KR102442465B1 - Rotary compressor - Google Patents

Abstract

The rotary compressor according to the present invention is recessed in at least one side of a side surface of a vane or a cylinder corresponding thereto to have a predetermined volume, and a lateral pressure space forming a discharge pressure is formed, thereby reducing the lateral reaction force applied to the vane to reduce the vane It is possible to reduce the mechanical friction loss between the cylinder and the cylinder. In addition, by increasing the back pressure applied to the vanes through this, the refrigerant leakage that may occur when the vanes and the rollers are separated is suppressed, thereby improving the compressor efficiency. In addition, this configuration can be applied to a conventional rotary compressor to which a circular roller is applied to improve compressor efficiency.

Description

Rotary Compressor

The present invention relates to a compressor, and more particularly, to a rotary compressor in which a suction chamber and a compression chamber are separated by a vane in contact with a rotating roller.

In general, a compressor may be divided into a rotary type and a reciprocating type according to a method of compressing a refrigerant. In the rotary compressor, the volume of the compression space is varied while the piston rotates or revolves in the cylinder, and in the reciprocating compressor, the volume of the compression space is varied while the piston reciprocates in the cylinder. As a rotary compressor, a rotary compressor which compresses a refrigerant while a piston rotates using the rotational force of an electric part is known.

In the case of rotary compressors, the development of technologies related to high efficiency and miniaturization is continuously emphasized. In addition, in the case of miniaturization, technology has been developed to satisfy more cooling capacity by increasing the variable range of the compressor operating speed.

The rotary compressor as described above can be divided into a single rotary compressor and a double rotary compressor according to the number of cylinders. The double rotary compressor may be divided into a method of forming a plurality of compression spaces by stacking a plurality of cylinders, and a method of forming a plurality of compression spaces in one cylinder.

In the former case, a plurality of rollers are provided with a height difference on the rotating shaft, and the plurality of rollers rotate eccentrically in the compression space of each cylinder while alternately suctioning, compressing, and discharging the refrigerant in each compression space. Therefore, in the former case, as the plurality of cylinders are installed in the axial direction, the size of the compressor increases as much as possible, and the material cost increases.

On the other hand, in the latter case, one roller 2 having an elliptical shape is provided on the rotation shaft 1 as shown in FIG. 1 , and the one roller 2 is one with two vanes 3A and 3B. A plurality of compression spaces V1 and V2 are formed in the cylinder 4 and the refrigerant is simultaneously sucked, compressed and discharged from both compression spaces V1 and V2 while performing concentric rotational motion. Therefore, in the latter case, since the refrigerant is sucked, compressed, and discharged in the same phase in the two compression spaces V1 and V2, the sliding area of the mechanism is reduced while compressing a large volume during one rotation, and compactness is possible, and It has the advantage of being able to increase the speed due to the reduction of the journal negative reaction force as the gas force is offset.

However, in the conventional rotary compressor as described above, the vane 2 protrudes from the vane slots 4A and 4B to partition between the suction chambers V11 and V21 and the compression chambers V12 and V22, The vanes 3A and 3B are subjected to a lateral gas force F _side according to the pressure difference between the suction chamber and the compression chamber. Accordingly, as shown in FIG. 2, on both sides of the vane 3A in contact with the vane slot 4A, the first side surface 3a in contact with the inner peripheral side open end of the vane slot 4A and the second side surface contacting the outer peripheral side open end ( Reaction forces R1 and R2 in opposite directions are generated in 3b), respectively, and at the same time, the above-described lateral gas force F _side is further applied to the second side 3b protruding into the compression space V1. Therefore, the reaction forces R1 and R2 applied to both sides of the vane greatly increased, so that the vane 3A and the vane slot 4A were excessively closely contacted and the mechanical friction loss between the vane and the cylinder increased. There was a problem. .

In addition, in the conventional rotary compressor, as the vanes 3A and 3B receive a larger lateral gas force F _side in the suction chamber direction by the relatively high pressure of the compression chamber, between the roller and the vane There was also a problem in that a gap was generated and the contact force between the roller and the vane was excessively reduced and the refrigerant leaked. In this case, in the case of the elliptical roller 2, the area of the vanes exposed to the compression chamber increases as the maximum protrusion amount of the vanes 3A and 3B increases. _side ) is further increased, and there is also a problem that the refrigerant leakage may be aggravated.

An object of the present invention is to provide a compressor capable of reducing the mechanical friction loss between the vane and the cylinder by reducing the reaction force applied to the vane.

Another object of the present invention is to provide a compressor capable of suppressing leakage of refrigerant between the roller and the vane while improving the contact force between the roller and the vane by increasing the back pressure on the vane.

In order to achieve the object of the present invention, by forming a space in which the discharge pressure is filled between the cylinder and the vane, it is to provide a compressor capable of canceling the gas force received by the vane from the compression chamber.

In addition, in order to achieve the object of the present invention, by increasing the force received by the vane in the opposite direction of the roller by making the contact surface of the vane in contact with the roller widely formed on the side of the compression chamber, the contact force between the vane and the roller is reduced by reducing the contact force between the cylinder and the vane. It is intended to provide a compressor capable of reducing friction loss.

In addition, in order to achieve the object of the present invention, the casing; a driving motor provided in the inner space of the casing; a rotating shaft that transmits the rotational force of the driving motor; a cylinder installed on one side of the driving motor; a roller provided on the rotating shaft to rotate, at least two portions of an outer circumferential surface contacting the inner circumferential surface of the cylinder so that at least two compression spaces are formed in the cylinder; and at least two or more vanes that are in contact with the outer circumferential surface of the roller and partition the two or more compression spaces into a suction chamber and a compression chamber, respectively, wherein the side surface of the vane or a cylinder corresponding thereto has a predetermined volume and forms a discharge pressure A compressor may be provided, characterized in that the space portion is formed.

Here, the side pressure space portion may be formed on a surface corresponding to the suction chamber side with respect to the vane.

And, the side pressure space portion may communicate with the inner space of the casing.

In addition, in a state in which the vane is maximally protruded into the compression space, the outer peripheral end of the side pressure space may communicate with the inner space of the casing.

And, the side pressure space portion may be formed on the side of the vane.

And, the side pressure space portion may be formed in the middle of the side of the vane.

In addition, the side pressure space portion may be formed to be stepped by a predetermined length from the opposite end of the roller toward the roller.

In addition, the lateral pressure space may be formed in the middle of the vane in the height direction, and a bearing surface in contact with the cylinder may be formed on at least one of both upper and lower sides of the lateral pressure space.

And, a vane slot is formed in the cylinder to insert the vane, and the side pressure space portion is formed such that at least a portion overlaps the vane slot, and the length of the portion overlapping the vane slot in the side pressure space portion is the length of the vane. It may be increased or decreased in proportion to the length protruding into the compression space.

In addition, a length of a portion of the side pressure space portion overlapping with the vane slot may be formed to be the same as a length at which the vane protrudes into the compression space.

In addition, the side pressure space portion may be formed in a cylinder corresponding to the side surface of the vane.

And, a vane slot into which the vane is inserted is formed in the cylinder, and the vane slot has an inner peripheral side opening surface and an outer peripheral side opening surface, and the lateral pressure space is formed in the direction from the outer peripheral side opening surface to the inner peripheral side opening surface. It may be formed on the inner wall surface of the vane slot.

In addition, in order to achieve the object of the present invention, the casing; a driving motor provided in the inner space of the casing; a rotating shaft that transmits the rotational force of the driving motor; a cylinder installed on one side of the driving motor; a roller provided on the rotating shaft to rotate; and a vane movably provided in the cylinder, in contact with the outer circumferential surface of the roller, and partitioning a compression space formed by the cylinder and the roller into a suction chamber and a compression chamber; There may be provided a compressor in which a lateral pressure space having a predetermined volume and forming a discharge pressure is formed.

Here, the side pressure space portion may be formed on a side surface corresponding to the suction chamber with respect to the vane.

In addition, in order to achieve the object of the present invention, a driving motor; a rotating shaft that transmits the rotational force of the driving motor; a cylinder installed on one side of the driving motor; a roller integrally provided with the rotating shaft to rotate; and a vane movably provided in the cylinder, in contact with the outer circumferential surface of the roller, and partitioning a compression space formed by the cylinder and the roller into a suction chamber and a compression chamber; There may be provided a compressor in which a lateral pressure space having a predetermined volume and forming a discharge pressure is formed.

Here, the side pressure space portion may be formed on a side surface corresponding to the suction chamber with respect to the vane.

The rotary compressor according to the present invention can reduce the mechanical friction loss between the vanes and the cylinder by reducing the lateral reaction force applied to the vanes by forming a lateral pressure space portion having a discharge pressure between the vanes and the corresponding vane slots.

In addition, by increasing the back pressure applied to the vanes through this, the refrigerant leakage that may occur when the vanes and the rollers are separated is suppressed, thereby improving the compressor efficiency.

1 is a cross-sectional view showing an example of a conventional elliptical rotary compressor;
2 is a cross-sectional view showing the relationship between the forces acting on the vanes in the rotary compressor according to FIG. 1;
3 is a longitudinal cross-sectional view showing an elliptical rotary compressor according to the present invention;
4 is an exploded perspective view of the compression unit in the compressor according to FIG. 3;
5 is a transverse view showing a compression part in the compressor according to FIG. 3;
6 and 7 are an exploded perspective view and a combined cross-sectional view of an example of a side pressure space in the compressor according to FIG. 3;
8 is a schematic diagram showing the relationship between the forces acting on the vanes in the compressor according to FIG. 5;
9 is a cross-sectional view showing the relationship between the force acting on the vane according to the rotation angle of the roller in the compression unit according to FIG. 5;
10 is a graph showing changes in the reaction force applied to the front side and the rear side of the vane, respectively;
11 is a perspective view showing another embodiment of the lateral pressure space in the compressor according to FIG. 5;
12 is a cross-sectional view showing a compression part having a side pressure space part according to FIG. 10;
13 and 14 are cross-sectional views showing another embodiment of the lateral pressure space in the compressor according to FIG. 5;
15 is a plan view showing an embodiment of a shape of a vane when a circular roller is integrally formed with a rotating shaft in a rotary compressor according to the present invention;

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

3 is a longitudinal cross-sectional view showing an elliptical rotary compressor according to the present invention, FIG. 4 is an exploded perspective view of the compression unit in the compressor according to FIG. 3 , and FIG. 5 is a lateral view showing the compression unit in the compressor according to FIG. 3 .

As shown in this figure, in the rotary compressor according to the present embodiment, the electric part 20 is installed inside the casing 10 , and the lower side of the electric part 20 is mechanically connected by a rotating shaft 30 . The unit 100 may be installed.

The casing 10 may include a cylindrical shell 11 , an upper shell 12 covering an upper portion of the cylindrical shell 11 , and a lower shell 13 covering a lower portion of the cylindrical shell 11 .

On the side surface of the cylindrical shell 11, a first refrigerant suction pipe SP1 communicating with a first compression space S11 to be described later of the compression unit 100 and a second refrigerant suction pipe SP2 communicating with a second compression space S12 ) can be through-coupled. The first refrigerant suction pipe SP1 and the second refrigerant suction pipe SP2 may be coupled to both sides at a distance of 180° in the circumferential direction.

A refrigerant discharge pipe DP communicating with the inside of the casing 10 may be coupled through the upper portion of the upper shell 12 . The refrigerant discharge pipe DP corresponds to a passage through which the compressed refrigerant discharged from the compression unit 4 into the inner space of the casing 10 is discharged to the outside of the casing 10, and separates oil mixed in the discharged refrigerant. An oil separator (not shown) may be installed outside the casing 10 by being connected to the inside of the casing 10 or the refrigerant discharge pipe DP.

The electric part 20 may include a stator 21 press-fitted to the inner circumferential surface of the casing 10 and fixed, and a rotor 22 rotatably inserted and installed inside the stator 21 .

One end of the rotating shaft 30 is press-fitted to the rotor 22 and coupled, and the other end of the rotating shaft 30 may be supported by a main bearing 110 and a sub bearing 120 to be described later.

The rotary shaft 30 has an oil flow path 31 for guiding the oil to the sliding part in the axial direction, and the lower shell 13 side end of the rotary shaft 30 sucks the oil stored in the lower shell 13 . The oil feeder 32 may be coupled.

The compression unit 100 is installed between the main bearing 110 and the sub-bearing 120 for supporting the rotating shaft 30, and the main bearing 110 and the sub-bearing 120 to form a compression space. The cylinder 130. , a roller 140 formed on the rotation shaft 30 and rotating in the compression space V of the cylinder 130, a vane 150 that is in contact with the outer peripheral surface of the roller 140 and is movably coupled to the cylinder 130 ) may be included. The roller 140 is in contact with the inner circumferential surface 130a of the cylinder 130 in at least two places to partition the compression space V of the cylinder 130 into at least two or more, and the vane 150 is provided with at least two or more. Thus, two or more compression spaces can be divided into a suction chamber and a compression chamber, respectively. Hereinafter, a compression unit having two compression spaces will be described as a representative example.

The main bearing 110 is formed in a disk shape, and a side wall portion 111 may be formed at an edge thereof to be shrink-fitted or welded to the inner circumferential surface of the casing 10 . In the center of the main bearing 110 , the main bearing part 112 is formed to protrude upward, and the shaft bearing hole 113 may be formed through the main bearing part 112 so that the rotation shaft 30 is inserted and supported.

One side of the main bearing unit 112 communicates with a first compression space (V1) and a second compression space (V2) to be described later, and the refrigerant compressed in the respective compression spaces (V1) and (V2) of the casing (10). A first discharge port 114a and a second discharge port 114b for discharging to the inner space 11 may be formed.

The first discharge port 114a and the second discharge port 114b may be formed with an interval of 180° in the circumferential direction. However, the first outlet and the second outlet may be formed on the sub-bearing 120 in some cases.

The sub-bearing 120 is formed in a disk shape and may be bolted to the main bearing 110 together with the cylinder 130 . Of course, when the cylinder 130 is fixed to the casing 10 , it may be bolted to the cylinder 130 together with the main bearing 110 , and when the sub-bearing 120 is fixed to the casing 10 , The cylinder 130 and the main bearing 110 may be bolted to the sub bearing 120 .

And in the center of the sub bearing 120, the sub bearing 122 is formed to protrude downward, and the sub bearing 122 is penetrated on the same axis as the bearing hole 113 of the main bearing 110 to the rotation shaft 30 ) may be formed with a shaft hole 123 for supporting the lower end.

The cylinder 130 may be formed in an annular shape having an inner circumferential surface 130a of a perfect circle shape. And on both sides of the inner circumferential surface of the cylinder 130, a first vane slot 131 and a second vane slot 135 into which a first vane 151 and a second vane 152 to be described later are respectively inserted movably in the radial direction are provided. can be formed.

The first vane slot 131 and the second vane slot 135 may be formed in the radial direction, but in some cases, the inner circumferential opening surface is positioned on the discharge side with respect to an imaginary line passing through the center of rotation of the roller 140 . It may be formed to be inclined. In addition, the first vane slot 131 and the second vane slot 135 may be formed with an interval of 180° in the circumferential direction.

A first suction port 132 and a second suction port 136 may be formed at one side of the first vane slot 131 and the second vane slot 135 in the circumferential direction.

The first suction port 132 and the second suction port 136 may be formed with an interval of 180° in the circumferential direction. The first suction port 132 and the second suction port 136 may be formed in the cylinder 130, but may also be formed in the sub-bearing or the main bearing in some cases.

On the other side in the circumferential direction of the first vane slot 131 and the second vane slot 135, a first discharge guide groove 133 and a first discharge guide groove 133 to correspond to the first discharge port 114a and the second discharge port 114b of the main bearing, respectively. 2 A discharge guide groove 137 may be formed.

The first discharge guide groove 133 and the second discharge guide groove 137 may be formed with an interval of 180° in the circumferential direction. Here, the first discharge guide groove 133 and the second discharge guide groove 137 may not be formed in some cases.

The roller 140 may be integrally formed with the rotating shaft 30 , or may be post-assembled and coupled to the rotating shaft 30 . The roller 140 may be formed in an elliptical shape in which the outer peripheral surface of the roller is in contact with the inner peripheral surface 130a forming the compression space V of the cylinder 130 at two places.

The roller 140 may be formed in a three-dimensional shape in which a plane formed in an ellipse is projected in a direction perpendicular to the plane. In this case, the long axis length of the roller 140 may be formed to have substantially the same length as the inner diameter of the cylinder 130 , and the minor axis length of the roller 140 may be formed shorter than the inner diameter of the cylinder 130 . Accordingly, the roller 140 has an upper surface 141 in contact with the lower surface of the main bearing 110 , a lower surface 142 of the roller in contact with the upper surface of the sub bearing 120 , and an ellipse among the outer peripheral surfaces 143 of the roller 140 . Both vertices in the long axis direction of the cylinder 130 may be rotated concentrically with the compression space V and the rotation shaft 30 of the cylinder in a state in which they are in contact with the inner circumferential surface 130a of the cylinder 130 . At this time, a portion of the outer circumferential surface 143 of the roller 140 excluding both vertices in the long axis direction of the ellipse may be spaced apart from the inner circumferential surface 130a of the cylinder 130 .

Meanwhile, the vane 150 may include a first vane 151 and a second vane 152 . Since the first vane 151 and the second vane 152 are formed to have the same shape and are disposed at intervals of 180° along the circumferential direction, hereinafter, the first vane will be viewed as a center.

The first vane 151 is a first vane body 155 that is slidably inserted into the first vane slot 131, and a first vane body 155 convexly protruded to the front end (roller direction end) of the first vane body 155. It may be made of one vane protrusion 156 .

The first vane body 155 may be formed in a substantially rectangular shape having a predetermined length, width, and height.

The length of the first vane 451 is the first vane 451 while the first vane body is not separated from the first vane slot 131 when the first vane 451 is moved in contact with the outer circumferential surface of the roller 44, the first vane It may be formed to a length that can be sufficiently supported by the first vane slot 131 when it protrudes from the slot 131 to the maximum. Still, the length of the first vane may be preferably formed to a length that the first vane body can keep to a minimum the friction loss generated between the first vane slots 131 . Here, the length of the first vane is a distance extended in the moving direction of the first vane 151 , and is the sum of the first vane body 155 and the first vane protrusion 156 .

The width of the first vane 151 may be appropriately adjusted in consideration of the strength of the vane, the volume of the compression space, and the like. That is, if the width of the first vane 151 is too large, the dead volume generated on both sides of the contact point between the vane and the roller increases, and if the width of the vane is too small, the compression chamber pressure cannot be sufficiently supported and reliability may decrease have. Here, the width of the first vane 151 is a distance in a direction perpendicular to the longitudinal direction of the first vane on a plane perpendicular to the axial direction of the rotation shaft 30 in the first vane body.

The height of the first vane 151 may be formed so that both compression spaces V1 and V2 partitioned by the first vane 151 do not communicate with each other. That is, the height of the first vane 151 may be formed so that the first vane 151 can contact the main bearing 110 and the sub-bearing 120 . Here, the height of the first vane 151 is a distance in a direction perpendicular to both the length and width of the vane body or the vane protrusion.

The first vane protrusion 156 may be formed in various ways. For example, the radius of curvature of the first vane protrusion 156 may be equal to half the thickness between both sides of the first vane body 155 . Accordingly, the first vane protrusion 156 may be formed in a semicircular cross-section perpendicular to the rotation shaft 30 . Accordingly, the first vane protrusion 156 is connected to both sides of the first vane 151 so as not to be angled, respectively, so that the first vane protrusion 156 has a common tangent to both sides of the first vane 151, respectively. can be formed to meet.

In addition, the first vane protrusion 156 may have a radius of curvature greater than half the thickness between both sides of the first vane 151 . In this case, the contact portion of the first vane protrusion 156 is dispersed, so that wear of the first vane protrusion 156 can be suppressed.

In addition, the first vane protrusion 156 may have a central point (ie, the center of the radius of curvature) P formed on the longitudinal center line CL of the first vane body 155 . Accordingly, when the roller 140 is positioned at a rotation angle of 90°, the center point P of the first vane protrusion may be in contact with the outer circumferential surface of the roller 140 .

Meanwhile, since the second vane 152 is formed in the same manner as the first vane 151 , a detailed description thereof will be omitted.

In the drawings, reference numeral 130b denotes a through hole of a cylinder through which the inner space of the casing and the vane slot communicate, V11 and V12 denote a first suction chamber and a first compression chamber forming a first compression space, and V21 and V22 denote a second A second suction chamber and a second compression chamber forming a compression space.

In the rotary compressor according to this embodiment as described above, power is applied to the transmission unit 20 so that the rotor 22 of the transmission unit 20 and the rotating shaft 23 coupled to the rotor 22 rotate When , the roller 140 rotates together with the rotation shaft 30 to inject refrigerant into the first suction chamber V11 of the first compression space V1 of the cylinder 130 and the second compression space V2 of the second compression space V2. It is simultaneously sucked into the suction chamber (V21).

This refrigerant is compressed by the roller 140, the first vane 151, and the second vane 152 in the first compression chamber V12 and the second compression space V2 of the first compression space V1. A series of compressed refrigerants simultaneously discharged into the inner space of the casing 10 through the first discharge port 114a and the second discharge port 114b provided in the main bearing 110 are simultaneously compressed in the chamber V22. will repeat the process.

As such, as the refrigerant is simultaneously sucked into the first compression space V1 and the second compression space V2 and compressed in the two compression spaces V1 and V2, the gas force transferred to the center of the rotation shaft 30 is Compressor vibration can be remarkably reduced as they cancel each other and the reaction force in the radial direction becomes almost zero.

However, when the roller has an elliptical shape and two vanes respectively contact the outer peripheral surface of the roller as in this embodiment, the roller and the vane meet at two contact points. As a result, not only the mechanical friction loss between the roller and the vane increases compared to the conventional roller, which is circular, but also the roller does not rotate, so that the linear speed between the vane and the roller increases, further increasing the mechanical friction loss. . In addition, when the contact force between the roller and the vane increases, the friction loss between the vane and the vane slot into which the vane is inserted also increases, thereby further reducing the efficiency of the compressor.

In particular, as the roller is formed in an elliptical shape, the maximum protrusion of the vane is also increased compared to the case of the conventional circular roller, and the lateral gas force (F _side ) received by the vane from the compression chamber also increases, thereby increasing the cylinder and the vane. As the reaction force between them increases, the mechanical friction loss between the cylinder and the vane further increases, and the compressor efficiency may be further reduced.

Therefore, in this embodiment, by forming a lateral pressure space portion to generate a counter force (F _gas ) of the discharge pressure between the vane slot and the suction side of the vane, the lateral gas force (F _side ) is offset by the reaction force received by both sides of the vane can reduce Through this, it is possible to suppress excessive close contact between the cylinder and the vane, thereby reducing the friction loss between the cylinder and the vane.

Here, since the lateral pressure space portion is formed to act on both the first vane and the second vane, the lateral pressure space portion formed in the first vane will be described as a representative example. Accordingly, when the word 'vane' refers to the first vane, it may actually include both the first vane and the second vane.

6 and 7 are an exploded perspective view and a combined cross-sectional view of an example of a side pressure space in the compressor according to FIG. is a cross-sectional view showing the relationship between the force acting on the vane according to the rotation angle of the roller in the compression unit according to FIG. 5 .

6 to 8 , the side pressure space S according to the present embodiment may be formed on the first side surface 151a corresponding to the suction chamber among both sides of the first vane 151 .

In addition, the side pressure space (S) may be formed to have a predetermined area and depth in the center of the first side surface (151a) of the first vane (151). However, the side pressure space portion (S) of the roller to such an extent that it can communicate with the inner space of the casing 10 even when the first vane 151 is maximally protruded, that is, when the rotation angle of the roller 140 is 90. It is preferable to be formed so as to have a length on the opposite side (rear end). Accordingly, at the time when the vane receives the greatest lateral gas force (F _side ) from the compression chamber, the inside of the lateral pressure space can be communicated with the inner space of the casing, which is a high-pressure region, so that the lateral gas force (F _side ) in the opposite direction counter force (F _gas ) can be formed.

In addition, the side pressure space portion (S) has a length such that the front end of the roller side does not communicate with the suction chamber (V11), in particular, the front end of the roller side is the maximum protrusion point of the first vane (the rotation angle of the roller is 90 ° is preferably formed so as not to be exposed to the suction chamber (V11) at the time). Accordingly, when the vane receives the largest gas force from the compression chamber, the inside of the lateral pressure space is prevented from communicating with the suction chamber, which is a low pressure region, thereby forming a counter force (F _gas ) in the opposite direction to the lateral gas force (F _side ). can do.

Here, the side pressure space (S) may be formed to be variable in proportion to the protrusion length (L1) of the first vane (151). That is, the range that substantially forms the counter force F _gas in the side pressure space portion S is the area covered by the vane slot 131 (hatched portions in FIGS. 8 and 9, hereinafter side pressure area) (S1) to be. This side pressure region (S1) corresponds to a region generating a substantial counter force (F _gas ). Accordingly, the length L2 of the hatched counter force region S1 may be increased or decreased in proportion to the protrusion length L1 at which the vane 151 is exposed to the compression chamber V22 when the vane moves. For example, the length (L2) of the substantial counter force region may be preferably formed to be the same as the protrusion length (L1) of the vane.

In addition, the side pressure space (S) may be formed in the middle of the height direction of the vane. Accordingly, the bearing surface 151c in contact with the inner wall surface of the vane slot 131 may be formed on at least one of the upper and lower sides of the side pressure space S.

The operational effects of the rotary compressor according to the present embodiment as described above are as follows.

That is, as shown in (a) of FIG. 9 , when the point in time when the long-axis direction end of the roller 140 contacts the center point of the first vane 151 is 0°, the rotation angle of the roller 140 is 0° The front end of the first vane 151 is inserted into the first vane slot 131 while in contact with the outer peripheral surface of the roller 140 . At this time, most of the side pressure space portion (S) is in a state exposed to the through hole (130b) of the cylinder.

Then, as shown in FIG. 9 (b), when the roller 140 starts to rotate counterclockwise, the first vane 151 is in contact with the outer circumferential surface of the roller 140 from the first vane slot 131. begins to protrude. At this time, a portion of the front side of the side pressure space portion (S) is inserted into the first vane slot 131, but the rear side is still exposed to the through hole 130b of the cylinder. Therefore, even if the front side second side surface 151b of the first vane is exposed to the compression space V22 and receives the lateral gas force F _side , the counter force F of the lateral pressure space portion (more precisely, the counter force region S1) _gas ) can be offset by In addition, the first reaction force R1 applied to the first side surface 151a of the first vane at the inner peripheral side opening surface of the vane slot 131 and the second side surface of the first vane at the outer peripheral side opening surface of the vane slot 131 Since the second reaction force R2 applied to (151b) is canceled, eventually the forces applied to the first side and the second side of the first vane cancel or attenuate each other, so that the mechanical friction loss between the cylinder and the vane is greatly reduced.

And, as shown in (c) of Figure 9, while the roller 140 rotates up to 90 °, the first vane 151 continuously protrudes so that the rotation angle of the roller 140 protrudes from 90 ° to the maximum. , As shown in (d) and (a) of Figure 9, while the roller 140 is rotated again up to 180 °, the first vane 151 is completely inserted into the first vane slot 131 as the amount of protrusion decreases. Even at this time, the counter force F _gas generated in the lateral pressure space portion ((more precisely, the counter force region S1 )) cancels the opposite gas force F _side , thereby greatly improving the friction loss between the cylinder and the vane.

10 shows the change of the reaction force applied to the front side and the rear side of the vane, respectively. As shown in this figure, the first reaction force ( It can be seen that both R1) and the second reaction force R2 are greatly reduced. This can be interpreted as the counter force (F _gas) formed by the lateral pressure space (S) significantly offset the lateral gas force (F _side ).

On the other hand, another embodiment of the lateral pressure space in the rotary compressor according to the present invention is as follows. That is, in the above-described embodiment, the side pressure space portion is formed in a groove shape in the center of the side surface of the vane, but in this embodiment, the side pressure space portion is formed at the rear end of the side surface of the vane.

11 is a perspective view showing another embodiment of the lateral pressure space in the compressor according to FIG. 5 , and FIG. 12 is a cross-sectional view showing the compression unit having the lateral pressure space according to FIG. 11 . Referring to this, the side pressure space according to the present embodiment may be formed to be recessed by a predetermined length in the direction of the front end starting from the rear end of the first side surface 151a of the first vane 151 .

Even in this case, the bearing surfaces 151c may be respectively formed on both upper and lower sides of the side pressure space S. And, the length L2 of the side pressure space S is formed to such a degree that the counter force area S1, which is a substantial area of the side pressure space portion, can be proportional to the protrusion length L1 of the vane, as in the above-described embodiment. may be desirable.

Since the basic configuration of the side pressure space according to the present embodiment as described above and the effect thereof are substantially the same as those of the above-described embodiment, a detailed description thereof will be omitted.

On the other hand, another embodiment of the lateral pressure space in the rotary compressor according to the present invention is as follows. That is, in the above-described embodiment, the side pressure space portion is formed on the side surface of the vane, but in this embodiment, the side pressure space portion is formed on the side surface of the vane slot.

13 and 14 are cross-sectional views showing another embodiment of the lateral pressure space in the compressor according to FIG. 5 . Referring to this, the side pressure space portion S may be engraved to have a predetermined length and depth in the middle of the side wall surface of the vane slot 131 . In addition, the gas passage 130e may be formed in a hole shape to communicate between the through hole 130b of the cylinder 130 and the side pressure space S so as to supply a high-pressure discharge pressure to the side pressure space S. have.

Even in this case, bearing surfaces (unsigned) may be formed on both upper and lower sides of the lateral pressure space S. However, in this case, since the length L3 of the side pressure space is fixed, the length L3 of the side pressure space may be preferably formed to correspond to the maximum protrusion length L1 of the vane. This is because the largest lateral gas force (F _side ) is received from the compression chamber (V22) when the vane 151 is maximally protruded. In order to properly offset this, the lateral pressure space part corresponds to the maximum protrusion length (L1) of the vane. It may be desirable for (S) to be formed.

Here, as shown in FIG. 14 , the side pressure space portion S may be engraved by a predetermined length from the through hole 130b of the cylinder toward the inner peripheral opening surface. However, in this case, it is easy in terms of processing of the side pressure space (S), but there may be a limitation in the length of the side pressure space (S). That is, if the length of the side pressure space portion is too long, the front end of the vane must be formed in consideration of being caught in the side pressure space portion, so that the degree of freedom in design can be relatively lowered that much compared to the embodiment of FIG. 13 .

On the other hand, although not shown in the drawings, all of the above-described embodiments may be equally applied to a conventional rotary compressor in which the roller has a circular shape. Since the basic configuration and effect thereof are substantially the same as those of the above-described embodiments, a detailed description thereof will be omitted.

However, when the roller is integrally formed with the rotating shaft while the circular roller is applied to eliminate the rotational motion of the roller, mechanical friction loss compared to the case where the roller rotates about the outer circumferential surface of the rotary shaft (to be precise, the outer circumferential surface of the eccentric) can be improved by about 30%.

That is, when the roller is inserted into the eccentric part of the rotating shaft and the roller rotates, friction loss occurs between the roller and the eccentric part of the rotating shaft, thereby reducing compressor efficiency. When integrally formed, the friction loss between the roller and the rotating shaft is removed, thereby improving the friction loss of the entire compressor and improving the compressor efficiency.

However, when the circular roller is coupled to the rotating shaft under the same conditions as the diameter and height of the cylinder, the contact force between the roller and the vane increases and the reaction force may also increase. Therefore, when the counter force corresponding to the lateral gas force is increased, the frictional loss between the cylinder and the vane can be reduced by reducing the reaction force generated on the inner peripheral side opening surface and the outer peripheral side opening surface of the vane slot.

For example, as shown in FIG. 15, a circular roller is integrally formed with the rotation shaft, and a side pressure space portion may be formed on the side of the vane in contact with the outer circumferential surface of the roller or the inner wall surface of the suction side of the vane slot in contact with the side of the vane. have.

In addition, the lateral pressure space may communicate with the through hole of the cylinder for forming a high-pressure discharge pressure, and the lateral pressure space may always form a discharge pressure.

Accordingly, as described above, as a counter force is formed on the side surface of the vane corresponding to the force caused by the compression chamber pressure, the reaction force formed between the vane and the vane slot is reduced, so that the mechanical friction loss between the entire cylinder and the vane is reduced. and, through this, compressor efficiency may be improved.

Claims (16)

casing;
a driving motor provided in the inner space of the casing;
a rotating shaft that transmits the rotational force of the driving motor;
It is installed on one side of the driving motor, a compression space is formed in the center, and a through hole penetrating in the axial direction is formed outside the compression space to communicate with the inner space of the casing, and a space between the compression space and the through hole is formed. a cylinder in which a vane slot is formed to penetrate in a radial direction;
a roller provided on the rotating shaft to rotate, at least two or more portions of an outer circumferential surface contacting the inner circumferential surface of the cylinder so that at least two compression spaces are formed in the cylinder; and
One end faces the compression space and the other end is slidably inserted into the vane slot so as to face the through hole, and the other end includes a vane that is in contact with the outer circumferential surface of the roller to partition the compression space into a suction chamber and a compression chamber, respectively,
A side pressure space forming a discharge pressure is formed on the inner wall surface of the vane slot,
The side pressure space portion is formed between an inner peripheral side opening surface of the vane slot communicating with the compression space and an outer peripheral side opening surface of the vane slot communicating with the through hole,
A gas passage connecting the through hole and the side pressure space is formed on one side of the side pressure space in the radial direction,
the gas passage,
The compressor, characterized in that formed on one side of the circumferential direction of the vane slot by penetrating between the inner circumferential surface of the through hole and one side of the side pressure space outside the outer circumferential opening surface in a hole shape. According to claim 1,
The compressor, characterized in that the side pressure space portion is formed on a surface corresponding to the suction chamber side with respect to the vane. delete delete delete delete delete delete delete delete delete delete delete delete delete delete

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