KR20220121970A - Rotary compressor - Google Patents

Abstract

A rotary compressor according to the present embodiment includes a shell; a drive motor; a main bearing and a sub-bearing; a cylinder; a roller; a vane; and a discharge muffler provided in the sub-bearing to accommodate a discharge port provided in the sub-bearing. The discharge muffler is provided with a discharge space accommodating the discharge port and is formed with a refrigerant discharge hole spaced apart from the discharge port and penetrating the discharge space, and at least one partition wall partitioning the discharge space may be formed between the discharge hole and the refrigerant discharge hole. Through this, it is possible to reduce vibration noise through the discharge muffler in a low pressure, top-compression and spring-supported type rotary compressor.

Description

Rotary Compressor

The present invention relates to a rotary compressor.

A compressor is a device that compresses a refrigerant by transferring the power generated from the electric part to the compression part. In the compressor, the transmission unit and the compression unit may be installed together inside the shell, or the transmission unit may be installed outside the shell and connected to the compression unit inside the shell using a separate power transmission mechanism. The former is called a hermetic compressor, and the latter is called an open compressor.

The hermetic compressor is classified into a low-pressure compressor and a high-pressure compressor according to the refrigerant filled in the inner space of the shell. The low-pressure compressor is a method in which the low-temperature and low-pressure refrigerant circulated through the refrigeration cycle is filled in the inner space of the shell, and in the high-pressure compressor, the high-temperature and high-pressure refrigerant discharged from the compression unit is filled in the inner space of the shell.

The low-pressure compressor cools the motor constituting the electric part as the inner space of the shell is filled with a low-temperature refrigerant, so that the motor efficiency can be improved. On the other hand, in the high-pressure compressor, the refrigerant discharged from the compression unit circulates in the inner space of the shell, so that the oil separation effect can be improved.

In addition, the hermetic compressor may be divided into a lower compression type and an upper compression type according to the positions of the electric part and the compression part. The lower compression type is a method in which the compression part is located lower than the transmission part, and the upper compression type is a method in which the compression part is located above the transmission part.

The lower compression type is advantageous for refueling because the compression part is adjacent to the oil stored in the shell, but the high temperature loop pipe is immersed in the oil stored in the shell and the oil viscosity may be lowered. On the other hand, the upper compression type is disadvantageous for refueling as the distance between the compression part and the oil is greater than that of the lower compression type, but the high temperature loop pipe is not immersed in the oil stored in the shell, which may be advantageous in maintaining the oil viscosity.

In addition, the hermetic compressor may be divided into a shell-supported type and a spring-supported type according to a method of supporting the compressor body including a transmission unit and a compression unit. In the shell-supported type, the compressor body is fixed and supported by the shell, and in the spring-supported type, the compressor body is separated from the shell and supported by a spring.

In the shell support type, the compressor body is firmly supported by fixing the compressor body to the shell, so that the vibration of the compressor body is low but the compressor vibration is increased. On the other hand, in the spring-supported type, as the compressor body is supported by a spring, the vibration of the compressor body increases, but the vibration of the compressor body is attenuated by the spring, so that the shell vibration is reduced and the compressor vibration is lowered.

Patent Document 1 (Korean Patent Application Laid-Open No. 10-2000-0059891) discloses a rotary compressor of a low pressure type and an upper compression type. Patent Document 1 is made of a shell fixing method in which the compressor body including the transmission part and the compression part is fixed in close contact with the inner circumferential surface of the shell. This can be aggravated by compressor vibrations as described above.

Patent Document 2 (Japanese Patent Laid-Open No. 2004-232524) discloses a low-pressure type and shell-supported rotary compressor. Patent Document 2 has a double shell structure, and the compressor body is fixed to the inner shell in a shell-supporting manner, and the inner shell is supported by the outer shell in a spring-supported manner. The inner space of the inner shell is filled with the discharged refrigerant and is in a high pressure state, and this refrigerant is directly discharged without passing through the inner space of the outer shell. Accordingly, the inner space of the outer shell is maintained in a low pressure state.

In Patent Document 2, the inner shell surrounding the electric part is cooled by the refrigerant filled in the inner space of the outer shell, so that the motor efficiency can be improved. In addition, since the inner shell to which the compressor body is fixed is supported by a spring on the outer shell, the vibration of the compressor body can be improved to some extent and the shell vibration can also be lowered.

However, in Patent Document 2, since the shell is composed of an inner shell and an outer shell, the volume and weight of the compressor may increase, and the number of parts may increase, thereby increasing the manufacturing cost. In addition, Patent Document 2 is a low pressure type and lower compression type, so there is not enough space to install a long loop pipe, and the roof pipe is immersed in the oil stored in the shell and the temperature of the oil rises. friction loss may occur.

Accordingly, a rotary compressor such as Patent Document 3 (Chinese Patent Publication No. 101260884 A) has been proposed. Patent Document 3 is a low pressure type, upper compression type, and consists of a spring support type.

Patent Document 3 is composed of a single shell, so it is possible to reduce the volume and weight of the compressor and reduce the number of parts, thereby reducing the manufacturing cost. In addition, as the compression part is located above the transmission part, it prevents the roof pipe from being submerged in oil to prevent an increase in oil temperature and to prevent excessive decrease in oil viscosity that occurs when the oil temperature rises, thereby reducing friction loss in the compression part. . In addition, Patent Document 3 can reduce the vibration of the compressor as much as it is possible to form a long roof pipe by using the upper space of the shell.

However, in the conventional rotary compressor as described above, as the compression unit is located above the transmission unit, it may be difficult to smoothly supply oil to the compression unit. In particular, in the case of a low-pressure compressor such as Patent Document 2, since the inside of the compression part constituting the high pressure is separated from the inner space of the shell making the low pressure, the oil scattered from the upper end of the rotating shaft cannot be supplied to the inside of the compression part, resulting in frictional loss. can occur.

In addition, in the conventional rotary compressor, when an oil supply passage connecting the inner space of the shell and the interior of the compression unit is formed in the compression unit, a portion of the refrigerant compressed in the compression chamber leaks into the inner space of the shell through the oil supply passage, resulting in compression loss This can happen.

In addition, in the conventional rotary compressor, vibration and noise may be generated while the compressed refrigerant is discharged. In particular, when the transmission unit and the compression unit are elastically supported with respect to the shell as in Patent Document 3, vibration by the refrigerant discharged from the compression unit is excited, thereby increasing the overall compressor vibration and noise.

Korean Patent Publication No. 10-2000-0059891 (published date: October 16, 2000) Japanese Laid-Open Patent Publication No. 2004-232524 (published on August 19, 2004) Chinese Laid-Open Patent No. 101260884 (published on: 2008.09.10.)

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotary compressor capable of reducing friction loss in a compression part while being of a low pressure type, an upper compression type, and a spring supported type.

Furthermore, an object of the present invention is to provide a rotary compressor in which the oil stored in the shell is supplied to the compression unit to suppress friction loss in the compression unit.

Furthermore, an object of the present invention is to provide a rotary compressor capable of collecting oil scattered from a rotating shaft and supplying it to the compression unit without leakage.

Another object of the present invention is to suppress the leakage of oil or refrigerant into the inner space of the shell through the oil supply passage that communicates between the inner space of the shell and the inside of the compression part while being of a low pressure type, an upper compression type, and a spring supported type. It is intended to provide a rotary compressor.

Furthermore, an object of the present invention is to provide a rotary compressor that selectively opens and closes the oil supply passage to suppress the reverse flow of oil or refrigerant supplied to the compression unit.

Furthermore, an object of the present invention is to provide a rotary compressor capable of suppressing leakage of oil or refrigerant even without a separate non-return valve.

Another object of the present invention is to provide a rotary compressor capable of suppressing compressor vibration and noise while being of a low pressure type, an upper compression type, and a spring supported type.

Furthermore, an object of the present invention is to provide a rotary compressor capable of suppressing vibration and noise generated by the refrigerant discharged from the compression unit.

Furthermore, an object of the present invention is to provide a rotary compressor that includes a discharge muffler on the discharge side of the compression unit, and can reduce manufacturing cost by simplifying the structure of the discharge muffler.

In order to achieve the object of the present invention, it includes a discharge cover provided with a discharge space to accommodate the discharge port, wherein the discharge cover is formed in an annular outer wall portion and annularly formed at a predetermined interval in the radial direction from the outer wall portion It may include an inner wall portion disposed with a, and an upper wall portion connecting one end of the outer wall portion and one end of the inner wall portion in a radial direction. The discharge space may be provided with a partition wall partitioning the discharge space, and the partition wall may be formed by connecting the outer wall portion, the inner wall portion, and the upper wall portion.

For example, at least one of the partition walls may be provided across both ends of a discharge valve that opens and closes the discharge port.

Specifically, the rotary compressor according to the present embodiment may include a shell, a main bearing and a sub-bearing, a cylinder, a roller, a vane, and a discharge muffler. The driving motor may be elastically supported while being spaced apart from the inner circumferential surface of the shell. The main bearing and the sub-bearing may be provided above the driving motor to support the rotation shaft of the driving motor. A cylinder may be provided between the main bearing and the sub-bearing to form a compression chamber therein. The roller may be provided on the rotation shaft and provided inside the cylinder. The vane may be slidably inserted into the vane slot provided in the cylinder and provided between the cylinder and the roller. A discharge muffler may be provided in the sub-bearing to accommodate a discharge port provided in the sub-bearing.

For example, the discharge muffler may include a discharge space accommodating the discharge port. A refrigerant discharge hole that is spaced apart from the discharge port and passes through the discharge space may be formed. At least one partition wall partitioning the discharge space may be formed between the discharge port and the refrigerant discharge hole. Through this, since the discharged refrigerant is discharged after moving through the discharge space for a long time, vibration noise generated when the refrigerant is discharged can be effectively reduced.

For example, the discharge space may be formed in an annular shape having an outer circumferential surface and an inner circumferential surface, and an upper surface connecting one end of the outer circumferential surface and one end of the inner circumferential surface. The partition wall may extend from an outer circumferential surface, an inner circumferential surface, and an upper surface of the discharge space, and at least one partition wall may be provided on a line connecting the shortest distance between the discharge port and the refrigerant discharge hole. Through this, by suppressing the refrigerant discharged through the discharge port from moving directly to the refrigerant discharge hole, it is possible to increase the vibration and noise attenuation effect in the discharge space.

For example, the partition wall may include a first partition wall positioned on a line connecting the shortest distance between the discharge port and the refrigerant discharge hole. The first partition wall may be provided across both ends of a discharge valve that opens and closes the discharge port. Through this, the refrigerant can be guided to the refrigerant discharge hole while circulating along the discharge space.

As another example, the first partition wall may be formed in a direction perpendicular to an imaginary line connecting both ends of the discharge valve. Through this, it is possible to suppress the formation of the refrigerant stagnant space on the side surface of the first partition wall.

As another example, the first partition wall may extend in the longitudinal direction of the discharge valve to form a valve fixing part for fixing one end of the discharge valve to the sub-bearing or a retainer part for limiting the opening amount of the discharge valve. have. Through this, it is possible to simplify the manufacturing process by excluding a separate valve retainer while easily fixing the discharge valve.

For example, the sub-bearing may be provided with a discharge valve for opening and closing the discharge port. The partition wall may include at least one second partition spaced apart from the discharge valve. The second barrier rib may be formed as a communication part so that both spaces separated by the second barrier rib communicate with each other. Through this, the discharge space is divided into a plurality of chambers to more effectively attenuate vibration noise.

As another example, the discharge space may be divided into a plurality of spaces by the second partition wall. The plurality of spaces may be formed in different volumes. Through this, it is possible to attenuate vibration noise of various bands.

As another example, the plurality of spaces may have a larger volume as they are adjacent to the refrigerant discharge hole. Through this, it is possible to reduce the bottleneck in the refrigerant discharge hole while effectively reducing the vibration noise of the refrigerant.

For example, the discharge muffler may include a discharge muffler body portion in which the discharge space is formed in an annular shape, and a discharge muffler fixing portion extending radially from an outer peripheral end of the discharge muffler body portion. The partition wall may connect between an outer wall surface and an inner wall surface of the discharge muffler body forming the discharge space. Through this, it is possible to secure rigidity while closely partitioning the discharge space.

As another example, the valve accommodating part may be formed to protrude outward from the outer wall surface of the discharge muffler body part. One end of the discharge valve for opening and closing the discharge port may be inserted into the valve accommodating part. Through this, the discharge valve can be installed inside the discharge space without increasing the overall size of the discharge muffler, thereby reducing the size of the compressor.

As another example, the valve accommodating part may be formed to protrude outward from the outer wall surface of the discharge muffler body part. The valve accommodating part may communicate with the discharge space. The refrigerant discharge hole may pass through the valve accommodating part. Through this, it is possible to more effectively reduce the vibration noise of the refrigerant by locating the refrigerant discharge hole as far as possible from the discharge port.

As another example, the valve accommodating part may be formed to protrude outward from the outer wall surface of the discharge muffler body part. The partition wall may extend from one end adjacent to the discharge port to an inner wall surface of the discharge muffler body portion among both ends of the valve receiving portion in the circumferential direction. Through this, it is possible to more effectively reduce the vibration noise of the refrigerant by locating the refrigerant discharge hole as far as possible from the discharge port.

For example, the cylinder may be provided on an axially upper side of the driving motor. The driving motor may be elastically supported with respect to the shell by a support part spaced apart from the inner circumferential surface of the shell and having elasticity. Through this, it is possible to minimize the vibration generated in the compressor body from being transmitted to the outside of the shell through the shell, thereby reducing the compressor vibration.

As another example, it may further include an oil supply guide for supplying the oil pumped from the shell to the compression chamber. The oil supply guide part, the oil supply passage hole may be formed to pass through the sub-bearing or the cylinder to communicate with the vane slot provided in the cylinder. Through this, the oil pumped from the shell is supplied between the vanes constituting the compression unit and the vane slots to smoothly lubricate the compression unit of the rotary compressor forming the low pressure type.

As another example, an oil supply guide for collecting oil may be provided on the upper side of the rotation shaft. The outlet of the oil supply guide may communicate with the oil supply passage hole through the inner space of the shell. Through this, it is possible to increase the oil supply effect to the compression unit by collecting the oil scattered from the upper end of the rotary shaft and supplying the concentrated oil to the compression unit.

As another example, the sub-bearing or the cylinder may be provided with a non-return valve for opening and closing the oil supply passage hole. Through this, the oil supplied to the compression unit and the refrigerant compressed in the compression unit may be suppressed from leaking through the oil supply guide.

As another example, an oil supply guide for collecting oil and guiding it toward the oil supply passage hole may be provided on the upper side of the rotation shaft. The outlet of the oil supply guide may be connected to the oil supply guide pipe to the oil supply passage hole. Through this, it is possible to quickly supply the oil scattered from the rotating shaft to the compression unit, and at the same time prevent a reverse flow of oil or refrigerant in the compression unit without a separate non-return valve.

In the rotary compressor according to the present embodiment, the discharge muffler may include a discharge space for accommodating the discharge port and a refrigerant discharge hole for discharging the refrigerant, and at least one partition wall may be formed between the discharge port and the refrigerant discharge hole. Through this, by forming a long discharge path of the discharged refrigerant, it is possible to effectively reduce vibration noise generated when the refrigerant is discharged.

In the rotary compressor according to the present embodiment, the partition wall may be formed on a line connecting the shortest distance between the discharge port and the refrigerant discharge hole. Through this, it is possible to suppress the direct movement of the refrigerant discharged through the discharge hole to the refrigerant discharge hole, thereby increasing the effect of reducing vibration and noise of the refrigerant.

In the rotary compressor according to the present embodiment, a valve fixing part and a retainer part may be formed on the partition wall extending in the longitudinal direction of the discharge valve. Through this, it is possible to simplify the manufacturing process by excluding a separate valve retainer while easily fixing the discharge valve.

In the rotary compressor according to the present embodiment, a plurality of partition walls are formed to be spaced apart by a predetermined interval along the discharge space, and a communication part may be formed in one partition wall so that both spaces communicate with each other. Through this, the discharge space is divided into a plurality of chambers to more effectively attenuate vibration noise.

The rotary compressor according to the present embodiment may be formed by connecting an outer wall surface and an inner wall surface of the discharge muffler body portion in which the partition wall forms the discharge space. Through this, it is possible to secure rigidity while closely partitioning the discharge space.

In the rotary compressor according to the present embodiment, the valve accommodating part is formed to protrude outward from the outer wall surface of the discharge muffler body part, and one end of the discharge valve may be inserted into the valve accommodating part. Through this, the discharge valve can be installed inside the discharge space without increasing the overall size of the discharge muffler, thereby reducing the size of the compressor.

In addition, the rotary compressor according to the present embodiment, by elastically supporting the rotary type compressor body with respect to the shell forming the exterior, it is possible to reduce the vibration noise of the compressor by blocking the vibration transmitted from the compressor body from being transmitted to the shell. Through this, the volume and weight of the rotary compressor can be reduced, and the number of parts can be reduced, thereby lowering the manufacturing cost.

In addition, since the rotary compressor according to the present embodiment is configured as a low pressure type, the electric part can be rapidly cooled by the cold refrigerant sucked into the inner space of the shell. Through this, the motor efficiency can be increased to improve the compressor performance.

In addition, the rotary compressor according to the present embodiment is configured as an upper compression type, so that the loop pipe constituting the discharge flow path can be installed to be separated without being submerged in the oil filled in the inner space of the shell. Through this, it is possible to prevent the oil inside the shell from being heated by the high-temperature refrigerant discharged through the loop pipe in advance, thereby suppressing the viscosity of the oil from lowering and reducing frictional losses on each bearing surface of the compressor body.

In addition, the rotary compressor according to this embodiment is of a low pressure type and an upper compression type, and by having an oil supply guide and an oil supply passage in the compressor body, pumps the oil stored in the shell to the upper end of the compression unit, and supplies the oil with the oil supply guide and oil supply Through the passage, it is possible to supply smoothly and quickly to the sliding part of the compression part. As a result, oil is smoothly supplied between the vanes and the vane slots constituting the bearing surface of the compressor body or between the vanes and the rollers, thereby reducing friction loss due to insufficient oil on each bearing surface.

1 is an exploded perspective view showing the compressor body in the rotary compressor according to the present embodiment;
2 is a perspective view showing the compressor body assembled in FIG. 1;
3 is a cross-sectional view showing the inside of the rotary compressor according to FIG. 2;
4 is a plan view showing the inside of the compression unit in FIG. 3;
5 is a perspective view showing the compression part in breakage to explain the oil supply part in FIG. 1;
6 is a cross-sectional view showing the operation of the non-return valve for opening and closing the oil supply passage in FIG. 5;
Figure 7 is a perspective view shown to explain another embodiment for the oil supply guide in Figure 5;
8 is a perspective view showing the discharge muffler in FIG. 1 disassembled from the compression unit;
9 is a perspective view showing the discharge muffler from the lower side in FIG. 8;
10 is a plan view showing the discharge muffler assembling the compression unit in FIG. 8;
11 is a cross-sectional view IV-IV of FIG. 10;
12 is a V-V front sectional view of FIG. 10;
13 is an exploded perspective view showing another embodiment of the discharge muffler in FIG. 8;
14 is a cross-sectional view VI-VI of FIG. 13;
15 is a perspective view showing another embodiment of the discharge muffler in FIG. 8 from the bottom;
16 is a plan view showing the discharge muffler assembling the compression unit in FIG. 16;
17 is a perspective view showing another embodiment of the discharge muffler in FIG. 8 from the bottom;
18 is a plan view showing the discharge muffler of FIG. 17 assembling the compression unit;

Hereinafter, a rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. In this specification, the same or similar reference numerals are assigned to the same and similar components even in different embodiments, and the description is replaced with the first description.

In addition, the rotary compressor may be divided into a contact rotary compressor and a hinged vane rotary compressor according to the presence or absence of coupling between the roller and the vane. The contact rotary compressor is a method in which the vanes are in sliding contact with the rollers, and the hinged vane rotary compressor is a method in which the vanes are hinged to the rollers.

Although this embodiment describes a rotary compressor to which the hinge vane method is applied, the present invention is not limited thereto, and all known rotary compressors may be applied. However, hereinafter, since a hinge vane type rotary compressor is described as a representative example, it may be understood that the rotary compressor is defined by abbreviating the hinge vane rotary compressor unless otherwise specified in the description below.

1 is an exploded perspective view showing the compressor body in the rotary compressor according to this embodiment, FIG. 2 is a perspective view showing the compressor body assembled in FIG. 1, and FIG. 3 is a cross-sectional view showing the inside of the rotary compressor according to FIG. 4 is a plan view showing the inside of the compression unit in FIG. 3 , FIG. 5 is a perspective view showing the compression unit in FIG. 1 by breaking it to explain the oil supply unit, and FIG. 6 is a non-return valve for opening and closing the oil supply passage in FIG. 5 . It is a cross-sectional view shown to explain the operation of, Figure 7 is a perspective view shown to explain another embodiment for the oil supply guide in Figure 5.

1 to 7 , the rotary compressor according to the present embodiment includes a shell 110 forming an external appearance, a compressor body C provided in an inner space 110a of the shell 110, and a compressor body C ) to the shell 110, the support 150, the suction/discharge unit 160 for guiding the refrigerant to the compressor body (C) and discharging the compressed refrigerant, and the oil contained in the oil reservoir of the shell 110 to the compressor body (C) includes an oil supply unit 170 for supplying. The compressor body (C) is coupled to the electric part 120 for providing a driving force, the electric part 120, the rotational shaft 130 and the electric motor for transmitting the rotational force generated in the electric part 120 to the compression part 140 to be described later. It includes a compression unit 140 for compressing the refrigerant by receiving the driving force from the eastern part (120).

The shell 110 has the inner space 110a sealed, so that the compressor body C, the support part 150, the suction/discharge part 160 and the oil supply part 170 are accommodated. The shell 110 is made of an aluminum alloy (hereinafter, abbreviated as aluminum) which is light and has a high thermal conductivity, and includes a lower shell 111 and an upper shell 112 .

The lower shell 111 is formed in a substantially hemispherical shape. A suction pipe 115 , a discharge pipe 116 , and a process pipe 117 are respectively penetrated and coupled to the lower shell 111 . The suction pipe 115 , the discharge pipe 116 , and the process pipe 117 may be coupled to the lower shell 111 by an insert die casting method, respectively.

The upper shell 112 is formed in a substantially hemispherical shape like the lower shell 111 . The upper shell 112 is coupled to the lower shell 111 from the upper side of the lower shell 111 to form the inner space 110a of the shell 110 .

In addition, the upper shell 112 may be joined to the lower shell 111 by welding, but when the lower shell 111 and the upper shell 112 are formed of an aluminum material that is difficult to weld, they may be bolted together.

Next, the electric part will be described.

The electric part 120 according to the present embodiment includes a stator 121 and a rotor 122 .

The stator 121 is spaced apart from the inner circumferential surface of the shell 110 and is elastically supported against the inner space 110a of the shell 110 , that is, the bottom surface of the lower shell 111 , and the rotor 122 is the stator 121 . ) is rotatably installed inside the

The stator 121 according to the present embodiment includes a stator core 1211 and a stator coil 1212 .

The stator core 1211 is made of a metal material such as an electrical steel plate, and when a voltage is applied to the electric part 120 from the outside, the stator coil 1212 and the rotor 122, which will be described later, interact with each other through electromagnetic force. carry out

In addition, the stator core 1211 is formed in a substantially rectangular cylindrical shape. For example, the inner circumferential surface of the stator core 1211 may be formed in a circular shape, and the outer circumferential surface may be formed in a rectangular shape. Bolt holes (not shown) are formed through each of the four corners of the stator core 1211, and fixed self-fastening bolts (not shown) pass through each bolt hole, respectively, and are fastened to the main bearing 141 to be described later. Accordingly, the stator core 1211 is fixed to the lower surface of the main bearing 141 by the fixing self-fastening bolts.

In addition, in a state where the stator core 1211 is spaced apart from the inner circumferential surface of the shell 110 in the axial and radial directions, the lower end of the stator core 1211 is attached to a support spring 152 to be described later with respect to the bottom surface of the shell 110 . supported by Accordingly, the vibration generated during operation may be suppressed from being directly transmitted to the shell 110 .

The stator coil 1212 is wound inside the stator core 1211 . As described above, when a voltage is applied from the outside, the stator coil 1212 generates an electromagnetic force to perform electromagnetic interaction with the stator core 1211 and the rotor 122 . Through this, the electric unit 120 generates a driving force for the reciprocating motion of the compression unit 140 .

An insulator 1213 is disposed between the stator core 1211 and the stator coil 1212 . Accordingly, by suppressing direct contact between the stator core 1211 and the stator coil 1212, electromagnetic interaction may be smoothly performed.

The rotor 122 according to this embodiment includes a rotor core 1221 and a magnet 1222 .

The rotor core 1221, like the stator core 1211, is made of a metal material such as an electrical steel sheet, and is formed in a substantially cylindrical shape. A rotation shaft 130 to be described later may be press-fitted to the center of the rotor core 1221 . The rotating shaft 130 is radially supported at both ends in the axial direction with respect to the eccentric portion 134 by a main bearing 141 and a sub bearing 142 to be described later, and the rotating shaft 130 will be described later. .

The magnet 1222 is made of a permanent magnet, and may be inserted and coupled at equal intervals along the circumferential direction of the rotor core 1221 . The rotor 122 rotates through electromagnetic interaction with the stator core 1211 and the stator coil 1212 when a voltage is applied. Accordingly, while the rotation shaft 130 rotates together with the rotor 122 , the rotational force of the transmission unit 120 is transmitted to the compression unit 140 .

Next, the compression unit will be described.

3 and 4 , the compression unit 140 according to the present embodiment includes a main bearing 141 , a sub bearing 142 , a cylinder 143 , and a vane roller 144 .

The main bearing 141 and the sub bearing 142 are provided on both sides of the axial direction with the cylinder 143 interposed therebetween to form a compression chamber V inside the cylinder 143 .

In addition, the main bearing 141 and the sub-bearing 142 radially support the lower end and the upper end of the rotating shaft 130 on both sides of the cylinder 143 in the axial direction. The vane roller 144 is coupled to the eccentric portion 134 of the rotating shaft 130 to compress the refrigerant while rotating in the cylinder 143 .

The main bearing 141 may have a main plate portion 1411 formed in a disk shape, and a stator fixing protrusion 1412 may be formed at an edge of the main plate portion 1411 . The stator fixing protrusion 1412 may be formed to protrude downward from the four corners of the main plate portion 1411 toward the transmission unit 120 .

In addition, the stator fixing protrusion 1412 is fastened to the stator 121 by a fixing self-fastening bolt (unsigned), and may be elastically supported by the lower shell 111 together with the stator 121 of the transmission unit 120 .

In the center of the main plate part 1411, a main bearing protrusion 1413 is formed to protrude downward toward the electric part 120, and the main bearing protrusion 1413 has a main bearing part 132 of the rotating shaft 130 to be described later. A main bearing hole 1413a may be formed therethrough to be inserted and supported.

The sub-bearing 142 may have a sub-plate portion 1421 formed in a disk shape, and may be bolted to the main bearing 141 together with the cylinder 143 . Of course, when the cylinder 143 is fixed to the shell 110 , the main bearing 141 may be bolted to the cylinder 143 together with the sub bearing 142 , respectively, and the sub bearing 142 is the shell 110 . ), the cylinder 143 and the main bearing 141 may be bolted to the sub bearing 142 .

In the center of the sub-plate part 1421, a sub-bearing protrusion 1422 protrudes upward toward the upper surface of the shell 110, and the sub-bearing protrusion 1422 has a sub-bearing hole 1422a and the same as the main bearing hole 1413a. It is formed by penetrating on the axis. The sub-bearing hole 1422a supports the upper end of the rotation shaft 130 .

Referring back to FIG. 4 , the cylinder 143 is formed in an annular shape. The inner circumferential surface of the cylinder 143 is formed in a perfect circle shape having the same inner diameter. The inner diameter of the cylinder 143 is formed larger than the outer diameter of the roller (1441). Accordingly, a compression chamber V is formed between the inner peripheral surface of the cylinder 143 and the outer peripheral surface of the roller 1441 .

For example, the inner circumferential surface of the cylinder 143 is the outer wall surface of the compression chamber V, the outer circumferential surface of the roller 1441 is the inner wall surface of the compression chamber V, and the vane 1445 is the compression chamber V side. Each wall can be formed. Therefore, as the roller 1441 rotates, the outer wall surface of the compression chamber V forms a fixed wall, while the inner wall surface and the side wall surface of the compression chamber V form a variable wall whose position is variable. have.

A suction port 1431 is formed in the cylinder 143, a vane slot 1432 is formed on one side in the circumferential direction of the suction port 1431, and a discharge guide groove is formed on the opposite side of the suction port 1431 with the vane slot 1432 interposed therebetween. (1433) is formed.

The suction port 1431 may be formed so as to radially penetrate the inner circumferential surface from the outer circumferential surface of the cylinder 143 . The suction port 1431 may be formed to have a single inner diameter. However, when the outlet extension portion 1613a is formed at the outlet end of the suction muffler 161 to be described later, the extension portion insertion groove 1431a may be stepped on the outer peripheral side of the suction port 1431 so that the outlet extension portion is inserted. have. Accordingly, even when the outlet extension portion 1613a provided at the outlet end of the suction muffler 161 is inserted into the suction port 1431 , the reduction in the inner diameter of the suction port 1431 can be suppressed to secure the refrigerant suction amount.

In addition, a muffler mounting groove 1435 into which a suction muffler outlet 1613 to be described later is inserted and coupled may be formed on the outer periphery of the suction port 1431 . The muffler mounting groove 1435 may be formed by being depressed in the radial direction from the outer circumferential surface of the cylinder 143 .

For example, the muffler mounting groove 1435 may be formed in a substantially hexahedral shape to correspond to the suction muffler outlet 1613 . Specifically, the muffler mounting groove 1435 has both sides in the circumferential direction and a radially inner surface facing the suction port 1431 are each formed in a closed shape, and both axial side surfaces and the radially outer surface are formed in an open shape, respectively. can

Here, the blocked side surfaces of the muffler mounting groove 1435 form a support surface for supporting the side surfaces of the suction muffler outlet 1613 facing the muffler mounting groove 1435 . For example, both sides of the muffler mounting groove 1435 in the circumferential direction form a first muffler support surface 1435a, and the inner surface of the muffler mounting groove 1435 forms a second muffler support surface 1435b. .

Accordingly, the suction muffler outlet 1613, which will be described later, may be inserted and coupled from the outer circumferential side to the inner circumferential side of the muffler mounting groove 1435 . In addition, as both the upper and lower axial sides of the muffler mounting groove 1435 are opened, the cross-sectional area of the suction muffler outlet 1613 is made as large as possible, so that the flow path area of the suction muffler outlet 1613 is maximized. can The muffler mounting groove 1435 will be described again later with the suction muffler 161 .

The vane slot 1432 is elongated in a direction toward the outer circumferential surface on the inner circumferential surface of the cylinder 143 . The inner circumferential side of the vane slot 1432 is opened, and the outer circumferential side is formed to be blocked or blocked by the inner circumferential surface of the shell 110 .

The vane slot 1432 is formed to have a width approximately similar to the thickness or width of the vane 1445 so that the vane 1445 of the vane roller 144 to be described later can slide. Accordingly, both sides of the vane 1445 are supported by both inner wall surfaces of the vane slot 1432 and slide in a substantially straight line.

The discharge guide groove 1433 is formed by chamfering the inner edge of the cylinder 143 in a hemispherical shape. The discharge guide groove 1433 serves to guide the refrigerant compressed in the compression chamber V of the cylinder 143 to the discharge port 1423 of the sub-bearing 142 . Accordingly, the discharge guide groove 1433 is formed at a position overlapping the discharge port 1423 when projected in the axial direction so as to communicate with the discharge port 1423 .

However, since the discharge guide groove 1433 generates a dead volume, it is preferable not to form the discharge guide groove 1433 as much as possible. .

Meanwhile, compression chamber sealing grooves (unsigned) are formed on both upper and lower sides of the cylinder 143 , and a first sealing member 1461 made of an O-ring or gasket may be inserted into the compression chamber sealing groove.

For example, the first sealing member 1461 may be formed in an annular shape and installed along the periphery of the compression chamber (V). Specifically, the first sealing member 1461 surrounds the outer periphery of the vane slot 1432 and the outer periphery of the discharge guide groove 1433, and seals between the inner periphery of the muffler mounting groove 1435 and the compression chamber (V). It can be installed through the face.

Accordingly, the first sealing member 1461, including the vane slot 1432 and the discharge guide groove 1433, encloses and seals the compression chamber V, and at the same time seals between the compression chamber V and the muffler mounting groove 1435. separated and sealed. Through this, it is possible to suppress leakage of the high-pressure refrigerant compressed in the compression chamber V into the internal space 110a of the shell 110 constituting the relatively low-pressure part.

The first sealing member 1461 may be installed on both sides of the cylinder 143 in the axial direction, but in some cases, it is installed on the main bearing 141 or the sub bearing 142 facing both sides of the cylinder 143 . it might be

Meanwhile, the vane roller 144 includes a roller 1441 and a vane 1445 as described above. The roller 1441 and the vane 1445 may be formed as a single body, or may be combined to perform a relative motion. Hereinafter, the present embodiment will be mainly described with respect to an example in which the roller and the vane are rotatably coupled.

Referring back to FIG. 4 , the roller 1441 is formed in a cylindrical shape. The roller 1441 may be formed in a perfect circle shape having the same center as the inner circumferential surface and the outer circumferential surface, or may be formed in a perfect circle shape in which the inner circumferential surface and the outer circumferential surface of the roller 1441 have different centers.

In addition, the axial height of the roller 1441 is formed to be substantially equal to the height of the inner peripheral surface of the cylinder (143). However, since the roller 1441 must slide with respect to the main bearing 141 and the sub-bearing 142 , the axial height of the roller 1441 may be formed to be slightly smaller than the height of the inner circumferential surface of the cylinder 143 .

In addition, the inner peripheral height and the outer peripheral height of the roller 1441 is formed to be substantially the same. Accordingly, both axial end surfaces connecting between the inner peripheral surface and the outer peripheral surface of the roller 1441 form a sealing surface, respectively. These sealing surfaces are at right angles to the inner circumferential surface or the outer circumferential surface of the roller 1441, respectively. However, the edge between the inner circumferential surface of the roller 1441 and each sealing surface or the edge between the outer circumferential surface of the roller 1441 and each sealing surface may be slightly inclined or curved.

In addition, the roller 1441 is rotatably inserted and coupled to the eccentric portion 134 of the rotating shaft 130, and the vane 1445 is slidably coupled to the vane slot 1432 of the cylinder 143 to the roller 1441. is hinged to the outer circumferential surface of the Accordingly, when the rotating shaft 130 rotates, the roller 1441 makes a reciprocating motion inside the cylinder 143 by the eccentric part 134 and the vane 1445 is coupled to the roller 1441. will do

Also, the rollers 1441 may be aligned to be co-center with respect to the cylinder 143, but may be aligned slightly eccentrically in some cases.

In addition, the roller 1441 is formed in an annular shape so that its inner circumferential surface has an inner diameter sufficient to be in sliding contact with the outer circumferential surface of the eccentric portion 134 of the rotation shaft 130 . The radial width (thickness) of the roller 1441 is formed to a thickness sufficient to secure a sealing distance from the hinge groove 1411 to be described later.

In addition, the thickness of the roller 1441 may be uniformly formed along the circumferential direction, or may be formed differently in some cases. For example, the inner peripheral surface of the roller 1441 may be formed in an elliptical shape.

However, in order to minimize the load during rotation of the rotating shaft 130, the inner and outer peripheral surfaces of the roller 1441 are formed in a round shape having the same center, and the radial thickness of the roller 1441 is uniformly formed along the circumferential direction. may be desirable.

In addition, one hinge groove 1411 is formed on the outer peripheral surface of the roller 1441 so that a vane hinge portion 1445b of a vane 1445 to be described later is inserted and rotated. The hinge groove 1411 is formed in an arc shape with an open outer circumferential surface.

The inner diameter of the hinge groove 1411 is formed to be larger than the outer diameter of the vane hinge portion 1445b, and is formed to a size sufficient to slide without falling out while the vane hinge portion 1445b is inserted.

Meanwhile, referring back to FIG. 4 , the vane 1445 includes a vane body portion 1445a and a vane hinge portion 1445b.

The vane body portion 1445a is a portion constituting the vane body, and is formed in a flat plate shape having a predetermined length and thickness. For example, the vane body portion 1445a is generally formed in a rectangular hexahedral shape. In addition, the vane body portion 1445a is formed with a length such that the vane 1445 remains in the vane slot 1432 even in a state in which the roller 1441 has completely moved to the opposite side of the vane slot 1432 .

The vane hinge portion 1445b is formed to extend to the front end of the vane body portion 1445a facing the roller 1441 . The vane hinge portion 1445b is inserted into the hinge groove 1411 and has a rotatable cross-sectional area. The vane hinge portion 1445b may be formed in a semi-circular shape or a substantially circular cross-sectional shape excluding the connecting portion to correspond to the hinge groove 1411 .

Next, the support part will be described.

Referring back to FIG. 3 , the support part 150 according to the present embodiment includes a spring cap 151 and a support spring 152 . The support part 150 supports between the lower surface of the electric part and the bottom surface of the lower shell 111 facing it, and generally supports the four corners of the electric part 120 with respect to the shell 110 . Accordingly, the support unit 150 forms a support unit as a pair of the spring cap 151 and the support spring 152 so that each support unit supports the four corners of the compressor body C. Hereinafter, a pair of support units will be described as a representative example.

The spring cap 151 according to the present embodiment is fixed to the first spring cap 1511 fixed to the bottom surface of the lower shell 111 and the lower surface of the electric part 120 (to be precise, the lower surface of the stator core). It may be formed of a second spring cap 1512 .

The first spring cap 1511 and the second spring cap 1512 may be disposed on a coaxial line in the axial direction, or may be disposed on different axial lines in some cases. When the first spring cap 1511 and the second spring cap 1512 are arranged on different axial lines, it is advantageous to arrange the second spring cap 1512 to be positioned outside the first spring cap 1511 . .

Each of the first spring cap 1511 and the second spring cap 1512 may be formed of a rubber material, or may be formed by being wrapped around an outer circumferential surface of a metal material with a rubber or plastic material in consideration of installation rigidity and cushioning.

For example, since the first spring cap 1511 is inserted into the cap fixing groove (not shown) in the metal lower shell 111 to be firmly fixed, it may be formed of a metal material. However, since the second spring cap 1512 is inserted into and fixed to the bolt head (not shown) of the fixing self-fastening bolt (not shown) protruding in the axial direction from the lower surface of the stator core 1211, it may be formed of a rubber or plastic material. can

The support spring 152 may be formed of a compression coil spring. One end of the support spring 152 may be inserted into and fixed to the first spring cap 1511 , and the other end of the support spring 152 may be inserted and fixed into the second spring cap 1512 . Accordingly, the stator core 1211 may be elastically supported by the shell by the support spring 152 .

Next, the suction/discharge part will be described.

Referring back to FIGS. 1 to 4 , the suction/discharge unit 160 according to the present embodiment includes a suction muffler 161 and a discharge muffler 162 . The suction muffler 161 may be coupled to the outer circumferential surface of the cylinder 143 , and the discharge muffler 162 may be coupled to the upper surface of the sub-bearing 142 . Accordingly, the suction muffler 161 is located below the sub-bearing 142 , and the discharge muffler 162 is located above the sub-bearing 142 .

In addition, the inlet of the suction muffler 161 is spaced apart from the inner circumferential surface of the shell 110 and communicates with the inner space 110a of the shell 110 , and the outlet of the suction muffler 161 communicates with the suction port 1431 to the compression chamber. It can be directly connected to (V). Accordingly, the refrigerant sucked through the suction pipe 115 flows into the suction muffler 161 through the inner space 110a of the shell 110, and the refrigerant flows into the compression chamber V through the suction muffler 161. is inhaled with

In addition, the inlet of the discharge muffler 162 is coupled to the sub bearing 142 to directly communicate with the discharge port 1423 , and the outlet of the discharge muffler 162 is connected to the roof pipe 118 and directly to the discharge pipe 116 . can be connected Accordingly, the roof pipe 118 connects between the discharge muffler 162 and the discharge pipe 116 at a position higher than the oil level of the oil filled in the inner space 110a of the shell 110, and thereby the compression chamber ( The refrigerant discharged from V) is discharged to the outside of the compressor through the discharge muffler 162 , the loop pipe 118 , and the discharge pipe 116 without heating the oil in the inner space 110a of the shell 110 .

A detailed look at the suction muffler and the discharge muffler is as follows. The suction muffler will be described first.

1 to 4 , the suction muffler 161 according to the present embodiment may include a suction muffler body 1611 , a suction muffler inlet 1612 , and a suction muffler outlet 1613 . have. The suction muffler 161 may have a suction space 1611a to be described later formed therein by assembling a plurality of members. In this embodiment, the suction muffler 161 may be formed by assembling the lower muffler and the upper muffler.

A suction space 1611a having a predetermined volume is formed inside the suction muffler body 1611 . The suction muffler body 1611 may be formed as a single member, or may be formed by assembling a plurality of members. However, since the suction muffler body 1611 needs to have a suction space 1611a therein, it may be formed by assembling a plurality of members.

The inside of the suction space 1611a may be formed as a single space, but may be formed to have a plurality of spaces or flow paths in order to increase the noise attenuation effect. For this, it may be formed according to the internal shape of a conventional muffler.

The suction muffler inlet 1612 may communicate with the lower half of the suction space 1611a. In addition, as the suction muffler 161 is disposed adjacent to the outer circumferential surface of the compressor body C including the electric part, the suction muffler inlet 1612 may be preferably formed on the outer surface of the suction muffler body 1611. have.

The suction muffler inlet 1612 may be preferably formed eccentrically to one side in the circumferential direction to secure the length of the suction passage. Accordingly, the suction muffler outlet 1613 to be described later may be eccentrically formed on the opposite side of the suction muffler inlet 1612 in the circumferential direction.

The suction muffler outlet 1613 may communicate with the upper half of the suction space 1611a. The suction muffler outlet 1613 may be formed successively to the suction muffler body 1611 . However, the outlet portion 1613 of the suction muffler is coupled to the outer circumferential surface of the cylinder 143 , and the main bearing 141 is positioned below the cylinder 143 . Then, when the suction muffler outlet 1613 is formed successively to the suction muffler body 1611 , the suction muffler body 1611 should be installed at a radially widened position avoiding interference with the main bearing 141 . Then, the lateral diameter of the compressor may increase, making it difficult to downsize the compressor.

Accordingly, the suction muffler body 1611 and the suction muffler outlet 1613 may be connected by the suction muffler connection unit 1614 . The suction muffler connecting portion 1614 may be formed to be long like a neck portion of a kind of muffler.

The suction muffler connection part 1614 may be formed to be inclined in a direction from the suction muffler body part 1611 toward the cylinder 143 . Accordingly, the flow resistance of the refrigerant from the suction muffler main body 1611 to the suction muffler outlet 1613 is reduced, so that the refrigerant can be smoothly sucked into the suction port 1431 of the cylinder 143 .

Meanwhile, the suction muffler outlet 1613 may be formed to correspond to the cross-sectional shape of the muffler mounting groove 1435 of the cylinder 143 . For example, the suction muffler outlet 1613 may have a substantially rectangular cross-sectional shape when projected in a radial direction. Accordingly, both sides of the suction muffler outlet 1613 in the circumferential direction may be respectively closely adhered to and supported in the circumferential direction of the muffler mounting groove 1435 in the circumferential direction.

Also, on both sides of the suction muffler outlet 1613 in the circumferential direction, a muffler fixing unit 1615 may be formed to extend in the circumferential direction. The muffler fixing part 1615 may be formed in a curved shape having the same curvature as that of the outer circumferential surface of the cylinder 143 . Accordingly, the muffler fixing part 1615 may be fixed in close contact with the outer circumferential surface of the cylinder 143 .

In addition, a fastening hole 1615a is formed in the muffler fixing part 1615 , and a fastening groove 143a may be formed on the outer peripheral surface of the cylinder 143 facing the fastening hole 1615a. Accordingly, the muffler fixing part 1615 is fastened by the muffler fastening bolt 1616 that penetrates the fastening hole 1615a and is fastened to the fastening groove 143a, and then the suction muffler 161 is stably attached to the cylinder 143. can be fastened and fixed.

In addition, a muffler sealing member 1617 may be provided between the suction muffler outlet 1613 and the inner surface of the muffler mounting groove 1435 of the cylinder 143 facing the same in the radial direction. The muffler sealing member 1617 is formed of an O-ring or a flat gasket, and when an outlet extension part 1613a to be described later is formed in the suction muffler outlet part 1613, it wraps around the outlet extension part 1613a and the suction muffler outlet part ( 1613) and the inner surface of the muffler mounting groove 1435 may be in close contact.

Accordingly, a part of the oil in the shell 110 inner space 110a (for example, oil flowing into the oil supply passage hole 1771 of the oil supply unit 170 to be described later) is partially transferred to the suction muffler 161 and the cylinder 143 . ) through the gap between the intake port 1431 can be suppressed.

On the other hand, an outlet extension portion 1613a may be formed to extend toward the cylinder 143 at the suction muffler outlet portion 1613 . The outlet extension portion 1613a is formed in a cylindrical shape, and may be radially supported by being inserted into the extension portion insertion groove 1431a of the suction port 1431 described above. Accordingly, when the suction muffler 161 is inserted into the muffler mounting groove 1435 to be coupled, the assembly position of the suction muffler 161 is easily aligned and the refrigerant between the suction muffler 161 and the suction port 1431 . It can effectively block leakage or oil inflow.

Meanwhile, although not shown in the drawings, it is possible to fix the front end surface of the suction muffler outlet 1613 in close contact with the outer circumferential surface of the cylinder 143 without forming a muffler mounting groove in the cylinder 143 .

In addition, in the above-described embodiment, the muffler fixing part 1615 is integrally extended to the suction muffler 161, but in some cases, a separate muffler fastened to the cylinder 143 without integrally forming the muffler fixing part. The suction muffler 161 may be fixed to the cylinder 143 using a fixing member (not shown).

Next, the discharge muffler will be described.

1 and 5 , the discharge muffler 162 according to the present embodiment includes a discharge muffler body 1621 having a discharge space 1621a to accommodate the discharge port 1423 , and a discharge muffler body 1621 . ) and includes a discharge muffler fixing part 1622 that is extended from and fixed to the upper surface of the sub-bearing 142 .

A refrigerant discharge hole 1628a to which the loop pipe 118 is connected may be formed on the outer peripheral surface of the discharge muffler body 1621 . Accordingly, the refrigerant discharged to the discharge space 1621a moves to the condenser through the loop pipe 118 and the discharge pipe 116 while the discharge noise is canceled in the discharge space 1621a.

In addition, the sub-bearing protrusion 1422 may be inserted and coupled to the inner circumferential surface of the discharge muffler body 1621 . The central portion of the upper surface of the discharge muffler body 1621 extending from the inner circumferential surface of the discharge muffler body 1621 is opened, and the upper end of the rotation shaft 130 is opened to the outside of the discharge muffler 162 . Accordingly, the upper end of the rotary shaft 130 in which the oil pumping hole 1371, which will be described later, is formed is opened to the outside of the discharge muffler 162, and the oil transferred through the oil pumping hole 1371 is transferred to the outside of the discharge muffler 162. will be emitted as This oil is supplied to the rear side of the vane slot 1432 by an oil supply guide 176 to be described later. The discharge muffler 1621 will be described again later.

Next, the oil supply part will be described.

5 to 7 , the oil supply unit 170 according to the present embodiment includes an oil pumping unit 171 and an oil supply guide unit 175 .

The oil pumping unit 171 is a part that pumps oil stored in the inner space 110a of the shell 110 and supplies it to the bearing surface or the compression unit, and the oil pumping unit 171 according to this embodiment is an oil pumping passage ( 172) and an oil pump 173.

The oil pumping passage 172 is a part for guiding the pumped oil to the main bearing part 132 and the sub bearing part 133 of the rotary shaft 130, and the oil pumping passage 172 is an oil pumping hole 1721, oil supply. It includes a hole 1722 , a first oil supply groove 1723 , a second oil supply groove 1724 , and a third oil supply groove 1725 .

The oil pump 173 is provided at the lower end of the rotating shaft 130 to pump the oil stored in the inner space 110a of the shell 110 to the oil pumping passage 172, and the oil pump 173 according to the present embodiment. ) may consist of a centrifugal pump. However, the oil pump 173 is not necessarily limited to only a centrifugal pump, and in some cases, a gear pump, a viscous pump, etc. to be described later may be applied. However, when the oil pump 173 is a centrifugal pump, it includes a pump housing 1731 and a pump blade 1732 . The oil pumping unit including the oil pump according to the present embodiment will be described again later along with the rotating shaft.

The oil supply guide 175 is a part for guiding the oil pumped by the oil pumping unit to the compression unit, and the oil supply guide 175 according to this embodiment includes the oil supply guide 176 and the oil supply passage 177 . .

The oil supply guide 176 serves to collect the oil scattered from the upper end of the rotation shaft 130 , and the oil supply passage 177 is connected to the oil supply guide 176 to guide the oil to the corresponding position. Accordingly, based on the flow order of the oil, the oil supply guide 176 is provided on the downstream side of the rotation shaft 130 , and the oil supply passage 177 is located on the downstream side rather than the oil supply guide 176 .

The oil supply guide 176 may be provided outside the upper wall surface of the discharge muffler 162 . The oil supply guide 176 may be integrally formed with the discharge muffler 162, and may be welded or fastened depending on the material. The oil supply guide 176 may be formed of metal or may be formed of a material such as plastic.

In addition, the oil supply guide 176 has an open lower surface in contact with the discharge muffler 162 , and the side and upper surfaces of the oil supply guide 176 may be formed in a closed shape so as to collect oil scattered from the upper end of the rotation shaft 130 . Accordingly, a portion of the side and the upper surface of the oil supply guide 176 may form an oil receiving space 1761 together with the upper surface of the discharge muffler 163 . However, the side of the side that faces the oil supply passage 177 among the side forming the oil receiving space 1761 may be opened to form a guide outlet 1762 .

On the outer circumferential surface of the guide outlet 1762, a refueling guide protrusion 1763 that forms a part of the refueling guide 175 may be formed. The oil supply guide protrusion 1763 may be provided between the oil supply guide 176 and the oil supply passage 177 . Accordingly, the oil collected by the oil supply guide 176 can be smoothly moved to the oil supply passage hole 1771 by the oil supply guide protrusion 1763 .

The oil supply guide protrusion 1763 may be formed to be symmetrical with each other at a predetermined interval along the circumferential direction. One end of the refueling guide protrusion 1763 has two refueling guide protrusions 1763 extending from both sides of the refueling guide 176, respectively, and at the other end of the refueling guide protrusion 1763, between the two refueling guide protrusions 1763. The oil supply passage hole 1771 may be formed to be accommodated. Accordingly, an oil supply passage is made between the oil supply guide 176 and the oil supply passage 177 by the oil supply guide protrusion 1763 of two pairs.

The oil supply guide protrusion 1763 according to this embodiment may be made of a first guide protrusion 1763a and a second guide protrusion 1763b. The oil supply guide protrusion 1763 may extend from the oil supply guide 176 and be formed to be seated on at least one of the outer surface of the discharge muffler 162 and the outer surface of the sub bearing 142, and the outer surface of the discharge muffler 162 and It may be formed to extend from at least one of the outer surfaces of the sub-bearing 142 . In this embodiment, the oil supply guide protrusion 1763 will be described mainly on an example extending from the oil supply guide 176.

The first guide protrusion 1763a may be continuously formed along the upper surface and the side surface of the discharge muffler 162 . The first guide protrusion 1763a may be integrally formed with the oil supply guide 176 as described above, or may be integrally formed with the outer surface of the discharge muffler 162 . In addition, the first guide protrusion 1763a may be post-assembled to the oil supply guide 176 or the discharge muffler 162 .

The second guide protrusion 1763b may be formed on the upper surface of the sub-bearing 142 in succession to the first guide protrusion 1763a. For example, the second guide protrusion 1763b may be formed to surround a portion of the circumference of the oil supply passage hole 1771 to be described later. Accordingly, the oil guided by the oil supply guide protrusion 1763 can move to the oil supply passage hole 1771 without flowing out to another place.

The oil supply passage 177 is formed through the sub bearing 142 and the cylinder 143 so as to supply the oil guided by the oil supply guide 176 to the rear of the compression unit 140 , precisely the vane slot 1432 . can be For example, the oil supply passage 177 may include an oil supply passage hole 1771 formed in the sub-bearing 142 .

The inlet end of the oil supply passage hole 1771 is opened toward the inner space 110a of the shell 110 so as to be exposed to the inner space 110a of the shell 110 . Accordingly, the inlet end of the oil supply passage hole 1771 communicates with the oil supply guide 176 through the inner space 110a of the shell 110 .

The outlet end of the oil supply passage hole 1771 communicates with the vane slot 1432 . However, when an oil supply storage groove 1772 to be described later is formed on the outer periphery of the vane slot 1432, the outlet end of the oil supply passage hole 1771 is communicated with the vane slot 1432 through the oil supply storage groove 1772. can

Accordingly, the oil receiving space 1761 of the oil supply guide 176 communicates with the vane slot 1432 through the oil supply passage hole 1771, and the oil collected by the oil supply guide 176 is the oil supply passage hole 1771. It may be supplied to the vane slot 1432 through.

The circumferential width of the oil supply passage hole 1771 may be formed wider than the circumferential width of the vane slot 1432 . Accordingly, the oil that is collected by the oil supply guide 176 and moves to the lower space of the shell 110 can be accommodated by the oil supply passage hole 1771 .

On the other hand, on the outer peripheral side of the vane slot 1432, the oil supply storage groove 1772 that is recessed by a predetermined width and depth may be formed.

The cross-sectional area of the oil supply storage groove 1772 may be formed to be substantially the same as the cross-sectional area of the oil supply passage hole 1771 , for example, wider than the vane slot 1432 . Accordingly, the oil moving to the oil supply passage hole 1771 is accommodated in the oil supply storage groove 1772, a certain amount of oil can always be stored in the rear of the vane slot 1432. While this oil is supplied to the compression chamber (V) through a gap between the vane 1445 and the vane slot 1432 during operation of the compressor, it is stored in the middle of the oil supply passage 177 when the compressor is stopped. When the compressor is restarted, it can be quickly supplied to the compression chamber (V).

For example, during the operation of the compressor, the vane 1445 moves forward and backward. When the vane 1445 moves backward toward the oil supply storage groove 1772, the pressure of the oil supply storage groove 1772 rises, and as the pressure of the oil supply storage groove 1772 rises, the oil supply storage groove 1772. The stored oil is rapidly moved to the inner periphery of the cylinder 143 through the gap between the vane 1445 and the vane slot 1432 , that is, to the side where the vane 1445 and the roller 1441 are connected. On the other hand, when the compressor is stopped, the cross-sectional area of the oil supply storage groove 1772 is relatively wide compared to the cross-sectional area of the vane slot 1432, and a certain amount of oil remains in the oil supply storage groove 1772, and this oil is transferred to the vane ( It can be quickly supplied between the 1445 and the vane slot 1432 .

In the drawings, unexplained reference numeral 135 denotes a roller alignment part, 136 denotes a friction avoidance, 1626a denotes a sub-bearing through hole, and 1721a and 1721b denote first and second pumping holes.

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

That is, when power is applied to the electric part 120 , the rotor 122 rotates. When the rotor 122 rotates, the rotation shaft 130 coupled to the rotor 122 rotates while transmitting the rotational force to the vane roller 144 coupled to the eccentric portion 134 of the rotation shaft 130 . .

Then, the roller 1441 of the vane roller 144 rotates, and the vane 1445 is inserted into the cylinder 143 and reciprocating while sucking the refrigerant into the compression chamber V of the cylinder 143 and compressing it. do.

The compressed refrigerant is continuously compressed by the rollers 1441 and the vanes 1445 of the vane roller 144 to open the discharge valve 145 provided in the main bearing 141 and the discharge muffler ( 162), the discharged refrigerant is discharged to the condenser constituting the refrigerating cycle through the loop pipe 118 and the discharge pipe 116, repeating a series of processes.

At this time, the oil stored in the inner space 110a of the shell 110 is pumped by the oil pump 173 provided at the lower end of the rotary shaft 130, and the pumped oil is pumped through the oil pumping passage 172 through the rotary shaft ( 130) is transferred towards the top.

A part of this oil passes through the oil supply hole 1722, the first oil supply groove 1723, the second oil supply groove 1724, and the third oil supply groove 1725 while passing through the main bearing surface (Mb) and the sub bearing surface (Sb). is supplied to The oil lubricating the main bearing surface Mb and the sub bearing surface Sb flows out from the upper end of the sub bearing 142 into the inside of the oil supply guide 176 , that is, into the oil receiving space 1761 .

On the other hand, the remaining oil transferred to the upper end of the rotary shaft 130 through the oil pumping passage 172 is scattered from the upper end of the rotary shaft 130, and this oil is transmitted by the upper surface of the discharge muffler 162 and the oil supply guide 176. It is collected in the formed oil receiving space 1761 .

As described above, the oil lubricating the bearing surfaces Mb (Sb) and the oil scattered from the rotary shaft 130 are the upper surface of the discharge muffler 162 and the sub bearing 142 through the guide outlet 1762 of the oil supply guide 176. ) and flows down the top surface of the

This oil is guided to the vane slot 1432 through the oil supply passage hole 1771 and the oil supply storage groove 1772 of the sub bearing 142, and the oil guided to the vane slot 1432 is the vane 1445 reciprocating motion. When moving toward the compression chamber (V) through the gap between the vane 1445 and the vane slot 1432, lubricating between the vane 1445 and the vane slot 1432 or the bearing surface of the roller 1451 to lubricate

In addition, as described above, as an oil supply storage groove 1772 is formed on the outer peripheral side of the vane slot 1432, a certain amount of oil is stored in the oil supply storage groove 1772, and the oil stored in the oil supply storage groove 1772 is a compressor. During operation, oil is continuously supplied to the compression chamber (V), and a certain amount of oil is stored even when the compressor is stopped. Through this, it is possible to reduce friction loss due to insufficient oil in the compression unit 140 including the vane 1445 and the vane slot 1432 .

On the other hand, in the rotary compressor according to the present embodiment, as the inner space 110a of the shell 110 is a low-pressure compressor constituting the low-pressure part, oil or refrigerant flows into the internal space 110a of the shell 110 in the compression part 140 . ), which may backflow or leak.

For example, as the pressure of the oil supply storage groove 1772 increases when the vane 1445 moves backward, some of the oil stored in the oil supply storage groove 1772 passes through the oil supply passage hole 1771 of the shell 110. A portion of the refrigerant that flows backward into the inner space 110a or is compressed in the compression unit 140 passes through a gap between the vane 1445 and the vane slot 1432 through the oil supply passage hole 1771 inside the shell 110. It may leak into the space 110a.

Accordingly, a non-return valve 1773 for opening and closing the oil supply passage hole 1771 forming the middle of the oil supply passage 177 may be installed as shown in FIG. 6 . The non-return valve 1773 is a reed valve having one end of a fixed portion 1773a fixed between the sub-bearing 142 and the cylinder 43, and the other end of the opening/closing portion 1773b for opening and closing the oil supply passage hole 1771. Shape or may be made of a ball valve inserted into the inside of the oil supply passage hole (1771).

Alternatively, as shown in FIG. 7 , between the guide outlet 1762 and the oil supply passage hole 1771 of the oil supply guide 176 may be sealed and connected with the oil supply guide pipe 1774 . The oil supply passage hole 1771 may be formed to communicate with the oil supply storage groove 1772 through both sides of the sub-bearing 142 in the axial direction, and penetrate the both sides of the cylinder 143 in the radial direction to penetrate the oil supply storage groove ( 1772) may be formed to communicate.

Through this, in this embodiment, the oil stored in the oil supply storage groove 1772 or a part of the refrigerant compressed in the compression unit is prevented from leaking into the inner space 110a of the shell 110 through the oil supply passage 177, Compressor performance can be improved.

In this way, it is possible to configure a spring-supported rotary compressor that elastically supports the compressor body comprising the electric part and the rotary compression part from the shell using a single shell in this way. Accordingly, it is possible to reduce the vibration noise of the compressor by preventing the vibration generated in the compressor body from being transmitted to the shell. Through this, it is possible to reduce the manufacturing cost by reducing the volume and weight of the compressor and reducing the number of parts while configuring the low-vibration rotary compressor.

In addition, by configuring a spring-supported rotary compressor of an upper compression type in which the compression part is located above the transmission part, the loop pipe constituting the discharge flow path inside the shell is discharged with the compression part without being submerged in the oil stored in the internal space of the shell. It can be installed to connect between pipes. Accordingly, it is possible to prevent in advance that the oil stored in the shell is heated by the high-temperature refrigerant discharged through the loop pipe. Through this, it is possible to reduce the friction loss on each bearing surface of the compressor body by suppressing the lowering of the viscosity of the oil.

In addition, by configuring the upper compression type rotary compressor, which is a low pressure method in which the inner space of the shell achieves suction pressure, the electric part is rapidly cooled by the cold refrigerant sucked into the inner space of the shell, thereby improving motor efficiency and compressor performance. have.

In addition, it is possible to smoothly supply the oil stored in the shell to the bearing surface and the compression part by using the oil pumping part and the oil supply guide part while configuring the low-pressure, spring-supported, and upper-compression rotary compressor. Through this, it is possible to reduce friction loss due to lack of oil in the bearing surface and the compression part.

Meanwhile, in the rotary compressor according to the present embodiment, vibration and noise may be generated due to pressure pulsation while the refrigerant compressed in the compression chamber is discharged. Accordingly, in this embodiment, as described above, since the discharge muffler is provided on the upper side of the compression unit, vibration and noise generated when the refrigerant is discharged can be attenuated.

FIG. 8 is a perspective view showing the discharge muffler in FIG. 1 being disassembled from the compression unit, FIG. 9 is a perspective view showing the discharge muffler from the lower side in FIG. 8, and FIG. , FIG. 11 is a cross-sectional view IV-IV of FIG. 10 , and FIG. 12 is a cross-sectional view taken along the line V-V of FIG. 10 .

8 to 12 , the discharge muffler 162 according to the present embodiment includes a discharge muffler body 1621 , a discharge muffler fixing unit 1622 , and a partition wall 1623 . The discharge muffler body 1621 is provided with a discharge space 1621a accommodating the discharge port 1423 , and the discharge muffler fixing unit 1622 extends from the discharge muffler body 1621 to the upper surface of the sub bearing 142 . It is fixed, and the partition wall 1623 may be formed to cross the middle of the discharge space and divide it into one or a plurality of chambers (unsigned).

The discharge muffler body 1621 includes an outer wall surface 1625 of an inner wall surface 1626 , and an upper wall surface 1627 connecting the outer wall surface 1625 and the inner wall surface 1626 . Accordingly, the outer wall surface 1625 forms the outer peripheral surface of the discharge space 1621a, the inner wall surface 1626 forms the inner peripheral surface of the discharge space 1621a, and the upper wall surface 1627 forms the upper surface of the discharge space 1621a. The space 1621a forms an annular space with an open lower surface.

The outer wall surface 1625 may be formed in a circular cross-sectional shape having the same inner diameter. However, in some cases, a plurality of curves may be combined to form a substantially petal shape.

A valve accommodating part 1628 is formed on one side of the outer wall surface 1625 , and fixed ends of the discharge valve 1451 and the valve retainer 1452 may be inserted into the valve accommodating part 1628 . The valve accommodating part 1628 may be formed to protrude outward so as to have a width and a height sufficient to insert the head of the fastening bolt 1453 for fastening the fixed end of the discharge valve 1451 .

The valve accommodating part 1628 has an inner peripheral side in communication with the discharge space 1621a, and a refrigerant discharge hole 1628a is formed through a main surface thereof. The end of the loop pipe 118 may be inserted and coupled to the refrigerant discharge hole 1628a. Accordingly, the refrigerant discharged to the discharge space 1621a may be guided to the discharge pipe 116 through the loop pipe 118 inserted into the refrigerant discharge hole 1628a.

Although not shown in the drawings, the refrigerant discharge hole 1628a is formed through the outer wall surface 1625 from the outside of the valve accommodating portion 1628 without penetrating the valve accommodating portion 1628, or through the upper wall 1627. may be formed.

The inner wall surface 1626 may be formed in a circular cross-sectional shape having the same inner diameter. The inner wall surface 1626 may be coupled to the inner peripheral surface through which the sub-bearing protrusion 1422 is penetrated. A second sealing member 1462 may be inserted between the inner peripheral surface of the inner wall surface 1626 and the outer peripheral surface of the sub-bearing protrusion 1442 facing it.

For example, a sealing groove 1422b is formed on the outer peripheral surface of the sub-bearing protrusion 1422 , and a second sealing member 1462 such as an O-ring may be inserted into the sealing groove 1422b. Accordingly, the inner peripheral side of the discharge space 1621a is tightly sealed, and the high-pressure refrigerant discharged into the discharge space 1621a can be suppressed from leaking between the inner wall surface 1626 and the outer peripheral surface of the sub-bearing protrusion 1422. .

The upper wall surface 1627 may be formed in an annular shape, so that the outer peripheral surface of the upper wall surface 1627 may be connected to the outer wall surface 1625 , and the inner peripheral surface of the upper wall surface 1627 may be connected to the inner wall surface 1626 . Accordingly, the outer diameter of the upper wall surface 1627 may be equal to the outer diameter of the outer wall surface 1625 , and the inner diameter of the upper wall surface 1627 may be equal to the inner diameter of the inner wall surface 1626 .

The discharge muffler fixing part 1622 according to the present embodiment may be formed as an annular plate. A plurality of bolt holes (unsigned) may be formed in the discharge muffler fixing part 1622 to be bolted to the sub-plate part 1421 of the sub-bearing 142 .

A third sealing member 1463 may be provided between the discharge muffler fixing part 1622 and the sub-plate part 1421 facing it. The third sealing member 1463 may be formed of a gasket, and may be formed of an annular plate having substantially the same width as the discharge muffler fixing part 1622 . Accordingly, the outer peripheral side of the discharge space 1621a is tightly sealed by the third sealing member 1463, and the high-pressure refrigerant discharged into the discharge space 1621a is discharged from the discharge muffler fixing part 1622 and the sub-plate part 1421. leakage can be prevented.

The partition wall 1623 according to the present embodiment is formed to extend as a single body from the outer wall surface 1625, the inner wall surface 1626, and the upper wall surface 1627 constituting the discharge space 1621a, and the lower surface thereof is the discharge space 1621a. ) can be formed approximately equal to the depth of the In other words, the lower end surface of the partition wall 1623 may be formed to be substantially the same as the lower end surface of the outer wall surface 1625 or the inner wall surface 1626 .

The partition wall 1623 may be formed on a line connecting the shortest distance between the discharge port 1423 and the refrigerant discharge hole (or the fixing point of the discharge valve) 1628a. For example, the partition wall 1623 may be provided across between the open/close end and the fixed end forming both ends of the discharge valve 1451 , or more precisely, between both ends of the valve retainer 1452 .

Specifically, a valve accommodating groove 1421a is formed in a rectangular shape on the upper surface of the sub-plate portion 1421, and at one end of the valve accommodating groove 1421a, a discharge port 1423 penetrates the sub-plate portion 1421 in the axial direction. is formed A valve accommodating extension groove 1421b is further formed to extend around the outlet 1423 corresponding to one end of the valve accommodating groove 1421a, and the other end of the valve accommodating groove 1421a corresponding to the opposite end of the outlet 1423 is a valve A fastening groove 1421c is formed.

The depth of the valve accommodating groove 1421a may be formed to a depth equal to the sum of the thickness of the discharge valve 1451 and the thickness of the valve retainer 1452 . Accordingly, the upper surface of the fixed side of the valve retainer 1452 achieves substantially the same height as the upper surface of the sub-plate portion 1421, and thus the partition wall 1623 forms a discharge space 1621a even though the bottom surface thereof forms the same plane. may be in close contact with the upper surface of the sub-plate portion 1421 and the upper surface of the valve retainer 1452 . Then, the partition wall 1623 partitions between the discharge port and the refrigerant discharge hole (to be more precise, the end of the loop pipe) 1628a, and the refrigerant discharged through the discharge port passes through the partition wall 1623 and is directly discharged to the refrigerant discharge hole 1628a. can be restrained

The partition wall 1623 may be formed in a direction perpendicular to an imaginary line connecting both ends of the discharge valve 1451 . Accordingly, it is possible to suppress the formation of a refrigerant stagnant space between the side surface of the partition wall 1623 and the outer wall surface 1625 and the inner wall surface 1626 connected thereto. For example, when the partition wall 1623 is formed to be inclined with respect to the above-described virtual line, one end of both ends of the partition wall 1623 is connected to the outer wall surface 1625 or the inner wall surface 1626 between the valleys. ), a hollow space may be formed. Then, the refrigerant may stagnate in this space and the compressor efficiency may be reduced. Therefore, as in the present embodiment, the partition wall 1623 may be preferably formed in a direction orthogonal to the above-described virtual line.

In addition, at one side of the partition wall 1623, that is, at the end of the side facing the refrigerant discharge hole 1628a, the discharge guide is curved with a predetermined curvature between the outer wall surface 1625 forming the discharge muffler body part 1621. A groove (unsigned) may be formed. Accordingly, it is possible to suppress the refrigerant flowing from the discharge space 1621a to the refrigerant discharge hole 1628a from being stagnant between the outer wall surface 1625 of the discharge muffler body 1621 and the partition wall 1623 .

For example, the partition wall 1623 may extend from one end adjacent to the discharge port 1423 to the inner wall surface 1621b of the discharge muffler body 1621 among both ends of the valve accommodating portion 1428 in the circumferential direction. Accordingly, it is possible to more effectively reduce the vibration noise of the refrigerant by locating the refrigerant discharge hole 1628a as far as possible from the discharge port 1423 .

In the discharge muffler 162 according to this embodiment, as the partition wall 1623 is formed in the discharge space 1621a, the refrigerant discharged to the discharge space 1621a through the discharge port 1423 circulates along the discharge space 1621a. After moving as if it can be discharged through the loop pipe 118 coupled to the refrigerant discharge hole (1628a).

Referring to FIG. 10 , the refrigerant discharged into the discharge space 1621a through the discharge port 1423 is blocked by the partition wall 1623 and cannot move directly from the discharge port 1423 to the adjacent refrigerant discharge hole 1628a. Then, the refrigerant moves in a direction away from the first side (discharge port side) of the partition wall 1623 through the valve accommodating extension groove 1421b extending along the periphery of the discharge port 1423 . This refrigerant is discharged through the loop pipe 118 coupled to the refrigerant discharge hole 1628a after moving toward the second side (refrigerant discharge hole side) of the partition wall 1623 by turning far along the discharge space 1621a.

At this time, as the refrigerant moves far away along the discharge space 1621a, vibration and noise generated when the refrigerant is discharged may be attenuated inside the discharge muffler 162 . Through this, the vibration noise of the compressor can be effectively reduced.

In addition, since the refrigerant flowing into the roof pipe 118 passes through the discharge muffler 162 , vibration noise is reduced, so that the vibration load applied to the roof pipe 118 can be reduced. Then, the damping effect in the loop pipe 118 is further improved, so that the vibration and noise damping effect of the compressor can be further improved.

In addition, as the vibration load applied to the loop pipe 118 decreases, the length of the loop pipe 118 can be reduced compared to the same condition, so that the installation of the loop pipe 118 is easier, such as reducing the number of bending of the loop pipe 118 . It can be easy. In addition, by suppressing the roof pipe 118 from being submerged in the oil inside the shell, it is possible to suppress overheating of the oil inside the shell.

On the other hand, another embodiment of the partition wall is as follows.

That is, in the above-described embodiment, the valve retainer is separately provided and fastened with a separate bolt together with the discharge valve. have.

13 is an exploded perspective view showing another embodiment of the discharge muffler in FIG. 8 , and FIG. 14 is a front cross-sectional view VI-VI of FIG. 13 .

13 and 14 , the partition wall 1623 according to the present embodiment may include a partition wall portion 1623a, a retainer portion 1623b, and a valve fixing protrusion 1623c.

The partition wall portion 1623a may be formed in substantially the same manner as in the above-described embodiment. For example, the partition wall portion 1623a according to the present embodiment extends from the outer wall surface 1625 and the inner wall surface 1626 of the discharge muffler body 1621 to connect the outer wall surface 1625 and the inner wall surface 1626 . formed to do Accordingly, the discharge space 1621a may be partitioned by the partition wall 1623a.

The partition wall portion 1623a may be formed transversely in a direction orthogonal to an imaginary line connecting both ends of the discharge valve 1451 as in the above-described embodiment. Accordingly, it is possible to suppress the direct movement of the refrigerant discharged from the discharge port 1423 to the refrigerant discharge hole 1628a, thereby increasing the vibration and noise attenuation effect.

The retainer portion 1623b may be formed to extend in a direction crossing the partition wall portion 1623a. For example, the retainer portion 1623b according to the present embodiment may extend in a direction perpendicular to or slightly inclined with respect to the partition wall portion 1623a on both sides of the partition wall portion 1623a.

The retainer portion 1623b may be formed to be longer in the axial direction than the partition wall portion 1623a. Accordingly, the lower end of the retainer portion 1623b may be partially inserted into the valve accommodating groove 1421a like the valve retainer 1452 of the above-described embodiment.

The lower surface of the retainer portion 1623b may be formed to be stepped, or may be formed to be curved to have a predetermined curvature. For example, the lower end surface of the retainer part 1623b may be formed to have a flat surface while the other side is curved to correspond to the open shape of the discharge valve 1451 . Accordingly, one side of the retainer portion 1623b is in close contact with the fixed portion of the discharge valve 1451 to press and fix the fixed portion, while the other side is spaced apart from the opening and closing portion of the discharge valve 1451 to limit the amount of opening of the opening and closing portion. have.

The valve fixing protrusion 1623c may extend from the flat end of the lower end surface of the retainer 1623b toward the valve fastening groove 1421c of the sub-plate portion 1421 . Accordingly, the valve fixing protrusion 1623c may be inserted into the valve fastening groove 1421c of the sub-plate part 1421 through the fastening hole (unsigned) of the discharge valve 1451 .

The valve fixing protrusion 1623c suppresses the discharge valve 1451 from being twisted in the lateral direction, and it is not necessary to be fastened to the valve fastening groove 1421c. Accordingly, the valve fixing protrusion 1623c may be formed as thin as possible, and when the discharge valve 1451 is closely inserted into the valve receiving groove 1421c, the valve fixing protrusion 1623c is excluded and the retainer portion 1623b). The Roman discharge valve 1451 may be fixed.

As described above, even when the retainer portion 1623b is provided on the partition wall 1623, the overall configuration of the partition wall (the partition wall portion) 1623 according to the present embodiment and the effect thereof are similar to those of the above-described embodiment. However, in this embodiment, since the retainer portion 1623b is integrally formed with the partition wall 1623, there is no need to separately provide a valve retainer. Accordingly, it is possible to reduce the manufacturing cost by reducing the assembly man-hours for the valve retainer.

Also, the discharge valve 1451 may be fixed by using the retainer portion 1623b or by using the valve fixing protrusion 1623c extending from the retainer portion 1623b. Accordingly, it is possible to reduce the manufacturing cost by reducing the number of assembling man-hours for the discharge valve 1451 .

On the other hand, another embodiment of the partition wall is as follows.

That is, in the above-described embodiments, there is only one barrier rib, but in some cases, a plurality of barrier ribs may be formed along the discharge space 1621a.

FIG. 15 is a perspective view showing another embodiment of the discharge muffler in FIG. 8, FIG. 16 is a plan view showing the discharge muffler assembling the compression unit in FIG. 16, and FIG. 17 is another embodiment of the discharge muffler in FIG. Another embodiment is a perspective view from the lower side, and FIG. 18 is a plan view showing the discharge muffler assembling the compression unit in FIG. 17 .

15 and 16 , the partition wall according to the present embodiment may include a first partition wall 16231 and a second partition wall 16232 .

The first partition wall 16231 may be formed between the discharge port and the refrigerant discharge hole 1628a as in the above-described embodiments. The first partition wall 16231 may have a flat bottom surface as in the embodiment of FIG. 9 , and as in the embodiment of FIG. 13 , it has a retainer portion 1623b or a valve fixing protrusion 1623c to form a curved surface. it might be With respect to the first partition wall 16231, since the configuration and effects thereof are the same as those of the above-described embodiments, a detailed description thereof will be replaced with the description of the above-described embodiments.

The second partition wall 15232 is generally similar to the first partition wall 16231 . For example, the second partition wall 16232 may extend from the outer wall surface 1625, the inner wall surface 1626, and the upper wall surface 1627 to partition the discharge space 1621a into a plurality of chambers 1621a1 and 1621a2. can However, a communication groove 16232a may be formed on the lower end surface of the second partition wall 16232 . The communication groove 16232a constitutes the neck portion of the Hello Holz silencer, and it may be preferable in terms of noise attenuation to be formed as small as possible.

However, if the communication groove 16232a is too small, the flow resistance of the refrigerant increases, and on the contrary, if the communication groove 16232a is too large, the noise attenuation effect may be halved. Accordingly, the communication groove 16232a may be formed to be small within a range in which the flow resistance of the refrigerant does not increase excessively, for example, 1/5 to 1/2 or less of the area of the second partition wall 16232 .

Also, the second partition wall 16232 may be formed at a position that is approximately 180° with respect to the first partition wall 16231 . Accordingly, the volumes of both chambers 1621a1 and 1621a2 partitioned by the first partition wall 16231 and the second partition wall 16232 may be substantially the same. Then, it is possible to suppress the decrease in compressor efficiency by reducing the flow resistance of the refrigerant while increasing the noise attenuation effect of the refrigerant, and to suppress the refrigerant from being a bottleneck in the vicinity of the refrigerant discharge hole 1628a, so that the refrigerant can be smoothly discharged. .

However, in some cases, the second partition wall 16232 is formed at a position that is less than 180° (eg, 90°) with respect to the first partition wall 16231 , or exceeds 180° (eg, 270°) with respect to the first partition wall 16231 . may be formed in In the former case, the bottleneck in the second chamber (the chamber in which the refrigerant discharge hole is accommodated) 1621a2 may be alleviated and the noise attenuation effect may be improved. In the latter case, the noise attenuation effect in the first chamber (the chamber in which the discharge port is accommodated) 1621a1 may be improved.

Meanwhile, referring to FIGS. 17 and 18 , the partition wall according to the present embodiment may include a first partition wall 16231 , a second partition wall 16232 , and a third partition wall 16233 .

The first partition wall 16231 may be formed between the discharge port and the refrigerant discharge hole 1628a as in the above-described embodiments. The first partition wall 16231 may have a flat bottom surface as in the embodiment of FIG. 9 , and as in the embodiment of FIG. 13 , it has a retainer portion 1623b or a valve fixing protrusion 1623c to form a curved surface. it might be With respect to the first partition wall 16231, since the configuration and effects thereof are the same as those of the above-described embodiments, a detailed description thereof will be replaced with the description of the above-described embodiments.

The second partition wall 16232 and the third partition wall 16233 are generally similar to the first partition wall 16231 . For example, the second partition wall 16232 and the third partition wall 16233 extend from the outer wall surface 1625, the inner wall surface 1626, and the upper wall surface 1627, respectively, to form the discharge space 1621a into a plurality of chambers 1621a1. (1621a2) (1621a3) may be formed to partition. However, communication grooves 16232a and 16233a may be respectively formed on the bottom surface of the second partition wall 16232 and the bottom surface of the third partition wall 16233 . The communication groove 16232a of the second partition wall 16232 and the communication groove 16233a of the third partition wall 16233 may be formed to have the same size or different sizes. Since these communication grooves 16232a and 16233a are similar to the configuration and effects thereof in the embodiment of FIG. 15 described above, a description thereof is replaced with the description of the embodiment described above.

The first partition wall 16231 , the second partition wall 16232 , and the third partition wall 16233 may be formed at equal intervals along the circumferential direction or may be formed at different intervals. In the former case, the volume of the plurality of chambers 1621a1, 1621a2, 1621a3 partitioned by each of the partition walls 16231, 16232, 16233 is formed to be almost the same, and it is possible to suppress an increase in the flow resistance of the refrigerant, The noise reduction effect can be kept constant. The latter may attenuate noise in various bands as the volumes of the plurality of chambers 1621a1 , 1621a2 , and 1621a3 partitioned by each of the partition walls 16231 , 16232 , and 16233 are different.

In addition, when each of the partition walls 16231, 16232, and 16233 are formed at different intervals, the volume of the chamber may decrease toward the discharge port 1423, and vice versa, toward the refrigerant discharge hole 1628a. It may be formed to reduce the volume of the chamber. In the former case, the bottleneck in the third chamber (the chamber in which the refrigerant discharge hole is accommodated) 1621a3 may be alleviated and the noise attenuation effect may be improved. In the latter case, the noise attenuation effect in the first chamber (the chamber in which the discharge port is accommodated) 1621a1 may be improved. This embodiment shows an example in which the volume decreases toward the discharge port 1423 as in the former case.

Although not shown in the drawings, a communication hole may be formed instead of the communication groove, or a circumferential length of the communication groove or the communication hole may be formed to be longer than the thickness of the partition wall. In this case, as the length of the neck increases, the noise attenuation effect may be improved.

110: shell 110a: inner space
111: lower shell 112: upper shell
115: suction pipe 116: discharge pipe
117: process pipe 118: loop pipe
120: electric part 121: stator
1211: stator core 1212: stator coil
1213: insulator 122: rotor
1221: rotor core 1221a: bearing insertion groove
1222: magnet 130: axis of rotation
131: rotor coupling part 132: main bearing part
133: sub-bearing part 134: eccentric part
140: compression unit 141: main bearing
1411: main plate portion 1412: stator fixing projection
1413: main bearing projection 1413a: main bearing hole
142: sub bearing 1421: sub-plate part
1421a: valve accommodating groove 1421b: valve accommodating extended groove
1421c: valve fastening groove 1422: sub-bearing protrusion
1422a: sub bearing hole 1422b: sealing groove
1423: outlet 143: cylinder
143a: fastening groove 1431: suction port
1431a: extension part insertion groove 1432: vane slot
1433: discharge guide groove 1435: muffler mounting groove
1435a: first muffler support surface 1435b: second muffler support surface
144: vane roller 1441: roller
1441a: hinge groove 1445: vane
1445a: vane body part 1445b: hinge protrusion
1451: discharge valve 1452: valve retainer
1453: valve fastening bolt 1461: first sealing member
1462: second sealing member 1463: third sealing member
150: support 151: spring cap
1511: first spring cap 1512: second spring cap
152: support spring 160: suction/discharge part
161: suction muffler 1611: suction muffler body part
1611a: suction space 1612: suction muffler inlet
1613: suction muffler outlet 1614: suction muffler connection part
1615: muffler fixing part 1615a: fastening hole
1616: muffler fastening bolt 162: discharge muffler
1621: discharge muffler body part 1621a: discharge space
1621a1, 1621a2, 1621a3: first, second, and third chambers 1621b: refrigerant discharge hole
1622: discharge muffler fixing part 1623, 16231, 16232, 16233: bulkhead
1623a: bulkhead part 1623b: retainer part
1623c: valve fixing protrusion 16232a, 16233a: communication groove
1625: outer wall surface 1626: inner wall surface
1626a: sub-bearing through hole 1627: upper wall surface
1628: valve receiving part 1628a: refrigerant discharge hole
170: oil supply unit 171: oil pumping unit
172: oil pumping passage 1721: oil pumping hole
1721a: first pumping hole 1721b: first, second pumping hole
1722: oil supply hole 1723: first oil supply groove
1724: second oil supply groove 1725: third oil supply groove
1726: oil supply communication groove 173: oil pump
1731: pump housing 1732: pump blade
175: refueling guide 176: refueling guide
1761: oil receiving space 1762: guide exit
1763: refueling guide protrusion 1763a: first guide protrusion
1763b: second guide protrusion 177: oil supply passage
1771: oil supply passage hole 1772: oil storage groove
1773: non-return valve 1773a: fixed part
1773b: opening/closing unit 1774: refueling guide pipe
C: Compressor body V: Compression chamber

Claims (17)

shell;
a driving motor spaced apart from the inner circumferential surface of the shell and elastically supported;
a main bearing and a sub-bearing provided on an upper side of the driving motor to support a rotation shaft of the driving motor;
a cylinder provided between the main bearing and the sub-bearing to form a compression chamber therein;
a roller provided on the rotating shaft and provided inside the cylinder;
a vane slidably inserted into the vane slot provided in the cylinder and provided between the cylinder and the roller; and
and a discharge muffler provided in the sub-bearing to receive the discharge port provided in the sub-bearing;
The discharge muffler is
A discharge space for accommodating the discharge port is provided, and a refrigerant discharge hole passing through the discharge space is formed spaced apart from the discharge port,
At least one partition wall partitioning the discharge space is formed between the discharge port and the refrigerant discharge hole. According to claim 1,
The discharge space is formed in an annular shape having an outer circumferential surface and an inner circumferential surface, and an upper surface connecting one end of the outer circumferential surface and one end of the inner circumferential surface,
The partition wall,
At least one rotary compressor extending from an outer circumferential surface, an inner circumferential surface, and an upper surface of the discharge space and provided on a line connecting the shortest distance between the discharge port and the refrigerant discharge hole. According to claim 1,
The partition wall includes a first partition wall positioned on a line connecting the shortest distance between the discharge port and the refrigerant discharge hole,
The first partition wall,
A rotary compressor provided across both ends of a discharge valve that opens and closes the discharge port. 4. The method of claim 3,
The first partition wall,
A rotary compressor formed in a direction perpendicular to an imaginary line connecting both ends of the discharge valve. 4. The method of claim 3,
The first partition wall,
A rotary compressor extending in the longitudinal direction of the discharge valve to form a valve fixing portion for fixing one end of the discharge valve to the sub-bearing or a retainer portion for limiting an opening amount of the discharge valve. According to claim 1,
A discharge valve for opening and closing the discharge port is provided in the sub-bearing;
The partition wall includes at least one second partition spaced apart from the discharge valve,
The second partition wall,
A rotary compressor in which a communication portion is formed so that both spaces partitioned by the second partition wall communicate with each other. 7. The method of claim 6,
The discharge space is divided into a plurality of spaces by the second partition wall, and the plurality of spaces are formed in different volumes. 8. The method of claim 7,
A rotary compressor in which the plurality of spaces have a larger volume as they are adjacent to the refrigerant discharge hole. According to claim 1,
The discharge muffler is
a discharge muffler body portion having the discharge space formed in an annular shape; and a discharge muffler fixing portion extending radially from an outer peripheral end of the discharge muffler body portion;
The partition wall,
A rotary compressor connecting an outer wall surface and an inner wall surface of the discharge muffler body forming the discharge space. 10. The method of claim 9,
A valve accommodating portion is formed to protrude outward from an outer wall surface of the discharge muffler body portion, and one end of a discharge valve for opening and closing the discharge port is inserted into the valve accommodating portion. 10. The method of claim 9,
A valve accommodating part is formed to protrude outward from an outer wall surface of the discharge muffler body part, and the valve accommodating part communicates with the discharge space,
A rotary compressor through which the refrigerant discharge hole is penetrated in the valve accommodating part. 10. The method of claim 9,
A valve accommodating part is formed to protrude outward from the outer wall surface of the discharge muffler body,
The partition wall,
a rotary compressor extending from one end adjacent to the discharge port to an inner wall surface of the discharge muffler body from among both ends of the valve receiving unit in the circumferential direction. 13. The method according to any one of claims 1 to 12,
The cylinder is provided on the axial direction upper side of the drive motor,
The drive motor is spaced apart from the inner circumferential surface of the shell and is elastically supported with respect to the shell by a support part having elasticity. 14. The method of claim 13,
Further comprising an oil supply guide for supplying the oil pumped from the shell to the compression chamber,
The refueling guide unit,
A rotary compressor in which an oil supply passage hole is formed so as to pass through the sub-bearing or the cylinder and communicate with a vane slot provided in the cylinder. 15. The method of claim 14,
An oil supply guide for collecting oil is provided on the upper side of the rotating shaft,
The outlet of the oil supply guide is in communication with the oil supply passage hole through the inner space of the shell. 15. The method of claim 14,
A rotary compressor provided with a non-return valve for opening and closing the oil supply passage hole in the sub-bearing or the cylinder. 15. The method of claim 14,
An oil supply guide is provided on the upper side of the rotation shaft to collect oil and guide it toward the oil supply passage hole,
The outlet of the oil supply guide is a rotary compressor connected to the oil supply guide pipe to the oil supply passage hole.

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