KR20220063805A - Rotary compressor - Google Patents

Abstract

According to an embodiment of the present invention, a rotary compressor is provided with bearing parts on both sides of an eccentric part, respectively, and a roller alignment part may be formed between the eccentric part and at least one bearing part to align the assembly position of a roller before inserting the roller into the eccentric part. Accordingly, the outer diameter of the bearing part is increased so that the roller can be easily assembled into the eccentric part even in a state where an outer circumferential surface of the bearing part protrudes radially from an outer circumferential surface of the eccentric part. Through this, it is possible to downsize the compressor by reducing the axial length of the bearing part while securing the bearing area by increasing the outer diameter of the bearing part.

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. The electric part and the compression part may be installed inside the same shell or may be installed in different shells and connected 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 divided 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 in 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, so it may be advantageous to maintain 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 the transmission unit and the compression unit. In the shell-supported type, the compressor body is fixed to 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. However, in the spring-supported type, since the compressor body vibrates inside the shell, a further gap between the compressor body and the shell is required, which may be disadvantageous for miniaturization of the compressor.

In addition, the hermetic compressor may be divided into a one-end support type and a double-end support type according to a method of supporting the rotating shaft. The one-end support type is a method in which the rotating shaft is supported only on one side centered on the compression part, and the double-end support type is a method in which the rotation shaft is supported from both sides centering on the compression part.

As the one end support type forms a bearing surface on only one side of the rotation shaft, it is easy to manufacture and assemble the rotation shaft and the bearing member corresponding thereto. However, as the bearing load increases and the rotating shaft is supported only at one end, the behavior of the rotating shaft becomes unstable, and leakage between the compression chambers may occur. On the other hand, since the both-end support type has bearing surfaces on both sides in the axial direction of the rotating shaft, it may be difficult to manufacture and assemble the rotating shaft and the corresponding bearing member. However, since the bearing load is evenly distributed to both bearing members, the bearing load on each bearing member is reduced, and at the same time, by supporting the rotating shaft from both sides, the behavior of the rotating shaft is stabilized and leakage between the compression chambers can be effectively suppressed.

Patent Document 1 (Korean Patent Application Laid-Open No. 10-2000-0059891) discloses a rotary compressor of a low pressure type, an upper compression type, and a dual end support 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 support type, and the inner shell is supported by the outer shell in a spring support type. 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 increase, and the number of parts increases, 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. The rotary compressor disclosed in Patent Document 3 is of a low pressure type, an upper compression type, a spring support type, and a double end 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 manufacturing cost. In addition, as the compression part is located above the transmission part, the roof pipe is not immersed in oil to prevent an increase in oil temperature and to prevent excessive drop in oil viscosity that occurs when the oil temperature rises, thereby reducing friction loss in the compression part. . In addition, in Patent Document 3, since a long loop pipe can be formed by using the upper space of the shell, vibration of the compressor can be reduced that much, and by supporting both ends of the rotating shaft, the bearing load is reduced and leakage between the compression chambers is effectively suppressed. can do.

In addition, as all of the conventional rotary compressors disclosed in the above-described patent documents are of the both-end support type, the bearing load on each bearing member is reduced and the behavior of the rotating shaft is stabilized, thereby effectively suppressing leakage between the compression chambers.

In such a conventional rotary compressor, an eccentric portion is formed in the upper half of the rotating shaft, and a main bearing portion is formed on the lower side around the eccentric portion, and a sub-bearing portion is formed on the upper side, respectively. An annular roller is rotatably inserted into the outer peripheral surface of the eccentric. The roller may be inserted in the upper direction from the lower end of the eccentric portion, or may be inserted in the opposite direction from the upper end to the lower end.

In addition, in the conventional rotary compressor, the bearing area of the main bearing part, the bearing area of the sub-bearing part, and the outer diameter of the eccentric part are related to each other, and these are also related to whether the compressor is miniaturized.

For example, in the rotary compressor of the upper compression type and both ends supported type, if the distance from the center of the eccentric part to the center of the main bearing part is long, the bearing load on the sub bearing part increases. Then, since the bearing area of the sub-bearing part must be enlarged, the outer diameter of the sub-bearing part must be enlarged or the axial length must be increased.

However, if the outer diameter of the sub-bearing part is enlarged, the outer diameter of the eccentric part also increases in consideration of the assembly of the roller. can be lowered In addition, the inner diameter of the cylinder increases as the outer diameter of the eccentric portion increases in the same compression chamber volume, which is disadvantageous in terms of miniaturization and weight reduction of the compressor. In addition, it may be disadvantageous in terms of vibration and noise of the compressor.

On the other hand, when the axial length of the sub-bearing part is increased, the overall length of the rotating shaft is increased, so that the axial height of the compressor is increased, which is disadvantageous in terms of miniaturization of the compressor.

In addition, in the conventional rotary compressor of the upper compression type and both ends supported type, an oil pumping passage connected from the inside to the outside of the rotary shaft is formed, and an oil pump is applied to the lower end of the oil pumping passage to pump the oil stored in the shell to pump the compression unit. It is being transferred from the lower end of the rotating shaft to the upper end.

In general, as an oil pump, a gear pump to which a trochoid gear is applied, a viscous pump to which a screw gear is applied, and a centrifugal pump to which a propeller is applied are mainly known. The gear pump is disadvantageous because of its complicated structure and high manufacturing cost. Since the viscous pump has a complicated structure in which the screw gear is fixed to the rotating shaft, and the oil has to pass through a long spiral pumping passage, the pumping amount may vary greatly depending on the operating speed. Centrifugal pumps are relatively inexpensive and structurally simple compared to previous gear pumps and viscous pumps.

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

The first object of the present invention is to reduce the overall length of the rotating shaft by reducing the axial length while maintaining the bearing area of the bearing in a double-end support type supporting both ends of the rotating shaft with an eccentric part therebetween, thereby reducing the size of the compressor. It is intended to provide a compressor.

Furthermore, an object of the present invention is to provide a rotary compressor capable of reducing the axial length of the bearing part while the radius of both bearing parts is greater than or equal to the shortest eccentric radius of the eccentric part.

Furthermore, the present invention provides a roller alignment part between the eccentric part and the bearing part so that the roller can be inserted into the eccentric part through one of the bearing parts while the radius of both bearing parts is formed larger than the shortest eccentric radius of the eccentric part. An object of the present invention is to provide a rotary compressor capable of reducing the axial length of both bearings.

A second object of the present invention is to provide a rotary compressor capable of achieving miniaturization, weight reduction, and low vibration of the compressor by reducing the outer diameter of the eccentric part while maintaining the same volume of compression chamber in a double-end support type supporting both ends of a rotating shaft with an eccentric part therebetween. It is intended to provide

Furthermore, an object of the present invention is to provide a rotary compressor in which the shortest eccentric radius of the eccentric is smaller than or equal to the radius of both bearings provided on both sides of the eccentric.

Furthermore, the present invention is a rotary compressor capable of reducing the outer diameter of the eccentric by allowing the roller to be smoothly inserted into the eccentric while the shortest eccentric radius of the eccentric is formed to be smaller than or equal to the radius of both bearings provided on both sides of the eccentric The purpose is to provide

A third object of the present invention is to provide a rotary compressor that is an upper compression type and a support type at both ends and capable of smoothly transferring oil from the lower end to the upper end of the rotating shaft.

Furthermore, an object of the present invention is to provide a rotary compressor capable of reducing the manufacturing cost of the oil pump while smoothly transferring oil from the lower end to the upper end of the rotating shaft.

Furthermore, an object of the present invention is to provide a rotary compressor capable of suppressing enlargement of the diameter of the rotary shaft by allowing oil to be smoothly transferred toward the upper end of the rotary shaft while applying a relatively inexpensive centrifugal pump.

A fourth object of the present invention is to provide a rotary compressor of a low pressure type, an upper compression type, a spring support type, a double end support type, and in which the oil stored in the shell can be supplied to the compression unit.

Furthermore, an object of the present invention is to provide a rotary compressor provided with an oil supply guide so that the oil supplied to the compression unit is smoothly supplied between the vanes and the vane slots.

Furthermore, an object of the present invention is to provide a rotary compressor capable of suppressing the oil or compressed refrigerant supplied to the compression unit from flowing backward or leaking out of the shell through the oil supply guide.

In order to achieve the first object of the present invention, there may be provided a rotary compressor comprising a transmission unit and a compression unit positioned above the transmission unit, and a rotary shaft connecting between the transmission unit and the compression unit. The rotating shaft may have a main bearing portion formed on the side of the transmission with an eccentric portion interposed therebetween, and a sub-bearing portion formed on an opposite side of the main bearing portion. A radius of the main bearing part or a radius of the sub-bearing part may be formed to be larger than a shortest eccentric radius of the eccentric part. Through this, instead of increasing the outer diameter of the main bearing part or the sub-bearing part, it is possible to reduce the overall length of the rotating shaft by reducing the axial length to achieve miniaturization of the compressor.

For example, a roller alignment unit capable of aligning the assembly position of the rollers may be formed on one side of the eccentric portion in the axial direction. Through this, before inserting the roller into the eccentric part, it is possible to insert the roller into the eccentric part after readjusting the assembly position of the roller in the roller alignment part. Accordingly, while forming the outer diameter of the bearing portion larger than the outer diameter of the eccentric, it is possible to smoothly insert the roller into the eccentric.

As another example, the roller alignment part may be formed between the eccentric part and the main bearing part. Through this, as the roller alignment part is formed on the side of the main bearing part having a relatively spare length, it is possible to reduce the overall length of the rotation shaft while forming the roller alignment part having a predetermined axial length on the rotation shaft.

In order to achieve the second object of the present invention, there may be provided a rotary compressor including a transmission unit and a compression unit positioned above the transmission unit, and a rotary shaft connecting between the transmission unit and the compression unit. The rotating shaft may form a main bearing part on the side of the transmission with an eccentric part therebetween, and a sub-bearing part on the opposite side of the main bearing part. The shortest eccentric radius of the eccentric part may be formed to be smaller than a radius of the main bearing part or a radius of the sub-bearing part. Through this, the volume of the compression chamber can be maintained by increasing the amount of eccentricity of the eccentric while reducing the outer diameter of the eccentric. Accordingly, the outer diameter of the eccentric portion is reduced to achieve miniaturization, weight reduction, and low vibration of the compressor.

For example, a roller alignment part capable of aligning the assembly position of the rollers is formed on one side of the axial direction of the eccentric part, and the axial length of the roller alignment part may be formed to be greater than the axial length of the rollers. Through this, by re-adjusting the assembly position of the roller in the roller alignment part before inserting the roller into the eccentric part, the outer diameter of the eccentric part can be reduced, and the roller can be smoothly inserted into the eccentric part and combined.

As another example, the outer diameter of the eccentric portion may be formed larger than the outer diameter of the roller alignment portion. Through this, the roller can be easily inserted into the eccentric part while reducing the outer diameter of the eccentric part by preventing the roller from being caught in the eccentric part when inserting the roller into the eccentric part.

In order to achieve the third object of the present invention, a shell in which oil is stored in the inner space, the electric part provided in the inner space of the shell, and the compression part located above the electric part, between the electric part and the compression part A rotary compressor including a compressor body provided with a rotating shaft connecting the rotary compressors may be provided. An oil pump may be provided at a lower end of the rotary shaft, and an oil pumping passage for guiding oil pumped from the oil pump to an upper end of the rotary shaft may be formed on the rotary shaft. Through this, the oil can be smoothly transferred from the lower end to the upper end of the rotary shaft while being of the upper compression type and the both ends supported.

For example, the oil pump may be a centrifugal pump including a pump housing inserted into a lower end of the rotation shaft and a pump blade provided in the pump housing. Through this, it is possible to reduce the manufacturing cost of the oil pump by simplifying the structure of the oil pump.

As another example, an oil pumping hole may be formed inside the rotation shaft, and an oil supply hole and oil supply groove communicating with the oil pumping hole may be formed on an outer circumferential surface of the rotation shaft. An oil supply hole communicating with the oil pumping hole may be formed in the lower half of the rotation shaft so as to be adjacent to the oil pump. Through this, the pumping power is improved by applying the centrifugal pump to the lower end of the rotating shaft while the pumped oil generates centrifugal force quickly. can be transferred smoothly.

In order to achieve the fourth object of the present invention, it is provided spaced apart from the inner circumferential surface of the shell, a rotary compressor including a transmission unit and a compression unit positioned above the transmission unit may be provided. The compression unit may include a compressor body made of a rotary compression method, a support unit for elastically supporting the compressor body with respect to the shell, and an oil supply passage provided in the compressor body to supply oil to the inside of the compression unit. Through this, oil can be smoothly supplied to the compression part while being a low pressure type, an upper compression type, and a spring supported type.

For example, an oil supply passage hole may be formed in the sub-bearing or cylinder constituting the compression part. Through this, the oil scattered into the inner space of the shell can be smoothly supplied to the inside of the compression unit.

As another example, an oil supply passage groove may be formed on a side surface of the vane constituting the compression part or an inner surface of the vane slot facing the same. This allows the oil to move quickly between the vane and the vane slot.

In addition, in order to achieve the object of the present invention, a rotary compressor including a shell, a transmission part, a cylinder, a main bearing and a sub-bearing, a rotating shaft and a roller may be provided. Oil may be stored in the inner space of the shell, and the electric part may be provided in the inner space of the shell. The cylinder may be provided at one axial direction of the transmission part in the inner space of the shell, and the main bearing and the sub bearing may be coupled to both sides of the cylinder in the axial direction to form a compression chamber together with the cylinder. The rotating shaft is accommodated in the compression chamber of the cylinder and has an eccentric part eccentric with respect to the shaft center, a main bearing part provided on both sides in the axial direction with the eccentric part therebetween and supported in a radial direction by the main bearing and the sub-bearing, respectively and a sub-bearing unit. The roller is formed in an annular shape and may be inserted into the outer circumferential surface of the eccentric part. Specifically, a roller alignment part may be formed on one side of the axial direction of the eccentric part on the rotation shaft, and the axial length of the roller alignment part may be formed to be longer (larger) than the axial length of the roller. Through this, by properly aligning the assembly positions of the rollers before inserting the rollers into the eccentric, even if the outer circumferential surface of the main bearing or sub-bearing part is the same as the outer circumferential surface of the eccentric or protrudes from the outer circumferential surface of the eccentric, the roller can be easily assembled. . Accordingly, it is possible to reduce the length of the bearing portion on the side where the roller is not inserted, thereby reducing the size of the compressor.

Here, the radius of the main bearing part or the radius of the sub bearing part may be formed to be greater than or equal to the radius of the shortest eccentricity of the eccentric part. The radius of the roller alignment part may be formed smaller than the shortest eccentric radius of the eccentric part. Through this, even if the outer peripheral surface of the main bearing part or the outer peripheral surface of the sub-bearing part protrudes in a radial direction than a part of the eccentric, that is, the outer peripheral surface of the part having the shortest eccentric radius, the roller can be easily inserted into the eccentric and coupled. Accordingly, it is possible to appropriately secure the outer diameter of the main bearing portion or the outer diameter of the sub-bearing portion, thereby reducing the axial length of the main bearing portion or the axial length of the sub-bearing portion.

In addition, the center of the roller alignment part may be formed to be located on the same axis as the center of the main bearing part or the center of the sub-bearing part. Through this, an annular space having the same cross-sectional area in the circumferential direction is formed between the outer peripheral surface of the roller alignment part and the bearing hole facing the same, so that oil can be uniformly pumped.

In addition, the center of the roller alignment part may be formed at a position eccentric from the center of the main bearing part or the center of the sub-bearing part. Through this, the cross-sectional area of the portion adjacent to the oil supply groove among the outer peripheral surfaces of the roller alignment unit is enlarged, and the pumping path of the oil is shortened, so that the oil can be transferred quickly.

Here, the main bearing part may extend toward the electric part based on the eccentric part. The roller alignment part may be formed between the eccentric part and the main bearing part. Through this, as the roller alignment part is formed on the side of the main bearing part having a relatively long axial length, it is possible to suppress the overall length of the rotating shaft from becoming longer while having the roller alignment part, thereby achieving miniaturization of the compressor.

In addition, the outer diameter of the sub-bearing part may be formed to be larger than the outer diameter of the roller alignment part. Through this, it is possible to secure the bearing area of the sub-bearing part to secure the reliability of the compressor.

In addition, the axial length of the sub-bearing part may be shorter than or equal to the axial length of the roller alignment part. Through this, it is possible to achieve miniaturization of the compressor by reducing the axial length of the sub-bearing part.

In addition, a friction avoidance may be further formed between the main bearing unit and the roller alignment unit. An outer diameter of the friction avoidance portion may be smaller than an outer diameter of the main bearing portion and larger than an outer diameter of the roller alignment portion. Through this, the lubrication effect on the bearing surface can be increased by reducing the leakage of oil to the bearing surface while minimizing the length of the main bearing.

And, the center of the friction avoidance may be formed on the same axis as the axial center of the rotation shaft. Through this, the gap between the outer circumferential surface of the friction avoidance and the inner circumferential surface of the bearing hole facing the same is maintained so that the oil can be uniformly transported along the outer circumferential surface of the friction avoiding member.

Here, the distance from the axial center of the rotating shaft to the outer peripheral surface of the main bearing part is a first radius, the distance from the axial center of the rotating shaft to the outer peripheral surface of the sub-bearing part is the second radius, and from the axial center of the rotating shaft to the eccentric part The shortest distance may be referred to as the first shortest eccentric radius. The first radius and the second radius may be formed to be greater than or equal to the first shortest eccentric radius. Through this, it is possible to reduce the outer diameter of the eccentric by increasing the eccentricity of the eccentric. Accordingly, the compressor can be downsized by maintaining the compressor volume while reducing the inner diameter of the cylinder. In addition, it is possible to reduce the size of the bearing member by reducing the bearing load due to the eccentric portion, thereby reducing the weight of the compressor and at the same time reducing the vibration noise of the compressor. In addition, it is possible to reduce the overall length of the rotating shaft by reducing the axial length of each bearing part while securing the bearing area of the main bearing part or the sub-bearing part.

In addition, the center of the roller alignment part may be formed on the same axis line with respect to the axis center of the rotation shaft, and a third radius constituting the radius of the roller alignment part may be formed to be smaller than the first shortest eccentric radius. Through this, as the rollers aligned in the roller alignment part are inserted without being caught in the eccentric part, the roller can be easily inserted into the eccentric part and assembled. Accordingly, it is possible to reduce the size of the compressor by reducing the axial length of the bearing portion on the side where the roller is not inserted.

And, the center of the roller alignment part is formed to be eccentric with respect to the axial center of the rotation shaft, and the shortest distance from the axial center of the rotation shaft to the outer peripheral surface of the roller alignment part may be referred to as a second shortest eccentric radius. The second shortest eccentric radius may be smaller than the first shortest eccentric radius. Through this, while having the roller alignment part, it is possible to suppress excessive thinning of the outer diameter of the roller alignment part, thereby increasing the rigidity in the roller alignment part. In addition, as the cross-sectional area of the portion adjacent to the oil supply groove among the outer peripheral surfaces of the roller alignment unit is enlarged, the pumping path of oil is shortened, so that the oil can be transferred quickly.

Here, the axial distance from the center of the main bearing part to the center of the eccentric part may be referred to as a first axial distance, and the axial distance from the center of the sub-bearing part to the center of the eccentric part may be referred to as a second axial distance. The second axial distance may be shorter than the first axial distance. The roller alignment part may be formed between the main bearing part and the eccentric part. Through this, it is possible to suppress an increase in the axial length of the rotating shaft due to the roller alignment part as the roller alignment part is formed using the extra length formed between the main bearing part and the eccentric part.

In addition, a friction avoidance may be further formed between the main bearing unit and the roller alignment unit. The center of the friction avoidance may be formed on the same axis as the axis of the rotation shaft. An outer diameter of the friction avoidance portion may be smaller than an outer diameter of the main bearing portion and larger than an outer diameter of the roller alignment portion. Through this, the lubrication effect on the bearing surface can be increased by reducing the leakage of oil to the bearing surface while minimizing the length of the main bearing.

Here, the sub-bearing part may be formed to extend in a direction opposite to the electric part based on the eccentric part. The roller alignment part may be formed between the sub-bearing part and the eccentric part. Through this, the roller can be easily assembled by assembling the roller through a relatively short sub-bearing part.

In addition, the shortest radius of the eccentric portion of the eccentric may be formed to be smaller than the radius of the sub-bearing portion. The radius of the roller alignment part may be formed smaller than the shortest eccentric radius of the eccentric part. Through this, even if the outer circumferential surface of the sub-bearing part protrudes in the radial direction than the shortest eccentric radius of the eccentric part, the roller can be easily inserted into the eccentric part and combined. Accordingly, it is possible to appropriately secure the outer diameter of the sub-bearing part, thereby reducing the axial length of the sub-bearing part.

Here, an oil pump may be provided at an end of the rotation shaft toward the main bearing to pump oil stored in the inner space of the shell. An oil pumping passage for guiding the oil pumped by the oil pump to the other end of the rotation shaft may be formed in the rotation shaft. Through this, the oil stored in the shell can be smoothly supplied to each bearing surface and the compression unit, thereby improving compressor performance.

Also, the oil pump may be a centrifugal pump. The main bearing part may be formed to be positioned at a lower end of the main bearing. Through this, the oil can be smoothly transferred to the upper end of the rotary shaft by supplementing the pumping power of the oil pump while lowering the manufacturing cost of the oil pump.

In addition, an oil pumping hole may be formed at an end of the rotation shaft on the side of the main bearing. The oil supply hole may penetrate from the inner peripheral surface of the oil pumping hole to the outer peripheral surface of the main bearing part. A first oil supply groove for communicating the oil supply hole between the outer peripheral surface of the roller alignment part and the inner peripheral surface of the main bearing facing it may be formed in the outer peripheral surface of the rotating shaft. Through this, the oil pumped by the oil pump can quickly have centrifugal force, so that the oil can be smoothly pumped up to the upper end of the rotation shaft while applying the oil pump having a relatively low pumping force.

A friction avoidance may be formed between the main bearing unit and the roller alignment unit. An outer diameter of the friction avoidance portion may be smaller than an outer diameter of the main bearing portion and larger than an outer diameter of the roller alignment portion. The first oil supply groove may extend along the outer circumferential surface of the friction avoidance skin and pass through a stepped surface forming a boundary between the friction avoidance skin and the roller alignment unit. Through this, the oil transferred along the outer circumferential surface of the rotary shaft smoothly lubricates the main bearing surface, and at the same time, an oil communication space is formed on the outer circumferential surface of the roller alignment unit so that the oil is transferred toward the upper end of the rotary shaft without leakage.

And, the eccentric portion may be formed with a second oil supply groove for communicating both sides in the axial direction. The second oil supply groove may be recessed by a predetermined depth from the outer circumferential surface of the eccentric part to communicate between both sides of the eccentric part in the axial direction. Through this, the oil accumulated between the outer peripheral surface of the roller alignment part and the inner peripheral surface of the bearing hole facing the same is smoothly transferred toward the sub-bearing part, thereby enhancing the oil pumping effect.

In addition, a third oil supply groove may be formed on an outer peripheral surface of the sub-bearing part or an inner peripheral surface of the sub-bearing facing the same. Through this, the oil transferred to the sub-bearing part can be transferred to the upper end of the rotating shaft while lubricating the sub-bearing surface.

And, between the second oil supply groove and the third oil supply groove, an oil supply communication groove may be formed. The oil supply communication groove may be formed in an annular shape on an outer peripheral surface of the sub-bearing part extending from the eccentric part. Through this, the oil transferred to the sub-bearing unit can be smoothly transferred to the oil supply groove provided on the sub-bearing surface.

Here, the cylinder may be provided at an axial direction upper side of the transmission part. The electric part 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 reduce the compressor vibration by minimizing the vibration generated in the compressor body from being transmitted to the outside of the shell through the shell.

And, 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.

In addition, 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.

In addition, 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, it is possible to suppress the leakage of the oil supplied to the compression unit and the refrigerant compressed in the compression unit through the oil supply guide.

In addition, 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 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 this embodiment, bearing parts are provided on both sides of the eccentric part, respectively, and between the eccentric part and the bearing part, roller alignment parts for aligning the assembly positions of the rollers before inserting the rollers into the eccentric part may be formed. Accordingly, the outer diameter of the bearing portion is increased, so that the roller can be easily assembled to the eccentric portion even in a state in which the outer peripheral surface of the bearing portion is the same as a part of the outer peripheral surface of the eccentric portion in the radial direction or protrudes. Through this, the compressor can be miniaturized by increasing the outer diameter of the bearing part to secure the bearing area while reducing the axial length of the bearing part.

In addition, in the rotary compressor according to this embodiment, as the roller alignment part is formed on the side of the main bearing part having a relatively free length with respect to the eccentric part, the overall length of the rotating shaft does not become long due to the roller alignment part while forming the roller alignment part The compressor can be downsized.

In addition, in the rotary compressor according to the present embodiment, the outer diameter of the eccentric portion can be reduced as the amount of the eccentricity of the eccentric portion is increased by the roller alignment portion of the eccentric portion. Accordingly, it is possible to reduce the size of the bearing by reducing the inner diameter of the cylinder and at the same time reducing the bearing load to achieve miniaturization, weight reduction, and low vibration of the compressor.

In addition, in the rotary compressor according to this embodiment, the oil stored in the lower part of the shell can be smoothly pumped to the upper end of the rotary shaft while applying an oil pump of a centrifugal pump to the lower end of the rotary shaft in the rotary compressor of the upper compression type and both ends supported. there is. As a result, an inexpensive oil pump can be used with a relatively simple structure and a small number of parts, thereby reducing the manufacturing cost of the compressor.

In addition, in the rotary compressor according to the present embodiment, the starting end of the oil supply groove may be disposed adjacent to the oil pump as the main bearing part of the rotating shaft is continuously formed in the rotor coupling part in the lower half of the rotating shaft. Through this, it is possible to increase the centrifugal force against oil without increasing the outer diameter of the rotating shaft or increasing the length and number of turns of the oil supply groove, and oil can be transferred to the upper end of the rotating shaft while applying an oil pump with a centrifugal pump.

In addition, in the rotary compressor according to the present embodiment, as the main bearing part of the rotating shaft is formed in the lower half of the rotating shaft, it is possible to lower the bearing load of the main bearing part. Through this, it is possible to increase the motor efficiency by reducing the diameter or length of the part corresponding to the main bearing on the rotating shaft. In addition, as the main bearing part is formed in the lower half of the rotating shaft, a roller alignment part may be formed between the main bearing part and the eccentric part, and through this, the roller can be easily assembled without increasing the length of the rotating shaft.

In addition, the rotary compressor according to the present embodiment, by elastically supporting the rotary 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, by configuring the rotary compressor according to the present embodiment of the upper compression type, the loop pipe constituting the discharge flow path can be installed so that it is 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 roof pipe in advance, thereby suppressing the viscosity of the oil from lowering and reducing friction loss 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 can be supplied smoothly and quickly to the sliding part of the compression part. Through this, 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 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;
7 is a perspective view showing another embodiment for the oil supply guide in FIG. 5;
8 is a perspective view showing the rotation shaft according to the present embodiment from one side;
9 is a perspective view showing the rotation shaft according to the present embodiment from the other side;
10 is a front view showing the rotation shaft according to the present embodiment from one side;
11 is an enlarged front view of the sub-bearing part and the roller alignment part in FIG. 10;
12 is a plan view showing the axis of rotation in the axial direction in FIG. 10;
13 is a view sequentially showing the process of coupling the roller to the eccentric part of the rotating shaft according to the present embodiment;
14 is a perspective view showing the outer surface of the rotating shaft by breaking the bearing to explain the passage through which oil is pumped in the oil pumping unit according to the present embodiment;
15 is a cross-sectional view showing the inner surface of the rotation shaft in FIG. 14;
16 is a perspective view showing another embodiment of the rotation shaft;
17 is a front view of FIG. 16;
18 is a perspective view showing another embodiment of the rotation shaft;
19 is a cross-sectional view of FIG. 18;
20 is a perspective view showing another embodiment of the rotation shaft;
Fig. 21 is a cross-sectional view of Fig. 20;

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 numbers 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 whether or not the rollers and the vanes are coupled. 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 can be understood that the rotary compressor is defined as abbreviated 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. FIG. 4 is a plan view illustrating 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 a refueling unit 170 for supplying. The compressor body (C) includes a transmission unit 120 providing a driving force, a rotating shaft 130 and a motor coupled to the transmission unit 120 to transmit the rotational force generated in the transmission unit 120 to a compression unit 140 to be described later. It includes a compression unit 140 that receives the driving force from the eastern part 120 and compresses the refrigerant.

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 coupled to the lower shell 111 by welding, but when the lower shell 111 and the upper shell 112 are made 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 sheet, and when a voltage is applied from the outside to the electric part 120, 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, 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, direct contact between the stator core 1211 and the stator coil 1212 is suppressed, so that electromagnetic interaction can 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 has 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 rotary shaft 130 has both ends in the axial direction with respect to the eccentric portion 134 to be radially supported by a main bearing 141 and a sub bearing 142 to be described later, respectively, the rotary 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 electric 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 transmission unit 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 peripheral surface of the cylinder 143 is the outer wall surface of the compression chamber (V), the outer peripheral surface of the roller 1441 is the inner wall surface of the compression chamber (V), 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. there is.

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 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 periphery side of the suction port 1431 so that the outlet extension portion is inserted. there is. 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 , it is possible to suppress a decrease in the inner diameter of the suction port 1431 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 inlet 1431 are each formed in a closed shape, and both axial side surfaces and radially outer surfaces are each formed in an open shape. 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 it. 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 to be described later may be inserted and coupled from the outer circumferential side of the muffler mounting groove 1435 to the inner circumferential side. And, as both sides of the muffler mounting groove 1435 in the upper and lower axial directions 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 secured as much as possible. can The muffler mounting groove 1435 will be described again later with the suction muffler 161 .

The vane slot 1432 is elongated in the 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, which will be described later, slides. Accordingly, both sides of the vane 1445 are supported by both inner wall surfaces of the vane slot 1432 and slide approximately in a 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 the compression chamber sealing member 146 made of an O-ring or gasket may be inserted into the compression chamber sealing groove.

For example, the compression chamber sealing member 146 may be formed in an annular shape and installed along the periphery of the compression chamber (V). Specifically, the compression chamber sealing member 146 surrounds the outer peripheral side of the vane slot 1432 and the outer peripheral side of the discharge guide groove 1433, and seals between the inner peripheral side of the muffler mounting groove 1435 and the compression chamber (V). It can be installed through the face.

Accordingly, the compression chamber sealing member 146, 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. It is 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 compression chamber sealing member 146 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 formed 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 formed to 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 cocentric 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 formed uniformly along the circumferential direction. it 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 unit 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 formed in a rectangular hexahedral shape as a whole. 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 formed to have 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 this 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 (precisely, 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 disposed on different axial lines, it is advantageous that the second spring cap 1512 is 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 communicate with 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 . there is. 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. there is.

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 consecutively to the suction muffler body 1611 . However, the outlet portion 1613 of the suction muffler is coupled to the outer peripheral 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 part 1611 and the suction muffler outlet part 1613 may be connected by the suction muffler connection part 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 portion 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.

In addition, the muffler fixing part 1615 may be formed to extend in the circumferential direction on both sides of the suction muffler outlet 1613 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 peripheral 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. It can be fastened with

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 1613a to be described later is formed on the suction muffler outlet 1613, the outlet extension 1613a is wrapped around the suction muffler outlet portion ( 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, the outlet extension portion 1613a of the suction muffler outlet portion 1613 may be formed to extend toward the cylinder (143). 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 formed with 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 fixed to the upper surface of the sub-bearing 142 .

The discharge muffler body part 1621 is composed of a side wall surface and an upper wall surface forming the discharge space 1621a, and the side wall surface forming the discharge space 1621a is connected to the roof pipe 118 to form the discharge space 1621a. A refrigerant discharge hole 1621b for guiding the discharged refrigerant to the discharge pipe 116 may be formed. Accordingly, the refrigerant discharged to the discharge space 1621a is discharged to the loop pipe 118 through the refrigerant discharge hole 1621b while the discharge noise is canceled in the discharge space 1621a, and the refrigerant is discharged through the discharge pipe 116 through the condenser.

Also, a bearing part through-hole 1621c through which the sub-bearing protrusion 1422 penetrates may be formed in the center of the upper wall surface of the discharge muffler body 1621 . The bearing part through-hole 1621c may be formed by simply passing through the upper wall surface of the discharge muffler body part 1621 . However, since the sub-bearing protrusion 1422 is inserted through the bearing part through-hole 1621c, a sealing member (unsigned) can be installed between the sub-bearing protrusion 1422 and the inner side of the discharge space 1621a. It may be formed into a cylindrical shape by bending.

In addition, as the rotation shaft 130 is inserted into the sub-bearing protrusion 1422 , 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 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. This will be explained again in the refueling department.

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 portion 132 and the sub bearing portion 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 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 an oil supply guide 176 and an 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 provided to be 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 a 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 sides forming the oil receiving space 1761 may be opened to form a guide outlet 1762 .

An oil supply guide protrusion 1763 that forms a part of the oil supply guide portion 175 may be formed on the outer peripheral surface of the guide outlet 1762 . 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 smoothly move to the oil supply passage hole 1771 by the oil supply guide protrusion 1763 .

Two oil supply guide protrusions 1763 may be formed symmetrically 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, the oil supply flow path 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 to supply the oil guided by the oil supply guide 176 toward 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, an 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 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 quickly 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, so a certain amount of oil remains in the oil supply storage groove 1772, and this oil is transferred to the vane ( 1445) and between the vane slot 1432 can be quickly supplied.

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.

This 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 refrigeration 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 rotation shaft 130, and the pumped oil is the oil pumping passage 172 through the rotation 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 transferred 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 the oil supply storage groove 1772 is formed on the outer periphery 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 the 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, and oil can be quickly supplied to the compression chamber (V) when the compressor is restarted. 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 this embodiment, as the internal space 110a of the shell 110 is a low-pressure compressor constituting the low-pressure part, the oil or refrigerant is supplied to 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. Part of the refrigerant that flows back 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 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 rotary compressor of the upper compression type and 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. there is.

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.

On the other hand, as the rotary compressor according to the present embodiment is of a dual-end support type, a main bearing part and a sub-bearing part are provided on both sides of the eccentric part, respectively, and the total length of the rotation shaft becomes long, and this increases the overall height of the compressor. may be detrimental to the miniaturization of Therefore, it may be advantageous to miniaturize the compressor only when the overall length of the rotating shaft is suppressed. In particular, when the rotary compressor according to the present embodiment is applied to a small product such as a water purifier, it is very important to reduce the height of the compressor to realize miniaturization.

In general, in a rotary compressor of both end support type, an eccentric portion is formed in the middle of a rotation shaft, and a main bearing portion is formed on one side of the eccentric portion and a sub-bearing portion is formed on the other side of the eccentric portion, respectively. Accordingly, the roller is inserted into the eccentric portion after passing through either one of the main bearing portion and the sub-bearing portion. At this time, in order for the roller to be inserted toward the bearing part (for example, the sub-bearing part) formed consecutively from the eccentric part, the outer peripheral surface of the eccentric part must protrude radially or at least the same as the outer peripheral surface of the sub-bearing part so that the roller is inserted without being caught in the eccentric part. can

If the outer circumferential surface of the eccentric is depressed in the radial direction than the outer circumferential surface of the sub-bearing part, one side of the inner circumferential surface of the roller is in close contact with the sub-bearing part, and the other side of the inner circumferential surface of the roller is caught on the axial side of the eccentric. Then, the roller cannot be inserted into the outer circumferential surface of the eccentric part while the movement toward the eccentric part is restricted by the sub-bearing part and the eccentric part. Therefore, to insert the annular roller into the eccentric part, the shortest eccentric radius of the eccentric part must be greater than or at least equal to the outer diameter of the bearing part.

However, when the shortest eccentric radius of the eccentric is greater than or at least equal to the outer diameter of the sub-bearing portion, the outer peripheral surface of the eccentric protrudes or at least becomes equal to the outer peripheral surface of the sub-bearing portion. Then, since the outer diameter of the bearing part must be reduced that much, the length of the sub-bearing part is increased in order to maintain an appropriate bearing area of the sub-bearing part. This is disadvantageous to miniaturization of the compressor.

In other words, since the outer diameter and the axial length of the bearing part are in inverse proportion to each other, increasing the outer diameter of the bearing part as much as possible reduces the axial length of the bearing part and is advantageous in miniaturizing the compressor.

In addition, the rotary compressor can achieve miniaturization and weight reduction of the compressor even by increasing the amount of eccentricity of the eccentric portion. That is, when the volume of the compression chamber of the rotary compressor is the same, by increasing the eccentricity of the eccentric, the outer diameter of the eccentric can be reduced. When the outer diameter of the eccentric portion is reduced, the outer diameter of the roller and the inner diameter of the cylinder are reduced, thereby making it possible to reduce the size and weight of the compressor. In addition, as the outer diameter of the eccentric portion decreases, the bearing load of both bearings is lowered, and the size of both bearing members can be reduced to the extent that the bearing load of the bearing is lowered, which is advantageous for downsizing and reducing the weight of the compressor.

However, in a state in which the outer diameter of the eccentric part that determines the volume of the compression part is determined, the structure similar to the conventional rotation shaft, that is, the structure in which the main bearing part and the sub-bearing part are adjacent to or sequentially formed on both sides of the eccentric part, is the main bearing part or There is a limit to reducing the outer diameter of the sub-bearing part.

Accordingly, in the present embodiment, a roller alignment unit capable of aligning the assembly position of the rollers may be formed in the middle of the rotation shaft applied to the rotary compressor of the both-end support type. Through this, it is possible to easily insert the roller into the eccentric part while increasing the outer diameter of the bearing part successively formed from the eccentric part to reduce the axial length to achieve miniaturization of the compressor.

In addition, by reducing the outer diameter of the eccentric by increasing the eccentricity of the eccentric under the condition that the volume of the compression chamber is the same due to the roller alignment part, it is possible to achieve miniaturization, weight reduction, and low vibration of the compressor.

8 is a perspective view showing the rotation shaft according to the present embodiment from one side, FIG. 9 is a perspective view showing the rotation shaft according to the present embodiment from the other side, and FIG. is an enlarged front view of the sub-bearing unit and the roller alignment unit in FIG. 10 , and FIG. 12 is a plan view showing the rotation shaft in the axial direction in FIG. 10 .

8 to 12 , the rotation shaft 130 according to this embodiment has a main bearing 141 provided on the lower side with respect to the cylinder 143 and a sub bearing 142 provided on the upper side with respect to the cylinder 143 as described above. each supported by Accordingly, the rotary shaft 130 forms a support type at both ends.

For example, the rotating shaft 130 according to this embodiment has a rotor coupling part 131 , a main bearing part 132 , a sub bearing part 133 , an eccentric part 134 , a roller alignment part 135 , and friction. It includes an avoidance part 136 .

The rotor coupling part 131 according to the present embodiment is a part press-fitted to the rotor core 1221 , and forms a lower end of the rotation shaft 130 . The lower end of the rotor coupling part 131 is extended longer than the lower end of the rotor 122 , and the inlet of the oil pumping hole 1721 is formed at the lower end of the rotor coupling part 131 , and the oil pumping hole 1721 is formed. An oil pump 173 may be installed at the inlet of the . The oil pumping hole 1721 and the oil pump 173 will be described in detail later while explaining the oil pumping passage 172 .

The outer diameter D1 of the rotor coupling part 131 may be formed to be substantially the same as the outer diameter D2 of the main bearing part 132 . Accordingly, on the inner peripheral surface of the rotor core 1221, the bearing insertion groove portion 1221a is formed so as to be stepped from the top to the bottom by a predetermined depth, so that the main bearing protrusion 1413 can be inserted.

The main bearing part 132 according to the present embodiment is a part that forms the main bearing surface Mb together with the main bearing 141 and is rotatably inserted into the main bearing hole 1413a.

The main bearing part 132 is formed on the same axis as the rotor coupling part 131 , and is continuously formed in the middle of the rotation shaft 130 , that is, at the upper end of the rotor coupling part 131 . Accordingly, the center of the main bearing surface Mb is located far from the center of the eccentric portion 134 , that is, the compression chamber, and thus the bearing load (lower bearing load) in the main bearing portion 132 is reduced.

The outer diameter D2 of the main bearing portion 132 is formed to be substantially the same as the outer diameter D1 of the rotor coupling portion 131 as described above, and is approximately the same as the inner diameter (unsigned) of the main bearing hole 1413a. is formed Accordingly, the oil flowing into the main bearing surface Mb through the oil supply hole 1722 forming a part of the oil pumping passage 172 does not flow down toward the rotor coupling portion 131, but rather of the oil pumping passage 172. Through the first oil supply groove 1723, which forms a part, it can be smoothly transferred toward the friction avoiding skin 136 located on the upper side of the main bearing part 132. (See FIG. 15)

The axial length L2 of the main bearing part 132 may be formed to be substantially the same as the axial length L1 of the rotor coupling part 131 . Accordingly, the main bearing part 132 may be formed to extend from the rotor coupling part 31 to have substantially the same standard.

The sub-bearing part 133 according to the present embodiment is a part that forms the sub-bearing surface Sb together with the sub-bearing 142, and is rotatably inserted into the sub-bearing hole 1413a.

The center P3 of the sub-bearing part 133 is formed on the same axis as the center P1 of the rotor coupling part 131 and the center P2 of the main bearing part 132, and the eccentric part 134 is formed on the same axis. It extends axially from the top. Accordingly, the center P3 of the sub-bearing portion 133 is located close to the center P4 of the eccentric portion 134, that is, the compression chamber V. Accordingly, the bearing load in the sub-bearing part 133 (the upper bearing load is greater than the bearing load (lower bearing load) in the main bearing part 132. Due to this (considering the gas reaction force in the compression chamber), the The bearing part 133 requires a larger bearing area than the main bearing part 132 .

The bearing area of the sub-bearing surface Sb is determined by the outer diameter or axial length of the sub-bearing part 133 . However, since the outer diameter of the sub-bearing part 133 affects the volumes of the discharge port 1423 , the discharge valve 145 , and the discharge muffler 162 , enlarging the outer diameter of the sub-bearing unit 133 is limited.

Since the axial length L3 of the sub-bearing part 133 affects the miniaturization of the compressor, the enlargement of the axial length L3 of the sub-bearing part 133 is also limited. In particular, when the compressor body (C) is supported in a spring-supported type, a large amount of fluctuation of the compressor body (C) occurs, so that a relatively large space in the longitudinal direction is required on the upper side of the shell 110 . Therefore, when the axial length L3 of the sub-bearing part 133 is increased, a larger space is required, and the compressor may eventually become enlarged.

Accordingly, the outer diameter D3 of the sub-bearing part 133 according to the present embodiment is formed smaller than the outer diameter D2 of the main bearing part 132, and is approximately equal to the outer diameter D6 of the friction avoiding skin 136, which will be described later. can be formed in the same way. The axial length L3 of the sub-bearing part 133 is approximately equal to the axial length L2 of the main bearing unit 132 or approximately equal to the axial length L5 of the roller alignment unit 135 to be described later Or it may be formed slightly larger or smaller.

However, in some cases, the outer diameter D3 of the sub-bearing part 133 is formed to be greater than or equal to the outer diameter D2 of the main bearing part 132, and the axial length L3 of the sub-bearing part 133 is It may be formed shorter than the axial length L2 of the main bearing part 132 .

The eccentric part 134 according to this embodiment is a part that transmits the rotational force of the electric part 120 to the vane roller 144, and the roller 1441 of the vane roller 144 described above is rotatably inserted into the cylinder ( 143), that is, accommodated in the space forming the compression chamber (V).

The eccentric part 134 is formed between the main bearing part 132 and the sub-bearing part 133 . Specifically, the eccentric part 134 is formed between the roller alignment part 135 and the sub-bearing part 133 .

The eccentric portion 134 is formed to be eccentric with respect to the rotor coupling portion 131 , the main bearing portion 132 , and the sub-bearing portion 133 . Accordingly, the eccentric part 134 makes a pivoting motion with respect to the axial center Os of the rotating shaft 130, and the roller 1441 of the vane roller 144 coupled to the eccentric part 134 is the cylinder 143. The refrigerant is compressed while rotating inside.

The outer diameter D4 of the eccentric part 134 is formed to be larger than the outer diameter D2 of the main bearing part 132 and the outer diameter D3 of the sub-bearing part 133 . That is, the outer diameter D4 of the eccentric portion 134 is formed to be larger than the inner diameter (unsigned) of the main bearing hole 1413a and the inner diameter (unsigned) of the sub-bearing hole 1422a. Accordingly, both sides of the eccentric portion 134 in the axial direction may be axially supported by the main plate portion 1411 of the main bearing 141 and the sub-plate portion 1421 of the sub-bearing 142 , respectively.

In addition, the axial length (axial height) L4 of the eccentric portion 134 is formed to be substantially equal to or smaller than the axial length (height) L7 of the roller 1441 . Accordingly, in order to insert the roller 1441 into the eccentric part 134 , the shortest eccentric radius D11 of the eccentric part 134 is the radius (first radius) D21 of the main bearing part 132 and the sub-bearing part It is advantageous in terms of assembly of the roller 1441 because the above-described roller insertable length can be secured when it is formed larger than the radius (second radius) D31 of (133).

Here, the shortest eccentric radius D41 of the eccentric part 134 is the radial length (or radial distance) connecting the outer peripheral surface of the eccentric part 134 from the axial center line (hereinafter, axial center) Os of the rotation shaft 130 . It is defined as the shortest length (or the shortest distance), and the radii D21 and D31 of each of the bearing parts 132 and 133 may be defined as radii from the axial center Os.

However, when the shortest eccentric radius D41 of the eccentric part 134 is greater than or equal to the radius D21 of the main bearing part 132 and the radius D31 of the sub-bearing part 133, the eccentric part 134 is Although it is advantageous in terms of assembly of the roller 1441 as the outer diameter D4 increases, the axial length L2 of the main bearing part 132 or the axial length L3 of the sub-bearing part 133 must be increased. It is disadvantageous to the miniaturization of This increases the inner diameter of the cylinder 143, which is more disadvantageous for miniaturization of the compressor, as well as increases the weight of the eccentric portion 134, which is disadvantageous for motor efficiency and low vibration of the compressor.

On the other hand, when the shortest eccentric radius D41 of the eccentric part 134 is formed smaller than the radius D21 of the main bearing part 132 and the radius D31 of the sub-bearing part 133, the outer peripheral surface of the main bearing part 132 Alternatively, the protruding portion A3 in which the outer circumferential surface of the sub-bearing portion 133 protrudes in a radial direction than the outer circumferential surface of the eccentric portion 134 is generated, making it difficult to assemble the roller.

Accordingly, in this embodiment, the shortest eccentric radius D41 of the eccentric part 134 is formed smaller than the radius D21 of the main bearing part 132 and the radius D31 of the sub-bearing part 133, and the eccentric part 134 ) adjacent one side, specifically, between the eccentric part 134 and the main bearing part 132, the roller alignment part 135 may be formed in succession. Accordingly, the shortest eccentric radius D41 of the eccentric portion 134 is formed smaller than the radius D21 of the main bearing portion 132 . Then, even if a part of the outer peripheral surface of the eccentric part 134 is depressed toward the axial center Os of the rotation shaft 130 rather than the outer peripheral surface of the main bearing part 132 , the roller 1441 before assembling the roller 1441 to the eccentric part 134 , the roller 1441 ) can adjust the assembly position of the roller 1441 so that it is assembled without being caught on the eccentric portion 134 . Then, the roller 1441 can be easily inserted into the eccentric portion 134 .

In other words, in this embodiment, the radius D21 of the main bearing part 132 or the radius D31 of the sub-bearing part 133 is greater than or equal to the shortest eccentric radius D41 of the eccentric part 134, so that the roller Even if the insertable length is not secured, the roller 1441 can be easily inserted into the eccentric part 134 using the roller alignment part 135 .

8 to 10 , the roller alignment part 135 according to this embodiment is a part for re-adjusting the assembly position before inserting the roller 1441 into the eccentric part 134 , and the roller alignment according to the present embodiment The portion 135 is continuously formed in a direction from the lower surface of the eccentric portion 134 toward the main bearing portion 132 .

For example, the roller alignment part 135 is depressed by a preset depth or has a stepped shape when viewed with respect to the main bearing part 132 . Accordingly, the outer diameter (D5) of the roller alignment part 135 is formed smaller than the outer diameter (D2) of the main bearing part (132).

The outer diameter D5 of the roller alignment part 135 may be smaller than the outer diameter D3 of the sub-bearing part 133 . Accordingly, when the center P5 of the roller alignment unit 135 is located on the same axis as the axis center Os of the rotation shaft 130, the radius (third radius) D51 of the roller alignment unit 135 is D51. may be formed to be smaller than the radius (second radius) D31 of the sub-bearing part 133 .

The center P5 of the roller alignment unit 135 may be formed to coincide with the axis center Os of the rotation shaft 130 . That is, the center (P5) of the roller alignment part 135 is the center (P6) of the friction avoidance part 136, the center (P2) of the main bearing part 132, and the center (P1) of the rotor coupling part 131 It can be formed to coincide with both. Accordingly, the roller alignment part 135 may be formed in an annular shape, whereby the oil flowing into the roller alignment part 135 through the friction avoidance part 136 is introduced into the second oil supply groove of the eccentric part 134 to be described later. 1724) can be transferred smoothly.

In addition, since the roller alignment unit 135 is a section in which the radial insertion position of the roller 1441 is adjusted and aligned as described above, the axial length L5 of the roller alignment unit 135 is at least that of the roller 1441 . It is preferable to be formed larger than the axial height (L7). Accordingly, the roller 1441 can be easily inserted into the eccentric part 134 while forming the inner diameter of the roller 1441 to be substantially the same as the outer diameter D4 of the eccentric part 134 .

13 is a view sequentially showing the process of coupling the roller to the eccentric portion of the rotation shaft according to the present embodiment.

First, as shown in Figure 13 (a), the roller 1441 is inserted from the lower end of the rotation shaft (130). At this time, as the inner diameter D7 of the roller 1441 is larger than the outer diameter D1 of the rotor coupling part 131 or the outer diameter D2 of the main bearing part 132), the center of the roller 1441 (P7) The axial center Os of the rotating shaft 130 and the center P4 of the eccentric portion 134 do not need to coincide with each other. In this state, the roller 1441 is in a free state.

Next, as shown in (b) of FIG. 13 , the roller 1441 is pushed up along the rotation shaft 130 to enter the roller alignment unit 135 . Even at this time, as the inner diameter D7 of the roller 1441 is formed larger than the outer diameter D5 of the roller alignment part 135, the center P7 of the roller 1441 and the axis center of the rotation shaft 130 (Os) and The center P4 of the eccentric portion 134 need not coincide. Therefore, even in this state, the roller 1441 maintains a free state in the eccentric state with respect to the eccentric portion 134 .

Next, as shown in (c) of FIG. 13 , the roller 1441 is moved in the radial direction so that the center P7 of the roller 1441 is aligned with the center P4 of the eccentric portion 134 . At this time, since the axial height (axial length) L4 of the roller 1441 is formed smaller than the axial length L5 of the roller alignment part 135, the roller 1441 freely moves in the radial direction. Therefore, the roller 1441 may align the assembly position in a state in which it is horizontally maintained with respect to the rotation shaft 130 .

Next, as shown in (d) of FIG. 13 , the roller 1441 is pushed up in the axial direction and inserted into the eccentric portion 134 . Here, the inner diameter D7 of the roller 1441 is formed to be substantially equal to the outer diameter D4 of the eccentric portion 134 , and the shortest eccentric radius D41 of the eccentric portion 134 is the radius of the roller alignment portion 135 . It is in a state formed to be greater than or equal to (D51). Accordingly, when the roller 1441 is inserted into the eccentric portion 134, it is possible to secure the roller insertable length. And in the step shown in Figure 13 (c), the roller 1441 is a state in which the center (P7) of the roller 1441 and the center (P4) of the eccentric part 134 in the roller alignment part 135 are matched, The roller 1441 can be easily inserted into the eccentric 134 .

In this way, the outer diameter of the bearing part according to the present embodiment is increased, so that the roller can be easily assembled to the eccentric part even in a state in which the outer peripheral surface of the eccentric part is depressed in the radial direction than the outer peripheral surface of the bearing part. Through this, the compressor can be miniaturized by increasing the outer diameter of the bearing part to secure the bearing area while reducing the axial length of the bearing part.

In addition, since the roller alignment part according to the present embodiment is formed on the side of the main bearing having a relatively free length with respect to the eccentric part, the overall length of the rotating shaft does not become long due to the roller alignment part, so that the compressor can be miniaturized.

In addition, the eccentric according to the present embodiment can reduce the outer diameter of the eccentric by the amount of the eccentric by the roller alignment part is increased. Accordingly, it is possible to reduce the size of the bearing by reducing the inner diameter of the cylinder and at the same time reducing the bearing load to achieve miniaturization, weight reduction, and low vibration of the compressor.

On the other hand, the rotary shaft 130 according to the present embodiment is further provided with an oil pumping unit 171 for supplying the oil stored in the lower portion of the shell 110 to the compression unit 140 . 14 is a perspective view showing the outer surface of the rotating shaft by breaking the bearing in order to explain a passage through which oil is pumped in the oil pumping unit according to the present embodiment, and FIG. 15 is a cross-sectional view showing the inner surface of the rotating shaft in FIG. 14 .

14 and 15 , the oil pumping unit 171 according to the present embodiment includes an oil pumping passage 172 and an oil pump 173 as described above.

A portion of the oil pumping passage 172 may be formed on the rotation shaft 130 , and a portion may be formed on the rotation shaft 130 or the main bearing 141 or sub bearing 142 facing the rotation shaft 130 . The oil pump 173 may be provided to communicate with the inlet end of the oil pumping passage 172 at the lower end of the rotation shaft 130 .

The oil pumping passage 172 is an oil pumping hole 1721, an oil supply hole 1722, a first oil supply groove 1723, a second oil supply groove 1724, and a third oil supply groove 1725 according to the order in which the oil is pumped. Made of, the oil supply communication groove 1726 may be provided between the second oil supply groove 1724 and the third oil supply groove 1725 .

The oil pumping hole 1721 may be formed to penetrate the inside of the rotation shaft 130 in the axial direction. Of course, the oil pumping hole 1721 may be formed to be inclined inside the rotation shaft 130, or may be formed up to a predetermined height from the lower end without penetrating the entire axial direction. However, in this embodiment, an example in which the oil pumping hole 1721 penetrates the inside of the rotation shaft 130 in the axial direction will be mainly described.

The oil pumping hole 1721 may be formed with the same inner diameter along the axial direction. However, the oil supply hole 1722 is formed at an intermediate height of the rotation shaft 130 , and a part of the pumped oil is transferred to the outside of the rotation shaft 130 . Accordingly, the oil pumping hole 1721 is a first pumping hole 1721a having a first inner diameter D81 up to the intermediate height, for example, the oil supply hole 1722, and the oil supply hole 1722 through the first inner diameter ( It may be formed as a second pumping hole 1721b having a second inner diameter D82 smaller than D81. Of course, the oil pumping hole 1721 may further include a third pumping hole (not shown) having a third inner diameter (not shown).

However, the inner diameter (unsigned) of the oil pumping hole 1721 is advantageous in terms of motor efficiency by reducing the weight of the rotary shaft 130 to be formed as large as possible within the range that satisfies the rigidity of the rotary shaft 130, and oil pumping It can be advantageous in terms of lubrication as it can lower the flow path resistance.

The inner peripheral surface of the first pumping hole 1721a may be formed in a smooth tube shape. However, a first internal oil supply groove (not shown) may be further formed so that a portion of the pumped oil can quickly move to the upper end of the rotary shaft 130 . The first internal refueling groove may be formed in a spiral shape, but may be formed in various other shapes.

The inner circumferential surface of the second pumping hole 1721b may be formed in a smooth tube shape. However, the second pumping hole (1721b), like the first pumping hole (1721a), a second internal oil supply groove (not shown) may be further formed. The second internal oil supply groove may be formed in a spiral shape like the first internal oil supply groove, but may be formed in various other shapes.

The oil supply hole 1722 serves to transfer the oil pumped to the first pumping hole 1721a toward the outer peripheral surface of the main bearing part 132 . Accordingly, the oil supply hole 1722 may be formed to penetrate from the inner peripheral surface of the oil pumping hole 1721 to the outer peripheral surface. Specifically, it may be formed by penetrating from the inner circumferential surface of the first pumping hole 1721a to the outer circumferential surface of the main bearing part 132 .

The oil supply hole 1722 is smaller than the first inner diameter D81 of the first pumping hole 1721a), and may be formed to be smaller than or equal to the second inner diameter D82 of the second pumping hole 1721b. Accordingly, a portion of the oil pumped to the first pumping hole 1721a may be divided into the oil supply hole 1722 , and the remainder may be divided into the second pumping hole 1721b and pumped.

At this time, when the inner diameter (D83) of the oil supply hole (1722) and the inner diameter (D82) of the second pumping hole are almost the same, the amount of oil pumped to both sides is similar, and the bearing surface (Ms) (Sb) is Of course, oil may be uniformly and quickly supplied to the compression unit 140 .

The first oil supply groove 1723 spreads the oil transferred to the outer peripheral surface of the main bearing part 132 through the oil supply hole 1722 from the main bearing surface Mb, and serves to transfer the oil toward the sub bearing part 133. do. Accordingly, the first oil supply groove 1723 is formed to have substantially the same cross-sectional area as the oil supply hole 1722 , is connected to the outer end of the oil supply hole 1722 and extends toward the roller alignment unit 135 .

For example, the first oil supply groove 1723 starts from the lower half of the main bearing part 132 and passes through the upper half of the main bearing part 132 and then passes through the friction avoidance skin 136 from the bottom to the top. can be

In other words, the first oil supply groove 1723 may be continuously formed along the outer circumferential surface of the main bearing portion 132 and the outer circumferential surface of the friction avoidance portion 136 . Accordingly, the first oil supply groove 1723 communicates with the oil supply hole 1722 , and the outlet of the first oil supply groove 1723 is a friction circuit forming a boundary between the friction avoidance part 136 and the roller alignment part 135 . It may be formed through the stepped surface 136a of the skin 136 .

The first oil supply groove 1723 may extend in the axial direction, and may extend in a spiral by a predetermined angle with respect to the axial direction.

However, when the first oil supply groove 1723 is formed to extend in the axial direction, the length of the first oil supply groove 1723 is shortened to the shortest distance, while the centrifugal force against the oil is weakened, so that the oil may not be transferred smoothly. Accordingly, it may be advantageous in terms of oil pumping that the first oil supply groove 1723 is formed in a spiral shape having an appropriate inclination angle with respect to the axial direction.

In addition, the oil passing through the first oil supply groove 1723 serves to lubricate the main bearing surface Mb. Therefore, if the first oil supply groove 1723 is formed to be long in the circumferential direction of the main bearing part 132, the bearing area can be enlarged, which can be advantageous in terms of lubrication. However, if the length of the first oil supply groove 1723 is too long, oil may be accumulated in the first oil supply groove 1723, so the turn angle of the first oil supply groove 1723 is approximately 180 to 360°. It may be formed in a shape. The turn angle of the first oil supply groove 1723 is proportional to the total length (L) of the rotating shaft 130 may be changed according to the capacity of the compressor.

The second oil supply groove 1724 serves to guide the oil transferred to the roller alignment unit 135 to be transferred toward the sub-bearing unit 133 through the eccentric unit 134 . Accordingly, the second oil supply groove 1724 is formed to have substantially the same cross-sectional area as the first oil supply groove 1723, and is formed by being recessed in the outer peripheral surface of the eccentric portion 134 or formed through the eccentric portion 134. can

The second oil supply groove 1724 according to the present embodiment may be formed to be recessed in the outer peripheral surface of the eccentric portion (134). In this case, the second oil supply groove 1724 may be formed in the vicinity of the position of the shortest eccentric radius (D41). Accordingly, when projected in the axial direction, the second oil supply groove 1724 may be formed at a position overlapping the roller alignment part 135 (see FIG. 4).

Then, while maintaining the contact area (torque transmission area) between the roller 1441 and the eccentric part 134 by minimizing the cross-sectional area of the second oil supply groove 1724, the second oil supply groove 1724 communicates with the roller alignment part 135. ), the passage area can be secured to the maximum.

Although not shown in the drawings, the second oil supply groove 1724 may be formed on the inner circumferential surface of the roller 1441 facing the outer circumferential surface of the eccentric portion 134 . However, since the roller 1441 is rotatably coupled with respect to the eccentric portion 134 , the oil supply amount may not be constant while the position of the second oil supply groove 1724 is changed. Therefore, if possible, it may be advantageous to form the second oil supply groove 1724 in the eccentric portion 134 .

The third oil supply groove 1725 diffuses the oil transferred to the outer peripheral surface of the sub-bearing part 133 through the second oil supply groove 1724 from the sub-bearing surface Sb, and is provided at the top of the rotation shaft 130 at the same time. It serves to transfer to the oil receiving space 1761 of the oil supply guide 176. Accordingly, the third oil supply groove 1725 is formed to have substantially the same cross-sectional area as the second oil supply groove 1724 , communicates with the second oil supply groove 1724 and extends toward the oil supply guide 176 .

The third oil supply groove 1725 may be formed in the axial direction like the first oil supply groove 1723, or it may be formed in a spiral shape. Even in this case, it is advantageous in terms of lubrication that the third oil supply groove 1725 is formed in a spiral shape.

The third oil supply groove 1725 may be formed on the outer peripheral surface of the sub-bearing part 133 constituting the rotation shaft 130, and may be formed on the inner peripheral surface of the sub-bearing hole 1422a forming the sub-bearing 142 facing it. there is. This embodiment shows an example in which the third oil supply groove 1725 is formed on the inner peripheral surface of the sub-bearing hole 1422a.

The third oil supply groove 1725 may be formed with an oil supply communication groove 1726 depending on the formation position thereof. For example, when the third oil supply groove 1725 is formed on the outer peripheral surface of the sub-bearing part 133, the third oil supply groove 1725 is directly connected to always communicate with the second oil supply groove 1724. can In this case, there may be no need to form a separate oil supply communication groove (1726).

However, when the third oil supply groove 1725 is formed on the inner peripheral surface of the sub-bearing hole 1422a, the position of the second oil supply groove 1724 varies according to the rotation of the rotating shaft 130, so the second oil supply groove 1724. And the third oil supply groove (1725) can not always communicate. Accordingly, the oil supply communication groove 1726 may be formed on the outer peripheral surface of the sub-bearing part 133 or the inner peripheral surface of the sub-bearing hole 1422a facing it.

Referring back to FIG. 4 , the oil supply communication groove 1726 passes through the second oil supply groove 1724 and passes the oil to the sub bearing unit 133 in the circumferential direction from the lower end of the sub bearing unit 133 as described above. It plays a role in spreading along. Accordingly, the oil supply communication groove 1726 may be formed in an annular shape at the lower end of the sub-bearing unit 133 , that is, at the lower end of the sub-bearing unit 133 connected to the upper surface of the eccentric unit 134 .

The cross-sectional area of the oil supply communication groove 1726 may be formed to be substantially the same as the cross-sectional area of the second oil supply groove 1724 or the third oil supply groove 1725 . Accordingly, the oil transferred to the oil supply communication groove 1726 through the second oil supply groove 1724 may be transferred to the third oil supply groove 1725 without clogging.

On the other hand, the oil pump 173 serves to pump the oil stored in the lower portion of the shell 110 toward the compression unit. The oil pump 173 may be variously applied, such as a positive displacement pump, a viscous pump, and a centrifugal pump. However, as described above, the gear pump and the viscous pump have a complicated structure and increase the number of parts and assembly work, which may increase the manufacturing cost. Accordingly, in this embodiment, a relatively simple and inexpensive centrifugal pump can be applied. Therefore, the pump described below as the oil pump 173 may be understood as a centrifugal pump unless specifically defined separately.

Referring back to FIGS. 14 and 15 , the oil pump 173 according to the present embodiment may include a pump housing 1731 and a pump blade 1732 .

The pump housing 1731 has an inlet end 1731a that has a conical shape gradually narrowing toward an open end, but may be formed in a cylindrical shape as a whole. The outlet end 1731b of the pump housing 1731 may be press-fitted to the outer peripheral surface of the lower end of the rotation shaft 130 to be fixedly coupled. If necessary, the outlet end of the pump housing may be fixed to the rotating shaft by spot welding or screwing.

The inner space of the pump housing 1731 is an empty space, and the pump blade 1732 is inserted and fixed. For example, a blade fixing groove 1731c may be formed in a side surface of the pump housing 1731 so that both sides of the pump blade 1732 are inserted and fixed.

The pump blade 1732 may include a blade body 1732a and a blade fixing protrusion 1732b.

The blade body 1732a may be formed in a simple flat plate shape, or may be twisted in a propeller shape if necessary.

The blade fixing protrusion 1732b may be formed to protrude radially from both sides of the blade body 1732a. The blade fixing protrusion 1732b is inserted and fixed in the blade fixing groove 1731c of the pump housing 1731 . Accordingly, even if the pump blade 1732 rotates at a high speed while being inserted into the pump housing 1731 , it is not detached from the pump housing 1731 and can smoothly and continuously pump oil.

The process of pumping the oil stored in the shell to the compression unit in the rotary compressor as described above is as follows.

That is, the oil pump 173 generates a pumping force while rotating together with the rotating shaft 130, and the oil stored in the shell by this pumping force is an oil pumping hole 1721 forming the inlet of the oil pumping passage 172. of the first pumping hole 1721a.

A portion of this oil is transferred along the first pumping hole 1721a, and then transferred toward the outer circumferential surface of the rotary shaft 130 through the oil supply hole 1722, and the rest of the oil is transferred along the second pumping hole 1721b along the upper end of the rotary shaft 130. is transferred to

The oil transferred to the oil supply hole 1722 is transferred to the roller alignment part 135 after lubricating the main bearing surface Mb along the first oil supply groove 1723 . At this time, the gap between the outer peripheral surface of the main bearing part 132 constituting the main bearing surface Mb and the inner peripheral surface of the main bearing hole 1413a is narrow, and the oil does not escape from the first oil supply groove 1723 and the first oil supply groove (1723) can be transferred.

In addition, as the outer diameter D6 of the friction avoiding skin 136 located on the upper side of the main bearing part 132 is formed smaller than the outer diameter D2 of the main bearing part 132, the outer peripheral surface of the friction avoiding skin 136 and The gap t2 between the inner peripheral surfaces of the main bearing hole 1413a is larger than the gap t1 in the main bearing surface Mb. However, the oil does not escape from the first oil supply groove 1723 by the stepped surface 132a of the main bearing part 132 forming the main bearing surface Mb on the lower side of the friction avoidance skin 136, and the first oil supply groove (1723) can be transferred.

The oil flowing into the roller alignment part 135 fills the inside of the roller alignment part 135 formed in an annular shape. The oil filling the roller alignment part 135 passes through the eccentric part 134 through the second oil supply groove 1724 and is then transferred to the sub-bearing part 133 . Accordingly, the oil transferred along the outer circumferential surface of the rotary shaft 130 smoothly lubricates the main bearing surface Mb, and at the same time, an oil communication space S is formed on the outer circumferential surface of the roller alignment unit 135 so that the oil is transferred to the rotary shaft. It can be transferred to the top of the 130 without leakage.

The oil transferred to the sub-bearing part 133 is transferred to the third oil supply groove 1725 through the annular oil supply communication groove 1726, and the oil is transferred to the rotation shaft 130 along the third oil supply groove 1725. As it moves to the top, it lubricates the sub-bearing surface (Sb).

The oil transferred to the upper end of the rotating shaft 130 is collected in the oil receiving space 1761 of the oil supply guide surrounding the upper end of the rotating shaft 130, and this oil is dispersed through the second pumping hole 1721b together with the oil. It is supplied to the compressor body (C) through the oil supply passage (177) described above.

On the other hand, the oil not supplied to the compressor body (C) flows down along the inner surface of the shell 110 or the outer surface of the compressor body (C) and is stored in the inner space 110a of the shell 110, and this oil is A series of processes supplied to the compressor body C through the oil pump 173 are repeated.

In this way, it is possible to smoothly pump the oil stored in the lower part of the shell to the upper end of the rotating shaft while applying an oil pump of a centrifugal pump to the lower end of the rotating shaft in the rotary compressor of the upper compression type and both end support type. As a result, an inexpensive oil pump can be used with a relatively simple structure and a small number of parts, thereby reducing the manufacturing cost of the compressor.

In addition, in the rotating shaft according to the present embodiment, the starting end of the oil supply groove may be disposed adjacent to the oil pump as the main bearing part is formed successively to the rotor coupling part in the lower half of the rotating shaft. Through this, centrifugal force against oil can be increased without increasing the outer diameter of the rotating shaft or increasing the length and number of turns of the oil supply groove. As a result, oil can be transferred to the upper end of the rotating shaft while applying an oil pump with a centrifugal pump.

In addition, in the rotating shaft according to the present embodiment, as the main bearing unit is formed in the lower half of the rotating shaft, it is possible to lower the bearing load of the main bearing unit. Through this, it is possible to increase the motor efficiency by reducing the diameter or length of the part corresponding to the main bearing on the rotating shaft. In addition, as the main bearing part is formed in the lower half of the rotating shaft, a roller alignment part may be formed between the main bearing part and the eccentric part, and through this, the roller can be easily assembled without increasing the length of the rotating shaft.

On the other hand, the case of another embodiment of the rotation shaft is as follows.

That is, in the above embodiments, the center of the roller alignment unit is formed to be positioned on the same axis as the axis center of the rotation shaft, but in some cases, the center of the roller alignment unit may be formed to be eccentric from the axis center of the rotation shaft.

16 is a perspective view showing another embodiment of the rotation shaft, and FIG. 17 is a front view of FIG. 16 .

16 and 17 , the rotating shaft 130 according to this embodiment has a rotor coupling part 131 , a main bearing part 132 , a sub bearing part 133 , and an eccentric part as in the above-described embodiments. 134 , a roller alignment part 135 and a friction avoidance part 136 .

The overall configuration of each of these parts constituting the rotation shaft 130 and the effect thereof are substantially the same as in the above-described embodiment, so a detailed description thereof is replaced with the description of the above-described embodiment.

However, in the rotation shaft 130 according to the present embodiment, the roller alignment part 135 may be formed eccentrically from the axial center Os of the rotation shaft 130 . For example, the outer diameter D5' of the roller alignment part 135 is formed to be substantially the same as the outer diameter D3 of the sub-bearing part 133, and the center P5 of the roller alignment part 135 is the rotation shaft 130 ) may be formed so that the center P4 of the eccentric portion 134 is spaced apart by a predetermined interval in the eccentric direction from the axial center Os.

Even in this case, the second shortest eccentric radius D52, which is the shortest length or shortest distance from the axial center Os of the rotating shaft 130 to the outer peripheral surface of the roller alignment part 135, is the second shortest eccentric radius of the eccentric part 134. 1 It must be formed to be less than or equal to the shortest eccentric radius (D41). Accordingly, the roller 1441 can be smoothly inserted into the eccentric part 134 after aligning the assembly position in the roller alignment part 135 .

The rotation shaft 130 according to the present embodiment is formed by extending the roller alignment part 135 in the eccentric direction of the eccentric part 134 , so that the outer diameter of the roller alignment part 135 may be enlarged. Through this, even if the amount of eccentricity of the eccentric part 134 increases, the rigidity of the roller alignment part 135 with respect to the rotation shaft 130 can be secured, and thus reliability can be maintained.

In addition, in this case, the oil communication space (S) formed between the outer peripheral surface of the roller alignment part 135 and the inner peripheral surface of the main bearing hole 1413a is formed in a crescent shape as much as the roller alignment part 135 is eccentric, The cross-sectional area of the oil communication space (S) adjacent to the second oil supply groove (1724) among the outer peripheral surface of the roller alignment part (135) may be enlarged. Then, the lateral area of the oil communication space (S) is reduced, the pumping path of oil passing through the oil communication space (S) is shortened, and the oil flowing into the oil receiving space can be quickly transferred to the second oil supply groove (1724). there is.

In addition, in this case, as the outer peripheral surface of the side where the roller alignment part 135 is eccentric is close to the inner peripheral surface of the main bearing hole 1413a, the outer peripheral surface opposite to the oil communication space S or the inner peripheral surface of the main bearing hole 1413a A connection oil supply groove 1727 may be further formed.

The connecting oil supply groove 1727 may be formed in a substantially spiral shape along the outer circumferential surface of the roller alignment part 135 or the inner circumferential surface of the main bearing hole 1413a. Accordingly, the oil in the oil communication space (S) can be transferred to the second oil supply groove (1724) more quickly.

On the other hand, another embodiment of the rotation shaft is as follows.

That is, in the above-described embodiments, the oil pumping hole is formed to penetrate the rotation shaft in the axial direction, but in some cases, the oil pumping hole may be formed only from the lower end to the middle height of the rotation shaft.

18 is a perspective view showing another embodiment of the rotation shaft, and FIG. 19 is a cross-sectional view of FIG. 18 .

18 and 19 , the rotation shaft 130 according to this embodiment has a rotor coupling part 131 , a main bearing part 132 , a sub bearing part 133 , and an eccentric part as in the above-described embodiments. 134 , a roller alignment part 135 and a friction avoidance part 136 .

In the rotary shaft 130 according to the present embodiment as described above, the oil pumping hole 1721, the oil supply hole 1722a, 1722b, the first oil supply groove 1723a, 1723b, and the second forming the oil pumping passage 172 are provided. The oil supply groove 1724, the third oil supply groove 1725, and the oil supply communication groove 1726 are formed.

The overall configuration of each of these parts constituting the rotation shaft 130 and the effect thereof are substantially the same as in the above-described embodiment, so a detailed description thereof is replaced with the description of the above-described embodiment.

However, the rotation shaft 130 according to the present embodiment has an oil pumping hole 1721 formed therein, and the oil pumping hole 1721 may be formed only from the lower end to the middle height of the rotation shaft 130 . For example, the oil pumping hole 1721 is formed only up to the range of the main bearing part 132 so that the oil supply holes 1722a and 1722b can communicate, and the friction avoidance part 136, the roller alignment part 135, The oil pumping hole may not be formed in the eccentric part 134 and the sub-bearing part 133 .

In other words, the oil pumping hole 1721 may be formed in the same shape as the so-called oil pumping groove blocked in the middle. Accordingly, a plurality of oil supply holes 1722a and 1722b may be formed. The plurality of oil supply holes 1722a and 1722b may be formed at equal intervals along the circumferential direction on the inner circumferential surface of the oil pumping hole 1721 .

As a plurality of oil supply holes 1722a and 1722b are formed, a plurality of first oil supply grooves 1723a and 1723b connected to each oil supply hole 1722a and 1722b may also be formed. The plurality of first oil supply grooves 1723 and 1723b may be spirally formed along the same direction as each other.

When the oil pumping hole 1721 is formed to the middle height of the rotation shaft 130 as described above, the outer diameter D5″ of the roller alignment part 135 can be formed smaller than that of the above-described embodiments. , it is possible to further reduce the outer diameter of the eccentric portion 134 by further increasing the amount of eccentricity of the eccentric portion (134).

In addition, when the outer diameter D5″ of the roller alignment unit 135 decreases, the volume of the oil communication space S formed between the outer circumferential surface of the roller alignment unit 135 and the inner circumferential surface of the main bearing hole 1413a increases and the pressure As the difference increases, the oil in the oil pumping hole 1721 can be quickly pulled up into the oil communication space (S).

In addition, when the oil pumping hole 1721 is formed up to the middle height of the rotation shaft 130 , the oil to be pumped is provided on the outer peripheral surface of the rotation shaft 130 , oil supply holes 1722a and 1722b and oil supply grooves 1723 and 1724 . ) 1725 and 1726, so that the oil supply amount to the main bearing surface Mb and the sub-bearing surface Sb can be increased. Through this, oil is smoothly supplied to each of the bearing surfaces Mb and Sb even during low-speed operation or initial start, and frictional losses at each bearing surface Mb and Sb can be reduced.

On the other hand, another embodiment of the rotation shaft is as follows.

That is, in the above embodiments, the roller alignment part is formed on the side of the main bearing part, but in some cases, the roller alignment part may be formed on the side of the sub bearing part.

20 is a perspective view showing another embodiment of the rotation shaft, and FIG. 21 is a cross-sectional view of FIG. 20 .

Referring to FIGS. 20 and 21 , the overall configuration of each of these parts constituting the rotation shaft 130 according to the present embodiment or the effect thereof are substantially the same as those of the above-described embodiment, so a detailed description thereof is given in the embodiment described above. replaced by an explanation for

However, in this embodiment, the roller alignment part 135 may be formed between the sub-bearing part 133 and the eccentric part 134 . Accordingly, the length from the upper surface of the eccentric part 134 to the upper end of the sub-bearing part 133 is increased compared to the above-described embodiments. It may be disadvantageous to the miniaturization and weight reduction of

However, in this embodiment, the main bearing part 132 may be continuously formed on the lower surface of the eccentric part 134 . That is, the main bearing part 132 may be formed at an upper end of the first part A1 of the rotation shaft 130 .

Then, the main bearing part 132 bears a part of the bearing load that the sub-bearing part 133 has to bear, and for this reason, if the outer diameter of the sub-bearing part 133 is the same as in the embodiment of FIG. The axial length L3 ′ of the sub-bearing part 133 may be reduced than the axial length L3 in the embodiment of FIG. 10 . Accordingly, it is possible to reduce the increase in the total length (L″) of the rotation shaft 130 is increased.

In addition, the outer diameter (D3) of the sub-bearing part 133 is larger than the outer diameter (D5) of the roller alignment part 135 and smaller than the outer diameter (D2) of the main bearing part 132 as in the embodiment of FIG. can be formed in the same way. Then, it is possible to secure the bearing area of the sub-bearing part 133, thereby minimizing the lengthening of the axial length L3' of the sub-bearing part 133, and through this, the total length L' of the rotating shaft 130 ) can be further reduced.

The rotating shaft 130 according to this embodiment minimizes oil leakage from the oil pumping passage 172 as the main bearing portion 132 extends from the lower surface of the eccentric portion 134, thereby effectively lubricating the bearing surface. there is. Through this, the friction loss on the bearing surface can be reduced and the compressor performance can be improved.

Also, in this case, the oil pump 173 may be a gear pump having a relatively superior pumping force compared to a centrifugal pump.

In the above, specific embodiments of the present invention have been shown and described. However, since the present invention can be embodied in various forms without departing from the spirit or essential characteristics thereof, the embodiments described above should not be limited by the content of the detailed description.

In addition, even the embodiments not listed in the detailed description described above should be broadly interpreted within the scope of the technical spirit defined in the appended claims. And, all changes and modifications included within the technical scope of the claims and their equivalents should be included by the appended claims.

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
132a: stepped surface 133: sub-bearing part
134: eccentric part 135: roller alignment part
136: friction avoidance skin 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
1422: sub bearing projection 1422a: sub bearing hole
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: vane hinge part
145: discharge valve 146: compression chamber 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 1613a: outlet extension
1614: suction muffler connection part 1615: muffler fixing part
1615a: fastening hole 1616: muffler fastening bolt
1617: muffler sealing member 162: discharge muffler
1621: discharge muffler body 1621a: discharge space
1621b: refrigerant discharge hole 1621c: bearing part through hole
1622: discharge muffler fixing part 170: oil supply part
171: oil pumping unit 172: oil pumping passage
1721: oil pumping hole 1721a: first pumping hole
1721b: 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
1731a: inlet end of the pump housing 1731b: outlet end of the pump housing
1731c: blade fixing groove 1732: pump blade
1732a: blade body 1732b: blade fixing projection
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 supply storage home
1773: non-return valve 1773a: fixed part
1773b: opening/closing unit 1774: refueling guide pipe
A1: first part of the axis of rotation A2: second part of the axis of rotation
A3: Projected part C: Compressor body
D1: outer diameter of rotor coupling part D2: outer diameter of main bearing part
D21: Radius (first radius) of the main bearing part D3: Outer diameter of the sub-bearing part
D31: Radius of sub-bearing part (second radius) D3': Inner diameter of sub-bearing hole
D4: outer diameter of the eccentric
D41: Shortest eccentric radius of the eccentric (first shortest eccentric radius)
D5,D5',D5": outer diameter of roller alignment part D51: radius of roller alignment part (third radius)
D52: Shortest eccentric radius of roller alignment part (second shortest eccentric radius)
D7: inner diameter of roller D81: first inner diameter of oil pumping hole
D82: Second inner diameter of oil pumping hole D83: Inner diameter of oil supply hole
L: Total length of the rotating shaft L1: Axial length of the rotor coupling part
L2: Axial length of main bearing part L3: Axial length of sub bearing part
L5: Axial length (height) of the roller alignment part L7: Axial length (height) of the roller
P1: Center of rotor coupling part P2: Center of main bearing part
P3: Center of sub-bearing part P4: Center of eccentric part
P5: Center of roller alignment part P6: Center of friction avoidance skin
P7: Center of roller Mb: Main bearing surface
Sb: Sub-bearing surface Os: Axial center of the rotating shaft
S: Oil communication space V: Compression chamber

Claims (28)

a shell having an inner space to store oil;
an electric part provided in the inner space of the shell;
a cylinder provided at one axial direction of the electric part in the inner space of the shell to form a compression chamber;
a main bearing and a sub-bearing coupled to both sides of the cylinder in the axial direction to form the compression chamber together with the cylinder;
A main bearing part and a sub-bearing accommodated in the compression chamber of the cylinder and provided on both sides in the axial direction with an eccentric part with respect to the axial center and the eccentric part interposed therebetween and supported in a radial direction by the main bearing and the sub-bearing, respectively. a rotating shaft comprising a part; and
A roller formed in an annular shape and inserted into the outer circumferential surface of the eccentric portion;
A roller alignment part is formed on one side of the axial direction of the eccentric part on the rotating shaft, and an axial length of the roller alignment part is formed to be longer than an axial length of the roller. According to claim 1,
The radius of the main bearing part or the radius of the sub-bearing part is greater than or equal to the shortest eccentric radius of the eccentric part,
A radius of the roller alignment part is formed smaller than the shortest eccentric radius of the eccentric part. According to claim 1,
The center of the roller alignment part is formed to be located on the same axis as the center of the main bearing part or the center of the sub-bearing part. According to claim 1,
The center of the roller alignment part is formed at a position eccentric from the center of the main bearing part or the center of the sub-bearing part. According to claim 1,
The main bearing part extends toward the electric part based on the eccentric part,
The roller alignment part is formed between the eccentric part and the main bearing part. According to claim 1,
The outer diameter of the sub-bearing part is formed to be larger than the outer diameter of the roller alignment part. According to claim 1,
The axial length of the sub-bearing part is shorter than or equal to the axial length of the roller alignment part. According to claim 1,
A friction avoidance skin is further formed between the main bearing part and the roller alignment part,
The outer diameter of the friction avoidance is smaller than the outer diameter of the main bearing portion and is formed larger than the outer diameter of the roller alignment unit. 9. The method of claim 8,
The center of the friction avoidance rotary compressor is formed on the same axis as the axis center of the rotation shaft. According to claim 1,
A first radius is the distance from the axial center of the rotating shaft to the outer peripheral surface of the main bearing part, a second radius is the distance from the axial center of the rotating shaft to the outer peripheral surface of the sub-bearing part, and the shortest distance from the axial center of the rotating shaft to the eccentric part When is the first shortest eccentric radius,
The first radius and the second radius are formed to be greater than or equal to the first shortest eccentric radius. 11. The method of claim 10,
The center of the roller alignment part is formed on the same axis with respect to the axial center of the rotation shaft,
A third radius constituting the radius of the roller alignment part is formed to be smaller than the first shortest eccentric radius. 11. The method of claim 10,
The center of the roller alignment part is formed to be eccentric with respect to the axial center of the rotation shaft, and the shortest distance from the axial center of the rotation shaft to the outer peripheral surface of the roller alignment part is the second shortest eccentric radius,
The second shortest eccentric radius is a rotary compressor that is formed smaller than the first shortest eccentric radius. According to claim 1,
When the axial distance from the center of the main bearing part to the center of the eccentric part is a first axial distance, and the axial distance from the center of the sub-bearing part to the center of the eccentric part is a second axial distance,
The second axial distance is shorter than the first axial distance, and the roller alignment part is formed between the main bearing part and the eccentric part. 14. The method of claim 13,
A friction avoidance skin is further formed between the main bearing part and the roller alignment part,
The center of the friction avoidance is formed on the same axis as the axial center of the rotation shaft, and the outer diameter of the friction avoidance is smaller than the outer diameter of the main bearing part and larger than the outer diameter of the roller alignment part. According to claim 1,
The sub-bearing part is formed to extend in the opposite direction to the electric part based on the eccentric part,
The roller alignment part is formed between the sub-bearing part and the eccentric part. 16. The method of claim 15,
The shortest eccentric radius of the eccentric is less than or equal to the radius of the sub-bearing part,
A radius of the roller alignment part is formed smaller than the shortest eccentric radius of the eccentric part. According to claim 1,
An oil pump is provided at the end of the rotating shaft toward the main bearing to pump the oil stored in the inner space of the shell,
An oil pumping passage for guiding the oil pumped by the oil pump to the other end of the rotary shaft is formed in the rotary shaft. 18. The method of claim 17,
The oil pump is a centrifugal pump, and the main bearing part is formed to be located at a lower end of the main bearing. 18. The method of claim 17,
An oil pumping hole is formed at an end of the rotation shaft on the main bearing part side, and the oil supply hole penetrates from an inner peripheral surface of the oil pumping hole to an outer peripheral surface of the main bearing part,
A first oil supply groove is formed in the outer peripheral surface of the rotating shaft to communicate the oil supply hole between the outer peripheral surface of the roller alignment part and the inner peripheral surface of the main bearing facing it. 20. The method of claim 19,
A friction avoidance skin is formed between the main bearing part and the roller alignment part, and the outer diameter of the friction avoidance part is smaller than the outer diameter of the main bearing part and larger than the outer diameter of the roller alignment part,
The first oil supply groove is extended along the outer peripheral surface of the friction avoidance rotary compressor passing through the step surface forming a boundary between the friction avoidance and the roller alignment part. 18. The method of claim 17,
A second oil supply groove is formed in the eccentric portion to communicate both sides in the axial direction,
The second oil supply groove is recessed by a predetermined depth from the outer peripheral surface of the eccentric part rotary compressor for communicating between both sides of the axial direction of the eccentric part. 22. The method of claim 21,
A rotary compressor in which a third oil supply groove is formed on an outer peripheral surface of the sub-bearing part or an inner peripheral surface of the sub-bearing facing the same. 23. The method of claim 22,
An oil supply communication groove is formed between the second oil supply groove and the third oil supply groove,
The oil supply communication groove is formed in an annular shape on the outer peripheral surface of the sub-bearing part extending from the eccentric part. 24. The method according to any one of claims 1 to 23,
The cylinder is provided on the upper side in the axial direction of the electric part,
The electric part 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. 25. The method of claim 24,
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. 26. The method of claim 25,
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. 26. The method of claim 25,
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. 26. The method of claim 25,
An oil supply guide is provided on the upper side of the rotating 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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