KR102060179B1 - Linear compressor - Google Patents

Abstract

The present invention relates to a linear compressor. According to an embodiment of the present invention, the linear compressor comprises an insulation member disposed between a cylinder and a discharge unit. The cylinder comprises a discharge cylinder surface on which a discharge valve and the insulation member are mounted. The discharge cylinder surface can comprise: a discharge valve mounting unit protruding from the discharge cylinder surface for the discharge valve to be mounted on the discharge valve mounting unit; and a cylinder insulation mounting unit recessed on the discharge cylinder surface for the insulation member to be mounted on the cylinder insulation mounting unit.

Description

Linear compressor {Linear compressor}

The present invention relates to a linear compressor.

In general, a compressor is a mechanical device that increases power by compressing air, refrigerant, or other various working gases by receiving power from a power generator such as an electric motor or a turbine. It is used.

These compressors can be broadly classified into reciprocating compressors, rotary compressors, and scroll compressors.

The reciprocating compressor forms a compression space in which the working gas is sucked or discharged between the piston and the cylinder to compress the refrigerant while the piston linearly reciprocates in the cylinder.

In addition, the rotary compressor has a compression space for suction or discharge of the working gas is formed between the roller and the cylinder to be eccentrically rotated, and the roller is eccentrically rotated along the inner wall of the cylinder to compress the refrigerant.

In addition, the scroll compressor is formed between the orbiting scroll (Fixed scroll) and the fixed scroll (Fixed scroll) is formed a compression space for the suction or discharge of the working gas and the rotating scroll is rotated along the fixed scroll to compress the refrigerant.

Recently, a linear compressor has been developed in which the piston is directly connected to a drive motor for reciprocating linear motion, thereby improving compression efficiency without mechanical loss due to motion conversion and having a simple structure.

The linear compressor is configured to suck, compress and then discharge the refrigerant while the piston is reciprocally linearly moved inside the cylinder by the linear motor inside the sealed shell.

At this time, the linear motor is configured such that a permanent magnet is positioned between the inner stator and the outer stator, and the permanent magnet is driven to linearly reciprocate by mutual electromagnetic force between the permanent magnet and the inner (or outer) stator. In addition, as the permanent magnet is driven while being connected to the piston, the piston sucks and compresses the refrigerant while discharging the refrigerant while reciprocating linearly inside the cylinder.

 Regarding the linear compressor having such a structure, the present applicant has filed Prior Art 1.

<Previous Document 1>

1.Publication No. 10-2017-0124908 (Publication date: November 13, 2017)

2. Name of invention: linear compressor

According to the structure described in the prior document 1, the permanent magnet and the piston can be moved to compress the refrigerant. In detail, the suction refrigerant flows into the compression chamber through the piston port and is compressed by the movement of the piston. Then, the compressed high temperature refrigerant is discharged out of the shell through the discharge chamber formed in the discharge cover.

At this time, the linear compressor as in the prior document 1 has the following problems.

(1) As the compressed hot refrigerant flows to the front of the cylinder, relatively much heat can be transferred to the cylinder. Then, the heat transferred to the cylinder overheats the suction refrigerant contained in the piston. Accordingly, the volume of the suction refrigerant is increased, there is a problem that the compression efficiency is lowered.

(2) Also, heat of the discharge unit through which the high temperature refrigerant flows can be conducted to the frame. Accordingly, the frame is overheated and heat is transferred to the piston and the cylinder to overheat the suction refrigerant. Accordingly, the volume of the suction refrigerant is increased, there is a problem that the compression efficiency is lowered.

The present invention has been proposed to solve such a problem, and an object of the present invention is to provide a linear compressor having a heat insulating member seated on the front of the cylinder.

In addition, an object of the present invention is to provide a linear compressor provided with a heat insulating member extending to the front surface of the frame as well as the cylinder.

According to an aspect of the present invention, a linear compressor includes a piston reciprocating in an axial direction, a cylinder forming a compression space in which a refrigerant is compressed by the piston, a discharge unit forming a discharge space in which the refrigerant discharged from the compression space flows; The cylinder is accommodated inside, the frame coupled to the discharge unit, the discharge valve for opening and closing the compression space so that the refrigerant in the compression space is discharged to the discharge space and the heat insulation disposed between the cylinder and the discharge unit Member is included.

In addition, the cylinder includes a discharge cylinder surface on which the discharge valve and the heat insulating member are seated. In this case, the discharge cylinder surface, the discharge valve seating portion formed to protrude from the discharge cylinder surface, and the heat insulating member may be included in the discharge cylinder surface recessed formed in the discharge cylinder surface so as to seat the discharge valve. .

The heat insulating member has an inner diameter and an outer diameter and is provided in a ring shape extending in the radial direction. The heat insulating member may include a circular opening corresponding to the inner diameter and may be disposed at a radially outer side of the first heat insulating part and the first heat insulating part in contact with the discharge valve seat, and disposed at the cylinder heat insulating seat. Second insulation may be included.

In addition, the discharge valve seating portion is formed to protrude in the axial direction, the cylinder heat-insulating seating portion is formed to be recessed in the axial direction from the radially outer side of the discharge valve seating portion. In this case, the heat insulating member may extend in a radial direction from the discharge valve seating portion to the cylinder heat insulating seating portion.

According to the linear compressor according to the embodiment of the present invention having the above configuration, the following effects are obtained.

Through the heat insulating member seated on the front surface of the cylinder exposed to the discharge refrigerant, there is an advantage that it is possible to prevent the heat of the discharge refrigerant to be transferred to the cylinder.

In addition, as the heat transferred to the cylinder is reduced, there is an advantage that the heat transferred to the suction refrigerant contained in the piston can be minimized, and the compression efficiency can be improved by lowering the temperature of the suction refrigerant.

In addition, as the heat insulation member is disposed between the discharge cover and the frame having a relatively high temperature, the heat of the discharge cover can be prevented from being conducted to the frame.

1 is a diagram illustrating a linear compressor according to a first embodiment of the present invention.
2 is an exploded view illustrating an internal configuration of a linear compressor according to a first embodiment of the present invention.
3 is a cross-sectional view taken along line III-III ′ of FIG. 1.
4 is an exploded view illustrating the cylinder and the heat insulating member of the linear compressor according to the first embodiment of the present invention.
5 is a view illustrating part 'A' of FIG. 3 according to the operation of the linear compressor.
6 is an exploded view illustrating a discharge unit, a frame, a cylinder, and a heat insulating member of the linear compressor according to the second embodiment of the present invention.
7 is a cross-sectional view illustrating a coupling section of a discharge unit, a frame, a cylinder, and a heat insulating member of the linear compressor according to the second embodiment of the present invention.
FIG. 8 is an enlarged view of a portion 'B' of FIG. 7.

Hereinafter, some embodiments of the present invention will be described in detail with reference to the accompanying drawings. In adding reference numerals to the components of each drawing, it should be noted that the same reference numerals are assigned to the same components as much as possible even though they are shown in different drawings. In addition, in describing the embodiments of the present invention, when it is determined that a detailed description of a related well-known configuration or function interferes with the understanding of the embodiments of the present invention, the detailed description thereof will be omitted.

In addition, in describing the components of the embodiment of the present invention, terms such as first, second, A, B, (a), and (b) may be used. These terms are only for distinguishing the components from other components, and the nature, order or order of the components are not limited by the terms. If a component is described as being "connected", "coupled" or "connected" to another component, that component may be directly connected or connected to that other component, but between components It will be understood that may be "connected", "coupled" or "connected".

1 is a diagram illustrating a linear compressor according to a first embodiment of the present invention.

As shown in FIG. 1, the linear compressor 10 according to an exemplary embodiment of the present invention includes a shell 101 and shell covers 102 and 103 coupled to the shell 101. In a broad sense, the shell covers 102, 103 may be understood as one configuration of the shell 101.

Under the shell 101, the leg 50 may be coupled. The leg 50 may be coupled to a base of a product on which the linear compressor 10 is installed. For example, the product may include a refrigerator, and the base may include a machine room base of the refrigerator. As another example, the product may include an outdoor unit of an air conditioner, and the base may include a base of the outdoor unit.

The shell 101 has a substantially cylindrical shape, and may have an arrangement lying in the transverse direction, or an arrangement lying in the axial direction. Referring to FIG. 1, the shell 101 extends in the horizontal direction and may have a somewhat lower height in the radial direction. That is, since the linear compressor 10 may have a low height, for example, when the linear compressor 10 is installed in the machine room base of the refrigerator, the height of the machine room may be reduced.

In addition, the longitudinal central axis of the shell 101 coincides with the central axis of the compressor body, which will be described later, and the central axis of the compressor body coincides with the central axis of the cylinders and pistons constituting the compressor body.

On the outer surface of the shell 101, a terminal 108 may be installed. The terminal 108 is understood as a configuration for delivering external power to the motor assembly 140 (see FIG. 3) of the linear compressor 10. In particular, the terminal 108 may be connected to a lead wire of the coil 141c (see FIG. 3).

On the outside of the terminal 108, a bracket 109 is provided. The bracket 109 may include a plurality of brackets surrounding the terminal 108. The bracket 109 may perform a function of protecting the terminal 108 from an external shock or the like.

Both sides of the shell 101 are configured to be open. The shell covers 102 and 103 may be coupled to both sides of the opened shell 101. In detail, the shell covers 102 and 103 may include a first shell cover 102 (see FIG. 3) coupled to an open side of the shell 101 and an open side of the shell 101. Included is a second shell cover 103. By the shell covers 102 and 103, the inner space of the shell 101 may be sealed.

Referring to FIG. 1, the first shell cover 102 may be located at the right side of the linear compressor 10, and the second shell cover 103 may be located at the left side of the linear compressor 10. . In other words, the first and second shell covers 102 and 103 may be disposed to face each other. In addition, it may be understood that the first shell cover 102 is located on the suction side of the refrigerant, and the second shell cover 103 is located on the discharge side of the refrigerant.

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

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

For example, the suction pipe 104 may be coupled to the first shell cover 102. The refrigerant may be sucked into the linear compressor 10 along the axial direction through the suction pipe 104.

The discharge pipe 105 may be coupled to an outer circumferential surface of the shell 101. The refrigerant sucked through the suction pipe 104 may be compressed while flowing in the axial direction. In addition, the compressed refrigerant may be discharged through the discharge pipe 105. The discharge pipe 105 may be disposed at a position closer to the second shell cover 103 than to the first shell cover 102.

The process pipe 106 may be coupled to an outer circumferential surface of the shell 101. The worker may inject refrigerant into the linear compressor 10 through the process pipe 106.

In addition, the process pipe 106 may be coupled to the shell 101 at a different height from the discharge pipe 105 in order to avoid interference with the discharge pipe 105. The height is understood as the distance in the vertical direction from the leg 50. Since the discharge pipe 105 and the process pipe 106 are coupled to the outer circumferential surface of the shell 101 at different heights, work convenience can be achieved.

At least a portion of the second shell cover 103 may be adjacent to the inner circumferential surface of the shell 101, corresponding to the point at which the process pipe 106 is coupled. In other words, at least a portion of the second shell cover 103 may act as a resistance of the refrigerant injected through the process pipe 106.

Therefore, at the flow path viewpoint of the coolant, the flow path size of the coolant flowing through the process pipe 106 is reduced by the second shell cover 103 while entering the inner space of the shell 101 and passes therethrough. It is formed to grow again. In this process, the pressure of the refrigerant may be reduced to vaporize the refrigerant.

Also, in this process, the oil contained in the refrigerant may be separated. Therefore, as the refrigerant separated in oil flows into the piston 130 (see FIG. 3), the compression performance of the refrigerant may be improved. The fraction can be understood as the working oil present in the cooling system.

Inside the first and second shell covers 102 and 103, an apparatus for supporting the compressor main body disposed inside the shell 101 may be provided. Here, the compressor main body means a component provided in the shell 101, and may include, for example, a driving unit for back and forth reciprocating motion and a support unit for supporting the driving unit.

Hereinafter, the compressor main body will be described in detail.

2 is an exploded view illustrating an internal configuration of a linear compressor according to a first embodiment of the present invention, and FIG. 3 is a cross-sectional view taken along line III-III 'of FIG. 1.

2 and 3, the linear compressor 10 according to an embodiment of the present invention includes a frame 110, a cylinder 120, a piston 130 reciprocating linearly in the cylinder 120, and The motor assembly 140 is included as a linear motor for imparting a driving force to the piston 130. When the motor assembly 140 is driven, the piston 130 may reciprocate in the axial direction.

Hereinafter, the direction is defined.

The term "axial direction" may be understood as a direction in which the piston 130 reciprocates, that is, a transverse direction in FIG. 3. In the "axial direction", the direction from the suction pipe 104 toward the compression space P, that is, the direction in which the refrigerant flows, is referred to as "front", and the opposite direction is defined as "rear". When the piston 130 moves forward, the compression space P may be compressed.

On the other hand, the "radial direction" is a direction perpendicular to the direction in which the piston 130 reciprocating, it can be understood in the longitudinal direction of FIG. In addition, the direction away from the central axis of the piston 130 is defined as 'outer', the direction toward the 'inner'. As described above, the central axis of the piston 130 may coincide with the central axis of the shell 101.

The frame 110 is understood as a configuration for fixing the cylinder 120. The frame 110 is disposed to surround the cylinder 120. That is, the cylinder 120 may be positioned to be accommodated inside the frame 110. For example, the cylinder 120 may be press fitted into the frame 110. In addition, the cylinder 120 and the frame 110 may be made of aluminum or an aluminum alloy material.

The cylinder 120 is configured to receive at least a portion of the piston 130. In addition, in the cylinder 120, a compression space P in which a refrigerant is compressed by the piston 130 is formed.

In this case, the compression space P may be understood as a space formed between the suction valve 135 and the discharge valve 161 which will be described later. In addition, the suction valve 135 is formed at one side of the compression space P, and the discharge valve 161 is at the other side of the compression space P, that is, on the opposite side of the suction valve 135. Can be provided.

The piston 130 includes a substantially cylindrical piston body 131 and a piston flange 132 extending radially from the piston body 131. The piston body 131 may reciprocate in the cylinder 120, and the piston flange 132 may reciprocate in the outer side of the cylinder 120.

A suction hole 133 is formed in the front portion of the piston body 131 to introduce a refrigerant into the compression space P, and the suction hole 133 is selectively opened in front of the suction hole 133. Intake valve 135 is provided.

In addition, a fastening hole 136a to which a predetermined fastening member 136 is coupled is formed at the front portion of the piston body 131. In detail, the fastening hole 136a is positioned at the center of the front portion of the piston body 131, and a plurality of suction holes 133 are formed to surround the fastening hole 136a. In addition, the fastening member 136 is coupled to the fastening hole 136a through the suction valve 135 to fix the suction valve 135 to the front portion of the piston body 131.

The outer stator 141 is fixed to the frame 110 and is disposed to surround the cylinder 120, and an inner stator 148 spaced apart from the inner stator 141. And a permanent magnet 146 positioned in a space between the outer stator 141 and the inner stator 148.

The permanent magnet 146 may linearly reciprocate by mutual electromagnetic forces with the outer stator 141 and the inner stator 148. In addition, the permanent magnet 146 may be composed of a single magnet having one pole or a plurality of magnets having three poles are combined.

The permanent magnet 146 may be installed in the magnet frame 138. The magnet frame 138 has a substantially cylindrical shape and may be disposed to be inserted into a space between the outer stator 141 and the inner stator 148.

 Specifically, with reference to FIG. 3, the magnet frame 138 is coupled to the piston flange 132 and extends radially outward and can be bent axially forward. In this case, the permanent magnet 146 may be installed in the front portion of the magnet frame 138. Accordingly, when the permanent magnet 146 reciprocates, the piston 130 may reciprocate in the axial direction together with the permanent magnet 146 by the magnet frame 138.

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

The coil winding further includes a terminal portion 141d for guiding a power line connected to the coil 141c to be drawn or exposed to the outside of the outer stator 141. The terminal portion 141d may be inserted into the terminal insertion hole 1104 (see FIG. 6) provided in the frame 110.

The stator core 141a includes a plurality of core blocks formed by stacking a plurality of laminations in the circumferential direction. The plurality of core blocks may be arranged to surround at least a portion of the coil windings 141b and 141c.

The stator cover 149 is provided at one side of the outer stator 141. That is, one side of the outer stator 141 may be supported by the frame 110, and the other side thereof may be supported by the stator cover 149.

In addition, the linear compressor 10 further includes a cover fastening member 149a for fastening the stator cover 149 and the frame 110. The cover fastening member 149a extends forward through the stator cover 149 toward the frame 110 and may be coupled to the stator fastening hole 1102 (see FIG. 6) of the frame 110. have.

The inner stator 148 is fixed to the outer circumference of the frame 110. In addition, the inner stator 148 is configured by stacking a plurality of laminations in the circumferential direction from the outside of the frame 110.

In addition, the linear compressor 10 further includes a suction muffler 150 coupled to the piston 130 to reduce noise generated from the refrigerant sucked through the suction pipe 104. The refrigerant sucked through the suction pipe 104 flows into the piston 130 through the suction muffler 150. For example, in the process of passing the refrigerant through the suction muffler 150, the flow noise of the refrigerant may be reduced.

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

The first muffler 151 is located inside the piston 130, and the second muffler 152 is coupled to the rear side of the first muffler 151. The third muffler 153 may accommodate the second muffler 152 therein and may extend to the rear of the first muffler 151.

In view of the flow direction of the refrigerant, the refrigerant sucked through the suction pipe 104 may pass through the third muffler 153, the second muffler 152, and the first muffler 151 in order. In this process, the flow noise of the refrigerant can be reduced.

In addition, the suction muffler 150 further includes a muffler filter 154. The muffler filter 154 may be located at an interface at which the first muffler 151 and the second muffler 152 are coupled. For example, the muffler filter 154 may have a circular shape, and an outer circumferential portion of the muffler filter 154 may be supported between the first and second mufflers 151 and 152.

In addition, the linear compressor 10 further includes a supporter 137 supporting the piston 130. The supporter 137 may be coupled to the rear side of the piston 130, and may be formed to penetrate the muffler 150 therein. In addition, the piston flange 132, the magnet frame 138 and the supporter 137 may be fastened by a fastening member.

The balance weight 179 may be coupled to the supporter 137. The weight of the balance weight 179 may be determined based on the operating frequency range of the compressor body. In addition, the supporter 137 may be coupled to a spring support 137a coupled to the first resonant spring 176a to be described later.

In addition, the linear compressor 10 further includes a rear cover 170 coupled to the stator cover 149 and extending rearward. The rear cover 170 may include three support legs, and the three support legs may be coupled to the rear surface of the stator cover 149.

In addition, a spacer 178 may be located between the three support legs and the rear surface of the stator cover 149. By adjusting the thickness of the spacer 179, the distance from the stator cover 149 to the rear end of the rear cover 170 may be determined. The rear cover 170 may be spring-supported to the supporter 137.

In addition, the linear compressor 10 further includes an inflow guide 156 coupled to the rear cover 170 to guide the inflow of the refrigerant into the muffler 150. At least a portion of the inflow guide 156 may be inserted into the suction muffler 150.

In addition, the linear compressor 10 further includes a plurality of resonant springs 176a and 176b whose natural frequencies are adjusted to allow the piston 130 to resonate. The plurality of resonant springs 176a and 176b may include a first resonant spring 176a supported between the supporter 137 and the stator cover 149 and between the supporter 137 and the rear cover 170. A supported second resonant spring 176b is included.

By the action of the plurality of resonant springs (176a, 176b), the stable movement of the drive unit reciprocating in the linear compressor 10 is performed, it is possible to reduce the vibration or noise generated by the movement of the drive unit.

In addition, the linear compressor 10 includes a discharge unit 190 and a discharge valve assembly 160.

The discharge unit 190 forms a discharge space D of the refrigerant discharged from the compressed space P. The discharge unit 190 includes a discharge cover 191 coupled to the front surface of the frame 110 and a discharge plenum 192 disposed inside the discharge cover 191. In addition, the discharge unit 190 may further include a cylindrical fixing ring 193 in close contact with the inner circumferential surface of the discharge plenum 192.

The discharge valve assembly 160 is coupled to the inside of the discharge unit 190 and discharges the refrigerant compressed in the compression space P to the discharge space D. In addition, the discharge valve assembly 160 may include a spring assembly 163 which provides an elastic force in a direction in which the discharge valve 161 and the discharge valve 161 is in close contact with the front end of the cylinder 120. .

The spring assembly 163 may include a valve spring 164 in the form of a leaf spring, a spring support 165 positioned at an edge of the valve spring 164 to support the valve spring 164, and the spring support ( A friction ring 166 fitted to the outer circumferential surface of the 165 is included.

The front center portion of the discharge valve 161 is fixedly coupled to the center of the valve spring 164. In addition, the rear surface of the discharge valve 161 is in close contact with the front (or front) of the cylinder 120 by the elastic force of the valve spring 164.

When the pressure of the compression space (P) is more than the discharge pressure, the valve spring 164 is elastically deformed toward the discharge plenum 192. In addition, the discharge valve 161 is spaced apart from the front end of the cylinder 120, so that the refrigerant is discharge space (D) (or discharge) formed in the discharge plenum 192 in the compression space (P) Chamber).

That is, when the discharge valve 161 is supported on the front surface of the cylinder 120, the compression space (P) maintains a closed state, the discharge valve 161 is spaced apart from the front surface of the cylinder 120 When the compression space (P) is opened, the compressed refrigerant in the compression space (P) can be discharged.

In addition, the linear compressor 10 may further include a cover pipe 195. The cover pipe 195 discharges the refrigerant flowing to the discharge unit 190 to the outside. At this time, one end of the cover pipe 195 is coupled to the discharge cover 191, the other end is coupled to the discharge pipe 105. In addition, the cover pipe 195 may be formed of a flexible material, and at least a portion thereof may extend roundly along the inner circumferential surface of the shell 101.

In addition, the linear compressor 10 includes a plurality of sealing members for increasing the coupling force between the frame 110 and the components around the frame 110. The plurality of sealing members may have a ring shape.

In detail, the plurality of sealing members include first and second sealing members 129a and 129b provided at portions where the frame 110 and the cylinder 120 are coupled to each other. In this case, the first sealing member 129a is inserted into the frame 110 and installed, and the second sealing member 129b is inserted into the cylinder 120.

In addition, the plurality of sealing members include a third sealing member 129c provided at a portion at which the frame 110 and the inner stator 148 are coupled to each other. The third sealing member 129c may be inserted into the outer surface of the frame 110 and installed.

In addition, the plurality of sealing members may include a fourth sealing member 129d provided at a portion at which the frame 110 and the discharge cover 191 are coupled to each other. The fourth sealing member 129d may be inserted into the front surface of the frame 110 and installed.

In addition, the linear compressor 10 includes support devices 180 and 185 for fixing the compressor main body to the inner side of the shell 101. The support device includes a first support device 185 disposed on the suction side of the compressor body and a second support device 180 disposed on the discharge side of the compressor body.

The first support device 185 includes a suction spring 186 provided in a circular plate spring shape and a suction spring support 187 fitted to a central portion of the suction spring 186.

The outer edge of the suction spring 186 may be fixed to the rear surface of the rear cover 170 by a fastening member. The suction spring support 187 is coupled to the cover support 102a disposed at the inner center of the first shell cover 102. Accordingly, the rear end of the compressor main body may be elastically supported at the center of the first shell cover 102.

In addition, a suction stopper 102b may be provided at an inner edge of the first shell cover 102. The suction stopper 102b prevents the main body of the compressor, in particular, the motor assembly 140 from colliding with the shell 101 by the shaking, vibration, or impact generated during the transportation of the linear compressor 10. It is understood as a configuration.

In particular, the suction stopper 102b may be positioned adjacent to the rear cover 170. Accordingly, when shaking occurs in the linear compressor 10, the rear cover 170 may interfere with the suction stopper 102b to prevent the shock from being transmitted directly to the motor assembly 140.

The second support device 180 includes a pair of discharge support parts 181 extending in the radial direction. One end of the discharge support 181 is fixed to the discharge cover 191, and the other end is in close contact with the inner circumferential surface of the shell 101. Accordingly, the discharge support 181 may support the compressor body in the radial direction.

For example, the pair of discharge support parts 181 are disposed in a state in which they are opened at an angle ranging from 90 to 120 degrees in the circumferential direction with respect to the bottom end closest to the bottom surface. That is, the lower part of the compressor main body can support two points.

In addition, the second support device 180 may include a discharge spring (not shown) installed in the axial direction. For example, the discharge spring (not shown) may be disposed between the upper end of the discharge cover 191 and the second shell cover 103.

Based on this configuration, the compression process of the refrigerant will be described. As the linear compressor 10 is driven, the piston 130 is reciprocated axially in the cylinder 120. That is, power is input to the motor assembly 140, and the piston 130 may move together with the permanent magnet 146.

Accordingly, refrigerant is sucked into the shell 101 through the suction pipe 104. In addition, the suction refrigerant flows into the piston 130 through the muffler 150.

At this time, when the pressure of the compression space (P) is less than the suction pressure of the refrigerant, the suction valve 135 is deformed to open the compression space (P). Accordingly, the suction refrigerant contained in the piston 130 may flow into the compression space (P).

In addition, when the pressure of the compression space (P) is higher than the suction pressure of the refrigerant, the compression space (P) is closed by the suction valve 135. In addition, the refrigerant contained in the compression space P may be compressed by advancing the piston 130.

In addition, when the pressure of the compression space (P) is more than the pressure of the discharge space (D), the valve spring 164 is deformed forward and the discharge valve 161 is separated from the cylinder (120). That is, the compression space P is opened by the discharge valve 161. Accordingly, the refrigerant compressed in the compression space P flows into the discharge space D through the spaced space between the discharge valve 161 and the cylinder 120.

In addition, when the pressure of the compression space (P) is less than the pressure of the discharge space (D), the valve spring 164 provides a restoring force to the discharge valve 161, the discharge valve 161 is It is in close contact with the front end of the cylinder 120 again. That is, the compression space P is closed by the discharge valve 161.

The refrigerant flowing into the discharge space D is sequentially passed through the cover pipe 195 and the discharge pipe 105 to be discharged to the outside of the shell 101. In addition, the refrigerant discharged from the linear compressor 10 may be sucked into the linear compressor 10 and circulated through the predetermined device.

At this time, the compressed high-temperature refrigerant flows in the discharge space (D). Referring to FIG. 3, the front surface of the cylinder 120 is disposed to form the discharge space D. That is, the compressed high temperature refrigerant may flow in the front surface of the cylinder 120.

Accordingly, the front surface of the cylinder 120 receives a relatively large amount of lead in a high temperature refrigerant. In addition, such heat may be transferred to the cylinder 120 and the piston 130 accommodated in the cylinder 120. As a result, the temperature of the suction refrigerant flowing into the piston 130 is increased, thereby lowering the compression efficiency.

The linear compressor 10 according to the spirit of the present invention is provided with a heat insulating member 200 for preventing such heat transfer. The heat insulating member 200 may be disposed between the cylinder 120 and the discharge unit 190. That is, the heat insulating member 200 may be located at the rear of the discharge space (D).

In particular, the heat insulating member 200 may be disposed to cover the front surface of the cylinder 120. Hereinafter, the cylinder 120 and the heat insulating member 200 will be described in detail.

4 is an exploded view illustrating the cylinder and the heat insulating member of the linear compressor according to the first embodiment of the present invention.

As shown in FIG. 4, the cylinder 120 includes a cylinder body 121 extending in the axial direction and a cylinder flange 122 extending radially outward from the cylinder body 121. In this case, the cylinder body 121 and the cylinder flange 122 may be integrally formed with each other.

The cylinder body 121 is provided in a cylindrical shape in which the upper and lower ends in the axial direction are opened. In addition, the cylinder body 121 is provided with a piston accommodating portion 121a in which the piston 130 is accommodated. In detail, the piston body 131 is accommodated in the piston accommodating part 121a.

In addition, a portion of the piston accommodating part 121a may form the compression space P. FIG. In detail, the portion corresponding to the front of the piston body 131 of the piston receiving portion 121a may be understood as the compression space P.

In the cylinder body 121, a gas inlet 1210 through which the gas refrigerant flowing through the frame 110 flows is formed. Referring to FIG. 3, the frame 110 includes a gas hole 1106 through which a predetermined gas refrigerant flows and a gas flow passage 1130 extending from the gas hole 1106.

In particular, the gas passage 1130 extends through the frame 110 to the gas inlet 1210. That is, the gas passage 1130 provides a predetermined gas refrigerant to the outer circumferential surface of the cylinder body 121. At this time, the gas refrigerant corresponds to a part of the refrigerant discharged from the compression space (P).

The gas inlet 1210 is formed to be recessed radially inward from the outer circumferential surface of the cylinder body 121. In particular, the gas inlet 1210 may be formed to narrow the area along the radially inner side. Accordingly, the radially inner end of the gas inlet 1210 may form a tip.

In addition, the gas inlet 1210 extends in the circumferential direction along the outer circumferential surface of the cylinder body 121, and is configured to have a circular shape. In addition, the gas inlet 1210 may be provided in plurality in the axial direction. For example, the gas inlet 1210 may be provided in two, and one gas inlet 1210 is disposed to communicate with the gas channel 1130.

A cylinder filter member (not shown) may be installed at the gas inlet 1210. The cylinder filter member (not shown) functions to block foreign substances of a predetermined size or more from flowing into the cylinder 120. In addition, a function of adsorbing oil contained in the refrigerant may be performed.

In addition, the gas inlet 1210 may extend to the inner circumferential surface of the cylinder body 121. That is, the gas inlet 1210 may be understood as a portion communicating with the outer circumferential surface of the piston 130. Accordingly, some of the gas refrigerant flowing into the gas inlet 1210 may flow to the outer circumferential surface of the piston 130.

In summary, the gas refrigerant introduced into the gas hole 1106 flows to the gas inlet 1210 along the gas passage 1130. Accordingly, a predetermined refrigerant may be distributed along the outer circumferential surface of the cylinder body 121.

In addition, some gas refrigerant may flow to the outer circumferential surface of the piston 130 through the gas inlet 1210. The gas refrigerant flowing to the outer circumferential surface of the piston 130 may be distributed along the outer surface of the piston 130.

As such, a minute space is formed between the piston 130 and the cylinder 120 through the bearing refrigerant distributed on the outer surface of the piston 130. That is, the bearing refrigerant provides a floating force to the piston 130 to perform a function of a gas bearing for the piston 130.

Through this, the piston 130 and the cylinder 120 may be prevented from being worn due to the reciprocating motion of the piston 130. That is, the bearing function can be performed without using oil through the bearing refrigerant.

The cylinder body 121 is provided with a cylinder sealing member inserting portion 1212 into which the second sealing member 129b is inserted. The cylinder sealing member insertion part 1212 may be recessed inward in the radial direction from the outer circumferential surface of the cylinder body 121.

In addition, the cylinder sealing member insertion part 1212 may be located behind the gas inlet part 1210. Accordingly, the second sealing member 129b may increase the coupling force between the cylinder 120 and the frame 110 and may prevent the refrigerant from leaking to the rear of the cylinder 120.

The cylinder flange 122 is provided in a disk shape having a predetermined thickness in the axial direction. In detail, the cylinder flange 122 is provided in a ring shape having a predetermined thickness in the axial direction due to the piston receiving portion 121a provided at the radial center side.

In particular, the cylinder flange 122 extends radially at the front end of the cylinder body 121. The first sealing member 129a is disposed at the rear portion of the cylinder flange 122.

The first sealing member 129a may be disposed between the frame 110 and the cylinder 120 to increase the coupling force between the frame 110 and the cylinder 120. In addition, the first sealing member 129a may be installed in the frame 110 as described above.

In this case, the front surface of the cylinder 120 may be disposed on the same line in the radial direction as the front surface of the frame 110. That is, the cylinder 120 is inserted into and disposed inside the frame 110 as a whole. Hereinafter, the entire surface of the cylinder 120 is referred to as the discharge cylinder surface 1200.

The discharge cylinder surface 1200 may be understood to form a rear portion of the discharge space D together with the front surface of the frame 110. In detail, the discharge cylinder surface 1200 is located in an inner space formed by combining the frame 110 and the discharge cover 191. That is, a high temperature coolant may flow in the discharge cylinder surface 1200.

In addition, the discharge valve 161 and the heat insulating member 200 may be seated on the discharge cylinder surface 1200. In particular, the heat insulating member 200 may be seated on the discharge cylinder surface 1200 to reduce the contact area between the discharge cylinder surface 1200 and the high temperature refrigerant.

In addition, the discharge cylinder surface 1200 is provided in a ring shape extending in the radial direction as a whole. That is, the discharge cylinder surface 1200 is provided in a ring shape having an inner diameter and an outer diameter. At this time, the opening formed at the center side of the discharge cylinder surface 1200, that is, the inner diameter is formed by the piston receiving portion 121a.

The discharge cylinder surface 1200 has a cylinder heat insulating seating portion 1202 in which at least a portion of the heat insulating member 200 is seated. The cylinder insulation seating part 1202 may be formed by being recessed in the discharge cylinder surface 1200. In detail, the cylinder insulation seating portion 1202 is recessed axially rearward from the discharge cylinder surface 1200.

In addition, the cylinder insulation seating part 1202 may be formed at a radially center side of the discharge cylinder surface 1200. In detail, the cylinder insulation seating portion 1202 may extend in the circumferential direction and may be formed in a shape recessed in a ring shape as a whole. In addition, the diameter of the cylinder insulation seating portion 1202 is larger than the inner diameter of the discharge cylinder surface 1200 and smaller than the outer diameter.

The numerical value, for example, the depth recessed in the axial rear of the cylinder insulation seating unit 1202 may be formed differently according to the design. In addition, the cylinder insulation seating portion 1202 may be omitted as necessary.

In addition, a discharge valve seat 1204 on which at least a portion of the discharge valve 161 is seated is formed on the discharge cylinder surface 1200. The discharge valve seating portion 1204 may protrude from the discharge cylinder surface 1200. In detail, the discharge valve seating part 1204 may be formed to protrude axially forward from the discharge cylinder surface 1200.

In addition, the discharge valve seating portion 1204 may be formed at the radially inner end. In detail, the discharge valve seating part 1204 may be formed to extend in the circumferential direction and protrude in a ring shape as a whole. The inner diameter of the discharge valve seating portion 1204 is provided to be the same as the inner diameter of the discharge cylinder surface 1200.

Such a value of the discharge valve seating portion 1204, for example, the height protruding in the axial direction may be formed differently depending on the design. In addition, the discharge valve seating portion 1204 may be omitted as necessary.

Thus, the discharge cylinder surface 1200 is formed stepped in the axial direction. In detail, the discharge cylinder surface 1200 has the discharge valve seating portion 1204 protruded in the axial direction, and the cylinder insulating seating portion 1202 is recessed to form a step in three steps. In addition, the discharge valve seating portion 1204 is formed at the innermost side in the radial direction.

In addition, a heat insulating member fixing part 1206 may be formed on the discharge cylinder surface 1200. The heat insulating member fixing part 1206 is formed between the discharge valve seating portion 1204 and the cylinder heat insulating seating portion 1202 in a radial direction.

The heat insulating member fixing part 1206 is formed by being recessed in the discharge cylinder surface 1200. In detail, the heat insulating member fixing part 1206 may be formed in a plurality of recessed in the axial direction and spaced apart in the circumferential direction. In this case, the heat insulating member 200 may have a heat insulating member protrusion (not shown) inserted into the heat insulating member fixing part 1206.

Therefore, at least a part of the heat insulating member 200 may be inserted into the heat insulating member fixing part 1206. Accordingly, the heat insulating member 200 can be prevented from rotating in the circumferential direction. In FIG. 4, the insulating member fixing part 1206 is recessed in a circular shape and illustrated as four spaced apart in the circumferential direction, but this is merely exemplary.

The heat insulating member 200 has an inner diameter and an outer diameter, and may be formed in a ring shape extending in a radial direction. In this case, the heat insulating member 200 includes a first heat insulating part 2002 and a second heat insulating part 2004.

The first heat insulating part 2002 is provided to form a circular opening corresponding to the inner diameter. The first heat insulating part 2002 is disposed to radially contact the discharge valve seating part 1204. In other words, the outer diameter of the discharge valve seating portion 1204 and the inner diameter of the heat insulating member 200 may be provided in the same manner.

In addition, the axial length of the first heat insulating part 2002 may be the same as the height of the discharge valve seating portion 1204 protrudes in the axial direction. Accordingly, the axial upper surface of the first heat insulating part 2002 and the discharge valve seating part 1204 may be disposed on the same line.

In addition, the discharge valve 161 is seated on the axial upper surface of the first heat insulating part 2002 and the discharge valve seating portion 1204. That is, at least a part of the discharge valve 161 may be arranged to contact the heat insulating member 200.

The second heat insulation portion 2004 is located radially outward of the first heat insulation portion 2002. That is, the heat insulating member 200 may extend radially outward from the first heat insulating portion 2002 to the second heat insulating portion 2004. In addition, the second heat insulating part 2004 may be seated on the cylinder heat insulating seating part 1202.

In addition, the axial length of the second heat insulating part 2004 is greater than the axial length of the first heat insulating part 2002. In addition, an axial length of the second heat insulating part 2004 may be greater than a depth in which the cylinder heat insulating seating part 1202 is recessed in the axial direction.

Accordingly, when the second heat insulating part 2004 is seated on the cylinder heat insulating seating part 1202, at least a part of the second heat insulating part 2004 may protrude axially from the discharge cylinder surface 1200. Can be.

In this case, the discharge valve assembly 160 is positioned above the second heat insulating part 2004 in the axial direction. In detail, the second heat insulating part 2004 is disposed between the cylinder heat insulating seating part 1202 and the spring support part 165.

In particular, the second heat insulating part 2004 may be formed of an elastic material to be in close contact with the cylinder heat insulating seating part 1202 and the spring support part 165. Accordingly, it is possible to prevent the refrigerant from leaking between the discharge cylinder surface 1200 and the spring support 165.

In addition, the second heat insulating part 2004 may form a circular appearance corresponding to the outer diameter. That is, the heat insulating member 200 is provided in a shape extending radially outward from the first heat insulating portion 2002 to the second heat insulating portion 2004.

In addition, the outer diameter of the heat insulating member 200 is provided corresponding to the diameter of the cylinder heat insulating seating portion 1202. In this case, the corresponding means that the outer diameter of the heat insulating member 200 is smaller than the outer diameter of the cylinder heat-insulating seating portion 1202 and larger than the inner diameter.

As such, the heat insulating member 200 is provided to cover most of the discharge cylinder surface 1200. In this case, part of the discharge cylinder surface 1200 disposed radially outward from the heat insulating member 200 may prevent heat transfer because the flow of the discharge refrigerant is blocked by the second heat insulating part 2004.

In addition, the heat insulating member 200 may be formed of a material having a low heat transfer coefficient. For example, it may be provided with a material formed with plastic or heat shield coding. Accordingly, it is possible to minimize the transfer of the heat of the refrigerant discharged from the compression space (P) to the discharge cylinder surface 1200.

Based on such a structure, each situation when the linear compressor 10 is driven will be described.

5 is a view illustrating part 'A' of FIG. 3 according to the operation of the linear compressor.

5 illustrates the movement of the discharge valve 161 according to the driving of the linear compressor 10. In particular, the movement of the discharge valve 161 according to the relative pressure of the compression space (P) and the discharge space (D) is shown. However, this is a schematic view of the condition and movement for convenience of description and the present invention is not limited thereto.

In detail, (a) of FIG. 5 corresponds to a case where the pressures of the compression space P and the discharge space D are similar, and FIG. 5 (b) shows a case where the pressure of the compression space P is high. Corresponds to 5C corresponds to the case where the pressure of the discharge space D is high.

As shown in FIG. 5, the discharge valve 161 is seated on the discharge valve seat 1204 in the radially outer side. At this time, the radial length of the discharge valve seating portion 1204 is called seating length (L1).

In addition, as described above, the discharge valve seating portion 1204 is formed in the radially inner side of the discharge cylinder surface 1200, the heat insulating member 200 on the radially outer side of the discharge valve seating portion 1204. Is encountered. Therefore, the seating portion length L1 may be calculated as a value obtained by subtracting the inner radius of the discharge cylinder surface 1200 from the inner radius of the heat insulating member 200.

In addition, a radial length in which the discharge valve 161 and the discharge cylinder surface 1200 overlap each other is referred to as a valve length L2. The valve length L2 may be calculated by subtracting the inner radius of the discharge cylinder surface 1200 from the outer radius of the discharge valve 161.

In detail, the outer end of the discharge valve 161 extends radially outward from the discharge valve seat 1204. Accordingly, the valve length L2 is provided longer than the seating portion length L1 (L1 <L2).

In addition, as described above, in the first heat insulating part 2002, the upper surface of the discharge valve seating part 1204 is disposed on the same line in the axial direction. Therefore, the discharge valve 161 may be disposed such that at least part of the heat insulating member 200 is in contact with the discharge valve 161. The radial length that the discharge valve 161 and the heat insulating member 200 contact each other corresponds to a value obtained by subtracting the seating length L1 from the valve length L2.

At this time, the valve length (L2) corresponds to the length for the discharge valve 161 is seated stably. Therefore, the valve length L2 is assumed to be a fixed value.

The seating portion length L1 corresponds to a radially inner length of the discharge cylinder surface 1200 that is not in contact with the heat insulating member 200. That is, the longer the seating portion length L1, the more the discharge cylinder surface 1200 may be exposed to the discharge refrigerant. That is, the heat of the discharge refrigerant may be more transferred to the discharge cylinder surface 1200.

On the other hand, as the seating portion length L1 is shorter, the length of the discharge valve 161 and the heat insulating member 200 is in contact with each other. Therefore, a relatively large external force may be applied to the heat insulating member 200 as the discharge valve 161 moves. Accordingly, there is a risk that breakage or the like of the heat insulating member 200 occurs.

Therefore, the seating portion length L1 should be appropriately provided. For example, the seating portion length L1 may be provided larger than 0.7 times the valve length L2 (0.7 * L2 <L1 <L2). This length is determined by experiment and can be calculated differently according to external conditions.

As shown in FIG. 5A, when the pressure of the compression space P and the discharge space D are similar, the discharge valve 161 is radially parallel to the discharge cylinder surface 1200. To be seated. For example, this may be the case when the compression space P is closed and the refrigerant is compressed.

At this time, the high-temperature discharge refrigerant compressed in the compression space (P) exists in the axial front of the discharge valve (161). In this case, the heat of the discharge refrigerant may not be directly transmitted to the discharge cylinder surface 1200 by the heat insulating member 200. That is, the heat insulating member 200 may cover the discharge cylinder surface 1200 to prevent exposure to the discharge refrigerant.

In addition, the second heat insulating part 2004 may prevent the discharge refrigerant from flowing outward in the radial direction. Accordingly, heat is not directly transferred by the discharge refrigerant to the outer end of the discharge cylinder surface 200 in which the heat insulating member 200 does not exist.

As shown in FIG. 5B, when the pressure of the compression space P is high, the discharge valve 161 is spaced axially forward from the discharge cylinder surface 1200. For example, the compression may be completed by the piston 130, the compression space P is opened by the discharge valve 161, and the compressed refrigerant may be discharged.

As shown by arrows in FIG. 5B, discharge refrigerant flows from the compression space P to the discharge space D. FIG. At this time, most of the discharge cylinder surface 1200 is not exposed to the discharge refrigerant by the heat insulating member 200. That is, the heat of the discharge refrigerant may be prevented from being transferred to the discharge cylinder surface 1200.

As shown in FIG. 5C, when the pressure of the discharge space D is high, the discharge valve 161 is moved axially backward toward the discharge cylinder surface 1200. For example, the compression space P may be opened by the suction valve 135 so that the suction refrigerant flows into the compression space P.

At this time, the discharge valve 161 is moved to the rear in the axial direction and in close contact with the discharge cylinder surface 1200. In particular, the radially outer side of the discharge valve 161 is in close contact with the discharge cylinder surface 1200 is limited to move in the axial direction. Then, the center side of the discharge valve 161 is further protruded in the axial direction to the pressure of the refrigerant. Therefore, as a whole, the center side is convexly protruded rearward and is provided in the form of a bent waist.

In this process, an impact is applied to the discharge cylinder surface 1200 by the movement of the discharge valve 161. At this time, since the outer end of the discharge valve 161 is disposed in an inclined state, only the discharge valve seating portion 1204 may be contacted.

That is, the discharge valve 161 may not contact the heat insulating member 200. Therefore, the external force due to the impact is not applied to the heat insulating member 200. Therefore, breakage of the heat insulating member 200 can be prevented.

In the above, the heat insulating member 200 seated on the cylinder 120 has been described. The heat of the discharge refrigerant can be prevented from being transferred to the cylinder 120 by the heat insulating member 200.

In this case, heat may also be transferred to the frame 110 accommodating the cylinder 120 by the discharge refrigerant. Accordingly, the heat insulating member according to the spirit of the present invention may be seated on the cylinder 120 and the frame 110 to prevent heat transfer of the discharged refrigerant.

For convenience of description, FIGS. 1 to 5 are referred to as the linear compressor according to the first embodiment, and FIGS. 6 to 8 are referred to as the linear compressor according to the second embodiment. In this case, the linear compressors according to the first and second embodiments are provided in the same configuration except for the front surface of the cylinder 120 and the frame 110 on which the heat insulating member and the heat insulating member are seated.

Therefore, the same reference numerals are used, and redundant descriptions are omitted and the above descriptions are cited. In addition, in the case of a similar configuration, the reference numeral 'a' is used to identify the difference. Hereinafter, the heat insulating member 200a of the linear compressor according to the second embodiment will be described.

6 is an exploded view illustrating a discharge unit, a frame, a cylinder, and a heat insulating member of a linear compressor according to a second embodiment of the present invention, and FIG. 7 is a discharge unit of a linear compressor according to a second embodiment of the present invention. , A cross-sectional view of the coupling section of the frame, the cylinder and the heat insulating member. 8 is an enlarged view of a portion 'B' of FIG. 7.

6 and 7, the frame 110 and the discharge unit 190 will be described in detail. This is common to both linear compressors according to the first and second embodiments.

6 and 7, the discharge unit 190 and the frame 110 may be coupled through a predetermined fastening member (not shown). In particular, the discharge unit 190 and the frame 110 may be coupled to support three points.

The frame 110 includes a frame body 111 extending in the axial direction and a frame flange 112 extending radially outward from the frame body 111. In this case, the frame body 111 and the frame flange 112 may be integrally formed with each other.

The frame body 111 is provided in a cylindrical shape in which the upper and lower ends in the axial direction are opened. In addition, a cylinder accommodating part (not shown) in which the cylinder 120 is accommodated is provided in the frame body 111. Accordingly, the cylinder 120 is accommodated in the radially inner side of the frame body 111, and at least a portion of the piston 130 is accommodated in the radially inner side of the cylinder 120.

In addition, sealing member inserting parts 1117 and 1118 are formed in the frame main body 111. The sealing member inserting part is formed inside the frame main body 111 to insert the first sealing member 129a. A first sealing member insert 1117 is included. In addition, the sealing member inserting portion includes a third sealing member inserting portion 1118 formed on the outer circumferential surface of the frame main body 111 and into which the third sealing member 129c is inserted.

In addition, the inner stator 148 is coupled to a radially outer side of the frame body 111. In addition, the outer stator 141 is disposed on the radially outer side of the inner stator 148, and the permanent magnet 146 is movably disposed between the inner stator 148 and the outer stator 141. do.

The frame flange 112 is provided in a disk shape having a predetermined thickness in the axial direction. In detail, the frame flange 112 is provided in a ring shape having a predetermined thickness in the axial direction due to the cylinder receiving portion (not shown) provided on the radial center side.

In particular, the frame flange 112 extends radially at the front end of the frame body 111. Accordingly, the inner stator 148, the permanent magnet 146, and the outer stator 141 disposed on the radially outer side of the frame body 111 are disposed axially behind the frame flange 112. .

In addition, the frame flange 112 is formed with a plurality of openings penetrating in the axial direction. In this case, the plurality of openings include a discharge fastening hole 1100, a stator fastening hole 1102, and a terminal insertion hole 1104.

A predetermined fastening member (not shown) for fastening the discharge cover 191 and the frame 110 is inserted into the discharge fastening hole 1100. In detail, the fastening member (not shown) may be inserted into the front of the frame 110 through the discharge cover 191.

The cover fastening member 149a described above is inserted into the stator fastening hole 1102. The cover fastening member 149a couples the stator cover 149 and the frame 110 to the axial direction of the outer stator 141 disposed between the stator cover 149 and the frame 110. Can be fixed

The terminal insertion hole 1104 is inserted into the terminal portion 141d of the outer stator 141 described above. That is, the terminal portion 141d may be penetrated forward from the rear of the frame 110 through the terminal insertion hole 1104 to be drawn out or exposed to the outside.

In this case, the discharge fastening hole 1100, the stator fastening hole 1102 and the terminal insertion hole 1104 may be provided in plural numbers, and may be sequentially spaced apart in the circumferential direction. For example, the discharge fastening holes 1100, the stator fastening holes 1102, and the terminal insertion holes 1104 may be provided in three, respectively, and may be disposed at intervals of 120 degrees in the circumferential direction.

In addition, the terminal insertion hole 1104, the discharge fastening hole 1100, and the stator fastening hole 1102 are sequentially spaced apart in the circumferential direction. In addition, the adjacent openings may be spaced apart by 30 degrees in the circumferential direction.

For example, the terminal insertion holes 1104 and the discharge coupling holes 1100 are spaced apart by 30 degrees in the circumferential direction. In addition, each of the discharge fastening holes 1100 and the stator fastening holes 1102 are spaced apart by 30 degrees in the circumferential direction. On the other hand, each of the terminal insertion hole 1104 and the stator fastening hole 1102 is disposed spaced 60 degrees in the circumferential direction.

Each arrangement is based on the circumferential center of the terminal insertion hole 1104, the discharge fastening hole 1100, and the stator fastening hole 1102.

At this time, the front surface of the frame flange 112 is called the discharge frame surface 1120, the rear surface is referred to as the motor frame surface 1125. That is, the discharge frame surface 1120 and the motor frame surface 1125 correspond to surfaces facing in the axial direction. In detail, the discharge frame surface 1120 corresponds to a surface in contact with the discharge cover 191. In addition, the motor frame surface 1125 corresponds to a surface adjacent to the motor assembly 140.

In addition, the gas hole 1106 described above is formed in the discharge frame surface 1120. The gas hole 1106 is formed recessed in the axial direction from the discharge frame surface 1120. In addition, the gas hole 1106 may be equipped with a gas filter 1107 for filtering foreign matter of the flowing gas.

In addition, referring to FIG. 6, a predetermined recessed structure may be formed on the discharge frame surface 1120. This is to prevent the transfer of heat of the discharged refrigerant is not limited in its depth and shape.

As described above, the discharge unit 190 includes the discharge cover 191, the discharge plenum 192, and the fixing ring 193. The discharge cover 191, the discharge plenum 192 and the fixing ring 193 may be formed of different materials and manufacturing methods.

At this time, the discharge plenum 192 is coupled to the inside of the discharge cover 191, the fixing ring 193 is coupled to the inside of the discharge plenum 192. In particular, a plurality of discharge spaces D are formed by combining the discharge cover 191 and the discharge plenum 192. The discharge space D may be understood as a space in which the refrigerant discharged from the compression space P flows.

The discharge cover 191 may be provided in a ball shape as a whole. In detail, the discharge cover 191 may be provided in a shape in which one surface is opened and an inner space is formed. In particular, the discharge cover 191 may be arranged so that the rear in the axial direction.

The discharge cover 191 may include a cover flange portion 1910 coupled to the frame 110, a chamber portion 1915 extending axially forward from the cover flange portion 1910, and the chamber portion 1915. A support device fixture 1917 extending axially forward is included.

The cover flange portion 1910 is configured to be in close contact with the front surface of the frame 110. In detail, the cover flange portion 1910 is disposed in close contact with the discharge frame surface 1120.

In addition, the cover flange portion 1910 has a predetermined thickness in the axial direction and extends in the radial direction. Accordingly, the cover flange portion 1910 may be provided in a disk shape as a whole.

In this case, the cover flange portion 1910 is relatively smaller than the diameter of the discharge frame surface 1120. For example, the diameter of the cover flange portion 1910 may be provided as 0.6 to 0.8 times the diameter of the discharge frame surface 1120. In the conventional linear compressor, the diameter of the cover flange portion is provided at 0.9 times or more of the diameter of the discharge frame surface.

Such a structure is for minimizing heat transferred from the cover flange portion 1910 to the frame 110. In detail, as the cover flange portion 1910 is disposed in close contact with the discharge frame surface 1120, heat of the discharge cover 191 is conducted to the frame 110 through the cover flange portion 1910. Can be.

At this time, since the thermal conductivity is proportional to the contact area, the amount of heat conducted is changed according to the contact area between the cover flange portion 1910 and the discharge frame surface 1120. That is, the contact area with the discharge frame surface 1120 may be minimized by minimizing the diameter of the cover flange portion 1910. Accordingly, the amount of heat conducted from the discharge cover 191 to the frame 110 can be minimized.

In addition, a heat insulating member 200a to be described later is disposed between the discharge cover 191 and the discharge frame surface 1120. Accordingly, the heat transmitted from the discharge cover 191 to the discharge frame 1120 may be almost blocked.

In addition, as the area in contact with the cover flange portion 190 decreases, a relatively large portion of the discharge frame surface 1120 may be exposed to the inside of the shell 101.

The surface exposed to the inside of the shell 101 is in contact with the refrigerant (hereinafter, the shell refrigerant) accommodated inside the shell 101 generates heat transfer. In particular, since the shell refrigerant is provided at a temperature similar to that of the suction refrigerant, convection heat transfer is generated from the frame 110 to the shell refrigerant. In addition, since convective heat transfer is proportional to the contact area, the larger the surface exposed to the inside of the shell 101, the greater the amount of heat radiated.

In summary, as the area of the cover flange portion 1910 decreases, the heat conducted to the frame 110 decreases. In addition, heat radiation to the shell refrigerant in the frame 110 may be effectively generated.

Therefore, the temperature of the frame 110 may be kept relatively low. Accordingly, less heat is transmitted to the cylinder 120 and the piston 110 disposed inside the frame 110. As a result, the temperature of the suction refrigerant is prevented from rising, and the compression efficiency is improved.

In the central portion of the cover flange portion 1910, an opening communicating with the open axial rear is formed. Through the opening, the discharge plenum 192 may be mounted inside the discharge cover 191. In addition, the opening may be understood as an opening in which the discharge valve assembly 160 is installed.

In addition, the cover flange portion 1910 includes a flange fastening hole 1911a through which a fastening member (not shown) for coupling with the frame 110 passes. The flange fastening hole 1911a penetrates in the axial direction, and a plurality of flange fastening holes 1911a are formed.

In particular, the flange fastening hole 1911a may be provided in a size, number, and position corresponding to the discharge fastening hole 1100. Therefore, the flange fastening hole 1911a may be provided in three spaced 120 degrees in the circumferential direction.

In this case, the discharge cover 191 includes a cover fastening portion 1911 protruding radially from the cover flange portion 1910 to form the flange fastening hole 1911a. That is, the flange fastening hole 1911a is disposed radially outward of the cover flange portion 1910a. In other words, the discharge fastening hole 1100 may be located at a radially outer side of the cover flange portion 1910a.

The cover fastening portion 1911 may be provided in three spaced 120 degrees in the circumferential direction corresponding to the flange fastening hole 1911a. In addition, an edge of the cover fastening portion 1911 may be formed thicker in the axial direction than the cover flange portion 1910. This flange fastening hole (1911a) is a portion that is coupled by the fastening member, it can be understood to prevent damage because a relatively large external force is applied.

The chamber 1915 and the support device fixing unit 1917 may be formed in a cylindrical shape. In detail, the chamber 1915 and the support device fixing unit 1917 each have a predetermined outer diameter in the radial direction and extend in the axial direction. At this time, the outer diameter of the support device fixing portion 1917 is formed smaller than the outer diameter of the chamber portion 1915.

In addition, the outer diameter of the chamber portion 1915 is formed smaller than the outer diameter of the cover flange portion 1910. That is, the discharge cover 191 is formed with a step in which the outer diameter gradually decreases toward the axial front.

In addition, the chamber portion 1915 and the support device fixing portion 1917 are provided in an axial rearward open shape. Accordingly, the chamber portion 1915 and the support device fixing portion 1917 are formed in a cylindrical side surface and a circular front surface.

The chamber unit 1915 may further include a pipe coupling unit (not shown) to which the cover pipe 195 is coupled. In particular, the cover pipe 195 may be coupled to the chamber unit 1915 to communicate with any one of the plurality of discharge spaces (D). In detail, the cover pipe 195 may communicate with the discharge space D through which the refrigerant is finally passed.

In addition, an upper surface of the chamber unit 1915 may be formed by recessing at least a part of the chamber to avoid interference with the cover pipe 195. As a result, when the cover pipe 195 is coupled to the chamber portion 1915, the cover pipe 195 may be prevented from contacting the front surface of the chamber portion 1915.

In the supporting device fixing unit 1917, fixing fastening units 1917a and 1917b to which the second supporting device 180 described above is coupled are formed. The fixing fastening part includes a first fixing fastening part 1917a to which the discharge support part 181 is coupled and a second fixing fastening part 1917b to which the discharge spring (not shown) is installed.

The first fastening portion 1917a may be formed by recessing or penetrating radially inward from an outer surface of the support device fixing portion 1917. In addition, the first fastening portions 1917a may be provided in pairs spaced in the circumferential direction corresponding to the discharge support portions 181 provided as a pair.

The second fastening portion 1917b may be formed by being recessed in the axial direction from the front of the support device fixing portion 1917. Accordingly, at least a portion of the discharge spring (not shown) may be inserted into the second fastening portion 1917b.

In addition, the discharge cover 191 includes a partition sleeve 1912 for partitioning the internal space. The compartment sleeve 1912 may be formed in a cylindrical shape extending axially rearward from an upper surface of the chamber portion 1915.

In addition, the outer diameter of the partition sleeve 1912 is formed smaller than the inner diameter of the discharge cover 191. In detail, the compartment sleeve 1912 is radially spaced apart from the inner surface of the discharge cover 191 such that a predetermined space is formed between the compartment sleeve 1912 and the inner surface of the discharge cover 191. Is formed.

Accordingly, the inner space of the discharge cover 191 may be divided radially inward and outward by the partition sleeve 1912. In this case, a first discharge chamber D1 and a second discharge chamber D2 are formed in the radially inner side of the division sleeve 1912. In addition, a third discharge chamber D3 is formed at the radially outer side of the partition sleeve 1912.

In addition, the discharge plenum 192 may be fitted into the compartment sleeve 1912. In detail, at least a portion of the discharge plenum 192 may be inserted into the compartment sleeve 1912 in close contact with an inner surface of the compartment sleeve 1912.

In addition, the partition sleeve 1912 may be formed with a first guide groove 1912a, a second guide groove 1912b, and a third guide groove 1912c.

The first guide groove 1912a may be recessed radially outward from an inner side surface of the partition sleeve 1912 and extend in an axial direction. In particular, the first guide groove 1912a is formed extending from the axial front to the axial rear than the position at which the discharge plenum 192 is inserted.

The second guide groove 1912b may be recessed radially outward from the inner side surface of the partition sleeve 1912 and extend in the circumferential direction. In particular, the second guide groove 1912b is formed in the inner surface of the partition sleeve 1912 in contact with the discharge plenum 192. In addition, the second guide groove 1912b may be formed to communicate with the first guide groove 1912a.

The third guide groove 1912c may be formed to be recessed in the axial direction at the axial rear end of the partition sleeve 1912. Accordingly, the rear end of the compartment sleeve 1912 may be formed stepped. In addition, the third guide groove 1912c may be formed to communicate with the second guide groove 1912b.

That is, the third guide groove 1912c may be formed by recessing up to a portion where the second guide groove 1912b is formed. In addition, the third guide groove 1912c and the first guide groove 1912a may be formed to be spaced apart in the circumferential direction. For example, the third guide groove 1912c may be formed at a position facing the first guide groove 1912a, that is, at a position spaced 180 degrees in the circumferential direction.

Through such a structure, the refrigerant flowing into the second guide groove 1912b may be increased in the second guide groove 1912b. Accordingly, there is an effect that the pulsation noise of the refrigerant is effectively reduced.

At this time, the discharge cover 191 according to the idea of the present invention is characterized in that it is integrally manufactured by aluminum die casting. Therefore, unlike the conventional discharge cover, in the case of the discharge cover 191 of the present invention, the welding process can be omitted. Therefore, the manufacturing process of the discharge cover 191 is simplified, and as a result, product defects are minimized, thereby reducing the product cost. In addition, since there is no dimensional tolerance due to welding, leakage of the refrigerant can be prevented.

Accordingly, the cover flange portion 1910, the chamber portion 1915, and the support device fixing portion 1917 described above may be integrally formed and separated for convenience of description.

The discharge plenum 192 includes a plenum flange 1920, a plenum seat 1922, a plenum body 1924, and a plenum extension 1926. In this case, the discharge plenum 192 may be integrally formed of engineering plastic. That is, each configuration of the discharge plenum 192 to be described later is divided for convenience of description.

In addition, each configuration of the discharge plenum 192 may be formed to the same thickness. Accordingly, the plenum flange 1920, the plenum seating portion 1922, the plenum body 1924, and the plenum extension 1926 may be provided to extend in the same thickness.

The plenum flange 1920 forms an axial bottom surface of the discharge plenum 192. That is, the plenum flange 1920 is located at the lowermost side in the axial direction from the discharge plenum 192. In detail, the plenum flange 1920 has an axial thickness and may be provided in a ring shape extending in a radial direction.

At this time, the outer diameter of the plenum flange 1920 is provided with a size corresponding to the inner diameter of the discharge cover 191. In this case, the corresponding means the same or considering the assembly tolerance in the inner diameter of the discharge cover 191.

In particular, the plenum flange 1920 functions to close the axial rear of the third discharge chamber D3. That is, as the plenum flange 1920 is seated inside the discharge cover 191, the refrigerant of the third discharge chamber D3 may be prevented from flowing backward in the axial direction.

In addition, the inner diameter of the plenum flange 1920 is provided with a size corresponding to the spring assembly 163. In detail, the plenum flange 1920 may extend radially inward adjacent to an outer surface of the spring support 165.

The plenum seat 1922 extends radially inward from the plenum flange 1920 such that the spring assembly 163 is seated. In detail, the plenum seating portion 1922 extends bent axially forward at the radially inner end of the plenum flange 1920 and is bent again radially inward. Accordingly, the plenum seating portion 1922 is provided in a cylindrical shape in which one end located in the axial front as a whole is bent radially inward.

At this time, the plenum seating portion 1922 is in contact with the axial rear end of the compartment sleeve 1912. In other words, the compartment sleeve 1912 extends axially rearward from the inside of the front of the chamber portion 1915 to the plenum seating portion 1922. That is, the plenum seater 1922 may be understood to be disposed between the spring support 165 and the partition sleeve 1912 in the axial direction.

At this time, the axial rear end of the plenum seating portion 1922 and the partition sleeve 1912 are in close contact with each other. In other words, the plenum seat 1922 and the compartment sleeve 1912 are understood to be in axial contact. Accordingly, it is possible to prevent the refrigerant from flowing between the plenum seating portion 1922 and the compartment sleeve 1912.

As described above, the third guide groove 1912c is formed to be recessed in the axial direction at the rear end of the partition sleeve 1912. Accordingly, the refrigerant may flow along the third guide groove 1912c between the compartment sleeve 1912 and the plenum seat 1922. That is, the third guide groove 1912c forms a flow path of the refrigerant passing through the partition sleeve 1912 and the plenum seating portion 1922.

The plenum body 1924 extends radially inward from the plenum seat 1922 to form a first discharge chamber D1. In detail, the plenum body 1924 extends bent axially forward at the radially inner end of the plenum seat 1922 and is bent again radially inward.

Accordingly, the plenum body 1924 is provided in a cylindrical shape, one end of which is located in the axial front as a whole is bent inward in the radial direction. At this time, the inner surface of the plenum body 1924 and the partition sleeve 1912 is in close contact with each other. In other words, it is understood that the plenum body 1924 and the compartment sleeve 1912 are in radial contact with each other. Accordingly, it is possible to prevent the refrigerant from flowing between the plenum body 1924 and the compartment sleeve 1912.

As described above, the first and second seating grooves 1912a and 1912b are formed by being recessed in the inner surface of the partition sleeve 1912. Accordingly, the refrigerant may flow through the partition sleeve 1912 and the plenum body 1924 along the first and second seating grooves 1912a and 1912b. That is, the first and second seating grooves 1912a and 1912b form a flow path of the refrigerant passing through the partition sleeve 1912 and the plenum body 1924.

In addition, the first discharge chamber D1 and the second discharge chamber D2 may be divided based on the plenum body 1924b. In detail, the first discharge chamber D1 is formed at the axial rear of the plenum body 1924, and the second discharge chamber D2 is formed at the axial front of the plenum body 1924. .

The plenum extension 1926 extends axially rearward at the radially inner end of the plenum body 1924. That is, the opening formed in the central portion of the plenum body 1924 extends rearward in the axial direction to form a predetermined passage.

In this way, the coolant of the first discharge chamber D1 flows to the second discharge chamber D2 in the passage formed by the plenum extension 1926. In particular, the refrigerant of the first discharge chamber D1 may flow forward along the plenum extension 1926.

The plenum extension 1926 may also extend axially rearward to contact the spring assembly 163. In detail, the axial rear end of the plenum extension 1926 may abut the front surface of the spring support 165.

The fixing ring 193 is inserted into an inner circumferential surface of the discharge plenum 192. Accordingly, the discharge plenum 192 can be prevented from being separated from the discharge cover 191.

That is, the fixing ring 193 may be understood as a configuration for fixing the discharge plenum 192. In particular, the fixing ring 193 may be inserted into the inner circumferential surface of the plenum body 1924 by a press pitting method.

The fixing ring 193 may be formed of a material having a thermal expansion coefficient greater than that of the discharge plenum 192. For example, the fixing ring 193 is formed of stainless steel, and the discharge plenum 192 is formed of an engineering plastic material.

In this case, the fixing ring 193 may be formed to have a predetermined assembly tolerance with the discharge plenum 192 at room temperature. Accordingly, the fixing ring 193 can be relatively easily coupled to the discharge plenum 192.

When the linear compressor 10 starts, the discharge plenum 192 and the fixing ring 193 are expanded by receiving heat from the refrigerant discharged from the compression space P. In this case, the fixing ring 193 may be inflated more than the discharge plenum 192 to be in close contact with the discharge plenum 192. Accordingly, the discharge plenum 192 may be in close contact with the discharge cover 191.

In addition, the discharge plenum 192 is strongly adhered to the discharge cover 191 side by the fixing ring 193, so that the refrigerant leaks between the discharge cover 191 and the discharge plenum 192. Can be prevented.

In addition, the linear compressor 10 includes a gasket 194 disposed between the frame 110 and the discharge cover 191. In detail, the gasket 194 is disposed between the cover coupler 1911 and the discharge frame surface 1120.

In particular, the gasket 194 may be located at a portion where the frame 110 and the discharge cover 191 are fastened. That is, the gasket 194 is understood as a configuration for tightly coupling the frame 110 and the discharge cover 191.

The gasket 194 may be provided in plural numbers. In particular, the plurality of gaskets 194 are provided at a number and positions corresponding to the flange fastening hole 1911a and the discharge fastening hole 1100. That is, the plurality of gaskets 194 may be provided in three spaced 120 degrees in the circumferential direction.

In addition, the gasket 194 is provided in a ring shape having a gasket through hole 194a formed at a center side thereof. The gasket through hole 194a may have a size corresponding to the flange fastening hole 1911a and the discharge fastening hole 1100.

In addition, the outer diameter of the gasket 194 may be smaller than the outer side of the cover coupling portion 1911. Accordingly, when the gasket through hole 194a is disposed to coincide with the flange fastening hole 1911a, the gasket 194 may be positioned inside the cover coupling part 1911.

The discharge cover 191, the gasket 194, and the frame 110 sequentially rotate the flange fastening hole 1911a, the gasket through hole 194a, and the discharge fastening hole 1100 in the axial direction from the top downward. Laminated to be placed. In addition, as the fastening member penetrates through the flange fastening hole 1911a, the gasket through hole 194a, and the discharge fastening hole 1100, the discharge cover 191, the gasket 194, and the frame 110. ) May be combined.

Hereinafter, the flow of the refrigerant in the discharge space D will be described in detail based on such a configuration. As described above, the discharge space D includes the first discharge chamber D1, the second discharge chamber D2, and the third discharge chamber D3.

In addition, the first, second, and third discharge chambers D1, D2, and D3 are formed by the discharge cover 191 and the discharge plenum 192. The first discharge chamber D1 is formed by the discharge plenum 192, and the second and third discharge chambers D2 and D3 are disposed between the discharge plenum 192 and the discharge cover 191. Is formed.

In addition, the second discharge chamber D2 is formed in the axial front of the first discharge chamber D1, and the third discharge chamber D3 is the radius of the first and second discharge chambers D1 and D2. It is formed outside the direction.

In addition, the discharge cover 191, the discharge plenum 192 and the fixing ring 193 are closely coupled to each other. In addition, the discharge valve assembly 160 may be seated at the rear of the discharge plenum 192.

When the pressure of the compression space P is equal to or greater than the pressure of the discharge space D, the valve spring 164 is elastically deformed toward the discharge plenum 192. Accordingly, the discharge valve 161 opens the compression space P so that the compressed refrigerant in the compression space P is guided to the first discharge chamber D1.

The refrigerant guided to the first discharge chamber D1 is guided to the second discharge chamber D2 through the discharge plenum 192. At this time, the refrigerant of the first discharge chamber D1 passes through the plenum extension 1926 having a narrow cross-sectional area, and then is discharged into the second discharge chamber D2 having a wide cross-sectional area. Accordingly, noise due to pulsation of the refrigerant can be significantly reduced.

The refrigerant guided to the second discharge chamber D2 is moved axially backward along the first guide groove 1912a and moves circumferentially along the second guide groove 1912b. The refrigerant moved in the circumferential direction along the second guide groove 1912b is guided to the third discharge chamber D3 through the third guide groove 1912c.

In this case, the refrigerant of the second discharge chamber D2 passes through the first guide groove 1912a, the second guide groove 1912b, and the third guide groove 1912c having a narrow cross-sectional area, and then has a large cross-sectional area. It is discharged to the third discharge chamber (D3). Thus, noise due to pulsation of the refrigerant can be reduced once more.

In this case, the third discharge chamber D3 is provided in communication with the cover pipe 195. Therefore, the coolant guided to the third discharge chamber D3 flows to the cover pipe 195. The refrigerant guided to the cover pipe 195 may be discharged to the outside of the linear compressor 10 through the discharge pipe 105.

As such, the refrigerant discharged from the compression space P may flow in the discharge space D formed in the discharge unit 190. In particular, the refrigerant discharged from the compression space P may pass through the first discharge chamber D1, the second discharge chamber D2, and the third discharge chamber D3.

In this case, continuous delivery may be generated from the discharge refrigerant to the frame 110 and the cylinder 120. In addition, heat of the frame 110 and the cylinder 120 may be transferred to the suction refrigerant accommodated in the piston 130. Therefore, the volume of the suction refrigerant is increased and the compression efficiency can be reduced.

6 to 8, the linear compressor 10 according to the second embodiment of the present invention is provided with a heat insulating member 200a for preventing such heat transfer. In detail, the heat insulating member 200a may be disposed to cover the front surface of the cylinder 120 and the frame 110.

In particular, the heat insulating member 200a is seated on the discharge cylinder surface 1200 and the discharge frame surface 1120.

The discharge cylinder surface 1200 is provided with a cylinder heat insulating seat 1202 on which at least a portion of the heat insulating member 200a is seated and a discharge valve seat 1204 on which at least a part of the discharge valve 161 is seated. .

On the discharge frame surface 1120, a frame heat insulating seat 1121 to which at least a portion of the heat insulating member 200a is seated is formed.

The frame insulation seating unit 1121 is provided in a ring shape, and is formed recessed in the axial direction from the discharge frame surface 1120. In particular, the frame insulation seating portion 1121 is formed in the radially outer side than the gas hole 1106. In addition, the terminal insertion hole 1104, the discharge fastening hole 1100 and the stator fastening hole 1102 are formed in the radially outer side than the frame insulating seating portion 1121.

In addition, the cover flange portion 1910 may be provided with a diameter corresponding to the frame insulating seating portion 1121. In detail, the diameter of the cover flange portion 1910 is provided slightly larger than the diameter of the frame heat-insulating seat portion 1121.

The heat insulating member 200a may have an inner diameter and an outer diameter, and may be formed in a ring shape extending in a radial direction. In this case, the heat insulating member 200a includes a first heat insulating part 2002a, a second heat insulating part 2006, and a third heat insulating part 2004a.

The first heat insulating part 2002a is provided to form a circular opening corresponding to the inner diameter. In addition, the first heat insulating part 2002a may be disposed to radially contact the discharge valve seating part 1204. In other words, the outer diameter of the discharge valve seating portion 1204 and the inner diameter of the heat insulating member 200 may be provided in the same manner.

In addition, the axial length of the first heat insulating part 2002a may be equal to the height of the discharge valve seating part 1204 protruding in the axial direction. Therefore, the axial upper surface of the first heat insulating part 2002a and the discharge valve seating part 1204 may be disposed on the same line.

The second heat insulating part 2006 may be seated on the cylinder heat insulating seating part 1202. In addition, the axial length of the second heat insulating part 2006 is greater than the axial length of the first heat insulating part 2002a. In addition, an axial length of the second heat insulating part 2006 may be greater than a depth in which the cylinder heat insulating seat part 1202 is recessed in the axial direction.

Accordingly, when the second heat insulating part 2006 is seated on the cylinder heat insulating seating part 1202, at least a part of the second heat insulating part 2006 may protrude axially from the discharge cylinder surface 1200. Can be.

In this case, the discharge valve assembly 160 is positioned above the second heat insulating part 2006 in the axial direction. In detail, the second heat insulating part 2006 is disposed between the second cylinder heat insulating seating part 1202 and the spring support part 165.

In particular, the second heat insulating part 2006 may be formed of an elastic material to be in close contact with the cylinder heat insulating seating part 1202 and the spring support part 165. Accordingly, it is possible to prevent the refrigerant from leaking between the discharge cylinder surface 1200 and the spring support 165.

The third heat insulating part 2004a may be seated on the frame heat insulating seating part 1121. That is, the third heat insulating part 2004a is located radially outward from the first heat insulating part 2002a and the second heat insulating part 2006.

In addition, the axial length of the third heat insulating part 2004a is greater than the axial length of the first heat insulating part 2002a. In addition, the axial length of the third heat insulating part 2004a may be the same as the axial length of the second heat insulating part 2006.

In addition, an axial length of the third heat insulating part 2004a may be greater than a depth in which the frame heat insulating seating part 1121 is recessed in the axial direction. Accordingly, when the third heat insulating part 2004a is seated on the frame heat insulating seating part 1121, at least a part of the third heat insulating part 2004a may protrude axially from the frame cylinder surface 1120. Can be.

In this case, the discharge cover 1911 is positioned above the axial direction of the third heat insulating part 2004a. In detail, the third heat insulating part 2004a is disposed between the frame heat insulating seating part 1121 and the cover flange part 1910.

In particular, the third heat insulating part 2004a may be formed of an elastic material and may be in close contact with the frame heat insulating seating part 1121 and the cover flange part 1910. Accordingly, it is possible to prevent the refrigerant from leaking between the discharge frame surface 1120 and the discharge cover 191.

In this case, the fourth sealing member 129d is omitted in the linear compressor according to the second embodiment. This is because the heat insulating member 200a functions as the fourth sealing member 129d. In detail, the third heat insulating part 2004a may function as the fourth sealing member 129d.

In addition, the third heat insulating part 2004a may form a circular appearance corresponding to the outer diameter. That is, the heat insulating member 200a is provided in a shape extending radially outward from the first heat insulating portion 2002a to the third heat insulating portion 2004a. Thus, the second heat insulation portion 2006 is located between the radial direction of the first heat insulation portion 2002a and the third heat insulation portion 2004a.

In addition, the outer diameter of the heat insulating member 200a is provided corresponding to the diameter of the frame heat insulating seating portion 1121. In this case, the corresponding means that the outer diameter of the heat insulating member 200a is smaller than the outer diameter of the frame insulating seating portion 1121 and is larger than the inner diameter.

In addition, a heat insulation through hole 2000 corresponding to the gas hole 1106 is formed in the heat insulation member 200a. In detail, the heat insulating through hole 2000 is axially penetrated between the third heat insulating part 2004a and the second heat insulating part 2006 in a radial direction.

As such, the heat insulating member 200a is provided to cover the discharge cylinder surface 1200 and the discharge frame surface 1120. Accordingly, the discharge refrigerant may be prevented from directly contacting the discharge cylinder surface 1200 and the discharge frame surface 1120. Therefore, the heat of the discharged refrigerant may be prevented from being transferred to the cylinder 120 and the piston 130.

In addition, the heat insulating member 200a may be disposed between the discharge frame surface 1120 and the discharge cover 191 to block heat conducted from the discharge cover 191 to the discharge frame surface 1120.

In addition, the heat insulating member 200a may function as a sealing member to prevent leakage of the refrigerant. Accordingly, the sealing member can be omitted, and the convenience of installation can be increased.

10: compressor 110: frame
120: cylinder 190: discharge unit
191: discharge cover 200: heat insulating member
1100: discharge frame surface 1200: discharge cylinder surface
1910: cover flange portion 2002, 2002a: first heat insulating portion
2004, 2006: 2nd insulation part 2004a: 3rd insulation part

Claims (15)

A piston reciprocating in the axial direction;
A cylinder forming a compression space in which the refrigerant is compressed by the piston;
A discharge unit forming a discharge space through which the refrigerant discharged from the compressed space flows;
A frame accommodating the cylinder and coupled to the discharge unit;
A discharge valve for opening and closing the compressed space so that the refrigerant in the compressed space is discharged into the discharge space; And
And a heat insulating member disposed between the cylinder and the discharge unit.
The cylinder includes a discharge cylinder surface on which the discharge valve and the heat insulating member are seated,
On the discharge cylinder surface,
A discharge valve seating portion formed to protrude from the discharge cylinder surface so that the discharge valve is seated; And
A cylinder insulation seating portion formed by being recessed in the discharge cylinder surface so that the insulation member is seated;
Linear compressor characterized in that it is included. The method of claim 1,
The heat insulating member is provided in a ring shape extending in the radial direction having an inner diameter and an outer diameter,
The heat insulating member,
A first heat insulating part forming a circular opening corresponding to the inner diameter and contacting the discharge valve seat; And
And a second heat insulating part disposed radially outward of the first heat insulating part and disposed in the cylinder heat insulating seating part. The method of claim 2,
And the axial length of the first heat insulating part is smaller than the axial length of the second heat insulating part. The method of claim 2,
The cylinder insulating seating portion is formed recessed in the axial direction from the discharge cylinder surface,
And a depth in which the cylinder insulation seating portion is recessed in the axial direction is smaller than an axial length of the second insulation portion. The method of claim 2,
The discharge valve seating portion is formed to protrude in the axial direction from the discharge cylinder surface,
And a height in which the discharge valve seat portion protrudes in the axial direction is the same as the axial length of the first heat insulating part. The method of claim 2,
A spring assembly for providing an elastic force so that the discharge valve is in close contact with the discharge cylinder surface,
The spring assembly,
A valve spring having a central portion fixedly coupled to the discharge valve; And
A spring support positioned at an edge of the valve spring to support the valve spring;
And the second heat insulating part is disposed between the spring support part and the cylinder heat insulating seating part. The method of claim 2,
The discharge cylinder surface is provided in a ring shape extending in the radial direction,
The discharge valve seating portion is formed to protrude axially upward at a radially inner end of the discharge cylinder surface,
And the first heat insulating part is disposed in contact with a radially outer side of the discharge valve seating part. The method of claim 7, wherein
The discharge valve seating portion and the axial upper surface of the first heat insulating portion are arranged on the same line,
And the discharge valve is disposed on the discharge cylinder surface so as to contact the discharge valve seat and the axial upper surface of the first heat insulating part. The method of claim 2,
The heat insulating member,
And a third heat insulating part positioned radially outward of the second heat insulating part and forming a circular appearance corresponding to the outer diameter. The method of claim 9,
The frame includes a discharge frame surface coupled to the discharge unit,
The discharge frame surface is a linear compressor, characterized in that it comprises a frame insulating seating recessed formed in the discharge frame surface so that the third heat insulating portion is seated. The method of claim 10,
In the discharge unit,
A cover flange part seated on the discharge frame surface and coupled to the frame,
And the third heat insulating part is disposed between the cover flange part and the frame heat insulating seating part. The method of claim 1,
The discharge cylinder surface, the linear compressor, characterized in that it further comprises a heat insulating member fixing portion formed recessed in the discharge cylinder surface so that at least a portion of the heat insulating member is inserted. The method of claim 12,
The discharge valve seating portion and the cylinder insulation seating portion extend in the circumferential direction and are each formed in a ring shape.
The insulating member fixing portion is a linear compressor, characterized in that formed in a plurality of spaced apart in the circumferential direction. The method of claim 13,
The discharge cylinder surface is formed extending in the radial direction,
And the discharge valve seating unit, the heat insulating member fixing unit, and the cylinder heat insulating seating unit are sequentially formed from the radially inner side to the outer side. The method of claim 1,
The discharge valve seating portion is formed to protrude in the axial direction,
The cylinder insulating seating portion is formed recessed in the axial direction from the radially outer side of the discharge valve seating portion,
The heat insulating member is a linear compressor, characterized in that extending in the radial direction from the discharge valve seating portion to the cylinder heat insulating seating portion.

Images