KR20190032885A - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
KR20190032885A
KR20190032885A KR1020170121275A KR20170121275A KR20190032885A KR 20190032885 A KR20190032885 A KR 20190032885A KR 1020170121275 A KR1020170121275 A KR 1020170121275A KR 20170121275 A KR20170121275 A KR 20170121275A KR 20190032885 A KR20190032885 A KR 20190032885A
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South Korea
Prior art keywords
space
flapping
compressor
refrigerant
discharge
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KR1020170121275A
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Korean (ko)
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KR101981099B1 (en
Inventor
최기철
홍언표
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엘지전자 주식회사
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Priority to KR1020170121275A priority Critical patent/KR101981099B1/en
Publication of KR20190032885A publication Critical patent/KR20190032885A/en
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Publication of KR101981099B1 publication Critical patent/KR101981099B1/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
    • F04B39/023Hermetic 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
    • F04B39/12Casings; Cylinders; Cylinder heads; Fluid connections

Abstract

A linear compressor according to the present invention includes: a casing having a sealed inner space; A compressor body provided in an inner space of the casing, the piston body being coupled to a moving member reciprocating with respect to the stator, the piston reciprocating with respect to the cylinder to compress the refrigerant; And a flapping member provided in the vibration direction of the compressor body and moving together with the compressor body to facilitate the flow of the surrounding refrigerant. Accordingly, the flow of the coolant inside the casing becomes active, and the compressor can be quickly dissipated.

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.

In the conventional gas lubricated linear compressor, the refrigerant compressed in the compression space of the cylinder is discharged to the discharge space of the discharge cover to heat the discharge cover. However, the heat radiation area of the discharge cover is small, . This can heat the cylinder through the frame in contact with the discharge cover to increase the suction loss or the compression loss as described above.

In addition, the conventional gas-lubricated linear compressor has a problem that the internal space of the casing is narrow and the refrigerant can not circulate smoothly in the internal space of the casing, thereby raising the temperature inside the casing.

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 rapidly cooling a discharge cover for containing refrigerant discharged in a compression space and preventing the cylinder from overheating through a frame in contact with the discharge cover.

Another object of the present invention is to provide a linear compressor capable of reducing the temperature of the entire compressor by promoting the flow of refrigerant in the internal space of the casing.

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, a linear compressor in which a flapping member vibrating together with the compressor body in the casing is installed outside the compressor body may be provided have.

Here, the flapping member may be provided on one side in the vibration direction of the compressor body.

Further, the flapping member may be formed in a disc shape in which the center portion is fixed.

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 compressor body provided in an inner space of the casing, the piston body being coupled to a moving member reciprocating with respect to the stator, the piston reciprocating with respect to the cylinder to compress the refrigerant; And a flapping member provided in the vibration direction of the compressor body and moving together with the compressor body to promote the flow of the surrounding refrigerant.

Here, the flapping member may be coupled to one side in the vibration direction of the compressor body.

The compressor body may further include at least one discharge cover having a discharge space for receiving the refrigerant discharged from the cylinder, and the flapping member may be provided to contact one side of the discharge cover.

The discharge cover may be provided with a guide member extending in a vibration direction of the compressor body, and the flapping member may be inserted into the guide member and coupled thereto.

At least one of both sides of the vibration direction of the compressor body is coupled with a leaf spring, and the leaf spring can be coupled to the guide member.

The guide member may be coupled with a compression coil spring supported on an inner circumferential surface of the casing, and the flapping member may be provided between the compression coil spring and the discharge cover.

The flapping member may be formed in a disc shape having at least one slit.

A plurality of the slits may be formed, and the plurality of slits may be formed so that neighboring slits overlap radially.

At least one slit of the slit may be formed in a radial direction.

The flapping member may be formed to have the same frequency as the operation frequency of the compressor body.

The flapping member may include a position fixing part formed at the center and fixed to the compressor body; An elastic part extending in the radial direction at the position fixing part and having a predetermined elasticity; And a swing plate portion extending in the radial direction at the elastic portion and formed at the rim portion and causing the elastic portion to swing relative to the position fixing portion to flow the refrigerant.

The compressor may further include a gas bearing for guiding a part of the refrigerant compressed in the compressor body between the cylinder and the piston, and lubricating the space between the cylinder and the piston with the refrigerant.

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; At least one discharge cover spaced from an inner circumferential surface of the casing and coupled to the compression unit, the discharge space being provided with a discharge space for receiving the refrigerant discharged from the compression space; And a flapping member provided between one axial side of the discharge cover and an inner surface of the casing facing the axial end of the discharge cover, the flapping member vibrating together with the compression unit to promote the flow of the surrounding refrigerant have.

The flapper may be formed in a circular plate shape. The center portion may be fixed to the guide member. The edge portion may be maintained in a free state. have.

Further, the flapping member may be formed in a disc shape, the rim portion may be fixed to the discharge cover, and the central portion may be kept free.

Since the linear compressor according to the present invention is provided with the flapping member for promoting the flow of the refrigerant while vibrating together with the compressor body, the refrigerant in the casing is actively moved to improve the heat radiation effect on the entire compressor including the discharge cover have.

Further, since the flapping member is fixed to the member to be coupled to the discharge cover, the refrigerant flow around the discharge cover can be actively activated, so that the discharge cover is quickly discharged, and the heat of the discharge cover is transferred to the compression unit Can be minimized.

In addition, as the frapping member promotes the flow of the refrigerant filled in the inner space of the casing, the flow rate of the refrigerant circulating in the casing is increased, thereby increasing the convective heat transfer coefficient of the refrigerant and improving the heat radiation effect for the compressor .

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 a state in which the discharge cover assembly according to FIG.
Fig. 5 is a front view showing a discharge cover assembly including a flapping member in the linear compressor according to Fig. 1, Fig.
Figs. 6A and 6B are respectively a front view and a rear view of the flapping member according to Fig. 5,
Figs. 7A and 7B are cross-sectional views taken along the line "IV-IV" in Fig. 6B, showing embodiments of the swing plate portion of the flapping member,
FIG. 8 is a longitudinal sectional view for explaining the operation of the flapping member according to FIG. 1,
FIG. 9 is a front view showing another embodiment of the flapping member according to FIG. 1;
10 and 11 are longitudinal sectional views showing other embodiments of a method for fixing the flapping member according to FIG. 1,
12 is a longitudinal sectional view showing another embodiment of the linear compressor according to the present invention,

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. A gasket 165 for heat insulation and an O-ring 166 for suppressing leakage of the refrigerant in the first discharge space 104a may be provided between the discharge cover assembly 160 and 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.

However, 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. This is because when the second space portion 162a is completely accommodated in the third space portion 163a, the third space portion 163a is formed too large to enlarge the discharge cover assembly 160, 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.

The inner diameter D11 of the first space 161a may be larger than the inner diameter D2 of the cylinder 141. In addition, the first space portion 161a may be formed to have a width enough to receive the bearing inlet groove 125a forming the inlet of the gas bearing described above.

Of course, even if the inner diameter D11 of the first space portion 161a is formed to be small enough to accommodate the inlet of the gas bearing, the first discharge space 104a may be separated from the bearing inlet groove 125a Or a part of the first discharge space 104a may be formed to communicate with the bearing inlet groove 125a by radially protruding a part of the first discharge space 104a. The second space portion 162a and the second space portion 162a may also be formed into a non-circular cross-sectional shape as needed.

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 of overlapping each other, The first cover 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.

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 in a straight line 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.

A part of the refrigerant discharged into the first discharge space 104a flows into the bearing hole 125a of the cylinder 141 through the bearing inlet hole 125a and the bearing communicating hole 125b and the bearing communicating groove 125c of the gas bearing, 141a to the outer peripheral surface of the piston 142 to support the piston 142 with respect to the cylinder 141. [ On the other hand, the remaining refrigerant moves to the second discharge space 104b through the first communication hole 105a, and then flows through the second communication hole 105b, the connection pipe 106, and the third communication hole 105c 3, the noise is attenuated while moving to the discharge space 104c. The refrigerant moving 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.

At this time, 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 and the piston. However, when the oil bearing is excluded and the gas bearing is applied As the high-temperature refrigerant flows into the space between the cylinder and the piston, the temperature of the compressed portion further rises and the temperature rise of the refrigerant described above can be further increased.

Further, since the temperature of the discharge cover assembly is maintained at a high temperature of about 70 캜 by the refrigerant discharged from the compression space to the discharge cover assembly, the refrigerant is discharged to the discharge side of the cylinder, which is in contact with the refrigerant held in the discharge cover assembly, The temperature of the liquid also increases. Then, the temperature of the refrigerant described above may further rise, and the compressor efficiency may be lowered.

Accordingly, it is an object of the present invention to provide a discharge cover assembly that can quickly dissipate heat from the discharge cover assembly, prevent the heat from being transmitted from the discharge cover assembly to the compression unit during operation of the compressor, And to provide a linear compressor.

To this end, the present embodiment can provide a flapping member around the discharge cover assembly to facilitate the flow of the refrigerant, so that the refrigerant quickly dissipates the discharge cover assembly.

Referring to FIGS. 1 to 4, the flapping member 170 according to the present embodiment may be provided to face the front surface of the third cover 163 forming the outermost surface of the discharge cover assembly 160. The flapping member 170 may be inserted and coupled to a support guide 117b coupled to the third cover 163. The flapping member 170 is coupled between the discharge cover assembly 160 and the second support spring 117 so that the compressor body C vibrates together when the compressor body C vibrates, The flow of the refrigerant circulating in the space 101 can be promoted.

5 to 7B, the flapping member 170 is formed in a circular plate shape, and a center portion thereof is formed with a position fixing portion 171 so as to be fixed to the support guide 117b. In the position fixing portion 171, The fixing hole 171a may be formed to penetrate through the through hole 171b.

Since the entire thickness of the flapping member 170 is formed to be the same, the fixing hole 171a may be formed as a simple through hole. However, since the flapping member 170 itself is formed of a thin steel plate, when the position fixing portion 171 is formed only by the fixing hole 171a, the coupling force to the support guide 117b may be weakened or the third cover 163 may be damaged. The flapping effect may be limited. Therefore, as shown in FIG. 7A, the position fixing portion 171 may further include a boss portion 171b extending in the axial direction in the fixing hole 171a. The boss portion 171b may be formed in the shape of a kind of burr.

Accordingly, even when the flapping member 170 is press-fitted into the support guide 117b, the fixed area can be enlarged and stably fixed. Even if the flapping member 170 is engaged with the rear end of the support guide 117b on the discharge cover side, the boss portion 171b So that a sufficient space can be secured such that the later described swing plate portion 173 of the flapping member 170 to be returned can smoothly perform the swing motion.

An elastic portion 172 extending from the position fixing portion 171 and increasing the elastic modulus of the flapping member 170 may be formed at a radially intermediate position of the flapping member 170.

The elastic portion 172 may be formed as a slit as shown in Figs. 6A and 6B. For example, the elastic portion 172 may be formed such that a plurality of slits 172a are respectively formed in an arc shape and radially overlap each other by a predetermined length along the circumferential direction. As a result, the cross-sectional area of the connecting portion 172b remaining between the plurality of slits 172a is narrowed to form the elastic portion 172. [ Although not shown in the drawings, the slits 172a may be formed in a radial direction or in an oblique direction.

A swing plate portion 173 extending from the elastic portion 172 may be formed at the rim of the flapping member 170.

The swing plate portion 173 may be formed in an annular disc shape. Further, the swing plate portion 173 can increase the flow amount of the refrigerant, which is large enough to allow swinging movement. Therefore, the outer diameter of the swing plate portion 173 can be advantageously increased as long as the outer diameter of the swing plate portion 173 does not interfere with surrounding components. For example, the outer diameter of the swing plate portion 173 may be formed so as not to interfere with the loop pipe 115a or the coupling pipe 106 as shown in FIG.

However, the outer diameter of the swing plate portion 173 can be adjusted by the loop pipe 115a or the connecting pipe 106 when the flapping member 170 is located on the front side of the loop pipe 115a or the connecting pipe 106 But may not be limited.

Although not shown in the drawing, the swing plate portion 173 may be thicker than the position fixing portion 171 or the elastic portion 172, depending on the case. Accordingly, even when the width of the swing plate portion 173 (or the outer diameter of the swing plate portion) is small, the elastic coefficient of the elastic portion 172 can be increased to amplify the swing motion of the flapping member 170.

Here, the swing motion can be amplified by increasing the weight of the swing plate 173 while maintaining the same width or outer diameter of the swing plate 18 '. For example, as shown in FIG. 7B, the swing plate portion 173 may be folded a plurality of times to form a bent portion 173a, thereby increasing the weight while maintaining the same outer diameter of the swing plate portion 173.

Meanwhile, it is preferable that the flapping member 170 according to the present embodiment is formed to have the same frequency as the operation frequency of the compressor main body C. Accordingly, the flapping member 170 is resonated with the compressor main body C, and the vibration is amplified to further enhance the flapping effect.

The above-described linear compressor according to the present invention has the following operational effects.

That is, since the compressor main body C including the linear motor 130 and the compression unit 140 is elastically supported on the casing 110 by the plurality of support springs 116 and 117, The compressor body C vibrates with respect to the casing 110 during the reciprocating movement of the piston 142 of the compression unit 140 connected to the muffler 133 and the muvers 133 thereof.

8, the flapping member 170 vibrates together with the compressor main body C so that the swing plate portion 173 of the flapping member 170 flaps in the front-rear direction by the elastic portion 172 This causes a swing motion, which causes a forced flow effect on the refrigerant in the inner space 101 of the casing 110. [

The flow of the refrigerant in the inner space 101 of the casing 110 is promoted by the flapping member 170 to increase the convective heat transfer coefficient and heat generated in the compressor main body C is transmitted to the casing 110 ). ≪ / RTI > Particularly, since the heat of the discharge cover assembly 160 quickly dissipates and the temperature of the discharge cover assembly 160 is prevented from being transmitted to the frame 120 and the cylinder 141, the compression space 103b or the suction passage 103a Can be prevented from being overheated and the compressor efficiency can be improved.

In addition, the refrigerant filled in the internal space of the casing is actively flowed by the flapping member 170, and the low-temperature refrigerant effectively contacts the compressor body C, so that the heat radiation effect on the entire compressor can be improved .

Meanwhile, another embodiment of the flapping member according to the present invention is as follows. That is, in the above-described embodiment, the slit is formed in the middle portion of the flapping member, but in this embodiment, the slit is formed in the radial direction on the outer peripheral surface of the flapping member.

9, the slit 173b according to the present embodiment is divided into a predetermined depth in the radial direction from the outer circumferential surface of the swing plate portion 173 constituting the flapping member 170 toward the position fixing portion 171 . Although only one slit 173b may be formed, a plurality of slits 173b may be formed at equal intervals in the circumferential direction.

In this case, the elastic portion 172 may be omitted in consideration of the outer diameter of the flapping member 170, and in some cases, an elastic portion may be provided as in the above-described embodiment.

When the slit 173b is formed in the radial direction from the outer circumferential surface to the inner circumferential surface as described above, the number of the swing plate portions 173 may be divided by the number of the slits 173b. Accordingly, even when the outer diameter of the swing plate portion 173 is small, the elastic coefficient of each swing plate portion 173 is improved and the movement of the swing plate portion 173 is promoted as the swing plate portion 173 is slightly broken have.

In the meantime, as described above, the fixing hole 171a constituting the position fixing portion 171 can be press-fitted into the support guide 117b. However, in this case, the flapping member 170 may not be firmly fixed to the support guide 117b due to a machining error or the like. In view of this, as shown in Fig. 10, the support surface 117b1 may be stepped on the support guide 117b to support one end of the flapping member 170 in the axial direction. The support surface 117b1 may be formed on the rear end side inserted into the third cover 163 in consideration of the fact that the end surface of the boss portion 171b is brought into close contact with the front surface of the third cover 163. [

Meanwhile, another embodiment of the flapping member according to the present invention is as follows. That is, in the above-described embodiment, the position fixing portion is formed at the central portion of the flapping member. In this embodiment, however, the position fixing portion is formed at the edge portion of the flapping member.

For example, as shown in FIG. 11, the flapping member 170 may be fixed to the discharge cover assembly 160 with a rim portion of the rear surface facing the discharge cover assembly 160. To this end, a plurality of support protrusions 175 extending in the axial direction are formed on the front surface of the discharge cover assembly 160, and a rim of the flapping member 170 may be bolted to the support protrusion 175. The support protrusion 175 may be fixed to the front surface of the third cover 163 constituting the discharge cover assembly 160 by welding.

The rim portion of the flapping member 170 forms the position fixing portion 171 and the central portion of the flapping member 170 forms the flow plate portion 173. [

A through hole 170a through which the support guide 117b is inserted is formed at the center of the flapping member 170. The inner diameter of the through hole 170a may be larger than the outer diameter of the support guide 117b. Accordingly, the central portion of the flapping member 170 forms the free end and forms the swing plate portion 173.

The basic structure of the flapping member according to the present embodiment as described above and the operation and effect of the flapping member according to the present embodiment can be formed similarly to the above-described embodiment. Therefore, detailed description thereof will be omitted. However, in the present embodiment, since the edge portion fixing portion 171 is formed at the edge portion and the flow plate portion 173 is formed at the center portion, the possibility that the flow plate portion 173 is interfered with peripheral components can be reduced. In addition, since the flow plate portion 173 is formed at the center portion, the refrigerant flow velocity in the vicinity of the discharge cover assembly 160 is increased, thereby enhancing the heat radiating effect for the discharge cover assembly.

Meanwhile, another embodiment of the linear compressor according to the present invention is as follows. That is, in the above-described embodiment, the support springs made of leaf springs are coupled to both sides of the compressor body. However, in this embodiment, at least one of the support springs is provided with a compression coil spring.

For example, as shown in FIG. 12, the second support spring 217 for supporting the front side of the compressor main body C may be provided with a plurality of compression coil springs. One end of the second support spring 217 is fixed to the inner circumferential surface of the shell 111 and the other end of the second support spring 217 is inserted into the spring groove 117b2 provided on the outer circumferential surface of the support guide 117b, Can be fixed.

One end of the support guide 117b is inserted and fixed to the front surface of the third cover 163 and the other end of the support guide 117b is provided at the center of the second shell cover 113 And can be inserted and supported in the guide groove 113b. The guide groove 113b serves as a stopper for preventing the compressor main body C from being shaken during operation of the compressor by inserting the support guide 117b.

The gap G1 between the outer circumferential surface of the support guide 117b and the inner circumferential surface of the guide groove 113b is set to a radius that can slide in the axial direction in a state where the support guide 117b is inserted into the guide groove 113b Directional spacing.

The gap G2 between the front surface of the support guide 117b and the inner surface of the guide groove 113b is set such that the support guide 117b can reciprocate in the axial direction together with the compressor main body C May be formed to have an axial gap.

Further, a flapping member 170 may be provided between the discharge valve assembly 160 and the second shell cover 113. The flapping member 170 may be coupled to an end or an intermediate portion of the support guide 117b. The flapping member 170 may be press-fitted into the support guide 117b or fastened with bolts or the like as described in the above-described embodiments.

The basic structure and operation effects of the flapping member according to the present embodiment as described above are similar to those of the above-described embodiment, and thus description thereof will be substituted for the above-described embodiments. However, in the case where the second support spring 217 disposed at least on the front side as in the present embodiment is constituted by a coil spring, as in the above-described embodiments, the second support spring 217 is formed of a leaf spring A large space can be secured. This reduces the possibility that the flapping member 170 is interfered with peripheral components when the flapping member 170 is oscillated, and the outer diameter of the flapping member 170 can be enlarged. Accordingly, the size of the flapping member 170 can be increased to more actively promote the flow of the refrigerant, thereby further enhancing the heat dissipation effect of the compressor.

100: Linear compressor 101: Suction space
102: Suction flow path 103: Compression space
104a, 104b, 104c: Discharge spaces 105a, 105b, 105c:
106: connector 110: casing
120: frame 121:
122: flange portion 130: linear motor
130a: stator 130b:
131: outer stator 132: inner stator
133b: magnet 140: compression unit
141: cylinder 142: piston
143: Suction valve 144: Discharge valve assembly
145: discharge cover assembly 146, 147, 148: first, second, and third cover
170: flapping member 171:
172: elastic portion 173:

Claims (15)

  1. A casing having a sealed inner space;
    A compressor body provided in an inner space of the casing, the piston body being coupled to a moving member reciprocating with respect to the stator, the piston reciprocating with respect to the cylinder to compress the refrigerant; And
    And a flapping member provided in the vibration direction of the compressor body and moving together with the compressor body to facilitate the flow of the surrounding refrigerant.
  2. The method according to claim 1,
    Wherein the flapping member is coupled to one side of the compressor body in the vibration direction.
  3. 3. The method of claim 2,
    The compressor body further includes at least one discharge cover having a discharge space for receiving the refrigerant discharged from the cylinder,
    And the flapping member is provided so as to abut on one side of the discharge cover.
  4. The method of claim 3,
    Wherein the discharge cover is provided with a guide member extending in a vibration direction of the compressor body,
    And the flapping member is inserted and coupled to the guide member.
  5. 5. The method of claim 4,
    Wherein at least one of both sides of the vibrating direction of the compressor body is coupled with a leaf spring,
    And the leaf spring is coupled to the guide member.
  6. 5. The method of claim 4,
    A compression coil spring supported on an inner circumferential surface of the casing is coupled to the guide member,
    And the flapping member is provided between the compression coil spring and the discharge cover.
  7. The method according to claim 1,
    Wherein the flapping member is formed in a disc shape having at least one slit.
  8. 8. The method of claim 7,
    Wherein a plurality of the slits are formed, and the plurality of slits are formed so that neighboring slits overlap in a radial direction.
  9. 8. The method of claim 7,
    Wherein at least one of the slits is formed in a radial direction.
  10. The method according to claim 1,
    Wherein the flapping member is formed to have the same frequency as the operating frequency of the compressor body.
  11. The method of claim 1, wherein the flapping member comprises:
    A position fixing part formed at a center part and fixed to the compressor main body;
    An elastic part extending in the radial direction at the position fixing part and having a predetermined elasticity; And
    And a swing plate portion extending in the radial direction at the elastic portion and formed at a rim portion and causing the elastic portion to swing relative to the position fixing portion to flow the refrigerant.
  12. 12. The method according to any one of claims 1 to 11,
    Further comprising a gas bearing for guiding a part of the refrigerant compressed in the compressor body between the cylinder and the piston to lubricate between the cylinder and the piston as refrigerant.
  13. 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;
    At least one discharge cover spaced from an inner circumferential surface of the casing and coupled to the compression unit, the discharge space being provided with a discharge space for receiving the refrigerant discharged from the compression space; And
    And a flapping member provided between one axial side of the discharge cover and an inner side of the casing facing the axial direction, the flapping member vibrating together with the compression unit to promote the flow of the surrounding refrigerant.
  14. 14. The method of claim 13,
    Further comprising a guide member extending axially from one side of the discharge cover,
    Wherein the flapping member is formed in a disc shape so that a central portion thereof is fixed to the guide member, and a rim portion thereof is held in a free state.
  15. 14. The method of claim 13,
    Wherein the flapping member is formed in a disc shape, the rim portion is fixed to the discharge cover, and the central portion is held in a free state.
KR1020170121275A 2017-09-20 2017-09-20 Linear compressor KR101981099B1 (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20010109542A (en) * 2000-05-29 2001-12-12 구자홍 Structure for reducing windage loss of linear compressor
KR20150031726A (en) * 2013-09-16 2015-03-25 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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20010109542A (en) * 2000-05-29 2001-12-12 구자홍 Structure for reducing windage loss of linear compressor
KR20150031726A (en) * 2013-09-16 2015-03-25 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

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