WO2018194294A1

WO2018194294A1 - Rotary compressor

Info

Publication number: WO2018194294A1
Application number: PCT/KR2018/003884
Authority: WO
Inventors: 강승민; 신진웅; 노기율
Original assignee: 엘지전자 주식회사
Priority date: 2017-04-18
Filing date: 2018-04-03
Publication date: 2018-10-25
Also published as: CN110520624A; KR20180116984A; KR102338127B1; CN110520624B

Abstract

The present invention relates to a compressor comprising: a driving motor; a rotary shaft; a main bearing and a sub bearing fixed to a case, and provided along the rotary shaft; a cylinder fixedly provided between the main bearing and the sub bearing, accommodating a refrigerant in the center portion thereof, and having a suction port and a discharge port respectively formed in the radial direction; a roller of which one side is positioned inside the cylinder so as to come in contact with the inner peripheral surface of the cylinder, and which rotates together with the rotary shaft so as to form a compression space inside the cylinder; and at least two vanes insertively provided in the roller, and protruding by the rotation of the roller so as to divide the compression space into a suction chamber and a compression chamber while coming in contact with the inner peripheral surface of the cylinder, wherein a discharge port groove, which is formed to expand the end portion of the discharge port and increases the flow rate of the compressed refrigerant, is formed at one side of the inner peripheral surface of the cylinder.

Description

Rotary compressor

The present invention relates to a rotary compressor for compressing a refrigerant sucked into a compression space of a cylinder and then discharging it.

The compressor is applied to a vapor compression refrigeration cycle such as a refrigerator or an air conditioner. The compressor may be classified into an indirect suction method and a direct suction method according to a method of sucking refrigerant into a compression chamber.

The indirect suction method is a method in which the refrigerant circulating the refrigeration cycle is sucked into the compression chamber after entering the inner space of the compressor, and the direct suction method is a method in which the refrigerant is directly sucked into the compression chamber, unlike the indirect suction method. The indirect suction method may be referred to as a low pressure compressor, and the direct suction method may be referred to as a high pressure compressor.

In the low pressure compressor, since a refrigerant is first introduced into the internal space of the compressor, liquid refrigerant or oil is filtered out of the internal space of the compressor case, and thus no separate accumulator is provided. In contrast, in order to prevent liquid refrigerant or oil from flowing into the compression chamber, the high pressure compressor is usually provided with an accumulator on the suction side of the compression chamber.

The compressor may be classified into a rotary type and a reciprocating type according to a method of compressing a refrigerant.

A rotary compressor is a method of changing the volume of the compression space while rotating or turning in a rolling piston (hereinafter referred to as a roller). A reciprocating compressor is used to change the volume of the compression space while the rolling piston reciprocates in a cylinder. That's the way.

As the rotary compressor, there is a rotary compressor that compresses the refrigerant by using the rotational force of the electric drive.

In recent years, increasing the efficiency while gradually reducing the size of the rotary compressor has been the goal of the main technology development. In addition, research has been continuously made to obtain a larger cooling capacity by increasing the operating speed variable range of a miniaturized rotary compressor.

The rotary compressor includes a drive motor and a compression unit inside the case forming an exterior, and compresses and discharges the sucked refrigerant. The drive motor is composed of a rotor and a stator in the order of the rotation axis. When power is applied to the stator, the rotor rotates the rotating shaft while rotating inside the stator.

The compression unit includes a cylinder forming a compression space, a rolling piston (hereinafter referred to as a roller) coupled to the rotating shaft, and a vane that divides the compression space into a suction chamber and a compression chamber.

Inside the cylinder, there is provided a roller that rotates about a rotating shaft and forms a plurality of compression spaces together with the vanes. The roller is in concentric rotation with the axis of rotation.

The outer circumferential surface of the roller is provided with a plurality of vane slots radially, each vane is slid from the vane slot to protrude. Each vane protrudes from the vane slot and comes into close contact with the inner circumferential surface of the cylinder by the back pressure of the oil formed at the rear end and the centrifugal force by the rotation of the roller, thereby compressing the refrigerant contained in the inner space of the cylinder. That is, the refrigerant flowing into the suction chamber may be compressed to a predetermined pressure by vanes moving along the inner circumferential surface of the cylinder, and then discharged to the refrigeration cycle apparatus through the discharge pipe.

In the conventional rotary compressor, the vane moves along the inner circumferential surface of the cylinder to form a continuous compression mechanism, so that the pressure of the sucked refrigerant quickly reaches the discharge pressure. In this case, as the refrigerant is compressed to a pressure greater than the pressure to be compressed, overcompression loss occurs. Overcompression of the refrigerant causes unnecessary compression loss, reduces compressor efficiency, and causes mechanical breakage.

Conventional rotary compressors use a method of bypassing and discharging a part of the compressed refrigerant through the side of the cylinder, or use a method of increasing the diameter of the discharge port to prevent overcompression of the refrigerant in the compression space.

However, there is a limit in preventing overcompression of the refrigerant even by bypass, and even though the diameter of the discharge port is increased, it must be smaller than the thickness of the vane.

An object of the present invention is to prevent the over-compression of the refrigerant by preventing a rapid rise in pressure due to the compression of the refrigerant in the compression space, thereby to propose a structure of a compressor that can increase the compression efficiency by reducing the compression loss It is for.

One object of the present invention is to limit the rise of the refrigerant contained in the compression space to a pressure higher than the desired pressure.

An object of the present invention is to limit the pressure formed in the compression chamber to rise above a certain pressure by bypassing a part of the high pressure refrigerant compressed in the compression space.

The present invention is to propose a structure of a compressor that can reduce the speed at which the compressed refrigerant is discharged through the discharge port.

In order to achieve the object of the present invention, the rotary compressor according to the present invention includes a drive motor generating a rotational force in the case, a rotation shaft coupled with the driving motor to transmit the rotational force, and a main bearing and a sub-bearing installed along the rotational shaft. And a cylinder fixedly installed between the main bearing and the sub-bearing, the refrigerant being accommodated in the center portion, and having a suction port and a discharge port respectively formed in a radial direction, and extending at one end of the discharge port on an inner circumferential surface of the cylinder. And a discharge port groove is formed to increase the flow rate of the compressed refrigerant. By the discharge port groove, it is possible to obtain the effect that the movement passage of the compressed refrigerant is expanded.

According to an example related to the present invention, the cylinder has a bypass port positioned in front of the discharge port based on the direction in which the refrigerant is compressed so that an end portion of the bypass port is extended so that the flow rate of the moving refrigerant increases. Bypass grooves may be formed. By the bypass groove, it is possible to obtain the effect of expanding the passage through which the compressed refrigerant can move.

According to an example related to the present disclosure, a bypass hole may be formed in the main bearing and the sub bearing so as to communicate with the inner space of the case at a position overlapping with the compression space. By the bypass hole, a part of the compressed refrigerant is discharged, thereby limiting overcompression of the refrigerant.

In the rotary compressor according to the above configuration, the refrigerant compressed by the discharge port groove formed at the end of the discharge port can be discharged, and the refrigerant contained in the compression chamber can be prevented from being overcompressed, so that the compressor can be instructed. The loss can be reduced. When the overcompression of the refrigerant is prevented, the force acting on the side of the vane is reduced, so that the impact or wear of the vane with the vane slot can be reduced.

In addition, by the bypass port groove formed at the end of the bypass port, a part of the compressed refrigerant can be discharged, thereby preventing overcompression of the refrigerant in the compression chamber. Accordingly, it is possible to reduce the command loss of the compressor and to reduce the force acting on the side of the vane, thereby reducing the impact or wear of the vane with the vane slot.

In addition, by partially discharging the refrigerant having a rise in pressure through the bypass hole, the pressure of the refrigerant can be prevented from rising excessively in the compression chamber, and the loss due to the overcompression of the refrigerant can be reduced. By partially discharging the compressed refrigerant, it is possible to limit the increase in the discharge speed of the refrigerant at the discharge port, and to reduce the loss due to the discharge.

1 is a cross-sectional view showing the inside of a rotary compressor.

FIG. 2 is an enlarged view of the inside of the rotary compressor of FIG. 1. FIG.

3 is a plan view showing a state of the compression unit.

4 is a perspective view showing a state of a cylinder installed in a rotary compressor according to the present invention.

(A), (b), (c) is an enlarged view which shows the state of a discharge port and a discharge port groove.

6 is a perspective view showing a state of the cylinder 133.

7 is a conceptual view showing a state in which reaction force is formed on the vane.

8 is a graph showing reaction forces formed on the side of the vanes according to the rotation angle of the rotation shaft.

9 is a plan view of the compression unit viewed from above.

10 is a view showing a state of a discharge valve formed in the bypass hole.

11 is a graph showing the effect of the bypass hole.

12 is a graph showing the bypass hole effect.

EMBODIMENT OF THE INVENTION Hereinafter, the rotary compressor which concerns on this invention is demonstrated in detail with reference to drawings.

As used herein, the singular forms "a", "an" and "the" include plural forms unless the context clearly indicates otherwise.

In the following description of the embodiments disclosed herein, if it is determined that the detailed description of the related known technology may obscure the gist of the embodiments disclosed herein, the detailed description thereof will be omitted.

The accompanying drawings are only for easily understanding the embodiments disclosed in the present specification, and the technical idea disclosed in the present specification is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and technical scope of the present invention are included. It should be understood to include water or substitutes.

1 is a cross-sectional view showing the inside of the rotary compressor 100.

The rotary compressor 100 includes a case 110, a drive motor 120, and a compression unit 130.

The case 110 may form an outer shape, may have a cylindrical shape extending along one direction, and may be formed along an extending direction of the rotation shaft 123.

Inside the case 110, a cylinder 133 is formed to form the compression spaces V1 and V2 such that the sucked refrigerant is compressed and then discharged.

The case 110 is composed of an upper shell 110a, an intermediate shell 110b and a lower shell 110c. The drive motor 120 and the compression unit 130 may be fixedly installed on the inner surface of the intermediate shell 110b, and the upper and

lower shells

110a and 110c are respectively disposed on the upper and lower portions of the intermediate shell 110b. Positioned to limit the external exposure of components located therein.

The compression unit 130 serves to compress and discharge the refrigerant, and includes a roller 134, a vane 135, a cylinder 133, a main bearing 131, and a sub bearing 132.

The drive motor 120 is positioned above the compression unit 130 and serves to provide power for compressing the refrigerant. The drive motor 120 includes a stator 121, a rotor 122, and a rotation shaft 123.

The stator 121 is installed to be fixed to the inside of the case 110 and may be mounted on the inner circumferential surface of the cylindrical case 110 by shrinking. In addition, the stator 121 may be positioned to be fixed to the inner peripheral surface of the intermediate shell (110b).

The rotor 122 may be spaced apart from the stator 121 and may be disposed inside the stator 121. When power is applied to the stator 121, the rotor 122 is rotated by a force generated according to a magnetic field formed between the stator 121 and the rotor 122, and penetrates the center of the rotor 122. The rotational force is transmitted to the rotating shaft 123.

A suction port 133a is installed at one side of the intermediate shell 110b, and a discharge pipe 114 is installed at one side of the upper shell 110a to allow the refrigerant to flow out from the inside of the case 110.

The suction port 133a communicates with the suction pipe 113 and the case 110 from an evaporator (not shown) forming a refrigeration cycle, and the discharge port (not shown) is connected with the discharge pipe 114 and the case from a condenser (not shown). It will communicate (110).

The compression unit 130 installed inside the case 110 compresses the sucked refrigerant and discharges the compressed refrigerant. Intake and discharge of the refrigerant are performed in the cylinder 133 forming the compression spaces V1 and V2.

The rotary compressor 100 according to the present invention has a structure in which an end portion of the discharge port 133b is expanded in the process of compressing and discharging the refrigerant flowing through the suction port 133a formed in the cylinder 133. By having this, the compressed refrigerant can be discharged more smoothly.

FIG. 2 is an enlarged view of the inside of the rotary compressor 100 of FIG. 1, and FIG. 3 is a plan view illustrating the compression unit 130.

A roller 134 is formed inside the cylinder 133 to rotate about the rotation shaft 123 and to form the compression spaces V1 and V2 while contacting the inner circumferential surface 133a of the cylinder 133. The roller 134 is installed on an eccentric portion (not shown) formed on the rotation shaft 123, and the roller 134 rotates while forming one contact point P between the inner circumferential surfaces of the cylinder 133.

The roller 134 is positioned inside the cylinder 133 so that one side is in contact with the inner circumferential surface of the cylinder 133, and rotates together with the rotation shaft 123 to compress the spaces V1 and V2 inside the cylinder 133. Will form.

The vane 135 is installed at one side of the cylinder 133. The vanes 135 protrude into the compression spaces V1 and V2, and contact the outer circumferential surfaces of the roller 134 to form the compression spaces V1 and V2 inside the cylinder 133, respectively, in the suction chamber V1 and the compression chamber V2. Will be partitioned into The vanes 135 may be formed of at least two or more pieces, and each vane 135 may be positioned inside the roller 134 and may be symmetric with each other.

As the rotation shaft 123 rotates, each vane 135 moves while being in contact with the inner circumferential surface of the cylinder 133 while rotating together with the roller 134, and the space portion and the roller 134 formed at the center of the cylinder 133. Between the compression space (V) is formed.

After the vane 135 moves, the refrigerant flowing from the suction port 133a is compressed and then moved along the discharge port 133b, and the discharge holes are formed in the main bearing 131 and the sub bearing 132, respectively. 143, 144 will be discharged along.

However, since the contact point between the cylinder 133 and the roller 134 is maintained at the same position, and the front end of the vane 135 moves along the inner circumferential surface of the cylinder 133, the pressure formed in the compression space (V1, V2) Since the vane 135 has a continuous compression mechanism and the pressure of the compression chamber V2 reaches the discharge pressure quickly, a loss due to overcompression occurs, resulting in a decrease in efficiency.

In the conventional rotary compressor, since the compressed refrigerant is discharged at one time through the discharge holes 143 and 144 communicating with the compression spaces V1 and V2 of the cylinder 133, the refrigerant that has not been discharged is There was a problem that overcompression occurs.

When overcompression of the refrigerant contained in the compression space (V1, V2) occurs, unnecessary compression loss occurs to reduce the efficiency of the compressor, there is a problem that causes mechanical damage.

Accordingly, the present invention discharges in order of the bypass port 133c and the discharge port 133b formed in the cylinder 133 so as to reduce the mechanical loss due to overcompression of the refrigerant. In addition, the ends of the discharge port 133b and the bypass port 133c are extended to have a structure capable of increasing the flow rate of the compressed refrigerant.

4 is a perspective view showing a state of the cylinder 133 installed in the rotary compressor 100 according to the present invention.

The cylinder 133 has a space portion in the center thereof, and forms compression spaces V1 and V2 between the rollers 134.

On the inner circumferential surface of the cylinder 133, a suction port 133a through which the refrigerant is sucked into the compression spaces V1 and V2 is formed, and the discharge for moving the compressed refrigerant along the moving direction of the

vanes

135a, 135b, 135c. The port 133b is formed. Two discharge ports 133b may be formed on the inner circumferential surface of the cylinder 133 up and down.

In the rotary compressor 100, as the roller 134 rotates, the

vanes

135a, 135b, and 135c protrude from the roller 134, and the front end portions of the

vanes

135a, 135b, and 135c are in contact with the inner circumferential surface of the cylinder 133. It is possible to compress the sucked refrigerant while moving in contact.

In the conventional invention, the pressure of the refrigerant quickly reaches the discharge pressure by the movement of the

vanes

135a, 135b, and 135c, and there is a problem in that an indication loss due to overcompression is increased. If the diameter of the discharge port 133b is increased, the discharge area can be enlarged compared to the capacity, and this may be considered. Since there is a problem that leakage between V1 and the compression chamber V2 occurs, the limit exists.

The rotary compressor 100 according to the present invention is configured to extend the end of the discharge port 133b through which the refrigerant compressed by the rotation of the

vanes

135a, 135b, and 135c is discharged, and may increase the flow rate of the compressed refrigerant. And a discharge port groove 133b '.

The discharge port groove 133b 'may be formed to be recessed along the inner circumferential surface of the cylinder. Accordingly, by separately forming a moving flow path of the refrigerant communicating with the hole of the discharge port 133b, discharge of the compressed refrigerant may be performed. It can be done more smoothly.

5A, 5B, and 5C are enlarged views showing the state of the discharge port 133b and the discharge port groove 133b '.

The discharge port groove 133b 'has an inner circumferential surface of the cylinder 133 so as to extend the end of the discharge port 133b in order to solve the problem that the diameter of the discharge port 133b is limited by the width of the vane 135. The shape is recessed along, so as to increase the moving flow rate of the refrigerant.

The discharge port groove 133b 'is formed to extend the end of the discharge port 133b at the start of the discharge port 133b. The discharge port groove 133b 'may be formed in the shape of a groove having a constant depth along the shape of the inner circumferential surface of the cylinder 133.

As shown in FIG. 5, the discharge port groove 133b ′ may be formed to have a height greater than the height of the discharge port 133b, and may have a width larger than the diameter of the discharge port 133b. The discharge port groove 133b 'may be formed along a direction in which the vane 135 moves in one end of the discharge port 133b, and extends along an inner circumferential surface of the cylinder 133 on one side of the discharge port 133b. Can be.

The discharge port groove 133b 'may be formed to overlap some or all of the ends of the discharge port 133b. (A) and (b) of FIG. 5 have a shape in which the end portion of the discharge port 133b and the discharge port groove 133b 'overlap with each other, and (c) the end portion and the discharge port groove of the discharge port 133b. The shape so that all of 133b 'may overlap is shown.

As the area overlapping with the end of the discharge port 133b is wider, the flow rate at which the refrigerant compressed in the compression chamber V2 can move through the discharge port groove 133b 'may be increased, thereby further increasing overcompression of the refrigerant. It can be effectively prevented.

Since the refrigerant compressed in the compression chamber V2 may be discharged through the discharge port groove 133b ', the flow rate may be larger than that of the compressed refrigerant being discharged only by the discharge port 133b. It is possible to limit the sudden increase in the internal pressure of the.

6 is a perspective view illustrating the cylinder 133.

The cylinder 133 has a space portion at the center thereof, and forms compression spaces V1 and V2 between the rollers 134.

On the inner circumferential surface of the cylinder 133, a suction port 133a through which the refrigerant is sucked into the compression space is formed, and a discharge port 133b for moving the compressed refrigerant along the moving direction of the vane 135 is formed. Two discharge ports 133b may be formed on the inner circumferential surface of the cylinder 133 up and down.

The cylinder 133 may further include a bypass port 133c positioned forward of the discharge port 133b based on the direction in which the refrigerant is compressed to discharge the compressed refrigerant.

The bypass port 133c partially discharges the refrigerant during compression, thereby limiting an increase in the internal pressure of the compression chamber V2. When the compressed refrigerant is discharged only in the discharge port 133b, since the internal pressure of the compression chamber V2 is continuously increased due to the movement of the vane 135, the bypass port 133c is a part of the compressed refrigerant. By discharging, it is possible to prevent overcompression of the refrigerant.

The diameter of the bypass port 133c is limited by the width of the vane 135 so that leakage between the compression chamber V2 and the suction chamber V1 is prevented. Accordingly, the bypass port groove 133c 'may be formed on the inner circumferential surface of the cylinder 133 so that the end portion of the bypass port 133c is extended to increase the flow rate of the refrigerant. The bypass port groove 133c 'may be formed to be recessed along the inner circumferential surface of the cylinder 133. Accordingly, by separately forming the moving flow path of the refrigerant communicating with the hole of the bypass port 133c, the compressed refrigerant can be smoothly discharged.

The bypass port groove 133c ′ may have a height greater than the height of the bypass port 133c, and may have a width larger than the diameter of the bypass port 133c. The bypass port groove 133c 'may be formed along a direction in which the vane 135 moves in one end of the bypass port 133c, and extends along an inner circumferential surface of the cylinder 133 on one side of the bypass port 133c. Could be. In FIG. 6, only one bypass port 133c is formed in the cylinder 133, but one or more number of bypass ports 133c may be formed in the cylinder 133. 133c 'may be formed.

FIG. 7 is a conceptual diagram illustrating how reaction force is formed in the vane 135.

The vane 135 protrudes by the rotation of the roller 134, and the front end of the vane 135 forms a compression of the refrigerant while contacting the inner circumferential surface of the cylinder 133. Along the moving direction of the vane 135, the compression chamber (V2) is located in the front, the suction chamber (V1) is located in the rear. Since the pressure of the compression chamber V2 is higher than the pressure of the suction chamber V1, the force acting on the vane 135 by the pressure of the compression chamber V2 is the vane by the pressure of the suction chamber V1. Greater than the force acting on 135. That is, the side force Fp acts on the side of the vane 135 in the direction of the suction chamber from the compression chamber V2. By the side force Fp, the vanes 135 collide with the vane slots or cause large wear.

In particular, the side force Fp becomes larger at a position where the pressure in the compression chamber V2 rises sharply, and the force acting on the side of the vane 135 has a large pressure formed in the compression chamber V2. In this case, the side force Fp also becomes large.

The rotary compressor 100 according to the present invention includes a discharge port groove 133b 'configured to enlarge the area of the discharge port 133b, and a bypass port groove 133c' configured to enlarge the area of the bypass port 133c. Each of these is formed, thereby preventing the overcompression phenomenon in which the pressure of the refrigerant in the compression chamber V2 rises above the set value. That is, the reaction force increases on the side surface of the vane 135 by preventing the pressure of the refrigerant formed in the compression chamber V2 from increasing more than necessary, thereby limiting the increase in the side force Fp formed on the side surface of the vane 135. You can stop doing so. As a result, the frictional loss of the side surface of the vane 135 can be reduced.

8 is a graph showing the reaction force formed on the side of the vane according to the rotation angle of the rotation shaft.

In the graph, the horizontal axis represents the rotation angle of the rotation axis, and the vertical axis represents the magnitude of reaction force formed on the side of the vane 135.

Here, the reaction force is formed by the side force Fp formed on the side of the vane 135.

The side force Fp formed on the side of the vane 135 increases from the compression start time at which compression is started to the discharge start time at which discharge is started. Specifically, the lateral force Fp increases between about 160 ° of compression start time and about 220 ° of discharge start time, and starts to decrease after 220 ° where bypass port 133c is formed.

According to the present invention, the compression chamber (133b ') is formed to enlarge the area of the discharge port (133b) and the bypass port groove (133c') to enlarge the area of the bypass port (133c). The overcompression phenomenon in which the pressure of the refrigerant at V2) rises above the set value can be prevented. In particular, it can be seen that there is an effect that can reduce the side force (Fp) between approximately 220 ° point where the bypass port groove (133c ') is formed from approximately 260 ° point where the discharge port groove (133b') is formed. . Accordingly, the force acting on the side of the vane 135 is reduced, thereby reducing the frictional loss generated between the side of the vane 135 and the vane slot, thereby reducing the mechanical loss of the compressor.

9 is a plan view of the compression unit viewed from above.

The compressor according to the present invention includes a bypass hole 140 capable of reducing an indication loss due to overcompression so as to reduce the pressure rise in the compression spaces V1 and V2.

The bypass hole 140 is formed at a position overlapping the compression space V of the main bearing 131 and the sub-bearing 132, and the vane 135 moves in contact with the inner circumferential surface of the cylinder 133. It serves to reduce the pressure of the refrigerant contained in the compression space (V1, V2) formed along. The refrigerant flowing out through the bypass hole 140 moves to the inner space of the case 10.

The compression unit 130 is formed by stacking the main bearing 131, the cylinder 133, and the sub bearing 132 in order from the top to the bottom.

The main bearing 131 and the cylinder 133, the sub-bearing 132 and the cylinder 133 may be screwed into the screw hole 143 and fixed. The roller 134 is located in the inner space formed at the center of the cylinder 133, the vane 135 is in contact with the inner circumferential surface of the cylinder 133, the compression space between the roller 134 and the inner circumferential surface of the cylinder 133 (V) is formed.

The compression spaces V1 and V2 communicate with the suction port 133a, the bypass port 133c, and the discharge port 133b into which the refrigerant is introduced.

The roller 134 and the cylinder 133 have one contact point P. FIG. An imaginary line connecting the contact point P and the center of the rotation shaft 123 is a reference line, and the angle at this time is referred to as 0 °. The rotation angle means an angle measured in a counterclockwise direction between the reference line and a line connecting a specific position and the center of the rotation axis 123.

When the first vane 135a is positioned at the end of the suction port 133a, which is the point at which suction is completed, the position and the rotation axis 123 of the second vane 135b positioned at a predetermined angle apart from the first vane 135a. The angle formed by the line connecting the centers of h) forms an angle between approximately 160 ° and 165 °, which is called the compression start angle β. Here, the position of the end of the suction port 133a, which is the point at which suction is completed, forms an angle between approximately 40 ° and 45 °. In addition, the bypass port 133c formed on the side surface of the cylinder 133 is formed at the point where the rotation angle is about 270 °, and the angle to the position of the start point of the bypass port 133c is called the discharge start time γ. .

The bypass hole 140 may be formed at a position where the main bearing 131, the sub bearing 132, and the compression space V overlap each other. The bypass hole 140 may be formed between the compression start time and the discharge start time. Specifically, the bypass hole 140 is located in an area between the angle of β, which is the compression start time, and the angle of γ, which is the discharge start time. For example, the bypass hole 140 may be formed at a position between 160 ° and 270 ° based on the contact point P, and may overlap the compression space V. FIG.

As the driving motor 20 rotates, when the rotating shaft 123 rotates counterclockwise, the roller 134 installed on the rotating shaft 123 rotates counterclockwise, and the roller 134 is counterclockwise. The refrigerant flowing into the compression space (V1, V2) of the cylinder 133 through the suction port 133a is located in the space formed between the inner circumferential surface of the cylinder 133 and each vane 135, the vane According to the movement of the 135, the gap between the outer circumferential surface of the roller 134 and the inner circumferential surface of the cylinder 133 may be narrowed and compression may be performed. The compressed refrigerant partially flows out through the bypass port 133c, and finally moves along the discharge passage 142 by the movement of the vanes 135.

Through the bypass hole 140, the compressed refrigerant may move, and overcompression may be prevented in the compression of the refrigerant due to the movement of the vane 135.

The bypass hole 140 is formed upward from the lower surface of the main bearing 131 to communicate the compression space V and the internal space of the case 10. In addition, the bypass hole 140 is formed downward from the upper surface of the sub-bearing 132, it may be made to communicate the compression space (V1, V2) and the internal space of the case 10.

The bypass hole 140 may be formed at a position where the main bearing 131 and the compression space V, the sub bearing 132 and the compression spaces V1 and V2 overlap each other. The bypass hole 140 may be formed of at least one or more pieces, and may be formed to be spaced apart from each other along an arc of a predetermined length. The bypass hole 140 may be formed as a circular hole, the diameter of the bypass hole 140 should be smaller than the thickness of the vanes 135. This is because when the diameter of the bypass hole 140 is larger than the thickness of the vane 135, a leakage phenomenon occurs between the compression spaces V1 and V2 partitioned by the vanes 135.

10 is a view showing a state of the discharge valve 150 formed in the bypass hole.

The discharge valve 150 may be fixed to the upper surface of the main bearing 131 and the lower surface of the sub bearing 132, and may be formed to cover the bypass holes 140. The discharge valve 150 may form the opening and closing of the bypass hole 140 by the pressure formed in the compression space (V).

The discharge valve 150 may have a number corresponding to the number of the bypass holes 140. A plurality of discharge valves 150 may be formed to cover each bypass hole 140. In this case, each of the discharge valves 150 may be moved upward based on one end fixed by the pressure formed in each bypass hole 140.

11 and 12 are graphs illustrating the effect of the bypass hole 140.

The rotary compressor according to the present invention, in addition to the bypass port 133c and the discharge port 133b formed on one side of the inner peripheral surface of the cylinder 133 so as to communicate with the compression space (V1, V2), the main bearing 131 and Bypass holes 140 may be formed in the sub-bearings 132, respectively.

As the vane 135 rotates in the compression direction, the refrigerant contained in the compression spaces V1 and V2 is compressed, and a portion of the refrigerant compressed in the compression spaces V1 and V2 is discharged through the bypass port 133c. The compressed refrigerant is discharged through the discharge port 133b positioned beyond the bypass port 133c. In this case, the flow rate of the compressed refrigerant moved through the discharge port 133b and the bypass port 133c may be increased by the discharge port groove 133b 'and the bypass port groove 133c', as described above. .

When the driving motor rotates at a high speed of 40 Hz or more in the rotary compressor 100, the amount of the refrigerant compressed through the vanes 135 also increases, so that the compressed refrigerant may be smoothly discharged from the main bearing 131 and the sub bearing. In 132, the bypass hole 140 may be formed in an area overlapping the compression spaces V1 and V2.

Since the bypass hole 140 may be formed in plural, it is possible to bring about an effect of increasing the effective discharge area.

11 is a graph showing the velocity of the mass flow rate of the refrigerant contained in the compression spaces V1 and V2. In the graph, the horizontal axis represents the rotation angle of the rotation axis, and the vertical axis represents the velocity of the mass flow rate in the compression spaces V1 and V2.

Here, the dotted line shows that the bypass hole 140 is not formed in each bearing, and the solid line shows the case where the bypass hole 140 is formed in each bearing 131, 132. As shown in the graph, when the bypass hole 140 is formed in the rotary compressor 100 in the rotary compressor rotating at 60 Hz, it can be seen that the flow rate of the refrigerant contained in the compression space V decreases as a whole. That is, when the bypass hole 140 is formed, it is possible to confirm that the flow rate of the refrigerant is reduced overall. In addition, the flow rate of the refrigerant at the time of discharge is reduced to reduce the loss of the compressor.

12 is a graph showing a change in pressure in the compression chamber according to the rotation angle.

Here, the dotted line indicates the case where the bypass hole 140 does not exist, and the solid line indicates the case where the bypass hole 140 is formed.

As shown by the dotted line, when the bypass hole 140 is not formed in the rotary compressor, when the rotation angle is about 240 °, the pressure in the compression spaces V1 and V2 continues to increase, causing the refrigerant to overcompress. Done. This unnecessarily compresses the refrigerant, causing a decrease in the efficiency of the compressor. The hatched portion in the graph shows the loss due to overcompression that occurs as the pressure in the compression chamber V2 rises from approximately 240 °.

The bypass hole 140 is formed in a region between the compression start time β and the discharge start time γ, and may be formed between approximately 160 ° and 270 °. For example, when the bypass holes 140, 240, and 340 are formed from around 240 ° of rotation angle, the pressure in the compression chamber V2 is no longer increased to the maximum of approximately 22.5 kgf / cm ^ 2. Can be kept constant. Through the bypass hole 140, some of the refrigerant whose pressure is increased may flow out, and thus the pressure of the compression chamber V2 may continuously increase to prevent the refrigerant from being overcompressed.

In addition, since the portion of the refrigerant compressed in the compression spaces V1 and V2 is discharged through the bypass hole 140, the flow rate of the refrigerant discharged through the discharge port can be finally reduced. Thus, the efficiency of the compressor can be further increased.

What has been described above is only embodiments for implementing a rotary compressor according to the present invention, the present invention is not limited to the above embodiments, and do not depart from the gist of the present invention as claimed in the claims below. Anyone skilled in the art to which the present invention pertains within the scope will have the technical idea of the present invention to the extent that various modifications can be made.

The present invention may be applied and applied in various industries for producing and using a compressor for compressing a refrigerant and then discharging it.

Claims

A drive motor generating a rotational force inside the case;

A rotating shaft coupled to the driving motor to transmit a rotating force;

A main bearing and a sub bearing fixed to the case and installed along the rotating shaft;

A cylinder fixedly installed between the main bearing and the sub-bearing, the refrigerant being accommodated in the center, and the suction port and the discharge port respectively formed in the radial direction;

A roller positioned at one side of the cylinder to be in contact with the inner circumferential surface of the cylinder and rotating together with the rotating shaft to form a compression space in the cylinder; And

It is inserted into the roller and includes at least two vanes protruding by the rotation of the roller to contact the inner peripheral surface of the cylinder and partition the compression space into a suction chamber and a compression chamber,

Compressor, characterized in that the discharge port groove is formed on one side of the inner peripheral surface of the cylinder to extend the end of the discharge port and to increase the flow rate of the compressed refrigerant.
The method of claim 1,

The discharge port groove, characterized in that the compressor is formed along the inner peripheral surface of the cylinder.
The method of claim 1,

The discharge port groove, characterized in that formed in the direction of movement of the vane at one end of the discharge port.
The method of claim 1,

The discharge port groove, the compressor characterized in that extending along the inner peripheral surface of the cylinder on one side of the discharge port.
The method of claim 1,

And the bypass hole is formed in the main bearing and the sub-bearing so as to communicate with the inner space of the case at a position overlapping with the compression space.
The method of claim 5,

Compressor, characterized in that consisting of at least one or more of the bypass hole.
The method of claim 5,

And a discharge valve fixedly installed at an upper surface of the main bearing and a lower surface of the sub-bearing, respectively, to cover the bypass hole and to open and close the bypass hole.
The method of claim 1,

The cylinder is provided with a bypass port positioned forward of the discharge port on the basis of the direction in which the refrigerant is compressed to discharge the compressed refrigerant,

The bypass port,

Compressor, characterized in that the bypass port groove is formed on one side so that the flow rate of the moving refrigerant is extended by the end of the bypass port is increased.
The method of claim 8,

And the bypass port groove has a shape that is recessed along an inner circumferential surface of the cylinder.