1311a and 1311a on which the main and sub-side second pockets 1313b and 1323b face each other. 1321a) is completely open and does not communicate. That is, the main second bearing protrusion 1314b and the sub-side second bearing protrusion 1324b block most of the main second pocket 1313b and the sub-side second pocket 1323b, but some of them Each of the second pockets 1313b and 1323b is blocked by placing 1315 and 1325.

In the flange portion 1312 of the main bearing 131, a first pocket 1313a and a second pocket 1313b on the main side described above are formed at predetermined intervals along the circumferential direction, and the flange portion of the sub-bearing 132 ( In 1322, the sub-side first pocket 1323a and the second pocket 1323b described above are formed at predetermined intervals along the circumferential direction.

The inner circumferential sides of the main first pocket 1313a and the second pocket 1313b are blocked by the main first bearing protrusion 1314a and the second bearing protrusion 1314b, respectively, and the sub-side first pocket 1323a and The inner circumferential side of the second pocket 1323b is blocked by the sub-side first bearing protrusion 1324a and the second bearing protrusion 1324b, respectively. Accordingly, the bearing portion 1311 of the main bearing 131 forms a cylindrical bearing surface 1311a having a substantially continuous surface, and the bearing portion 1321 of the sub bearing 132 is a cylindrical shape having a substantially continuous surface. The bearing surface 1321a is formed. In addition, the main side first bearing protrusion 1314a and the second bearing protrusion 1314b, and the sub-side first bearing protrusion 1324a and the second bearing protrusion 1324b form a kind of elastic bearing surface.

The first oil groove 1311b described above is formed on the bearing surface 1311a of the main bearing 131, and the second oil groove 1321b described above is formed on the bearing surface 1321a of the sub bearing 132. A first communication passage 1315 for communicating the main bearing surface 1311a and the main second pocket 1313b is formed in the main second bearing protrusion 1314b, and the sub-side second bearing protrusion 1324b has a sub A second communication passage 1325 for communicating the bearing surface 1321a and the second sub-side pocket 1323b is formed.

The first communication channel 1315 is formed at a position overlapping with the second bearing protrusion 1315b on the main side and at the same time as the first oil groove 1311b, and the second communication channel 1325 is a second bearing protrusion on the sub side. It is formed at a position overlapping with the second oil groove 1321b while overlapping with the 1324b.

In addition, the first communication passage 1315 and the second communication passage 1325 are formed as communication holes penetrating between the inner and outer peripheral surfaces of the main and sub-side second bearing protrusions 1315b and 1325b as shown in FIG. Alternatively, although not shown in the drawing, the main side second bearing protrusion 1315b and the sub side second bearing protrusion 1325b may be formed as a communication groove recessed to have a predetermined width and depth in cross-sections.

The vane rotary compressor according to the present embodiment as described above also stabilizes the behavior of the rotating shaft 123 as most of the main-side second pocket 1313b and the sub-side second pocket 1323b form a continuous bearing surface. To increase the mechanical efficiency of the compressor.

In addition, as the main second bearing protrusion 1314b and the sub-side second bearing protrusion 1324b almost close the main second pocket 1313b and the sub-side second pocket 1323b except for the communication passage. The main second pocket 1313b and the sub-side second pocket 1323b maintain a constant volume. Through this, the pressure pulsation of the back pressure supporting the vanes in the second pocket 1313b on the main side and the second pocket 1323b on the sub side is reduced to stabilize the behavior of the vanes and suppress vibration, thereby suppressing vibration between the vanes and the cylinder. It is possible to improve the compression efficiency by reducing the collision noise and reducing the leakage between the compression chambers.

In addition, even when driving for a long time, foreign substances can be prevented from flowing into the second pocket 1313b on the main side and the second pocket 1323b on the sub side, and then flowing between the bearing surfaces 1311a and 1321a and the rotating shaft 123 and accumulating. It may be, through this, it is possible to suppress the wear of the bearings 131, 132 or the rotary shaft 123.

Further, in the vane rotary compressor according to the present embodiment, a plurality of vanes are provided on the outer circumferential surface of the roller to form a plurality of compression chambers per rotation of the roller. Then, as the suction stroke (suction cycle) is shortened, the area of the compression chamber, that is, the area of the suction chamber, decreases, thereby reducing the suction flow rate of the refrigerant. Then, a pressure drop is generated for each compression chamber, and the performance coefficient of the refrigeration cycle including the compressor may decrease.

This phenomenon may occur even more when the inner peripheral surface of the cylinder is formed in an asymmetrical shape. That is, when the compression stroke is increased by forming the inner peripheral surface of the cylinder in an asymmetric shape, the suction stroke (suction cycle) decreases as the compression stroke increases. Then, as described above, as the area of the suction chamber constituting the compression chamber becomes smaller, the suction flow rate of the refrigerant further decreases, thereby causing a larger pressure drop in each compression chamber.

In view of this, in this embodiment, the suction flow rate of the refrigerant is increased by increasing the suction period by expanding the area of the suction port. However, since the suction port is defined by the height of the cylinder as described above, there is a limit to expanding the area of the suction port. In particular, when the suction port is formed as a single circle, there is a limit to enlargement of the size of the suction port. Accordingly, in this embodiment, the suction port is moved as close to the contact point as possible, and the suction port is formed in an irregular shape or a combination of a plurality of shapes having different inner diameters, so that the end of the suction port is positioned as far away from the contact point as possible. That is, the suction start point of the suction port is as advanced as possible, while the suction completion point of the suction port is delayed as much as possible, thereby expanding the actual suction area of the suction port. For convenience, the part close to the contact point is defined as the starting end of the inlet.

6 and 7 are a perspective view and a plan view showing a cylinder in the vane rotary compressor according to the present embodiment, and FIG. 8 is a radial direction from the inner circumferential surface of the cylinder to explain the first suction unit and the second suction unit according to the present embodiment. It is a front view shown.

As shown in these drawings, the suction port 1331 according to the present embodiment may include a first suction unit 1331a and a second suction unit 1331b. Accordingly, the suction port 1331 according to the present embodiment may have a circumferential length D1 longer than an axial length D2.

The first suction unit 1331a is formed to penetrate between the inner and outer circumferential surfaces of the cylinder 133, as shown in FIGS. 1 to 3 above. The first suction unit 1331a may be formed in a radial direction from the center of the outer diameter of the cylinder 133 (hereinafter, the center of the cylinder) Oc. However, the first suction part 1331a is not necessarily formed in the normal direction. However, since the first suction part 1331a is formed in a normal direction, when assembling other parts, the assembly standard is unified, and assembling the compressor may be facilitated.

Further, the first suction unit 1331a may be formed in a circular cross-sectional shape when projected in the radial direction. However, the first suction unit 1331a is preferably formed to secure an appropriate axial sealing length D3 from the upper and lower surfaces of the cylinder 133 to the first suction unit 1331a in consideration of refrigerant leakage. The axial sealing length D3 may be formed by about 2 mm each of the top and bottom. The first suction unit 1331a may be formed in various ways, such as a square, polygon, or ellipse in addition to a circle, and in these cases, it is preferable that the first suction unit 1331a is formed to secure the axial sealing distance D3 described above.

Meanwhile, the second suction unit 1331b may be formed in a rectangular cross-sectional shape when projected in the radial direction. However, it is preferable that the second suction unit 1331b is formed to secure an axial sealing distance as well as the first suction unit 1331a. However, since the second suction unit 1331b according to the present embodiment is formed smaller than the first suction unit 1331a, a larger axial sealing distance than the first suction unit 1331a can be secured. The second suction unit 1331b may be formed in various shapes other than a rectangular cross-sectional shape. This will be described later.

Meanwhile, the suction port according to the present embodiment may be formed to be closer to the contact point compared to the conventional suction port. 9 is a schematic view showing a position of a suction port according to the present embodiment compared with a conventional suction port position.

9, the center line of the first suction unit (or first suction port) 1331a is a first virtual line L1, and a line passing through the contact point P at the cylinder center Oc is a second virtual line L2. , When the line passing from the cylinder center Oc to the end of the second suction unit (or second suction port) 1331b is referred to as the third virtual line L3, the first virtual line L1 and the second virtual line ( The first intervening angle α1 between L2) may be formed to be 0.8 to 1.2 times greater than the second intervening angle α2 between the first virtual line L1 and the third virtual line L3.

In FIG. 9, referring to FIG. 11, which will be described later, an example is shown in which the first intervening angle α1 is 1.0 times the second intervening angle α2, that is, the first intervening angle α1 and the second intervening angle α2 are the same. .

That is, if the angle between the second virtual line L2 and the third virtual line L3, which can be referred to as the suction cycle, is approximately 60 degrees, the suction port 1331 is the starting end based on the cylinder center Oc. The angle from to the end is about 40 degrees.

First, since the end of the conventional suction port (S) meets the third virtual line (L3'), the start end of the conventional suction port (S) is approximately 20 degrees apart from the second virtual line (L2') passing through the contact point (P). Starts at the point where In other words, the conventional suction port (S) is formed at a position separated by about 20 degrees from the contact point (P).

On the other hand, in the suction port 1331 of the present embodiment, the angle between the start end and the end of the first suction unit 1331a is approximately 40 degrees, which is the same as that of the conventional suction port S. Then, since the second suction unit 1331b of the present embodiment is formed to extend approximately 10 degrees from the end of the first suction unit 1331a, the starting end of the first suction unit 1331a is a contact point ( It should be formed by moving approximately 10 degrees toward P). That is, the first suction unit 1331a of the present embodiment starts at a position spaced approximately 10 degrees from the second virtual line L2. Accordingly, the suction port 1331 of this embodiment is formed at a position approximately 10 degrees ahead of the conventional suction port S. Then, the end of the suction port 1331 of this embodiment is formed to the same angle as the end of the conventional suction port (S).

In general, since the rollers of the vane rotary compressor are circular, it is advantageous to secure a wide suction area of the suction chamber if the suction port is located far from the contact point. Therefore, in a vane rotary compressor, it is advantageous that the suction port is located as far away from the contact point as possible within a range in which the compression period is not shortened, since it is possible to maximize the suction area of the suction chamber.

To this end, in the conventional vane rotary compressor, as shown in FIG. 9, the first angle α1' is formed to be approximately 1.5 times the second angle angle α2'. However, this is disadvantageous in increasing the suction flow rate of the refrigerant since the suction start point at which the suction port S is opened is delayed as described above. Hereinafter, the suction flow rate of the refrigerant means the same as the mass flow rate of the refrigerant, but will be described as the suction flow rate of the refrigerant for convenience.

Accordingly, in this embodiment, the first suction unit 1331a is positioned as close as possible to the contact point P, while the second suction unit 1331b is positioned as far as possible from the contact point P, thereby forming the suction cycle as long as possible. will be. Through this, the suction flow rate of the refrigerant is increased to suppress the pressure drop.

On the other hand, as shown in Figs. 6 to 8, the first suction unit 1331a must secure an appropriate circumferential sealing distance D4 between the contact point P. To this end, the first suction unit ( 1331a) is located approximately 10 degrees apart from the contact point (P). The circumferential sealing distance (D4) may be about 2mm or so.

As described above, when the first suction unit 1331a is formed by moving to be close to the contact point P, the suction completion point (i.e., as the suction start point of the first suction unit 1331a moves toward the contact point P) Compression start point) also moves toward the contact point (P). Then, as the first suction unit 1331a moves toward the contact point P, the suction area may be rather reduced. Accordingly, in the present embodiment, the second suction unit 1331b described above may be additionally formed to reduce the suction area generated when the first suction unit 1331a moves toward the contact point P, and thereby compensate for the suction loss.

Hereinafter, a second suction unit will be described. As shown in FIG. 8, the second suction unit 1331b according to the present embodiment is formed in communication with one side of the first suction unit 1331a. The second suction part 1331b is formed to extend toward the rear side opposite to the contact point P based on the first suction part 1331a. That is, as the first suction part 1331a is formed as close as possible to the contact point P, the second suction part 1331b is at one side of the first suction part 1331a, that is, the rotational direction of the rotation shaft 123 (or , Is formed on the rear side of the first suction unit 1331a along the circumferential direction based on the rotational direction of the roller. For convenience, the contact point P side is defined as the front side and the opposite side as the rear side based on the first suction unit 1331a.

Meanwhile, the second suction unit 1331b may be formed on the front side toward the contact point P based on the first suction unit 1331a. However, when the second suction unit 1331b is formed on the front side based on the first suction unit 1331a, the suction area may be reduced compared to that on the rear side.

That is, in the vane rotary compressor, as the roller 134 is formed in a circular shape as described above, the area of the suction chamber decreases as it approaches the contact point P. Therefore, if the second suction unit 1331b having a smaller area than the first suction unit 1331a is formed on the front side of the first suction unit 1331a, the suction start point is pulled but the refrigerant flowing into the suction chamber is The suction flow may not increase significantly.

Furthermore, when a part of the second suction part 1331b is covered by a vane rotating together with the roller, the suction flow rate of the refrigerant may hardly increase. Therefore, the first suction part 1331a is formed on the front side of the second suction part 1331b as in the present embodiment. Since the suction stroke starts, the suction area of the suction chamber is enlarged to increase the suction flow rate of the refrigerant. It can be advantageous to make it happen.

Further, the second suction unit 1331b may be formed to be symmetrical to each other with respect to a virtual line passing through the center of the first suction unit 1331a in the circumferential direction. Accordingly, the refrigerant can be uniformly sucked.

In addition, the second suction unit 1331b may be formed to have a predetermined width and depth on the inner peripheral surface 133a of the cylinder 133. For example, as shown in FIG. 8, the circumferential length D6 of the second suction unit 1331b may be shorter than the circumferential length D5 of the first suction unit 1331a. The circumferential length D6 of the second suction unit 1331b may be formed to be approximately 30% or less of the circumferential length D5 of the first suction unit 1331a. If the circumferential length D6 of the second suction unit 1331b is excessively long, the compression start point is delayed and the compression cycle is shortened. Then, as the refrigerant is compressed in a short time, compression efficiency may decrease. Accordingly, it is preferable that the second suction unit 1331b be formed as wide as possible and not to delay the compression start point. Accordingly, the cross-sectional area of the second suction part 1331b may be formed to be approximately 20% or less of the cross-sectional area of the first suction part 1331a.

Also, as described above, the second suction unit 1331b may be formed in various shapes. That is, it is advantageous in terms of the suction flow rate of the refrigerant to form the second suction unit 1331b as wide as possible without delaying the compression start point. 6 and 8, the second suction unit 1331b may be formed in a rectangular cross-sectional shape when projected radially from the inner peripheral surface of the cylinder 133.

However, when the second suction part 1331b is formed in a square shape, it may be advantageous to increase the suction flow rate of the refrigerant while the suction area is wider than the circular or elliptical length to be described later. However, it may be disadvantageous in terms of surface pressure supporting the front surface of the vane. That is, if the second suction part 1331b is square, the contact surface that the vane contacts is suddenly increased at the end of the second suction part 1331b. Then, the surface pressure supporting the vane may change rapidly and the behavior of the vane may become unstable. Accordingly, the second suction unit 1331b having a circular or elliptical shape, which will be described later, may gradually increase the surface pressure to the vane, and thus it may be preferable in terms of the behavior of the vane. These will be described later together with the shape of the second suction unit.

Meanwhile, as described above, when the suction port 1331 is formed of the first suction unit 1331a and the second suction unit 1331b in the vane rotary compressor, the suction flow rate increases as the suction cycle of the refrigerant increases. Through this, it is possible to increase the performance of the refrigeration cycle including the compressor by suppressing the pressure drop in the compression chamber.

That is, if the first suction part 1331a and the second suction part 1331b are arranged in a circumferential direction by communicating with each other as in this embodiment, the suction port 1331 can be brought as close as possible toward the contact point P, so that suction starts. At the same time, as the time point is advanced, the first suction unit 1331a, which has a larger area than the second suction unit 1331b, is positioned at the contact point, thereby further increasing the suction flow rate of the refrigerant from the start of suction.

On the other hand, the second suction unit 1331b may be formed by extending to maintain the original suction completion point, similar to the conventional suction port. Then, even when the vane passes through the first suction unit 1331a, the second suction unit 1331b remains open, so that the refrigerant continues to flow into the compression chamber through the second suction unit 1331b. Then, while the suction period in the compression chamber is extended by the range of the second suction unit 1331b, a substantial suction area of the compression chamber may be expanded. Through this, it is possible to increase compression efficiency by reducing the pressure drop in the compression chamber relative to the area of the same compression space.

10A to 10D are schematic diagrams illustrating a process of forming a compression chamber according to a position of a vane in the vane rotary compressor according to the present embodiment.

First, FIG. 10A shows a state in which the preceding vane 1351 approaches the start end of the first suction unit 1331a. Then, on the rear side of the preceding vane 1351, the second contact point P2 between the preceding vane 1351 and the cylinder 133, and the contact point between the roller 134 and the cylinder 133 (hereinafter, the first contact point) ( A first compression chamber V1 is formed between P1). At this time, since the preceding vane 1351 has not yet passed through the start end of the first suction unit 1331a, the first compression chamber V1 has formed a suction area, but the refrigerant is not sucked into the first compression chamber V1. It is not in a state.

10B shows a state in which the preceding vane 1351 has reached the boundary point between the first suction unit 1331a and the second suction unit 1331b. In general, the suction port of a vane rotary compressor forms a maximum suction area (or maximum open area) for a corresponding compression chamber when the vane reaches the circumferential end of the suction port. Accordingly, in this embodiment, when the preceding vane 1351 reaches the boundary point between the first suction unit 1331a and the second suction unit 1352, the first compression chamber reaches the maximum suction area. In this state, the refrigerant is no longer sucked into the preceding compression chamber, but only into the following first compression chamber (V1). However, in this embodiment, as the second suction unit 1331b is formed, some refrigerant may be sucked into the preceding compression chamber.

10C is a state in which the preceding vane 1351 has passed through the second suction unit 1331b. This means that the refrigerant is no longer sucked into the preceding compression chamber, and only the refrigerant is sucked into the following first compression chamber. Accordingly, the compression in the preceding compression chamber proceeds while the refrigerant is continuously sucked in the following first compression chamber V1.

10D shows a state in which the preceding vane 1351 as well as the trailing vane 1352 have passed through the second suction unit 1331b. This is a state in which the suction stroke of the first compression chamber V1 is completed and the compression stroke proceeds. Therefore, afterwards, while the suction area of the first compression chamber V1 is reduced, compression is performed on the sucked refrigerant.

When comparing the suction port according to the present embodiment with the conventional suction port, it is the same as the graph shown in FIG. 11. 11 is a graph showing a comparison of the suction flow rate in the compression chamber and the suction area of the compression chamber with respect to the rotation angle of the roller in order to explain the effect of the present embodiment. The suction flow rate of the refrigerant refers to the mass flow rate of the refrigerant sucked into the compression chamber.

In this graph, the rotation angle of the roller or the rotation shaft (specifically, the preceding vane) was defined as the rotation angle, and the rotation angle defined the contact point between the cylinder and the roller at 0 degrees. In addition, this is a result of an experiment based on the fact that the first suction unit of this embodiment and the conventional suction port have the same shape and the same area, and the first suction unit of this embodiment is formed by moving toward the contact point by approximately 10 degrees compared to the conventional suction port. to be. In addition, this is the result of an experiment based on an example in which three vanes are arranged at 120 degree intervals.

Referring to FIG. 9, the first suction part 1331a and the conventional suction port S of the present embodiment are formed to have the same shape and area, but the suction port of this embodiment is approximately 10 degrees of rotation angle compared to the conventional suction port. It is formed close to the contact point. Accordingly, as shown in FIG. 11, the suction flow rate of the refrigerant to the compression chamber in the present embodiment and in the related art is changed to a substantially the same pattern with a difference of approximately 10 degrees up to a specific rotation angle.

First, until the rotation angle is approximately 10 degrees, neither the present embodiment nor the conventional manufacturer have formed the suction area of the suction port for the compression chamber. This is a state corresponding to FIG. 10A and is a state before the first suction unit communicates with the compression chamber.

Next, when the rotation angle becomes about 10 degrees, in this embodiment, the suction area of the suction port for the compression chamber starts to be formed. On the other hand, conventionally, the suction area for the compression chamber is still in a state before being formed. Conventionally, when the rotation angle is about 20 degrees, the suction area of the suction port for the compression chamber starts to be formed. However, in the present embodiment, when the rotation angle is about 20 degrees, the suction area of the suction port for the compression chamber is substantially enlarged. Therefore, the suction flow rate of the refrigerant is already higher in this embodiment than in the prior art.

Next, when the rotation angle is about 50 degrees, the present embodiment reaches the maximum suction area. Conventionally, it has not yet reached the maximum suction area. This is a state corresponding to FIG. 10B. Thereafter, the suction flow rate of the refrigerant increases to the maximum while maintaining the maximum suction area until the rotation angle is approximately 50 to 130 degrees, and then gradually decreases. Conventionally, when the rotation angle is about 60 degrees, the maximum suction area is reached.

Next, when the rotation angle is about 130 degrees, in the present embodiment, the suction area for the compression chamber begins to decrease, and the suction flow rate of the refrigerant begins to rapidly decrease. This is a state in which the trailing vane has reached the start end of the first suction unit. Conventionally, the suction area starts to decrease only when the rotation angle is approximately 140 degrees.

Next, when the rotation angle is about 180 degrees, in this embodiment, the suction area for the compression chamber becomes zero, and compression of the compression chamber is started. This is a state corresponding to FIG. 10D, and the suction flow rate of the refrigerant is theoretically zero. Here, even in the prior art, the compression start angle is formed at about 180 degrees. This is, in the case of the present embodiment, the start end of the first suction unit is formed 10 degrees ahead of the conventional one, but in this embodiment, the compression start angle can be formed as in the prior art as the second suction unit is additionally formed.

If the second suction part is not formed in this embodiment, the suction completion angle in this embodiment is formed 10 degrees before the compression start angle. Then, the compressor operates in a state in which the refrigerant is not sucked as much as possible compared to the volume of the compression chamber. Then, the refrigerant expands while the compressor is operating by approximately 10 degrees, and then starts compression, so that the compressor efficiency may be greatly reduced. Accordingly, when the suction start angle is advanced as in the present embodiment, the efficiency of the compressor should be prevented from deteriorating only when the suction completion angle and the compression start angle are matched.

Meanwhile, as described above, it is desirable to increase the area of the second suction unit 1331b in order to increase the amount of refrigerant suction in the second half of the suction stroke of the present embodiment. However, since the circumferential length of the second suction unit 1331b is determined together with the compression start point, the axial direction of the second suction unit 1331b is enlarged to the maximum, thereby increasing the area of the second suction unit 1331b. I can.

12 to 14 are front views showing another embodiment of a suction port according to the present embodiment.

As shown in FIG. 12, the second suction part 1331b according to the present embodiment is formed in a square shape, but the axial height D7 of the second suction part 1331b is the axial height of the first suction part 1331a. (Or inner diameter) (D2) can be formed in the same manner. Through this, the area of the second suction unit can be maximized. However, as described above, when the second suction unit 1331b is formed in a square shape, the surface pressure on the vane at the point where the second suction unit 1331b ends is rapidly changing and the behavior of the vanes may become unstable.

In consideration of this, the second suction unit 1331b is formed in a circular shape as shown in FIG. 13, but the axial height D7 may be formed equal to the axial height D2 of the first suction unit 1331a. . In this case, the second suction part 1331b is formed at a position where a part thereof overlaps the first suction part 1331a, and if the part overlapped with the first suction part 1331a is connected to a virtual circle, the second suction part (1331b) has an elliptical shape. Then, the area of the second suction unit 1331b becomes narrower toward the rear, and conversely, the sealing distance D3 is gradually enlarged. Accordingly, while increasing the area of the second suction unit 1331b, it is possible to suppress a sudden change in the surface pressure to the vane.

However, the second suction unit 1331b is formed in a circular shape as shown in FIG. 14, but the axial height D7, which is the inner diameter of the virtual circle, is smaller than the axial height D2, which is the inner diameter of the first suction unit 1331a. Can be formed. In this case, when the second suction unit 1331b connects the overlapped portion on the first suction unit 1331a with a virtual circle, the second suction unit 1331b has a true circle shape consisting of one curvature. Then, as in the embodiment of FIG. 13, the area of the second suction unit 1331b becomes narrower toward the rear, and the sealing distance gradually increases. Accordingly, while increasing the area of the second suction unit 1331b, it is possible to suppress a sudden change in the surface pressure to the vane. However, in this embodiment, compared to the embodiment of FIG. 13, as the area of the second suction unit 1331b is smaller, the sealing distance D3 is further enlarged to increase the surface pressure against the vane, thereby supporting the vane more stably. can do.

In addition, although not shown in the drawings, the second suction unit may be formed in various ways, such as a wedge shape or an angled shape.

As the second suction unit 1331b according to the present embodiments as described above is formed to decrease in cross-sectional area in a direction away from the first suction unit 1331a, the vane is It is possible to stabilize the behavior of the vane by suppressing an excessive increase in the fluctuation range of the surface pressure to and through this, it is possible to increase the compression efficiency by suppressing leakage between the compression chambers.

Meanwhile, the second suction units 1331b described above may have the same depth along the circumferential direction. When the second suction part 1331b has the same depth along the circumferential direction, it is possible to facilitate the processing of the cylinder including the second suction part 1331b. However, when the depth of the second suction part 1331b is the same, the end, that is, the point forming the suction completion angle is stepped. Then, the refrigerant sucked into the suction chamber through the second suction part 1331b may form a vortex, resulting in suction loss. Accordingly, the second suction unit 1331b may have different depths along the circumferential direction.

15 to 17 are perspective views and cross-sectional views showing other embodiments of the second suction unit according to the present embodiment.

15 and 16, the second suction unit 1331b according to the present embodiment may have an inner peripheral surface inclined in a longitudinal direction. That is, the second suction unit 1331b has a shape that becomes deeper from the inner circumferential surface 133a of the cylinder 133 toward the outer circumferential surface, that is, the inner circumferential surface of the second suction unit 1331b is formed as an inclined surface portion 1331c having a predetermined inclination angle. I can. Accordingly, the second suction unit 1331b may be formed to be deepest in contact with the first suction unit 1331a and to be shallower as the distance from the first suction unit 1331a in the circumferential direction of the cylinder 133 increases.

As described above, when the inclined surface portion 1331c is formed on the inner circumferential surface of the second suction unit 1331b, the refrigerant flowing from the first suction unit 1331a to the second suction unit 1331b is gently inclined surface portion 1331c. As it moves along, the refrigerant can be quickly sucked. In addition, the stepped surface is not formed even at the point at which the suction completion angle is achieved, so that the occurrence of eddy current in the suctioned refrigerant can be suppressed. Accordingly, as the refrigerant rapidly flows into the suction chamber constituting the compression chamber through the second suction unit 1331b, the suction flow rate of the refrigerant may be increased. Then, it is possible to increase compression efficiency by suppressing the occurrence of a pressure drop for the refrigerant in the compression chamber.

Referring to FIG. 17, the second suction unit 1331b according to the present embodiment has an inner circumferential surface formed of an inclined surface portion 1331c as shown in FIG. 16 described above, and a cylinder 133 is disposed at the end of the second suction unit 1331b. A space portion 1331d recessed to the same depth on the inner peripheral surface of) may be further formed. That is, a space portion 1331d having a straight surface so as to be parallel to the first suction portion 1331a may be formed at an inner end of the inclined surface portion 1331c. Accordingly, in the second suction unit 1331b, as the start end forms the inclined surface portion 1331c, the refrigerant is rapidly sucked and the space portion 1331d is formed at the end, so that the volume of the suction port is enlarged. It can be inhaled more quickly.

On the other hand, when the environment-friendly refrigerant R32 is applied to the vane rotary compressor as described above, the effect can be enhanced.

As described above, the eco-friendly refrigerant R32 has been developed as a refrigerant that replaces R410a. However, R32 has a smaller refrigerant particle density than R410a, resulting in insufficient mass flow. Then, the amount of refrigerant intake is reduced compared to the volume of the same compression chamber. In particular, when the inner circumferential surface of the cylinder has an asymmetrical shape, the suction period may be shortened and the amount of refrigerant suction may be further reduced. Then, a pressure drop in the compression chamber may occur, and thus the above-described increase in suction loss and a decrease in volumetric efficiency may further increase, and the performance coefficient of the compressor may be further lowered. This may occur more significantly in a heating low temperature condition, a high pressure ratio condition (Pd/Ps ≥ 6), and a high speed operation condition (80 Hz or more).

However, as in the present embodiment, the suction port is formed of a first suction unit 1331a and a second suction unit 1331b, and the second suction unit 1331b is centered on the first suction unit 1331a. As it is extended (rear side with respect to the rotational direction of the rotating shaft), the suction completion point (or compression start point) is delayed, thereby increasing the actual suction area of the compression chamber, increasing the amount of refrigerant sucked into the compression chamber. . Then, even if a refrigerant having a low particle density such as R32 is applied to a vane rotary compressor, the discharge pressure can be maintained at a similar level as when a refrigerant such as R410a is applied. Accordingly, R32 having a low global warming index can be used as an alternative refrigerant instead of a refrigerant having a high global warming index such as R410.

Claims (14)

A cylinder having an inner circumferential surface formed in an asymmetrical oval shape, and spaced apart from the suction port and the discharge port by a predetermined distance in the circumferential direction;
A main bearing and a sub-bearing coupled to the cylinder to form a compression space together with the cylinder;
A rotation shaft supported in a radial direction by the main bearing and the sub bearing;
A roller eccentrically accommodated in the compression space to form a contact point with the inner circumferential surface of the cylinder, rotates together with the rotation shaft, and has a plurality of vane slots formed along the circumferential direction; And
A plurality of vanes each slidably inserted into the vane slots of the rollers and protruding in a direction toward the inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers; and
The suction port,
A first suction part formed to penetrate between the inner and outer circumferential surfaces of the cylinder; And
A second suction unit formed in a groove shape having a predetermined depth on the inner circumferential surface of the cylinder and communicating with the first suction unit at the opposite side of the contact point based on the first suction unit, and
The second suction unit,
A vane rotary compressor, characterized in that extending from an inner circumferential surface of the first suction unit located opposite to the discharge port with respect to the middle of the circumferential direction of the first suction unit in the rotational direction of the rotation shaft along the inner circumferential surface of the cylinder. The method of claim 1,
A line passing through the longitudinal center of the first suction unit is a first virtual line, a line passing through the center of the outer diameter of the cylinder and the contact point is a second virtual line, and a line passing through the center of the outer diameter of the cylinder and the end of the second suction unit. When it comes to the third virtual line,
The vane rotary compressor, characterized in that the first angle between the first virtual line and the second virtual line is formed to form a range of 0.8 to 1.2 times the second angle between the first virtual line and the third virtual line. The method of claim 2,
The vane rotary compressor, characterized in that the first and second angles are the same. The method of claim 1,
The vane rotary compressor, characterized in that the area of the first suction part is formed larger than the area of the second suction part. The method of claim 4,
Vane rotary compressor, characterized in that the cross-sectional area of the second suction part is formed equally in the rotation direction of the rotation shaft. The method of claim 4,
Vane rotary compressor, characterized in that the cross-sectional area of the second suction unit is formed to gradually decrease in the rotational direction of the rotation shaft. The method of claim 4,
An axial height of the second suction unit is formed to be smaller than an axial height of the first suction unit. The method of claim 4,
An axial height of the second suction unit is formed equal to the axial height of the first suction unit. The method of claim 1,
The second suction part is a vane rotary compressor, characterized in that formed to have the same depth along the circumferential direction of the cylinder. The method of claim 1,
The vane rotary compressor, characterized in that the second suction unit is formed to be inclined to become deeper as the first suction unit approaches. The method of claim 10,
The second suction part is a vane rotary compressor, characterized in that a space part formed in a straight plane parallel to the first suction part from an inner circumferential surface of the cylinder to a predetermined depth. The method according to any one of claims 1 to 11,
The suction port is a vane rotary compressor, characterized in that the length in the circumferential direction is formed larger than the length in the axial direction. The method of claim 12,
At least one of the plurality of bearings has a back pressure pocket in communication with the rear side of the vane slot, and the back pressure pocket is separated along a circumferential direction to form a plurality of pockets having different internal pressures,
On the inner circumferential side of the plurality of pockets facing the outer circumferential surface of the rotation shaft, a bearing protrusion forming a radial bearing surface with respect to the outer circumferential surface of the rotation shaft is formed in a cylindrical shape,
The plurality of pockets,
A first pocket having a first pressure; And
Consisting of; a second pocket having a pressure higher than the first pressure,
The vane rotary compressor, characterized in that a communication passage is formed at a portion of the bearing protrusion facing the second pocket to communicate an inner circumferential surface and an outer circumferential surface of the bearing protrusion. The method of claim 13,
The communication flow path is formed as a communication groove recessed in the upper surface of the bearing protrusion or a communication hole penetrating between the inner circumferential surface and the outer circumferential surface of the bearing protrusion.

Images