KR20190040812A - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
KR20190040812A
KR20190040812A KR1020170131609A KR20170131609A KR20190040812A KR 20190040812 A KR20190040812 A KR 20190040812A KR 1020170131609 A KR1020170131609 A KR 1020170131609A KR 20170131609 A KR20170131609 A KR 20170131609A KR 20190040812 A KR20190040812 A KR 20190040812A
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KR
South Korea
Prior art keywords
space
discharge
cover
inlet
cylinder
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KR1020170131609A
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Korean (ko)
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KR101981101B1 (en
Inventor
노기원
Original Assignee
엘지전자 주식회사
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Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to KR1020170131609A priority Critical patent/KR101981101B1/en
Priority claimed from EP18199473.2A external-priority patent/EP3470673A1/en
Publication of KR20190040812A publication Critical patent/KR20190040812A/en
Application granted granted Critical
Publication of KR101981101B1 publication Critical patent/KR101981101B1/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
    • F04B39/02Lubrication
    • F04B39/0223Lubrication characterised by the compressor type
    • F04B39/0276Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
    • 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
    • F04B39/06Cooling; Heating; Prevention of freezing

Abstract

The present invention relates to a linear compressor. According to the present invention, the linear compressor includes: a casing having a sealed inner space; a linear motor installed in the inner space of the casing and having a motor reciprocating on a stator; a compression unit installed at intervals on the inner circumference of the casing and having a compression space in a cylinder while a piston connected to the mover of the linear motor reciprocates in the cylinder; a gas bearing lubricating between the cylinder and the piston by guiding a part of a refrigerant discharged from the compression space into a gap between the cylinder and the piston; and at least one or more discharge covers connected to the compression unit and including a discharge space to accommodate the refrigerant discharged from the compression space. An inlet of the gas bearing is connected to the discharge space of the other discharge cover except for the discharge cover coming into contact with the compression space. Therefore, the linear compressor can improve the efficiency of the compressor by preventing the heat from being transferred from the discharge cover to a frame.

Description

[0001] LINEAR COMPRESSOR [0002]

The present invention relates to a linear compressor for lubricating between a cylinder and a piston with a refrigerant.

Generally, a compressor is a device that receives power from a power generating device such as a motor or a turbine and compresses a working fluid such as air or refrigerant. Compressors are widely applied to industrial and household appliances, especially vapor compression refrigeration cycles (hereinafter referred to as " refrigeration cycles ").

Such a compressor can be classified into a reciprocating compressor, a rotary compressor, and a scroll compressor according to a method of compressing a refrigerant. The reciprocating compressor is a system in which a compression space is formed between a piston and a cylinder, and a piston reciprocates linearly to compress the fluid. The rotary compressor compresses the fluid by a roller eccentrically rotated in the cylinder. The scroll compressor is a spiral type And the fluid is compressed.

BACKGROUND ART [0002] Reciprocating compressors are known as a crank system that compresses a refrigerant by converting a rotational force of a rotary motor into a linear motion, and a vibration system that compresses a refrigerant by using a linear motor that performs linear reciprocating motion. The oscillating type reciprocating compressor is referred to as a linear compressor. The linear compressor has no mechanical loss in converting the rotational motion into a linear reciprocating motion, thereby improving the efficiency and simplifying the structure.

On the other hand, the linear compressor can be divided into an oil-lubricated linear compressor and a gas-type linear compressor according to the lubrication system. The oil-lubricated linear compressor is configured to store a predetermined amount of oil in the casing and lubricate the cylinder and the piston using the oil, as disclosed in Patent Document 1 (Korean Patent Laid-Open Publication No. KR10-2015-0040027). On the other hand, as disclosed in Patent Document 2 (Korean Patent Laid-Open Publication No. KR10-2016-0024217), the gas-lubricated linear compressor has a structure in which a part of the refrigerant discharged from the compression space without guiding oil into the casing is guided between the cylinder and the piston And is configured to lubricate between the cylinder and the piston by the gas force of the refrigerant.

The oil-lubricated linear compressor can prevent the cylinder and the piston from being overheated by the heat of the motor, the heat of compression, etc., as the oil of relatively low temperature is supplied between the cylinder and the piston. As a result, the oil-lubricated linear compressor can prevent the suction loss from being generated by suppressing the rise of the refrigerant heated by the suction passage of the refrigerant passing through the suction passage of the piston into the compression chamber of the cylinder.

However, in the oil-lubricated linear compressor, when the oil discharged to the refrigeration cycle apparatus together with the refrigerant is not smoothly recovered to the compressor, oil shortage may occur in the casing of the compressor. Which may cause the reliability to deteriorate.

On the other hand, the gas-lubricated linear compressor is advantageous in that it can be downsized as compared with the oil-lubricated linear compressor and lubricates between the cylinder and the piston with the refrigerant, so that the reliability of the compressor is not lowered due to oil shortage.

However, in the conventional gas lubricating type linear compressor as described above, since the cylinder and the piston are heated by the refrigerant by using the high-temperature refrigerant gas, the refrigerant is sucked into the compression space, The refrigerant compressed in the space is overheated to cause a suction loss or a compression loss.

Further, in the conventional gas lubricated linear compressor, the refrigerant discharged from the compression space of the cylinder to the discharge space of the discharge cover heats the discharge cover, and the heated discharge cover transfers heat to the frame in contact with the discharge cover, There is a problem that the suction loss and the compression loss described above are increased.

Further, in the conventional gas lubricated linear compressor, the refrigerant discharged from the compression space of the cylinder to the discharge space of the discharge cover directly contacts the frame and the cylinder, and the frame is heated together with the cylinder, so that the suction loss and the compression loss, There was also a problem.

Korean Unexamined Patent Application Publication No. 10-2015-0040027 A (published on Apr. 14, 2014) Korean Patent Laid-Open Publication No. KR10-2016-0024217 A (published on March 23, 2014)

It is an object of the present invention to provide a linear compressor capable of suppressing generation of suction loss or compression loss due to overheat of a refrigerant compressed by the refrigerant in the compression space or a refrigerant sucked into the compression space by the cylinder and the piston heated by the refrigerant I'm trying to.

Another object of the present invention is to provide a linear compressor capable of preventing the cylinder and the piston from being heated by allowing the refrigerant lubricating between the cylinder and the piston to flow at a relatively low temperature.

It is another object of the present invention to provide a linear compressor capable of preventing conduction of heat between a discharge cover and a frame so as to suppress heating of the frame by the discharge cover.

It is another object of the present invention to provide a refrigerating apparatus which is capable of preventing the refrigerant discharged to the discharge space of the discharge cover from contacting the frame and the cylinder and suppressing the heating of the frame and the cylinder by the refrigerant discharged to the discharge cover, And to provide a linear compressor capable of increasing the linearity of the linear compressor.

In order to achieve the object of the present invention, in a linear compressor in which a gas bearing is applied between a cylinder and a piston, the inlet of the gas bearing communicates with another discharge space excluding a discharge space communicating with the cylinder. May be provided.

In this case, at least a part of the first discharge space may be accommodated in the second discharge space, in the order of the first, second, and third discharge spaces communicating with the compression space.

Further, in order to achieve the object of the present invention, there is provided an air conditioner comprising: a casing having a sealed inner space; A linear motor provided in an inner space of the casing and reciprocating with respect to the stator; A compression unit arranged to be spaced apart from an inner circumferential surface of the casing, the piston connected to the mover of the linear motor reciprocating in the cylinder and forming a compression space in the cylinder; A gas bearing for guiding a part of the refrigerant discharged from the compression space between the cylinder and the piston to lubricate between the cylinder and the piston; And at least one discharge cover coupled to the compression unit and having a discharge space for receiving the refrigerant discharged from the compression space, wherein the gas bearing has a discharge cover which is in contact with the compression space And is communicated with the discharge space of the discharge cover other than the discharge space of the discharge cover.

Here, the first discharge space forming the first discharge space is accommodated in the second discharge space forming the second discharge space, and the inlet of the gas bearing is connected to the second discharge space It can communicate with the space.

The discharge cover has a plurality of discharge covers each having a discharge space and each of the discharge spaces sequentially communicating with each other, and the plurality of discharge covers have a space portion forming each discharge space, The space portion of the discharge cover communicating with the inlet of the discharge cover may be formed into a non-circular cross-sectional shape.

The space portion of the discharge cover communicating with the inlet of the gas bearing may have a convex portion protruding in a radial direction to face the inlet of the gas bearing to receive the inlet of the gas bearing.

The discharge cover has a plurality of discharge covers each having a discharge space and each of the discharge spaces sequentially communicating with each other, and the plurality of discharge covers have a space portion forming each discharge space, The space portion of the discharge cover accommodated in the space portion of the discharge cover communicating with the inlet of the discharge cover may be formed into a non-circular cross-sectional shape.

The space portion of the discharge cover accommodated in the space portion of the discharge cover communicating with the inlet of the gas bearing may be recessed in the radial direction so as not to overlap with the inlet of the gas bearing.

The discharge cover in contact with the compression unit may have a fixing part for covering the inlet of the gas bearing, and the fixing part may be provided with a first gas hole communicating the discharge space with the inlet of the gas bearing.

A heat insulating member may be interposed between the discharge cover and the compression unit to block heat from being transferred from the discharge cover to the compression unit.

The heat insulating member may be formed to overlap with the fixing portion, and the heat insulating member may be provided with a second gas hole communicating with the first gas hole and communicating the discharge space with the inlet of the gas bearing.

In addition, a sealing member surrounding the inlet of the gas bearing is provided around the inlet of the gas bearing, and the sealing member can be in close contact with the heat insulating member or the fixing portion.

At least one heat-insulating space portion communicating with the internal space of the casing is formed between the discharge member and the compression unit, separated from the discharge space of the discharge cover. Between the compression unit and the heat- And a sealing member for separating the space portion from the discharge space.

The linear compressor according to the present invention can prevent the cylinder and the piston from being heated by introducing the inlet of the gas bearing into the gas bearing at a relatively low temperature by connecting the inlet of the gas bearing with the discharge cover at least second from the compression space . This makes it possible to increase the efficiency of the compressor by suppressing the overheating of the refrigerant in the suction passage and the compression space.

Further, by providing a heat insulating cover between the discharge cover and the frame to prevent heat from being conducted from the discharge cover to the frame, it is possible to suppress the overheating of the refrigerant in the suction passage and the compression space, thereby increasing the compressor efficiency.

Further, the heat insulating cover covers the front face of the frame or the front face of the cylinder to block or reduce the direct contact of the refrigerant received in the discharge cover with the frame or the cylinder, so that the frame or the cylinder is heated by the refrigerant contained in the discharge cover, Can be suppressed from being heated. The refrigerant in the suction passage and the compression space can be prevented from being overheated, thereby improving the efficiency of the compressor.

In addition, a heat insulating space is formed between the heat insulating cover and the frame, and the heat insulating space is communicated with the internal space of the casing so that the refrigerant of the suction pressure is filled in the heat insulating space, So that the efficiency of the compressor can be further increased.

1 is a longitudinal sectional view showing a linear compressor according to the present invention,
FIG. 2 is a perspective view of the discharge cover assembly shown in FIG. 1,
FIG. 3 is a perspective view of the discharge cover assembly shown in FIG. 2,
FIG. 4 is a longitudinal sectional view showing the discharge cover assembly according to FIG.
Fig. 5 is a longitudinal sectional view enlarged around the bearing inlet groove in Fig. 4,
FIGS. 6 and 7 are plan views for explaining embodiments in which the bearing inlet groove communicates with the second space portion in FIG. 5;
FIG. 8 is an exploded perspective view showing a part of an embodiment in which a heat insulating cover is included in the linear compressor according to FIG. 1;
Figure 9 is a longitudinal section view of a portion of the embodiment of Figure 8,
10 is a longitudinal sectional view showing another embodiment of the heat insulating cover in Fig.

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

The linear compressor according to the present invention performs an operation of sucking and compressing a fluid, and discharging a compressed fluid. The linear compressor according to the present invention may be a constituent of a refrigeration cycle. Hereinafter, the fluid will be described by taking a refrigerant circulating in a refrigeration cycle as an example.

Referring to FIG. 1, the linear compressor 100 according to the present embodiment is configured such that the inner space 101 of the casing 110 forms a closed space, and the inner space 101 of the casing 110 A frame 120 that is resiliently supported by the springs 161 and 162 may be provided. A linear motor 130 is coupled to the frame 120 and the linear motor 130 is coupled to a compression unit 140 for sucking, compressing and discharging the refrigerant. Accordingly, the compression unit 140 can be coupled to the frame 120 together with the linear motor 130, and can be elastically supported with respect to the casing 110.

The casing 110 may be formed of a thermally conductive material. The heat generated in the inner space 101 of the casing 110 can be dissipated through the casing 110 to the outside.

The casing 110 includes a shell 111 having openings at both ends and formed into a substantially cylindrical shape in a substantially transverse direction, a first shell cover 112 coupled to the rear side of the shell 111, 2 shell cover 113 as shown in FIG. The first shell cover 112 is disposed on the right side of the shell 111 and the second shell cover 113 is disposed on the left side of the shell 111 Can be combined. In a broad sense, the first shell cover 112 and the second shell cover 113 may form part of the shell 111. [

The inner diameter of the shell 110 may vary according to the size of the linear motor 130. However, since the linear compressor 100 of the present embodiment excludes the oil bearings and the gas bearing is applied, (101) need not be filled with oil. Therefore, the inner diameter of the shell 110 is formed to be as small as possible, for example, to such an extent that the flange portion 122 of the frame 120, which will be described later, can be spaced apart from the inner peripheral surface 111a of the casing 110 May be desirable. Accordingly, in the linear compressor 100 according to the present embodiment, the outer diameter of the shell 111 can be formed to be very small as compared with the above-described Patent Document 1.

The first shell cover 112 is coupled to the shell 111 so as to seal the rear side of the shell 111 as described above and the suction tube 114 can be inserted and coupled to the first shell cover 112 .

A cylindrical suction side support member 116a is coupled to the inner circumferential surface of the first shell cover 112. The suction side support member 116a is coupled to the first support spring 116 of the leaf spring . And the suction guide 116b may be inserted into the suction side support member 116a. The center of the first support spring 116 is coupled to the suction guide 116b described above, while the edge of the first support spring 116 can be coupled to the back cover 134 to be described later. The rear side of the compressor main body C including the back cover 134 is elastically supported by the first support spring 116 in the radial direction of the casing 110 including the first shell cover 112 .

The suction guide 116b is formed in a cylindrical shape and communicates with the suction pipe 114 so that the refrigerant sucked through the suction pipe 114 passes through the suction guide 116b and is sucked into the suction muffler assembly 150 Lt; / RTI >

A damping member 116c made of rubber or the like may be provided between the suction side support member 116a and the suction guide 116b. Accordingly, it is possible to prevent the vibration, which may be generated in the course of suction of the refrigerant through the suction pipe 114, from being transmitted from the suction guide 116b to the suction side support member 116a.

The second shell cover 113 is coupled to the shell 111 so as to seal the front side of the shell 111 as described above and includes a discharge pipe 115 connected to the loop pipe 115a to be described later Can be inserted and combined. Accordingly, the refrigerant discharged from the compression space 103b passes through the discharge cover assembly 160, which will be described later, and is discharged through the loop pipe 115a and the discharge pipe 115 to the refrigeration cycle.

The discharge side support member 117a is coupled to the inner circumferential surface of the shell 111 where the inner side surface of the second shell cover 113 or the inner side surface of the second shell cover 113 is in contact with the discharge side support member 117a, And a second support spring 117 made of a leaf spring can be engaged.

The central portion of the second support spring 117 may be coupled by a support guide 117b, a support cover 117c and a first support bracket 117d which are coupled to a discharge cover assembly 160 to be described later. The first support bracket 117d can be inserted into the second support bracket 113a fixed to the inner circumferential surface of the second shell cover 113 and supported in the axial direction and the radial direction. The front side of the compressor main body C including the discharge cover assembly 160 which will be described later is fixed to the casing 110 including the second shell cover 113 by the second support spring 117 in the radial direction It can be resiliently supported.

Meanwhile, a frame 120 constituting a part of the compressor main body C is provided in the casing 110. The frame 120 may be coupled with a motor 141 constituted by a linear motor 130 and a cylinder 141 constituting a compression unit 140. The frame 120 can be resiliently supported with respect to the casing 110 by the first support spring 116 and the second support spring 117 together with the linear motor 130 and the compression unit 140. [

The frame 120 may include a body portion 121 formed in a cylindrical shape and a flange portion 122 extending in a radial direction from a front end of the body portion 121.

An inner stator 132 to be described later may be coupled to the outer circumferential surface of the body portion 121 and a cylinder 141 may be coupled to the inner circumferential surface of the body portion 121, respectively. An outer stator 131 to be described later is attached to the rear surface of the flange portion 122 and a discharge cover assembly 160 to be described later can be coupled to the front surface of the flange portion 122, respectively.

A bearing communicating hole 125b which penetrates from the bearing inlet groove 125a to the inner circumferential face of the body portion 121 is formed at one side of the front surface of the flange portion 122, And a bearing communicating groove 125c may be formed in the inner circumferential surface of the body portion 121 to communicate with the bearing communicating hole 125b.

The bearing communicating hole 125b is formed to be inclined toward the inner circumferential surface of the body portion 121 by a hole having a smaller cross sectional area than the bearing entrance groove 125a . The bearing communication groove 125c may be formed in an annular shape having a predetermined depth and an axial length on the inner peripheral surface of the body portion 121. [ However, the bearing communication groove 125c may be formed on the outer circumferential surface of the cylinder 141 in contact with the inner circumferential surface of the body portion 121, or may be formed on the inner circumferential surface of the body portion 121 and the outer circumferential surface of the cylinder 141, respectively.

A bearing hole 141a may be formed in the cylinder 141 corresponding to the bearing communicating groove 125c to form a nozzle part of the gas bearing. This will be described again while explaining the cylinder.

Meanwhile, the linear motor 130 may include a stator 130a and a motor 130b that reciprocates with respect to the stator 130a.

The stator 130a includes an outer stator 131 fixed to the flange portion 122 of the frame 120 and an inner stator 132 disposed inside the outer stator 131 by a predetermined gap 130c Lt; / RTI > The inner stator 132 may be inserted and coupled to the outer circumferential surface of the body portion 121 so as to surround the body portion 121 of the frame 120. [

The outer stator 131 includes a stator core 136 laminated so as to surround the coil winding body 135 and the coil winding body 135. The coil winding body 135 includes a bobbin 135a and a bobbin 135a And a coil 135b wound in the circumferential direction may be included. The cross section of the coil 135b may be circular or polygonal, and may have a hexagonal shape, for example.

In addition, the stator core 136 may be laminated with a plurality of lamination sheets radially, and a plurality of lamination blocks may be laminated along the circumferential direction.

A stator cover 137 may be provided on the other side of the outer stator 131. Accordingly, one side portion of the outer stator 131 can be supported by the frame 120, and the other side portion can be supported by the stator cover 137, respectively.

The inner stator 132 may be inserted and fixed to the outer peripheral surface of the frame 120. The inner stator 132 may be formed by stacking a plurality of laminations radially.

Meanwhile, the mover 130b may be formed of a magnet holder 133a and a magnet 133b supported by the magnet folder 133a. One end of the magnet holder 133a is coupled to the piston 142 and the other end of the magnet holder 133a is reciprocally inserted into the gap between the outer stator 131 and the inner stator 132.

The magnet 133b may be adhered and fixed to the outer circumferential surface of the magnet holder 133a or may be fixed using a separate fixing ring (not shown). The magnet 133b can reciprocate linearly together with the magnet holder 133a by the mutual electromagnetic force formed between the outer stator 131 and the inner stator 132. [

A spring supporter 138 is coupled to the other end of the magnet holder 133a together with a piston 142. A motor 130b of the linear motor 130 and a motor 130b of the compression unit 140 are connected to both sides of the spring supporter 138, A first resonance spring 139a and a second resonance spring 139b for resonating the piston 142 may be provided.

Here, the first resonance spring 139a is disposed between the rear surface of the stator cover 137 and the front surface of the spring supporter 138, the second resonance spring 139b is disposed between the rear surface of the spring supporter 138 and the back surface 134, respectively. The back cover 134 is coupled to the stator cover 137 and can support the other end of the second resonance spring 139b in the axial direction as described above. The mover 130b of the linear motor 130 and the piston 142 of the compression unit 140 are linearly moved along the axial direction by the electromagnetic force of the linear motor 130 and the elastic forces of the resonance springs 139a and 139b. So that the refrigerant can be sucked into the compression space 103b to be compressed and discharged.

On the other hand, the compression unit 140 may include a cylinder 141, a piston 142, a suction valve 143, and a discharge valve assembly 144.

The cylinder 141 is formed in a cylindrical shape so as to have a compression space 103b therein and can be inserted and fixed to the inner circumferential surface of the frame 120. [ A discharge cover assembly 160 to be described later in which refrigerant compressed in the compression space 103b is discharged is provided on the front side of the suction muffler assembly 150 to be described later in which the refrigerant is sucked into the compression space 103b Respectively.

The cylinder 141 may be provided with a remaining portion of a gas bearing for supplying a discharge gas between the cylinder 141 and the piston 142 to gas lubrication between the cylinder 141 and the piston. For example, in the cylinder 141, the compressed refrigerant, which is radially passed through the bearing communicating groove 125c and communicated with the bearing communicating groove 125c, is communicated with the inner circumferential surface of the cylinder 141 and the inner circumferential surface of the piston 142 A bearing hole 141a for guiding to the outer circumferential surface can be formed. Of course, as described above, the bearing communicating groove 125c may be formed on the outer circumferential surface of the cylinder 141, which is more advantageous from the viewpoint of processing.

The bearing hole 141a may be formed as a fine hole so that the inlet is wide and the outlet is a nozzle. And a filter (not shown) for blocking foreign matter from entering the bearing hole 141a. The filter may be a metal mesh filter or may be formed by winding a member such as a cecile. Therefore, the inlet and outlet of the bearing hole 141a may be formed individually so as to communicate with each other independently. The inlet may be formed as an annular groove, and the outlet may be formed at a predetermined distance along the annular groove.

The bearing hole 141a may be formed only on the side adjacent to the compression space 103b (hereinafter referred to as the front side) with respect to the axial center of the cylinder 141, Or may be formed on the rear side.

The piston 142 may have a cylindrical shape such that the piston 142 has a suction passage 103a therein and the front end is partially opened while the rear end is fully opened. As described above, the rear end of the piston 142, which is an open end, is connected to the magnet holder 133a and can reciprocate together with the magnet holder 133a.

A suction port 142a communicating between the suction passage 103a and the compression space 103b is formed at the front end of the piston 142. The suction port 142a is selectively provided on the front surface of the piston 142, A suction valve 143 may be provided. The refrigerant sucked into the inner space 101 of the casing 110 is discharged through the suction passage 103a and the suction port 142a of the piston 142 while opening the suction valve 143, As shown in FIG.

At the front end of the cylinder 141, a discharge valve assembly 144 for opening and closing the compression space 103b may be detachably provided.

The discharge valve assembly 144 may include a discharge valve 144a and a valve spring 144b provided on the front side of the discharge valve 144a to elastically support the discharge valve 144a. The valve spring 144b may be formed of a compression coil spring, but may be formed of a leaf spring in consideration of an occupied space or reliability. Thus, when the pressure in the compression space 103b becomes equal to or higher than the discharge pressure, the valve spring 144b is deformed forward to open the discharge valve 144a, and the refrigerant is discharged from the compression space 103b, And discharged into the first discharge space 104a of the assembly 160. [ When discharge of the refrigerant is completed, the valve spring 144b provides a restoring force to the discharge valve 144a so that the discharge valve 144a is closed.

Meanwhile, a suction muffler assembly 150 is coupled to the rear end of the piston 142 to attenuate the noise generated during the suction of the refrigerant.

The suction muffler assembly 150 includes a suction muffler 151 communicating with the internal space 101 of the casing 110 and an internal guide connected to one side of the suction muffler 151 to guide the refrigerant to the suction port 142a 152).

The suction muffler 151 is provided outside the piston 142, and a plurality of sound-deadening spaces 102 may be formed therein by the baffle. Although the suction muffler 151 may be formed of metal, it may be formed of a plastic material in consideration of weight and insulation.

The inner guide 152 may be formed in a pipe shape so as to communicate with the noise space of the suction muffler and may be inserted deeply into the suction passage 103a of the piston 142. [ The inner guide 152 may be formed in a cylindrical shape having the same inner diameters at both ends, but it may be formed larger than the inner diameter of the rear end, which is the opposite side of the inner diameter of the front end which is the discharge side.

Meanwhile, a discharge cover assembly 160 for attenuating noise generated in the process of discharging the refrigerant in the discharge space 103b may be coupled to the front surface of the frame 120. [

The discharge cover assembly 160 may be provided on the front side of the cylinder to receive the discharge valve assembly 144. For this purpose, the discharge cover assembly 160 may be fixedly coupled to the front face of the flange portion 122, which constitutes a part of the frame 120.

Here, the discharge cover assembly 160 is formed of a thermally conductive material. When the high-temperature refrigerant flows into the discharge cover assembly 160, the heat contained in the refrigerant is transferred to the casing 110 through the discharge cover assembly 160 and dissipated to the outside of the compressor.

The discharge cover assembly 160 may be composed of a single discharge cover, or may be arranged so that a plurality of discharge covers sequentially communicate with each other. In this embodiment, the case where there are three discharge covers will be described as an example.

FIG. 2 is a perspective view of the discharge cover assembly shown in FIG. 1, and FIG. 3 is a perspective view of the discharge cover assembly shown in FIG. 10 is a longitudinal sectional view showing the assembled state.

Referring to these drawings, when there are three discharge covers, a discharge space (hereinafter referred to as a first discharge space) 104a of a discharge cover (hereinafter, referred to as a first cover) 161 coupled to the frame 120, (Hereinafter referred to as the second discharge space) 104b of the second discharge cover (hereinafter referred to as the second cover) 162 which is coupled to the front side of the first discharge chamber 161 and the second discharge space 104b communicates with the discharge space (Hereinafter referred to as a third discharge space) 104c of a third discharge cover (hereinafter referred to as a third cover) 163 coupled to the front side of the cover 162. [

2, a first space portion 161a is formed in a central portion of the first cover 161, a second space portion 162a is formed in a central portion of the second cover 162, And a third space portion 163a may be formed at the center portion.

The first space portion 161a includes a first discharge space 104a for accommodating the compression space 103b and a second space portion 162a for accommodating the first discharge space 104a. And the third space portion 163a may be formed with a third discharge space 104c for accommodating the second discharge space 104b.

The first discharge space 104a selectively communicates with the compression space 103b by the discharge valve 144a and the second discharge space 104b communicates with the first discharge space 104a. And the space 104c can communicate with the second discharge space 104b. Accordingly, the refrigerant discharged in the compression space 103b passes through the first discharge space 104a, the second discharge space 104b, and the third discharge space 104c in order to attenuate the discharge noise, And can be discharged to the outside of the casing 110 through the loop pipe 115a and the discharge pipe 115 communicating with the valve unit 163a.

 Here, the second space 162a may be formed to be wider than the first space 161a so that the first space 161a can be completely accommodated in the second space 162a. The first communication hole 105a may be formed in the first space portion 161a and the first communication hole 105a may be formed in the second discharge space 104b. Accordingly, the first discharge space 104a and the second discharge space 104b can be directly communicated by the first communication hole 105a.

The second space portion 162a may be formed such that a portion of the second space portion 162a is exposed to the outside of the third space portion 163a without being completely accommodated in the third space portion 163a. If the second space portion 162a is sufficiently accommodated in the third space portion 163a, the third space portion 163a may become too large and the discharge cover assembly 160 may be enlarged, Interference with parts may occur or the size of the entire compressor may increase.

Accordingly, the third space 163a is formed to be smaller than the second space 162a, and the third space 163a is formed in the second discharge space 104b and the third space 163a of the second space 162a, And the third discharge space 104c.

To this end, the second communication hole 105b formed in the second space portion 162a and the third communication hole 105c formed in the third space portion 163a are spaced apart from each other by a predetermined distance, and the second communication hole 105b and the third communication hole 105c may be connected to each other by a connection pipe 106. [ As a result, the third space 163a is not formed too large, so that the interference with the peripheral components and the increase in the size of the entire compressor can be suppressed, and the noise attenuation effect can be further increased by the length of the coupling pipe 106 .

A part of the first space portion 161a is exposed outside the range of the second space portion 162a so that the first discharge space 104a and the second space portion 161a of the first space portion 161a 162a may be connected to each other through a separate connection pipe (not shown). In this case, as the length of the coupling pipe becomes long, the effect of attenuating noise in the first cover 161 and the second cover 162 can be further improved.

On the other hand, the bearing inlet groove may communicate with the second discharge space. FIG. 5 is an enlarged longitudinal sectional view of the vicinity of the bearing inlet groove in FIG. 4, and FIGS. 6 and 7 are plan views for explaining embodiments in which the bearing inlet groove communicates with the second space portion in FIG.

4, the distance D11 from the center of the piston 142 to the inner circumferential surface of the first space portion 161a is larger than the distance D2 from the inner circumferential surface of the cylinder 141 to the inner circumferential surface of the cylinder 141, May be smaller than a distance (D13) to the inner peripheral surface of the outer circumferential surface (125a). 5, the inlet groove 125a of the bearing has a second space portion 162a which is the second discharge space 104b outside the first space portion 161a constituting the first discharge space 104a, ). ≪ / RTI >

However, when the distance D11 to the inner circumferential surface of the first space portion 161a is smaller than the distance D13 to the outer circumferential inner surface of the bearing inlet groove 125a, the side surface of the first space portion 161a has a substantially circular shape When the distance D11 to the inner peripheral surface of the first space portion 161a is formed to be equal to or greater than the distance D13 to the outer peripheral surface of the bearing inlet groove 125a, the first space portion 161a ) May be formed in a non-circular shape.

For example, when the distance D11 from the inner circumferential surface of the first space portion 161a to the inner circumferential surface of the bearing inlet groove 125a is larger than the distance D13 as shown in Fig. 6, And the bearing entrance groove 125a is positioned outside the recess 161a1 so that the portion facing the bearing inlet groove 125a is recessed toward the center, The inlet groove 125a can be excluded from the first discharge space 104a.

Accordingly, the bearing inlet groove 125a is located outside the first space portion 161a and is not in communication with the first discharge space 104a. Instead, the bearing inlet groove 125a is located inside the second space portion 162a, And communicates with the discharge space 104b. 3 to 5, the refrigerant introduced into the bearing inlet groove 125a is not directly introduced into the first discharge space 104a but flows out of the first discharge space 104a, The refrigerant which has moved to the second discharge space 104b through the space 104a flows in the second discharge space 104b.

Here, the second space 162a may be formed in a circular shape with a side surface thereof, or may be formed in a non-circular shape in some cases. When the side surface of the second space portion 162a is formed in a circular shape, the inner diameter of the second space portion 162a should be larger than the outer diameter D13 of the bearing inlet groove 125a. However, The distance D14 may be formed to be smaller than the distance D13 to the outer peripheral surface of the bearing inlet groove 125a to the inner peripheral surface of the second space portion 162a when the side surface of the portion 162a is non- have.

As shown in FIG. 7, when the side surface of the second space portion 162a is formed in a non-circular shape, a convex portion 162a1 extending outwardly enough to receive the bearing inlet groove 125a may be formed. The second space portion 162a communicates with the first space portion 161a through the first communication hole 105a and communicates with the bearing inlet groove 125a through the first gas hole 161b1 to be described later .

The first space portion 161a may be folded in one step in the first fixing portion 161b, which will be described later, and formed to be convex on the front side. However, it is preferable that the first space portion 161a is folded in two or more stages to form a plurality of step surfaces S1 and S2.

For example, the first space section 161a is formed with the first stepped surface S1 and the second stepped surface S2 in the order close to the frame. In the first stepped surface S1, And the discharge valve assembly is inserted into the second stepped surface S2 so as to be supported in the axial direction.

The first communication hole 105a is disposed closer to the cylinder 141 than the valve spring 144b and the flow path resistance to the refrigerant discharged from the compression space 103b to the first discharge space 104a is reduced . Thereby, the refrigerant discharged into the first discharge space 104a can quickly move to the second discharge space 104b through the first communication hole 105a.

The discharge valve assembly 144 fixed to the second stepped surface S2 is configured such that the discharge valve 144a is elastically supported by a valve spring 144b formed of a leaf spring, Thereby opening and closing the space 103b. Therefore, it is preferable that the depth D12 of the first discharge space 104a is formed to be at least larger than the thickness D3 of the discharge valve 144a.

The first cover 161 includes a first fixing portion 161b extending from the edge of the first space portion 161a and a second fixing portion 161b extending from the edge of the second space portion 162a. The second fixing portion 162b and the third cover 163 may further include a third fixing portion 163b extending from the edge of the third space portion 163a. The first cover 161 is coupled to the frame 120 by the first fixing portion 161b and the second cover 162 is coupled to the first cover 161 by the second fixing portion 162b. And the third cover 163 can be coupled to the second cover 162 by the third fixing portion 163b.

Each of the space portions 161a, 162a and 163a is convexly formed so as to have the discharge spaces 104a, 104b and 104c, respectively, while the respective fixing portions 161b, 162b and 163b May be formed in a flange shape extending radially in the respective space portions 161a, 162a, and 163a so as to be closely attached to the front surface of the flange portion 122 of the frame 120. [

The first fixing portion 161b and the second fixing portion 162b are formed to be wide and can be bolted to the flange portion 122 of the frame 120 by the same bolts in a state where they are overlapped with each other and the third fixing portion 163b May be formed narrower than the first and second fixing portions 161b and 162b and welded or attached to the front surface of the second cover 162 to be fixed.

4 and 5, a gasket 165 for heat insulation is provided between the first fixing part 161b and the frame 120, and a second discharge space 104b is provided inside the gasket 165, The first sealing member 166 may be provided to prevent the refrigerant from leaking. The gasket 165 may be formed of a material having a lower thermal conductivity than the first cover 161 and the first sealing member 166 may be an O-ring made of a material having a low thermal conductivity such as rubber .

As described above, since the first space portion 161a is positioned inside the bearing inlet groove 125a, the first fixing portion 161b is formed to cover the bearing inlet groove 125a and extend in the radial direction . The first fixing portion 162b is formed with the first gas hole 161b1 at a position where the bearing inlet groove 125a is opposed to the second fixing portion 162b so that the second discharge space 162a communicates with the bearing inlet groove 125a . At this time, since the refrigerant in the second discharge space 162a may leak between the first cover 161 and the frame 120 in the course of flowing into the bearing inlet groove 125a, A second sealing member 167 such as an O-ring may be provided.

The linear compressor according to this embodiment operates as follows.

That is, when a current is applied to the coil 135b of the linear motor 130, a magnetic flux is formed between the outer stator 131 and the inner stator 132. By the electromagnetic force generated by the magnetic flux, And the magnet 130b made of the magnet 133b reciprocate in a straight line at the gap between the outer stator 131 and the inner stator 132. [

Then, the piston 142 connected to the magnet holder 130b reciprocates linearly in the cylinder 141, and the volume of the compression space 103b is increased or decreased. At this time, when the volume of the compression space 103b is increased due to the backward movement of the piston 142, the suction valve 143 is opened so that the refrigerant in the suction passage 103a is sucked into the compression space 103b, The piston 142 compresses the refrigerant in the compression space 103b when the volume of the compression space 103b is reduced. The compressed refrigerant is discharged into the first discharge space 104a while opening the discharge valve 144a.

Then, the refrigerant discharged into the first discharge space 104a moves to the second discharge space 104b through the first communication hole 105a, and then flows into the second communication hole 105b and the connection pipe 106, 3 communication hole 105c to the third discharge space 104c. At this time, a part of the refrigerant moving from the first discharge space 104a to the second discharge space 104b flows through the first gas passage 161b1 provided in the first fixing portion 161b to the bearing The refrigerant flows into the inlet groove 125a through the bearing communicating hole 125b and the bearing communicating groove 125c and the bearing hole 141a of the cylinder 141 and the inner peripheral surface of the cylinder 141 and the piston 142, So as to lubricate between the cylinder 141 and the piston 142.

The refrigerant moving from the second discharge space 104b to the third discharge space 104c is discharged to the outside of the compressor through the loop pipe 115a and the discharge pipe 115 and is moved to the condenser of the refrigeration cycle And repeats a series of processes.

However, during the operation of the compressor, motor heat is generated in the linear motor 130, and the compressed heat is received by the refrigerant discharged from the compression space 103b in the discharge cover assembly 160. [ The motor heat and the compression heat are transferred to the cylinder 141 and the piston 142 through the frame 120, respectively.

The refrigerant sucked into the compression space 103b of the cylinder 141 as well as the refrigerant sucked into the suction passage 103a of the piston 142 is heated and the suction loss or the compression loss is generated Which may reduce the efficiency of the compressor as a whole.

Particularly, when the oil bearing is applied to the linear compressor, the temperature of the compression portion can be lowered by circulating the relatively low temperature oil between the cylinder 141 and the piston 142. However, as in the present embodiment, When the bearing is applied, since the high-temperature refrigerant flows into the space between the cylinder 141 and the piston 142, the temperature of the compressed portion further rises and the temperature rise of the refrigerant described above can be further increased.

Furthermore, the temperature of the refrigerant discharged from the compression space 103b to the discharge cover assembly 160 is maintained at a high temperature of about 70 ° C. Therefore, when the refrigerant discharged from the compression space 103b out of the respective covers constituting the discharge cover assembly 160 flows into the gas bearing in the discharge space 104a of the first cover 161 in which the refrigerant is first received, The coolant may be supplied directly between the cylinder 141 and the piston 142 so that the temperature of the cylinder 141 and the piston 142 may be further increased.

However, as in the present embodiment, when the refrigerant in the second discharge space 104b having a relatively lower temperature than the refrigerant in the first discharge space 104a is supplied to the gas bearing, the temperature of the cylinder and the piston is excessively heated . That is, the refrigerant flowing into the first discharge space 104a is radiated by the low-temperature refrigerant filled in the inner space 101 of the casing 110 so that the first cover 161 is lowered to around 60 ° C As the refrigerant moves to the second discharge space 104b and is supplied to the gas bearing, the heat transmitted from the discharge cover assembly 160 to the compression portion is lowered. This prevents overheating of the refrigerant being sucked or the refrigerant being compressed, thereby preventing suction loss or compression loss from occurring in the compression unit.

Meanwhile, another embodiment of the linear compressor according to the present invention is as follows.

That is, in the above-described embodiment, the gasket is provided between the first fixing part and the front face of the frame to insulate a part of the area where the first fixing part and the frame come into contact with each other, As the frame was in direct contact, heat transfer due to conduction could be increased. In addition, the front surface of the frame or the front surface of the cylinder is exposed to the first discharge space, and the refrigerant in the first discharge space is brought into contact with the frame or the cylinder, thereby further increasing the temperature of the frame and the cylinder.

Accordingly, in this embodiment, a heat insulating cover is provided between the first fixing part and the front surface of the frame so that heat of the first fixing part is conducted to the frame or the refrigerant in the first discharge space is prevented from contacting the frame or the cylinder, And the cylinder can be suppressed from being heated.

FIG. 8 is an exploded perspective view showing a part of an embodiment in which a heat insulating cover is included in the linear compressor according to FIG. 1, and FIG. 9 is a longitudinal sectional view showing part of the embodiment according to FIG.

2 and 8, the heat insulating cover 170 is provided between the front surface 122b of the frame 120 and the first fixing portion 161b of the first cover 161, and the first cover 161 may be bolted to the frame 120. The heat insulating cover 170 may be formed of a material having a thermal conductivity lower than that of the first cover 161. The heat insulating cover 170 can prevent direct contact of the first cover 161 with the frame 120 and prevent the heat contained in the first cover 161 from being transmitted to the frame 120 .

8 and 9, a part of the heat insulating cover 170 according to the present embodiment is positioned between the frame 120 and the first fixing part 161b to block heat transfer due to conduction, And a part of the first space portion 161a may be located between the frame 120 and the cylinder 141 and the first space portion 161a to prevent heat transfer due to convection. A portion located between the frame 120 and the first fixing portion 161b is referred to as a first heat insulating portion 171 and a portion between the frame 120 and the cylinder 141 and the first space portion 161a And the portion where it is positioned is referred to as a second heat insulating portion 172.

The first heat insulating portion 171 is formed on the outer side of the heat insulating cover 170 and the second heat insulating portion 172 is formed on the inner side of the heat insulating cover 170. Accordingly, the first heat insulating portion 171 is supported on the outer ridge 122c provided on the front surface 122b of the frame 120 while the second heat insulating portion 172 is supported on the front surface of the frame 120 122b and the first sealing member 166 provided on the front surface 122b of the frame 120. [

A spacing groove 122e is formed between the outer and inner protrusions 122c and 122d by a predetermined depth to form a heat insulating space V. The spacing groove 122e has an outer protrusion 122c, So that it can communicate with the inner space of the casing. As a result, the refrigerant having the relatively low suction pressure is filled in the spacing groove 122e constituting the heat insulating space portion (V).

The second insulating portion of the heat insulating cover can be supported on the inner side surface of the inner protrusion 122d. The front surface 122b of the frame 120 is covered with the heat insulating cover 170 so that the space between the spacing groove 122e of the frame 120 and the rear surface of the heat insulating cover 170 is filled with the above- (V) may be formed.

The inner protruding portion 122d is provided in the rear surface of the heat insulating cover V so that the first sealing member 166 for sealing between the first discharge space 104a and the heat insulating space portion V is inserted One sealing member insertion groove 122f may be formed. The first sealing member 166 is in close contact with the inner rear surface of the heat insulating cover 170 so that the spacing groove 122e is communicated with the first discharge space 104a formed in the first space 161a of the first cover 161 Of course, can be separated from the compression space 103b formed in the cylinder 141 and maintained in a sealed state.

On the other hand, the above-described bearing inlet groove 125a may be formed in the spacing groove 122e. As the bearing inlet groove 125a communicates with the second discharge space 104b, a second sealing member insertion groove 122g is formed so as to surround the bearing inlet groove 125a, a second sealing member insertion groove 122g is formed, The second sealing member 167 may be inserted into the second sealing member 167.

A second gas hole 170a is formed between the outer peripheral surface 170a and the inner peripheral surface 170b of the second heat insulating portion 172 so that the refrigerant in the second discharge space 104b can be introduced into the bearing inlet groove 125a And the second gas hole 170 may be formed coaxially with the first gas hole 161b1.

When the first heat insulating portion 171 of the heat insulating cover 170 made of a material having a low thermal conductivity is positioned between the first fixing portion 161b and the front surface 122b of the frame 120, It is possible to prevent heat from being conducted in the direction of the frame 120 from the frame 161 to prevent the frame 120 from being heated.

The second heat insulating portion 172 of the heat insulating cover 170 is positioned between the first space portion 161a and the front surface 122b of the frame 120 and the front surface 141b of the cylinder 141 The first discharge space 104a forming the interior of the first space portion 161a is interrupted between the front surface 122b of the frame 120 and the front surface 141b of the cylinder 141. [ The refrigerant in the first discharge space 104a can not directly contact the frame 120 or the cylinder 141 and the frame 120 or the cylinder 141 is heated directly by the refrigerant in the first cover 161 Can be suppressed.

Furthermore, a heat insulating space portion V, which is a spacing groove 122e, is formed between the second heat insulating portion 172 of the heat insulating cover 170 and the front surface 122b of the frame 120, and the heat insulating space portion V The relatively cold refrigerant flows into the inner space 101 of the casing 110. [ Therefore, the heat toward the frame 120 or the cylinder 141 in the first discharge space 104a is blocked in the heat-insulating space portion V so that the frame 120 and the cylinder 141 are prevented from being heated more effectively .

Thus, overheating of the refrigerant in the suction passage or the compression space can be suppressed while the temperature of the frame is maintained at about 60 DEG C or lower, whereby the suction loss and the compression loss of the refrigerant can be reduced and the efficiency of the compressor can be improved .

On the other hand, the second heat insulating portion of the heat insulating cover according to the present embodiment may be formed to cover a part of the cylinder beyond the frame. 10 is a longitudinal sectional view showing another embodiment of the heat insulating cover in FIG.

As shown in this figure, in this embodiment, as the heat insulating cover 170 completely covers the front surface 122b of the frame 120, the refrigerant in the first discharge space 104a directly contacts the frame 120 You can block things. In addition, as the heat insulating cover 170 partially covers the front surface 141b of the cylinder 141, the area of the cylinder 141 in which the refrigerant directly contacts the first discharge space 104a is also reduced.

Accordingly, it is possible to reduce heating of the frame 120 and the cylinder 141 by the refrigerant, thereby suppressing the overheating of the refrigerant in the compression space and the suction space.

In the above-described embodiments, the bearing inlet groove communicates with the discharge space of the second cover. However, in some cases, the bearing inlet groove may communicate with the discharge space of the third cover. In this case, the third cover may be formed to have an area capable of accommodating both the first cover and the second cover, but in some cases, the third cover is formed to be smaller than the first cover and the second cover, May be connected to the bearing inlet grooves.

101: inner space of casing 102: noise space
103a: Suction flow path 103b: Compression space
104a, 104b, 104c: Discharge spaces 105a, 105b, 105c:
106: connector 110: casing
120: frame 121:
122: flange portion 122b: front face of the frame
122c: outer projecting portion 122d: inner projecting portion
122e: spacing grooves 122f, 122g: first and second sealing member insertion grooves
130: Linear motor 130a:
130b: Mover 140: Compression unit
141: cylinder 141b: front face of the cylinder
142: piston 143: suction valve
144: Discharge valve assembly 160: Discharge cover assembly
161, 162, and 163: first, second, and third covers 161a, 162a, and 163a:
161a: concave portion 162a1: convex portion
161b, 162b, 163b: first, second and third fixing parts 161b1:
170: Insulation cover 170a: Second gas cylinder
V:

Claims (11)

  1. A casing having a sealed inner space;
    A linear motor provided in an inner space of the casing and reciprocating with respect to the stator;
    A compression unit arranged to be spaced apart from an inner circumferential surface of the casing, the piston connected to the mover of the linear motor reciprocating in the cylinder and forming a compression space in the cylinder;
    A gas bearing for guiding a part of the refrigerant discharged from the compression space between the cylinder and the piston to lubricate between the cylinder and the piston; And
    And at least one discharge cover coupled to the compression unit and having a discharge space for receiving the refrigerant discharged from the compression space,
    Wherein the gas bearing is communicated with a discharge space of another discharge cover excluding an discharge cover whose inlet is in contact with the compression space.
  2. The method according to claim 1,
    The first discharging space forming the first discharging space is accommodated in the second discharging space forming the second discharging space,
    And an inlet of the gas bearing communicates with the second discharge space.
  3. The method according to claim 1,
    Wherein the discharge cover comprises a plurality of discharge covers each having a discharge space and each of the discharge spaces sequentially communicating with each other,
    Wherein the plurality of discharge covers have a space portion forming each discharge space, and the space portion of the discharge cover communicating with the inlet of the gas bearing is formed into a non-circular cross-sectional shape.
  4. The method of claim 3,
    Wherein a space portion of the discharge cover communicating with an inlet of the gas bearing has a convex portion formed to protrude in a radial direction and face the inlet of the gas bearing to receive the inlet of the gas bearing.
  5. The method according to claim 1,
    Wherein the discharge cover comprises a plurality of discharge covers each having a discharge space and each of the discharge spaces sequentially communicating with each other,
    Characterized in that the plurality of discharge covers each have a space portion forming a discharge space and the space portion of the discharge cover accommodated in the space portion of the discharge cover communicating with the inlet of the gas bearing is formed into a non- compressor.
  6. 6. The method of claim 5,
    Wherein the space portion of the discharge cover accommodated in the space portion of the discharge cover communicating with the inlet of the gas bearing is recessed in the radial direction so that a recess is formed so as not to overlap with the inlet of the gas bearing.
  7. 7. The method according to any one of claims 1 to 6,
    Wherein the discharge cover in contact with the compression unit has a fixing part for covering the inlet of the gas bearing,
    Wherein the fixed portion is provided with a first gas hole communicating the discharge space and the inlet of the gas bearing.
  8. 8. The method of claim 7,
    And a heat insulating member interposed between the discharge cover and the compression unit to block transmission of heat from the discharge cover to the compression unit.
  9. 9. The method of claim 8,
    Wherein the heat insulating member is formed so as to overlap with the fixing portion, and the heat insulating member is provided with a second gas hole communicating with the first gas hole and communicating the discharge space with the inlet of the gas bearing.
  10. 10. The method of claim 9,
    A sealing member surrounding the inlet of the gas bearing is provided in the periphery of the inlet of the gas bearing,
    And the sealing member is in close contact with the heat insulating member or the fixing portion.
  11. 9. The method of claim 8,
    Wherein at least one heat insulating space portion communicating with the internal space of the casing is formed between the discharge cover and the compression unit and separated from the discharge space of the discharge cover,
    And a sealing member separating between the heat insulating space and the discharge space is provided between the compression unit and the heat insulating member.
KR1020170131609A 2017-10-11 2017-10-11 Linear compressor KR101981101B1 (en)

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KR1020170131609A KR101981101B1 (en) 2017-10-11 2017-10-11 Linear compressor
EP18199473.2A EP3470673A1 (en) 2017-10-11 2018-10-10 Linear compressor
CN201821644792.6U CN209228564U (en) 2017-10-11 2018-10-10 Linearkompressor
US16/157,825 US20190107312A1 (en) 2017-10-11 2018-10-11 Linear compressor

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060081482A (en) * 2005-01-07 2006-07-13 엘지전자 주식회사 Linear compressor
KR20140030744A (en) * 2012-09-03 2014-03-12 엘지전자 주식회사 Reciprocating compressor
KR20150040027A (en) 2013-10-04 2015-04-14 엘지전자 주식회사 A linear compressor
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor
KR20170074527A (en) * 2015-12-22 2017-06-30 엘지전자 주식회사 A linear compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060081482A (en) * 2005-01-07 2006-07-13 엘지전자 주식회사 Linear compressor
KR20140030744A (en) * 2012-09-03 2014-03-12 엘지전자 주식회사 Reciprocating compressor
KR20150040027A (en) 2013-10-04 2015-04-14 엘지전자 주식회사 A linear compressor
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor
KR20170074527A (en) * 2015-12-22 2017-06-30 엘지전자 주식회사 A linear compressor

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