KR20200093350A - Vain rotary compressor - Google Patents

Abstract

According to the present invention, a vane rotary compressor includes: a cylinder including a suction port; a main bearing and a sub bearing combined with the cylinder to form a compression space together with the cylinder; a rotary shaft supported by the main bearing and the sub bearing in a radial direction; a roller eccentrically stored in the compression space to form a contact point with the inner circumferential surface of the cylinder, rotated together with the rotary shaft, and having a plurality of vane slots formed in a circumferential direction; and a plurality of vanes inserted into the vane slots of the roller, respectively, and protruding in a direction toward the inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers. The suction port includes: a first suction part formed by penetrating between the outer and inner circumferential surfaces of the cylinder; and a second suction part formed in a groove shape having a preset depth on the inner circumferential surface of the cylinder, connected to the first suction part on the opposite side of the contact point with respect to the first suction part, and extended from the inner circumferential surface of the cylinder in a rotating direction of the rotary shaft. Therefore, the vane rotary compressor is capable of suppressing pressure deterioration by increasing the suction flow rate of a refrigerant.

Description

VAN ROTARY COMPRESSOR

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

The rotary compressor can be divided into a method in which the vane slides into the cylinder and contacts the roller, and a vane slips into the roller and contacts the cylinder. Generally, the former is called a rotary compressor, and the latter is called a vane rotary compressor.

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

The rotary compressor independently forms a compression chamber for the number of vanes per revolution 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, and 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 a global warming index (GWP), such as R32, R410a, and CO ₂ .

In a vane rotary compressor, as one compression space is divided into a plurality of compression chambers, as the compression stroke is shortened, the coefficient of performance (COP) of the compressor may be reduced. Accordingly, the vane rotary compressor disclosed in the patent document [Japanese Patent Publication: JP2014-040797A, (published date: 2014.03.06)] has an inner circumferential surface of the cylinder formed in an asymmetrical shape so as to increase the compression stroke (compression cycle).

However, in the conventional vane rotary compressor as described above, as the compression stroke (compression cycle) increases, the suction stroke (suction cycle) decreases conversely. Then, the suction flow rate of the refrigerant sucked into the compression chamber constituting the suction chamber is reduced, and a pressure drop in the compression chamber may occur. Then, as the volumetric efficiency in the compression chamber decreases, the performance coefficient of the compressor decreases. This problem occurs as a characteristic of a vane rotary compressor, as in the case of an asymmetric elliptical shape in the case of a circular or symmetrical elliptical shape of the inner circumferential surface of the cylinder. However, in the case of an asymmetric ellipse, the above-described problem may be more serious.

In addition, in the conventional vane rotary compressor, the area of the inlet is limited by the axial height of the cylinder as the inlet is formed through the cylinder in the radial direction. Furthermore, since the sealing distance must be secured on both sides of the 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, and a pressure drop may occur while the suction flow rate of the refrigerant is reduced.

In addition, in the conventional vane rotary compressor, when the environmentally friendly refrigerant R32 is applied, the above-described problem may be more serious. That is, R32 was developed as a refrigerant to replace R410a, but the particle density of the refrigerant is smaller than that of R410a, resulting in insufficient mass flow rate. Then, the pressure drop compared to the volume of the same compression chamber occurs, so that the increase in suction loss and the decrease in volume efficiency resulting from the above-described increase may further increase the performance coefficient of the compressor. This can occur more significantly under low temperature heating conditions, high pressure ratio conditions (Pd/Ps ≥ 6), and high speed operating conditions (80 Hz or more).

Patent document: Japanese published patent: JP2014-040797A, (published date: 2014.03.06)

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

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

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

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

In addition, another object of the present invention is to increase the suction flow rate of the refrigerant by increasing the suction cycle even when applying the eco-friendly refrigerant R32, thereby reducing the pressure drop in the compression chamber to improve the vane rotary compressor. I want to provide.

In order to achieve the object of the present invention, the suction port is intended to provide a vane rotary compressor characterized in that the circumferential length is formed longer than the axial length.

Furthermore, 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.

Furthermore, the present invention includes a suction guide groove formed at a position close to a contact point between a cylinder and a roller, and a suction guide groove communicating with the suction hole and formed to be located farther from the contact point than the main suction hole, 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 inlet.

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 the radial direction by the main bearing and the sub bearing; A roller which is eccentrically accommodated in the compression space to form a contact point with the inner circumferential surface of the cylinder and rotates with the rotating shaft, and a plurality of vane slots formed along the circumferential direction; And a plurality of vanes that slide into the vane slots of the roller, and protrude in the direction toward the inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers. The intake port includes an inner circumferential surface of the cylinder. A first suction part formed through the outer peripheral surface; And a groove shape having a predetermined depth on the inner circumferential surface of the cylinder, communicating with the first suction part on the opposite side of the contact point based on the first suction part, and extending in the rotational direction of the rotating shaft from the inner circumferential surface of the cylinder. A vane rotary compressor may be provided, characterized in that it comprises; a second suction portion formed.

Here, the line passing through the longitudinal center of the first suction unit, the first virtual line, the line passing through the contact point and the center of the outer diameter center of the cylinder, the second virtual line, passing through the center of the outer diameter center 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 such that a second angle between the first virtual line and the third virtual line ranges from 0.8 to 1.2 times. have.

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

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

Further, the cross-sectional area of the second suction part may be formed in the same direction in the rotational direction of the rotation shaft.

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

In addition, the axial height of the second suction part may be smaller than the axial height of the first suction part.

In addition, the axial height of the second suction part may be the same as the axial height of the first suction part.

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

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

In addition, the second suction part may be formed with a space portion having a straight surface 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 circumferential length greater than the axial length.

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

And, the plurality of pockets, a first pocket having a first pressure; And a second pocket having a pressure higher than the first pressure; consisting of, in the bearing protrusion of the second pocket, the communication passage to communicate the outer circumferential surface opposite to the inner circumferential surface of the bearing protrusion facing the outer circumferential surface of the rotating shaft Can be formed.

In the vane rotary compressor according to the present invention, the suction start angle of the suction port is moved to be close to the contact point, and at the same time, the suction completion angle and the compression start angle are delayed as much as possible, thereby extending the suction cycle while maintaining the compression cycle of the compression chamber and inhaling the refrigerant. The flow rate can be increased. Through this, the pressure drop compared to the volume of the same compression chamber can be suppressed to improve the performance of the compressor.

In addition, in the vane rotary compressor according to the present invention, a plurality of suction ports communicating with each other are arranged in the circumferential direction, thereby increasing the suction area while securing the sealing distance of the suction ports formed through the radial direction. Through this, the suction cycle of the refrigerant can be extended by extending the suction cycle.

In addition, 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 reducing the pressure drop in the compression chamber even when applying the eco-friendly refrigerant R32. The coefficient can be increased.

In addition, the vane rotary compressor according to the present invention can enhance the effects described above even under low temperature heating conditions, high pressure ratio conditions, and high speed operation conditions.

1 is a cross-sectional view showing an example of a vane rotary compressor according to the present invention in longitudinal section,
2 and 3 are cross-sectional views of the compression unit applied to FIG. 1, and FIG. 2 is a cross-sectional view taken along line "IV-IV" in FIG. 1, and FIG. 3 is a cross-sectional view taken along line "V-V" in FIG. 2,
4 (a) to 4 (d) are cross-sectional views showing a process in which refrigerant is sucked, compressed and discharged from the cylinder according to this embodiment
5 is a cross-sectional view of a vane rotary compressor according to this embodiment, showing a compression section in longitudinal section to explain the back pressure of each back pressure chamber;
6 and 7 is 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 the first suction part and the second suction part according to the present embodiment,
Figure 9 is a schematic view showing the position of the inlet according to the present embodiment compared to the conventional inlet position,
10A to 10D are schematic views showing to explain the process of forming the compression chamber according to the position of the vane in the vane rotary compressor according to the present embodiment;
11 is a graph showing the suction flow rate in the compression chamber and the suction area of the compression chamber compared to the prior art for explaining the effect of the operation according to the present embodiment,
12 to 14 are front views showing another embodiment of the intake according to this embodiment,
15 to 17 are perspective and cross-sectional views showing other embodiments of the second suction unit according to the present embodiment.

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

Referring to Figure 1, the vane rotary compressor according to the present invention, the 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 arranged 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 arranged on both left and right sides.

The driving motor 120 serves to provide power to compress the refrigerant. The driving motor 120 includes a stator 121, a rotor 122, and a rotating 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 shrinking or the like. For example, the stator 121 may be fixedly installed on the inner circumferential 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. At the center of the rotor 122, a rotating shaft 123 is press-fitted and coupled. Accordingly, the rotating shaft 123 rotates concentrically with the rotor 120.

In the center of the rotating shaft 123, an oil passage 125 is formed in the axial direction, and in the middle of the oil passage 125, oil through holes 126a and 126b are formed through the outer circumferential surface of the rotating shaft 123. The oil through holes 126a and 126b are made up of a first oil through hole 126a belonging to the range of the first water condensing part 1311 and a second oil through hole 126b belonging to the range of the second condensing part 1321, which will be described later. . Each of the first oil through hole 126a and the second oil through hole 126b may be formed one by one, or may be formed by a plurality of oil through holes. This embodiment shows an example in which a plurality of dogs are formed.

The oil feeder 127 is installed in the middle or bottom 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 along the oil passage 125, and then through the second oil through hole 126b. To the sub-bearing surface (1321a), it is supplied to the main bearing surface (1311a) through the first oil through hole (126b).

The first oil through hole 126a is preferably formed to overlap the first oil groove 1311b, which will be described later, and the second oil through hole 126b overlaps the second oil groove 1321b. Through this, the oil supplied to the bearing surfaces 1311a and 1321a of the main bearing 131 and 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 main side second pocket 1313b and the sub side second pocket 1323b. This will be described later.

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

1 and 2, the main bearing 131 and the sub-bearing 132 are fixedly installed in the casing 110 and spaced apart from each other along the rotation axis 123. The main bearing 131 and the sub-bearing 132 serve to support the rotating shaft 123 in the radial direction while simultaneously supporting the cylinder 133 and the roller 134 in the axial direction. Accordingly, the main bearing 131 and the sub-bearing 132 are radially extending from the water-reducing parts 1311 and 1321 and the water-reducing parts 1311 and 1321, which radially support the rotating shaft 123. Each of the branches 1312 and 1322 may be formed. For convenience, the water-reducing portion of the main bearing 131 is the first water-reducing portion 1311 and the flange portion is the first flange portion 1312, and the water-reducing portion of the sub-bearing 132 is the second water-reducing portion 1321 and the second flange portion It is defined as (1322).

Referring to FIGS. 1 and 3, the first shaft part 1311 and the second shaft part 1321 are respectively formed in a bush shape, and the first flange portion and the second flange portion are formed in a disk shape. A first oil groove 1311b is provided on a radial bearing surface (hereinafter abbreviated as a bearing surface or a first bearing surface) 1311a, which is an inner circumferential surface of the first shaft part 1311, and an inner peripheral surface of the second shaft part 1321 A second oil groove 1321b is formed on the radial bearing surface (hereinafter abbreviated as a bearing surface or a second bearing surface) 1321a, respectively. The first oil groove 1311b is formed by a straight line or a diagonal line between the upper and lower ends of the first shaft portion 1311, and the second oil groove 1321b is a straight line or a diagonal line between the upper and lower ends of the second shaft portion 1321 Is formed into.

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 flow path 1315 and the second communication flow path 1325 are for guiding oil flowing into the bearing surfaces 1311a and 1321a to the main back pressure pocket 1313 and the sub back pressure pocket 1323. This will be described later with the back pressure pocket.

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

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

The main side first pocket 1313a forms a lower pressure than the main side second pocket 1313b, for example, an intermediate pressure between the suction pressure and the discharge pressure, and the sub side first pocket 1323a is a sub side agent A pressure lower than that of the two pockets 1323b is formed, for example, an intermediate pressure almost equal to that of the main first pocket 1313a. The main side first pocket 1313a provides a fine passage between the main side first bearing protrusion 1314a and the upper surface 134a of the roller 134, and the sub side first pocket 1323a is a sub side product to be described later. 1 As the oil passes through the micro-paths between the bearing protrusion 1314a and the lower surface 134b of the roller 134, respectively, and flows into the main and sub-side first pockets 1313a and 1323a, pressure is reduced to form an intermediate pressure. do. However, the main side second pocket 1313b and the sub side second pocket 1323b have a main bearing surface 1311a and a sub bearing surface 1321a through the first oil through hole 126a and the second oil through hole 126b. Since the oil flowing into the first and second flow passages 1315 and 2nd communication passages 1325 to be described later flows into the main and sub-side second pockets 1313b and 1323b, the pressure in the discharge or near discharge pressure Will maintain. This will be described later.

In the cylinder 133, an inner circumferential surface forming the compression space V is formed in an elliptical shape. The inner circumferential surface of the cylinder 133 may be formed in a symmetrical elliptical 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 asymmetric oval shape having several pairs of long and short axes. This asymmetric elliptical cylinder 133 is usually referred to as a 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 elliptical shape.

2 and 3, the hybrid cylinder according to the present embodiment (hereinafter abbreviated as a cylinder) 133 may be formed in a circular outer circumferential surface, even if it is non-circular, the inner circumferential surface of the casing 110 If it is a fixed shape, it may be sufficient. 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 may be concluded.

In addition, an empty space portion is formed in the central portion of the cylinder 133 to form a compressed space V including an inner circumferential surface. The empty space portion is sealed by the main bearing 131 and the sub-bearing 132 to form a compressed space V. The roller 134 to be described later is rotatably coupled to the compression space V.

The inner circumferential surface 133a of the cylinder 133 is centered at a point where the inner circumferential surface 133a of the cylinder 133 and the outer circumferential surface 134c of the roller 134 are almost in contact, respectively, and the inlet 1331 and the outlet ( 1332a) (1332b) are formed.

The suction port 1331 is a first suction portion 1331a formed through the inner circumferential surface of the cylinder 133 to the outer circumferential surface, and a second extending in a circumferential direction from one end of the first suction portion 1331a to form a groove It may be made of a suction unit (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. It is indirectly connected to the discharge pipe 114 through-coupled to the casing 110. Accordingly, the refrigerant is sucked directly into the compression space V through the suction port 1331, while the compressed refrigerant is discharged through the discharge port 1332a and 1332b into the inner space 110 of the casing 110 and then discharged. It is discharged to the pipe 114. Therefore, the internal space 110 of the casing 110 maintains a high pressure state that achieves discharge pressure.

In addition, while a separate suction valve is not installed in the suction port 1331, discharge valves 1335a and 1335b that open and close the discharge ports 1332a and 1332b are installed in the discharge ports 1332a and 1332b. The discharge valves 1335a and 1335b may be formed of a reed type 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 required in addition to a reed type valve, such as a piston valve.

In addition, when the discharge valves 1335a and 1335b are made of a reed type valve, valve grooves 1336a and 1336b are formed on the outer circumferential surface of the cylinder 133 so that the discharge valves 1335a and 1335b can be mounted. Accordingly, the length of the discharge ports 1332a and 1332b is reduced to a minimum, thereby reducing the dead volume. The valve grooves 1336a and 1336b may be formed in a triangular shape so as to secure a flat valve seat surface as shown in FIGS. 2 and 3.

On the other hand, a plurality of discharge ports 1332a and 1332b are formed along a compression path (compression direction). For convenience, the plurality of discharge ports 1332a and 1332b are discharge ports located on the upstream side of the compression path as a secondary discharge port (or first discharge port) 1332a, and the discharge ports located on the downstream side are the main discharge ports (or the 2 discharge port) 1332b.

However, the secondary discharge port is not necessarily an essential configuration, and can be selectively formed as necessary. For example, if the inner circumferential surface 133a of the cylinder 133 is formed to have a long compression cycle, as described later, to reduce the overcompression of the refrigerant appropriately, a secondary discharge port may not be formed. However, in order to reduce the amount of overcompression of the compressed refrigerant to a minimum, the conventional secondary discharge port 1332a may be formed in front of the main discharge port 1332b, that is, on the upstream side of the main discharge port 1332b based on the compression progression direction. 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 outer circumferential surface 134c of the roller 134 is formed in a circular shape, and a rotating shaft 123 is integrally coupled to the center of the roller 134. Thus, the roller 134 has a center (Or) coinciding with the axis center (Os) of the rotating shaft 123, and the concentric rotation with the rotating 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, referred to as the center of the cylinder for convenience) (Oc). One side of the outer peripheral surface 134c of the roller 134 is almost in contact with the inner peripheral surface 133a of the cylinder 133. Here, when one point of the cylinder 133 that one side of the outer circumferential surface of the roller 134 is closest to the inner circumferential surface of the cylinder 133 and the roller 134 is almost in contact with the cylinder 133 is called a contact point P , The contact point P and the center line passing through the center of the cylinder 133 may be a position corresponding to the shortening of the elliptic curve forming the inner circumferential surface 133a of the cylinder 133.

The roller 134 is formed along a circumferential direction on its outer circumferential surface, and a plurality of vane slots 1341a, 1341b, 1341c are formed at appropriate locations, and vanes 1351, 1352, and 1353 are provided for each vane slot 1341a, 1341b, 1341c. ) Are each inserted 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 is 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, so that the vane length can be sufficiently secured.

Here, the direction in which the vanes 1351, 1352, and 1353 are inclined is reverse to the rotational direction of the rollers 134, that is, the front surface of the vanes 1351, 1352, and 1353 that contact the inner circumferential surface 133a of the cylinder 133. Tilting toward the rotational direction of the roller 134 may be preferable because the compression start angle can be pulled toward the rotational direction of the roller 134 so that compression can be started quickly.

In addition, at the inner end of the vane slots 1341a, 1341b, 1341c, oil (or refrigerant) is introduced to the rear side of the vanes 1351, 1352, and 1353, so that each vane 1351, 1352, 1353 is inserted into the cylinder 133. Back pressure chambers 1334a, 1334b, and 1334c that can be forced in the inner peripheral surface direction are formed. For convenience, the direction toward the cylinder based on the direction of movement of the vane is defined as the front side and the opposite side as the rear side.

The back pressure chambers 1334a, 1334b, and 1334c are sealed by the main bearing 131 and the sub bearing 132. The back pressure chambers 1334a, 1334b, and 1334c may each independently communicate with the back pressure pockets 1313 and 1323, but a plurality of back pressure chambers 1334a, 1334b, and 1334c may be provided by the back pressure pockets 1313 and 1323. It may be formed to communicate with each other.

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

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

When the vanes 1351, 1352, and 1353 are the vanes closest to the contact point P based on the direction of compression, the first vanes 1351, and then the second vanes 1352, the third vanes 1351 , Between the first vane 1351 and the second vane 1352, between the second vane 1352 and the third vane 1351, between the third vane 1351 and the first vane 1351 Spaced by the same circumferential angle.

Accordingly, 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 1351 is the second compression chamber. (V2), when the compression chamber formed by the third vane 1351 and the first vane 1351 is called the third compression chamber V3, all the compression chambers V1, V2, and V3 have the same volume at the same crank angle Will have

The vanes 1351, 1352, and 1353 are formed in a substantially rectangular parallelepiped shape. Here, the surface in contact with the inner circumferential surface 133a of the cylinder 133 among both ends of the vane is defined 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, and 1353 are formed in a curved shape to make a line contact with the inner circumferential surface 133a of the cylinder 133, and the rear surfaces of the vanes 1351, 1352, and 1353 are back pressure chambers 1334a, 1334b, 1334c) to be evenly formed so as to be evenly subjected to back pressure.

In the drawing, reference numeral 110b is an upper shell and 110c is a lower shell.

In the vane rotary compressor equipped with the hybrid cylinder as described above, power is applied to the driving motor 120, and the rotor 122 of the driving motor 120 and the rotating shaft 123 coupled to the rotor 122 are provided. When rotating, the roller 134 rotates with the rotating shaft 123.

Then, the vane (1351,1352,1353) centrifugal force generated by the rotation of the roller 134 and the back pressure of the back pressure chamber (1334a, 1334b, 1334c) provided on the rear side of the vane (1351,1352,1353) By being drawn out from each vane slot 1341a,1341b,1341c, the front surface of each vane 1351,1352,1353 comes into contact with the inner circumferential surface 133a of the cylinder 133.

Then, the compression space V of the cylinder 133 is equal to the number of the compression chambers (including the suction chamber or the discharge chamber) by the number of vanes 1351, 1352, and 1353 (including the suction chamber and the discharge chamber) (V1) ,V2,V3), and each of the compression chambers (V1, V2, V3) moves along the rotation of the roller 134 to the shape of the inner circumferential surface 133a of the cylinder 133 and the eccentricity of the roller 134. The volume is varied by, and the refrigerant filled in each of the compression chambers (V1, V2, V3) sucks, compresses, and discharges refrigerant while moving along the rollers 134 and vanes 1351, 1352, and 1353.

The details are as follows. 4 (a) to 4 (d) are cross-sectional views showing a process in which refrigerant is sucked and compressed in a cylinder according to the present embodiment. 4(a) to 4(d), the main bearing is projected and illustrated, and the sub-bearing not shown in the drawing is the same as the main bearing.

As shown in FIG. 4(a), the volume of the first compression chamber V1 is continuously increased until the first vane 1351 passes through the intake 1331 and the second vane 1352 reaches the point at which suction is completed. Thus, the refrigerant is continuously introduced from the inlet 1331 to the first compression chamber V1.

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

As shown in FIG. 4(b), when the second vane 1352 proceeds with the compression stroke past the completion point of suction (or the compression start time), the first compression chamber V1 becomes a sealed state and the roller 134 With it, it moves in the direction of the discharge port. In this process, while the volume of the first compression chamber (V1) is continuously reduced, 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 preceded by the first compression chamber (V1) Refrigerant leakage may occur while communicating with the seal (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 located in a stage before entering the main side second pocket 1313b after passing through the main side first pocket 1313a. Accordingly, the back pressure formed in the first back pressure chamber 1334a of the first vane 1351 is raised from the intermediate pressure to the discharge pressure. Accordingly, it is possible to suppress the first vane 1351 from being pushed backward while the back pressure of the first back pressure chamber 1334a increases.

As shown in FIG. 4C, when the first vane 1351 passes through the first outlet 1332a and the second vane 1352 does not reach the first outlet 1332a, the first compression chamber (V1) is in communication 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) falls to a predetermined pressure. Of course, if there is no first discharge port 1332a, the refrigerant in the first compression chamber V1 is not discharged, but 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 completely in communication with the second pocket 1313b on the main side, so that the first back pressure chamber 1334a forms almost discharge pressure. Then, while the first vane 1351 is prevented from being pushed by the back pressure of the first back pressure chamber 1334a, leakage between the compression chambers can be suppressed.

4(d), 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 through the second discharge port 1332b into the inner space of the casing 110.

At this time, the back pressure chamber 1334a of the first vane 1351 is just before entering the main side first pocket 1313a, which is the intermediate pressure region, after passing through the second side pocket 1313b, which is the discharge pressure region. Therefore, the back pressure formed in the back pressure chamber 1334a of the first vane 1351 is immediately 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 side second pocket 1313b, which is the discharge pressure region, and a back pressure corresponding to the discharge pressure is formed in the second back pressure chamber 1334b.

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

Referring to FIG. 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 main side first pocket 1313a, and is located in the second pocket 1313b. A discharge pressure Pd (actually a pressure slightly lower than the discharge pressure) is formed at the rear end of the second vane 1352 to be formed. In particular, the main side second pocket 1313b is in direct communication with the oil passage 125 through the first oil passage 126a and the first communication passage 1315, thereby communicating with the main side second pocket 1313b. It is possible to prevent the pressure of the second back pressure chamber 1334b from being raised above the discharge pressure Pd. Accordingly, an intermediate pressure Pm that is significantly lower than the discharge pressure Pd is formed in the first side pocket 1313a, thereby increasing the mechanical efficiency between the cylinder 133 and the vane 135, and the second side of the main side. The pocket 1313b2 has a pressure slightly lower than the discharge pressure Pd or the discharge pressure Pd, so that the vane is properly adhered to the cylinder to suppress leakage between the compression chambers and increase 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 this embodiment communicates with the oil passage (125) through the first oil through hole (126a), and the back pressure on the sub side 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.

2 and 3 again, the main side first pocket 1313a and the sub side first pocket 1323a are main side and sub side by the main side and sub side first bearing protrusions 1314a and 1324a. The first pockets 1313a and 1323a are closed for each bearing surface 1311a and 1321a facing each other. 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 holes 126a and 126b, and then the main The pressure is reduced while passing between the upper and lower surfaces 134a or 134b of the rollers 134 facing the side and sub-side first bearing protrusions 1314a and 1324a, thereby forming an intermediate pressure.

On the other hand, the main side second pocket 1313b and the sub side second pocket 1323b are the main side and the sub side second pockets 1313b and 1323b by the main side and sub side second bearing protrusions 1314b and 1324b. ) Are in communication 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 second and second side bearing protrusions 1314b and 1324b and flows into the respective second pockets 1313b and 1323b, a pressure slightly lower than the discharge pressure or the discharge pressure is formed.

However, the main side second pocket 1313b and the sub side second pocket 1323b according to the present embodiment have respective bearing surfaces 1311a) facing the main side and sub side second pockets 1313b and 1323b. 1321a) is not fully opened and communicated with. That is, the main side second bearing protrusion 1314b and the sub side second bearing protrusion 1324b mostly block the main side second pocket 1313b and the sub side second pocket 1323b, but some are in a communication flow path. 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, the aforementioned main side first pocket 1313a and second pocket 1313b are formed at regular intervals along the circumferential direction, and the flange portion of the sub bearing 132 ( In 1322), the aforementioned sub-side first pocket 1323a and second pocket 1323b are formed at regular intervals along the circumferential direction.

The inner circumferential sides of the main side first pocket 1313a and the second pocket 1313b are blocked by the main side first bearing protrusion 1314a and the second bearing protrusion 1314b, respectively, and the sub side first pocket 1323a 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 water bearing portion 1311 of the main bearing 131 forms a cylindrical bearing surface 1311a having an almost continuous surface, and the water bearing portion 1321 of the sub bearing 132 has a cylindrical shape having an almost continuous surface. To form the bearing surface (1321a) of. 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 communicating the main bearing surface 1311a and the main second pocket 1313b is formed in the second bearing bearing portion 1314b on the main side, and a sub is provided on the second bearing bearing portion 1324b. A second communication channel 1325 is formed to communicate the bearing surface 1321a and the sub-side second pocket 1323b.

The first communication flow path 1315 is formed at a position overlapping with the main second side bearing protrusion 1315b and at the same time overlapping with the first oil groove 1311b, and the second communication flow path 1325 is a sub-side second bearing protrusion. It overlaps with (1324b) and is formed at a position overlapping with the second oil groove (1321b).

In addition, the first communication passage 1315 and the second communication passage 1325 are formed as communication holes penetrating between the inner circumferential surface and the outer circumferential surface of the main and sub-side second bearing protrusions 1315b and 1325b as shown in FIG. 5. Alternatively, although not shown in the drawing, the cross section of the main side second bearing protrusion 1315b and the sub side second bearing protrusion 1325b may be formed as a recessed communication groove having a predetermined width and depth.

As described above, the vane rotary compressor according to the present embodiment 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 continuous bearing surfaces. To increase the mechanical efficiency of the compressor.

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

In addition, it is possible to prevent foreign matter from flowing into the second side pocket 1313b and the second side pocket 1323b of the main side and flowing between the bearing surfaces 1311a and 1321a and the rotating shaft 123 even during long-time operation. Through this, it is possible to suppress the wear of the bearings 131, 132 or the rotating shaft 123.

In addition, the vane rotary compressor according to the present embodiment is provided with a plurality of vanes 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) becomes shorter, the area of the compression chamber, that is, the area of the suction chamber becomes smaller, so that the suction flow rate of the refrigerant decreases. Then, a pressure drop is generated for each compression chamber, and the coefficient of performance of the refrigeration cycle including the compressor may decrease.

This phenomenon can be caused even larger when the inner circumferential surface of the cylinder is formed in an asymmetric shape. That is, when the inner peripheral surface of the cylinder is formed in an asymmetrical shape to increase the compression stroke, 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 is further reduced, and a pressure drop in each compression chamber is generated more.

In view of this, in the present exemplary embodiment, the suction flow rate of the refrigerant is to be expanded by extending the suction cycle by increasing the area of the suction port. However, since the intake port is defined by the height of the cylinder as described above, there is a limit in expanding the area of the intake port. In particular, when the intake port is formed of a single circle, there is a limit in expanding the size of the intake port. Accordingly, in the present embodiment, the suction port is moved as close as possible to the contact point, and at the same time, the suction port is formed in a non-spherical shape or a combination of a plurality of shapes with different inner diameters to form the end of the suction port as far as possible from the contact point. That is, the intake initiation point of the intake port is advanced as much as possible, while the inhalation completion point of the intake port is delayed as much as possible to increase the actual intake area of the intake port. For convenience, the portion 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 describe the first suction part and the second suction part 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 be formed to have a longer circumferential length D1 than an axial length D2.

The first suction part 1331a is formed through the inner circumferential surface and the outer circumferential surface of the cylinder 133 as shown in FIGS. 1 to 3 above. The first suction part 1331a may be formed in a normal direction 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, as the first suction part 1331a is formed in the normal direction, assembly of the compressor may be easy as the assembly standards are unified when assembling other parts.

Also, the first suction part 1331a may be formed in a circular cross-sectional shape when projecting 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 approximately 2 mm above and below each. The first suction part 1331a may be formed in various ways, such as a rectangle, a polygon, or an oval, in addition to a circle, and even in these cases, it is preferably formed to secure the axial sealing distance D3 described above.

Meanwhile, the second suction part 1331b may be formed in a rectangular cross-sectional shape when projecting in the radial direction. However, the second suction part 1331b is also preferably formed to secure an axial sealing distance, similarly to the first suction part 1331a. However, since the second suction part 1331b according to the present embodiment is formed smaller than the first suction part 1331a, it is usually possible to secure a larger axial sealing distance than the first suction part 1331a. The second suction part 1331b may be formed in various shapes in addition to 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 than the conventional suction port. 9 is a schematic view showing the position of the inlet according to the present embodiment compared to the conventional inlet position.

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

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

That is, when the angle between the second virtual line L2 and the third virtual line L3, which can be referred to as a suction cycle, is about 60 degrees, the suction port 1331 is a starting end based on the cylinder center Oc. The angle of incidence 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 starting end of the conventional suction port S is spaced approximately 20 degrees from the second virtual line L2' passing through the contact point P. Begins at the point where it was. In other words, the conventional inlet (S) is formed at a position spaced about 20 degrees from the contact point (P).

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

Normally, the vane rotary compressor has a circular roller, so it is advantageous for the suction port to be located far from the contact point to secure a wide suction area of the suction chamber. Therefore, in the vane rotary compressor, it is advantageous that the suction port is located as far from the contact point as possible within the range in which the compression cycle is not shortened, thereby ensuring the suction area of the suction chamber to the maximum.

To this end, the conventional vane rotary compressor is formed such that the first angle (α1') is approximately 1.5 times that of the second angle (α2') as shown in FIG. However, as described above, it is disadvantageous to increase the suction flow rate of the refrigerant since the intake opening time at which the suction port S is opened is delayed. Hereinafter, the suction flow rate of the refrigerant has the same meaning as the mass flow rate of the refrigerant, but for convenience, it is described as the suction flow rate of the refrigerant.

Accordingly, in the present embodiment, the first suction part 1331a is positioned as close as possible to the contact point P, while the second suction part 1331b is positioned as far as possible from the contact point P to form the suction cycle as long as possible. will be. Through this, the pressure drop is suppressed by increasing the suction flow rate of the refrigerant.

Meanwhile, as shown in FIGS. 6 to 8, the first suction part 1331a should secure an appropriate circumferential sealing distance D4 between the contact point P, and for this purpose, as shown in FIG. 9, the first suction part ( 1331a) is positioned about 10 degrees away from the contact point (P). The circumferential sealing distance D4 may be approximately 2 mm.

As described above, when the first suction part 1331a is formed to move close to the contact point P, the suction start point (ie, the suction start point of the first suction part 1331a moves toward the contact point P), that is, Compression start point) also moves toward the contact point (P). Then, as the first suction part 1331a moves toward the contact point P, the suction area may be reduced. Accordingly, the present exemplary embodiment may further form the second suction unit 1331b described above, thereby compensating for a reduction in suction area generated when the first suction unit 1331a moves toward the contact point P and the resulting suction loss.

Hereinafter, the second suction part will be described. 8, the second suction part 1331b according to the present embodiment is formed in communication with one side of the first suction part 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 one side of the first suction part 1331a, that is, the rotational direction of the rotating shaft 123 (or , It is formed on the rear side of the first suction unit 1331a along the circumferential direction based on the rotation 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 portion 1331a.

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

That is, in the vane rotary compressor, as described above, since the roller 134 is formed in a circular shape, the area of the suction chamber decreases as it approaches the contact point P. Therefore, when the second suction part 1331b having a smaller area than the first suction part 1331a is formed on the front side of the first suction part 1331a, the starting point of suction may be drawn even if the suction start point is pulled. The intake flow rate may not increase significantly.

Furthermore, if a part of the second suction part 1331b is covered by a vane rotating with the roller, the suction flow rate of the refrigerant may hardly increase. Therefore, as in the present embodiment, since the first suction part 1331a is formed on the front side of the second suction part 1331b, the suction area of the suction chamber is increased from the start of the suction stroke to increase the suction flow rate of the refrigerant. It can be advantageous to do.

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

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

In addition, as described above, the second suction part 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 part 1331b as wide as possible without delaying the starting point of compression. 6 and 8, the second suction part 1331b may be formed in a rectangular cross-sectional shape when projecting in the radial direction from the inner circumferential 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 compared to the same circumferential length rather than the circular or elliptical shape described later. However, it can be disadvantageous in terms of the surface pressure supporting the front surface of the vane. That is, when the second suction part 1331b is rectangular, the contact surface that the vane contacts is suddenly increased at the end of the second suction part 1331b. Then, while the surface pressure supporting the vane changes rapidly, the behavior of the vane may become unstable. Therefore, the second suction part 1331b may be preferably formed in a circular or elliptical shape, which will be described later, to gradually increase the surface pressure with respect to the vane, and may be preferable in terms of vane behavior. These will be described later together with the shape of the second suction part.

On the other hand, as described above, when the suction port 1331 is formed as the first suction unit 1331a and the second suction unit 1331b in the vane rotary compressor, the suction cycle of the refrigerant increases and the suction flow rate increases. Through this, the pressure drop in the compression chamber can be suppressed to improve the performance of the refrigeration cycle including the compressor.

That is, when the first suction part 1331a and the second suction part 1331b are arranged in a circumferential direction as in this embodiment, the suction port 1331 can be brought as close as possible to the contact point P, and suction is started. At the same time, the suction flow rate of the refrigerant can be further increased from the start of suction as the first suction portion 1331a having a larger area than the second suction portion 1331b is located at the contact point.

On the other hand, the second suction unit 1331b may be formed to extend to maintain the original suction completion point as in the conventional suction port. Then, even when the vane passes through the first suction part 1331a, the second suction part 1331b remains open, and the refrigerant continues to flow into the compression chamber through the second suction part 1331b. Then, while the suction cycle in the compression chamber is extended by the range of the second suction unit 1331b, the actual suction area of the compression chamber can be enlarged. Through this, it is possible to increase the 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 views shown to explain a process of forming a compression chamber according to the position of a vane in the vane rotary compressor according to the present embodiment.

First, FIG. 10A is a state in which the leading vane 1351 approaches the start end of the first suction part 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, the first vane 1351 has not yet passed the start end of the first suction unit 1331a, so that the first compression chamber V1 forms a suction area, but the refrigerant is not sucked into the first compression chamber V1. It is in a bad condition.

10B is a state in which the leading vane 1351 has reached the boundary point between the first suction part 1331a and the second suction part 1331b. In general, the suction port of the vane rotary compressor forms a maximum suction area (or maximum opening area) for the corresponding compression chamber when the vane reaches the circumferential end of the suction port. Therefore, in the present embodiment, when the preceding vane 1351 reaches the boundary between the first suction part 1331a and the second suction part 1351, the first compression chamber reaches the maximum suction area. In this state, the refrigerant is no longer sucked into the preceding compression chamber, but is sucked only into the trailing first compression chamber V1. However, in the present embodiment, as the second suction part 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 part 1331b. This means that the refrigerant is no longer sucked into the preceding compression chamber, and the refrigerant is sucked only into the trailing first compression chamber. Therefore, the compression is performed in the preceding compression chamber, while the refrigerant in the subsequent compression chamber V1 is continuously sucked.

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

The intake port according to the present embodiment is compared with the conventional intake port, and the graph is shown in FIG. 11. 11 is a graph showing the suction flow rate in the compression chamber and the suction area of the compression chamber compared to the prior art for explaining the effect of the operation according to the present embodiment. The refrigerant flow rate means the mass flow rate of the refrigerant that is sucked into the corresponding compression chamber.

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

Referring to FIG. 9, the first suction unit 1331a and the conventional suction port S of this embodiment are formed to have the same shape and area, but the suction port of this embodiment is rotated by approximately 10 degrees 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 this embodiment and the prior art is changed to almost the same pattern with a difference of approximately 10 degrees to a specific rotation angle.

First, until the rotation angle is approximately 10 degrees, both the present embodiment and the prior art are in a state where the suction area of the suction port is not formed for the corresponding compression chamber. This is a state in which FIG. 10A corresponds to a state before the first suction part communicates with the compression chamber.

Next, when the rotation angle becomes approximately 10 degrees, this embodiment starts to form the suction area of the suction port for the corresponding compression chamber. On the other hand, in the prior art, the suction area for the corresponding compression chamber is not yet formed. Conventionally, the rotational angle should be approximately 20 degrees, so that the suction area of the suction port to the compression chamber starts to form. However, in the present embodiment, when the rotation angle becomes approximately 20 degrees, the suction area of the suction port for the corresponding compression chamber is already enlarged. Therefore, the suction flow rate of the refrigerant is already in a state where the present embodiment has more than the conventional one.

Next, when the rotation angle is about 50 degrees, the present embodiment reaches the maximum suction area. Conventionally, it is before reaching the maximum suction area. This is the state corresponding to FIG. 10B. Thereafter, the suction angle of the refrigerant increases to the maximum while the maximum suction area is maintained until the rotation angle is about 50 to 130 degrees, and then gradually decreases. Conventionally, when the rotation angle is approximately 60 degrees, the maximum suction area is reached.

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

Next, when the rotation angle becomes approximately 180 degrees, the present embodiment starts compression for the compression chamber while the suction area for the compression chamber becomes zero. This is the state corresponding to FIG. 10D, and the suction flow rate of the refrigerant is theoretically zero. Here, the compression start angle is formed at about 180 degrees in the related art. In the case of this embodiment, the starting end of the first suction part is formed about 10 degrees ahead of the conventional one, but in the present embodiment, as the second suction part is further formed, it is possible to form the same compression start angle as in the prior art.

If the second suction part is not formed in the present embodiment, the suction completion angle of this embodiment is formed 10 degrees ahead of the compression start angle. Then, the compressor is operated in a state in which the refrigerant is not sucked to the maximum level compared to the volume of the compression chamber. Then, the refrigerant expands while the compressor is operated for approximately 10 degrees, and then starts to compress, so that the compressor efficiency may be greatly reduced. Therefore, when the suction start angle is advanced as in the present embodiment, the suction completion angle and the compression start angle must be matched to prevent the compressor from being deteriorated.

On the other hand, as described above, it is preferable to increase the area of the second suction unit 1331b in order to increase the refrigerant suction amount in the second half of the suction stroke of the present embodiment. However, since the circumferential length of the second suction part 1331b is determined together with the starting point of compression, eventually the axial direction of the second suction part 1331b is enlarged to the maximum to increase the area of the second suction part 1331b. Can.

12 to 14 are front views showing another embodiment of the intake according to the present embodiment.

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). Through this, the area of the second suction unit can be maximized. However, as described above, when the second suction part 1331b is formed in a square shape, the vane behavior may become unstable while the surface pressure to the vane changes rapidly at the point where the second suction part 1331b ends.

In consideration of this, as shown in FIG. 13, the second suction part 1331b is formed in a circular shape, and the axial height D7 may be formed to be the same as the axial height D2 of the first suction part 1331a. . In this case, the second suction part 1331b is formed at a position where a part of the first suction part 1331a overlaps, and when the part overlapped with the first suction part 1331a is connected as a virtual circle, the second suction part (1331b) has an oval shape. Then, the area of the second suction part 1331b becomes narrower toward the rear side, and conversely, the sealing distance D3 gradually increases. Accordingly, it is possible to suppress the surface pressure of the vane from rapidly changing while expanding the area of the second suction part 1331b.

However, the second suction part 1331b is formed in a circular shape as shown in FIG. 14, and 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 part 1331a. Can be formed. In this case, when the second suction part 1331b connects a portion overlapped with the first suction part 1331a as a virtual circle, the second suction part 1331b has a round shape composed of one curvature. Then, as shown in the embodiment of FIG. 13, the second suction part 1331b becomes narrower toward the rear side, and conversely, the sealing distance gradually increases. Accordingly, it is possible to suppress the sudden change in the surface pressure with respect to the vane while expanding the area of the second suction part 1331b. However, in the present embodiment, as the area of the second suction part 1331b is smaller than that of the embodiment of FIG. 13, 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 illustrated 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 part 1331b according to the present embodiments as described above is formed to decrease in cross-sectional area toward the direction away from the first suction part 1331a, the vane passes through the suction port 1331. By suppressing the fluctuation of the surface pressure fluctuation excessively, the behavior of the vane can be stabilized, and through this, leakage between the compression chambers can be suppressed to increase the compression efficiency.

Meanwhile, the second suction parts 1331b described above may have the same depth along the circumferential direction. When the depths are equally formed along the circumferential direction of the second suction part 1331b, it is possible to facilitate 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 unit 1331b forms a vortex, and suction loss may occur. Therefore, the second suction part 1331b may have different depths along the circumferential direction.

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

15 and 16, the second suction part 1331b according to the present exemplary embodiment may have an inner circumferential surface inclined along the longitudinal direction. That is, the second suction part 1331b is formed to be deeper toward the outer circumferential surface from the inner circumferential surface 133a of the cylinder 133, that is, the inner circumferential surface of the second suction part 1331b is formed as an inclined surface part 1331c having a predetermined inclination angle Can. Accordingly, the second suction part 1331b may be formed shallower as the side in contact with the first suction part 1331a is deepest and further away from the first suction part 1331a in the circumferential direction of the cylinder 133.

As described above, when the inclined surface portion 1331c is formed on the inner circumferential surface of the second suction portion 1331b, the refrigerant flowing from the first suction portion 1331a to the second suction portion 1331b is gently inclined portion 1331c. As it moves along, the refrigerant can be quickly sucked. In addition, even at the point where the suction completion angle is achieved, a step surface is not formed, so that vortex generation in the sucked refrigerant can be suppressed. Accordingly, the refrigerant flows rapidly through the second suction unit 1331b into the suction chamber forming the compression chamber, and thus the suction flow rate of the refrigerant may be increased. Then, the pressure drop for the refrigerant in the compression chamber can be suppressed to increase the compression efficiency.

Referring to FIG. 17, in the second suction part 1331b according to the present embodiment, the inner circumferential surface is formed of an inclined surface part 1331c as illustrated in FIG. 16 described above, and a cylinder 133 is provided at the end of the second suction part 1331b. ), a space portion 1331d recessed to the same depth on the inner circumferential surface may be further formed. That is, a space portion 1331d having a straight surface may be formed at an inner end of the inclined surface portion 1331c to be parallel to the first suction portion 1331a. Accordingly, the second suction part 1331b rapidly cools the refrigerant as the starting end forms the inclined surface part 1331c, and at the same time forms a space 1331d at the end, thereby expanding the volume of the suction port to cool the refrigerant. It can be inhaled more quickly.

On the other hand, when the eco-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 was developed as a refrigerant that replaces R410a. However, R32 has a smaller particle density of the refrigerant than R410a, resulting in insufficient mass flow rate. Then, the refrigerant intake amount is reduced compared to the volume of the same compression chamber. In particular, when the inner circumferential surface of the cylinder has an asymmetric shape, the suction cycle may be shortened, and the refrigerant suction amount may be further reduced. Then, the pressure drop in the compression chamber occurs, and the increase in suction loss described above and the decrease in volume efficiency resulting from the increase in the compression coefficient may be further reduced. This can occur more significantly under low temperature heating conditions, high pressure ratio conditions (Pd/Ps ≥ 6), and high speed operating conditions (80 Hz or more).

However, as in the present embodiment, the suction port is composed of the first suction unit 1331a and the second suction unit 1331b, and the second suction unit 1331b is centered around the first suction unit 1331a. As the extension is formed toward the rear side based on the rotational direction of the rotating shaft, the completion point of suction (or the start point of compression) is delayed, thereby increasing the actual suction area of the compression chamber and increasing the amount of refrigerant sucked into the compression chamber. . Then, even when a refrigerant having a low particle density such as R32 is applied to the vane rotary compressor, it is possible to maintain a discharge pressure similar to that when applying a refrigerant such as R410a. Accordingly, instead of a refrigerant having a high global warming index such as R410, it is possible to utilize R32 having a low global warming index as an alternative refrigerant.

Claims (14)

A cylinder equipped with an intake 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 the radial direction by the main bearing and the sub bearing;
A roller which is eccentrically accommodated in the compression space to form a contact point with the inner circumferential surface of the cylinder and rotates with the rotating shaft, and a plurality of vane slots formed along the circumferential direction; And
It includes; a plurality of vanes that slide into the vane slots of the rollers and protrude in the direction toward the inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers.
The inlet,
A first suction part formed through the inner peripheral surface and the outer peripheral surface of the cylinder; And
It is formed in a groove shape having a predetermined depth on the inner circumferential surface of the cylinder, communicates with the first suction portion on the opposite side of the contact point based on the first suction portion, and extends in the rotational direction of the rotation axis on the inner circumferential surface of the cylinder The second suction unit; vane rotary compressor comprising a. According to claim 1,
A line passing through the longitudinal center of the first suction part, a first virtual line, a line passing through the center of the outer diameter of the cylinder and the contact point, a second virtual line, a line passing through the center of the outer diameter of the cylinder and the end of the second suction part Speaking of 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 so that the second angle between the first virtual line and the third virtual line ranges from 0.8 to 1.2 times. According to claim 2,
A vane rotary compressor, wherein the first angle and the second angle are the same. According to claim 1,
The second suction part
The vane rotary compressor, characterized in that the area of the first suction portion is formed larger than the area of the second suction portion. According to claim 4,
The vane rotary compressor, characterized in that the second suction part has the same cross-sectional area in the rotational direction of the rotating shaft. According to claim 4,
The vane rotary compressor, characterized in that the cross-sectional area of the second suction part is gradually reduced in the rotational direction of the rotating shaft. According to claim 4,
The axial height of the second suction portion is smaller than the axial height of the first suction portion vane rotary compressor. According to claim 4,
Vane rotary compressor, characterized in that the axial height of the second suction portion is formed equal to the axial height of the first suction portion. According to claim 1,
The second suction portion vane rotary compressor, characterized in that formed to have the same depth along the circumferential direction of the cylinder. According to claim 1,
The second suction unit is vane rotary compressor characterized in that it is formed to be inclined to become deeper as it approaches the first suction unit. The method of claim 10,
The second suction unit is a vane rotary compressor, characterized in that a space portion having a straight surface parallel to the first suction unit is formed to a predetermined depth from the inner circumferential surface of the cylinder. The method according to any one of claims 1 to 11,
The suction port is a vane rotary compressor, characterized in that the circumferential length is formed larger than the axial length. The method of claim 12,
A back pressure pocket communicating with the rear side of the vane slot is formed on at least one bearing among the plurality of bearings, and the back pressure pocket is separated along a circumferential direction and formed of a plurality of pockets having different internal pressures,
The plurality of pockets,
A vane rotary compressor, characterized in that bearing protrusions provided on an inner circumferential side facing the outer circumferential surface of the rotating shaft and forming a radial bearing surface with respect to the outer circumferential surface of the rotating shaft are respectively formed. The method of claim 13,
The plurality of pockets,
A first pocket having a first pressure; And
It is made of; a second pocket having a pressure higher than the first pressure,
A vane rotary compressor, characterized in that a communication flow path is formed in the bearing protrusion of the second pocket so as to communicate an inner circumferential surface opposite to the inner circumferential surface of the bearing protrusion facing the outer circumferential surface of the rotating shaft.

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