KR20210079030A - Compressor - Google Patents

Abstract

Disclosed is a compressor. The compressor according to the present specification comprises: a frame including a main body accommodating a cylinder, a protrusion unit protruding outwardly from the main body, and a first coupling unit formed at a rear end of the protrusion unit; an inner stator including a second coupling unit, formed at a front end and coupled to the first coupling unit, and a first groove formed at a rear end, and disposed on the outer circumferential surface of the frame; and a fixation ring disposed in the first groove and pressing the inner stator inward. An object of the present invention is to provide the compressor capable of preventing occurrence of tolerances between components.

Description

Compressor {COMPRESSOR}

This specification relates to a compressor. More particularly, it relates to a linear compressor that compresses a refrigerant by a linear reciprocating motion of a piston.

In general, a compressor refers to a device configured to compress a working fluid such as air or a refrigerant by receiving power from a power generating device such as a motor or a turbine. Specifically, the compressor is widely applied to the entire industry, home appliances, in particular, a vapor compression refrigeration cycle (hereinafter referred to as a 'refrigeration cycle').

Such a compressor may be classified into a reciprocating compressor, a rotary compressor (rotary compressor), and a scroll compressor according to a method of compressing the refrigerant.

In the reciprocating compressor, a compression space is formed between the piston and the cylinder and the piston moves linearly to compress the fluid. The rotary compressor compresses the fluid by eccentrically rotating rollers inside the cylinder, and the scroll compressor is a spiral It is a method of compressing the fluid by rotating a pair of scrolls in engagement.

Recently, among reciprocating compressors, the use of a linear compressor using a linear reciprocating motion without using a crankshaft is gradually increasing. The linear compressor has advantages in that the efficiency of the compressor is improved because the mechanical loss involved in converting the rotary motion into a linear reciprocating motion is small, and the structure is relatively simple.

The linear compressor is configured such that a cylinder is positioned inside a casing forming a closed space to form a compression chamber, and a piston covering the compression chamber reciprocates within the cylinder. In a linear compressor, the fluid in the enclosed space is sucked into the compression chamber when the piston is positioned at the bottom dead center (BDC), and the fluid in the compression chamber is sucked into the compression chamber when the piston is positioned at the top dead center (TDC, Top Dead Center). The process of being compressed and discharged is repeated.

A compression unit and a driving unit are respectively installed inside the linear compressor, and through movement generated in the driving unit, the compression unit performs a process of compressing and discharging refrigerant while resonating by a resonance spring.

The piston of the linear compressor sucks the refrigerant into the casing through the suction pipe while reciprocating at high speed inside the cylinder by the resonance spring, and then is discharged from the compression space through the forward movement of the piston and moves to the condenser through the discharge pipe. A series of processes are repeatedly performed.

Referring to FIG. 8 , in Korean Patent Application Laid-Open No. 2003-00661527, an inner stator 1030 (inner stator) is adhesively fixed to the outer circumferential surface of the cylinder 1010 by an adhesive (epoxy). At this time, the stator 1030 is fixed to the outer circumferential surface of the cylinder 1010 by spirally coupling the male screw 1020 formed on one end of the cylinder 1010 and the female screw 1050 formed on the inner surface of the fixing ring 1040 . do.

However, in the case of helical bonding, there was a problem in that foreign matter was generated and tolerances between the components were generated.

Korean Patent Publication No. 2003-00661527 A (2003.08.09. Announcement)

An object to be solved by the present specification is to provide a compressor capable of preventing the occurrence of foreign substances and the occurrence of tolerances between components.

A compressor according to an aspect of the present specification for achieving the above object is a frame including a body accommodating a cylinder, a protrusion protruding outwardly from the body, and a first coupling portion formed at the rear end of the protrusion ; an inner stator formed at the front end and including a second coupling part coupled to the first coupling part, and a first groove formed at the rear end, disposed on an outer circumferential surface of the frame; and a fixing ring disposed in the first groove and urging the inner stator inward.

In addition, the first coupling portion may include a first coupling groove formed in a region in contact with the main body of the rear end of the protrusion.

In addition, the second coupling part may include a first coupling protrusion that protrudes forward from the front end of the inner stator and is disposed in the first coupling groove.

In addition, the frame may include a second coupling protrusion extending rearward from the outside of the first coupling groove, and the inner stator may include a second coupling groove formed at a rear end and in which the second coupling protrusion is disposed. .

Also, the inner stator may include a third coupling protrusion extending forward from the outside of the second coupling groove, and an inner surface of the third coupling protrusion may be disposed on an outer surface of the second coupling protrusion.

In addition, the third coupling protrusion may protrude forward than the first coupling protrusion.

In addition, a thickness of the third coupling protrusion in the first direction may be greater than a thickness of the first coupling protrusion in the first direction.

In addition, the inner stator may include a first protrusion formed inside the first groove and a second protrusion formed outside the first groove, and the second protrusion may protrude rearward than the first protrusion. have.

Also, a thickness of the second protrusion in the first direction may be greater than a thickness of the first protrusion in the first direction.

Also, a length of the first groove in a second direction may be greater than a length of the fixing ring in the second direction.

In addition, the fixing ring may be formed of a non-magnetic material.

Through the present specification, it is possible to provide a compressor capable of preventing the occurrence of foreign substances and the occurrence of tolerances between components.

1 is a perspective view of a compressor according to an embodiment of the present specification.
2 is a cross-sectional view of a compressor according to an embodiment of the present specification.
3 is a perspective view of an inner stator fixing structure according to an embodiment of the present specification.
4 is an exploded perspective view of an inner stator fixing structure according to an embodiment of the present specification.
5 is a cross-sectional view of an inner stator fixing structure according to an embodiment of the present specification.
6 is an enlarged view of part 'A' of FIG. 5 .
7 is a cross-sectional view of an inner stator according to an embodiment of the present specification.
8 is a cross-sectional view of an inner stator fixing structure according to the related art.

Hereinafter, the embodiments disclosed in the present specification (discloser) will be described in detail with reference to the accompanying drawings, but the same or similar components are assigned the same reference numbers regardless of reference numerals, and redundant description thereof will be omitted.

In the description of the embodiments disclosed herein, when a component is referred to as “connected” or “connected” to another component, it may be directly connected or connected to the other component, but It should be understood that other components may exist in between.

In addition, in describing the embodiments disclosed in the present specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in the present specification, the detailed description thereof will be omitted. In addition, the accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and the technical spirit disclosed herein is not limited by the accompanying drawings, and all changes included in the spirit and scope of the present specification , should be understood to include equivalents or substitutes.

On the other hand, the terms of the specification (discloser) can be replaced with terms such as document, specification, description.

1 is a perspective view of a compressor according to an embodiment of the present specification.

Referring to FIG. 1 , the linear compressor 100 according to an embodiment of the present specification may include a shell 111 and shell covers 112 and 113 coupled to the shell 111 . In a broad sense, the shell covers 112 and 113 may be understood as one configuration of the shell 111 .

The lower side of the shell 111, the leg 20 may be coupled. The leg 20 may be coupled to the base of the product on which the linear compressor 100 is installed. For example, the product may include a refrigerator, and the base may include a machine room base of the refrigerator. As another example, the product may include the outdoor unit of the air conditioner, and the base may include the base of the outdoor unit.

The shell 111 has a substantially cylindrical shape, and may form an arrangement lying in a transverse direction or an arrangement lying in an axial direction. Referring to FIG. 1 , the shell 111 extends long in the horizontal direction, and may have a rather low height in the radial direction. That is, since the linear compressor 100 may have a low height, for example, when the linear compressor 100 is installed at the base of the machine room of the refrigerator, there is an advantage that the height of the machine room can be reduced.

In addition, the longitudinal central axis of the shell 111 coincides with the central axis of the main body of the compressor 100 to be described later, and the central axis of the main body of the compressor 100 is the cylinder 140 and the piston constituting the main body of the compressor 100 . coincides with the central axis of (150).

The terminal 30 may be installed on the outer surface of the shell 111 . The terminal 30 may transmit external power to the driving unit 130 of the linear compressor 100 . Specifically, the terminal 30 may be connected to a lead wire of the coil 132b.

A bracket 31 may be installed on the outside of the terminal 30 . The bracket 31 may include a plurality of brackets surrounding the terminal 30 . The bracket 31 may function to protect the terminal 30 from an external impact.

Both sides of the shell 111 may be open. Shell covers 112 and 113 may be coupled to both sides of the opened shell 111 . Specifically, the shell covers 112 and 113 include a first shell cover 112 coupled to one open side of the shell 111 and a second shell cover 113 coupled to the other open side of the shell 111 . ) may be included. The inner space of the shell 111 may be sealed by the shell covers 112 and 113 .

Referring to FIG. 1 , the first shell cover 112 may be located on the right side of the linear compressor 100 , and the second shell cover 113 may be located on the left side of the linear compressor 100 . In other words, the first and second shell covers 112 and 113 may be disposed to face each other. In addition, it may be understood that the first shell cover 112 is located on the suction side of the refrigerant, and the second shell cover 113 is located on the discharge side of the refrigerant.

The linear compressor 100 is provided on the shell 111 or the shell covers 112 and 113 and may include a plurality of pipes 114 , 115 , and 40 capable of sucking, discharging, or injecting refrigerant.

A plurality of pipes (114, 115, 40) is a suction pipe (114) for allowing the refrigerant to be sucked into the linear compressor (100), and a discharge pipe (115) for allowing the compressed refrigerant to be discharged from the linear compressor (100), It may include a replenishment pipe 40 for replenishing the refrigerant to the linear compressor 100 .

For example, the suction pipe 114 may be coupled to the first shell cover 112 . The refrigerant may be sucked into the linear compressor 100 along the axial direction through the suction pipe 114 .

The discharge pipe 115 may be coupled to the outer peripheral surface of the shell 111 . The refrigerant sucked through the suction pipe 114 may be compressed while flowing in the axial direction. And the compressed refrigerant may be discharged through the discharge pipe (115). The discharge pipe 115 may be disposed at a position closer to the second shell cover 113 than the first shell cover 112 .

The supplementary pipe 40 may be coupled to the outer circumferential surface of the shell 111 . The operator may inject the refrigerant into the linear compressor 100 through the supplementary pipe 40 .

The supplementary pipe 40 may be coupled to the shell 111 at a different height from the discharge pipe 115 in order to avoid interference with the discharge pipe 115 . Here, the height may be understood as the distance in the vertical direction from the leg 20 . As the discharge pipe 115 and the supplement pipe 40 are coupled to the outer peripheral surface of the shell 111 at different heights, work convenience can be promoted.

At least a portion of the second shell cover 113 may be adjacent to the inner circumferential surface of the shell 111 corresponding to the point at which the supplementary pipe 40 is coupled. In other words, at least a portion of the second shell cover 113 may act as a resistance of the refrigerant injected through the supplementary pipe 40 .

Therefore, from the viewpoint of the flow path of the refrigerant, the size of the flow path of the refrigerant introduced through the supplementary pipe 40 is reduced by the second shell cover 113 while entering the inner space of the shell 111, and becomes larger again as it passes through. is formed to In this process, the pressure of the refrigerant is reduced and the refrigerant may be vaporized, and in this process, the oil contained in the refrigerant may be separated. Accordingly, as the refrigerant from which the oil is separated flows into the interior of the piston 150, the compression performance of the refrigerant may be improved. Oil can be understood as the hydraulic fluid present in the cooling system.

2 is a cross-sectional view for explaining the structure of the compressor 100 .

Hereinafter, the compressor according to the present specification will be described as an example of a linear compressor in which a piston sucks and compresses a fluid while linear reciprocating motion, and discharges the compressed fluid.

The linear compressor may be a component of a refrigeration cycle, and the fluid compressed in the linear compressor may be a refrigerant circulating in the refrigeration cycle. The refrigeration cycle may include a condenser, an expansion device and an evaporator in addition to the compressor. In addition, the linear compressor may be used as one component of the cooling system of the refrigerator, and is not limited thereto, and may be widely used throughout the industry.

Referring to FIG. 2 , the compressor 100 may include a casing 110 and a body accommodated in the casing 110 . The main body of the compressor 100 includes a frame 120 , a cylinder 140 fixed to the frame 120 , a piston 150 linearly reciprocating within the cylinder 140 , and a piston fixed to the frame 120 . It may include a driving unit 130 that applies a driving force to 150 . Here, the cylinder 140 and the piston 150 may be referred to as compression units 140 and 150 .

The compressor 100 may include bearing means for reducing friction between the cylinder 140 and the piston 150 . The bearing means may be oil bearings or gas bearings. Alternatively, a mechanical bearing may be used as the bearing means.

The main body of the compressor 100 may be elastically supported by support springs 116 and 117 installed at both inner ends of the casing 110 . The support springs 116 and 117 may include a first support spring 116 for supporting the rear of the body and a second support spring 117 for supporting the front of the body. The support springs 116 and 117 may include leaf springs. The support springs 116 and 117 may absorb vibrations and shocks generated according to the reciprocating motion of the piston 150 while supporting the internal components of the main body of the compressor 100 .

The casing 110 may form an enclosed space. The sealed space includes an accommodation space 101 accommodating the sucked refrigerant, a suction space 102 filled with the refrigerant before being compressed, a compression space 103 for compressing the refrigerant, and a discharge space filled with the compressed refrigerant ( 104) may be included.

The refrigerant sucked from the suction pipe 114 connected to the rear side of the casing 110 is filled in the receiving space 101 , and the refrigerant in the suction space 102 communicating with the receiving space 101 is compressed in the compression space 103 . is discharged to the discharge space 104 , and may be discharged to the outside through the discharge pipe 115 connected to the front side of the casing 110 .

The casing 110 includes a shell 111 having both ends open and formed in a substantially transversely long cylindrical shape, a first shell cover 112 coupled to the rear side of the shell 111, and a second coupled to the front side. It may include a shell cover 113 . Here, the front side may be interpreted to mean a direction in which the compressed refrigerant is discharged to the left of the drawing, and the rear side may be interpreted to mean a direction in which the refrigerant is introduced to the right side of the drawing. In addition, the first shell cover 112 or the second shell cover 113 may be integrally formed with the shell 111 .

The casing 110 may be formed of a thermally conductive material. Through this, the heat generated in the inner space of the casing 110 can be quickly radiated to the outside.

The first shell cover 112 may be coupled to the shell 111 to seal the rear side of the shell 111 , and the suction pipe 114 may be inserted and coupled to the center of the first shell cover 112 .

The rear side of the main body of the compressor 100 may be elastically supported in the radial direction of the first shell cover 112 by the first support spring 116 .

The first support spring 116 may include a circular leaf spring. The edge of the first support spring 116 may be elastically supported in the forward direction with respect to the back cover 123 by the support bracket 123a. The opened central portion of the first support spring 116 may be supported in a rearward direction with respect to the first shell cover 112 by the suction guide 116a.

The suction guide 116a may have a through passage formed therein. The suction guide 116a may be formed in a cylindrical shape. The suction guide 116a may be coupled to the central opening of the first support spring 116 to the front outer circumferential surface, and the rear end may be supported by the first shell cover 112 . At this time, a separate suction-side support member 116b may be interposed between the suction guide 116a and the inner surface of the first shell cover 112 .

The rear side of the suction guide 116a communicates with the suction pipe 114 , and the refrigerant sucked through the suction pipe 114 passes through the suction guide 116a and can be smoothly introduced into the muffler unit 160 to be described later.

A damping member 116c may be disposed between the suction guide 116a and the suction-side support member 116b. The damping member 116c may be formed of a rubber material or the like. Accordingly, it is possible to block the vibration that may be generated while the refrigerant is sucked through the suction pipe 114 from being transmitted to the first shell cover 112 .

The second shell cover 113 may be coupled to the shell 111 to seal the front side of the shell 111 , and the discharge pipe 115 may be inserted through the roof pipe 115a to be coupled thereto. The refrigerant discharged from the compression space 103 may be discharged into the refrigerating cycle through the loop pipe 115a and the discharge pipe 115 after passing through the discharge cover assembly 180 .

The front side of the main body of the compressor 100 may be elastically supported in the radial direction of the shell 111 or the second shell cover 113 by the second support spring 117 .

The second support spring 117 may include a circular leaf spring. The opened central portion of the second support spring 117 may be supported in a rearward direction with respect to the discharge cover assembly 180 by the first support guide 117b. The edge portion of the second support spring 117 may be supported in the forward direction with respect to the inner surface of the shell 111 or the inner peripheral surface of the shell 111 adjacent to the second shell cover 113 by the support bracket 117a. .

Unlike FIG. 2 , the edge of the second support spring 117 is adjacent to the inner surface of the shell 111 or the second shell cover 113 through a separate bracket (not shown) coupled to the second shell cover 113 . It may be supported in the forward direction with respect to the inner circumferential surface of the shell 111 .

The first support guide 117b may be formed in a cylindrical shape. A cross-section of the first support guide 117 may include a plurality of diameters. The front side of the first support guide 117 may be inserted into the central opening of the second support spring 117 , and the rear side may be inserted into the central opening of the discharge cover assembly 180 . The support cover 117c may be coupled to the front side of the first support guide 117b with the second support spring 117 interposed therebetween. A cup-shaped second support guide 117d concave in the front may be coupled to the front side of the support cover 117c. A cup-shaped third support guide 117e corresponding to the second support guide 117d and recessed rearward may be coupled to the inside of the second shell cover 113 . The second support guide 117d may be inserted into the inside of the third support guide 117e to be supported in the axial direction and/or the radial direction. In this case, a gap may be formed between the second support guide 117d and the third support guide 117e.

The frame 120 may include a body portion 121 supporting the outer circumferential surface of the cylinder 140 , and a first flange portion 122 connected to one side of the body portion 121 and supporting the driving unit 130 . can The frame 120 may be elastically supported with respect to the casing 110 by the first and second support springs 116 and 117 together with the driving unit 130 and the cylinder 140 .

The body portion 121 may surround the outer circumferential surface of the cylinder 140 . The body part 121 may be formed in a cylindrical shape. The first flange part 122 may be formed to extend radially from the front end of the body part 121 .

A cylinder 140 may be coupled to the inner circumferential surface of the body portion 121 . An inner stator 134 may be coupled to an outer circumferential surface of the body portion 121 . For example, the cylinder 140 may be fixed to the inner circumferential surface of the body portion 121 by press fitting, and the inner stator 134 may be fixed using a separate fixing ring (not shown).

The outer stator 131 may be coupled to the rear surface of the first flange part 122 , and the discharge cover assembly 180 may be coupled to the front surface thereof. For example, the outer stator 131 and the discharge cover assembly 180 may be fixed through a mechanical coupling means.

A bearing inlet groove 125a constituting a part of the gas bearing is formed on one side of the front surface of the first flange portion 122 , and a bearing communication hole 125b penetrates from the bearing inlet groove 125a to the inner circumferential surface of the body portion 121 . ) is formed, and a gas groove 125c communicating with the bearing communication hole 125b may be formed on the inner circumferential surface of the body portion 121 .

The bearing inlet groove 125a is formed by being depressed in the axial direction to a predetermined depth, and the bearing communication hole 125b is a hole having a smaller cross-sectional area than the bearing inlet groove 125a and is inclined toward the inner circumferential surface of the body portion 121. can In addition, the gas groove 125c may be formed in an annular shape having a predetermined depth and an axial length on the inner peripheral surface of the body portion 121 . Alternatively, the gas groove 125c may be formed on the outer circumferential surface of the cylinder 140 in contact with the inner circumferential surface of the body portion 121 or may be formed on both the inner circumferential surface of the body portion 121 and the outer circumferential surface of the cylinder 140 .

In addition, a gas inlet 142 corresponding to the gas groove 125c may be formed on the outer peripheral surface of the cylinder 140 . The gas inlet 142 forms a kind of nozzle part in the gas bearing.

Meanwhile, the frame 120 and the cylinder 140 may be formed of aluminum or an aluminum alloy material.

The cylinder 140 may be formed in a cylindrical shape in which both ends are open. The piston 150 may be inserted through the rear end of the cylinder 140 . The front end of the cylinder 140 may be closed via the discharge valve assembly 170 . A compression space 103 may be formed between the cylinder 140 , the front end of the piston 150 , and the discharge valve assembly 170 . Here, the front end of the piston 150 may be referred to as a head portion (151). The volume of the compression space 103 increases when the piston 150 moves backward, and decreases as the piston 150 moves forward. That is, the refrigerant introduced into the compression space 103 may be compressed while the piston 150 moves forward and discharged through the discharge valve assembly 170 .

The cylinder 140 may include a second flange portion 141 disposed at the front end. The second flange portion 141 may be bent to the outside of the cylinder 140 . The second flange portion 141 may extend in an outer circumferential direction of the cylinder 140 . The second flange portion 141 of the cylinder 140 may be coupled to the frame 120 . For example, a flange groove corresponding to the second flange portion 141 of the cylinder 140 may be formed at the front end of the frame 120 , and the second flange portion 141 of the cylinder 140 may be It may be inserted into the flange groove and coupled through a coupling member.

On the other hand, a gas bearing means capable of lubricating the gas between the cylinder 140 and the piston 150 by supplying the discharge gas at an interval between the outer circumferential surface of the piston 150 and the outer circumferential surface of the cylinder 140 may be provided. The gas discharged between the cylinder 140 and the piston 150 may provide levitation force to the piston 150 to reduce friction between the piston 150 and the cylinder 140 .

For example, the cylinder 140 may include a gas inlet 142 . The gas inlet 142 may communicate with the gas groove 125c formed on the inner circumferential surface of the body 121 . The gas inlet 142 may radially penetrate the cylinder 140 . The gas inlet 142 may guide the compressed refrigerant flowing into the gas groove 125c between the inner circumferential surface of the cylinder 140 and the outer circumferential surface of the piston 150 . Alternatively, in consideration of the convenience of processing, the gas groove 125c may be formed on the outer peripheral surface of the cylinder 140 .

The inlet of the gas inlet 142 may be relatively wide, and the outlet may be formed as a fine through hole to serve as a nozzle. A filter (not shown) for blocking the inflow of foreign substances may be additionally provided at the inlet of the gas inlet 142 . The filter may be a metal mesh filter, or may be formed by winding a member such as Cecil.

A plurality of gas inlets 142 may be independently formed, or a plurality of inlets may be formed in an annular groove and a plurality of outlets may be formed at regular intervals along the annular groove. The gas inlet 142 may be formed only on the front side with respect to the middle of the cylinder 140 in the axial direction. In contrast, the gas inlet 142 is located in the middle of the cylinder 140 in the axial direction in consideration of the deflection of the piston 150 . It may also be formed on the rear side based on the .

The piston 150 is inserted into the open end at the rear of the cylinder 140 , and is provided to seal the rear of the compression space 103 .

The piston 150 may include a head part 151 and a guide part 152 . The head part 151 may be formed in a disk shape. The head part 151 may be partially open. The head part 151 may partition the compression space 103 . The guide part 152 may extend rearward from the outer circumferential surface of the head part 151 . The guide part 152 may be formed in a cylindrical shape. The guide part 152 may have an empty interior and may be partially sealed by the head part 151 at the front. The rear of the guide part 152 may be opened to be connected to the muffler unit 160 . The head unit 151 may be provided as a separate member coupled to the guide unit 152 . Alternatively, the head part 151 and the guide part 152 may be integrally formed.

The piston 150 may include a suction port 154 . The suction port 154 may pass through the head part 151 . The suction port 154 may communicate with the suction space 102 and the compression space 103 inside the piston 150 . For example, the refrigerant flowing into the suction space 102 inside the piston 150 from the receiving space 101 passes through the suction port 154 and the compression space 103 between the piston 150 and the cylinder 140 . ) can be inhaled.

The suction port 154 may extend in an axial direction of the piston 150 . The suction port 154 may be inclined in the axial direction of the piston 150 . For example, the suction port 154 may extend toward the rear of the piston 150 to be inclined in a direction away from the central axis.

The suction port 154 may have a circular cross-section. The suction port 154 may have a constant inner diameter. Alternatively, the suction port 154 may be formed as a long hole in which the opening extends in the radial direction of the head portion 151, or may be formed such that the inner diameter thereof increases toward the rear.

A plurality of suction ports 154 may be formed in any one or more directions of a radial direction and a circumferential direction of the head unit 151 .

A suction valve 155 for selectively opening and closing the suction port 154 may be mounted on the head 151 of the piston 150 adjacent to the compression space 103 . The suction valve 155 may open or close the suction port 154 by operating by elastic deformation. That is, the suction valve 155 may be elastically deformed to open the suction port 154 by the pressure of the refrigerant flowing into the compression space 103 through the suction port 154 .

The piston 150 may be connected to the mover 135 . The mover 135 may reciprocate in the front-rear direction according to the movement of the piston 150 . An inner stator 134 and a cylinder 140 may be disposed between the mover 135 and the piston 150 . The mover 135 and the piston 150 may be connected to each other by a magnet frame 136 formed by bypassing the cylinder 140 and the inner stator 134 to the rear.

The muffler unit 160 may be coupled to the rear of the piston 150 to attenuate noise generated while the refrigerant is sucked into the piston 150 . The refrigerant sucked through the suction pipe 114 may flow into the suction space 102 inside the piston 150 through the muffler unit 160 .

The muffler unit 160 includes a suction muffler 161 communicating with the receiving space 101 of the casing 110 , and an inner guide 162 connected to the front of the suction muffler 161 and guiding the refrigerant to the suction port 154 . ) may be included.

The suction muffler 161 may be located at the rear of the piston 142 , the rear opening may be disposed adjacent to the suction pipe 114 , and the front end may be coupled to the rear of the piston 142 . The suction muffler 161 may have a flow path formed in the axial direction to guide the refrigerant in the accommodation space 101 to the suction space 102 inside the piston 150 .

A plurality of noise spaces divided by baffles may be formed inside the suction muffler 161 . The suction muffler 161 may be formed by coupling two or more members to each other, and for example, a plurality of noise spaces may be formed while the second suction muffler is press-fitted inside the first suction muffler. In addition, the suction muffler 161 may be formed of a plastic material in consideration of weight or insulation.

One side of the inner guide 162 may communicate with the noise space of the suction muffler 161 , and the other side may be deeply inserted into the interior of the piston 142 . The inner guide 162 may be formed in a pipe shape. Both ends of the inner guide 162 may have the same inner diameter. The inner guide 162 may be formed in a cylindrical shape. Alternatively, the inner diameter of the front end, which is the discharge side, may be formed to be larger than the inner diameter of the rear end, which is the opposite side.

The suction muffler 161 and the inner guide 162 may be provided in various shapes, and the pressure of the refrigerant passing through the muffler unit 160 may be adjusted through them. The suction muffler 161 and the inner guide 162 may be integrally formed.

The discharge valve assembly 170 may include a discharge valve 171 and a valve spring 172 provided on the front side of the discharge valve 171 to elastically support the discharge valve 171 . The discharge valve assembly 170 may selectively discharge the refrigerant compressed in the compression space 103 . Here, the compression space 103 means a space formed between the intake valve 155 and the discharge valve 171 .

The discharge valve 171 may be disposed to support the front surface of the cylinder 140 . The discharge valve 171 may selectively open and close the front opening of the cylinder 140 . The discharge valve 171 may open or close the compression space 103 by operating by elastic deformation. The discharge valve 171 may be elastically deformed to open the compression space 103 by the pressure of the refrigerant flowing into the discharge space 104 through the compression space 103 . For example, in a state in which the discharge valve 171 is supported on the front surface of the cylinder 140 , the compression space 103 maintains a closed state, and the discharge valve 171 is spaced apart from the front surface of the cylinder 140 . The compressed refrigerant of the compressed space 103 may be discharged to the open space in the .

The valve spring 172 may be provided between the discharge valve 171 and the discharge cover assembly 180 to provide an elastic force in the axial direction. The valve spring 172 may be provided as a compression coil spring, or may be provided as a leaf spring in consideration of occupied space or reliability.

When the pressure in the compression space 103 is equal to or greater than the discharge pressure, the valve spring 172 deforms forward to open the discharge valve 171 , and the refrigerant is discharged from the compression space 103 to the discharge cover assembly 180 . It may be discharged to the first discharge space 104a. When the discharge of the refrigerant is completed, the valve spring 172 may provide a restoring force to the discharge valve 171 to close the discharge valve 171 .

A process in which the refrigerant flows into the compression space 103 through the suction valve 155 and the refrigerant in the compression space 103 is discharged to the discharge space 104 through the discharge valve 171 will be described as follows.

In the course of the piston 150 reciprocating and linear motion inside the cylinder 140 , when the pressure in the compression space 103 becomes less than a predetermined suction pressure, the suction valve 155 is opened and the refrigerant flows into the compression space 103 . is inhaled On the other hand, when the pressure of the compression space 103 exceeds the predetermined suction pressure, the refrigerant in the compression space 103 is compressed in the closed state of the suction valve 155 .

On the other hand, when the pressure in the compression space 103 is greater than or equal to the predetermined discharge pressure, the valve spring 172 deforms forward and opens the discharge valve 171 connected thereto, and the refrigerant is discharged from the compression space 103 into the discharge cover assembly ( It is discharged to the discharge space 104 of 180). When the discharge of the refrigerant is completed, the valve spring 172 provides a restoring force to the discharge valve 171 , and the discharge valve 171 is closed to seal the front of the compression space 103 .

The discharge cover assembly 180 is installed in front of the compression space 103 to form a discharge space 104 for accommodating the refrigerant discharged from the compression space 103 , and is coupled to the front of the frame 120 to provide the refrigerant. Noise generated in the process of being discharged from the compressed space 103 may be attenuated. The discharge cover assembly 180 may be coupled to the front of the first flange portion 122 of the frame 120 while accommodating the discharge valve assembly 170 . For example, the discharge cover assembly 180 may be coupled to the first flange part 122 through a mechanical coupling member.

And between the discharge cover assembly 180 and the frame 120, a gasket 165 for insulation and an O-ring 166 (O-ring) for suppressing leakage of the refrigerant in the discharge space 104 may be provided. .

The discharge cover assembly 180 may be formed of a thermally conductive material. Accordingly, when a high-temperature refrigerant flows into the discharge cover assembly 180 , the heat of the refrigerant is transferred to the casing 110 through the discharge cover assembly 180 to be radiated to the outside of the compressor.

The discharge cover assembly 180 may include a single discharge cover, or a plurality of discharge covers may be arranged to communicate sequentially. When the discharge cover assembly 180 is provided with a plurality of discharge covers, the discharge space 104 may include a plurality of space portions partitioned by each discharge cover. The plurality of space portions may be disposed in the front-rear direction and may communicate with each other.

For example, when there are three discharge covers, the discharge space 104 is a first discharge space 104a formed between the frame 120 and the first discharge cover 181 coupled to the front side of the frame 120 . and a second discharging space 104b formed between the second discharging cover 182 and the first discharging cover 181 communicating with the first discharging space 104a and coupled to the front side of the first discharging cover 181 . ) and a third discharge space ( ) formed between the third discharge cover 183 and the second discharge cover 182 communicating with the second discharge space 104b and coupled to the front side of the second discharge cover 182 ( 104c).

In addition, the first discharge space 104a selectively communicates with the compression space 103 by the discharge valve 171 , the second discharge space 104b communicates with the first discharge space 104a , and the third discharge The space 104c may communicate with the second discharge space 104b. Accordingly, the refrigerant discharged from the compression space 103 passes through the first discharge space 104a, the second discharge space 104b, and the third discharge space 104c in sequence, the discharge noise is attenuated, and the third discharge It may be discharged to the outside of the casing 110 through the roof pipe 115a and the discharge pipe 115 communicating with the cover 183 .

The driving unit 130 includes an outer stator 131 disposed between the shell 111 and the frame 120 to surround the body portion 121 of the frame 120 , and between the outer stator 131 and the cylinder 140 . It may include an inner stator 134 disposed to surround the cylinder 140 , and a mover 135 disposed between the outer stator 131 and the inner stator 134 .

The outer stator 131 may be coupled to the rear of the first flange portion 122 of the frame 120 , and the inner stator 134 may be coupled to an outer circumferential surface of the body portion 121 of the frame 120 . In addition, the inner stator 134 may be disposed to be spaced apart from the inside of the outer stator 131 , and the mover 135 may be disposed in a space between the outer stator 131 and the inner stator 134 .

A winding coil may be mounted on the outer stator 131 , and the mover 135 may include a permanent magnet. The permanent magnet may be configured as a single magnet having one pole, or by combining a plurality of magnets having three poles.

The outer stator 131 may include a coil winding body 132 surrounding the axial direction in a circumferential direction and a stator core 133 stacked while surrounding the coil winding body 132 . The coil winding body 132 may include a hollow cylindrical bobbin 132a and a coil 132b wound in a circumferential direction of the bobbin 132a. The cross-section of the coil 132b may be formed in a circular or polygonal shape, for example, may have a hexagonal shape. In the stator core 133 , a plurality of lamination sheets may be radially stacked, and a plurality of lamination blocks may be stacked along a circumferential direction.

The front side of the outer stator 131 may be supported by the first flange part 122 of the frame 120 , and the rear side may be supported by the stator cover 137 . For example, the stator cover 137 may be provided in the shape of a hollow disk, the outer stator 131 may be supported on the front surface, and the resonance spring 190 may be supported on the rear surface.

The inner stator 134 may be configured by stacking a plurality of laminations on the outer circumferential surface of the body portion 121 of the frame 120 in the circumferential direction.

One side of the mover 135 may be coupled to and supported by the magnet frame 136 . The magnet frame 136 has a substantially cylindrical shape and may be disposed to be inserted into a space between the outer stator 131 and the inner stator 134 . And the magnet frame 136 is coupled to the rear side of the piston 150 may be provided to move together with the piston (150).

For example, the rear end of the magnet frame 136 is bent and extended in the radial direction to form a first coupling portion 136a, the first coupling portion 136a is a third formed in the rear of the piston (150) It may be coupled to the flange portion 153 . The first coupling portion 136a of the magnet frame 136 and the third flange portion 153 of the piston 150 may be coupled through a mechanical coupling member.

Furthermore, a fourth flange portion 161a formed in front of the suction muffler 161 is interposed between the third flange portion 153 of the piston 150 and the first coupling portion 136a of the magnet frame 136 . can Accordingly, the piston 150, the muffler unit 160, and the mover 135 may be linearly reciprocated together in a state in which they are integrally coupled.

When a current is applied to the driving unit 130 , a magnetic flux is formed in the winding coil, and the magnetic flux formed in the winding coil of the outer stator 131 and the magnetic flux formed by the permanent magnet of the mover 135 are mutually Electromagnetic force is generated by the action, so that the mover 135 can move. In addition, at the same time as the reciprocating movement of the mover 135 in the axial direction, the piston 150 connected to the magnet frame 136 may also reciprocate in the axial direction integrally with the mover 135 .

Meanwhile, the driving unit 130 and the compression units 140 and 150 may be supported in the axial direction by the support springs 116 and 117 and the resonance spring 190 .

The resonance spring 118 amplifies the vibration implemented by the reciprocating motion of the mover 135 and the piston 150, thereby achieving effective compression of the refrigerant. Specifically, the resonance spring 118 may be adjusted to a frequency corresponding to the natural frequency of the piston 150 to allow the piston 150 to resonate. In addition, the resonance spring 118 may induce a stable movement of the piston 150 to reduce vibration and noise generation.

The resonant spring 118 may be an axially extending coil spring. Both ends of the resonance spring 118 may be connected to the vibrating body and the fixed body, respectively. For example, one end of the resonance spring 118 may be connected to the magnet frame 136 , and the other end may be connected to the back cover 123 . Accordingly, the resonance spring 118 may be elastically deformed between the vibrating body vibrating at one end and the fixed body fixed at the other end.

The natural frequency of the resonant spring 118 is designed to match the resonant frequency of the mover 135 and the piston 150 during operation of the compressor 100 , thereby amplifying the reciprocating motion of the piston 150 . However, since the back cover 123 provided as a fixed body is elastically supported by the casing 110 through the first support spring 116 , it may not be strictly fixed.

The resonance spring 118 may include a first resonance spring 118a supported on the rear side with respect to the spring supporter 119 and a second resonance spring 118b supported on the front side.

The spring supporter 119 includes a body portion 119a surrounding the suction muffler 161, a second coupling portion 119b bent in the inner radial direction from the front of the body portion 119a, and the body portion 119a. It may include a support portion 119c bent from the rear to the outer radial direction.

The front surface of the second coupling part 119b of the spring supporter 119 may be supported by the first coupling part 136a of the magnet frame 136 . The inner diameter of the second coupling portion 119b of the spring supporter 119 may surround the outer diameter of the suction muffler 161 . For example, the second coupling portion 119b of the spring supporter 119, the first coupling portion 136a of the magnet frame 136, and the third flange portion 153 of the piston 150 are sequentially disposed. It may then be integrally coupled through a mechanical member. At this time, the fourth flange portion 161a of the suction muffler 161 is interposed between the third flange portion 153 of the piston 150 and the first coupling portion 136a of the magnet frame 136 to be fixed together. It can be as described above.

The first resonance spring 118a may be disposed between the front surface of the back cover 123 and the rear surface of the spring supporter 119 . The second resonance spring 118b may be disposed between the rear surface of the stator cover 137 and the front surface of the spring supporter 119 .

A plurality of first and second resonance springs 118a and 118b may be disposed in a circumferential direction of the central axis. The first resonant spring 118a and the second resonant spring 118b may be disposed in parallel in the axial direction or may be disposed to cross each other. The first and second resonance springs 118a and 118b may be disposed at regular intervals in the radial direction of the central axis. For example, the first and second resonant springs 118a and 118b may be provided three each, and may be disposed at intervals of 120 degrees in the radial direction of the central axis.

The compressor 100 may include a plurality of sealing members capable of increasing the coupling force between the frame 120 and components around it.

For example, the plurality of sealing members are interposed in a portion where the frame 120 and the discharge cover assembly 180 are coupled, and a first sealing member inserted into an installation groove provided at a front end of the frame 120 and the frame ( It may include a second sealing member provided at a portion where the 120 and the cylinder 140 are coupled and inserted into the installation groove provided on the outer surface of the cylinder 140 . The second sealing member prevents the refrigerant in the gas groove 125c formed between the inner circumferential surface of the frame 120 and the outer circumferential surface of the cylinder 140 from leaking to the outside, and increases the coupling force between the frame 120 and the cylinder 140 . can be increased In addition, the plurality of sealing members may further include a third sealing member provided at a portion where the frame 120 and the inner stator 134 are coupled and inserted into an installation groove provided on an outer surface of the frame 120 . Here, the first to third sealing members may have a ring shape.

The operation of the linear compressor 100 described above is as follows.

First, when a current is applied to the driving unit 130 , a magnetic flux may be formed in the outer stator 131 by the current flowing through the coil 132b. The magnetic flux formed in the outer stator 131 generates an electromagnetic force, and the mover 135 having a permanent magnet may linearly reciprocate by the generated electromagnetic force. This electromagnetic force is generated in the direction (forward direction) toward the top dead center (TDC) of the piston 150 during the compression stroke, and the piston 150 moves to the bottom dead center (BDC) during the suction stroke. ) may occur alternately in the direction toward (rear direction). That is, the driving unit 130 may generate thrust, which is a force that pushes the mover 135 and the piston 150 in the moving direction.

The piston 150 linearly reciprocating within the cylinder 140 may repeatedly increase or decrease the volume of the compression space 103 .

When the piston 150 moves in a direction (rear direction) to increase the volume of the compression space 103 , the pressure of the compression space 103 may decrease. Accordingly, the suction valve 155 mounted on the front of the piston 150 is opened, and the refrigerant staying in the suction space 102 may be sucked into the compression space 103 along the suction port 154 . This suction stroke may proceed until the piston 150 is positioned at the bottom dead center by maximally increasing the volume of the compression space 103 .

The piston 150 that has reached the bottom dead center may perform a compression stroke while moving in a direction (forward direction) in which the movement direction is changed to decrease the volume of the compression space 103 . During the compression stroke, the suctioned refrigerant may be compressed while the pressure of the compression space 103 is increased. When the pressure of the compression space 103 reaches the set pressure, the discharge valve 171 is pushed out by the pressure of the compression space 103 and is opened from the cylinder 140, and the refrigerant is discharged from the discharge space 104 through the spaced apart space. ) can be discharged. This compression stroke may be continued while the piston 150 moves to the top dead center where the volume of the compression space 103 is minimized.

As the suction stroke and the compression stroke of the piston 150 are repeated, the refrigerant introduced into the receiving space 101 inside the compressor 100 through the suction pipe 114 is transferred to the suction guide 116a, the suction muffler 161, and the inner guide ( 162) flows into the suction space 102 inside the piston 150 in turn, and the refrigerant in the suction space 102 flows into the compression space 103 inside the cylinder 140 during the suction stroke of the piston 150. can be imported. After the refrigerant in the compression space 103 is compressed during the compression stroke of the piston 150 and discharged to the discharge space 104 , it is discharged to the outside of the compressor 100 through the loop pipe 115a and the discharge pipe 115 . flow can be formed.

3 is a perspective view of an inner stator fixing structure according to an embodiment of the present specification. 4 is an exploded perspective view of an inner stator fixing structure according to an embodiment of the present specification. 5 is a cross-sectional view of an inner stator fixing structure according to an embodiment of the present specification. 6 is an enlarged view of part 'A' of FIG. 5 . 7 is a cross-sectional view of an inner stator according to an embodiment of the present specification.

3 to 7 , the compressor 100 according to an embodiment of the present specification may include a frame 210 , an inner stator 220 , and a fixing ring 230 , but some of these It may be implemented except for the configuration, and additional configurations are not excluded.

The compressor 100 according to the exemplary embodiment of the present specification may include an inner stator fixing structure 200 . The inner stator fixing structure 200 may include a frame 210 , an inner stator 220 , and a fixing ring 230 , but may be implemented except for some of these, and exclude additional components. don't even

The compressor 100 may include a frame 210 . The frame 210 may accommodate the cylinder 140 . The frame 210 may support the cylinder 140 disposed inside. An inner stator 220 may be disposed on the frame 210 . An inner stator 220 may be disposed on an outer circumferential surface of the frame 210 .

The frame 210 may include a body 212 . The body 212 may accommodate the cylinder 140 . The body 212 may be formed in a cylindrical shape. A cylinder 140 may be disposed in the body 212 . An inner stator 220 may be disposed outside the main body 212 . The outer circumferential surface of the body 212 may contact the inner circumferential surface of the inner stator 220 . An adhesive may be disposed between the outer peripheral surface of the main body 212 and the inner peripheral surface of the inner stator 220 .

A flange portion may be formed in front of the body 212 . The flange portion may be formed to extend radially from the front end of the body 212 , and the outer stator 131 and the discharge cover assembly 180 may be coupled to each other.

The frame 210 may include a protrusion 214 . The protrusion 214 may protrude outward from the outer circumferential surface of the body 212 . The protrusion 212 may be formed between the body 212 and the flange portion. The protrusion 212 may be formed in a cylindrical shape. The protrusion 212 may be coupled to the inner stator 220 . The rear of the protrusion 212 may be coupled to the front of the inner stator 220 .

The frame 210 may include a first coupling part 216 . The first coupling portion 216 may be formed on the protrusion 214 . The first coupling portion 216 may be formed at the rear end of the protrusion 214 . The first coupling part 216 may be formed in a shape corresponding to the second coupling part 223 of the inner stator 220 . The second coupling part 223 of the inner stator 220 may be coupled to the first coupling part 216 .

The first coupling part 216 may include a first coupling groove 216 . The first coupling groove 216 may be concavely formed from the rear end of the protrusion 214 to the front. The first coupling groove 216 may be formed in a region in contact with the main body 212 of the rear end of the protrusion 214 . The first coupling groove 216 may be formed in a shape corresponding to the first coupling protrusion 223 of the inner stator 220 . The first coupling protrusion 223 of the inner stator 220 may be inserted into the first coupling groove 216 . Through this, one side of the inner stator 220 may be fixed to the frame 210 without a separate coupling member or helical coupling.

The frame 210 may include a second coupling protrusion 218 . The second coupling protrusion 218 may be disposed outside the first coupling groove 216 . The second coupling protrusion 218 may protrude rearward from the rear end of the protrusion 214 . The second coupling protrusion 218 may be formed in a shape corresponding to the second coupling groove 220 of the inner stator 220 . The second coupling protrusion 218 may be inserted into the second coupling groove 222 of the inner stator 220 . The inner surface of the second coupling protrusion 218 may be in contact with the outer surface of the first coupling protrusion 223 . The outer surface of the second coupling protrusion 218 may be in contact with the inner surface of the third coupling protrusion 224 . The thickness of the second coupling protrusion 218 in the first direction may be greater than the thickness of the body 212 in the first direction. Through this, the coupling force between one side of the inner stator 220 and the frame 210 may be improved. In an embodiment of the present specification, the first direction may mean an outward direction or an inward direction.

The compressor 100 may include an inner stator 220 . The inner stator 220 may be coupled to the frame 210 . The inner stator 220 may be formed in a cylindrical shape. The inner stator 220 may be disposed on the outer peripheral surface of the frame 210 . The inner stator 220 may be coupled to the outer peripheral surface of the frame 210 . The inner circumferential surface of the inner stator 220 may be in contact with the outer circumferential surface of the body 212 of the frame 210 . An adhesive may be disposed between the inner circumferential surface of the inner stator 220 and the outer circumferential surface of the body 212 of the frame 210 .

The inner stator 220 may include a second coupling part 223 . The second coupling part 223 may be formed at the front end of the inner stator 220 . The second coupling part 223 may be formed in a shape corresponding to the first coupling part 216 of the frame 210 . The second coupling part 223 may be coupled to the first coupling part 216 of the frame 210 .

The second coupling part 223 may include a first coupling protrusion 223 . The first coupling protrusion 223 may protrude forward from the front end of the inner stator 220 . The first coupling protrusion 223 may be inserted into the first coupling groove 216 of the frame 210 . The inner surface of the first coupling protrusion 223 may be in contact with the outer surface of the body 212 of the frame 210 . The outer surface of the first coupling protrusion 223 may be in contact with the inner surface of the second coupling protrusion 218 of the frame 210 . Through this, one side of the inner stator 220 can be fixed to the frame 210 without a separate coupling member or helical coupling.

The inner stator 220 may include a second coupling groove 222 . The second coupling groove 222 may be formed at the front end of the inner stator 220 . The second coupling groove 222 may be concavely formed from the front end of the inner stator 220 to the rear. The second coupling groove 222 may be disposed outside the first coupling protrusion 223 . The second coupling groove 222 may be disposed inside the third coupling protrusion 224 . The second coupling groove 222 may be formed in a shape corresponding to the second coupling protrusion 216 of the frame 210 . The second coupling protrusion 216 of the frame 210 may be inserted into the second coupling groove 222 . Through this, the coupling force between one side of the inner stator 220 and the frame 210 may be improved.

The inner stator 220 may include a third coupling protrusion 224 . The third coupling protrusion 224 may protrude forward from the front end of the inner stator 220 . The third coupling protrusion 224 may be disposed outside the second coupling groove 222 . The third coupling protrusion 224 may be disposed outside the second coupling protrusion 218 of the frame 210 . The inner surface of the third coupling protrusion 224 may be in contact with the outer surface of the second coupling protrusion 218 of the frame 210 . A thickness of the third coupling protrusion 224 in the first direction may be greater than a thickness of the first coupling protrusion 223 in the first direction. The third coupling protrusion 224 may protrude forward than the first coupling protrusion 223 . Through this, the coupling force between one side of the inner stator 220 and the frame 210 may be improved.

The inner stator 220 may include a first groove 226 . The first groove 224 may be formed at the rear end of the inner stator 220 . The first groove 224 may be concave from the rear end of the inner stator 220 to the front. The first groove 224 may be formed in a shape corresponding to the fixing ring 230 . A fixing ring 230 may be disposed in the first groove 224 . Through this, the other side of the inner stator 220 can be fixed to the frame 210 .

A length of the first groove 224 in the second direction may be greater than a length of the fixing ring 230 in the second direction. Specifically, the fixing ring 230 may be in contact with the bottom surface of the first groove 224 , and the fixing ring 230 may not be disposed behind the first groove 224 . Through this, it is possible to prevent the fixing ring 230 from being separated from the first groove 224 . In this specification, the second direction may mean a direction perpendicular to the first direction. For example, the second direction may mean a forward direction or a rearward direction.

The inner stator 220 may include a first protrusion 227 . The first protrusion 227 may be formed at the rear end of the inner stator 220 . The first protrusion 227 may protrude rearward from the rear end of the inner stator 220 . The first protrusion 227 may be formed inside the first groove 224 . The first protrusion 227 may contact the inner surface of the fixing ring 230 . The first protrusion 227 may protrude rearward than the fixing ring 230 . Through this, it is possible to prevent the fixing ring 230 from being separated from the first groove 224 .

The inner stator 220 may include a second protrusion 228 . The second protrusion 228 may be formed at the rear end of the inner stator 220 . The second protrusion 228 may protrude rearward from the rear end of the inner stator 220 . The second protrusion 228 may contact the outer surface of the fixing ring 230 . The second protrusion 228 may protrude rearward than the fixing ring 230 . Through this, it is possible to prevent the fixing ring 230 from being separated from the first groove 224 .

A thickness of the second protrusion 228 in the first direction may be greater than a thickness of the first protrusion 227 in the first direction. Through this, the inner stator 220 can be stably pressed against the body 212 of the frame 210 .

Compressor 100 may include a retaining ring 230 . The fixing ring 230 may be disposed on the inner stator 220 . The fixing ring 230 may fix the inner stator 220 to the frame 210 . The fixing ring 230 may be formed in a ring shape. The fixing ring 230 may press the inner stator 220 inward.

The fixing ring 230 may be disposed in the first groove 224 . A length of the fixing ring 230 in the second direction may be smaller than a length of the first groove 224 in the second direction. Through this, it is possible to prevent the fixing ring 230 from being separated from the first groove 224 .

The fixing ring 230 may be formed of a non-magnetic material. Through this, it is possible to prevent interference with the electromagnetic interaction occurring between the winding coil disposed on the outer stator 131 and the mover 135 .

Any or other embodiments of the present specification described above are not mutually exclusive or distinct. Any of the above-described embodiments or other embodiments of the present specification may be combined or combined with each configuration or function.

For example, it means that configuration A described in a specific embodiment and/or drawing may be combined with configuration B described in another embodiment and/or drawing. That is, even if the combination between the components is not directly described, it means that the combination is possible except for the case where it is described that the combination is impossible.

The above detailed description should not be construed as restrictive in all respects and should be considered as illustrative. The scope of this specification should be determined by a reasonable interpretation of the appended claims, and all modifications within the scope of equivalents of this specification are included in the scope of this specification.

100: compressor 101: accommodation space
102: suction space 103: compression space
104: discharge space 110: casing
111: shell 112: first shell cover
113: second shell cover 114: suction pipe
115: discharge pipe 115a: loop pipe
116: first support spring 116a: suction guide
116b: suction side support member 116c: damping member
117: second support spring 117a: support bracket
117b: first support guide 117c: support cover
117d: second support guide 117e: third support guide
118: resonant spring 118a: first resonant spring
118b: second resonance spring 119: spring supporter
119a: body portion 119b: second coupling portion
119c: support 120: frame
121: body portion 122: first flange portion
123: back cover 123a: support bracket
130: drive unit 131: outer stator
132: coil winding body, 132a: bobbin
132b: coil 133: stator core
134: inner stator 135: mover
136: magnet frame 136a: first coupling portion
137: stator cover 140: cylinder
141: second flange portion 142: gas inlet
150: piston 151: head portion
152: guide portion 153: third flange portion
154: suction port 155: suction valve
160: muffler unit 161: suction muffler
161a: fourth flange portion 162: inner guide
170: discharge valve assembly 171: discharge valve
172: valve spring 180: discharge cover assembly
181: first discharge cover 182: second discharge cover
183: third discharge cover 200: inner stator fixing structure
210: frame 220: inner stator
230: retaining ring

Claims (11)

a frame including a body accommodating a cylinder, a protrusion protruding outwardly from the body, and a first coupling portion formed at a rear end of the protrusion;
an inner stator formed at the front end and including a second coupling part coupled to the first coupling part, and a first groove formed at the rear end, and disposed on an outer circumferential surface of the frame; and
and a fixing ring disposed in the first groove and configured to press the inner stator inward. The method of claim 1,
The first coupling portion comprises a first coupling groove formed in a region in contact with the main body of the rear end of the protrusion. 3. The method of claim 2,
and the second coupling portion protrudes forward from the front end of the inner stator and includes a first coupling protrusion disposed in the first coupling groove. 3. The method of claim 2,
The frame includes a second coupling protrusion extending rearward from the outside of the first coupling groove,
and the inner stator includes a second coupling groove formed at a rear end and in which the second coupling protrusion is disposed. 5. The method of claim 4,
The inner stator includes a third coupling protrusion extending forward from the outside of the second coupling groove,
The inner surface of the third coupling protrusion is disposed on the outer surface of the second coupling protrusion. 6. The method of claim 5,
The third coupling protrusion protrudes forward than the first coupling protrusion. 6. The method of claim 5,
A compressor in which the thickness of the third coupling protrusion in the first direction is greater than the thickness of the first coupling protrusion in the first direction. The method of claim 1,
The inner stator includes a first protrusion formed inside the first groove and a second protrusion formed outside the first groove,
The second protrusion protrudes rearward than the first protrusion. 9. The method of claim 8,
A thickness of the second protrusion in the first direction is greater than a thickness of the first protrusion in the first direction. The method of claim 1,
A second direction length of the first groove is formed to be greater than the second direction length of the fixing ring. The method of claim 1,
The fixing ring is a compressor formed of a non-magnetic material.

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