KR102257658B1 - Compressor - Google Patents

Abstract

The compressor is started. The compressor according to the present specification includes a compressor body including a cylinder and a piston reciprocating in the axial direction within the cylinder, and a drive unit for driving the piston, a casing surrounding the compressor body, and a compressor body at one side in the axial direction of the compressor body. And a first support spring interposed between the and the casing, and a second support spring interposed between the compressor body and the casing on the other side of the compressor body in the axial direction, and the second support spring is in an axial direction or a direction adjacent to the axial direction. An axial support unit that is elastically deformed, and a radial support unit that is elastically deformed in a radial direction perpendicular to the axial direction or a direction adjacent to the radial direction.

Description

Compressor {Compressor}

This specification relates to a compressor. More specifically, it relates to a linear compressor for compressing a refrigerant by a linear reciprocating motion of a piston.

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

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

In the reciprocating compressor, a compression space is formed between the piston and the cylinder, and the piston linearly reciprocates to compress fluid, and 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 fluid by rotating a pair of scrolls made of.

Recently, among reciprocating compressors, the use of a linear compressor using a linear reciprocating motion without a crankshaft has been gradually increasing. The linear compressor has the advantage of having a relatively simple structure and improving the efficiency of the compressor because there is little mechanical loss associated with converting rotational motion to linear reciprocating motion.

In the linear compressor, a cylinder is positioned inside a casing forming a closed space to form a compression chamber, and a piston covering the compression chamber is configured to reciprocate inside the cylinder. In a linear compressor, fluid in the closed space is sucked into the compression chamber while 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). The process of being compressed and discharged is repeated.

The linear compressor is composed of a body portion including a mechanical structure, a shell protecting the body portion from the outside, and a support portion supporting the body portion between the body portion and the shell. The support part includes a pair of support springs disposed in front and rear of the main body and a structure for fixing the support spring.

In the case of a support spring, the characteristics of longitudinal and lateral stiffness are related to the noise and vibration characteristics of the compressor, and a design to lower the stiffness of the spring is required to reduce vibration and noise.

In connection with a linear compressor having such a structure, the present applicant has applied for Prior Publication Patent Publication No. 10-2017-0124889.

In the prior invention, a first support device provided on one side and a second support device provided on the other side to support the compressor body are provided as leaf springs. As described above, by supporting the compressor body using a leaf spring, it is possible to prevent the compressor body from colliding with the shell by reducing sagging of the body.

Here, the lateral stiffness means the stiffness in the movement direction of the piston to reduce the vibration of the main body, and the longitudinal stiffness means the stiffness in the gravitational direction to support the weight of the body. The smaller the stiffness of the spring, the better the vibration transmission characteristic (a characteristic that reduces vibration transmission).

However, in the case of the prior invention, since a leaf spring is used as a support spring, a problem of large longitudinal rigidity occurs. This is because in the case of a leaf spring, the stiffness ratio between the motion direction and the load direction differs greatly by about 1:10. Because of this large longitudinal stiffness, there is a problem that is vulnerable to reduction of noise and vibration in the direction of gravity.

In addition, when a leaf spring is used, the fastening method is complicated, so that mass productivity is poor and cost is increased.

Korean Patent Application Publication 10-2017-0124889 A (published on November 13, 2017)

The present specification provides a compressor employing a support spring structure capable of setting both longitudinal and lateral stiffness of a support spring supporting a compressor body portion to be small, and an object thereof.

A compressor according to an exemplary embodiment of the present specification includes: a compressor body including a cylinder, a piston reciprocating in an axial direction within the cylinder, and a drive unit driving the piston; A casing surrounding the compressor body; A first support spring interposed between the compressor body and the casing at one side of the compressor body in the axial direction; And a second support spring interposed between the compressor body and the casing on the other side of the compressor body in the axial direction, wherein the second support spring is elastically deformed in an axial direction or a direction adjacent to the axial direction. And, it may include a radial direction support unit elastically deformed in a radial direction perpendicular to the axial direction or a direction adjacent to the radial direction.

In addition, the casing includes a cylindrical shell for accommodating the compressor body therein, and a pair of shell covers respectively closing an axial front and a rear of the shell, and the axial support unit includes the compressor body and It may be interposed between any one of the pair of shell covers.

At this time, the axial support unit is supported on one side of the compressor body and the other side is supported on the second shell cover, and the radial support unit is supported on one side of the compressor body and on the other side of the shell. Can be supported by

Here, in the compressor body, a suction pipe through which refrigerant is sucked in one side in the axial direction is connected, a discharge pipe through which the refrigerant compressed from the cylinder is discharged is connected to the other side in the axial direction, and a discharge space is formed at the other side in the axial direction. And a cover assembly, wherein the axial support unit is supported in an axial direction or a direction adjacent to the discharge cover assembly, and the radial support unit is supported in a radial direction or a direction adjacent to the discharge cover assembly Can be.

Here, the discharge cover forms a support unit coupling portion protruding in the axial direction, the axial support unit is seated in a groove having one end recessed into one side of the support unit coupling portion, and the radial support unit is the support It may be seated on the outer surface of the unit coupling part.

In this case, the axial support unit may include a coil spring, and one end of the coil spring may be seated in a groove of the support unit coupling portion.

Alternatively, the radial support unit includes a coupling protrusion coupled to the support unit coupling portion, a leg portion connected to the coupling protrusion and extending in a radial direction or a direction adjacent to the radial direction, and a spring support portion provided at an end of the leg portion. , It may include a spring supported by the spring support and contracting in a radial direction or a direction adjacent to the radial direction.

In this case, the spring may be provided with a length that can be contracted larger than the outer diameter.

Alternatively, the axial support unit may include a coil spring provided with a shrinkable length equal to or smaller than an outer diameter.

In addition, the radial support unit may include a coil spring compressed in a direction parallel to the load direction of the compressor body when viewed in the axial direction.

Here, the coil spring may be provided with a length that can be contracted larger than an outer diameter.

Alternatively, the axial support unit may include a coil spring compressed in a direction parallel to a driving direction of the compressor body when viewed from above.

In addition, the radial direction support unit includes a plurality of coil springs compressed in a direction deviated from the load direction of the compressor body by a predetermined angle when viewed from the axial direction, and the plurality of coil springs are at an angle opposite to the load direction. Can be placed.

In addition, the radial support unit includes a coupling protrusion coupled to the compressor body, a leg portion connected to the coupling protrusion and extending in a radial direction or a direction adjacent to the radial direction, a spring support portion provided at an end of the leg portion, and the It may include a coil spring supported by the spring support and contracting in a radial direction or a direction adjacent to the radial direction.

Here, the radial direction support unit may include a pair disposed at an angle opposite to the load direction.

Alternatively, the leg portion is connected to the coupling protrusion on one side and the other side is branched and extended at an angle opposite to the load direction, and the spring support portion and the coil spring are plurally formed to correspond to the branched leg portions. Can be provided.

In addition, the axial support unit may include a coil spring elastically deformed in an axial direction, and the radial spring may include a coil spring elastically deformed in a load direction perpendicular to the axial direction.

According to another embodiment of the present specification, a compressor body including a cylinder, a piston reciprocating in an axial direction within the cylinder, and a drive unit driving the piston; A casing surrounding the compressor body; A first support spring interposed between the compressor body and the casing at one side of the compressor body in the axial direction; And a second support spring interposed between the compressor body and the casing on the other side of the compressor body in the axial direction, wherein the first support spring is provided as a leaf spring, and the second support spring drives the piston. A compressor including a coil spring supporting a directional load and a coil spring supporting a vertical load of the compressor body may be provided.

In this case, the coil spring supporting the vertical load may be elastically deformed in the load direction perpendicular to the axial direction.

Here, the coil spring supporting the load in the driving direction may be elastically deformed in the axial direction.

The compressor according to the present specification may improve vibration transmission characteristics in the movement direction (transverse direction) and gravity direction (longitudinal direction) of the piston by using a coil spring having a small rigidity instead of using a leaf spring having a large longitudinal rigidity.

In addition, according to at least one of the embodiments of the present specification, the main body is supported by one vertical spring having low rigidity, and the horizontal spring having low rigidity supports the transverse movement of the main body. The unit can be firmly supported, and collision between the body unit and the shell due to the inclination of the compressor can be prevented.

In addition, by simplifying the coupling structure of the spring, it is possible to shorten the manufacturing man-hour and reduce the cost.

1 is a perspective view showing a compressor.
2 is a cross-sectional view illustrating a structure of a compressor according to an exemplary embodiment of the present specification.
3 is a cross-sectional view illustrating a structure of a compressor according to another embodiment of the present specification.
4 is a perspective view showing a first support spring according to an embodiment of the present specification.
5 is a front view showing a second support spring according to an embodiment of the present specification.
6 is a cross-sectional view showing the coupling structure of the axial support unit.
7 is an exploded perspective view of a second support spring.
8 is a view showing a radial direction support unit according to the first embodiment of the present specification.
9 is a diagram showing a modified embodiment of FIG. 8.
10 is a front view showing a second support spring for explaining a radial support unit according to a second embodiment of the present specification.
11 is a front view showing a radial direction support unit according to a second embodiment of the present specification.
12 is a front view showing a second support spring for explaining a radial support unit according to a third embodiment of the present specification.
13 is a diagram showing the vibration level according to the stiffness of the support spring.

Hereinafter, exemplary embodiments disclosed in the present specification will be described in detail with reference to the accompanying drawings, but identical or similar elements are denoted by the same reference numerals regardless of reference numerals, and redundant descriptions thereof will be omitted.

In describing the embodiments disclosed in the present specification, when a component is referred to as being "connected" or "connected" to another component, it may be directly connected to or connected to the other component, It should be understood that other components may exist in the middle.

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

On the other hand, terms of the discloser may be replaced with terms such as document, specification, and description.

Hereinafter, the compressor according to the present specification will be described as an example of a linear compressor that sucks and compresses a fluid while performing a linear reciprocating motion of a piston, 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. In addition to the compressor, the refrigeration cycle includes a condenser, an expansion device, and an evaporator. In addition, the linear compressor may be used as a component of a cooling system of a refrigerator, but is not limited thereto and may be widely used throughout the industry.

1 is a perspective view showing a compressor.

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

On the lower side of the shell 111, the leg 20 may be coupled. The leg 20 may be coupled to a base of a 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 an outdoor unit of an air conditioner, and the base may include a base of the outdoor unit.

The shell 111 has a substantially cylindrical shape, and may be laid in a horizontal direction or laid in an axial direction. Referring to FIG. 1, the shell 111 extends long in the horizontal direction and may have a slightly lower 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 on a machine room base of a refrigerator, there is an advantage of reducing the height of the machine room.

In addition, the longitudinal central axis of the shell 111 coincides with the central axis of the compressor body to be described later, and the central axis of the compressor body coincides with the central axis of cylinders and pistons constituting the compressor body.

On the outer surface of the shell 111, a terminal 30 may be installed. The terminal 30 is understood as a configuration for transmitting external power to the motor assembly of the linear compressor 100 (refer to the drive unit 130 of FIG. 2). In particular, the terminal 30 may be connected to the lead wire of the coil (see 132b of FIG. 2).

Outside of the terminal 30, a bracket 31 is provided. The bracket 31 may include a plurality of brackets surrounding the terminal 30. The bracket 31 may perform a function of protecting the terminal 30 from external impacts.

Both sides of the shell 111 are configured to be opened. Shell covers 112 and 113 may be coupled to both sides of the opened shell 111. In detail, the shell covers 112 and 113 include a first shell cover 112 (see FIG. 2) coupled to one opened side of the shell 111 and a first shell cover 112 coupled to the other opened side of the shell 111. 2 shell cover 113 is included. By the shell covers 112 and 113, the inner space of the shell 111 may be sealed.

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 can 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 further includes a plurality of pipes 114, 115, and 40 which are provided in the shell 111 or the shell covers 112 and 113 and capable of inhaling, discharging, or injecting a refrigerant.

In the plurality of pipes 114, 115, 40, a suction pipe 114 through which refrigerant is sucked into the linear compressor 100, a discharge pipe 115 through which the compressed refrigerant is discharged from the linear compressor 100, and A supplement pipe 40 for replenishing the refrigerant to the linear compressor 100 is included.

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. In addition, the compressed refrigerant may be discharged through the discharge pipe 115. The discharge pipe 115 may be disposed 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. The height is understood as the distance from the leg 20 in the vertical direction. Since the discharge pipe 115 and the supplement pipe 40 are coupled to the outer circumferential surface of the shell 111 at different heights, convenience of operation may be achieved.

At least a portion of the second shell cover 113 may be positioned 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, in terms of the flow path of the refrigerant, the size of the flow path of the refrigerant flowing through the supplementary pipe 40 is reduced by the second shell cover 113 as it enters the inner space of the shell 111, and increases again after passing through it. Is formed to be In this process, the pressure of the refrigerant is reduced so that the refrigerant can be vaporized, and in this process, the oil contained in the refrigerant can be separated. Accordingly, as the refrigerant from which oil is separated flows into the piston (see 150 in FIG. 2), the compression performance of the refrigerant may be improved. Oil can be understood as the hydraulic oil present in the cooling system.

A device for supporting the compressor body disposed inside the shell 111 may be provided inside the first and second shell covers 112 and 113. Here, the compressor main body refers to a component provided inside the shell 111, and may include, for example, a driving unit for reciprocating motion and a support unit for supporting the driving unit.

2 is a cross-sectional view for explaining the structure of the compressor 100 according to an embodiment of the present specification.

Referring to FIG. 2, the compressor 100 includes a casing 110 and a main body accommodated in the casing 110, and the main body includes a frame 120, a cylinder 140 fixed to the frame 120, and , And a piston 150 for linear reciprocating motion inside the cylinder 140, and a driving unit 130 that is fixed to the frame 120 and provides a driving force to the piston 150. Here, the cylinder 140 and the piston 150 may be referred to as compression units 140 and 150.

In addition, the compressor 100 may include a bearing means for reducing friction between the cylinder 140 and the piston 150. The bearing means can be oil bearings or gas bearings. Alternatively, a mechanical bearing may be used as a 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 spring includes a first support spring 116 for supporting the rear of the main body and a second support spring 117 for supporting the front of the main body, and may be provided as a leaf spring. In addition, the support springs 116 and 117 may absorb vibrations and shocks generated by the reciprocating motion of the piston 150 while supporting the internal parts of the body.

The casing 110 may form an enclosed space, and the enclosed space includes a receiving space 101 in which the sucked refrigerant is accommodated, a suction space 102 filled with the refrigerant before being compressed, and a compression space for compressing the refrigerant. 103 and a discharge space 104 filled with the compressed refrigerant are formed.

That is, 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 space 103 It is compressed in and discharged to the discharge space 104, and discharged to the outside through a discharge pipe 115 connected to the front side of the casing 110.

The casing 110 has a shell 111 formed in an elongated cylindrical shape with an opening at both ends thereof, a first shell cover 112 coupled to the rear side of the shell 111, and a second shell cover 112 coupled to the front side. It may be made of a shell cover (113). Here, the front side denotes a direction in which the compressed refrigerant is discharged to the left side of the drawing, and the rear side denotes a direction in which the refrigerant flows 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.

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

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

In addition, the rear side of the compressor body may be elastically supported in the radial direction by the first shell cover 112 through the first support spring 116.

The first support spring 116 may be provided as a circular leaf spring, the edge portion is supported by the back cover 123 in the front direction through the support bracket 123a, and the opened central portion is provided through the suction guide 116a. It may be supported by the first shell cover 112 in the rear direction.

The suction guide 116a is formed in a cylindrical shape in which a through passage is provided. The suction guide 116a may have a central opening of the first support spring 116 coupled to the front outer circumferential surface, and the rear end may be supported by the first shell cover 112. In this case, 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.

In addition, 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 may smoothly flow into the muffler unit 160, which will be described later.

In addition, a damping member 116c made of a rubber material or the like may be installed between the suction guide 116a and the suction side support member 116b. Accordingly, it is possible to block the transmission of vibrations that may occur while the refrigerant is sucked through the suction pipe 114 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 and coupled through the roof pipe 115a. The refrigerant discharged from the compression space 103 may pass through the discharge cover assembly 180 and then be discharged to the refrigeration cycle through the roof pipe 115a and the discharge pipe 115.

In addition, the front side of the compressor body may be elastically supported in the radial direction by the shell 111 or the second shell cover 113 through the second support spring 117.

The second support spring 117 may be provided as a circular leaf spring, and the opened central portion is supported by the discharge cover assembly 180 in the rear direction through the first support guide 117b, and the edge portion is supported by the support bracket 117a. ) May be supported on the inner circumferential surface of the shell 111 adjacent to the shell 111 or the second shell cover 113 in the radial direction. Alternatively, unlike the drawings, the edge portion of the second support spring 117 may be supported by the second shell cover 113 in the front direction through a bracket (not shown).

The first support guide 117b is formed in a continuous cylindrical shape with different diameters, the front side is inserted into the central opening of the second support spring 117, and the rear side is inserted into the central opening of the discharge cover assembly 180. Can be inserted. In addition, 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. And the front side of the support cover (117c) is coupled with a cup-shaped second support guide (117d) that is concave forward, and the inside of the second shell cover (113) corresponds to the second support guide (117d) and is concave to the rear. The cup-shaped third support guide 117e may be coupled. The second support guide 117d may be inserted into the third support guide 117e and supported in the axial and radial directions. In this case, a gap may be formed between the second support guide 117d and the third support guide 117e.

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

The body portion 121 may be formed in a cylindrical shape surrounding the outer circumferential surface of the cylinder 140, and the flange portion 122 may be formed to extend in a radial direction from the front end of the body portion 121.

The cylinder 140 may be coupled to the inner circumferential surface of the body portion 121, and the inner stator 134 may be coupled to the outer circumferential surface. For example, the cylinder 140 may be fixed by press fitting to the inner circumferential surface of the body portion 121 and the inner stator 134 may be fixed using a fixing ring.

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

And a bearing inlet groove (125a) forming a part of the gas bearing is formed on one side of the front surface of the flange portion (122), and a bearing communication hole (125b) penetrating 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 formed to be inclined toward the inner circumferential surface of the body portion (121). I 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 where the inner circumferential surface of the body portion 121 contacts, 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 circumferential 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 made of aluminum or aluminum alloy.

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

In addition, the front end of the cylinder 140 may be bent outward to form a flange portion 141. The flange portion 141 of the cylinder 140 may be coupled to the frame 120. For example, a flange groove corresponding to the flange portion 141 of the cylinder 140 may be formed at the front end of the frame 120, and the flange portion 141 of the cylinder 140 is inserted into the flange groove. It can be coupled through a mechanical coupling member.

Meanwhile, a gas bearing means capable of lubricating gas between the cylinder 140 and the piston 150 by supplying 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 discharge gas between the cylinder 140 and the piston 150 provides a levitation force to the piston 150 to reduce friction of the piston 150 against the cylinder 140.

For example, the cylinder 140 communicates with the gas groove 125c formed on the inner circumferential surface of the body portion 121, passes through the cylinder 140 in the radial direction, and stores the compressed refrigerant flowing into the gas groove 125c. A gas inlet 142 for guiding between the inner circumferential surface of the cylinder 140 and the outer circumferential surface of the piston 150 may be formed. Alternatively, in consideration of the convenience of processing, the gas groove 125c may be formed on the outer circumferential 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 hole to serve as a nozzle. A filter (not shown) may be additionally provided at the inlet of the gas inlet 142 to block the inflow of foreign substances. The filter may be a metal mesh filter, or may be formed by winding a member such as cecil.

In addition, a plurality of gas inlets 142 may be independently formed, or an inlet may be formed as an annular groove and a plurality of outlets may be formed along the annular groove at predetermined intervals.

In addition, the gas inlet 142 may be formed only on the front side with respect to the middle of the axial direction of the cylinder 140, or may be formed at the rear side in consideration of the sagging of the piston 150.

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

The piston 150 includes a head portion 151 that divides the compression space 103 in a disk shape and a cylindrical guide portion 152 that extends rearward from the outer circumferential surface of the head portion 151. The head part 151 is provided to be partially open, the guide part 152 is empty inside, and the front part is partially sealed by the head part 151, but the rear part is opened so that it is connected to the muffler unit 160. It is prepared. In addition, the head portion 151 may be provided as a separate member coupled to the guide portion 152, or the head portion 151 and the guide portion 152 may be integrally formed.

In addition, a suction port 154 is formed through the head 151 of the piston 150. The suction port 154 is provided to communicate the suction space 102 and the compression space 103 inside the piston 150. For example, the refrigerant flowing from the receiving space 101 to the suction space 102 inside the piston 150 passes through the suction port 154 and passes through the compression space 103 between the piston 150 and the cylinder 140. ) Can be inhaled.

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

In addition, the suction port 154 may have a circular opening and a constant inner diameter. Alternatively, the suction port 154 may be formed as a long hole whose opening extends in the radial direction of the head portion 151, and may be formed such that the inner diameter increases toward the rear.

In addition, a plurality of suction ports 154 may be formed in one or more of a radial direction and a circumferential direction of the head unit 151.

In addition, 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 be operated by elastic deformation to open or close the suction port 154. That is, the suction valve 155 may be elastically deformed to open the suction port 154 by the pressure of the refrigerant flowing through the suction port 154 to the compression space 103.

In addition, the piston 150 is connected to the mover 135, and the mover 135 reciprocates in the front-rear direction according to the movement of the piston 150. An inner stator 134 and a cylinder 140 may be positioned between the mover 135 and the piston 150. In addition, 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 is coupled to the rear of the piston 150 and is provided to attenuate noise generated during the process of inhaling the refrigerant into the piston 150. The refrigerant sucked through the suction pipe 114 flows 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. ).

The suction muffler 161 is located at the rear of the piston 142, the rear opening is 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 receiving space 101 to the suction space 102 inside the piston 150.

In this case, a plurality of noise spaces partitioned by baffles may be formed inside the suction muffler 161. The suction muffler 161 may be formed by two or more members being coupled to each other. For example, a second suction muffler may be press-fitted into the first suction muffler to form a plurality of noise spaces. In addition, the suction muffler 161 may be formed of a plastic material in consideration of weight or insulation.

The inner guide 162 may have a pipe shape in which one side communicates with the noise space of the suction muffler 161 and the other side is deeply inserted into the piston 142. The inner guide 162 may be formed in a cylindrical shape in which both ends are provided with the same inner diameter, but in some cases, the inner diameter of the front end, which is the discharge side, may be formed 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, through which the pressure of the refrigerant passing through the muffler unit 160 can be adjusted. In addition, 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 at a 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 may be understood as a space formed between the suction valve 155 and the discharge valve 171.

The discharge valve 171 is disposed to be supported on the front surface of the cylinder 140 and may be mounted to selectively open and close the front opening of the cylinder 140. The discharge valve 171 may be operated by elastic deformation to open or close the compression space 103. 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 is maintained in a closed state, and the discharge valve 171 is spaced apart from the front surface of the cylinder 140. The compressed refrigerant in the compressed space 103 may be discharged from the space opened in FIG.

The valve spring 172 is 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 an occupied space or reliability aspect.

When the pressure in the compression space 103 is greater than or equal to 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 prevent the discharge cover assembly 180. It is discharged to the first discharge space 103a. And when the discharge of the refrigerant is completed, the valve spring 172 provides a restoring force to the discharge valve 171 so that the discharge valve 171 is closed.

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 through the discharge valve 171 is discharged to the discharge space 104 will be described as follows.

In the course of the piston 150 reciprocating and linear movement 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 is transferred to the compression space 103. Inhaled. On the other hand, when the pressure in the compression space 103 exceeds a predetermined suction pressure, the refrigerant in the compression space 103 is compressed while the suction valve 155 is closed.

On the other hand, when the pressure in the compression space 103 reaches a predetermined discharge pressure or more, the valve spring 172 deforms forward and opens the discharge valve 171 connected thereto, and the refrigerant is transferred from the compression space 103 to 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 to receive the refrigerant discharged from the compression space 103, and is coupled to the front of the frame 120 to allow the refrigerant to be Noise generated in the process of being discharged from the compression space 103 may be attenuated. The discharge cover assembly 180 may be coupled to the front of the 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 flange portion 122 through a mechanical coupling member.

In addition, between the discharge cover assembly 180 and the frame 120, a gasket 165 for heat insulation and an O-ring 166 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. Therefore, when a high-temperature refrigerant flows into the discharge cover assembly 180, heat of the refrigerant may be transferred to the casing 110 through the discharge cover assembly 180 to radiate heat to the outside of the compressor.

The discharge cover assembly 180 may be formed of one discharge cover, or may be arranged so that a plurality of discharge covers are sequentially communicated. When a plurality of discharge covers are provided, the discharge space 104 may include a plurality of spaces partitioned by each discharge cover. The plurality of space portions are arranged in the front-rear direction and communicate with each other.

For example, when there are three discharge covers, the discharge space 104 is a first discharge space 103a formed between the first discharge cover 181 and the frame 120 coupled to the front side of the frame 120 And, a second discharge space 103b formed between the second discharge cover 182 and the first discharge cover 181 communicating with the first discharge space 103a and coupled to the front side of the first discharge cover 181 ), and a third discharge space formed between the third discharge cover 183 and the second discharge cover 182 communicated with the second discharge space 103b and coupled to the front side of the second discharge cover 182 ( 103c).

And, the first discharge space (103a) is selectively communicated with the compression space (103) by the discharge valve (171), the second discharge space (103b) is communicated with the first discharge space (103a), and the third discharge The space 103c may communicate with the second discharge space 103b. Accordingly, the refrigerant discharged from the compression space 103 passes through the first discharge space 103a, the second discharge space 103b, and the third discharge space 103c in order to reduce the discharge noise, 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 communicated 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 flange portion 122 of the frame 120, and the inner stator 134 may be coupled to the outer peripheral 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 inner stator 131, and the mover 135 may be disposed in a space between the outer stator 131 and the inner stator 134.

The outer stator 131 may be equipped with a winding coil, and the mover 135 may have a permanent magnet. The permanent magnet may be composed of a single magnet having one pole, or may be composed of a combination of a plurality of magnets having three poles.

The outer stator 131 includes 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 the circumferential direction of the bobbin 132a. The cross section of the coil 132b may be formed in a circular or polygonal shape, and for example, may have a hexagonal shape. In addition, in the stator core 133, a plurality of lamination sheets may be radially stacked, or a plurality of lamination blocks may be stacked along a circumferential direction.

In addition, the front side of the outer stator 131 may be supported by the flange portion 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 a hollow disk shape, 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 is disposed to be inserted into a space between the outer stator 131 and the inner stator 134. In addition, the magnet frame 136 is coupled to the rear side of the piston 150 and is provided to move together with the piston 150.

For example, the rear end of the magnet frame 136 is bent and extended radially inward to form a coupling portion 136a, and the coupling portion 136a is on the flange portion 153 formed at the rear of the piston 150 Can be combined. The coupling portion 136a of the magnet frame 136 and the flange portion 153 of the piston 150 may be coupled through a mechanical coupling member.

Further, a flange portion 161a formed in front of the suction muffler 161 may be interposed between the flange portion 153 of the piston 150 and the coupling portion 136a of the magnet frame 136. Therefore, the piston 150, the muffler unit 160, and the mover 135 can 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 may move. In addition, the piston 150 connected to the magnet frame 136 is also reciprocated in the axial direction integrally with the mover 135 at the same time as the mover 135 reciprocates in the axial direction.

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 resonant spring 118 amplifies the vibration implemented by the reciprocating motion of the mover 135 and the piston 150, thereby effectively compressing the refrigerant. Specifically, the resonant spring 118 may be adjusted to a frequency corresponding to the natural frequency of the piston 150 so that the piston 150 can perform resonant motion. In addition, the resonance spring 118 may cause a stable movement of the piston 150 to reduce vibration and noise generation.

The resonance spring 118 may be a coil spring extending in the axial direction. Both ends of the resonance spring 118 may be connected to the vibrating body and the fixture, 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 fixture fixed to the other end.

The natural frequency of the resonance spring 118 is designed to match the resonance frequency of the mover 135 and the piston 150 when the compressor 100 is operated, so that the reciprocating motion of the piston 150 may be amplified. However, since the back cover 123 provided as a fixture 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 based on 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 coupling portion 119b bent in an inner radial direction from the front of the body portion 119a, and at the rear of the body portion 119a. A support part 119c that is bent in an outer radial direction may be provided.

The front surface of the coupling portion 119b of the spring supporter 119 may be supported by the coupling portion 136a of the magnet frame 136. In addition, the inner diameter of the coupling portion 119b of the spring supporter 119 may be provided to surround the outer diameter of the suction muffler 161. For example, the coupling portion 119b of the spring supporter 119, the coupling portion 136a of the magnet frame 136, and the flange portion 153 of the piston 150 are sequentially arranged and then integrated through a mechanical member. Can be combined with At this time, as described above, the flange portion 161a of the suction muffler 161 may be interposed between the flange portion 153 of the piston 150 and the coupling portion 136a of the magnet frame 136 to be fixed together. same.

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

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

On the other hand, the compressor 100 may include a plurality of sealing members capable of increasing the coupling force between the frame 120 and the surrounding parts.

For example, a plurality of sealing members may include a first sealing member interposed in a portion where the frame 120 and the discharge cover assembly 180 are coupled and inserted into an installation groove provided at the front end of the frame 120, and the frame ( 120) and the cylinder 140 may include a second sealing member that is provided in the coupling portion 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 prevents 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. Such electromagnetic force is generated in a direction (forward direction) toward the top dead center (TDC) of the piston 150 during the compression stroke, and the piston 150 is at the bottom dead center (BDC) during the suction stroke. It can occur alternately in the direction toward (rear). 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 increase and decrease the volume of the compression space 103 repeatedly.

When the piston 150 moves in the direction of increasing the volume of the compression space 103 (rear direction), the pressure in the compression space 103 decreases. Accordingly, the suction valve 155 mounted in front of the piston 150 is opened, and the refrigerant remaining in the suction space 102 can be sucked into the compression space 103 along the suction port 154. This suction stroke proceeds until the piston 150 increases the volume of the compression space 103 to the maximum and is located at the bottom dead center.

The piston 150 that has reached the bottom dead center performs a compression stroke while moving in a direction (forward direction) in which the movement direction is changed and the volume of the compression space 103 is reduced. During the compression stroke, as the pressure in the compression space 103 increases, the sucked refrigerant is compressed. When the pressure in the compression space 103 reaches the set pressure, the discharge valve 171 is pushed by the pressure in the compression space 103 and is opened from the cylinder 140, and the refrigerant is discharged through the spaced space. ) Is discharged. This compression stroke continues while the piston 150 moves to the top dead center where the volume of the compression space 103 is minimum.

As the suction stroke and the compression stroke of the piston 150 are repeated, the refrigerant flowing into the receiving space 101 inside the compressor 100 through the suction pipe 114 is a suction guide 116a, a suction muffler 161 and an inner guide ( 162, the refrigerant is introduced into the suction space 102 inside the piston 150, and the refrigerant in the suction space 102 goes to the compression space 103 inside the cylinder 140 during the suction stroke of the piston 150. Flow in. And after the refrigerant in the compression space 103 is compressed and discharged to the discharge space 104 during the compression stroke of the piston 150, it is passed through the loop pipe 115a and the discharge pipe 115 to the outside of the compressor 100. A discharged flow can be formed.

3 is a cross-sectional view illustrating a structure of a compressor 100-1 according to another exemplary embodiment of the present specification.

3, the compressor 100-1 includes a discharge cover assembly 190 and a discharge valve assembly.

The discharge cover assembly 190 forms a discharge space 104 of the refrigerant discharged from the compression space 103. The discharge cover assembly 190 includes a discharge cover 184 coupled to the front surface of the frame 120 and a discharge plenum 185 disposed inside the discharge cover 184. In addition, the discharge cover assembly 190 may further include a cylindrical fixing ring 186 that is in close contact with the inner circumferential surface of the discharge plenum 185.

The discharge valve assembly is coupled to the inside of the discharge cover assembly 190 and discharges the refrigerant compressed in the compression space 103 to the discharge space 104. In addition, the discharge valve assembly may include a spring assembly 175 that provides an elastic force in a direction in which the discharge valve 171 and the discharge valve 171 are in close contact with the front end of the cylinder 140.

The spring assembly 175 includes a valve spring 172 in the form of a leaf spring, a spring support 173 located at the edge of the valve spring 172 to support the valve spring 172, and an outer peripheral surface of the spring support 173. It may include a friction ring 174 fitted.

The front central portion of the discharge valve 171 is fixedly coupled to the center of the valve spring 172. And the rear surface of the discharge valve 171 is in close contact with the front (or front end) of the cylinder 140 by the elastic force of the valve spring 172.

When the pressure in the compression space 103 is greater than or equal to the discharge pressure, the valve spring 172 is elastically deformed in the direction of the discharge plenum 185. In addition, the discharge valve 171 is spaced apart from the front end of the cylinder 140, so that the refrigerant may be discharged from the compression space 103 to the discharge space 104 formed inside the discharge plenum 185.

That is, when the discharge valve 171 is supported on the front surface of the cylinder 140, the compression space 103 remains sealed, and when the discharge valve 171 is separated from the front surface of the cylinder 140, the compression space ( 103) is opened so that the compressed refrigerant inside the compression space 103 can be discharged.

The compression space 103 may be understood as a space formed between the suction valve 155 and the discharge valve 171. In addition, the suction valve 155 may be formed on one side of the compression space 103, and the discharge valve 171 may be provided on the other side of the compression space 103, that is, on the opposite side of the suction valve 155.

In the process of linear reciprocating movement of the piston 150 inside the cylinder 140, when the pressure in the compression space 103 becomes less than or equal to the suction pressure of the refrigerant, the suction valve 155 is opened to transfer the refrigerant to the compression space 103. Flows into.

On the other hand, when the pressure in the compression space 103 exceeds the suction pressure of the refrigerant, the suction valve 155 is closed and the refrigerant in the compression space 103 is compressed by the advance of the piston 130.

On the other hand, when the pressure in the compression space 103 is greater than the pressure (discharge pressure) in the discharge space 104, the valve spring 172 is deformed forward and the discharge valve 171 is separated from the cylinder 140. In addition, the refrigerant in the compression space 103 is discharged to the discharge space 104 formed in the discharge plenum 185 through a space spaced apart from the discharge valve 171 and the cylinder 140.

When the discharge of the refrigerant is completed, the valve spring 172 provides a restoring force to the discharge valve 171 so that the discharge valve 171 comes into close contact with the front end of the cylinder 140 again.

In addition, the linear compressor 100-1 may further include a loop pipe 115a connected to the discharge pipe 115. The roof pipe 115a discharges the refrigerant flowing through the discharge cover assembly 190 to the outside. At this time, one end of the roof pipe 115a is coupled to the discharge cover 184, and the other end is coupled to the discharge pipe 115. In addition, at least a portion of the roof pipe 115a is made of a flexible material, and may be bent and extended along the inner circumferential surface of the shell 111.

In addition, the linear compressor 100-1 may further include an axial support unit 210 and a radial support unit 200 for supporting the front end of the main body of the compressor 100-1.

The axial support unit 210 may be disposed parallel to the axial direction between the second shell cover 113 and the discharge cover 184. And the axial support unit 210 is supported in the mounting groove (113a), one end is concave from the rear to the front of the second shell cover 113, the other end is concave from the front to the rear of the discharge cover (184). It is supported in the mounting groove (184a).

In addition, the axial support units 210 and 210 are provided to be compressible and stretchable in the axial direction, support a load in the axial direction, and reduce vibration.

The radial support unit 200 may be disposed between the discharge cover 184 and the shell 111 in a direction perpendicular to the axial direction. And the radial direction support unit 200 is supported on the outer circumferential surface of the support unit coupling portion (184b) protruding forward of the discharge cover 184 at one end, and the other end is the shell 111 or the second shell cover 113 It can be supported on the inner circumferential surface of.

In addition, the radial support unit 200 is provided to be compressible and stretchable in a radial direction, support a load in a vertical direction, and reduce vibration. In this case, unlike the drawings, the radial support unit 200 may be disposed in a direction inclined forward by a predetermined degree in a direction perpendicular to the axial direction. That is, the radial direction support unit 200 may be disposed so that the lower portion of the radial direction support unit 200 is positioned in front of the upper portion.

In addition, the radial support unit 200 may include support units disposed in a plurality of directions. For example, a pair of support units 200 may be arranged in a state that is open at an angle ranging from 90 to 120 degrees to support the discharge cover assembly 190.

Meanwhile, the second shell cover 113 may be provided in a shape that prevents interference with the support unit 200. In detail, the second shell cover 113 may be formed such that a portion adjacent to the pair of support units 200 is bent outward in the axial direction.

In addition, the linear compressor 100-1 may include a frame 120 and a plurality of sealing members for increasing a coupling force between components around the frame 120. For example, the plurality of sealing members may have a ring shape.

4 is a perspective view showing a first support spring 116 according to an embodiment of the present specification.

The first support spring 116 according to the exemplary embodiment of the present specification may be provided with a leaf spring. When the first support spring 116 supports one side of the compressor body, sagging may be reduced. When the sagging phenomenon of the compressor body is reduced, it is possible to prevent the body from colliding with the shell 111 or the shell covers 112 and 113 during the operation of the compressor.

The first support spring 116 may be coupled to the first shell cover 112 through the suction guide 116a and the suction side support member 116b. The suction guide 116a is coupled to the center of the first support spring 116, and the suction-side support member 116b is coupled to the rear of the suction guide 116a to be fixed to the first shell cover 112.

The first support spring 116 is mounted such that the central axis is disposed parallel to the axial direction of the compressor body, and the leaf spring is disposed in a direction perpendicular to the axial direction. Due to the characteristics of the leaf spring, it can have large lateral stiffness (stiffness in a direction perpendicular to the axial direction of the compressor body) and small longitudinal stiffness (stiffness in the axial direction of the compressor body). For example, the leaf spring may have a lateral stiffness of about 1:10 compared to a longitudinal stiffness. Here, the longitudinal stiffness refers to the axial direction of the leaf spring, and the lateral stiffness refers to the width direction of the leaf spring.

As such, as the leaf spring has a large lateral stiffness characteristic, it may adversely affect vibration and noise characteristics. This is because the smaller the stiffness of the spring, the better the vibration and noise characteristics.

In addition, the leaf spring is coupled by pressing a rubber packing member therein, and there is a possibility that the rubber packing member may rotate relative to the leaf spring because there is no structure for preventing rotation of the leaf spring and the rubber packing member. For this reason, there is a possibility that the compressor body may rotate, and the radial vibration of the compressor body may increase. When the radial vibration of the compressor main body increases, there is a possibility that the compressor main body collides with the casing.

5 is a front view showing a second support spring 117 according to an embodiment of the present specification, and FIG. 6 is a cross-sectional view showing a coupling structure of the axial support unit 210. And Figure 7 is an exploded perspective view of the second support spring 117.

5 to 7, the second support spring 117 according to the embodiment of the present specification is provided in a structure including a coil spring. By using the coil spring in this way, the problem of the leaf spring described above can be solved.

Although the coil spring varies depending on the design, it may generally have a characteristic that the lateral stiffness compared to the longitudinal stiffness is 1:0.3 to 1:1.2. Here, the longitudinal stiffness refers to the direction in which the coil spring is compressed, and the lateral stiffness refers to the circumferential direction of the coil spring.

If a leaf spring disposed in the axial direction parallel to the first support spring 116 is applied to the second support spring 117, the vibration characteristics in the load direction of the compressor body may deteriorate because the lateral stiffness of the leaf spring is large. have. However, when a coil spring disposed in the load direction is applied to the second support spring 117, since the longitudinal stiffness of the coil spring is small, vibration characteristics in the load direction may be improved.

The second support spring 117 may include an axial support unit 210 and a radial support unit 200.

The axial support unit 210 may be disposed parallel to the axial direction between the second shell cover 113 and the discharge cover 184. And the axial support unit 210 is supported in the mounting groove (113a), one end is concave from the rear to the front of the second shell cover 113, the other end is concave from the front to the rear of the discharge cover (184). It is supported in the mounting groove (184a).

In addition, the axial support unit 210 is provided to be compressible and stretchable in the axial direction, support a load in the axial direction, and reduce vibration.

Meanwhile, the axial support unit 210 includes those disposed adjacent to the axial direction. For example, it may be arranged to be inclined in the vertical direction. However, when the axial support unit 210 is viewed from the front in the axial direction, if it is inclined out of the vertical direction, vibration in the width direction may deteriorate, which is not preferable.

And the discharge cover 184 may form a mounting groove (184a) for accommodating the rear end of the axial support unit 210 in the front. For example, the mounting groove 184a may be provided as a groove recessed in a circular shape corresponding to the outer diameter of the rear portion of the axial support unit 210. And the mounting groove (184a) may be formed in the front of the support unit coupling portion (184b) protruding forward from the discharge cover (184). One end of the axial support unit 210 is inserted and supported in the mounting groove 184a of the discharge cover 184, and movement in the radial direction may be restricted.

The second shell cover 113 may form a mounting groove 113a for accommodating the front end of the axial support unit 210 at the rear. For example, the mounting groove 113a may be provided as a groove recessed in a circular shape corresponding to the outer diameter of the front portion of the axial support unit 210. The other end of the axial support unit 210 is inserted and supported in the mounting groove 113a of the second shell cover 113, and movement in the radial direction may be restricted.

The axial support unit 210 may be selected to have an optimized axial length and rigidity. The axial length and stiffness may be selected such that the second shell cover 113 and the discharge cover 184 do not collide when compressed, while supporting the load of the main body and reducing vibration.

The radial support unit 200 may be disposed between the discharge cover 184 and the shell in a direction perpendicular to the axial direction. And the radial direction support unit 200 is supported on the outer circumferential surface of the support unit coupling portion (184b) protruding forward of the discharge cover 184 at one end, and the other end to the inner circumferential surface of the shell or the second shell cover 113 Can be supported.

In addition, the radial support unit 200 is provided to be compressible and stretchable in a radial direction, support a load in a vertical direction, and reduce vibration. In this case, unlike the drawings, the radial support unit 200 may be disposed in a direction inclined forward by a predetermined degree in a direction perpendicular to the axial direction. That is, the radial direction support unit 200 may be disposed so that the lower portion of the radial direction support unit 200 is positioned in front of the upper portion.

On the other hand, the radial direction support unit 200 includes those disposed adjacent to the radial direction. For example, it may be disposed inclined in the axial direction, or may be disposed inclined forward when viewed from the side. However, when only one radial support unit 200 is provided, when viewed from the front in the axial direction, when inclined out of the vertical direction, vibration in the width direction may deteriorate, which is not preferable. However, when the plurality of radial support units 200 are provided symmetrically in the width direction, this concern can be solved.

In addition, the radial support unit 200 may include a plurality of support units arranged in a direction symmetrical to the vertical direction. For example, when viewed from the axial direction, a pair of support units may be arranged in a state of being opened at an angle in the range of 90 to 120 degrees to support the discharge cover 184 assembly.

Meanwhile, the second shell cover 113 may be provided in a shape that prevents interference with the radial support unit 200. In detail, the second shell cover 113 may be formed such that a portion adjacent to the pair of radial support units 200 is bent outward in the axial direction.

In addition, the discharge cover 184 may form a support unit coupling portion 184b to which one end of the radial support unit 200 is coupled to the front. For example, the support unit coupling portion 184b protrudes in a cylindrical shape from the front surface of the discharge cover 184, and the diameter of the support unit coupling portion 184b is to be provided larger than the diameter of the axial support unit 210. I can.

The radial support units 200 may be provided in a pair. One end of the pair of radial support units 200 is coupled to the outer circumferential surface of the support unit coupling portion 184b of the discharge cover 184, and the other end may be in close contact with the inner circumferential surface of the shell. For example, the pair of radial support units 200 may be coupled to the support unit coupling portion 184b of the discharge cover 184 in a state that is open at an angle in the range of 90 to 120 degrees.

The arrangement angle of the pair of radial support units 200 may be set to support a vertical downward load and at the same time support a horizontal shake. For example, if the arrangement angle of the pair of radial support units 200 decreases, the vertical downward load can be better supported, and when the arrangement angle of the pair of radial support units 200 increases, the width direction You will be able to better support the shaking.

8 is a view showing the radial direction support unit 200 according to the first embodiment of the present specification.

Referring to FIG. 8, the radial support unit 200 according to the first embodiment is supported by the leg 201 extending in the radial direction in the axial direction and the support unit coupling portion 184b of the discharge cover 184 It may include a supporting portion 202 that is, a spring supporting portion 203 and a spring 204 provided at the front end of the leg portion 201, and a coupling protrusion 205 coupled to the supporting unit coupling portion 184b.

When the leg portion 201 is mounted, the support portion 202 extends in a vertical direction in the axial direction, and the support portion 202 extends outward from one end of the leg portion 201 to increase the support area, thereby enabling stable support. In addition, the support portion 202 may be provided in a concave curved shape corresponding to the convex curved surface of the support unit coupling portion 184b. In addition, a reinforcing rib may be formed between the leg portion 201 and the support portion 202.

The coupling protrusion 205 is formed protruding on one surface of the support portion 202 opposite to the leg portion 201, and a coupling groove 184c formed in the outer circumferential surface of the support unit coupling portion 184b of the discharge cover 184 It may be provided in a shape corresponding to this so as to be coupled to. In addition, the coupling protrusion 205 may be provided to be detachably attached to the discharge cover 184.

In addition, a vibration isolating member 202a capable of preventing transmission of vibration and shock may be provided between the support part 202 and the support unit coupling part 184b on the inner side of the support part 202.

Meanwhile, the radial support unit 200 may act not only with a radial load, but also an axial force and a circumferential torsional force. Therefore, the coupling protrusion 205 may be formed of a material capable of elastic deformation. For example, the coupling protrusion 205 may be made of a rubber material, and may be made of a fluorine-based rubber material. At this time, the coupling protrusion 205 and the anti-vibration member 202a may be integrally formed. For example, the coupling protrusion 205 and the anti-vibration member 202a may be injection formed of a rubber material.

The spring support 203 may be provided at the end of the leg 201 supported on the inner circumferential surface of the shell when mounted. The spring support part 203 is connected to the leg part 201 and supports the fixed spring support part 203a supporting one end of the spring 204 and the other end of the spring 204, and prevents contraction and extension of the spring 204. It may include a variable spring support (203b) moving along with it.

The fixed spring support 203a may extend outward from the end of the leg 201 to form a support surface capable of supporting one end of the spring 204. In addition, the fixed spring support 203a may have an outer diameter corresponding to the inner diameter of the spring 204 so as to prevent separation of the spring 204 and may form a fixing protrusion protruding in the longitudinal direction of the spring 204.

The variable spring support 203b has one side supporting the other end of the spring 204 and the other side supporting the inner circumferential surface of the shell. And the variable spring support (203a) has an outer diameter corresponding to the inner diameter of the spring 204 to prevent the separation of the spring 204 on the surface supporting the spring 204 and protruding in the longitudinal direction of the spring 204 Can form a fixed protrusion. In addition, the other surface supported by the shell may be provided as a curved surface, for example, may be provided as a curved surface corresponding to the radius of curvature of the inner circumferential surface of the shell.

Meanwhile, the meaning of "fixed" in the fixed spring support part 203a and the meaning of "variable" in the variable spring support part 203b may be understood as a relative movement. That is, the fixed spring support part 203a means that the fixed position is maintained with respect to the discharge cover 184 to which the radial support unit 200 is coupled, and the variable spring support part 203b is based on the discharge cover 184. It means moving away or closer in the radial direction. If the movement is described based on the shell 111, it may be described that the variable spring support 203b is provided at a fixed position on the shell 111, and the fixed spring support 203a is variable in position. .

The spring 204 may be a coil spring, and both ends may be supported by the spring support 203.

However, in the radial direction support unit 200 according to the first embodiment, there is a possibility that the spring 204 may be buckled. When a large vibration of the compressor main body occurs or a force acts from the outside, an external force exceeding the force set in the spring 204 may act, and at this time, the spring 204 may be buckled, thereby losing the support function of the main body.

In addition, when the length of the spring 204 is lengthened to reduce gravitational stiffness (longitudinal stiffness), there is a limit to reducing the longitudinal stiffness since buckling resistance becomes weak.

9 is a diagram showing a modified embodiment of FIG. 8.

Referring to FIG. 9, the radial support unit 200-1 according to the modified embodiment is for solving the problem that the spring 204 is buckling, and the spring support 203 has a variable spring support 203b at one end. It is connected to and the other end may further include a guide portion (203c) that is movably inserted into the fixed spring support portion (203a). The guide portion 203c extends through the center of the coil spring 204 and may be provided longer than the length when the spring 204 is relaxed. In addition, the guide part 203c may be provided to be movable in the contraction direction of the spring 204.

The guide portion 203c can prevent the spring 204 from being buckled by absorbing a force acting in a direction that deviates from the contraction direction of the spring 204.

However, since a circumferential torsional force also acts on the radial support unit 200-1, there is a risk that the guide portion 203c may be damaged in this case.

10 is a front view showing a second support spring 117 for explaining the radial support unit 200-2 according to the second embodiment of the present specification, and FIG. 11 is a radius according to the second embodiment of the present specification. It is a front view showing the direction support unit (200-2).

10 and 11, the radial direction support unit 200-2 according to the second embodiment of the present specification includes two leg portions 201-1 that are spread at a predetermined angle, and has two legs. The part 201-1 is characterized in that it is connected to both sides in one support extension part 202-1.

That is, unlike the radial direction support unit 200 according to the first embodiment described in FIGS. 5 to 8, wherein a pair of support units each having one leg 201 are installed at a predetermined angle, The radial direction support unit 200-2 according to the second embodiment of the specification is different in that two leg portions 201-1 extend to one support unit.

In this way, by integrating the two leg portions 201-1, there is an advantage of securing structural rigidity and reducing assembly tolerances.

In the case of the radial support units 200, 200-1, and 200-2 described above with reference to FIGS. 5 to 10, they are disposed at a predetermined angle in the circumferential direction from the load direction rather than the load direction of the body.

12 is a front view showing the radial direction support unit 200-3 according to the third embodiment of the present specification.

The support springs 116 and 117 may be a passage through which vibration is transmitted between the compressor body and the casing 110. Therefore, in order to effectively attenuate the transmitted vibration, the longitudinal and transverse rigidity of the support springs 116 and 117 must be small. The bearing capacity of a spring structure can be expressed as the product of stiffness and compression length. Therefore, if the compression length is increased, the same holding force can be maintained with less rigidity.

Referring to FIG. 12, the radial direction support unit 200-3 according to the third exemplary embodiment of the present specification is different in that it includes only one radial support unit extending below the 6 o'clock direction from the central axis.

The second support spring 117 according to the third embodiment of the present specification can stably support the body while reducing noise and vibration by reducing both longitudinal and lateral rigidity. When the radial support units 200, 200-1, and 200-2 are disposed in a state where they are at a predetermined angle from the vertical downward direction to the circumferential direction, there is a limit to reducing the longitudinal rigidity.

In order to reduce the longitudinal stiffness, the compression length of the spring must be lengthened. However, as long as the spring is arranged to be inclined in the load direction, as long as the spring length increases, the possibility of buckling increases. However, when the radial support unit (200-3) is disposed in the vertical downward direction (6 o'clock), the risk of buckling is reduced because the direction of the elastic restoring force and the load direction are identical, and the compression length of the spring is increased. It is possible to support the load of the body while reducing the longitudinal stiffness.

In addition, the second support spring 117 must act as a support force not only for the load of the compressor body but also for the force acting in a direction that deviates from the load direction. To this end, the second support spring 117 according to the third embodiment of the present specification includes an axial support unit 210 disposed in parallel with the axial direction between the second shell cover 113 and the discharge cover 184. It may contain more.

As such, the load of the main body is supported by one radial support unit 200-3 with low longitudinal rigidity, and the rotation or twist of the main body is supported by one axial support unit 210.

In addition, the axial support unit 210 may prevent buckling by providing the free length (retractable length) of the spring equal to or smaller than the outer diameter of the spring. This is because in the case of the axial support unit 210, a load acts in the transverse direction of the spring.

In addition, the radial support unit 200-3 may have a free length (retractable length) of the spring larger than the outer diameter of the spring to reduce longitudinal rigidity.

In addition, since the second support spring 117 according to the third embodiment of the present specification uses one axial support unit 210 and one radial support unit 200-3, it is a support that is a medium of vibration transmission. The spring can be minimized, and as described above, the vibration reduction effect can be increased by using a spring having a small rigidity.

13 is a diagram showing the vibration level according to the stiffness of the support spring.

Referring to FIG. 13, it can be seen the difference in vibration levels when springs having different spring constants are used for devices having the same weight.

In Fig. 13 (a), when the spring constant is 7000 N/m, the vibration level is shown as 100 gal (mm/sec2), and in Fig. 13 (b), when the spring constant is 4000 N/m, the vibration The Vibratrion Level appears as 55 gal (mm/sec2). That is, when the spring stiffness decreases from 7000 to 4000, the vibration level is reduced by almost half.

Through this, it can be seen that the vibration level decreases as the stiffness of the axial support unit 210 and the radial support unit 200 is reduced.

Certain or other embodiments of the present specification described above are not mutually exclusive or distinct from each other. Certain or other embodiments of the present specification described above may have their respective configurations or functions used in combination or combination.

For example, it means that a configuration A described in a specific embodiment and/or a drawing may be combined with a configuration B described in another embodiment and/or a drawing. That is, even if the combination between the components is not directly described, the combination is possible except for the case where the combination is described as 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 reasonable interpretation of the appended claims, and all changes within the equivalent scope of this specification are included in the scope of this specification.

20: leg, 30, terminal
100: compressor, 101: accommodating 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 resonant spring, 119: spring supporter,
119a: body portion, 19b: coupling portion,
119c: support, 120: frame,
121: body portion, 122: 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: coupling portion,
137: stator cover, 140: cylinder,
141: flange portion, 142: gas inlet,
150: piston, 151: head,
152: guide portion, 153: flange portion,
154: suction port, 155: suction valve,
160: muffler unit, 161: suction muffler,
161a: flange portion, 162: inner guide,
170: discharge valve assembly, 171: discharge valve,
172: valve spring, 173: spring support,
174: friction ring, 175: spring assembly,
180: discharge cover assembly, 181: first discharge cover,
182: second discharge cover, 183: third discharge cover,
184: discharge cover, 184a: mounting groove,
184b: support unit coupling portion, 184c: coupling groove,
185: discharge plenum, 186: retaining ring,
190: discharge cover assembly,
200: radial support unit, 201: leg,
202: support extension, 203a: fixed spring support,
203b: variable spring support, 204: spring,
205: coupling protrusion, 210: axial support unit.

Claims (21)

A compressor main body including a cylinder, a piston reciprocating in the axial direction within the cylinder, and a drive unit for driving the piston;
A casing surrounding the compressor body;
A first support spring interposed between the compressor body and the casing at one side of the compressor body in the axial direction; And
And a second support spring interposed between the compressor body and the casing on the other side of the compressor body in the axial direction,
The second support spring comprises an axial support unit elastically deformed in an axial direction or a direction adjacent to the axial direction, and a radial support unit elastically deformed in a radial direction perpendicular to the axial direction or a direction adjacent to the radial direction.
The method of claim 1,
The casing includes a cylindrical shell for accommodating the compressor body therein, and a first shell cover and a second shell cover respectively closing the front and rear ends of the shell in the axial direction,
The axial support unit is a compressor interposed between the compressor body and any one of the first and second shell covers.
The method of claim 2,
One side of the axial support unit is supported by the compressor body and the other side is supported by the second shell cover,
The radial support unit is a compressor in which one side is supported by the compressor body and the other side is supported by the shell.
The method of claim 3,
The compressor body is a discharge cover assembly in which a suction pipe through which refrigerant is sucked is connected to one side in the axial direction, a discharge pipe through which the refrigerant compressed from the cylinder is discharged is connected to the other side in the axial direction, and a discharge space is formed at the other side in the axial direction. Including,
The axial support unit is supported in an axial direction or a direction adjacent to the discharge cover assembly,
The radial direction support unit is a compressor supported in a radial direction or a direction adjacent to the radial direction to the discharge cover assembly.
The method of claim 4,
The discharge cover assembly includes a discharge cover having a support unit coupling portion protruding in the axial direction,
One end of the axial support unit is seated in a groove recessed into one side of the support unit coupling portion,
The radial support unit is a compressor that is seated on an outer surface of the support unit coupling portion.
The method of claim 5,
The axial support unit includes a coil spring, and one end of the coil spring is seated in a groove of the support unit coupling portion.
The method of claim 5,
The radial support unit includes a coupling protrusion coupled to the support unit coupling portion, a leg portion connected to the coupling protrusion and extending in a radial direction or a direction adjacent to the radial direction, and a spring support portion provided at an end of the leg portion, and the Compressor comprising a spring supported by the spring support and contracting in a radial direction or a direction adjacent to the radial direction.
The method of claim 7,
The spring is a compressor comprising a coil spring provided with a length that can be contracted larger than the outer diameter.
The method according to claim 6 or 8,
The axial support unit is a compressor including a coil spring provided with a shrinkable length equal to or smaller than an outer diameter.
The method of claim 1,
The radial support unit is a compressor including a coil spring compressed in a direction parallel to a load direction of the compressor body when viewed in an axial direction.
The method of claim 10,
The coil spring is a compressor in which a shrinkable length is provided larger than an outer diameter.
The method of claim 10,
The axial support unit is a compressor including a coil spring compressed in a direction parallel to a driving direction of the compressor body when viewed from above.
The method according to any one of claims 1 to 8,
The radial support unit includes a plurality of coil springs compressed in a direction deviated by a predetermined angle from the load direction of the compressor body when viewed from the axial direction,
The plurality of coil springs is a compressor disposed at an angle opposite to the load direction.
The method according to any one of claims 1 to 6,
The radial support unit includes a coupling protrusion coupled to the compressor body, a leg portion connected to the coupling protrusion and extending in a radial direction or a direction adjacent to the radial direction, a spring support portion provided at an end of the leg portion, and the spring support portion Compressor comprising a coil spring supported on and contracting in a radial direction or a direction adjacent to the radial direction.
The method of claim 14,
The radial direction support unit is a compressor comprising a pair disposed at an angle opposite to the load direction.
The method of claim 14,
One side of the leg portion is connected to the coupling protrusion and the other side is branched and extended at an angle opposite to the load direction,
The spring support part and the coil spring is provided in plural to correspond to each of the branched leg parts.
The method according to any one of claims 1 to 8,
The axial support unit includes a coil spring elastically deformed in an axial direction,
The radial support unit is a compressor comprising a coil spring elastically deformed in a load direction perpendicular to an axial direction.
A compressor main body including a cylinder, a piston reciprocating in the axial direction within the cylinder, and a drive unit for driving the piston;
A casing surrounding the compressor body;
A first support spring interposed between the compressor body and the casing at one side of the compressor body in the axial direction; And
And a second support spring interposed between the compressor body and the casing on the other side of the compressor body in the axial direction,
The first support spring is provided with a leaf spring,
The second support spring includes a coil spring supporting a load in a driving direction of the piston, and a coil spring supporting a load in a vertical direction of the compressor body.
The method of claim 18,
The coil spring supporting the vertical load is elastically deformed in the load direction perpendicular to the axial direction.
The method of claim 19,
The coil spring supporting the load in the driving direction is elastically deformed in the axial direction. The method of claim 6,
The other side of the coil spring is seated in a groove formed by being concave in the second shell cover.

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