KR101940489B1 - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
KR101940489B1
KR101940489B1 KR1020170125389A KR20170125389A KR101940489B1 KR 101940489 B1 KR101940489 B1 KR 101940489B1 KR 1020170125389 A KR1020170125389 A KR 1020170125389A KR 20170125389 A KR20170125389 A KR 20170125389A KR 101940489 B1 KR101940489 B1 KR 101940489B1
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KR
South Korea
Prior art keywords
cover
discharge
space
frame
casing
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Application number
KR1020170125389A
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Korean (ko)
Inventor
노기원
안광운
이종우
최기철
홍언표
Original Assignee
엘지전자 주식회사
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Priority to KR1020170125389A priority Critical patent/KR101940489B1/en
Application granted granted Critical
Publication of KR101940489B1 publication Critical patent/KR101940489B1/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
    • F04B39/0005Component 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 adaptations of pistons
    • 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
    • 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
    • F04B39/121Casings

Abstract

A linear compressor according to the present invention includes: a casing; a frame provided in an interior space of the casing; a cylinder inserted into and coupled to the frame; a piston provided in the interior of the cylinder to reciprocate; and at least one discharge cover fixed to the frame and provided with a discharge space. The discharge cover may include: a space part that forms the discharge space; a fixing part extending from the space part and fixed to the frame; and a heat radiating part spaced from the frame and extending from the fixing part, and formed to face an inner peripheral surface of the casing while having a predetermined interval from an inner peripheral surface of the casing. Accordingly, the heat radiation area of the discharge cover is expanded and the flow velocity of the refrigerant is increased as the interval between the discharge cover and the casing becomes narrower so that the heat of the discharge cover may be promptly radiated.

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.

Further, in the conventional gas lubricated linear compressor, the distance between the discharge cover and the casing is too long, so that the flow rate of the refrigerant passing between the discharge cover and the casing becomes slower than the same amount of refrigerant, The convection heat transfer coefficient for the discharge cover is lowered and the heat radiation effect for the discharge cover is further reduced as a whole. This can heat the cylinder through the frame in contact with the discharge cover, as described above, to further increase suction loss and compression loss.

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 increasing the cooling effect of the discharge cover by widening the heat radiating area of the discharge cover.

Another object of the present invention is to provide a linear compressor capable of increasing the flow velocity of the refrigerant passing between the discharge cover and the casing to increase the convective heat transfer coefficient and to quickly cool the discharge cover.

In order to achieve the object of the present invention, in a linear compressor to which a gas bearing is applied between a cylinder and a piston, a discharge cover for accommodating a discharge valve extends toward the inner circumferential surface of the casing to widen the heat radiation area for the discharge cover, A linear compressor capable of increasing the flow rate of the refrigerant in contact therewith can be provided.

Here, the heat dissipation unit may be formed parallel to the inner circumferential surface of the casing.

The outer diameter of the heat dissipation unit may be greater than or equal to the outer diameter of the frame to which the discharge cover is coupled.

Further, in order to achieve the object of the present invention, A linear motor provided in an inner space of the casing and reciprocating with respect to the stator; A frame which is provided in an inner space of the casing and supports the stator of the linear motor; A cylinder inserted into the frame and joined to form a compression space; A piston provided inside the cylinder and varying the volume of the compression space while reciprocating with the mover; And at least one discharge cover fixed to the frame and having a discharge space for receiving the refrigerant discharged from the compression space, wherein the discharge cover includes: a space portion forming the discharge space; A fixing part extending from the space part and fixed to the frame; And a heat dissipating unit having a predetermined gap between the outer circumferential surface of the casing and the inner circumferential surface of the casing, the heat dissipating unit facing the inner circumferential surface of the casing.

Here, the heat dissipation unit may be bent at least once in the fixing unit and extended along the inner circumferential surface of the casing.

At least one or more refrigerant holes may be formed along the circumferential direction of the heat dissipating unit.

The heat dissipating unit may include a first heat dissipating unit extending in a direction intersecting the radial direction of the cylinder at the fixing unit and a second heat dissipating unit extending in a direction intersecting the axial direction of the cylinder in the first heat dissipating unit Lt; / RTI >

The length of the first heat-radiating portion may be longer than the length of the second heat-radiating portion.

The outer diameter of the heat dissipation unit may be greater than or equal to the outer diameter of the frame.

The plurality of discharge covers are sequentially stacked in a direction away from the frame, and the plurality of discharge covers are stacked on the first cover in contact with the frame among the plurality of discharge covers, The heat dissipating portion may be formed.

The heat dissipation unit may be formed on the plurality of discharge covers.

The heat radiating portion of the first cover may be formed to be smaller than or equal to the heat radiating portion of the other discharge cover.

Further, in order to achieve the object of the present invention, A linear motor provided in an inner space of the casing and reciprocating with respect to the stator; A frame which is spaced apart from an inner circumferential surface of the casing and is provided in an inner space of the casing, the frame supporting the stator of the linear motor; A cylinder inserted into the frame and joined to form a compression space; A piston provided inside the cylinder and varying the volume of the compression space while reciprocating with the mover; A plurality of discharge covers fixed to the frame, spaced from an inner circumferential surface of the casing, each discharge space being provided to receive refrigerant discharged from the compression space, and each discharge space being sequentially communicated; And a gas bearing for guiding a part of the refrigerant discharged into the discharge space of the discharge cover between the cylinder and the piston to lubricate between the cylinder and the piston, wherein at least one of the plurality of discharge covers And a heat radiating portion that is bent in a direction parallel to the inner circumferential surface of the casing and extends by a predetermined height is provided on the outer circumferential surface.

Here, among the plurality of discharge covers, the outer diameter of the discharge cover in which the heat radiating portion is formed may be larger than or equal to the outer diameter of the frame.

The heat dissipation unit may have a height radially overlapping with a discharge space of another discharge cover adjacent to the discharge cover in which the heat dissipation unit is formed.

At least one or more refrigerant holes may be formed along the circumferential direction of the heat dissipating unit.

The heat dissipation unit may be formed on the plurality of discharge covers.

The discharging cover may include a second cover disposed on one side of the first cover and a third cover sequentially disposed on one side of the second cover, and the first cover may be communicated with the discharging space of the second cover, And the discharge space of the first cover and the discharge space of the second cover are communicated with each other through the communication hole, and the discharge space of the second cover and the discharge space of the third cover are communicated with each other through the communication hole As shown in Fig.

In the linear compressor according to the present invention, since the heat radiation portion is formed at the edge of the discharge cover, the heat radiation area for the discharge cover is enlarged, and the discharge cover can be quickly dissipated.

Further, since the heat radiation portion of the discharge cover is bent and extended along the inner circumferential surface of the casing, the heat radiation area of the discharge cover is enlarged while suppressing an excessive increase in the outer diameter thereof, have.

Further, since the heat radiation portion of the discharge cover extends toward the inner peripheral surface of the casing, the gap between the heat radiation portion of the discharge cover and the inner peripheral surface of the casing is narrowed to increase the flow rate of the refrigerant passing through the gap between the discharge cover and the casing. The convection heat transfer coefficient of the refrigerant can be increased to improve the heat radiation effect on the discharge cover.

In addition, by providing a heat-radiating portion on the discharge cover to increase heat radiation effect on the discharge cover, the heat of the discharge cover is prevented from being transmitted to the cylinder through the frame in contact with the discharge cover, Or by reducing the suction loss or compression loss that may occur as the compression space overheats, thereby increasing compressor efficiency.

In addition, since a plurality of refrigerant holes are formed in the heat radiating portion of the discharge cover, the refrigerant flows through the refrigerant holes, thereby reducing the flow resistance to the refrigerant. As a result, the refrigerant moves more smoothly, Can be improved.

Further, since the heat radiation portion of the discharge cover is formed in the axial direction and the radial direction, the refrigerant passing between the discharge cover and the casing forms turbulent flow while the contact between the refrigerant and the discharge cover is improved, .

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.
5 is a perspective view showing an embodiment of the first cover in the discharge cover assembly according to the present embodiment,
6 is a sectional view taken along the line "IV-IV" in Fig. 5,
FIGS. 7A and 8B are graphs showing the results of a comparison between the flow velocity and the temperature for the case where the first heat radiating portion is not formed in the first cover and the case where the first heat radiating portion is formed;
9 is a perspective view showing another embodiment of the first cover in the discharge cover assembly according to the present embodiment,
10 is a sectional view taken along the line "V-V" in Fig. 9,
11 is a perspective view showing another embodiment of the first cover in the discharge cover assembly according to the present embodiment,
12 is a sectional view taken along the line "VI-VI" in Fig. 11,
Fig. 13 and Fig. 14 are longitudinal sectional views showing other embodiments of the discharge cover assembly in the linear compressor according to Fig. 1;

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 may be inserted into the second support bracket 117e 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.

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.

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 formed separately from the bearing inlet groove 125a (Not shown), or may be formed to communicate with the bearing inlet groove 125a by radially protruding a part of the first discharge space 104a. Accordingly, the first space portion 161a and the second space portion 162a may be formed into a non-circular cross-sectional shape if necessary.

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, since the linear compressor according to the present invention has the heat radiation portion formed in the discharge cover assembly, the surface area of the discharge cover assembly can be enlarged, and the discharge cover assembly can be rapidly dissipated. In addition, by increasing the flow rate of the refrigerant by narrowing the gap between the heat dissipation unit and the casing, the convection heat transfer coefficient of the refrigerant can be increased, and the discharge cover assembly can be released more rapidly. It is possible to prevent the refrigerant sucked into the compression space or the refrigerant compressed in the compression space from being overheated, thereby preventing the suction loss or the compression loss in the compression unit from being generated.

The heat dissipating unit according to this embodiment may be formed on the first cover, the second cover, or the third cover, or may be formed on only a part of the cover. If only a part of the cover is formed with a heat dissipating part, it may be preferable to form the first cover closest to the frame and the cylinder and having the highest temperature of the refrigerant. Hereinafter, an example in which the heat radiating portion is formed only in the first cover will be described first.

5 is a perspective view showing the first cover in the discharge cover assembly according to the present embodiment, and FIG. 6 is a sectional view taken along line IV-IV in FIG. Referring to FIG. 4, the first cover 161 according to the present embodiment may include a first heat radiating portion 161c extending in the axial direction at a radial end of the first fixing portion 161b. Of course, the first heat radiating portion 161c may be formed to extend only in the radial direction from the first fixing portion 161b toward the inner peripheral surface 111a of the shell 111 without being bent in the axial direction.

In this case also, since the outer circumferential surface 160a of the first cover 161 (hereinafter, mixed with the outer circumferential surface of the discharge cover assembly) is adjacent to the inner circumferential surface 111a of the shell 111, the heat radiating effect can be enhanced. However, in this case, the thickness of the first fixing portion 161b is negligibly small compared to the thickness of the frame 120, so that the heat transfer area is very small, and the effect of releasing heat from the first cover 161 to the shell 110 It may not be big.

When the first fixing portion 161b extends only in the radial direction, the first fixing portion 161b is thin, so that it is formed between the outer peripheral surface 122a of the frame 120 and the inner peripheral surface 111a of the shell 111 Side refrigerant passage 107b formed between the outer peripheral surface 160a of the frame-side refrigerant passage 107a and the discharge cover assembly 160 and the inner peripheral surface 111a of the shell 111, Is not greatly increased. In particular, the axial length D5 of the cover-side coolant passage 107b formed around the first cover 161 of the discharge cover assembly 160, which is to be substantially radiated, does not increase significantly. Accordingly, the first fixing portion 161b does not greatly contribute to increasing the flow rate of the refrigerant in the cover side refrigerant passage 107b, but has a limitation in increasing the heat transfer effect due to the convection.

4 and 5, the first heat-radiating portion 161c in the first fixing portion 161b can enlarge the contact area between the refrigerant and the first cover 161, The heat transfer area to the cover 161 can be widened to enhance the heat radiating effect.

The cover side coolant passage 107b between the outer circumferential surface 160a of the first cover 161 and the inner circumferential surface 111a of the shell 111 becomes narrow and the flow velocity of the coolant passing through the cover side coolant passage 107b . This increases the convective heat transfer coefficient for the refrigerant passing through the cover side refrigerant passage 107b, and the heat radiation effect for the first cover 161 as a whole can be greatly improved.

 This prevents the first cover 161 heated by the refrigerant discharged into the first discharge space 104a from heating the frame 120 or the cylinder 141 while the temperature of the first cover 161 is lowered It is possible to prevent the refrigerant in the compression space 103b or the suction passage 103a from being overheated.

Here, the axial length D5 of the first heat-radiating portion 161c may be a length that overlaps with the discharge space 104b of the second cover 161 in the radial direction. However, it is preferable that the length D5 in the axial direction of the first heat-radiating portion 161c is as large as possible within a range in which the heat transfer effect is generated, because the heat transfer area can be increased.

However, if the axial length D5 of the first heat radiation portion 161c is too large, the axial length including the space between the first cover 161 and the shell 111, that is, the length D5 of the cover side refrigerant passage 107b, May be too long. Then, the flow resistance between the first cover 161 and the shell 111 may increase, and the flow velocity may be lowered.

The maximum axial length D5 of the first heat radiating portion 161c is greater than the sum of the first fixing portion 161b and the second fixing portion 162b but the total height D6 of the discharge cover assembly 160 , That is, smaller than the height from the frame 120 to the third space 163a.

The outer diameter D7 of the first heat radiating portion 161c may be the same or larger than the outer diameter D8 of the frame 120. [ However, if the outer diameter D7 of the first heat radiating portion 161c is too large, a gap (hereinafter referred to as a second gap) between the outer circumferential surface 160a of the first heat radiating portion 161c and the inner circumferential surface 111a of the shell 111 G2 are too narrow than the interval G1 between the outer peripheral surface 122a of the frame 120 and the inner peripheral surface 111a of the shell 111 (hereinafter referred to as the first gap). Accordingly, the flow path resistance to the refrigerant passing through the cover side coolant passage 107b may be excessively increased, and the flow rate of the coolant may be reduced. The outer diameter D7 of the first heat radiating portion 161c is preferably approximately the same as the outer diameter D8 of the frame 120 but may be slightly larger than the outer diameter D8 of the frame 120 .

For example, the second gap G2 may be about 2 to 3 mm. This may have a correlation with the height of the first heat radiation portion 161c described above. In other words, the second gap G2 may be slightly smaller if the axial length D5 of the first radiating portion 161c is larger. On the contrary, the axial length D5 of the first radiating portion 161c may be smaller, It is preferable that the second gap G2 is formed larger. Therefore, the axial length D5 of the first heat-radiating portion 161c is approximately 8 to 12 mm. Therefore, the second gap G2 is approximately 20 to 100 mm, more preferably 15 to 20 times the axial length D5 of the first heat- To about 30%.

5 and 6, the first heat-radiating portion 161c may be formed in a cylindrical shape clogging along the circumferential direction. In this case, as the surface area of the first heat-radiating portion 161c is enlarged, the area of contact with the refrigerant is increased to improve the heat radiation effect. Accordingly, the high-temperature refrigerant discharged into the first discharge space 104a can be rapidly transferred to the shell 111 through the first cover 161 and dissipated.

This can be confirmed through experiments. FIGS. 7A and 8B show the results of comparing the flow velocity and the temperature for the case where the first heat radiation portion is not formed on the first cover (hereinafter, case 1) and the case where the first heat radiation portion is formed Fig.

7A and 7B, the flow rates in the cover side refrigerant passage 107b formed between the inner peripheral surface 111a of the shell 111 and the outer peripheral surface 160a of the discharge cover assembly 160 are compared The case 2 (FIG. 7B) in which the first heat radiating portion 161c is formed is significantly increased as compared with the case 1 (FIG. 7A) in which the first heat radiating portion is not formed.

Generally, as the flow rate of the refrigerant increases, the convective heat transfer coefficient increases accordingly. Therefore, it can be predicted that the heat dissipation effect of the discharge cover assembly 160 as a whole can be improved as compared with the case of the case have.

This can be confirmed through FIGS. 8A and 8B. That is, in the case of the embodiment (2), the temperature of the first cover (161), particularly the temperature at the portion where the first space portion (161a) and the first fixing portion (161b) Can be seen. This is because, as described above, the heat dissipation area of the first cover 161 is larger and the refrigerant flow velocity between the first cover 161 and the shell 111 is larger than that of the case 1 Thereby decreasing the heat transferred from the discharge cover assembly 160 to the frame 120 and reducing the suction loss and the compression loss in the suction passage 103a and the compression space 103b So that the performance of the compressor as a whole can be expected to be improved.

In this way, since the heat radiation area of the discharge cover is enlarged by the heat radiation portion and the heat radiation portion is disposed so as to be close to the inner peripheral surface of the shell, the heat of the discharge cover can be quickly transmitted to the shell, so that the heat radiation effect of the discharge cover can be improved.

Further, since the heat radiating portion is formed to be close to the inner circumferential surface of the shell, the space between the discharge cover and the shell is narrowed, the flow rate of the refrigerant flowing between the discharge cover and the shell is increased and the convective heat transfer coefficient is increased. The heat dissipation effect on the discharge cover can be further improved.

Meanwhile, another embodiment of the discharge cover according to the present invention is as follows. That is, in the above-described embodiment, the first heat radiating portion is clogged, but in the present embodiment, a plurality of refrigerant holes are formed in the first heat radiating portion so that the refrigerant can pass through the first heat radiating portion.

For example, as shown in FIGS. 9 and 10, the first heat-radiating portion 161c may have at least one or more coolant through-holes 108a, preferably a plurality of coolant through-holes 108a, at regular intervals along the circumferential direction.

In this case, since a narrow space-side refrigerant passage 107b is formed with a flow space in which both refrigerants can move with respect to the first cover 161, the flow passage resistance is reduced to increase the flow rate or flow amount of the refrigerant . The heat transfer effect by convection between the first cover 161 and the casing 110 is improved so that the high temperature refrigerant discharged into the first discharge space 104a flows through the first cover 161 and the shell 111, The heat can be dissipated more quickly.

Here, it is preferable that the entire cross-sectional area of the coolant through-hole 108a is formed to be smaller than the surface area of the first heat-radiating portion 161c except for the coolant through-hole 108a because the heat radiation area can be ensured.

Further, another embodiment of the discharge cover according to the present invention is as follows. That is, in the above-described embodiments, the first heat-radiating portion is formed by bending the first fixing portion in one step, but the present embodiment forms the second heat-radiating portion by bending in the radial direction in the first heat- The second heat radiation portion may be bent in a direction toward the shell, but may be bent in a direction away from the shell. 11 and 12 are views showing an example in which the second heat radiation portion is bent in a direction toward the shell.

As shown in these drawings, the second heat-radiating portion 161d may be further extended and bent at the end of the first heat-radiating portion 161c. The heat transfer area for transferring the heat from the discharge cover 161 to the shell 111 is further enlarged and the second gap G2 between the shell 111 and the first cover 161 is further narrowed, By increasing the flow velocity, the heat radiation effect on the discharge cover as a whole can be further enhanced.

The second heat dissipation unit 161d may be bent toward the inner circumferential surface 111a of the shell 111 as described above, but may be bent in a direction away from the inner circumferential surface 111a of the shell 111, .

That is, as the second heat-radiating portion 161d is located as close as possible to the inner circumferential surface 111a of the shell 111, the second heat-radiating portion 161d is spaced apart from the shell 111 in the direction toward the shell 111 It may be absent. In consideration of this, the second heat-radiating portion 161d may be formed in a direction away from the inner circumferential surface 111a of the shell 111. [ In this case, the radial length D9 of the second heat radiating portion 161d is a length that does not interfere with the second cover 162 or the third cover 163, for example, the axial length D5 of the first heat radiating portion, It may be desirable to be formed smaller.

When the second heat dissipation part 161d is formed in a direction toward the inner circumferential surface 111a of the shell 111, the second gap G2 formed between the first cover 161 and the shell 111 may be formed to be more The convection heat transfer effect can be enhanced by increasing the flow rate of the refrigerant.

In addition to the possibility that the refrigerant contacts the first cover 161 by the second heat-radiating portion 161d, the heat transfer effect due to the convection may be improved while the fluid forms turbulence.

Meanwhile, another embodiment of the discharge cover assembly in the linear compressor according to the present embodiment is as follows. That is, in the above-described embodiments, the heat radiating portion is formed only in the first cover, but the heat radiating portion is also formed in the second cover 162 or the third cover 163 in this embodiment as shown in Figs. 13 and 14 .

First heat radiating portion 162c may be formed only in the second cover 162 but may be formed in both the first cover 161 and the second cover 162. In this case, And one heat-radiating portion 161c and 162c, respectively.

This is because the temperature of the refrigerant discharged to the first discharge space 104a of the first cover 161 is the highest, so that when the first heat radiation portion 162c is formed on the second cover 162, The heat radiation effect can be further enhanced by forming the first heat radiation portion 161c. Therefore, it is preferable that the first heat radiating portions 161c and 162c are formed by bending the first cover 161 and the second cover 162 in the axial direction, respectively.

13, the first heat radiating portion 161c of the first cover 161 and the first heat radiating portion 162c of the second cover 162 are spaced apart from each other by a predetermined distance, 162c and the refrigerant.

However, when the gap G3 between the first heat radiation portion 161c of the first cover 161 and the first heat radiation portion 162c of the second cover 162 is narrow, the two heat radiation portions 161c and 162c, May be brought into contact with each other. In this case, as the first heat radiating portions 161c and 162c of the first cover 161 and the second cover 162 are in contact with each other, the passage through which heat is transmitted is widened to improve the heat radiation effect .

The height D52 of the first heat radiation portion of the second cover 162 may be formed to be much higher than the height D5 of the first heat radiation portion of the first cover 161. [ In this case, the refrigerant passage holes 108a and 108b can be formed in the first heat radiating portion 162c of the second cover 162 as well as the first heat radiating portion 161c of the first cover 161, The refrigerant passage hole 108b formed in the first heat radiation portion 162c of the cover 162 is formed to have a larger sectional area than the refrigerant passage hole 108a formed in the first heat radiation portion 161c of the first cover 161 . Accordingly, the coolant can smoothly move while forming the first heat-radiating portion 162c of the second cover 162. [

The second heat radiating portion 162d may also be formed in the second cover 162 as in the case of forming the second heat radiating portion 161d in the first cover 161. [ The second heat-radiating portion 161d of the first cover 161 and the second heat-radiating portion 162d of the second cover 162 may be bent in the same direction or in opposite directions.

As described above, the second heat-radiating portion 161d of the first cover 161 and the second heat-radiating portion 162d of the second cover 162 may be formed with a sufficient distance therebetween. However, in some cases, the second heat-radiating portion 161d of the first cover 161 and the second heat-radiating portion 162d of the second cover 162 may be disposed in proximity to each other or may be in contact with each other.

In this case, the first heat radiation portion 161c of the first cover 161 and the first heat radiation portion 162c of the second cover 162 are disposed so as to be in proximity to or in contact with each other, The flow rate of the refrigerant can be increased by minimizing the stagnation between the first cover 162 and the second cover 162.

14, the first cover 163c may be formed on the third cover 163, or the first and second heat dissipation units 163c and 163d may be formed together. In this case, the first heat dissipating unit 163c and the second heat dissipating unit 163d are similar to the first heat dissipating unit 161c and the second heat dissipating unit 161d of the first cover 161 described above, Is omitted.

However, since the heat radiating portions 163c and 163d are formed in the third cover 163, the heat transmitted to the third cover 163 can be quickly dissipated. Accordingly, the temperature of the entire discharge cover assembly is lowered to minimize the transfer of heat to the frame or the cylinder by the discharged refrigerant, thereby further enhancing the performance of the compressor more effectively.

100: Linear compressor 101: Suction space
102: Suction flow path 103: Compression space
104a, 104b, 104c: Discharge spaces 105a, 105b, 105c:
106: Connector 107: Refrigerant passage
108a, 108b, and 108c: a coolant passage hole 110:
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
146a, 147a, 148a: Space part 146b, 147b, 148b:
146c, 147c, 148c: first heat-radiating portions 146a, 147a, 148a: second heat-
G1: Frame and shell spacing G2: Cover and shell spacing

Claims (15)

  1. Casing;
    A linear motor provided in an inner space of the casing and reciprocating with respect to the stator;
    A frame which is provided in an inner space of the casing and supports the stator of the linear motor;
    A cylinder inserted into the frame and joined to form a compression space;
    A piston provided inside the cylinder and varying the volume of the compression space while reciprocating with the mover; And
    And at least one discharge cover fixed to the frame and having a discharge space for receiving the refrigerant discharged from the compression space,
    A space portion forming the discharge space;
    A fixing part extending from the space part and fixed to the frame; And
    And a heat radiating portion which is spaced apart from the frame and extends from the fixing portion and is formed to face the inner circumferential surface of the casing with a predetermined gap between the inner circumferential surface and the inner circumferential surface of the casing.
  2. The method according to claim 1,
    Wherein the heat radiating portion is bent at least once in the fixing portion and extended along the casing.
  3. 3. The method of claim 2,
    Wherein at least one or more refrigerant holes are formed along the circumferential direction of the heat dissipating unit.
  4. The method according to claim 1,
    The heat dissipating portion may include a first heat dissipating portion extending in a direction intersecting the radial direction of the cylinder at the fixing portion and a second heat dissipating portion extending in a direction intersecting the axial direction of the cylinder in the first heat dissipating portion Features a linear compressor.
  5. 5. The method of claim 4,
    Wherein a length of the first heat-radiating portion is longer than a length of the second heat-radiating portion.
  6. The method according to claim 1,
    Wherein an outer diameter of the heat radiating portion is formed to be equal to or larger than an outer diameter of the frame.
  7. 7. The method according to any one of claims 1 to 6,
    Wherein the discharge covers are formed of a plurality of discharge spaces each having a respective discharge space, the plurality of discharge covers are sequentially stacked in a direction away from the frame,
    Wherein the heat radiating portion is formed on a first cover which contacts the frame among the plurality of discharge covers.
  8. 8. The method of claim 7,
    And the radiator is formed on the plurality of discharge covers.
  9. 9. The method of claim 8,
    And the heat radiating portion of the first cover is formed to be smaller than or equal to the heat radiating portion of the other discharge cover.
  10. Casing;
    A linear motor provided in an inner space of the casing and reciprocating with respect to the stator;
    A frame which is spaced apart from an inner circumferential surface of the casing and is provided in an inner space of the casing, the frame supporting the stator of the linear motor;
    A cylinder inserted into the frame and joined to form a compression space;
    A piston provided inside the cylinder and varying the volume of the compression space while reciprocating with the mover;
    A plurality of discharge covers fixed to the frame, spaced from an inner circumferential surface of the casing, each discharge space being provided to receive refrigerant discharged from the compression space, and each discharge space being sequentially communicated; And
    And a gas bearing for guiding a part of the refrigerant discharged to the discharge space of the discharge cover between the cylinder and the piston to lubricate between the cylinder and the piston,
    Wherein at least one discharge cover among the plurality of discharge covers is provided with a heat radiating portion that is bent in a direction parallel to an inner peripheral surface of the casing and extended by a predetermined height from an outer peripheral surface of the discharge cover.
  11. 11. The method of claim 10,
    Wherein an outer diameter of the discharge cover in which the heat radiating portion is formed is formed to be larger than or equal to an outer diameter of the frame.
  12. 11. The method of claim 10,
    Wherein the heat dissipating unit is formed to have a height that radially overlaps a discharge space of another discharge cover adjacent to the discharge cover in which the heat dissipating unit is formed.
  13. 11. The method of claim 10,
    Wherein at least one or more refrigerant holes are formed along the circumferential direction of the heat dissipating unit.
  14. 11. The method of claim 10,
    Wherein the heat radiating portion is formed in each of the plurality of discharge covers.
  15. 11. The method of claim 10,
    Wherein the discharge cover has a second cover disposed on one side of the first cover and a third cover sequentially disposed on one side of the second cover,
    A communication hole is formed in the first cover so as to be accommodated in the discharge space of the second cover, the discharge space of the first cover and the discharge space of the second cover communicate with each other through the communication hole,
    And the discharge space of the second cover and the discharge space of the third cover communicate with a connection pipe disposed outside the second cover.
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20000031925A (en) * 1998-11-11 2000-06-05 구자홍 Structure for emitting heat of venting cover in linear compressor
KR20060081482A (en) * 2005-01-07 2006-07-13 엘지전자 주식회사 Linear 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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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20000031925A (en) * 1998-11-11 2000-06-05 구자홍 Structure for emitting heat of venting cover in linear compressor
KR20060081482A (en) * 2005-01-07 2006-07-13 엘지전자 주식회사 Linear 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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