KR101990138B1 - Linear compressor and refrigerator including the same - Google Patents

Abstract

The present invention relates to a linear compressor and a refrigerator including the same. According to an embodiment of the present invention, the linear compressor comprises: a shell to which a suction pipe is coupled; a cylinder disposed in the shell and forming a compression space; a piston disposed to reciprocate in the cylinder so that refrigerant in the compression space can be compressed; and a muffler allowing the refrigerant sucked through the suction pipe to flow to be provided to the compression space. The muffler includes a plurality of flow pipes extending in the flow direction of the refrigerant and a plurality of through holes penetrated to be formed on at least one of the flow pipes.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a linear compressor,

The present invention relates to a linear compressor and a refrigerator including the same.

Generally, a refrigerator is a household appliance that allows food to be stored at a low temperature in an internal storage room that is shielded by a door. The refrigerator is provided with a cooling system, and the inside of the storage compartment is maintained at a temperature lower than the external temperature.

The cooling system is a system for generating cool air by circulating a coolant, and performs compression, condensation, expansion and evaporation of the coolant repeatedly. To this end, the cooling system includes a compressor, a condenser, an expansion device and an evaporator.

Generally, a compressor is a mechanical device that receives power from a power generating device such as an electric motor or a turbine to increase pressure by compressing air, refrigerant, or various other working fluids. In addition to the household appliance such as the refrigerator, It is widely used throughout.

The compressor is divided into a reciprocating compressor, a rotary compressor, and a scroll compressor according to a compression method of a working fluid.

Specifically, the reciprocating compressor includes a cylinder and a piston provided in the cylinder so as to be capable of reciprocating linearly. A compression space is formed between the piston head and the cylinder, and the compression space is increased or decreased by the linear reciprocating motion of the piston, so that the working fluid in the compression space is compressed to a high temperature and a high pressure.

Further, the rotary compressor includes a cylinder and a roller eccentrically rotating in the cylinder. The roller is eccentrically rotated in the cylinder to compress the working fluid supplied to the compression space to high temperature and high pressure.

Further, the scroll compressor includes a fixed scroll and a orbiting scroll that rotates around the fixed scroll. The orbiting scroll rotates and compresses the working fluid supplied to the compression space to a high temperature and a high pressure.

Recently, among the reciprocating compressors, there has been actively developed a linear compressor in which a piston is directly connected to a linear motor reciprocating linearly.

The linear compressor is provided with a linear motor for linearly reciprocating the piston. The linear motor is configured such that a permanent magnet is positioned between an inner stator and an outer stator, and the permanent magnet is driven to linearly reciprocate by the mutual electromagnetic force between the permanent magnet and the inner (or outer) stator. As the permanent magnet is driven with the piston connected thereto, the piston can reciprocate.

The piston reciprocates linearly in the cylinder inside the sealed shell to suck and compress the refrigerant. More specifically, the piston moves from the top dead center to the bottom dead center, the refrigerant is received in the compression chamber, the piston moves from the bottom dead center to the top dead center, and the refrigerant contained in the compression chamber is compressed. At this time, the higher the pressure of the suction gas flowing into the piston, the faster the suction valve opens and the more refrigerant can be accommodated in the compression chamber.

Regarding a linear compressor having such a structure, the present applicant has been registered by applying a patent application (hereinafter referred to as Prior Art 1).

<Prior Art 1>

1. Registration No .: 10-0579578 (Registration date: May 8, 2006)

2. Description of the invention: muffler of linear compressor

The prior art document 1 discloses a muffler disposed inside the piston. The muffler serves as noise reduction due to refrigerant flow and as a path through which the refrigerant sucked into the compressor moves to the piston.

According to the shape of the muffler described in the above-mentioned prior art 1, the pressure of the suction gas flowing to the piston along the muffler is relatively low. When the pressure of the suction gas is lowered, there is a problem that the refrigerant is received in the compression chamber or the refrigerant flows back to the piston in the compression chamber.

Particularly, when the speed of the piston is increased to increase the cooling capacity of the compressor, there is a mismatch between the time when the suction valve is opened and the time when the pressure of the gas is increased, or the pressure of the suction gas is small, so that less refrigerant is accommodated in the compression chamber, have. thereafter. The efficiency of the compressor is reduced.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a linear compressor having a muffler provided to increase the pressure of a refrigerant provided in a compression chamber, and a refrigerator including the same.

In particular, it is an object of the present invention to provide a linear compressor equipped with a muffler which can be changed into various shapes by changing the shape of a plurality of components included in the muffler, and a refrigerator including the same.

Another object of the present invention is to provide a linear compressor in which a greater amount of refrigerant is accommodated in a compression chamber as the pressure of the suction refrigerant increases, thereby increasing the cooling power and efficiency, and a refrigerator including the same.

A linear compressor according to an aspect of the present invention includes a shell to which a suction pipe is coupled, a cylinder disposed inside the shell to form a compression space, and a compression mechanism configured to reciprocate inside the cylinder to compress the refrigerant in the compression space And a muffler for flowing the refrigerant sucked through the suction pipe into the compression space, wherein the muffler includes a plurality of flow pipes extending in the flow direction of the coolant and at least one of the plurality of flow pipes A plurality of through holes are formed.

At this time, the plurality of through holes may be formed to have different sizes. In addition, the plurality of through holes may be formed along the periphery of the flow pipe.

In one embodiment of the present invention, the muffler includes a first muffler, a second muffler coupled to the rear side of the first muffler, a third muffler accommodating the second muffler inside and coupled to the rear side of the piston, And a perforated pipe disposed between the first muffler and the second muffler and having the plurality of through holes.

At this time, one end of the porous tube may be coupled to the first muffler, and the other end may be coupled to the second muffler.

The first muffler includes a first flow tube, a first coupling portion extending radially outwardly from the first flow tube, and a first suction portion extending rearward from the first coupling portion, and the second muffler includes A second flow tube, and a second coupling portion extending radially outwardly and forwardly from the second flow tube and contacting the first suction portion. The pores may be disposed radially inward of the first and second engagement portions. In other words, the perforated pipe may be disposed in a space formed by the first engagement portion, the first suction portion, and the second engagement portion.

The flow tube may include a first flow tube, a second flow tube disposed apart from the first flow tube, and a porous tube connecting the first flow tube and the second flow tube, wherein the plurality of through holes are formed. The perforated pipe may be formed to be thinner than the first flow tube and the second flow tube.

In another embodiment of the present invention, the muffler includes a first muffler, a second muffler coupled to a rear side of the first muffler, the second muffler having the plurality of through holes formed therein, and the second muffler, And a third muffler coupled to the rear side.

The flow tube may include a first flow tube provided in the first muffler and a second flow tube provided in the second muffler and connected to the first flow tube. At this time, the plurality of through holes may be formed in the second flow tube. The first flow tube may be disposed inside the piston, and the second flow tube may be disposed outside the piston to contact one end of the first flow tube.

According to the present invention, since the pressure of the refrigerant provided in the compression chamber is higher than that of the conventional refrigerant, more refrigerant is received and compressed in the compression chamber, thereby increasing the cooling power and efficiency of the compressor.

Further, even when the speed of the piston is increased to increase the cooling power of the compressor, the pressure of the suction refrigerant can be secured, thereby improving the responsiveness of the suction valve and ensuring a sufficient amount of refrigerant in the compression chamber.

In particular, there is an advantage that the pressure of the suction refrigerant can be easily secured by changing the shape of the muffler through which the suction refrigerant flows.

Further, it is possible to provide a muffler which can be changed into various shapes by changing the shapes of various configurations included in the muffler to secure the pressure of the suction refrigerant.

In addition, by reducing the size of the compressor including the internal components, the size of the machine room of the refrigerator can be reduced, thereby increasing the internal storage space of the refrigerator.

1 is a view illustrating a refrigerator according to an embodiment of the present invention.
2 is a view showing the appearance of a compressor according to an embodiment of the present invention.
3 is an exploded view of a shell and a shell cover of a compressor according to an embodiment of the present invention.
4 is an exploded perspective view of a compressor according to an embodiment of the present invention.
5 is a cross-sectional view taken along line V-V 'of FIG.
6 is a view showing a piston and a muffler of a compressor according to a first embodiment of the present invention.
FIG. 7 is an exploded view of a piston and a muffler of a compressor according to a first embodiment of the present invention. FIG.
8 is a cross-sectional view of a piston and a muffler of a compressor according to a first embodiment of the present invention.
9 is a cross-sectional view of a piston and a muffler of a compressor according to a second embodiment of the present invention.
10 is an exploded view of a muffler of a compressor according to a third embodiment of the present invention.
11 is a cross-sectional view of a piston and a muffler of a compressor according to a third embodiment of the present invention.
12 is an exploded view of a muffler of a compressor according to a fourth embodiment of the present invention.
13 is a cross-sectional view of a piston and a muffler of a compressor according to a fourth embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that, in adding reference numerals to the constituent elements of the drawings, the same constituent elements are denoted by the same reference symbols as possible even if they are shown in different drawings. In the following description of the embodiments of the present invention, a detailed description of known functions and configurations incorporated herein will be omitted when it may make the difference that the embodiments of the present invention are not conclusive.

In describing the components of the embodiment of the present invention, terms such as first, second, A, B, (a), and (b) may be used. These terms are intended to distinguish the constituent elements from other constituent elements, and the terms do not limit the nature, order or order of the constituent elements. When a component is described as being "connected", "coupled", or "connected" to another component, the component may be directly connected or connected to the other component, Quot; may be "connected," "coupled," or "connected. &Quot;

1 is a view illustrating a refrigerator according to an embodiment of the present invention.

1, a refrigerator 1 according to an embodiment of the present invention includes a cabinet 2 forming an outer appearance and at least one refrigerator door 3 coupled to the cabinet 2. As shown in FIG.

At least one storage chamber (4) is provided in the cabinet (2). The refrigerator door 3 may be rotatably or slidably connected to the front surface of the cabinet 2 to open or close the storage compartment 4. At this time, the storage chamber 4 may include at least one of a refrigerating chamber and a freezing chamber, and each chamber may be partitioned by a partition wall.

In addition, a machine room 5 in which the compressor 10 is disposed is provided in the cabinet 2. As shown in FIG. 1, the machine room 5 may be disposed at a lower rear portion of the cabinet 2.

At this time, the performance and efficiency of the refrigerator (1) can be determined according to the performance and efficiency of the compressor (10). That is, when the performance and efficiency of the compressor 10 are good, a necessary amount of cool air can be supplied to the storage chamber 4 with less power.

Hereinafter, the compressor 10 according to the present invention with improved performance and efficiency will be described in detail.

FIG. 2 is a view showing an appearance of a compressor according to an embodiment of the present invention, and FIG. 3 is an exploded view of a shell and a shell cover of a compressor according to an embodiment of the present invention.

2 and 3, a compressor 10 according to the teachings of the present invention includes a shell 101 and shell covers 102 and 103 coupled to the shell 101. In a broad sense, the shell covers 102 and 103 can be understood as one configuration of the shell 101. [

On the lower side of the shell 101, the legs 50 can be engaged. The legs 50 may be coupled to the base of the product on which the compressor 10 is installed. That is, the legs 50 may be coupled to the machine room 5 of the refrigerator 1 described above.

The shell 101 has a substantially cylindrical shape and can be arranged in a lateral direction or in an axial direction. 2, the shell 101 may be elongated in the transverse direction and may have a somewhat lower height in the radial direction.

That is, since the compressor 10 can have a low height, when the compressor 10 is installed in the machine room 5 of the refrigerator 1, the height of the machine room 5 can be reduced . Thereby, the volume of the storage chamber 4 in the cabinet 2 of the same volume can be increased.

A terminal 108 may be provided on the outer surface of the shell 101. The terminal 108 is understood as a configuration for transmitting external power to the motor assembly 140 (see Fig. 4) of the linear compressor. In particular, the terminal 108 may be connected to the lead of the coil 141c (see FIG. 4).

On the outside of the terminal 108, a bracket 109 is provided. The bracket 109 may include a plurality of brackets surrounding the terminal 108. The bracket 109 may function to protect the terminal 108 from an external impact or the like.

Both sides of the shell 101 are configured to be open. On both sides of the opened shell 101, the shell covers 102 and 103 can be coupled. More specifically, the shell covers 102 and 103 are provided with a first shell cover 102 coupled to one side of the shell 101 that is open and a second shell cover 102 coupled to the other side of the shell 101, And a shell cover 103 is included. By the shell covers 102 and 103, the inner space of the shell 101 can be sealed.

2, the first shell cover 102 may be located on the right side of the compressor 10 and the second shell cover 103 may be located on the left side of the compressor 10. In other words, the first and second shell covers 102 and 103 may be arranged to face each other.

The compressor 10 further includes a plurality of pipes 104, 105, and 106 which are provided in the shell 101 or the shell covers 102 and 103 and capable of sucking, discharging or injecting refrigerant.

The plurality of pipes 104, 105 and 106 are provided with a suction pipe 104 for allowing the refrigerant to be sucked into the compressor 10 and a discharge pipe 105 for discharging the compressed refrigerant from the compressor 10 And a process pipe 106 for replenishing the compressor 10 with refrigerant.

For example, the suction pipe 104 may be coupled to the first shell cover 102. The refrigerant can be sucked into the compressor (10) along the axial direction through the suction pipe (104).

The discharge pipe 105 may be coupled to the outer circumferential surface of the shell 101. The refrigerant sucked through the suction pipe 104 can be compressed while flowing in the axial direction. The compressed refrigerant can be discharged through the discharge pipe 105. The discharge pipe 105 may be disposed at a position adjacent to the second shell cover 103 than the first shell cover 102.

The process pipe 106 may be coupled to the outer circumferential surface of the shell 101. The operator can inject the refrigerant into the compressor 10 through the process pipe 106.

The process pipe 106 may be coupled to the shell 101 at a different height than the discharge pipe 105 to avoid interference with the discharge pipe 105. The height is understood as a distance in a vertical direction (or a radial direction) from the legs 50. The discharge pipe (105) and the process pipe (106) are coupled to the outer circumferential surface of the shell (101) at different heights.

At least a portion of the second shell cover 103 may be positioned adjacent to the inner circumferential surface of the shell 101, corresponding to the point where the process pipe 106 is coupled. In other words, at least a portion of the second shell cover 103 may act as a resistance of the refrigerant injected through the process pipe 106.

Therefore, from the viewpoint of the flow path of the refrigerant, the flow path size of the refrigerant flowing through the process pipe 106 is reduced by the second shell cover 103 while entering the inner space of the shell 101, And is formed to be larger again. In this process, the pressure of the refrigerant can be reduced to vaporize the refrigerant, and in this process, the oil contained in the refrigerant can be separated. Accordingly, the refrigerant compression performance can be improved while refrigerant from which oil has been separated flows into the interior of the piston 130 (see Fig. 4). The oil fraction can be understood as operating oil present in the cooling system.

On the inner surface of the first shell cover 102, a cover supporting portion 102a is provided. A second supporting device 185, which will be described later, may be coupled to the cover supporting portion 102a. The cover support portion 102a and the second support device 185 can be understood as devices for supporting the main body of the compressor 10. [ Here, the main body of the compressor refers to a part provided inside the shell 101, and may include, for example, a driving part moving forward and backward and a supporting part supporting the driving part.

The drive unit may include components such as a piston 130, a magnet frame 138, a permanent magnet 146, a supporter 137, and a muffler 200, which will be described later. The support portion may include components such as resonance springs 176a and 176b, a rear cover 170, a stator cover 149, a first support device 165, and a second support device 185, which will be described later .

A stopper 102b may be provided on the inner surface of the first shell cover 102. [ The stopper 102b is understood to be a structure for preventing the main body of the compressor, particularly the motor assembly 140, from being damaged by collision with the shell 101 due to vibration or impact generated during transportation of the compressor 10 . The stopper 102b is positioned adjacent to a rear cover 170 to be described later so that when the compressor 10 vibrates, the rear cover 170 interferes with the stopper 102b, It is possible to prevent the shock from being transmitted to the first arm 140.

The inner circumferential surface of the shell 101 may be provided with a spring coupling portion 101a. For example, the spring coupling portion 101a may be disposed at a position adjacent to the second shell cover 103. [ The spring coupling portion 101a may be coupled to a first support spring 166 of a first support device 165, which will be described later. The main body of the compressor can be stably supported on the inner side of the shell 101 by the engagement of the spring coupling portion 101a and the first support device 165. [

FIG. 4 is an exploded view of a compressor according to an embodiment of the present invention, and FIG. 5 is a cross-sectional view taken along line V-V 'of FIG.

4 and 5, a compressor 10 according to an embodiment of the present invention includes a cylinder 120 provided inside the shell 101 and a cylinder 120 provided inside the cylinder 120, And a motor assembly 140 as a linear motor that applies a driving force to the piston 130 and the piston 130. When the motor assembly 140 is driven, the piston 130 can reciprocate in the axial direction.

The compressor 10 further includes a muffler 200 connected to the piston 130 for reducing noise generated from the refrigerant sucked through the suction pipe 104. The refrigerant sucked through the suction pipe 104 flows into the piston 130 through the muffler 200.

For example, in the course of the refrigerant passing through the muffler 200, the flow noise of the refrigerant can be reduced. In addition, the muffler 200 may be provided in various shapes to adjust the pressure of the refrigerant passing through the muffler 200. Various shapes of such a muffler will be described in detail later.

Hereinafter, the directions are defined for convenience of explanation.

The term "axial direction" can be understood as a direction in which the piston 130 reciprocates, that is, a lateral direction in FIG. Of these "axial directions", the direction from the suction pipe 104 toward the compression space P, that is, the direction in which the refrigerant flows is referred to as "forward" and the opposite direction is defined as "rearward". For example, when the piston 130 moves forward, the compression space P can be compressed.

On the other hand, the term "radial direction" can be understood as the vertical direction of Fig. 5, which is a direction perpendicular to the direction in which the piston 130 reciprocates.

The piston 130 includes a substantially cylindrical piston body 131 and a piston flange 132 extending radially from the piston body 131. The piston body 131 reciprocates within the cylinder 120 and the piston flange 132 can reciprocate outside the cylinder 120.

The cylinder (120) is configured to receive at least a portion of the muffler (150) and at least a portion of the piston body (131).

A compression space P in which the refrigerant is compressed by the piston 130 is formed in the cylinder 120. A suction hole 133 for introducing the refrigerant into the compression space P is formed in a front portion of the piston main body 131. The suction hole 133 is opened and closed in front of the suction hole 133, A suction valve 135 is provided.

In addition, the compressor includes a discharge cover 160 and discharge valve assemblies 161 and 163. The discharge cover 160 is disposed in front of the compression space P to form a discharge space 160a for the refrigerant discharged from the compression space P. [ The discharge space 160a includes a plurality of spaces defined by inner walls of the discharge cover 160. The plurality of space portions are arranged in the front-rear direction and can communicate with each other.

The discharge valve assemblies 161 and 163 are coupled to the discharge cover 160 and selectively discharge the refrigerant compressed in the compression space P. The discharge valve assembly 161 or 163 is provided with a discharge valve 161 that opens when the pressure in the compression space P becomes equal to or higher than the discharge pressure and causes the refrigerant to flow into the discharge space 160a, And a spring assembly 163 provided between the discharge cover 160 and the discharge cover 160 to provide an elastic force in the axial direction.

The spring assembly 163 includes a valve spring 163a and a spring support portion 163b for supporting the valve spring 163a on the discharge cover 160. [ For example, the valve spring 163a may include a leaf spring. The spring support portion 163b may be integrally injection-molded into the valve spring 163a by an injection process.

The discharge valve 161 is coupled to the valve spring 163a and a rear portion or a rear surface of the discharge valve 161 is positioned to be capable of supporting the front surface of the cylinder 120. [ When the discharge valve 161 is supported on the front surface of the cylinder 120, the compression space P is maintained in a closed state. When the discharge valve 161 is separated from the front surface of the cylinder 120, The space P is opened so that the compressed refrigerant in the compression space P can be discharged.

That is, the compression space P is understood as a space formed between the suction valve 135 and the discharge valve 161. The suction valve 135 is formed on one side of the compression space P and the discharge valve 161 is disposed on the other side of the compression space P, that is, on the opposite side of the suction valve 135 Can be provided.

When the pressure in the compression space P becomes equal to or lower than the suction pressure in the reciprocating linear motion of the piston 130 in the cylinder 120, the suction valve 135 is opened, P). On the other hand, when the pressure in the compression space P becomes equal to or higher than the suction pressure, the refrigerant in the compression space P is compressed while the suction valve 135 is closed.

On the other hand, when the pressure in the compression space P becomes equal to or higher than the discharge pressure, the valve spring 163a is deformed forward to open the discharge valve 161, and the refrigerant is discharged from the compression space P , And is discharged to the discharge space of the discharge cover (160). When the discharge of the refrigerant is completed, the valve spring 163a provides a restoring force to the discharge valve 161 so that the discharge valve 161 is closed.

A cover pipe 162a is coupled to the discharge cover 160 to discharge the refrigerant flowing through the discharge space 160a of the discharge cover 160. [ For example, the cover pipe 162a may be made of a metal material.

A loop pipe 162b is further coupled to the cover pipe 162a to transmit the refrigerant flowing through the cover pipe 162a to the discharge pipe 105. [ One side of the loop pipe 162b may be coupled to the cover pipe 162a and the other side may be coupled to the discharge pipe 105. [

The loop pipe 162b is made of a flexible material and can be relatively long. The loop pipe 162b may extend from the cover pipe 162a along the inner circumferential surface of the shell 101 and may be coupled to the discharge pipe 105. [ For example, the loop pipe 162b may have a coiled shape.

The compressor (10) further includes a frame (110). The frame 110 is understood as a structure for fixing the cylinder 120. For example, the cylinder 120 may be press-fitted into the inside of the frame 110. The cylinder 120 and the frame 110 may be made of aluminum or an aluminum alloy.

The frame 110 is disposed to surround the cylinder 120. That is, the cylinder 120 may be positioned to be received inside the frame 110. The discharge cover 160 may be coupled to the front surface of the frame 110 by fastening members.

The motor assembly 140 includes an outer stator 141 fixed to the frame 110 so as to surround the cylinder 120 and an inner stator 148 disposed apart from the inner stator 141 And a permanent magnet 146 positioned in the space between the outer stator 141 and the inner stator 148.

The permanent magnets 146 can reciprocate linearly by mutual electromagnetic forces with the outer stator 141 and the inner stator 148. The permanent magnets 146 may be formed of a single magnet having one pole or a plurality of magnets having three poles.

The permanent magnet 146 may be installed on the magnet frame 138. The magnet frame 138 has a substantially cylindrical shape and may be arranged to be inserted into a space between the outer stator 141 and the inner stator 148.

 5, the magnet frame 138 is coupled to the piston flange 132 and extends in the outer radial direction and can be bent forward. The permanent magnet 146 may be installed at a front portion of the magnet frame 138. Accordingly, when the permanent magnet 146 reciprocates, the piston 130 can reciprocate axially together with the permanent magnet 146.

The outer stator 141 includes coil winding bodies 141b, 141c and 141d and a stator core 141a. The coil windings 141b, 141c and 141d include a bobbin 141b and a coil 141c wound around the bobbin in the circumferential direction. The coil windings 141b, 141c and 141d further include a terminal portion 141d for guiding the power line connected to the coil 141c to be drawn out or exposed to the outside of the outer stator 141. The terminal portion 141d may be arranged to be inserted into a terminal insertion portion provided in the frame 110. [

The stator core 141a includes a plurality of core blocks in which a plurality of laminations are stacked in a circumferential direction. The plurality of core blocks may be disposed so as to surround at least a part of the coil winding body 141b, 141c, and 141d.

A stator cover 149 is provided at one side of the outer stator 141. That is, one side of the outer stator 141 may be supported by the frame 110 and the other side may be supported by the stator cover 149.

The stator cover 149 and the frame 110 are fastened by a cover fastening member 149a. The cover fastening member 149a may extend forward toward the frame 110 through the stator cover 149 and may be coupled to a fastening hole provided in the frame 110. [

The inner stator 148 is fixed to the outer periphery of the frame 110. The inner stator 148 is formed by laminating a plurality of laminations in the circumferential direction from the outside of the frame 110.

The compressor (10) further includes a supporter (137) for supporting the piston (130). The supporter 137 is coupled to the rear side of the piston 130 and the muffler 200 may be disposed inside the supporter 137. The piston flange 132, the magnet frame 138, and the supporter 137 can be fastened by a fastening member.

To the supporter 137, a balance weight 179 may be combined. The weight of the balance weight 179 can be determined based on the operating frequency range of the compressor main body.

The compressor 10 further includes a rear cover 170 coupled to the stator cover 149 and extending rearwardly and supported by a second support device 185.

In detail, the rear cover 170 includes three support legs, and the three support legs can be coupled to the rear surface of the stator cover 149. [ A spacer 181 may be interposed between the three support legs and the rear surface of the stator cover 149. The distance from the stator cover 149 to the rear end of the rear cover 170 can be determined by adjusting the thickness of the spacer 181. The rear cover 170 may be spring-supported to the supporter 137.

The compressor 10 further includes an inlet guide unit 156 coupled to the rear cover 170 to guide refrigerant into the muffler 200. At least a portion of the inflow guide portion 156 may be inserted into the muffler 200.

The compressor (10) further includes a plurality of resonance springs (176a, 176b) whose natural frequencies are adjusted so that the piston (130) can resonate.

The plurality of resonance springs 176a and 176b are provided with a first resonance spring 176a supported between the supporter 137 and the stator cover 149 and a second resonance spring 176b between the supporter 137 and the rear cover 170 And a second resonance spring 176b supported. By the action of the plurality of resonance springs 176a and 176b, stable movement of the reciprocating drive unit is performed within the compressor 10, and vibration or noise generated by the movement of the drive unit can be reduced.

The supporter 137 includes a first spring support portion 137a coupled to the first resonance spring 176a.

The compressor 10 includes a plurality of sealing members 127, 128, 129a, and 129b for increasing a coupling force between the frame 110 and components around the frame 110. [

Specifically, the plurality of sealing members 127, 128, 129a, and 129b includes a first sealing member 127 provided at a portion where the frame 110 and the discharge cover 160 are coupled. The first sealing member 127 may be disposed in the first mounting groove of the frame 110.

The plurality of sealing members 127, 128, 129a and 129b may further include a second sealing member 128 provided at a portion where the frame 110 and the cylinder 120 are coupled. The second sealing member 128 may be disposed in the second mounting groove of the frame 110.

The plurality of sealing members 127, 128, 129a and 129b further include a third sealing member 129a provided between the cylinder 120 and the frame 110. [ The third sealing member 129a may be disposed in a cylinder groove formed in a rear portion of the cylinder 120. [ The third sealing member 129a prevents the refrigerant in the gas pocket formed between the inner circumferential surface of the frame and the outer circumferential surface of the cylinder from leaking out and functions to increase the coupling force between the frame 110 and the cylinder 120 Can be performed.

The plurality of sealing members 127, 128, 129a and 129b may further include a fourth sealing member 129b provided at a portion where the frame 110 and the inner stator 148 are coupled. The fourth sealing member 129b may be disposed in the third installation groove of the frame 110. [ The first to fourth sealing members 127, 128, 129a, and 129b may have a ring shape.

The compressor 10 further includes a first support device 165 coupled to the discharge cover 160 and supporting one side of the main body of the compressor 10. The first support device 165 may be disposed adjacent to the second shell cover 103 to elastically support the main body of the compressor 10. In detail, the first support device 165 includes a first support spring 166. [ The first support spring 166 may be coupled to the spring coupling portion 101a described with reference to FIG.

The compressor 10 further includes a second support device 185 coupled to the rear cover 170 to support the other side of the main body of the compressor 10. [ The second support device 185 may be coupled to the first shell cover 102 to elastically support the main body of the compressor 10. Specifically, the second support device 185 includes a second support spring 186. The second support spring 186 may be coupled to the cover support portion 102a described with reference to FIG.

The cylinder 120 includes a cylinder body 121 extending in the axial direction and a cylinder flange 122 provided outside the front portion of the cylinder body 121. The cylinder body 121 has a cylindrical shape having a central axis in the axial direction, and is inserted into the frame 110. Therefore, the outer circumferential surface of the cylinder body 121 may be positioned to face the inner circumferential surface of the frame 110.

The cylinder body 121 is formed with a gas inlet 126 through which at least a portion of the refrigerant discharged through the discharge valve 161 flows. The at least a part of the refrigerant is understood as a refrigerant used as a gas bearing between the piston 130 and the cylinder 120. [

5, the refrigerant used as the gas bearing passes through the gas holes 114 formed in the frame 110, and flows between the inner peripheral surface of the frame 110 and the outer peripheral surface of the cylinder 120 Flows into the formed gas pocket. The refrigerant in the gas pocket may flow to the gas inlet 126.

In detail, the gas inlet 126 may be configured to be recessed radially inward from the outer circumferential surface of the cylinder body 121. The gas inlet 126 may have a circular shape along an outer circumferential surface of the cylinder body 121 with respect to an axially central axis. A plurality of gas inflow portions 126 may be provided. For example, two gas inflow portions 126 may be provided.

The cylinder body 121 includes a cylinder nozzle 125 extending radially inwardly from the gas inlet 126. The cylinder nozzle 125 may extend to the inner circumferential surface of the cylinder body 121.

The refrigerant having passed through the gas inlet 126 flows into the space between the inner circumferential surface of the cylinder body 121 and the outer circumferential surface of the piston body 131 through the cylinder nozzle 125. This refrigerant provides a levitation force to the piston 130 to perform the function of a gas bearing for the piston 130.

FIG. 6 is a view showing a piston and a muffler of a compressor according to a first embodiment of the present invention, and FIG. 7 is an exploded view of a piston and a muffler of the compressor according to the first embodiment of the present invention.

6 and 7, the linear compressor according to the present invention includes a piston 130 having a suction hole 133 for sucking the refrigerant into the compression space P, and a piston 130 having the suction hole 133 And a suction valve 135 disposed on one side of the piston 130 for opening and closing. The valve 130 may further include a valve coupling member 134 coupled to the piston 130 to couple the suction valve 135 to the piston 130.

Further, the piston 130 is formed with a fastening hole 136 to which the valve fastening member 134 is coupled. At this time, the valve engaging member 134 is coupled to the fastening hole 136 through the suction valve 135. Accordingly, the suction valve 135 is fixed to the piston 130 at the center side by the valve engaging member 134.

Further, the edge of the suction valve 135 is bent forward, and the suction hole 133 can be opened. Further, the edge of the suction valve 135 may be returned to the rear side and the suction hole 133 may be closed.

The movement of the suction valve 135 is determined by the pressure. That is, the suction hole 133 is opened when the pressure at the rear end of the suction valve 135 is higher than the front end of the suction valve 135, and the suction hole 133 is closed when the pressure at the front end is higher than the rear end of the suction valve 135. At this time, when the suction valve 135 moves forward more quickly, a larger amount of refrigerant can be flowed into the compression space P through the suction hole 133.

That is, when the pressure of the refrigerant received in the rear end of the suction valve 135, that is, the inside of the piston 130 is high, a larger amount of refrigerant can flow through the suction hole 133. The pressure of the refrigerant may be adjusted by the muffler 200 accommodated in the piston 130.

As shown in FIGS. 6 and 7, the linear compressor according to the present invention includes a muffler 200 having a plurality of structures coupled to each other. In this case, the plurality of configurations are divided into a first muffler 210, a second muffler 220, and a third muffler 230 in order in FIG. 7 for convenience of explanation.

The first muffler 210 is positioned inside the piston 130 and the second muffler 220 is coupled to the rear side of the first muffler 210. The third muffler 230 accommodates the second muffler 220 and may extend to the rear of the first muffler 210.

A muffler filter (not shown) may be disposed at an interface between the first muffler 210 and the second muffler 220. For example, the muffler filter may have a circular shape, and an outer circumferential portion of the muffler filter may be supported between the first and second mufflers 210 and 220.

The refrigerant sucked through the suction pipe 104 can pass through the third muffler 230, the second muffler 220, and the first muffler 210 in this order from the viewpoint of the flow direction of the refrigerant. In this process, the flow noise of the refrigerant is reduced and the pressure can be raised.

At this time, the muffler 200 has at least one variable portion that changes the flow cross sectional area of the refrigerant. Specifically, it has a variable portion in which the flow cross-sectional area gradually widens in the flow direction of the refrigerant.

That is, the muffler 200 is shaped to increase the pressure of the refrigerant as the refrigerant flow rate is reduced by increasing the cross-sectional area of the refrigerant flowing through the Bernoulli's equation. Accordingly, the pressure of the refrigerant becomes higher, the suction valve 135 is bent more quickly, and a larger amount of refrigerant can flow into the suction hole 133.

Further, the muffler 200 according to the present invention has a plurality of variable portions. That is, the muffler 200 may be provided with a plurality of variable portions having a gradually increasing cross-sectional area. Hereinafter, an exemplary shape of the muffler 200 of the present invention will be described with reference to the drawings.

8 is a cross-sectional view of a piston and a muffler of a compressor according to a first embodiment of the present invention. The piston of Fig. 8 is simply shown for the sake of understanding.

As shown in Fig. 8, the muffler according to the first embodiment of the present invention is provided with a plurality of variable portions. At this time, the plurality of variable portions may be formed in a plurality of mufflers constituting the muffler 200, respectively.

8, the first muffler 210 includes a first flow pipe 212 through which refrigerant flows, a first coupling portion 214 that is seated on the piston 130, A first suction portion 216 is provided.

The first flow tube 212 is provided as a circular tube that extends in the flow direction of the refrigerant. One end of the first flow tube 212 adjacent to the second muffler 220 is connected to the inlet of the first flow tube 212 adjacent to the front end of the piston 130, The other end is called the exit.

At this time, the inlet diameter d2 and the outlet diameter d1 of the first flow tube 212 are different from each other. Particularly, the diameter d2 of the inlet portion of the first flow tube 212 is smaller than the diameter d1 of the outlet portion. Accordingly, the first flow tube 212 has a variable portion that extends from the inlet portion to the outlet portion. The outer side and the inner side of the first flow tube 212 have an inclined structure extending from the inlet portion to the outlet portion.

The first coupling portion 214 may extend radially beyond the inner diameter of the piston 130 at the outer side of the first flow tube 212 and may be seated at one end of the piston 130. That is, the first coupling portion 214 is formed at a position corresponding to one end of the piston 130. At this time, a predetermined groove corresponding to the first coupling portion 214 may be provided at one end of the piston 130.

Therefore, the front of the first flow tube 212 including the outlet portion may be disposed inside the piston 130 with respect to the first coupling portion 214. In addition, the diameter d1 of the outlet of the first flow tube 212 is smaller than the inner diameter of the piston 130.

The first suction portion 216 may extend further rearward than the first flow pipe 212 at the first engagement portion 214 and may contact one end of the second muffler 220. At this time, the first suction portion 216 may extend further rearward than the piston 130. The third muffler 230 is disposed outside the first suction portion 216.

8, the second muffler 220 includes a second flow pipe 222 through which refrigerant flows, a second coupling portion 224 extending from the second flow pipe 222 to one side, A suction portion 226 is provided.

The second flow pipe 222 is provided as a circular pipe extending in the flow direction of the refrigerant. Hereinafter, one end of the second flow pipe 222 adjacent to the first muffler 210 is referred to as an outlet portion and the other end thereof is referred to as an inlet portion, based on the flow direction of the refrigerant.

At this time, the inlet diameter d4 and the outlet diameter d3 of the second flow tube 222 are different from each other. Particularly, the diameter d4 of the inlet portion of the second flow tube 222 is smaller than the diameter d3 of the outlet portion. Accordingly, the second flow tube 222 has a variable portion extending from the inlet portion to the outlet portion. The outer side and the inner side of the second flow tube 222 have an inclined structure extending from the inlet portion to the outlet portion.

The second engagement portion 224 extends radially and forward from the outside of the second flow pipe 222 and contacts the first suction portion 216 of the first muffler 210. At this time, the second engagement portion 224 extends further forward than the second flow tube 222. That is, one end of the first suction portion 216 and one end of the second engagement portion 224 may be disposed to be in contact with each other, and may have diameters corresponding to each other. In addition, the third muffler 230 is disposed outside the second engagement portion 224.

The second suction portion 226 extends radially and rearward from the second flow pipe 222. That is, the second engaging portion 224 may be positioned in front of the second flow pipe 222, and the second suction portion 226 may be positioned in a rear direction.

Referring to FIG. 8, the third muffler 230 is provided with a third suction portion 236 through which the refrigerant is sucked, and a third coupling portion 234 coupled with the piston 130.

Referring to FIG. 5, at least a part of the inflow guide unit 156 described above may be inserted into the third suction unit 236. Accordingly, the third suction portion 236 may be formed in a shape corresponding to the inflow guide 156.

The third engaging part 234 overlaps with the first engaging part 214 and can be seated on one end of the piston 130. As the piston 130 and the supporter 137 are coupled to each other, the first coupling portion 214 and the third coupling portion 234 may be fixed.

The first flow tube 212 and the second flow tube 222 extend in the flow direction of the suction refrigerant with respect to the same central axis. The second flow pipe 222 is spaced apart from the first flow pipe 212 by a predetermined distance. That is, the inlet of the first flow tube 212 and the outlet of the second flow tube 222 are spaced apart from each other.

The diameter d3 of the outlet of the second flow tube 222 may be smaller than the diameter d2 of the inlet of the first flow tube 212. That is, the inlet diameter d4, the outlet diameter d3, the inlet diameter d2 of the first flow tube 212, and the outlet diameter d1 of the second flow tube 222 are increased (D1 > d2 > d3 > d4)

The refrigerant flowing into the third muffler 230 passes through the second flow pipe 222. In this case, That is, the refrigerant flows from the inlet portion to the outlet portion of the second flow tube 222, and as the diameter increases, the flow rate decreases and the pressure increases.

In addition, the refrigerant flows through the first flow tube 212 and flows to the front end of the piston 130. At this time, the refrigerant flows from the inlet portion to the outlet portion of the second flow tube 212, and as the diameter increases, the flow velocity decreases and the pressure increases.

According to such a variable portion, the refrigerant can flow to the front end of the piston 130 at a higher pressure. As a result, the suction valve 135 is opened earlier and more refrigerant can be introduced into the compression chamber.

In addition, the muffler 200 may be provided in various forms having a plurality of variable portions. Hereinafter, another exemplary shape of the muffler 200 of the present invention will be described with reference to the drawings.

9 is a cross-sectional view of a piston and a muffler of a compressor according to a second embodiment of the present invention. The same contents as those described above are omitted and the above description is referred to.

As shown in Fig. 9, the muffler according to the second embodiment of the present invention is provided with a plurality of variable portions. At this time, the plurality of variable portions may be formed in the first muffler 210a constituting the muffler 200. [

9, the first muffler 210a includes a first flow pipe 212a through which refrigerant flows, a first coupler 214a that is seated on the piston 130a, A first suction portion 216a is provided.

The first flow pipe (212a) is provided as a circular pipe extending in the flow direction of the refrigerant. One end of the first flow tube 212a adjacent to the second muffler 220a is connected to the inlet of the first flow tube 212a adjacent to the front end of the piston 130, The other end is called the exit.

Particularly, the inlet diameter d5 and the outlet diameter d1 of the first flow tube 212a are different from each other. Particularly, the diameter d5 of the inlet of the first flow tube 212a is smaller than the diameter d1 of the outlet. Accordingly, the first flow tube 212a has a plurality of variable portions extending from the inlet portion to the outlet portion as a whole.

At this time, the outer side of the first flow tube 212a is provided as a circular tube having a smooth inclined surface. On the other hand, the inside of the first flow tube 212a has a plurality of stages. For example, as shown in FIG. 9, the case where the inside of the first flow tube 212a is provided in five stages will be described.

Hereinafter, from the output section to the inlet section, it is divided into the first stage to the fifth stage. At this time, the diameter d1 of the first end corresponds to the diameter of the outlet portion, and the diameter d5 of the fifth end corresponds to the diameter of the inlet portion. Therefore, the diameter d1 of the first end is greater than the diameter d5 of the fifth end.

In addition, the diameter may be reduced from the first stage to the fifth stage. That is, the diameter d1 of the first stage> the diameter d2 of the second stage> the diameter d3 of the second stage> the diameter d4 of the fourth stage> the diameter d5 of the fifth stage. Each end may extend a predetermined length in the flow direction of the refrigerant.

8, the second muffler 220a includes a second flow pipe 222a through which the refrigerant flows, a second coupling portion 224a extending from the second flow pipe 222a to one side, A suction portion 226a is provided.

The second flow pipe 222a is a circular pipe extending in the flow direction of the refrigerant. Hereinafter, one end of the second flow pipe 222a adjacent to the first muffler 210a is referred to as an inlet portion and the other end is referred to as an outlet portion, based on the direction of flow of the refrigerant. At this time, the diameters of the inlet and outlet of the second flow tube 222a may be the same.

The refrigerant flowing into the third muffler 230a flows through the second flow pipe 222a and flows into the first flow pipe 212a.

In detail, the refrigerant flows into the inlet of the first flow tube 212a and is discharged to the outlet of the first flow tube 212a. Accordingly, the refrigerant passes through the fifth-stage to the first-stage and flows to the front end of the piston 130. At this time, as the diameter through which the refrigerant passes becomes larger, the flow rate of the refrigerant decreases and the pressure increases.

According to this structure, the refrigerant can flow to the front end of the piston 130 at a higher pressure. As a result, the suction valve 135 is opened earlier and more refrigerant can be introduced into the compression chamber.

In the foregoing, an exemplary shape of the muffler having a plurality of variable portions has been described and can be embodied in a variety of shapes.

In addition, the muffler 200 according to the present invention may include a plurality of through holes for reducing the flow noise of the refrigerant and increasing the pressure of the refrigerant. Hereinafter, an exemplary shape of the muffler 200 of the present invention will be described with reference to the drawings. The same contents as those described above are omitted and the above description is referred to.

FIG. 10 is an exploded view of a muffler of a compressor according to a third embodiment of the present invention, and FIG. 11 is a cross-sectional view of a piston and a muffler of a compressor according to a third embodiment of the present invention.

10 and 11, the muffler according to the third embodiment of the present invention is provided with a plurality of through holes. At this time, a plurality of through holes may be formed in a separate structure constituting the muffler 200.

10 and 11, the muffler 200 includes the first muffler 210b, the second muffler 220b, the third muffler 230b, and the pores 240. [

The perforated pipe 240 is provided in the shape of a cylindrical pipe having a plurality of through holes 242 formed therein. In addition, the pores 240 may be formed to be thin and elastic in comparison with the first muffler 210b, the second muffler 220b, and the third muffler 230b.

The size and the number of the through holes 242 may be different depending on the design. In addition, the plurality of through holes 242 may be formed to have different sizes. In particular, the size and number of such through holes 242 are determined in conjunction with the calculation of the frequency to reduce the noise.

The plurality of through holes 242 may be spaced apart from each other along the perimeter of the perforated pipe 240. For example, in FIGS. 10 and 11, the plurality of through holes 242 are formed in three lines along the perimeter of the perforated pipe 240.

The first muffler 210b includes a first flow pipe 212b through which refrigerant flows, a first coupling portion 214b that is seated on the piston 130, and a first suction portion 216b. Although the first flow tube 212b is illustrated as having a variable portion like the first flow tube 212 of the first embodiment, this is merely exemplary and the first flow tube 212b may be provided in various shapes.

The first coupling portion 214b may extend radially beyond the inner diameter of the piston 130 at the outer side of the first flow tube 212b and may be seated at one end of the piston 130. That is, the first coupling portion 214b is formed at a position corresponding to one end of the piston 130. [

Therefore, the front of the first flow tube 212b including the outlet portion may be disposed inside the piston 130 with respect to the first coupling portion 214b. In addition, the rear of the first flow tube 212b including the inlet may be coupled with the porous tube 240.

The second muffler 220b includes a second flow pipe 222b through which the refrigerant flows, a second coupling portion 224b and a second suction portion 226b extending from the second flow pipe 222b to one side Respectively. Although the second flow pipe 222b is illustrated as the second flow pipe 222a of the second embodiment, this is merely exemplary and the second flow pipe 222b may be provided in various shapes.

The second engagement portion 224b extends radially and forward from the outside of the second flow pipe 222b and contacts the first suction portion 216b of the first muffler 210b. At this time, the front of the second flow tube 222b including the outlet portion may be coupled to the pore tube 240 with reference to the second coupling portion 224b.

That is, one end of the porous tube 240 is coupled to the rear of the first flow tube 212b, and the other end is coupled to the front of the second flow tube 212b. In other words, the pores 240 are coupled to connect the outlet of the second flow tube 212b and the inlet of the first flow tube 212b.

In addition, the pore tube 240 may be disposed radially inward of the first coupling portion 214b and the second coupling portion 224b. In particular, the pore tube 240 may be disposed in a space formed by the first coupling portion 214b, the first suction portion 216b, and the second coupling portion 224b. Accordingly, the refrigerant may flow from the inside of the porous pipe 240 to the space through the plurality of through holes 242, or may flow into the porous pipe 240 in the space.

At this time, the outlet of the second flow tube 212b and the inlet of the first flow tube 212b may have the same diameter. The perforated pipe 240 may be formed to have the same diameter as the outlet of the second flow tube 212b and the inlet of the first flow tube 212b.

As shown in FIG. 11, the pore tube 240 can be fitted to the outside of the first flow tube 212b and the second flow tube 212b. The pores 240 may be coupled to the inside of the first flow tube 212b and the second flow tube 212b or correspond to the first flow tube 212b and the second flow tube 212b And may have a predetermined engagement groove.

Referring to FIG. 10, the assembling of the muffler 200 will be described. The pores 240 are fitted to the rear of the first muffler 210b. The second muffler 220b is fitted in the pores 240 and is disposed in contact with the first muffler 210b. That is, the first muffler 210b and the second muffler 220b are brought into contact with each other so that the perforated pipe 240 is positioned inside the first muffler 210b and the second muffler 220b. The third muffler 230b is in contact with the first muffler 210b such that the second muffler 220b is located inside.

The refrigerant flowing into the third muffler 230b passes through the second flow pipe 222b. The refrigerant flows through the second flow pipe 222b. Then, the refrigerant passes through the porous tube 240 and flows into the first flow tube 210b. At this time, the noise of the refrigerant can be reduced through the through hole 242 of the pore tube 240.

That is, the pore tube 240 may be connected to the first flow tube 210b and the second flow tube 222b to form one flow tube. In other words, it can be understood that the muffler 200 is provided with one flow tube formed of the first flow tube 210b, the second flow tube 222b, and the pore tube 240. At this time, the flow pipe means a predetermined pipe extending in the flow direction so as to flow the refrigerant in a predetermined flow direction to provide the compressed space.

At this time, it can be understood that a plurality of through holes 242 are formed in one flow tube. The plurality of through holes 242 may be formed in one flow pipe so as to be located outside the piston 130. In particular, the plurality of through holes 242 may be positioned between the first muffler 210 and the second muffler 210.

Also, the pressure of the refrigerant flowing through the pore tube 240 can be maintained relatively high by connecting the outlet of the second flow pipe 222b and the inlet of the first flow pipe 212b. As a result, the suction valve 135 is opened earlier and more refrigerant can be introduced into the compression chamber.

In addition, the muffler 200 may be provided in various forms having a plurality of through holes. Hereinafter, another exemplary shape of the muffler 200 of the present invention will be described with reference to the drawings.

FIG. 12 is an exploded view of a muffler of a compressor according to a fourth embodiment of the present invention, and FIG. 13 is a cross-sectional view of a piston and a muffler of a compressor according to a fourth embodiment of the present invention.

12 and 13, the muffler according to the fourth embodiment of the present invention is provided with a plurality of through holes. At this time, a plurality of through holes may be formed in the second muffler 220c.

12 and 13, the first muffler 210c includes a first flow pipe 212c through which refrigerant flows, a first coupling portion 214c that is seated on the piston 130, And a first suction portion 216c contacting the first suction portion 220c. Although the first flow tube 212c is illustrated as having a variable portion like the first flow tube 212 of the first embodiment, this is merely exemplary and the first flow tube 212c may be provided in various shapes.

The first coupling portion 214c may extend radially beyond the inner diameter of the piston 130 at the outer side of the first flow tube 212c and may be seated at one end of the piston 130. That is, the first engaging portion 214c is formed at a position corresponding to one end of the piston 130. [

The first suction portion 216c may extend rearward from the first engagement portion 214c and be in contact with the second muffler 220c. At this time, the first suction portion 216c may extend further backward than the first to third embodiments described above. In addition, the third muffler 230c is disposed outside the first suction portion 216c.

12 and 13, the second muffler 220c includes a second flow pipe 222c through which a coolant flows, a second coupler 224c extending from the second flow pipe 222c to one side, And a second suction portion 226c.

The second flow pipe 222c is provided as a circular pipe extending in the flow direction of the refrigerant. Hereinafter, one end of the second flow pipe 222a adjacent to the first muffler 210a is referred to as an inlet portion and the other end is referred to as an outlet portion, based on the direction of flow of the refrigerant. At this time, the diameter of the inlet portion and the diameter of the outlet portion of the second flow tube 222c are shown to be equal to each other, but this is merely an example.

The second flow tube 222c may extend to contact the outlet of the second flow tube 222c and the inlet of the first flow tube 212c. That is, the first flow tube 210c and the second flow tube 222c may be connected to form one flow tube. In other words, it can be understood that the muffler 200 is provided with one flow tube formed of the first flow tube 210c and the second flow tube 222c.

At this time, the diameter of the outlet of the second flow tube 222c and the diameter of the inlet of the first flow tube 212c may be the same.

The second engagement portion 224c extends radially outside the second flow tube 222c and contacts the first suction portion 216c of the first muffler 210c. That is, the first suction portion 216c and the second engagement portion 224c may be arranged to be in contact with each other. The third muffler 230c is disposed outside the second engagement portion 224c.

At this time, a plurality of through holes 228 may be formed in front of the second flow tube 222c including the outlet portion, with reference to the second coupling portion 224c. The size and number of the through holes 228 may be different depending on the design. The plurality of through holes 228 may be formed to have different sizes. In particular, the size and number of such through holes 228 are determined in conjunction with the calculation of the frequency to reduce the noise.

The refrigerant flowing into the third muffler 230c flows through the second flow pipe 222c in the muffler 200 having the above structure. At this time, the noise of the refrigerant can be reduced through the through hole 228 formed in the second flow pipe 222c.

The outlet of the second flow pipe 222c and the inlet of the first flow pipe 212c are connected to each other so that the pressure of the refrigerant passing through the second flow pipe 222c and the first flow pipe 212c Can be maintained relatively high. As a result, the suction valve 135 is opened earlier and more refrigerant can be introduced into the compression chamber.

The muffler of various shapes can reduce the noise of the refrigerant and maintain a relatively high pressure. Further, the variable portion and the through hole structure of the muffler described above may be respectively provided or may be provided at the same time. That is, mufflers of various shapes can be provided in various combinations other than the shapes shown in the drawings.

10: compressor 130: piston
200: muffler 210: first muffler
212: first flow tube 220: second muffler
222: second flow tube 230: third muffler
240: Porous pipe 242: Through hole

Claims (15)

A shell to which the suction pipe is coupled;
A cylinder disposed inside the shell to form a compression space;
A piston reciprocating inside the cylinder to compress the refrigerant in the compression space; And
And a muffler that flows the refrigerant sucked through the suction pipe and supplies the refrigerant to the compression space,
In the muffler,
A plurality of flow tubes extending in a flow direction of the refrigerant; And
And a plurality of through holes formed through at least one of the plurality of flow tubes,
In the muffler,
A first muffler;
A second muffler coupled to a rear side of the first muffler;
A third muffler that receives the second muffler therein and is coupled to the rear side of the piston; And
And a porous pipe disposed between the first muffler and the second muffler and having the plurality of through holes formed therein. delete The method according to claim 1,
Wherein one end of the porous tube is coupled to the first muffler and the other end is coupled to the second muffler. The method according to claim 1,
The first muffler includes a first flow tube, a first coupling portion extending radially outwardly from the first flow tube, and a first suction portion extending backward from the first coupling portion,
Wherein the second muffler includes a second flow tube, a second coupling portion extending radially outwardly and forwardly in the second flow tube and in contact with the first suction portion. 5. The method of claim 4,
And the perforated pipe is disposed radially inward of the first engagement portion and the second engagement portion. 5. The method of claim 4,
Wherein the porous pipe is disposed in a space defined by the first coupling portion, the first suction portion, and the second coupling portion. The method according to claim 1,
In the flow tube,
A first flow pipe provided in the first muffler; And
And a second flow pipe provided in the second muffler and spaced apart from the first flow pipe,
And the pores connect the first flow tube and the second flow tube. 8. The method of claim 7,
Wherein the porous tube is thinner than the first flow tube and the second flow tube. A shell to which the suction pipe is coupled;
A cylinder disposed inside the shell to form a compression space;
A piston reciprocating inside the cylinder to compress the refrigerant in the compression space; And
And a muffler that flows the refrigerant sucked through the suction pipe and supplies the refrigerant to the compression space,
In the muffler,
A plurality of flow tubes extending in a flow direction of the refrigerant; And
And a plurality of through holes formed through at least one of the plurality of flow tubes,
In the muffler,
A first muffler;
A second muffler coupled to a rear side of the first muffler and having the plurality of through holes formed therein; And
A third muffler accommodating the second muffler therein and being coupled to a rear side of the piston,
In the flow tube,
A first flow pipe provided in the first muffler; And
And a second flow tube provided in the second muffler and connected to the first flow tube. delete 10. The method of claim 9,
And the plurality of through holes are formed in the second flow tube. 10. The method of claim 9,
Wherein the first flow tube is disposed inside the piston and the second flow tube is disposed outside the piston so as to contact one end of the first flow tube. 10. The method according to any one of claims 1 to 9,
Wherein the plurality of through holes are formed in different sizes. 10. The method according to any one of claims 1 to 9,
And the plurality of through-holes are formed along the circumference of the flow tube. A refrigerator comprising a linear compressor according to any one of claims 1 to 9.

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