KR102622659B1 - Linear compressor - Google Patents

Abstract

A linear compressor is provided. A linear compressor according to one aspect of the present specification includes a cylinder; A piston that reciprocates in the axial direction within the cylinder; a first muffler unit coupled to the piston and forming a first refrigerant passage; a back cover including a first opening formed in a radial central area and disposed behind the piston; and a second muffler unit coupled to the rear of the back cover. At this time, the first muffler unit includes an inner guide disposed inside the piston, a first suction muffler disposed rearward of the inner guide, and a first muffler disposed rearward of the first suction muffler and penetrating the first opening. It includes a first extension portion, wherein the second muffler unit includes a second suction muffler in communication with the first extension portion, and a second suction muffler disposed on a radial outer side of the second suction muffler and in communication with the second suction muffler. Includes an extension part.

Description

Linear compressor{LINEAR COMPRESSOR}

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

In general, a compressor refers to a device that receives power from a power generating device such as a motor or turbine and compresses a working fluid such as air or refrigerant. Specifically, compressors are widely applied throughout industry and home appliances, especially vapor compression refrigeration cycles (hereinafter referred to as 'refrigeration cycles').

These compressors can be classified into reciprocating compressors, rotary compressors, and scroll compressors depending on the method of compressing the refrigerant.

The reciprocating compressor compresses the fluid by forming a compression space between the piston and the cylinder and the piston moves in a straight line. The rotary compressor compresses the fluid by a roller that rotates eccentrically inside the cylinder, and the scroll compressor uses a spiral compressor. This is a method in which a pair of scrolls are engaged and rotated to compress the fluid.

Recently, among reciprocating compressors, the use of linear compressors that use linear reciprocating motion without using a crankshaft is gradually increasing. Linear compressors have the advantage of improving compressor efficiency and having a relatively simple structure as the mechanical loss associated with converting rotary motion to linear reciprocating motion is small.

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

A compression unit and a drive unit (motor) are installed inside the linear compressor, and the compression unit performs the process of compressing and discharging the refrigerant while reciprocating in the axial direction through the movement generated by the drive unit.

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

Meanwhile, noise is generated as the piston reciprocates inside the cylinder and continuously suctions, compresses, and discharges the refrigerant. In order to reduce the noise generated in this way, the conventional linear compressor is equipped with a muffler. The muffler includes an insertion portion inserted into the piston, a silencer disposed axially rearward of the insertion portion and having a larger inner diameter than the insertion portion, and an extension portion extending axially rearward from the silencer.

The muffler is coupled to the piston by inserting and fixing the insertion part into the gas passage of the piston, and the extension part is located on the same line as the suction pipe coupled to the casing. Such a muffler reciprocates just before the piston moves in a straight line, and the refrigerant sucked into the suction pipe flows into the piston through the extension part, silencer part, and insertion part. And the noise generated in the compression space formed by the cylinder and piston is attenuated as it passes through the piston and muffler.

This linear compressor is disclosed in Korean Patent Publication No. 10-0314064 B (hereinafter referred to as Prior Art 1).

Meanwhile, in a refrigerator, a compressor, suction pipe, and cooling fan are typically arranged in that order from the axial front. Referring to FIG. 11, in a conventional linear compressor, the suction pipe 314 is coupled to the rear of the casing 110, that is, to the first shell cover 312. Therefore, since the suction pipe installation space (G2) where the suction pipe 314 can be placed is required between the casing 110 and the cooling fan (PAN), the space utilization inside the refrigerator machine room is low, and the space utilization by the cooling fan (PAN) is low. A problem occurs in which cooling efficiency decreases.

Additionally, the natural sound field frequency inside the casing of a compressor filled with suction refrigerant is inversely proportional to the casing length in each direction. Typically, the casing of a linear compressor is long in the axial direction and short in the radial direction, so the axial resonance noise has a low frequency and the radial resonance noise has a high frequency. Referring to FIG. 12, in a conventional linear compressor, pressure fluctuation sound is most strongly radiated in the axial direction along the extension of the muffler. Therefore, there was a problem in which the largest low-frequency resonance noise occurred in the range of 300 to 400 Hz, which is the axial natural sound field frequency.

Korean Patent Publication 10-0314064 B (2015.01.20. Announcement)

The problem that this specification aims to solve is to provide a linear compressor that can increase space efficiency by reducing the installation space of the suction pipe formed at the rear of the casing and increase compressor cooling efficiency by a cooling fan.

In addition, the aim is to provide a linear compressor that can reduce low-frequency resonance noise caused by the structure of the linear compressor being long in the axial direction.

A linear compressor according to one aspect of the present specification for achieving the above problem includes a cylinder; A piston that reciprocates in the axial direction within the cylinder; a first muffler unit coupled to the piston; a back cover including a first opening formed in a radial central area and disposed behind the piston; And it may include a second muffler unit coupled to the rear of the back cover.

At this time, the first muffler unit includes an inner guide disposed inside the piston, a first suction muffler disposed rearward of the inner guide, and a first muffler disposed rearward of the first suction muffler and penetrating the first opening. It includes a first extension portion, wherein the second muffler unit includes a second suction muffler in communication with the first extension portion, and a second suction muffler disposed on a radial outer side of the second suction muffler and in communication with the second suction muffler. It may include an extension part.

Through this, space efficiency can be increased by reducing the installation space for the suction pipe formed at the rear of the casing, and compressor cooling efficiency by the cooling fan can be increased.

In addition, low-frequency resonance noise caused by the structure of the linear compressor, which is formed to be long in the axial direction, can be reduced.

Additionally, a second noise space is formed between the second suction muffler and the rear of the back cover, and the rear end of the first extension may reciprocate in the axial direction within the second noise space.

Additionally, the second extension part may be in close contact with the back cover, and a second flow path communicating with the second noise space may be formed between the back cover and the second extension part.

Additionally, the second opening formed in the second extension may be disposed ahead of the second intake muffler.

Additionally, the second extension may include a vertical portion that communicates with the second suction muffler and extends radially outward, and a horizontal portion that communicates with the vertical portion and extends forward.

Additionally, the second muffler unit includes a second opening, and the second opening may overlap the first muffler unit in the radial direction.

Additionally, the inner peripheral surface of the first opening may be adjacent to the outer peripheral surface of the first extension part.

Additionally, the radial length of the inner surface of the second suction muffler may be larger than the inner diameter of the first extension part.

Additionally, the cross-sectional area of the flow path of the second intake muffler may be larger than the cross-sectional area of the flow path of the second extension.

Additionally, a casing accommodating the cylinder; a rear elastic member with one end connected to the casing and the other end connected to the back cover; And it may include a fixing member for fixing the second muffler unit to the back cover.

At this time, the second muffler unit includes a fixing part extending outward from the second intake muffler, the fixing member passes through the fixing part and is coupled to the back cover, and the other end of the rear elastic member is It may be disposed between the fixing part and the back cover.

Additionally, a casing accommodating the cylinder; and a suction pipe that radially penetrates the casing and supplies refrigerant to the second muffler unit.

Additionally, the second muffler unit includes a second opening formed in the second extension part, and one end of the suction pipe may face the second opening.

Additionally, it may include a nozzle portion disposed between the second opening and the suction pipe, and a radial inner radius of the nozzle portion may be smaller than a radial outer radius.

Additionally, the second muffler unit includes a connection auxiliary portion protruding to the outside of the second opening, and the radial inner side of the nozzle portion may be press-fitted to the connection auxiliary portion.

A linear compressor according to another aspect of the present specification for achieving the above problem includes a cylinder; A piston that reciprocates in the axial direction within the cylinder; And it may include a muffler unit that forms a flow path for the refrigerant supplied to the piston.

At this time, the flow path may include a first flow path extending rearward within the piston and a second flow path extending radially outward from the first flow path.

In addition, it includes a second noise space disposed between the first flow path and the second flow path, wherein the radial length of the second noise space is greater than the radial length of the first flow path, and the second noise space The cross-sectional area of the flow path may be larger than the cross-sectional area of the second flow path.

Additionally, a portion of the second flow path may extend forward from the radial outer side of the first flow path.

In addition, the muffler unit includes a first muffler unit forming the first flow path and a second muffler unit forming the second flow path, the first muffler unit is coupled to the piston, and the first muffler unit is coupled to the piston. The rear end of the unit may reciprocate in the axial direction inside the second muffler unit.

Additionally, a casing accommodating the cylinder; And it may include a suction pipe that penetrates the side of the casing and supplies refrigerant to the second flow path.

Through this specification, space efficiency can be increased by reducing the installation space of the suction pipe formed at the rear of the casing, and compressor cooling efficiency by the cooling fan can be increased.

In addition, low-frequency resonance noise caused by the structure of the linear compressor, which is formed to be long in the axial direction, can be reduced.

1 is a perspective view of a linear compressor according to an embodiment of the present specification.
Figure 2 is a cross-sectional view of a linear compressor according to an embodiment of the present specification.
Figure 3 is a rear view of the linear compressor according to an embodiment of the present specification with the first shell cover removed.
Figure 4 is a perspective view of a partial configuration of a linear compressor according to an embodiment of the present specification.
Figure 5 is a cross-sectional view of a portion of a linear compressor according to an embodiment of the present specification.
Figure 6 is an exploded perspective view of a portion of a linear compressor according to an embodiment of the present specification.
Figure 7 is a perspective view of a second muffler unit of a linear compressor according to an embodiment of the present specification.
Figure 8 is a cross-sectional view of a portion of a linear compressor according to another embodiment of the present specification.
Figure 9 is a perspective view of a second muffler unit of a linear compressor according to another embodiment of the present specification.
Figure 10 is a side view of a linear compressor according to an embodiment of the present specification.
Figure 11 is a side view of a linear compressor according to the prior art.
Figure 12 is a graph showing the magnitude (dB) of resonance noise by frequency (Hz) generated when a linear compressor according to the prior art is started.

Hereinafter, embodiments disclosed in the present specification (discloser) will be described in detail with reference to the attached drawings. However, identical or similar components will be assigned the same reference numbers regardless of reference numerals, and duplicate descriptions thereof will be omitted.

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

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

Meanwhile, the term ‘discloser’ can be replaced with terms such as document, specification, description, etc.

Figure 1 is a perspective view of a linear compressor 100 according to an embodiment of the present specification.

Referring to FIG. 1, a linear compressor 100 according to an embodiment of the present specification may include a casing 110. The casing 110 may include a shell 111 and shell covers 112 and 113 coupled to the shell 111. In a broad sense, the shell covers 112 and 113 may be understood as a component of the shell 111.

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

The shell 111 has a substantially cylindrical shape and can be arranged to lie horizontally or in an axial direction. Based on Figure 1, the shell 111 extends long in the horizontal direction and may have a somewhat low height in the radial direction. That is, since the linear compressor 100 can have a low height, for example, when the linear compressor 100 is installed in the machine room base of a refrigerator, there is an advantage in that the height of the machine room can be reduced.

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

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

A bracket 31 may be installed on the outside of the terminal 30. The bracket 31 may include a plurality of brackets surrounding the terminal 30. The bracket 31 may perform the function of protecting the terminal 30 from external shock, etc.

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

Based on 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 arranged to face each other. Additionally, it may be understood that the first shell cover 112 is located on the suction side of the refrigerant, and the second shell cover 113 is located on the discharge side of the refrigerant.

The linear compressor 100 is provided in the shell 111 or the shell covers 112 and 113 and may include a plurality of pipes 114, 115, and 40 through which refrigerant can be sucked in, discharged, or injected.

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

The suction pipe 114 penetrates the casing 110 in the radial direction and may supply refrigerant to the second muffler unit 190. Specifically, the suction pipe 114 may supply refrigerant to the second flow path 106 formed in the second extension portion 192 of the second muffler unit 190. At this time, the suction pipe 114 may penetrate the casing 110 at a position corresponding to the position of the second opening 193 formed in the second muffler unit 190 inside the casing 110.

When the casing 110 includes a cylindrical shell 111 with openings at both ends, and a first shell cover 112 and a second shell cover 113 coupled to both ends of the shell 111, the suction pipe 114 ) can be coupled by penetrating the shell 111 in the radial direction. Since the first shell cover 112 is inserted into the right opening of the shell 111 and welded, a portion where the edges of the shell 111 and the first shell cover 112 overlap in the radial direction may be formed. At this time, the suction pipe 114 may be coupled through the shell 111 at a position where the shell 111 and the first shell cover 112 do not overlap.

The discharge pipe 115 may be coupled to the outer peripheral surface of the shell 111. The refrigerant sucked through the suction pipe 114 may be compressed while flowing in the axial direction. And the compressed refrigerant can 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 supplement pipe 40 may be coupled to the outer peripheral surface of the shell 111. An operator can inject refrigerant into the linear compressor 100 through the supplement pipe 40.

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

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

Accordingly, the size 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 becomes larger again as it passes through it. 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. Therefore, as the oil-separated refrigerant flows into the piston 150, the compression performance of the refrigerant can be improved. Oil can be understood as operating oil present in the cooling system.

Figure 2 is a cross-sectional view of the linear compressor 100 according to an embodiment of the present specification. Figure 3 is a rear view of the linear compressor 100 according to an embodiment of the present specification with the first shell cover removed. Figure 4 is a perspective view of a partial configuration of the linear compressor 100 according to an embodiment of the present specification. Figure 5 is a cross-sectional view of a portion of the linear compressor 100 according to an embodiment of the present specification. Figure 6 is an exploded perspective view of a portion of the linear compressor 100 according to an embodiment of the present specification. Figure 7 is a perspective view of the second muffler unit 190 of the linear compressor 100 according to an embodiment of the present specification.

Hereinafter, the compressor according to the present specification will be described by taking as an example a linear compressor 100 in which the piston 150 performs a linear reciprocating motion to suction and compress fluid and discharge the compressed fluid.

The linear compressor 100 according to an embodiment of the present specification includes a cylinder 140, a piston 150, a muffler unit 160, 190, a spring supporter 119, a resonance spring 118, and a magnet. It may include a frame 136 and a mover 135, but may be implemented excluding some of these configurations, and additional configurations other than these are not excluded.

The detailed configuration of the linear compressor 100 according to an embodiment of the present specification according to FIGS. 4 to 8, which will not be described below, is the same as the detailed configuration of the linear compressor 100 according to an embodiment of the present specification according to FIG. 3. It can be understood that

The linear compressor 100 may be a component of a refrigeration cycle, and the fluid compressed in the linear compressor 100 may be a refrigerant that circulates in a refrigeration cycle. In addition to the compressor, the refrigeration cycle may include a condenser, an expansion device, and an evaporator. Additionally, the linear compressor 100 can be used as a component of the cooling system of a refrigerator, but is not limited to this and can be widely used throughout the industry.

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

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

The main body of the linear compressor 100 may be elastically supported by elastic members 116 and 117 installed inside the casing 110. The elastic members 116 and 117 may include a rear elastic member 116 supporting the rear of the main body and a front elastic member 117 supporting the front of the main body. The elastic members 116 and 117 may support internal parts of the main body of the linear compressor 100 and absorb vibration and shock generated according to the reciprocating motion of the piston 150.

The casing 110 may form a closed space. The sealed space includes a receiving space 101 in which the sucked refrigerant is accommodated, a suction space 102 filled with the refrigerant before compression, a compression space 103 in which the refrigerant is compressed, and a discharge space filled with the compressed refrigerant ( 104) may be included.

Part of the refrigerant sucked from the suction pipe 114 may be filled in the receiving space 101, and the remainder may flow into the second muffler unit 190. The refrigerant flowing into the second muffler unit 190 may move to the compression space 103 along the refrigerant flow paths 105 and 106 formed inside the first muffler unit 160 and the second muffler unit 190. . The refrigerant moving into the compression space 103 is compressed by the axial reciprocating motion of the piston 150 and discharged into the discharge space 104, and is discharged to the outside through the discharge pipe 115 connected to the front side of the casing 110. may be discharged.

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

Casing 110 may be formed of a thermally conductive material. Through this, heat generated in the internal space of the casing 110 can be quickly dissipated to the outside.

The linear compressor 100 may include a rear elastic member 116. The rear side of the main body of the linear compressor 100 may be elastically supported in the axial and/or radial directions by the rear elastic member 116. The rear elastic member 116 may have one end connected to the casing 110 and the other end connected to the back cover 123. The rear elastic member 116 can absorb vibration and shock generated according to the reciprocating motion of the piston 150.

The rear elastic members 116 may be formed as a pair. Referring to FIG. 4 , when viewed from the rear in the axial direction, the pair of rear elastic members 116 may be formed to be left and right symmetrical. In this case, the main body can be effectively elastically supported not only in the axial direction but also in the radial direction.

The rear elastic member 116 includes an elastic portion 116a having elasticity, a first connection portion 116b disposed at one end of the elastic portion 116a, and a second connection portion 116c disposed at the other end of the elastic portion 116a. ) may include.

One end of the elastic portion 116a may be fixed to the first connection portion 116b, and the first connection portion 116b may be connected to the inner peripheral surface of the casing 110. In this case, the rear elastic members 116 formed as a pair may share one first connection portion 116b. Accordingly, one end of the rear elastic member 116 may be connected to the inner peripheral surface of the casing 110.

The second connection portion 116c may be disposed between the back cover 123 and the first fixing portion 1961 of the second muffler unit 190. When the first fixing part 1961 is coupled to the back cover 123, the second connecting part 116c may also be coupled to the back cover 123. Accordingly, the other end of the rear elastic member 116 is coupled to the rear of the back cover 123, and the linear compressor 100 can be elastically supported in the axial and/or radial directions by the rear elastic member 116. .

When the front elastic member 117 is connected to the lower part of the inner peripheral surface of the casing 110, the first connection part 116b may be preferably connected to the upper part of the inner peripheral surface of the casing 110. However, unlike FIG. 3, when the front elastic member 117 is connected to the upper part of the inner peripheral surface of the casing 110, it may be desirable for the first connection portion 116b to be connected to the lower part of the inner peripheral surface of the casing 110.

When the front elastic member 117 and the rear elastic member 116 are connected to the lower and upper parts, or the upper and lower parts, respectively, on the inner peripheral surface of the casing 110 (i.e., connected to each other at diagonal positions when viewed from the side), the piston (150 ) can cancel out the rotational moment of the body that occurs due to the axial reciprocating motion. However, it is not limited to this, and the second connection portion 116c may be coupled to various positions on the inner peripheral surface of the casing 110 depending on the arrangement or shape of the internal structure of the casing 110.

The rear elastic member 116 may be formed of a wire spring. A wire spring can be formed by bending an elastic wire. At this time, the elastic coefficient of the wire spring can be adjusted by adjusting the bending direction, bending number, and bending degree.

Unlike FIGS. 2 to 7 , the rear elastic member 116 may be formed of various elastic members such as leaf springs and coil springs.

The second shell cover 113 is coupled to the shell 111 to seal the front side of the shell 111, and can be coupled by inserting the discharge pipe 115 through the loop pipe 115a. The refrigerant discharged from the compression space 103 may pass through the discharge cover assembly 180 and then be discharged into the refrigeration cycle through the loop pipe 115a and the discharge pipe 115.

The front side of the main body of the linear compressor 100 may be elastically supported by the front elastic member 117 in the axial direction and/or radial direction of the shell 111 or the second shell cover 113.

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

Unlike Figure 3, the edge portion of the front elastic member 117 is attached to the inner surface of the shell 111 or adjacent to the second shell cover 113 through a separate bracket (not shown) coupled to the second shell cover 113. It may be supported in the forward direction with respect to the inner peripheral surface of the shell 111.

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

The linear compressor 100 may include a back cover 123. The back cover 123 may include a back plate portion 123a, a bridge portion 123b, and a first opening portion 123c. The back cover 123 may be elastically supported in the axial and/or radial directions with respect to the casing 110 by the rear elastic member 116.

The back cover 123 may include a back plate portion 123a. The back plate portion 123a may extend radially outward from the first extension portion 163 of the first muffler unit 160. That is, the radial central area of the back plate portion 123a may include a first opening 123c through which the first extension 163 of the first muffler unit 160 can pass.

The back cover 123 may include a bridge portion 123b. The bridge portion 123b may extend axially forward from the radial outer side of the back plate portion 123a. The front end of the bridge portion 123b may be coupled to the first flange portion 122 of the frame 120 with the driving unit 130 interposed therebetween. That is, since the back cover 123 is coupled to the frame 120, it can be understood as a stator. Through this, the main body including the frame 120, the drive unit 130, etc. can be elastically supported in the axial and/or radial directions with respect to the casing 110.

The back cover 123 may include a first opening 123c. The first opening 123c may be formed in the radial central area of the back plate portion 123a. The first extension 163 of the first muffler unit 160 may reciprocate in the axial direction together with the piston 150 inside the first opening 123c.

The shape of the first opening 123c may correspond to the shape of the outer peripheral surface of the first extension 163 of the first muffler unit 160. For example, if the first extension 163 is in the form of a pipe with a circular cross-sectional shape, the first opening 123c may also be formed in a circular shape.

The inner peripheral surface of the first opening 123c may be adjacent to the outer peripheral surface of the first extension portion 163. Since the first extension 163 can reciprocate in the axial direction inside the first opening 123c, the radius of the first opening 123c is slightly smaller than the radius of the outer surface of the first extension 163. It can be big.

When the refrigerant flowing through the suction pipe 114 flows into the first muffler through the second muffler unit 190, all of the refrigerant inside the second muffler unit 190 moves to the first muffler unit 160. It may be desirable. However, as described above, since the radius of the first opening 123c is slightly larger than the radius of the outer surface of the first extension 163, a portion of the refrigerant passes through the gap between the accommodating space inside the casing 110 ( 101).

The frame 120 may include a body portion 121 supporting the outer peripheral surface of the cylinder 140, and a first flange portion 122 connected to one side of the body portion 121 and supporting the driving unit 130. You can. The frame 120 may be elastically supported with respect to the casing 110 by the rear and front elastic members 116 and 117 along with the drive unit 130 and the cylinder 140.

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

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

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

A bearing inlet groove 125a forming a part of the gas bearing is formed on one side of the front surface of the first flange portion 122, and a bearing communication hole 125b penetrates from the bearing inlet groove 125a to the inner peripheral surface of the body portion 121. ) is formed, and a gas groove 125c communicating through the bearing communication hole 125b may be formed on the inner peripheral 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 with a smaller cross-sectional area than the bearing inlet groove 125a and is formed inclined toward the inner peripheral surface of the body portion 121. You can. And the gas groove 125c may be formed in an annular shape with a predetermined depth and axial length on the inner peripheral surface of the body portion 121. Alternatively, the gas groove 125c may be formed on the outer peripheral surface of the cylinder 140 where the inner peripheral surface of the body portion 121 is in contact, or may be formed on both the inner peripheral surface of the body portion 121 and the outer peripheral surface of the cylinder 140.

Additionally, a gas inlet 142 corresponding to the gas groove 125c may be formed on the outer peripheral surface of the cylinder 140.

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

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

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

Meanwhile, a gas bearing means capable of providing gas lubrication between the cylinder 140 and the piston 150 by supplying discharge gas to the gap between the outer peripheral surface of the piston 150 and the outer peripheral surface of the cylinder 140 may be provided. The discharged gas between the cylinder 140 and the piston 150 may provide levitation force to the piston 150 to reduce friction occurring between the piston 150 and the cylinder 140.

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

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

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

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

The piston 150 may include a head portion 151 and a guide portion 152. The head portion 151 may be formed in a disk shape. The head portion 151 may be partially open. The head portion 151 may partition the compressed space 103. The guide portion 152 may extend rearward from the outer peripheral surface of the head portion 151. The guide portion 152 may be formed in a cylindrical shape. The guide part 152 may be empty inside, and the front may be partially closed by the head part 151. The rear of the guide portion 152 may be opened and connected to the first muffler unit 160. The head portion 151 may be provided as a separate member coupled to the guide portion 152. Alternatively, the head portion 151 and the guide portion 152 may be formed integrally.

Piston 150 may include suction port 154. The suction port 154 may penetrate the head portion 151. The suction port 154 may communicate with the suction space 102 and the compression space 103 inside the piston 150. For example, the refrigerant flowing from the receiving space 101 into the suction space 102 inside the piston 150 passes through the suction port 154 and enters 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. 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 in a direction away from the central axis toward the rear of the piston 150.

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

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

An intake valve 155 that selectively opens and closes the intake port 154 may be mounted on the head portion 151 of the piston 150 adjacent to the compression space 103. The suction valve 155 operates 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 and into the compression space 103.

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

The linear compressor 100 may include muffler units 160 and 190. The muffler units 160 and 190 include a first muffler unit 160 inserted into the rear of the piston 150 and coupled to the piston 150, and a second muffler unit 190 coupled to the rear of the back cover 123. may include. The muffler units 160 and 190 may be made of plastic material considering weight and insulation properties.

The muffler units 160 and 190 may include a first muffler unit 160. The first muffler unit 160 includes an inner guide 161 disposed inside the piston 150, a first suction muffler 162 disposed behind the inner guide 161, and a first suction muffler 162. It may include a first extension portion 163 that is disposed at the rear of and communicates with the second intake muffler 191.

The first muffler unit 160 may include an internal guide 161. One side of the inner guide 161 may be deeply inserted into the piston 150, and the other side may be in communication with the first suction muffler 162. The inner guide 161 may be formed in a pipe shape. The inner guide 161 may have the same inner diameter at both ends. The inner guide 161 may be formed in a cylindrical shape. Alternatively, the inner diameter of the front end on the discharge side may be formed to be larger than the inner diameter of the rear end on the opposite side.

The first muffler unit 160 may include a first suction muffler 162. The first suction muffler 162 may be disposed behind the inner guide 161. The first intake muffler 162 may be disposed inside the piston 150 and/or behind the piston 150. The first extension 163 may be disposed inside the first opening 123c formed in the back plate portion 123a of the back cover 123.

The first suction muffler 162 and the internal guide 161 can be provided in various shapes, and the pressure of the refrigerant passing through the muffler units 160 and 190 can be adjusted through them. The first suction muffler 162 and the inner guide 161 may be formed integrally.

The first muffler unit 160 may include a first extension portion 163. The first extension 163 may be disposed at the rear of the first intake muffler 162. The first extension 163 may be formed in a pipe shape. The first extension 163 may have the same inner diameter at both ends. The first extension 163 may be formed in a cylindrical shape.

The first extension 163 may penetrate the first opening 123c. That is, the first extension portion 163 may overlap the back plate portion 123a in the radial direction. At this time, the rear end of the first extension 163 penetrating the first opening 123c may be disposed inside the second suction muffler 191 coupled to the rear of the back cover 123. As a result, the first flow path 105 inside the first muffler unit 160 and the second flow path 106 inside the second muffler unit 190 can be communicated with each other.

The first muffler unit 160 may form a first flow path 105 within which refrigerant can flow. The first passage 105 may extend axially from the front through the inner guide 161 and the first suction muffler 162 to the first extension portion 163. The first passage 105 may guide the refrigerant flowing into the first extension 163 from the second muffler unit 190 to the suction space 102 inside the piston 150.

The first suction muffler 162 may form a first noise space 107 inside. The first noise space 107 may be disposed between the inner guide 161 and the first extension portion 163. The first noise space 107 may be formed to extend from the middle of the first flow path 105 outward in the radial direction of the first flow path 105 . Specifically, the radial length of the first noise space 107 may be larger than the inner diameter of the inner guide 161 and the inner diameter of the first extension portion 163.

The passage cross-sectional area increases when the refrigerant moves from the first passage 105 of the first extension 163 to the first noise space 107, and from the first noise space 107 back to the first passage 105 of the internal guide 161. It can be understood that it becomes smaller when moving to (105).

Unlike FIGS. 2 to 7 , a plurality of noise spaces divided by baffles may be formed inside the first intake muffler 162. That is, the first suction muffler 162 may be formed by combining two or more members.

The muffler units 160 and 190 may include a second muffler unit 190. The second muffler unit 190 may be coupled to the rear of the back cover 123. The second muffler unit 190 may communicate with the first muffler unit 160 at the rear of the first muffler unit 160. The second muffler unit 190 may include a second suction muffler 191, a second extension part 192, a second opening part 193, a connection auxiliary part 194, and a nozzle part 195. there is.

The second muffler unit 190 may include a second suction muffler 191. The second intake muffler 191 may be coupled to the rear of the back plate portion 123a. The second suction muffler 191 may be in close contact with the rear of the back cover 123. The rear of the second intake muffler 191 may be blocked. The second intake muffler 191 may be understood as a cap shape that covers the rear end of the first extension 163 from the rear. Since the rear of the second suction muffler 191 is blocked, the flow of refrigerant from the second suction muffler 191 to the axial rear may be blocked.

A second noise space 108 may be formed between the second suction muffler 191 and the rear of the back cover 123. The rear end of the first extension 163 may be disposed in the second noise space 108. At this time, the first muffler unit 160 including the first extension 163 is connected to the piston 150 and reciprocates in the axial direction, so the rear end of the first extension 163 is a second noise space ( 108) can reciprocate in the axial direction.

That is, the rear end of the first muffler unit 160 may reciprocate in the axial direction inside the second muffler unit 190. In this way, when the first muffler unit 160 reciprocates independently of the second muffler unit 190, the second muffler unit 190 is in communication with the first muffler unit 160, but may be fixed. You can. Accordingly, the refrigerant can stably flow into the second muffler unit 190 through the suction pipe 114. Additionally, it is possible to prevent the problem of durability degradation that may occur when the second muffler unit 190 collides with another part.

The second muffler unit 190 may include a second extension portion 192. The second extension portion 192 may be disposed on the radial outer side of the second suction muffler 191 and communicate with the second suction muffler 191.

The second extension portion 192 may be in close contact with the back cover 123. The second extension portion 192 may be blocked at the rear. Accordingly, a second flow path 106 communicating with the second noise space 108 may be formed between the back cover 123 and the second extension portion 192.

In this case, the surface of the second extension 192 on the back cover 123 side is not blocked, and the second flow path 106 may be formed by the second extension 192 being in close contact with the back cover 123. . Accordingly, the manufacturing cost of the second muffler unit 190 can be reduced, and space utilization inside the casing 110 can be improved.

It can be understood that the second flow path 106 is not limited to the inside of the second extension 192, but extends to the inside of the second suction muffler 191.

The radial length (r2) of the inner surface of the second suction muffler 191 may be larger than the inner diameter (r1) of the first extension portion 163. This means that, from the perspective of the passages 105 and 106 through which the refrigerant flows, the axial passage cross-sectional area of the second noise space 108 formed in the second intake muffler 191 is the cross-sectional area of the second noise space 108 formed in the first extension portion 163. It can be understood as being larger than the channel cross-sectional area of 1 channel (105).

The cross-sectional area S1 of the second suction muffler 191 may be larger than the cross-sectional area S2 of the second extension part 192. This can be understood as, from the perspective of the passages 105 and 106 through which the refrigerant flows, the radial passage cross-sectional area (S1) of the second noise space 108 is larger than the radial passage cross-sectional area (S2) of the second passageway (106). You can.

Specifically, the second noise space 108 may be disposed between the first extension part 163 and the second extension part 192. Therefore, it can be understood that the passage cross-sectional area increases when the refrigerant moves from the second passage 106 to the second noise space 108, and then decreases when it moves from the second noise space 108 back to the first passage 105. there is.

The linear compressor 100 according to an embodiment of the present specification does not include a partition in the second noise space 108 and the second flow passage 106 and may be formed as one space. However, unlike FIGS. 3 and 6, a partition wall (not shown) may be installed between the second noise space 108 and the second flow path 106 to form a plurality of connected spaces.

The second muffler unit 190 may include a second opening 193. The refrigerant flowing through the suction pipe 114 may flow into the second muffler unit 190 through the second opening 193. One end of the suction pipe 114 may face the second opening 193.

In contrast, since the accommodation space 101 inside the casing 110 is full of refrigerant, the linear compressor 100 can operate normally even if the suction pipe 114 does not necessarily face the second opening 193. However, as the linear compressor 100 operates, the refrigerant temperature inside the receiving space may increase due to heat generated in the compression space 103 inside the cylinder. As the temperature of the refrigerant increases, the compression efficiency of the linear compressor 100 may decrease. Accordingly, as the distance between the suction pipe 114 and the second opening 193 increases, refrigerant with a higher temperature flows into the second opening 193, and the compression efficiency of the linear compressor 100 may decrease.

On the other hand, when the suction pipe 114 faces the second opening 193, room temperature refrigerant flowing from outside the casing 110 can flow directly into the second opening 193, resulting in a decrease in efficiency due to an increase in the temperature of the refrigerant. Problems can be prevented. Accordingly, it may be desirable for one end of the suction pipe 114 to face the second opening 193.

The casing 110 of the linear compressor 100 according to an embodiment of the present specification includes a substantially cylindrical shell 111 with openings at both ends, a first shell cover 112 coupled to both ends of the shell 111, and It may include a second shell cover 113. Since the first shell cover 112 is inserted into the right opening of the shell 111 and welded, a portion where the edges of the shell 111 and the first shell cover 112 overlap in the radial direction may be formed. At this time, the suction pipe 114 may penetrate the shell 111 in the radial direction at a position where the shell 111 and the first shell cover 112 do not overlap in the radial direction. Therefore, it may be desirable for the suction pipe 114 to penetrate the shell 111 from the front.

In this way, when one end of the suction pipe 114 is disposed ahead of the first shell cover 112, the second opening 193 opposite the one end of the suction pipe 114 is also formed corresponding to the penetration position of the suction pipe 114. 2 It can be placed ahead of the intake muffler (191). That is, the second opening 193 may overlap the first muffler unit 160 in the radial direction.

In other words, the second extension portion 192 extends radially outward from the second suction muffler 191, and a portion of the extended portion may extend axially forward. At this time, the end extending forward in the axial direction may be disposed ahead of the second intake muffler 191.

Specifically, the second extension portion 192 includes a vertical portion 192a that communicates with the second suction muffler 191 and extends radially outward, and a horizontal portion 192b that communicates with the vertical portion 192a and extends forward. ) may include.

The vertical portion 192a may be in close contact with the back plate portion 123a of the back cover 123, and the horizontal portion 192b may be in close contact with the bridge portion 123b of the back cover 123. As a result, the second extension part 192 is in close contact with the back plate part 123a and the bridge part 123b of the back cover 123, and the refrigerant flows between the second extension part 192 and the back cover 123. A second flow path 106 may be formed.

The second opening 193 may be disposed in the horizontal portion 192b. The second opening 193 may overlap the first muffler unit 160 in the radial direction. Specifically, the horizontal portion 192b may extend further forward than the penetrating position of the suction pipe 114, and the second opening 193 may be positioned at a position corresponding to the position of one end of the suction pipe 114 on the horizontal portion 192b. can be placed in

The axial length of the vertical portion 192a of the second extension 192 may be equal to the axial length of the second suction muffler 191. That is, as shown in FIGS. 5 to 7, the rear of the second extension portion 192 and the rear of the second suction muffler 191 may be formed on the same plane. However, the axial length of the second extension portion 192 and the axial length of the second suction muffler 191 are formed differently depending on the internal configuration of the linear compressor 100 or the required degree of compression noise attenuation. It can be.

The second muffler unit 190 may include a nozzle unit 195. The nozzle unit 195 may be disposed between the second opening 193 and the suction pipe 114. The nozzle unit 195 can effectively guide the refrigerant supplied from the suction pipe 114 to the second opening 193.

The radially inner radius of the nozzle unit 195 may be smaller than the radially outer radius. The radius of the nozzle unit 195 may increase as it goes outward in the radial direction. In other words, the shape of the nozzle unit 195 can be understood as being formed in a funnel shape.

The radial outer radius of the nozzle unit 195 may be formed to be larger than the radius of the suction pipe 114. Through this, the refrigerant supplied from the suction pipe 114 can be effectively guided to the second opening 193.

Additionally, in order to effectively guide the refrigerant supplied from the suction pipe 114 to the second opening 193, it may be preferable that the distance between the second opening 193 and one end of the suction pipe 114 be smaller. In this case, the nozzle unit 195 may extend further outward in the radial direction than one end of the suction pipe 114.

The nozzle unit 195 may be formed of an elastic material. For example, it may be formed of rubber. If the nozzle unit 195 is made of an elastic material, it may be easy to press-fit the nozzle unit 195 into the connection part. In addition, as described above, when the distance between one end of the suction pipe 114 and the second opening 193 becomes short, if the nozzle portion 195 is formed of a rigid body rather than an elastic material, the reciprocation of the piston 150 A collision between the nozzle unit 195 and the suction pipe 114 may occur due to vibration of the main body due to movement. Such collisions may cause noise and may reduce the durability of the linear compressor 100. Therefore, it may be desirable for the nozzle portion 195 to be formed of an elastic material.

Alternatively, the nozzle portion 195 may be formed as a rigid body and formed integrally with the second extension portion 192. In this case, a certain gap may be provided between one end of the suction pipe 114 and the second opening 193 to solve the noise or durability problems described above.

Additionally, unlike FIGS. 2 to 7 , the linear compressor 100 may not include the nozzle unit 195.

The second muffler unit 190 may include a connection auxiliary part 194. The connection auxiliary part 194 may protrude to the outside of the second opening 193. The connection auxiliary part 194 may be formed in a cylindrical shape. The cross-sectional shape of the inner peripheral surface of the connection auxiliary part 194 may correspond to the shape of the second opening 193. The radial inner side of the nozzle portion 195 may be coupled to the connection portion by press fitting.

The second muffler unit 190 may include fixing parts 1961 and 1962. The fixing parts 1961 and 1962 may extend outward from the second intake muffler 191. At least one fixing part 1961 or 1962 may be formed.

For example, it may be desirable to have three fixing parts 1961 and 1962. If there are less than three, the fixing force of the second muffler unit 190 to the back cover 123 may be reduced due to vibration of the main body caused by the reciprocating motion of the piston 150. If more than three are formed, manufacturing costs may increase and the manufacturing process may become complicated due to excessive use of members. However, the present invention is not limited to this, and various waterway fixing parts 1961 and 1962 may be formed depending on the durability required for the linear compressor 100. When three fixing parts 1961 and 1962 are formed, each fixing part 1961 and 1962 may be formed at an interval of approximately 120 degrees from each other about an axis.

The fixing parts 1961 and 1962 may include a first fixing part 1961 and a second fixing part 1962. The first fixing part 1961 is a fixing part where the second connection part 116c of the rear elastic member 116 is disposed, and the second fixing part 1962 is a fixing part where the second connection part 116c of the rear elastic member 116 is disposed. It may be a fixed part that does not work.

Since the rear elastic members 116 are formed in pairs, the first fixing parts 1961 may also be formed in pairs. For example, when the rear elastic member 116 is connected to the upper part of the inner surface of the casing 110 as shown in FIGS. 3 to 8, based on FIG. 3, the first pair of fixing parts 1961 are the 2 Can be formed on the upper right and upper left sides of the intake muffler 191, respectively. In this case, the second fixing part 1962 may be formed at the lower part of the second suction muffler 191.

The second connection portion 116c of the rear elastic member 116 may be disposed between the back cover 123 and the first fixing portion 1961. At this time, a space capable of accommodating the second connection part 116c may be formed between the first fixing part 1961 and the back cover 123. Specifically, the first fixing part 1961 may be formed in a cap shape that can cover the second connecting part 116c forward. In this case, the axial length of the first fixing part 1961 may be greater than the axial length of the second fixing part 1962.

The first fixing part 1961 may include a first fixing hole 1961a, and the second fixing part 1962 may include a second fixing hole 1962a. The back cover 123 may include a third fixing hole 123d formed at a position corresponding to the first fixing hole 1961a and the second fixing hole 1962a. The second connection portion 116c may include a fourth fixing hole 116d formed at a position corresponding to the first fixing hole 1961a and the third fixing hole 123d.

The linear compressor 100 may include fixing members 1971 and 1972. The fixing members 1971 and 1972 may pass through the fixing parts 1961 and 1962 and be coupled to the back cover 123. The other end of the rear elastic member 116 may be disposed between the fixing parts 1961 and 1962 and the back cover 123.

Specifically, the fixing members 1971 and 1972 may include a first fixing member 1971 penetrating the first fixing part 1961 and a second fixing member 1972 penetrating the second fixing part 1962. You can. The first fixing member 1971 penetrates the first fixing hole 1961a, the fourth fixing hole 116d, and the third fixing hole 123d to couple the second suction muffler 191 to the back cover 123. You can. The second fixing member 1972 may couple the second suction muffler 191 to the back cover 123 by penetrating the second fixing hole 1962a and the third fixing hole 123d. In this case, since the axial length of the first fixing member 1961 is greater than the axial length of the second fixing member 1962, the axial length of the first fixing member 1971 is longer than that of the second fixing member 1972. It can be larger than the axial length.

Unlike FIGS. 2 to 7 , the second intake muffler 191 may be coupled to the back cover 123 in various ways. For example, when using an adhesive such as epoxy, the fixing members 1971 and 1972 may not be included.

Unlike FIGS. 2 to 7 , the rear elastic member 116 may be formed of various elastic members such as leaf springs and coil springs.

Hereinafter, the muffler units 160 and 190 will be described from the perspective of the passages 105 and 106 through which refrigerant flows.

The muffler units 160 and 190 may form passages 105 and 106 for the refrigerant supplied to the piston 150. The passages 105 and 106 may be understood as passages inside the muffler units 160 and 190 through which refrigerant flowing into the muffler units 160 and 190 from the suction pipe 114 can flow. The passages 105 and 106 may guide the refrigerant introduced from the suction pipe 114 to the internal suction space of the piston 150.

The flow paths 105 and 106 may include a first flow path 105 extending rearward within the piston 150 and a second flow path 106 extending radially outward from the first flow path 105. The first flow path 105 may refer to a flow path formed inside the first muffler unit 160, and the second flow path 106 may refer to a flow path formed inside the second muffler unit 190.

The second flow path 106 may communicate behind the first flow path 105. Specifically, the rear end of the first passage 105 may be disposed within the second noise space 108. The second extension 192 may also be in communication with the second noise space 108. Accordingly, the first flow path 105 and the second flow path 106 may communicate with each other.

A portion of the second flow path 106 may extend forward from the radial outer side of the first flow path 105. The refrigerant flowing from the suction pipe 114 may flow into the second flow path 106 through the second opening 193. At this time, as described above, it is preferable that the suction pipe 114 and the second opening 193 face each other. Therefore, when the suction pipe 114 penetrates the shell 111 from the front of the first shell cover 112 so as not to overlap the first shell cover 112, the second opening 193 is connected to the first muffler unit 160. and overlaps in the radial direction, and a portion of the second flow path 106 may extend forward corresponding to the position of the second opening 193.

The first muffler unit 160 is connected to the piston 150 and can reciprocate in the axial direction together with the piston 150. The second muffler unit 190 is coupled to the back cover 123 and can therefore be fixed. That is, the first muffler unit 160 may be a mover, and the second muffler unit 190 may be a stator. Accordingly, the rear end of the first passage 105 may be disposed in the second noise space 108 and may reciprocate in the axial direction within the second noise space 108.

The muffler units 160 and 190 may include a first noise space 107 and a second noise space 108. The first noise space 107 may be formed inside the first suction muffler 162, and the second noise space 108 may be formed inside the second suction muffler 191.

The first muffler unit 160 may include a first noise space 107. The first noise space 107 may be disposed between the inner guide 161 and the first extension 163. The first noise space 107 may be formed to extend from the middle of the first flow path 105 outward in the radial direction of the first flow path 105 . Therefore, the passage cross-sectional area increases when the refrigerant moves from the first passage 105 of the first extension 163 to the first noise space 107, and from the first noise space 107 again to the first noise space 107 of the internal guide 161. It can be understood that it becomes smaller when moving to 1 euro (105).

The second muffler unit 190 may include a second noise space 108. The second noise space 108 may be disposed between the first flow path 105 and the second flow path 106. The radial length r2 of the second noise space 108 may be larger than the inner diameter r1 of the first flow path 105. In other words, the axial passage cross-sectional area of the second noise space 108 may be larger than the passage cross-sectional area of the first passage 105.

Additionally, the cross-sectional area S1 of the second noise space 108 may be larger than the cross-sectional area S2 of the second noise space 106 . Therefore, it can be understood that the passage cross-sectional area increases when the refrigerant moves from the second passage 106 to the second noise space 108, and decreases when it moves from the second noise space 108 back to the first passage 105. .

When the linear compressor 100 is driven, the refrigerant is compressed in the compression space 103 inside the cylinder by the axial reciprocating motion of the piston 150, and is discharged into the discharge space 104. During this process, the pressure of the refrigerant changes and noise occurs. Compression noise generated in the compression space 103 and the piston 150 may move rearward along the flow path.

Compression noise generated in front of the piston 150 passes through the internal guide 161 and is radiated to the first noise space 107. At this time, since the cross-sectional area of the passage of the first noise space 107 increases, the sound pressure of the compressed noise can be lowered and the compressed noise can be attenuated. Additionally, part of the compressed noise may disappear while being reflected in the first noise space 107.

Compressed noise passing through the first noise space 107 may be radiated to the second noise space 108 along the first extension portion 163. At this time, since the cross-sectional area of the second noise space 108 increases, the sound pressure of the compressed noise can be lowered and the compressed noise can be attenuated. Additionally, part of the compressed noise may disappear while being reflected in the second noise space 108.

The linear compressor 100 according to an embodiment of the present specification may include at least two noise spaces capable of attenuating compression noise as described above. That is, the linear compressor of the prior art includes one muffler unit, but the linear compressor 100 according to an embodiment of the present specification includes at least two muffler units 160 and 190, thereby increasing the compression noise attenuation effect. You can do it.

Meanwhile, the second suction muffler 191 may be in close contact with the rear of the back cover 123. The rear of the second intake muffler 191 may be blocked. The second intake muffler 191 may be understood as a cap shape that covers the rear end of the first extension 163 from the rear. Since the rear of the second suction muffler 191 is blocked, the flow of refrigerant toward the axial rear in the second noise space 108 and the second flow path 106 may be blocked.

If the flow of refrigerant is not blocked at the axial rear of the flow path as in a conventional linear compressor, compression noise may move backward along the flow path and then be radiated directly into the receiving space inside the casing. In this way, the noise radiated into the accommodation space inside the casing may resonate with the refrigerant filled within the accommodation space. In other words, resonance noise may occur.

The above-mentioned resonance noise may occur in the axial and radial directions, respectively. Typically, in the case of the linear compressor 100, the axial length may be longer than the radial length. Therefore, axial resonance noise may have a lower frequency (300 to 400 hz) than radial resonance noise.

Unlike the linear compressor 100 according to an embodiment of the present specification, if the flow of refrigerant in the axial direction from the rear of the piston 150 is not blocked, compression noise may be radiated directly in the axial direction along the flow path. In this case, the noise radiated in the axial direction resonates with the refrigerant in the receiving space 101 in the axial direction, so low-frequency resonance noise may increase.

However, in the linear compressor 100 according to an embodiment of the present specification, as described above, the flow of refrigerant in the axial direction is blocked by the second muffler unit 190, so compression noise is generated in the flow paths 105 and 106. It can be prevented from radiating directly in the axial direction along the . Therefore, through the linear compressor 100 according to an embodiment of the present specification, low-frequency resonance noise generated by resonance in the axial direction with the refrigerant inside the accommodation space 101 can be reduced.

The linear compressor 100 may include a discharge valve assembly 170. The discharge valve assembly 170 may include a discharge valve 171 and a valve spring 172 provided on the front side of the discharge valve 171 to elastically support the discharge valve 171. The discharge valve assembly 170 can selectively discharge compressed refrigerant from the compression space 103. Here, the compressed space 103 refers to the space formed between the intake valve 155 and the discharge valve 171.

The discharge valve 171 may be placed on the front of the cylinder 140 to be supportable. The discharge valve 171 can selectively open and close the front opening of the cylinder 140. The discharge valve 171 operates by elastic deformation to open or close the compressed space 103. The discharge valve 171 may be elastically deformed to open the compression space 103 by the pressure of the refrigerant flowing through the compression space 103 and into the discharge space 104. For example, while the discharge valve 171 is supported on the front of the cylinder 140, the compression space 103 is maintained in a sealed state and the discharge valve 171 is spaced apart from the front of the cylinder 140. The compressed refrigerant in the compression space 103 may be discharged from the open space.

The valve spring 172 may be provided between the discharge valve 171 and the discharge cover assembly 180 to provide 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 considering space occupancy or reliability.

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

The process in which refrigerant flows into the compression space 103 through the suction valve 155 and discharges the refrigerant in the compression space 103 into the discharge space 104 through the discharge valve 171 is described as follows.

In the process of the piston 150 reciprocating linear motion inside the cylinder 140, when the pressure in the compression space 103 falls below the predetermined suction pressure, the suction valve 155 opens and the refrigerant flows into the compression space 103. It is 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.

Meanwhile, when the pressure of the compression space 103 exceeds the predetermined discharge pressure, the valve spring 172 deforms forward and opens the discharge valve 171 connected thereto, and the refrigerant is discharged from the compression space 103 to the discharge cover assembly ( It is discharged into the discharge space 104 of 180). When discharge of the refrigerant is completed, the valve spring 172 provides restoring force to the discharge valve 171, and the discharge valve 171 closes to seal the front of the compression space 103.

The discharge cover assembly 180 is installed in front of the compression space 103, forms a discharge space 104 that accommodates the refrigerant discharged from the compression space 103, and is coupled to the front of the frame 120 to allow the refrigerant to flow. Noise generated during the discharge process from the compressed space 103 can be reduced. The discharge cover assembly 180 may accommodate the discharge valve assembly 170 and be coupled to the front of the first flange portion 122 of the frame 120. For example, the discharge cover assembly 180 may be coupled to the first flange portion 122 through a mechanical coupling member.

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

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

The discharge cover assembly 180 may be composed of one discharge cover, or may be arranged so that a plurality of discharge covers sequentially communicate with each other. When the discharge cover assembly 180 is provided with a plurality of discharge covers, the discharge space 104 may include a plurality of space portions partitioned by each discharge cover. A plurality of space parts may be arranged in the front-back direction and communicate with each other.

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

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

The drive 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 a stator between the outer stator 131 and the cylinder 140. It may include an inner stator 134 disposed to surround the cylinder 140 and a mover 135 disposed between the outer stator 131 and the inner stator 134.

The outer stator 131 may be coupled to the rear of the first flange portion 122 of the frame 120, and the inner stator 134 may be coupled to the outer peripheral surface of the body portion 121 of the frame 120. Additionally, the inner stator 134 may be disposed to be spaced apart inside the outer stator 131, and the mover 135 may be disposed in the 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 include a permanent magnet. A permanent magnet may be composed of a single magnet with one pole, or may be composed of a plurality of magnets with three poles combined.

The outer stator 131 may include a coil winding body 132 surrounding the axial direction in the 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 circular or polygonal, for example, hexagonal. The stator core 133 may include a plurality of lamination sheets radially stacked, or a plurality of lamination blocks may be stacked along a circumferential direction.

The front side of the outer stator 131 may be supported by the first flange 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 the shape of a hollow disk, the outer stator 131 may be supported on the front side, and the resonance spring 118 may be supported on the rear side.

The inner stator 134 may be composed of a plurality of laminations stacked in the circumferential direction on the outer peripheral surface of the body portion 121 of the frame 120.

The mover 135 may be supported by being coupled to one side of the magnet frame 136. The magnet frame 136 has a substantially cylindrical shape and may be arranged to be inserted into the space between the outer stator 131 and the inner stator 134. Additionally, the magnet frame 136 may be coupled to the rear side of the piston 150 and be provided to move together with the piston 150.

As an example, the rear end of the magnet frame 136 is bent and extended radially inward to form a first coupling portion 136a, and the first coupling portion 136a is a third coupling portion formed at the rear of the piston 150. It may be coupled to the flange portion 153. The first coupling portion 136a of the magnet frame 136 and the third flange portion 153 of the piston 150 may be coupled through a mechanical coupling member.

Furthermore, through this, the piston 150, the first muffler unit 160, and the mover 135 can be integrally coupled and reciprocate in the axial direction together.

When current is applied to the drive unit 130, magnetic flux is formed in the winding coil, and the interaction between 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 Electromagnetic force is generated by the action, allowing the mover 135 to move. Additionally, at the same time as the axial reciprocating movement of the mover 135, the piston 150 connected to the magnet frame 136 may also reciprocate in the axial direction integrally with the mover 135.

Meanwhile, the driving unit 130 and the compression units 140 and 150 may be supported in the axial direction by the elastic members 116 and 117 and the resonant spring 118.

The resonant spring 118 can amplify the vibration realized by the reciprocating motion of the mover 135 and the piston 150, thereby achieving effective compression of the refrigerant. Specifically, the resonance spring 118 may be adjusted to a frequency corresponding to the natural frequency of the piston 150 to enable the piston 150 to move in resonance. Additionally, the resonance spring 118 can reduce vibration and noise generation by causing stable movement of the piston 150.

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

The natural frequency of the resonance spring 118 is designed to match the resonance frequencies of the mover 135 and the piston 150 when the linear compressor 100 is operating, thereby amplifying the reciprocating motion of the piston 150. However, since the back cover 123 provided as a fixture here is elastically supported by the rear elastic member 116 on the casing 110, it may not be strictly fixed.

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

The spring supporter 119 includes a body portion 119a surrounding the first intake muffler 162, a second coupling portion 119b bent in the inner radial direction at the front of the body portion 119a, and a body portion 119a. ) may include a support portion 119c bent in the outer radial direction at the rear.

The front surface of the second coupling portion 119b of the spring supporter 119 may be supported by the first coupling portion 136a of the magnet frame 136. The inner diameter of the second coupling portion 119b of the spring supporter 119 may surround the outer diameter of the first suction muffler 162. For example, the second coupling portion 119b of the spring supporter 119, the first coupling portion 136a of the magnet frame 136, and the third flange portion 153 of the piston 150 are arranged in order. Later, they can be integrally combined through mechanical members.

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

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

The linear compressor 100 may include a plurality of sealing members that can increase the coupling force between the frame 120 and its surrounding components.

For example, the plurality of sealing members include a first sealing member inserted into an installation groove provided at the front end of the frame 120 and a frame ( It may include a second sealing member provided at a portion where the cylinder 120 and the cylinder 140 are coupled and inserted into an 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 peripheral surface of the frame 120 and the outer peripheral surface of the cylinder 140 from leaking to the outside, and increases the coupling force between the frame 120 and the cylinder 140. can be increased. In addition, the plurality of sealing members may further include a third sealing member provided at a portion where the frame 120 and the inner stator 134 are coupled and inserted into an installation groove provided on the 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 current is applied to the driving unit 130, magnetic flux may be formed in the outer stator 131 by the current flowing in the coil 132b. The magnetic flux formed in the outer stator 131 generates electromagnetic force, and the mover 135 equipped with a permanent magnet can perform linear reciprocating motion by the generated electromagnetic force. This electromagnetic force is generated in the direction (forward direction) of the piston 150 toward top dead center (TDC) during the compression stroke, and during the intake stroke, the piston 150 is generated toward bottom dead center (BDC). ) may occur alternately in the direction facing (backward direction). That is, the driving unit 130 can generate thrust, which is a force that pushes the mover 135 and the piston 150 in the moving direction.

The piston 150, which linearly reciprocates inside the cylinder 140, may repeatedly increase or decrease the volume of the compression space 103.

When the piston 150 moves in a direction (rearward direction) to increase the volume of the compression space 103, the pressure of the compression space 103 may decrease. Accordingly, the intake valve 155 mounted in front of the piston 150 is opened, and the refrigerant remaining in the intake space 102 can be sucked into the compression space 103 along the intake port 154. This suction stroke may proceed until the piston 150 maximizes the volume of the compression space 103 and is located at bottom dead center.

The piston 150, which has reached the bottom dead center, may change its direction of movement and perform a compression stroke while moving in a direction (forward direction) that reduces the volume of the compression space 103. During the compression stroke, the pressure in the compression space 103 increases and the sucked refrigerant may be compressed. When the pressure of the compression space 103 reaches the set pressure, the discharge valve 171 is pushed by the pressure of the compression space 103 and opens from the cylinder 140, and the refrigerant flows into the discharge space 104 through the spaced apart space. ) can be discharged. This compression stroke may continue while the piston 150 moves to top dead center where the volume of the compression space 103 is minimal.

As the suction stroke and compression stroke of the piston 150 are repeated, the refrigerant flowing into the linear compressor 100 through the suction pipe 114 passes through the muffler units 160 and 190 and enters the suction space 102 inside the piston 150. ), and the refrigerant in the suction space 102 may flow into the compression space 103 inside the cylinder 140 during the suction stroke of the piston 150. During the compression stroke of the piston 150, the refrigerant in the compression space 103 is compressed and discharged into the discharge space 104, and then flows to the outside of the linear compressor 100 through the loop pipe 115a and the discharge pipe 115. A discharge stream may be formed.

Figure 8 is a cross-sectional view of a portion of the linear compressor 100 according to another embodiment of the present specification. Figure 9 is a perspective view of the second muffler unit 290 of the linear compressor 100 according to another embodiment of the present specification.

The detailed configuration of the linear compressor 100 according to another embodiment of the present specification according to FIGS. 8 to 9, which will not be described below, is the detailed configuration of the linear compressor 100 according to an embodiment of the present specification according to FIGS. 4 to 7. It can be understood as the same as composition.

Referring to FIGS. 8 and 9 , the linear compressor 100 may include a second muffler unit 290. The second muffler unit 290 may be coupled to the rear of the back cover 123. The second muffler unit 190 may communicate with the first muffler unit 160 at the rear of the first muffler unit 160.

The second muffler unit 290 may include a second suction muffler 291, a second extension part 292, and a connection auxiliary part 294.

The second muffler unit 290 may include a second suction muffler 291. The second intake muffler 291 may be coupled to the rear of the back plate portion 123a. The second suction muffler 191 may be in close contact with the rear of the back cover 123. The rear of the second intake muffler 291 may be blocked. The second intake muffler 291 may be understood as a cap shape that covers the rear end of the first extension 163 from the rear. Since the rear of the second suction muffler 291 is blocked, the flow of refrigerant from the second suction muffler 291 to the axial rear may be blocked.

A second noise space 208 may be formed between the second intake muffler 291 and the rear of the back cover 123. The rear end of the first extension 163 may be disposed in the second noise space 208. At this time, the first muffler unit 160 including the first extension 163 is connected to the piston 150 and reciprocates in the axial direction, so the rear end of the first extension 163 is a second noise space ( 208) can reciprocate in the axial direction.

The second muffler unit 190 may include a second extension portion 292. The second extension portion 292 may be disposed on the radial outer side of the second suction muffler 291 and communicate with the second suction muffler 291.

The second extension 292 may be formed in a pipe shape. The cross-sectional shape of the second extension portion 292 may be formed in various ways. For example, as shown in FIG. 9, the cross-sectional shape of the second extension portion 292 may be approximately rectangular. However, it is not limited to this, and the cross-sectional shape of the second extension portion 292 may be variously formed, such as circular, semicircular, or polygonal.

The second flow path 206 may be formed inside the second extension portion 292. The second flow path 206 may be formed independently from the back cover 123. That is, unlike the linear compressor 100 according to an embodiment of the present specification, the side of the back cover 223 of the second extension part 292 may be blocked. Accordingly, the second flow path 106 can be formed inside the second extension portion 292 even if it is not in close contact with the back cover 123. It can be understood that the second flow path 206 is not limited to the inside of the second extension portion 292, but extends to the inside of the second suction muffler 291.

The second extension portion 292 may be formed integrally with the second suction muffler 291. However, the present invention is not limited to this, and the second extension portion 292 may be manufactured separately and coupled to the second suction muffler 291. In this case, the second extension portion 292 and the second suction muffler 291 may be formed of the same material or may be formed of different materials.

When the second extension part 292 is formed and assembled separately from the second suction muffler 291, the shapes of each of the second suction muffler 291 and the second extension part 292 can be simplified. Accordingly, the manufacturing process can be simplified and manufacturing costs can be reduced.

Unlike FIGS. 8 and 9, the second extension portion 292 may be disposed at the rear of the second suction muffler 291 and communicate with the rear of the second suction muffler 291. In this case, in order to achieve the purpose of the present specification, the second extension portion 292 may be bent outward in the radial direction.

As described above, if the second extension part 292 is formed as a pipe, the second extension part 292 can be formed in a more free form. Accordingly, it may be easy to correspond to the position of the suction pipe 214 penetrating into the casing 210 and the position of the second opening 293 formed in the second extension part 292. Additionally, since the casing 110 can be formed into various shapes in response to the arrangement of the internal components, the space efficiency inside the casing 110 can be increased.

Additionally, if the temperature of the refrigerant flowing from the suction pipe 114 increases, there is a risk that the efficiency of the linear compressor 100 may decrease. 8 and 9, if the second extension portion 292 is not in close contact with the back cover 123, the heat generated as the refrigerant is compressed in the compression space 103 is directly transmitted to the second extension portion 292 through the back cover 123. Transfer to the extension part 292 can be prevented. Therefore, in the linear compressor 100 according to another embodiment of the present specification, an increase in the temperature of the refrigerant passing through the second flow path 206 formed inside the second extension portion 292 can be prevented, so that the linear compressor The compression efficiency of (100) can be increased.

Figure 10 is a side view of the linear compressor 100 according to an embodiment of the present specification.

Referring to FIG. 10, inside the machine room of a refrigerator, the linear compressor 100 and the cooling fan (PAN) may be generally arranged in that order from the front. At this time, the cooling fan (PAN) may serve to cool the heat of the casing 110 generated while the linear compressor 100 operates.

Referring to FIG. 10, in the linear compressor 100 according to an embodiment of the present specification, the suction pipe 114 may be coupled to the side of the casing 110, that is, penetrating the shell 111 in the radial direction.

When viewed from the side of the linear compressor 100, the outer portion of the suction pipe 114 of the casing 110 may be coupled to the casing 110 at a certain angle a. The outer portion of the casing 110 of the suction pipe 114 may be connected to a refrigerant pipe leading into the refrigerator machine room. At this time, depending on the structure of the refrigerator machine room or the entry location of the refrigerant pipe, the outer portion of the casing 110 of the suction pipe 114 may be arranged to form an appropriate angle (a). When viewed from the side of the casing 110, the angle (a) may have a positive (+) value or a negative (-) value based on the vertical line (L).

In the linear compressor 100 according to the present specification, the suction pipe installation space G1 between the cooling fan (PAN) and the linear compressor 100 can be reduced. Furthermore, only a minimum space for cooling is formed between the linear compressor 100 and the cooling fan (PAN), and the suction pipe installation space (G1) may not be required.

In this way, the space efficiency of the refrigerator machine room can be increased through the linear compressor 100 according to an embodiment of the present specification. Additionally, by reducing the distance between the linear compressor 100 and the cooling fan (PAN), cooling efficiency by the cooling fan (PAN) can be increased.

Without being limited to this, the outer portion of the casing 110 of the suction pipe 114 may be formed in various shapes depending on the structure of the refrigerator machine room or the location where the refrigerant pipe entering the machine room enters.

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

For example, this means that configuration A described in a particular embodiment and/or drawing may be combined with configuration B described in other embodiments and/or drawings. In other words, even if the combination between components is not directly explained, it means that combination is possible, except in cases where it is explained that combination is impossible.

The above detailed description should not be construed as restrictive in any respect and should be considered 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.

100: linear compressor 101: accommodation space
102: Suction space 103: Compression space
104: discharge space 105: first flow path
106: Second flow path 107: First noise space
108: second noise space 110: casing
111: shell 112: first shell cover
113: second shell cover 114: suction pipe
115: discharge pipe 115a: loop pipe
116: rear elastic member 116a: elastic portion
116b: first connection 116c: second connection
116d: fourth fixing hole 117: front elastic member
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
119b: second coupling portion 119c: support portion
119d: third coupling portion 119e: fourth coupling portion
120: frame 121: body part
122: first flange portion 123: back cover
123a: back plate part 123b: bridge part
123c: first opening 123d: third coupling hole
130: Drive unit 131: Outer stator
132: coil winding body, 132a: bobbin
132b: coil 133: stator core
134: Inner stator 135: Mover
136: Magnet frame 136a: First coupling portion
137: stator cover 140: cylinder
141: second flange portion 142: gas inlet
150: Piston 151: Head part
152: Guide portion 153: Third flange portion
154: suction port 155: suction valve
160: first muffler unit 161: internal guide
162: first intake muffler 163: first extension
170: Discharge valve assembly 171: Discharge valve
172: valve spring 180: discharge cover assembly
181: first discharge cover 182: second discharge cover
183: Third discharge cover 190: Second muffler unit
191: second intake muffler 192: second extension part
192a: vertical part 192b: horizontal part
193: second opening 194: connection auxiliary part
195: nozzle part 1961: first fixing part
1961a: first fixing hole 1962: second fixing part
1962a: second fixing hole 1971: first fixing member
1972: Second fixing member

Claims (20)

cylinder;
A piston that reciprocates in the axial direction within the cylinder;
a first muffler unit coupled to the piston;
a back cover including a first opening formed in a radial central area and disposed behind the piston; and
It includes a second muffler unit coupled to the rear of the back cover,
The first muffler unit includes a first suction muffler disposed behind the piston, and a first extension portion disposed behind the first suction muffler and penetrating the first opening,
The second muffler unit is a linear compressor including a second suction muffler in communication with the first extension portion, and a second extension portion disposed on a radial outer side of the second suction muffler and in communication with the second suction muffler. According to paragraph 1,
A second noise space is formed between the second intake muffler and the rear of the back cover,
A linear compressor in which the rear end of the first extension reciprocates in the axial direction within the second noise space. According to paragraph 2,
The second extension portion is in close contact with the back cover,
A linear compressor in which a second flow path communicating with the second noise space is formed between the back cover and the second extension part. According to paragraph 1,
The second muffler unit includes a second opening formed in the second extension part,
A linear compressor wherein the second opening overlaps the first muffler unit in a radial direction. According to paragraph 1,
The second extension part is a linear compressor including a vertical part that communicates with the second suction muffler and extends radially outward, and a horizontal part that communicates with the vertical part and extends forward. According to clause 4,
The second opening is a linear compressor disposed ahead of the second suction muffler. According to paragraph 1,
A linear compressor wherein the inner peripheral surface of the first opening is adjacent to the outer peripheral surface of the first extension portion. According to paragraph 1,
A linear compressor wherein the radial length of the inner surface of the second suction muffler is greater than the inner diameter of the first extension part. According to paragraph 1,
A linear compressor wherein the cross-sectional area of the second suction muffler is larger than the cross-sectional area of the second extension portion. According to paragraph 1,
A casing that accommodates the cylinder;
a rear elastic member with one end connected to the casing and the other end connected to the back cover; and
Includes a fixing member for fixing the second muffler unit to the back cover,
The second muffler unit includes a fixing portion extending outward from the second intake muffler,
The fixing member penetrates the fixing part and is coupled to the back cover,
The other end of the rear elastic member is a linear compressor disposed between the fixing part and the back cover. According to paragraph 1,
A casing that accommodates the cylinder; and
A linear compressor including a suction pipe that radially penetrates the casing and supplies refrigerant to the second muffler unit. According to clause 11,
The second muffler unit includes a second opening formed in the second extension part,
A linear compressor wherein one end of the suction pipe faces the second opening. According to clause 12,
A nozzle portion disposed between the second opening and the suction pipe,
A linear compressor in which the radially inner radius of the nozzle portion is smaller than the radially outer radius of the nozzle portion. According to clause 13,
The second muffler unit includes a connection auxiliary portion protruding outward from the second opening,
A linear compressor in which one side of the nozzle part is press-fitted to the connection auxiliary part. According to clause 13,
A linear compressor wherein the inner diameter of the radial outer side of the nozzle portion is larger than the outer diameter of the suction pipe. delete delete delete delete delete