KR20190034996A - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
KR20190034996A
KR20190034996A KR1020170123683A KR20170123683A KR20190034996A KR 20190034996 A KR20190034996 A KR 20190034996A KR 1020170123683 A KR1020170123683 A KR 1020170123683A KR 20170123683 A KR20170123683 A KR 20170123683A KR 20190034996 A KR20190034996 A KR 20190034996A
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KR
South Korea
Prior art keywords
guide
space
circumferential
casing
discharge
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KR1020170123683A
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Korean (ko)
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KR101981100B1 (en
Inventor
안광운
노기원
이경민
최기철
홍언표
Original Assignee
엘지전자 주식회사
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Priority to KR1020170123683A priority Critical patent/KR101981100B1/en
Publication of KR20190034996A publication Critical patent/KR20190034996A/en
Application granted granted Critical
Publication of KR101981100B1 publication Critical patent/KR101981100B1/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
    • F04B39/0027Pulsation and noise damping means
    • 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
    • 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
    • F04B39/14Provisions for readily assembling or disassembling

Abstract

A linear compressor according to the present invention includes: a casing; A linear motor in which the mover reciprocates with respect to the stator; A frame for supporting the stator of the linear motor; A cylinder defining a compression space; A piston which varies the volume of the compression space while reciprocating with the move- ment; At least one discharge cover having a discharge space for receiving the refrigerant discharged from the compression space; And a guide member protruding from the casing toward the discharge cover by a predetermined height or being recessed toward the inner circumferential surface of the casing to reduce a radial distance between the outer circumferential surface of the discharge cover and the inner circumferential surface of the casing.

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.

In the conventional gas lubricated linear compressor, the compressor main body is resiliently supported inside the casing, but the main body of the compressor may collide with the casing and be damaged when the compressor is transported. Accordingly, there is a problem that the stopper for restricting the movement of the compressor main body is installed inside the casing, which increases the material cost and complicates the assembling process.

In addition, the conventional gas-lubricated linear compressor has a problem that the noise generated by the compressor main body can not be effectively removed due to the small internal space of the casing, resulting in an increase in compressor noise.

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 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.

Another object of the present invention is to provide a linear compressor capable of easily forming a stopper for preventing a collision between a compressor main body and a casing in a state in which the compressor main body is resiliently supported on the casing, I am trying to provide.

Another object of the present invention is to provide a linear compressor in which noise generated in a compressor main body can be effectively reduced while achieving miniaturization.

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 guide member protruding from the inner peripheral surface of the casing toward the discharge cover or from the discharge cover toward the inner peripheral surface of the casing is provided, A linear compressor capable of increasing the flow rate of the refrigerant in contact with the cover can be provided.

Here, the guide member may be formed in an annular shape, and may be fixedly coupled to the inner circumferential surface of the casing, or integrally extended.

The guide member may be formed by bending the casing.

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 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; At least one discharge cover having a discharge space for receiving the refrigerant discharged from the compression space; And a guide member protruding from the casing by a predetermined height toward the discharge cover and reducing the radial distance between the outer circumferential surface of the discharge cover and the inner circumferential surface of the casing .

Here, the guide member may be coupled to the inner circumferential surface of the casing.

The entire outer peripheral surface of the guide member can be brought into contact with the inner peripheral surface of the casing.

The guide member may be formed in an annular shape so that the inner circumferential surface thereof is stepped.

At least one or more annular protrusions may be formed on the inner circumferential surface of the guide member.

The plurality of annular protrusions may be spaced along the axial direction, and the plurality of annular protrusions may have a height difference along the axial direction.

The guide member may be formed of one member.

The guide member may have a plurality of members overlapping in a radial direction, and a member located on the inner side among the plurality of members may have a short axial length.

The guide member may have a refrigerant passage groove recessed in the axial direction at an interval along the circumferential direction on the inner circumferential surface.

The gap between the inner peripheral surface of the casing and the outer peripheral surface of the discharge cover is formed to be different along the axial direction of the casing,

The inner diameter of the guide member may be larger on the side having the larger gap and smaller on the side having the smaller gap.

The guide member may be formed of a material having a thermal conductivity higher than that of the casing.

The gasket may further include 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, and lubricating the cylinder and the piston with the refrigerant.

Further, in order to achieve the object of the present invention, there is provided a linear motor in which a mover reciprocates with respect to a stator; A compression unit which forms a compression space in the cylinder while the piston connected to the mover of the linear motor reciprocates in the cylinder; At least one discharge cover coupled to the compression unit and having a discharge space for receiving the refrigerant discharged from the compression space; And an inner space for accommodating the linear motor, the compression unit, and the discharge cover, wherein a guide portion protruding from the discharge cover by a predetermined height is formed on the inner peripheral surface, and the guide portion is radially overlapped with the discharge cover And a casing formed in the casing.

Here, the guide portion may be formed in an annular shape.

The guide portion may have at least two inner circumferential surfaces having different heights along the axial direction.

The heat dissipating member may be inserted into the recessed outer circumferential surface of the guide portion.

A gas bearing may be further provided for guiding a part of the refrigerant discharged into the discharge space of the discharge cover to a space between the cylinder constituting the compression unit and the piston and lubricating the space between the cylinder and the piston as refrigerant.

In the linear compressor according to the present invention, as the guide member or the guide portion is protruded from the inner peripheral surface of the casing toward the outer peripheral surface of the discharge cover assembly, a gap between the discharge cover assembly and the guide member or the guide portion becomes narrow. As a result, the flow velocity of the refrigerant flowing along the outer circumferential surface of the discharge cover assembly increases to increase the convective heat transfer coefficient in the vicinity of the discharge cover assembly, whereby the heat of the discharge cover assembly is rapidly transferred to the casing through the guide member, The heat radiating effect for the cover assembly can be improved.

As the entire outer circumferential surface of the guide member or the guide portion is brought into contact with the casing, heat transmitted to the guide member is rapidly transferred to the casing by heat conduction, thereby increasing the temperature difference between the guide member or the guide portion and the discharge cover So that the heat radiation effect on the discharge cover assembly can be further improved.

In addition, since the guide member or the gap between the inner circumferential surface of the guide portion and the outer circumferential surface of the discharge cover or the inner diameter of the guide member is formed to be smaller than the inner diameter of the frame or the discharge cover, the guide member or the guide portion also serves as a stopper .

In addition, since the guide member or the guide portion is provided so as to surround the discharge cover, a kind of noise space is formed between the discharge cover and the guide member or the guide portion to reduce the noise of 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.
5 is a perspective view showing a guide member according to No. 1 broken,
FIG. 6 is a longitudinal sectional view showing a refrigerant flowing state around the guide member according to FIG. 1;
FIG. 7 is a longitudinal sectional view showing another embodiment of the guide member according to FIG. 1;
8 is a longitudinal sectional view showing still another embodiment of the guide member according to FIG.
9A and 9B are a vertical sectional view showing another embodiment of the guide member according to FIG. 1 and a sectional view taken along the line " IV-IV &
FIGS. 10 to 12 are views showing another embodiment of the linear compressor according to the present invention. FIGS. 10 and 11 are sectional views showing embodiments of the guide portion, and FIG. 12 is a cross- Sectional view showing the state.

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 116a 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 116a is coupled to the suction guide 116b described above, while the edge of the first support spring 116a 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 116a 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 116b made of a leaf spring can be engaged.

The front side of the compressor main body C including the discharge cover assembly 160 to be described later is moved radially to the casing 110 including the second shell cover 113 by the second support spring 116b 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 116a and the second support spring 116b 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.

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

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 that communicates with the inner space 101 of the casing 110 and an inner muffler 151 that is connected to one side of the suction muffler 151 and guides the refrigerant to the suction port 142a Guide 152 as shown in FIG.

The suction muffler 151 is provided outside the piston 142, and a plurality of noise spaces 103a 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. [

Here, 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. [

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. [

A first space portion 161a is formed in the center portion of the first cover 161 and a second space portion 162a is formed in the center portion of the second cover 162 and a second space portion 162b is formed in the center portion of the third cover 163, And a space portion 163a may be formed.

The first space portion 161a has a first discharge space 104a for accommodating the compression space 103b and the second space portion 162a is a second discharge space 104b for accommodating the first discharge space 104a. And the third space portion 163a may be formed with a third discharge space 104c that accommodates 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 third discharge space 104b, 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 portion 161a is preferably 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 . Accordingly, 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 in a wide flange shape and can be bolted to the flange portion 122 of the frame 120 by the same bolts in a state of overlapping each other, 3 fixing portion 163b may be formed narrower than the first and second fixing portions 161b and 162b and welded or attached to the front surface of the second cover 162 to be fixed.

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 133b of the magnet 133b reciprocate linearly at the gap between the outer stator 131 and the inner stator 132. [

Then, the piston 142 connected to the magnet holder 133 reciprocates linearly in the cylinder 141, so that 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 of the cylinder 141 and the outer circumferential surface of the piston 142 to support the piston 142 against the cylinder 141 while the remaining refrigerant is supplied through the first communication hole 105a to the second The noise is reduced while moving to the discharge space 104b and then to the third discharge space 104c through the second communication hole 105b, the coupling pipe 106 and the third communication hole 105c. 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, in the linear compressor according to the present invention, the guide member for guiding the refrigerant in the direction of the discharge cover assembly is provided between the inner circumferential surface of the casing and the discharge cover assembly to increase the flow rate of the refrigerant, The discharge cover assembly can be released quickly as the heat transfer coefficient increases. 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.

1 to 6, the outer peripheral surface of the guide member 170 according to the present embodiment is tightly fixed to the inner peripheral surface of the casing 110, and the inner peripheral surface thereof protrudes toward the discharge cover assembly 160, A guide member 170 for guiding the discharge cover assembly 160 toward the discharge cover assembly 160 may be provided.

The gap between the outer peripheral surface of the discharge cover assembly 160 and the inner peripheral surface of the guide member 170 is reduced by the guide member 170 so that the sectional area of the cover side refrigerant passage 107b to be described later decreases, The flow rate of the refrigerant passing through the passage 107b is increased. The heat of the discharge cover assembly 160 is quickly moved to the shell 111 of the casing 110 through the guide member 170 while the convective heat transfer coefficient of the refrigerant passing through the cover side refrigerant passage 107b is increased And as a result, the heat radiating effect for the discharge cover assembly 160 can be improved.

The guide member 170 according to the present embodiment may be formed into a cylindrical shape having the same circular cross-sectional shape as the inner peripheral surface 111a of the shell 111 or may be formed into an arc shape having a cut-away surface. Hereinafter, a cylindrical shape will be described as a representative example.

The guide member 170 may be formed in a cylindrical shape having the same outer diameter at both ends but different inner diameters.

In detail, the inner circumferential surface of the guide member 170 according to the present embodiment may be stepped so as to correspond to the shape of the outer circumferential surface of the discharge cover assembly 160. That is, the inner circumferential surface of the guide member 170 may be formed in consideration of the outer diameter from the first cover 161 to the third cover 163 constituting the discharge cover assembly 160. Accordingly, the guide member 170 can be formed at least one time in the axial middle portion, and the inner diameter of the rear side of the frame 120 can be formed larger than the inner diameter of the front side opposite thereto.

The inner circumferential surface 170a of the guide member 170 is spaced apart from the outer circumferential surface 160a of the discharge cover assembly 160 by a substantially constant distance and the first end 171 of the guide member 170 is spaced apart from the front surface of the frame 111 And may be spaced apart from the second end 122b by a predetermined distance.

A first gap G1 constituting the frame side coolant passage 107a is formed between the outer peripheral surface 122a of the frame 120 and the inner peripheral surface 111a of the shell 111, A second gap G2 constituting a part of the cover side coolant passage 107b is formed between the inner surface 170a of the guide member 170 and the front surface 122b of the frame 120, A third gap G3 forming the cover side coolant passage 107b may be formed between the outer circumferential surfaces 160a of the cover 160. Accordingly, as the frame refrigerant passage 107a and the cover side refrigerant passage 107b are communicated with each other by the first gap G1, the second gap G2, and the third gap G3, The inside refrigerant circulates between the front side and the rear side with respect to the frame 120 while moving through the frame refrigerant passage 107a and the cover side refrigerant passage 107b.

Here, the third gap G3 is not constant as the discharge cover assembly 160 forms the compressor main body C while the outer peripheral surface 160a of the discharge cover assembly 160 is not uniform. Therefore, the third gap G3 described above can be understood as the minimum gap between the discharge cover assembly 160 and the guide member 170. [

Here, the first gap G1, the second gap G2, and the third gap G3 may be formed to have the same size, which may be advantageous in terms of the coolant flow. However, as the compressor body C reciprocates with respect to the casing 110 with the outer diameter of the discharge cover assembly 160 being different for each of the covers 161, 162, and 163, (G2) and (G3) may be difficult to be formed with the same size. Therefore, in consideration of the reciprocating motion of the compressor main body C, the intervals G1, G2 and G3 may be different from each other when the compressor is stopped.

For example, when the second gap G2 or the third gap G3 is smaller than the first gap G1, the flow rate of the refrigerant passing through the cover side coolant passage 107b is increased while the discharge cover assembly 160 can be increased. However, if the second gap G2 is too small, particularly in the second gap G2 and the third gap G3, the front surface of the frame 120 constituting the compressor main body C during vibration of the compressor main body C, The guide member 170 may be damaged or the impact may be transmitted to the compressor main body C by colliding with the first end 171 of the guide member 170. [ Therefore, it is preferable from the viewpoint of reliability that the second gap G2 is formed to have a distance such that the compressor main body C and the guide member 170 do not collide with each other in consideration of the vibration distance of the compressor main body C.

The inner circumferential surface 170a of the guide member 170 has at least one intermediate stepped portion 177a (177a, 177b) at an intermediate position, since the third gap G3 has a smaller radial cross- May be formed. However, both the outer diameter of the first end 171 and the outer diameter of the second end 172 may be substantially the same as the inner diameter of the shell 111, and may be in contact with the inner circumferential surface of the shell 111. The contact area between the guide member 170 and the shell 111 is widened so that the heat transferred from the discharge valve assembly 160 to the guide member 170 can be quickly transferred to the shell 111 .

The guide member 170 may be formed of the same material as the shell 111 in consideration of the fact that the fixing portion of the guide member 170 is welded to the shell 111. However, ) May be formed of a material different from that of the shell. For example, when the shell 111 is formed of a cast iron series, the guide member 170 may be made of a material that is lighter than the shell 111 or the discharge cover assembly 160 and has high thermal conductivity.

The guide member 170 may be formed to be thinner than the thickness of the shell 111. The third gap G3 between the inner circumferential surface of the guide member 170 and the outer circumferential surface of the compressor body (precisely, the discharge cover assembly C) The first gap G1 between the outer circumferential surface 122a of the frame 120 and the inner circumferential surface 111a of the shell 111 may be set to a thickness smaller than or equal to the first gap G1. Thus, the guide member 170 can serve as a stopper for restricting the movement of the compressor main body C in the axial direction or the radial direction.

The guide member according to the present embodiment as described above has the following operational effects.

That is, the refrigerant is introduced into each of the discharge spaces 104a, 104b and 104c of the discharge cover assembly 160 composed of the first cover 161, the second cover 162 and the third cover 163, The covers 161, 162 and 163 constituting the discharge cover assembly 160 are heated by the refrigerant flowing into the discharge spaces 104a, 104b and 104c. If the temperature of the first cover 161 is not quickly radiated, the temperature of the frame in contact with the first cover 161 can also rise significantly have.

At this time, if there is no guide member as in the present embodiment in the casing 110, the third gap G3 between the discharge cover assembly 160 and the shell 111 is too large to lower the flow rate of the refrigerant, The convection heat transfer coefficient for the refrigerant between the discharge cover assembly 160 and the shell 111 is lowered. Then, the heat of the discharge cover assembly 160 can not be quickly transferred to the shell 111, so that the discharge cover assembly 160 is not effectively radiated. Then, as described above, the heat of the discharge cover assembly 160 is transmitted to the frame 120, causing suction loss or compression loss.

However, when the guide member 170 is positioned between the discharge cover assembly 160 and the shell 111 as in the present embodiment, the third gap G3 between the discharge cover assembly 160 and the shell 111, The flow rate of the refrigerant in the cover side coolant passage 107b is greatly increased and the convection heat transfer coefficient of the coolant between the discharge cover assembly 160 and the shell 111 is increased, 160 are quickly transferred to the guide member 170. The heat transferred to the guide member 170 is thermally conducted to the shell 111 through the guide member 170 and is radiated, and as a result, the temperature of the discharge cover assembly can be rapidly lowered.

Particularly, since the entire outer peripheral surface of the guide member 170 according to this embodiment is in contact with the inner peripheral surface 111a of the shell 111, the heat transfer area of the guide member 170 is enlarged, The heat transmitted to the member 170 can be quickly transferred to the shell 111 by heat conduction. The heat radiation effect on the discharge cover assembly 160 can be further improved.

This prevents the frame 120 and the cylinder 141 from being heated by the discharge cover assembly 160 while the temperature of the discharge cover assembly 160 including the first cover 161 is lowered, 103b or the suction passage 103a from being overheated.

In addition, the guide member 170 according to the present embodiment can prevent the compressor body C from moving during the conveyance of the compressor, thereby preventing the compressor from being damaged. For example, if the third gap G3 between the guide member 170 and the discharge cover assembly 160 according to the present embodiment is smaller than the first gap G1 between the frame 120 and the shell 111 The outer circumferential surface 160a of the discharge cover assembly 160 is pressed against the inner circumferential surface of the guide member 170 before the frame 120 contacts the shell 111 when the compressor main body C tries to move in the radial direction 170a. Accordingly, the guide member 170 serves as a radial stopper with respect to the compressor main body C.

The rear end 171 or the front end 172 of the guide member 170 is formed to overlap with the front surface 122b of the frame 120 or the front surface of the discharge cover assembly 160 in the axial direction , And serves as an axial stopper for restricting the compressor body C when it is about to move toward the front side.

Accordingly, since the movement of the compressor body is restricted by using the guide member 170 without providing a separate stopper for restricting the movement of the compressor body in the casing, it is possible to reduce the material cost And the assembly process can be simplified.

7, when the entire outer peripheral surface 170b of the guide member 170 contacts the inner peripheral surface 111a of the shell 111, at least one annular protrusion 176 is formed on the inner peripheral surface of the guide member 170, May be formed.

In this case, the guide member 170 may have a ring-shaped cross section and a fixed portion 175 may be formed, and the annular ridge 176 may be formed on the inner circumferential surface of the fixed portion 175 in a radial direction. The fixing portion 175 is welded to the inner circumferential surface 111a of the shell 111 by being positioned within the axial range of the discharge cover assembly 160 and the annular protruding portion 176 is axially extended from the inner peripheral surface of the fixing portion 175 At least one protrusion may be formed at regular intervals.

The annular protrusion 176 may be formed at the same height but the annular protrusion 176 is also formed in the discharge cover assembly 160 because the outer diameter of the discharge cover assembly 160 is formed differently according to the respective covers 161, 160 may be formed to correspond to the shape of the outer circumferential surface 160a. That is, the inner diameter of the rear side annular protrusion 176a corresponding to the outer circumferential surface of the second cover 162 may be larger than the inner diameter of the front side annular protrusion 176b corresponding to the outer circumferential surface of the third cover 163.

The guide member according to the present embodiment as described above is similar to the guide member described above with reference to FIG. 6, and therefore, a detailed description thereof will be omitted. However, compared to the embodiment of FIG. 6, the present embodiment forms the turbulent flow of the refrigerant by the annular protrusion 176, and the flow rate of the refrigerant further increases to further improve the heat radiating effect.

On the other hand, another embodiment of the guide member is as follows. That is, in the above-described embodiments, even if the guide member is formed of one member or a plurality of guide members are assembled in different directions, in the present embodiment, a plurality of guide members are stacked in a radial direction.

8, the guide member 170 according to the present embodiment is formed by stacking a plurality of (three in the drawing) layer layers from the inner circumferential surface of the casing 110 toward the outer circumferential surface 160a of the discharge cover assembly 160 . In this case, the first member 173a of the outermost layer has the longest axial length, the second member 173b of the intermediate layer has the intermediate length of the axial length, and the innermost third member 173c And the shortest axial length can be formed.

One end of the first member 173a, the second member 173b and the third member 173c coincide with each other while the other end of the third member 173c coincides with the axis 173a, 173b, Directional length difference may be generated.

The first member 173a, the second member 173b, and the third member 173c may be made of the same material, but they may be made of different materials depending on the case.

For example, the third member 173c having the shortest axial length may be formed of a material having the highest heat transfer coefficient, and the first member 173a having the longest axial length may be formed of a material having the lowest heat transfer coefficient have. Accordingly, it is possible to uniformly dissipate heat by compensating the heat transfer effect for each part. Of course, the heat transfer coefficient of the member having a large axial length can be made the largest, contrary to the above embodiment. This can further enhance the heat dissipation effect.

The guide member 170 according to the present embodiment is formed by assembling a plurality of members 173a, 173b and 173c so that the shape and material of the guide member 170 can be selected as required, Accordingly, not only the shape of the guide member 170 can be variously formed according to the shape of the discharge valve assembly 160, but also the heat radiation effect can be enhanced by suitably adjusting the material as necessary.

On the other hand, another embodiment of the guide member is as follows. That is, in the above-described embodiments, the guide member may be formed in an annular shape. In this embodiment, however, the guide member may be formed in an arc shape or may be formed on the inner circumferential surface at a predetermined distance in the circumferential direction.

9A and 9B, the outer circumferential surface of the guide member 170 is formed in an annular shape and is coupled to the inner circumferential surface 111a of the shell 111. The inner circumferential surface 170a of the guide member 170 is in the circumferential direction The refrigerant passage grooves 170c may be formed at regular intervals along the circumferential direction.

Here, the guide member 170 may be formed as a single body, and in some cases, the outer side and the inner side are separated from each other so that the outer side is formed into an annular shape, while the inner side is formed into an arc shape and joined to the outer side at intervals along the circumferential direction It is possible.

The gap G4 between the refrigerant passage grooves 170c is smaller than the third gap G3 between the inner peripheral surface 170a of the guide member 170 and the outer peripheral surface 160a of the discharge cover assembly 160 ) May be formed. Accordingly, even if the third gap G3 can not be formed sufficiently small when the guide member 170 is assembled due to the outer peripheral surface shape of the discharge cover assembly 160, the fourth gap G4 is formed to be sufficiently small, .

In the meantime, in the case where the linear compressor according to the present invention has another embodiment, the following will be described. That is, in the above-described embodiments, the guide member is separately manufactured and is coupled to the inner circumferential surface of the shell. However, in this embodiment, the guide is formed by using the shell.

For example, as shown in FIGS. 10 and 11, the shell 111 according to the present embodiment may have a guide portion 178 formed by bending a specific portion in the direction of the inner circumferential surface, that is, toward the discharge cover assembly 160 have.

Here, the guide portion 178 may be formed in an annular cross-sectional shape having a U-shaped cross-section, or may be formed to have a narrower front side space than the discharge cover assembly 160, As shown in Fig.

The guide part 178 may have one guide part 178 as shown in FIG. 10 or may have a plurality of guide parts (the first guide part 1781 and the second guide part 1782) As shown in Fig.

10, the inner circumferential surface 178a of the guide portion 178 is formed to have the same or substantially the same inner diameter along the axial direction so that the inner circumferential surface 178a of the guide portion 178 is in contact with the outer surface of the discharge cover assembly 160 And may be formed to face the outer circumferential surface 160a. 11, since the stepped surface is formed between the first guide portion 1781 and the second guide portion 1782, the inner diameter of the second guide portion 1782 is smaller than the inner diameter of the first guide portion 1781, The inner diameter of the inner tube can be made larger. The inner circumferential surface 1781a of the first guide portion 1781 is formed so as to face the outer circumferential surface 160a of the discharge cover assembly 160 and the rear surface 1782a of the second guide portion 1782 is fixed to the discharge cover assembly (More precisely, the second cover) 160 may be spaced apart from each other by a predetermined gap G5 while facing the front surface 160b.

The linear compressor according to the present embodiment has a narrow gap G3 between the inner peripheral surface 111a of the shell 111 and the outer peripheral surface 160a of the discharge cover assembly 160, So that the heat radiation effect can be enhanced.

In addition, since the guide portion 178 according to the present embodiment is formed using the shell 111, the manufacturing cost can be reduced by reducing the material cost and the assembling number, compared with the case of joining separate guide members.

11, the guide portion 178 supports the outer peripheral surface 160a of the discharge cover assembly 160 to serve as a radial stopper for restricting the radial direction with respect to the compressor main body C, It may also serve as an axial stopper when the first cover 1782 is formed to have a certain gap G5 in the axial direction from the front surface 160b of the discharge cover assembly 160. [

As a result, the entire area of the shell 111 is enlarged. In addition, since the shell 111 is formed integrally with the discharge cover assembly 160, The heat dissipation effect may be further improved as compared with the case where heat is transmitted through the guide member as in the above-described embodiments.

On the other hand, as shown in FIG. 12, the heat radiating member 179 may be inserted and coupled to the outer circumferential surface of the guide portion 178 according to the present embodiment.

Here, it is preferable that the heat radiating member 179 is formed of a material having a heat transfer coefficient higher than that of the shell 111 because heat radiation effect can be enhanced. The heat radiating members 179 may be formed in an arc shape and may be inserted radially outwardly of the casing 110, respectively.

When the heat dissipating member 179 is inserted into the guide portion 178, the heat dissipation effect on the casing 110 is further enhanced, and as a result, the efficiency of the overall compressor can be improved.

100: Linear compressor 101: Suction space
103a: Suction flow path 103b: Compression space
104a, 104b, 104c: Discharge spaces 105a, 105b, 105c:
106: connection pipe 107a, 107b: 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
160: discharge cover assembly 161, 162, 163: first, second, and third cover
170: guide member 171, 172: rearward, front end
175: fixing portion 176: annular protrusion
178: guide portion 179: radiation member
G1: Frame and shell spacing G2: Cover and frame spacing
G3: Cover and flow guide clearance

Claims (17)

  1. 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 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;
    At least one discharge cover having a discharge space for receiving the refrigerant discharged from the compression space; And
    And a guide member protruding from the casing by a predetermined height toward the discharge cover to reduce a radial distance between the outer circumferential surface of the discharge cover and the inner circumferential surface of the casing.
  2. The method according to claim 1,
    And the guide member is coupled to the inner circumferential surface of the casing.
  3. 3. The method of claim 2,
    Wherein the guide member is in contact with the entire inner circumferential surface of the casing.
  4. The method of claim 3,
    Wherein the guide member is formed in an annular shape so that an inner circumferential surface of the guide member is stepped.
  5. The method of claim 3,
    Wherein at least one annular protruding portion is formed on an inner peripheral surface of the guide member.
  6. 6. The method of claim 5,
    Wherein a plurality of the annular protrusions are formed at intervals along the axial direction, and the plurality of annular protrusions are formed to have a height difference along the axial direction.
  7. The method according to claim 1,
    Wherein the guide member is formed of one member.
  8. The method according to claim 1,
    Wherein the guide member is formed by overlapping a plurality of members in the radial direction, and a member located on the inner side among the plurality of members is formed to have a short axial length.
  9. The method according to claim 1,
    Wherein the guide member has an inner circumferential surface formed with a refrigerant passage groove recessed axially with an interval along the circumferential direction.
  10. The method according to claim 1,
    Wherein an interval between the inner circumferential surface of the casing and the outer circumferential surface of the discharge cover is formed differently along the axial direction of the casing,
    Wherein an inner diameter of the guide member is larger on the side where the interval is larger and smaller on the side where the interval is smaller.
  11. The method according to claim 1,
    Wherein the guide member is formed of a material having higher thermal conductivity than the casing.
  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 discharged to the discharge space of the discharge cover between the cylinder and the piston to lubricate between the cylinder and the piston with the refrigerant.
  13. A linear motor in which the mover reciprocates with respect to the stator;
    A compression unit which forms a compression space in the cylinder while the piston connected to the mover of the linear motor reciprocates in the cylinder;
    At least one discharge cover coupled to the compression unit and having a discharge space for receiving the refrigerant discharged from the compression space; And
    A guide portion having an inner circumferential surface protruding toward the discharge cover by a predetermined height is formed in the inner space for accommodating the linear motor, the compression unit, and the discharge cover, and the guide portion is disposed at a position overlapping the discharge cover in the radial direction And a casing formed in the casing.
  14. 14. The method of claim 13,
    Wherein the guide portion is formed in an annular shape.
  15. 14. The method of claim 13,
    Wherein the guide portion is formed with at least two or more inner circumferential surfaces having different inner diameters along the axial direction.
  16. 14. The method of claim 13,
    And a heat dissipating member is inserted into the recessed outer circumferential surface of the guide portion.
  17. 17. The method according to any one of claims 13 to 16,
    Further comprising a gas bearing for guiding a part of the refrigerant discharged into the discharge space of the discharge cover to a space between the cylinder constituting the compression unit and the piston and for lubricating the space between the cylinder and the piston by the refrigerant.
KR1020170123683A 2017-09-25 2017-09-25 Linear compressor KR101981100B1 (en)

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KR1020170123683A KR101981100B1 (en) 2017-09-25 2017-09-25 Linear compressor

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20150040027A (en) 2013-10-04 2015-04-14 엘지전자 주식회사 A linear compressor
KR20160010985A (en) * 2014-07-21 2016-01-29 엘지전자 주식회사 Linear compressor and linear motor
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor
KR20170086841A (en) * 2016-01-19 2017-07-27 엘지전자 주식회사 A linear compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20150040027A (en) 2013-10-04 2015-04-14 엘지전자 주식회사 A linear compressor
KR20160010985A (en) * 2014-07-21 2016-01-29 엘지전자 주식회사 Linear compressor and linear motor
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor
KR20170086841A (en) * 2016-01-19 2017-07-27 엘지전자 주식회사 A linear compressor

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