KR20180090520A - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
KR20180090520A
KR20180090520A KR1020170015470A KR20170015470A KR20180090520A KR 20180090520 A KR20180090520 A KR 20180090520A KR 1020170015470 A KR1020170015470 A KR 1020170015470A KR 20170015470 A KR20170015470 A KR 20170015470A KR 20180090520 A KR20180090520 A KR 20180090520A
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KR
South Korea
Prior art keywords
shell
frame
cylinder
piston
cover
Prior art date
Application number
KR1020170015470A
Other languages
Korean (ko)
Inventor
유효상
최기철
Original Assignee
엘지전자 주식회사
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Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to KR1020170015470A priority Critical patent/KR20180090520A/en
Publication of KR20180090520A publication Critical patent/KR20180090520A/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027Pulsation and noise damping means
    • F04B39/0055Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0072Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12Casings; Cylinders; Cylinder heads; Fluid connections

Abstract

A linear compressor according to an embodiment of the present invention includes: a cylinder defining a refrigerant compression space therein; A cylinder inserted in the cylinder and expanding or compressing the compression space while reciprocating in the axial direction of the cylinder and having a plurality of suction holes formed on the front surface thereof; A suction valve coupled to a front surface of the cylinder and selectively opening and closing the plurality of suction holes; A guide inserted through the center of the suction valve and inserted into the piston; And the body portion is inserted into the guide, and the head portion includes a fastening member engaged with the front end portion of the guide, and the guide protrudes from the front surface of the piston, and the suction valve is opened when the piston reciprocates linearly And moves relative to the guide in a direction opposite to the moving direction of the piston by inertia.

Description

[0001] Linear compressor [0002]

The present invention relates to a linear compressor.

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 operating gases. .

Such compressors are broadly classified into a reciprocating compressor that compresses the refrigerant while linearly reciprocating the piston inside the cylinder so that a compression space in which the working gas is sucked or discharged is formed between the piston and the cylinder, A rotary compressor for compressing the refrigerant while the roller is eccentrically rotated along the cylinder inner wall and a compression space in which a working space is sucked or discharged between the cylinder and the cylinder is formed between the eccentrically rotated roller and the cylinder, a scroll compressor in which a compression space in which an operating gas is sucked or discharged is formed between a fixed scroll and a fixed scroll and the orbiting scroll rotates along the fixed scroll to compress the refrigerant.

In recent years, among the reciprocating compressors, there has been developed a linear compressor in which a piston is directly connected to a driving motor that reciprocates linearly, so that compression efficiency can be improved without mechanical loss due to motion switching and a simple structure is constructed.

Normally, in a linear compressor, a piston is linearly reciprocated within a cylinder by a linear motor in a closed shell, and is configured to suck and compress the refrigerant, and then discharge the refrigerant.

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 in the state of being connected to the piston, the piston linearly reciprocates in the cylinder, sucks the refrigerant, compresses the refrigerant, and discharges the refrigerant.

The linear compressor disclosed in the following prior art is a structure in which the suction valve is fixed to the front surface of the piston by a fastening member such as a bolt. The central portion of the suction valve is fixed to the piston by the head portion of the bolt.

Referring to the linear compressor disclosed in the prior art, the space inside the shell of the compressor serves as a space for accommodating the compressor body, and also serves as a space for temporarily storing the refrigerant introduced through the suction pipe before compression.

The portion that generates heat in the linear compressor includes a linear motor portion and a discharge portion in which the discharge cover is located. Especially, in the discharge portion, the temperature in the discharge portion region is very high in the region where the refrigerant compressed at high temperature and high pressure exists, and the region in the opposite side of the discharge portion is relatively low in temperature as the region where the suction refrigerant exists.

The heat generated in the discharging portion is transferred through the space between the frame and the shell through the convection heat transfer to the opposite region of the discharging portion. Then, the temperature of the refrigerant entering the suction muffler is increased, and when the temperature of the suction refrigerant is increased, the compressor efficiency and the cooling power both decrease.

If the gap between the frame and the shell is made very small in order to block the temperature rise of the suction refrigerant due to such convective heat transfer, the frame and the shell collide with each other during the operation of the compressor to generate vibration and noise, There is a danger.

In addition, the frame and the shell may be damaged due to vibration generated during the transportation of the compressor.

Korea Patent Publication No. 2016-0024217 (March 04, 2016)

SUMMARY OF THE INVENTION The present invention is proposed to solve the above problems.

According to an aspect of the present invention, there is provided a linear compressor including: a compressor main body; And a cylindrical shell for receiving the compressor body, wherein the compressor body includes: a frame head which is erected in a direction orthogonal to the longitudinal direction of the shell; and a longitudinal direction of the shell at the rear center of the frame head, A frame including a frame body extending in the same direction; A cylinder penetrating the front surface of the frame head and inserted in the frame body to form a refrigerant compression space therein; A piston inserted in the cylinder and reciprocating in an axial direction of the cylinder to expand or compress the compression space; And an interval reducing member attached to the outer circumferential surface of the frame head facing the inner circumferential surface of the shell to minimize heat transfer from the front of the frame head to the rear of the frame head through a space between the shell and the frame can do.

The gap reducing member may include a gasket bonded to the outer circumferential surface of the frame head.

The gasket may have a width corresponding to the thickness of the frame head.

The gap reducing member may include an O-ring surrounding the outer circumferential surface of the frame head.

A groove for insertion of the O-ring may be formed on an outer circumferential surface of the frame head, and the O-ring may protrude from an outer circumferential surface of the frame head while the O-ring is inserted into the groove.

According to the linear compressor of the present invention, the space between the frame and the shell is minimized without bringing the frame into contact with the inner peripheral surface of the shell, and heat generated in the discharge portion is transferred to the refrigerant suction side There is an advantage that it can be minimized.

By minimizing the amount of heat transferred from the discharge portion to the refrigerant suction side, the temperature rise of the refrigerant guided to the compression space can be minimized and the compressor efficiency and cooling power drop can be minimized.

Further, since the space reducing member attached to the outer circumferential surface of the frame has elasticity, even if the frame vibrates in a direction approaching the shell, the effect that the space reducing member comes into contact with the shell and absorbs the impact can be obtained.

1 is an external perspective view showing a configuration of a linear compressor according to an embodiment of the present invention;
2 is an exploded perspective view of a shell and a shell cover of a linear compressor according to an embodiment of the present invention;
3 is an exploded perspective view of a main body of a linear compressor according to an embodiment of the present invention.
FIG. 4 is a longitudinal sectional view of a linear compressor according to an embodiment of the present invention taken along line I-I 'of FIG. 1; FIG.
5 is a partial cross-sectional view of a linear compressor with an interval reducing member according to another embodiment of the present invention.

Hereinafter, a linear compressor according to an embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 1 is an external perspective view showing a configuration of a linear compressor according to an embodiment of the present invention, and FIG. 2 is an exploded perspective view of a shell and a shell cover of a linear compressor according to an embodiment of the present invention.

Referring to FIGS. 1 and 2, a linear compressor 10 according to an embodiment of the present invention may include a shell 101 and a shell cover coupled to the shell 101. The shell cover may include a first shell cover 102 and a second shell cover 103.

In detail, the legs 50 can be coupled to the lower side of the shell 101. The legs 50 may be coupled to the base of the product on which the linear compressor 10 is installed. In one example, the product may include a refrigerator, and the base may include a machine room base of the refrigerator. As another example, the product may include an outdoor unit of the air conditioner, and the base may include a base of the outdoor unit.

The shell 101 has a cylindrical shape and is advantageous in that the height of the machine room can be reduced when the linear compressor 10 is installed in the machine room base of the refrigerator.

A terminal block 108 may be provided on the outer surface of the shell 101. The terminal block 108 can be understood as a connecting portion for transmitting external power to the motor assembly 140 (see FIG. 3) of the linear compressor.

On the outside of the terminal 108, a bracket 109 is provided. 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. At both ends of the opened shell 101, the first and second shell covers 102 and 103 may be coupled. By the shell covers 102 and 103, the inner space of the shell 101 can be sealed.

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

The linear compressor 10 may further include a plurality of pipes 104, 105 and 106 provided in the shell 101 or the shell covers 102 and 103 to suck and discharge the refrigerant.

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

For example, the suction pipe 104 may be coupled to the first shell cover 102. The refrigerant can be sucked into the linear 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 linear 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 peripheral surface of the shell (101) at different heights, so that the operator can enjoy the convenience of operation.

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 supporting portion 102a and the second supporting device 185 can be understood as devices for supporting the main body of the linear compressor 10. [ Here, the main body of the compressor refers to a set of parts 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 may include components such as a piston 130, a magnet frame 138, a permanent magnet 146, a supporter 137, and a suction muffler 150, as shown in Figures 3 and 4 . 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 and the like.

A stopper 102b may be provided on the inner surface of the first shell cover 102. [ The stopper 102b is configured to prevent the main body of the compressor, in particular, the motor assembly 140 from being damaged by colliding with the shell 101 due to vibration or impact generated during transportation of the linear compressor 10, do. The stopper 102b is located adjacent to a rear cover 170 to be described later so that when the linear compressor 10 is shaken, the rear cover 170 interferes with the stopper 102b, It is possible to prevent the shock from being transmitted to the assembly 140.

The inner circumferential surface of the shell 101 may be provided with a spring coupling portion 101a. For example, the spring engagement portion 101a may be disposed at a position adjacent to the second shell cover 103. A first support spring 166 of a first support device 165, which will be described later, may be coupled to the spring coupling portion 101a. The front end of the compressor main body can be stably supported without bumping against the shell 101 inside the shell 101 by the engagement of the spring coupling portion 101a and the first support device 165. [

FIG. 3 is an exploded perspective view of a main body of a linear compressor according to an embodiment of the present invention, and FIG. 4 is a longitudinal sectional view of a linear compressor according to an embodiment of the present invention taken along line I-I 'of FIG.

3 and 4, the main body of the linear compressor 10 according to the embodiment of the present invention is provided inside the shell 101. The main body of the linear compressor 10 includes a frame 110, A piston 130 moving reciprocally in the cylinder 120 and a motor assembly 140 applying a driving force to the piston 130. [ The motor assembly 140 may be a linear motor that linearly reciprocates the piston 130 in the axial direction of the shell 101.

In detail, the linear compressor 10 may further include a suction muffler 150. The suction muffler 150 is coupled to the piston 130 and is provided to reduce 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 suction muffler 150. For example, in the course of the refrigerant passing through the suction muffler 150, the flow noise of the refrigerant can be reduced.

The suction muffler 150 may include a plurality of mufflers. The plurality of mufflers may include a first muffler 151, a second muffler 152 and a third muffler 153 coupled to each other.

The first muffler 151 is positioned inside the piston 130 and the second muffler 152 is coupled to the rear end of the first muffler 151. The third muffler 153 accommodates the second muffler 152 therein, and the front end thereof may be coupled to the rear end of the first muffler 151. From the viewpoint of the flow direction of the refrigerant, the refrigerant sucked through the suction pipe 104 can pass through the third muffler 153, the second muffler 152 and the first muffler 151 in order. In this process, the flow noise of the refrigerant can be reduced.

A muffler filter 154 may be mounted on the suction muffler 150. The muffler filter 154 may be positioned at an interface between the first muffler 151 and the second muffler 152. For example, the muffler filter 154 may have a circular shape, and an edge of the muffler filter 154 may be supported between the mating surfaces of the first and second mufflers 151 and 152.

Here, the term "axial direction" can be understood as a direction coinciding with a reciprocating motion of the piston 130, and an extending direction of a central axis in the longitudinal direction of the cylindrical shell 101. In the "axial direction", 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 "frontward direction" and the direction opposite thereto is referred to as "rearward" direction ". When the piston 130 moves forward, the compression space P can be compressed.

On the other hand, "radial direction" may be defined as a radial direction of the shell 101, and a direction orthogonal to a direction in which the piston 130 reciprocates.

The piston 130 may include a substantially cylindrical piston body 131 and a piston flange 132 extending radially from the rear end of 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 piston body (131) is configured to receive at least a portion of the first muffler (151).

A compression space P in which the refrigerant is compressed by the piston 130 is formed in the cylinder 120. A plurality of suction holes 133 are formed at a predetermined distance from the center of the front surface of the piston body 131 in the radial direction.

In detail, the plurality of suction holes 133 are arranged in the circumferential direction of the piston 130, and the refrigerant flows into the compression space P through the plurality of suction holes 133. The plurality of suction holes 133 may be spaced apart from each other at a predetermined interval in the circumferential direction of the front surface of the piston 130, or may be formed of a plurality of groups.

In addition, a suction valve 135 for selectively opening the suction hole 133 is provided in front of the suction hole 133.

The suction valve 135 is fixed to the front surface of the piston body 131 by a fastening member 135a such as a screw or a bolt.

A discharge cover 190 is formed in front of the compression space P to form a discharge space for the refrigerant discharged from the compression space P and a compression chamber P coupled to the discharge cover 190, Discharge valve assemblies (161, 163) for discharging the refrigerant compressed in the discharge space.

The discharge cover 190 may be provided in a form in which a plurality of covers are stacked.

The discharge valve assembly may include a discharge assembly 161 and a spring assembly 163 that provides an elastic force in a direction in which the discharge valve 161 is in close contact with the front end of the cylinder 120.

The discharge valve 161 is separated from the front surface of the cylinder 120 when the pressure in the compression space P becomes equal to or higher than the discharge pressure, To be discharged into the discharge space.

When the pressure in the compression space P becomes equal to or higher than the discharge pressure, the spring assembly 163 contracts so that the discharge valve 161 is separated from the front end of the cylinder 120.

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 190. [ For example, the valve spring 163a may include a leaf spring.

The discharge valve 161 is coupled to the valve spring 163a and the rear or rear surface of the discharge valve 161 is closely contacted with the front surface (or the front end) 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.

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 provided on the other side of the compression space P, that is, on the opposite side of the suction valve 135 .

When the pressure in the compression space P becomes equal to or lower than the suction pressure of the refrigerant in the process of linearly reciprocating the piston 130 in the cylinder 120, the suction valve 135 is opened, And enters the compression space (P).

On the other hand, when the pressure in the compression space P becomes equal to or higher than the suction pressure of the refrigerant, the suction valve 135 is closed and the refrigerant in the compression space P is compressed by advancing the piston 130.

On the other hand, when the pressure in the compression space P is larger than the pressure (discharge pressure) in the discharge space, the valve spring 163a is deformed forward and the discharge valve 161 is separated from the cylinder 120. [ The refrigerant in the compression space P is discharged into the discharge space through a clearance between the discharge valve 161 and the cylinder 120.

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 brought into close contact with the front end of the cylinder 120 again.

The linear compressor 10 may further include a cover pipe 162a. The capper pipe 162a is connected to the discharge cover 190 and discharges the refrigerant flowing into the discharge space formed inside the discharge cover 190 to the outside.

The linear compressor 10 may further include a loop pipe 162b. One end of the loop pipe 162b is coupled to the discharge end of the cover pipe 162a and the other end of the loop pipe 162b is connected to the discharge pipe 105 formed in the shell 101. [

The loop pipe 162b is made of a flexible material and relatively longer than the cover pipe 162a. 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. [

Meanwhile, the frame 110 can be understood as a structure for fixing the cylinder 120. For example, the cylinder 120 may be press-fitted into the center of the frame 110. The discharge cover 190 may be coupled to the front surface of the frame 110 by a fastening member.

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 force between 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.

 In detail, the magnet frame 138 may be coupled to the piston flange 132 and extend forward (in the axial direction). The permanent magnet 146 may be attached to the front end of the magnet frame 138 or the outer circumferential surface of the magnet frame 138. When the permanent magnet 146 reciprocates in the axial direction, the piston 130 can reciprocate axially with the permanent magnet 146 as one body.

The outer stator 141 may include a coil winding body 141b, 141c and 141d and a stator core 141a. The coil windings 141b, 141c and 141d may include a bobbin 141b and a coil 141c wound in the circumferential direction of the bobbin. The coil windings 141b, 141c and 141d may 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 have.

The stator core 141a may include a plurality of core blocks formed by stacking a plurality of laminations in a circumferential direction. The plurality of core blocks may be arranged to surround at least a part of the coil winding body 141b, 141c.

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 linear compressor 10 may further include a cover fastening member 149a for fastening the stator cover 149 and the frame 110 together. The cover fastening member 149a may extend forward toward the frame 110 through the stator cover 149 and may be coupled to 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 linear compressor (10) may further include a supporter (137) for supporting a rear end of the piston (130). The supporter 137 is coupled to the rear side of the piston 130 and a hollow portion may be formed inside the supporter 137 to allow the muffler 150 to pass therethrough.

The piston flange portion 132, the magnet frame 138, and the supporter 137 may be joined together 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 linear compressor (10) may further include a rear cover (170). The rear cover 170 is coupled to the stator cover 149 and extends rearward and is supported by a second support device 185.

In detail, the rear cover 170 may include three support legs, and the three support legs may 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 linear compressor 10 may further include an inlet guide unit 156 coupled to the rear cover 170 to guide refrigerant into the muffler 150. At least a portion of the inflow guide portion 156 may be inserted into the suction muffler 150.

The linear compressor (10) may include a plurality of resonance springs whose natural frequencies are adjusted so that the piston (130) can resonate.

More specifically, the plurality of resonance springs include a plurality of first resonance springs 176a supported between the supporter 137 and the stator cover 149, and a plurality of first resonance springs 176b between the supporter 137 and the rear cover 170 And a plurality of second resonant springs 176b supported thereon.

By the action of the plurality of resonance springs, stable reciprocating motion of the compressor main body can be achieved within the shell 101 of the linear compressor 10, and generation of vibration or noise due to the movement of the compressor main body can be minimized .

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

The linear compressor 10 may include 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. [

The plurality of sealing members 127, 128, 129a and 129b may include a first sealing member 127 provided at a portion where the frame 110 and the discharge cover 190 are coupled.

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 plurality of sealing members 127, 128, 129a and 129b may further include a third sealing member 129a provided between the cylinder 120 and the frame 110. [

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 first to fourth sealing members 127, 128, 129a, and 129b may be ring-shaped.

The linear compressor 10 may further include a first support device 165 for supporting the front end of the main body of the compressor 10. In detail, the first supporting device 165 is coupled to the support coupling portion 290 of the discharge cover 190. 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, and the first support spring 166 can be coupled to the spring engagement portion 101a.

The linear compressor (10) may further include a second support device (185) for supporting a rear end of the main body of the compressor (10). The second support device 185 is coupled to the rear cover 170. The second support device 185 may be coupled to the first shell cover 102 to elastically support the main body of the compressor 10. In detail, the second support device 185 includes a second support spring 186, and the second support spring 186 can be coupled to the cover support 102a.

In addition, the interval reducing member 200 may be attached to the outer circumferential surface of the frame 110. Specifically, the gap reducing member 200 includes a gasket having a predetermined elasticity, and may be attached to the outer circumferential surface of the frame 110 in a circular strip shape.

In detail, the frame 110 may include a disc-shaped frame head 110a and a frame body 110b extending from the center of the rear surface of the frame head 110a to receive the cylinder 120. [ The interval reducing member 200 may be surrounded by the outer peripheral surface of the frame head 110a.

The gap reducing member 200 may be attached to the outer circumferential surface of the frame head 110a by an adhesive.

5 is a partial cross-sectional view of a linear compressor with an interval reducing member according to another embodiment of the present invention, which is a cross-sectional view of a compressor corresponding to portion A of FIG.

Referring to FIG. 5, the gap reducing member 200a according to another embodiment of the present invention may include an O-ring surrounding the outer peripheral surface of the frame head 110a.

In detail, a ring insertion groove 110c for fitting the O-ring is formed in the outer circumferential surface of the frame head 110a, and the interval reducing member 200a, that is, the O-ring can be inserted into the ring insertion groove 110c have. A part of the O-ring protrudes from the outer circumferential surface of the frame head 110a, and the space between the O-ring and the shell 101 can be reduced.

Therefore, heat emitted through the discharge cover 190 can be prevented from being transmitted to the refrigerant suction port through the narrowed gap by the interval reducing member 200a.

Further, the O-ring has elasticity because it is made of a rubber material. Therefore, even if the distance between the frame 110 and the shell 101 becomes narrow due to the internal vibration, the O-ring can collide with the inner circumferential surface of the shell 101 to absorb the impact.

Claims (5)

  1. A compressor body; And
    And a cylindrical shell for receiving the compressor body,
    The compressor main body includes:
    A frame body extending in a direction orthogonal to the longitudinal direction of the shell and a frame body extending in the same direction as the longitudinal direction of the shell at the rear center of the frame head;
    A cylinder penetrating the front surface of the frame head and inserted in the frame body to form a refrigerant compression space therein;
    A piston inserted in the cylinder and reciprocating in an axial direction of the cylinder to expand or compress the compression space; And
    And an interval reducing member attached to an outer circumferential surface of the frame head facing the inner circumferential surface of the shell to minimize heat transfer from the front of the frame head to the rear of the frame head through a space between the shell and the frame Linear compressors.
  2. The method according to claim 1,
    Wherein the spacing member includes a gasket bonded to an outer circumferential surface of the frame head.
  3. 3. The method of claim 2,
    And the width of the gasket is formed to be a size corresponding to the thickness of the frame head.
  4. The method according to claim 1,
    Wherein the spacing member includes an O-ring surrounding the outer circumferential surface of the frame head.
  5. 5. The method of claim 4,
    A groove for inserting the O-ring is formed on an outer circumferential surface of the frame head,
    Wherein the O-ring protrudes from the outer peripheral surface of the frame head in a state where the O-ring is inserted into the groove.
KR1020170015470A 2017-02-03 2017-02-03 Linear compressor KR20180090520A (en)

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KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor

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