CN212106205U - Discharge valve unit and compressor - Google Patents

Abstract

Disclosed are a discharge valve unit and a compressor. A discharge valve unit according to the present specification includes: a base made of plastic; a metal material combination component arranged on the base; and an elastic member coupled to the coupling member; the surface of the coupling member facing the base has roughness.

Description

Discharge valve unit and compressor

Technical Field

This specification relates to compressors. And more particularly, to a linear compressor compressing refrigerant by linear reciprocation of a piston.

Background

In general, a compressor is a device that obtains power from a power generation device such as a motor or a turbine to compress a working fluid such as air or refrigerant. In particular, compressors are widely used throughout industrial or household electric products, especially vapor compression type refrigeration cycles (hereinafter, referred to as "refrigeration cycles").

The above-mentioned compressors are classified into a Reciprocating compressor (Reciprocating compressor), a Rotary compressor (Rotary compressor), and a Scroll compressor (Scroll compressor) according to a method of compressing a refrigerant.

The reciprocating compressor compresses fluid by a linear reciprocating motion of a piston by forming a compression space between the piston and a cylinder, the rotary compressor compresses fluid by a roller centrifugally rotating inside the cylinder, and the scroll compressor compresses fluid by engaging a pair of spiral scrolls to rotate.

Recently, in the reciprocating Compressor, a linear Compressor (L initial Compressor) using a linear reciprocating motion without using a crankshaft is increasingly used. The linear compressor has the advantages of improved efficiency and simple structure due to the reduction of mechanical loss caused by converting rotary motion into linear reciprocating motion.

The linear compressor cylinder is located in the shell forming a closed space to form a compression chamber, and a piston covering the compression chamber reciprocates in the cylinder. The linear compressor repeats a process of sucking fluid in a closed space into a compression chamber during a piston reaches a Bottom Dead Center (BDC), and compressing and discharging the fluid in the compression chamber during a piston reaches a Top Dead Center (TDC).

A compression unit and a driving unit are respectively provided inside the linear compressor, and the compression unit performs a resonant motion by a resonant spring by a motion generated at the driving unit, thereby performing a process of compressing and discharging a refrigerant.

The piston of the linear compressor repeatedly performs a series of processes of reciprocating at a high speed inside the cylinder by the resonance spring, sucking the refrigerant into the inside of the casing through the suction pipe, discharging from the compression space by the forward movement of the piston, and moving to the condenser through the discharge pipe.

In addition, the linear compressor may be classified into an oil lubrication type linear compressor and a gas lubrication type linear compressor according to a lubrication manner.

As disclosed in patent document 1 (korean laid-open patent publication KR 10-2015-.

In contrast, as disclosed in patent document 2 (korean laid-open patent publication KR 10-2016-.

An oil lubricating linear compressor, in which oil having a relatively low temperature is supplied between a cylinder and a piston, can suppress the cylinder and the piston from becoming overheated due to heat of a motor, heat of compression, or the like. Thus, the oil lubrication type linear compressor suppresses the refrigerant passing through the suction passage of the piston from being heated during the suction into the compression chamber of the cylinder, thereby increasing the specific volume and preventing the occurrence of suction loss.

However, in the oil lubrication type linear compressor, when the oil discharged to the refrigeration cycle apparatus together with the refrigerant is not smoothly recovered to the compressor, an oil shortage phenomenon occurs inside a casing of the compressor, and such oil shortage inside the casing becomes a cause of possibly lowering the reliability of the compressor.

On the contrary, the gas lubrication type linear compressor is advantageous in that it can be miniaturized compared to the oil lubrication type linear compressor, and since the space between the cylinder and the piston is lubricated by the refrigerant, the reliability is not lowered due to the shortage of the oil.

In a conventional gas lubrication type linear compressor, a woven fabric woven from reinforcing fibers and a plastic resin infiltrated into the woven fabric in a molten state are laminated in a sheet (sheet) form to form a woven base, and finely divided fiber-reinforced plastic is provided on both sides of the woven base to form an elastic member joint. In the process of finely pulverizing the fiber-reinforced plastic, there is a problem that the mechanical property value is lowered due to breakage of the carbon fibers or the glass fibers. Further, when the elastic member is joined to the elastic member joining portion of the plastic material, there is a problem that foreign matter such as burrs (burr) is generated. In addition, since the fine fiber reinforced plastic is provided on both sides of the weaving base, there is a problem that mass productivity is reduced.

Prior art documents

Patent document 1: korean laid-open patent publication No. KR10-2015-0040027A (2015.04.14. publication)

Patent document 2: korean laid-open patent publication No. KR10-2016-0024217A (2016.03.04. publication)

SUMMERY OF THE UTILITY MODEL

The problem to be solved by the present specification is to provide a discharge valve unit and a compressor capable of improving mechanical property values.

In addition, a discharge valve and a compressor capable of preventing the generation of foreign matters are provided.

Further, a discharge valve and a compressor capable of improving mass productivity are provided.

To achieve the above object, a compressor according to an aspect of the present invention includes: a base made of plastic; a metal material combination component arranged on the base; and an elastic member coupled to the coupling member. In order to improve the bonding force between the base and the bonding member, one surface of the bonding member facing the base has roughness.

In addition, the combination part can be compressed and molded on the base.

In addition, the base may be formed of a Fiber Reinforced Plastic (CFRTP) material.

In addition, the elastic member may be riveted (rivet) to the coupling member.

In addition, the elastic member may include a first hole for coupling the coupling member, and a diameter of the first hole may correspond to a diameter of the coupling member.

Further, a space may be formed between the inner surface of the first hole and the coupling member.

In addition, the elastic member may include a groove concavely formed on an inner side surface of the first hole.

In addition, the coupling member may be provided in the groove when the elastic member is riveted to the coupling member.

The elastic member may include a body, a first hole formed in a central region of the body, and a plurality of second holes spaced apart from the first hole.

The plurality of second holes may be formed in a spiral shape, and the plurality of second holes may be formed in quasi-symmetry with respect to the first hole.

To achieve the above object, a compressor according to an aspect of the present invention includes: a frame; a cylinder provided in the frame to form a refrigerant compression space; a piston disposed in the cylinder and reciprocating in an axial direction; and a discharge valve unit coupled to the frame to form a refrigerant discharge space through which the refrigerant discharged from the compression space flows; the discharge valve unit includes a base made of a plastic material, a metal coupling member provided on the base, and an elastic member coupled to the coupling member; the surface of the coupling member facing the base has roughness.

The present specification can provide a discharge valve unit and a compressor capable of improving mechanical property values.

Further, a discharge valve and a compressor capable of preventing the generation of foreign matter can be provided.

Further, a discharge valve and a compressor capable of improving mass productivity can be provided.

Drawings

Fig. 1 is an oblique view of a compressor according to an embodiment of the present invention;

fig. 2 is a sectional view of a compressor according to an embodiment of the present invention;

fig. 3 is an exploded oblique view of a discharge valve unit according to an embodiment of the present invention;

fig. 4 is a plan view of an elastic member according to an embodiment of the present invention;

FIG. 5 is an enlarged view of portion A of FIG. 4;

fig. 6 is an oblique view of a discharge valve according to an embodiment of the present invention;

fig. 7 is an assembly process diagram of a discharge valve unit according to an embodiment of the present invention.

Fig. 8 is an assembly process diagram of a discharge valve unit according to an embodiment of the present invention.

Fig. 9 is an assembly process diagram of a discharge valve unit according to an embodiment of the present invention.

Fig. 10 is an assembly process diagram of a discharge valve unit according to an embodiment of the present invention.

Fig. 11 is an assembly process diagram of a discharge valve unit according to an embodiment of the present invention.

Description of the reference numerals

100: the compressor 101: accommodating space

102: suction space 103: compression space

104: discharge space 110: outer casing

111: shell 112: first shell cover

113: second cover 114: suction tube

115: discharge pipe 115 a: ring pipe

116: first support spring 116 a: suction guide

116 b: suction side support member 116 c: damping component

117: second support spring 117 a: supporting frame

117 b: first support guide 117 c: support cover

117 d: second support guide 117 e: third support guide

118: resonant spring 118 a: a first resonant spring

118 b: second resonant spring 119: spring support

119 a: spring body 119 b: second joint part

119 c: the support portion 120: frame structure

121: main body portion 122: first flange part

123: rear cover 123 a: supporting frame

130: the driving unit 131: outer stator

132: coil winding body 132 a: bobbin

132 b: coil 133: nail iron core

134: inner stator 135: propeller

136: the magnetic frame 136 a: a first combining part

137: stator cover 140: cylinder

141: second flange portion 142: gas inlet

150: piston 151: head part

152: the guide portion 153: second flange part

154: suction port 155: suction valve

160: muffler unit 161: suction muffler

161 a: fourth flange portion 162: internal guide

170: discharge valve unit 171: discharge valve

172: elastic member 180: discharge cover assembly

181: first discharge cover 182: second discharge cover

183: third discharge cover

Detailed Description

Hereinafter, embodiments disclosed in this specification (discloser) will be described in detail with reference to the drawings, and the same or similar structures are given the same reference numerals, and redundant description is omitted.

In describing the embodiments disclosed herein, one structure is "connected" or "coupled" to another structure by virtue of being directly connected or coupled to the other structure or by virtue of being connected or coupled via the other structure.

In describing the invention disclosed in the present specification, if it is considered that the detailed description of the related art disclosed therein hinders the understanding of the invention, the detailed description thereof will be omitted. In addition, the drawings are only for the purpose of facilitating understanding of the embodiments disclosed in the present specification, and are not intended to limit the technical ideas disclosed in the present invention, but include all modifications, equivalents, and substitutes falling within the spirit and technical scope of the present invention.

In addition, the term specification (disabler) may be replaced with a term of document, specification, descriptor, and the like.

As shown in fig. 1, a linear compressor 100 according to an embodiment of the present disclosure may include a shell 111 and shell covers 112 and 113 coupled to the shell 111. It is to be understood in a broad sense that the cover 112, 113 may be one formation of the housing 111.

On the underside of the housing 111, legs 20 may be incorporated. The leg 20 may be coupled to a base of a product to which the linear compressor 100 is mounted. For example, the product may comprise a refrigerator and the base may comprise a machine compartment base of the refrigerator. As another example, the product includes an outdoor unit of an air conditioner, and the base may include a base of the outdoor unit.

The housing 111 is generally cylindrical in shape and may be disposed in a transverse or axial manner. With reference to fig. 1, the shell 111 is elongated in the lateral direction and has a lower height in the radial direction. That is, since the linear compressor 100 may have a low height, for example, when the linear compressor 100 is disposed at a base of a machine room of a refrigerator, there is an advantage in that the height of the machine room can be reduced.

The longitudinal central axis of the casing 111 coincides with a central axis of a main body of the compressor 100, which will be described later, and the central axis of the main body of the compressor 100 coincides with central axes of the cylinder 140 and the piston 150 constituting the main body of the compressor 100.

Outside the housing 111, a terminal 30 may be provided. The terminal 30 may transmit an external power to the driving unit 130 of the linear compressor 100. Specifically, the terminal 30 may be connected to a lead of the coil 132 b.

On the outside of the terminal 30, a bracket 31 may be provided. The cradle 31 may include a plurality of cradles surrounding the terminal 30. The bracket 31 may function to protect the terminal 30 from external impact or the like.

Both side portions of the case 111 may be opened. Cover covers 112, 113 may be coupled to both side portions of the opened case 111. Specifically, the covers 112, 113 may include a first cover 112 coupled to one opened side portion of the case 111, and a second cover 113 coupled to the other opened side portion of the case 111. The inner space of the case 111 can be sealed by the case covers 112 and 113.

With reference to fig. 1, the first housing cover 112 may be located at a right side portion of the linear compressor 100, and the second housing cover 113 may be located at a left side portion of the linear compressor 100. In other words, the first and second covers 112, 113 can be disposed opposite to each other. In addition, it can be understood that the first case cover 112 is located on the suction side of the refrigerant, and the second case cover 113 is located on the discharge side of the refrigerant.

The linear compressor 100 may include a plurality of tubes 114, 115, 40 provided at the shell 111 or the shell covers 112, 113 to enable suction, discharge, or injection of refrigerant.

The plurality of pipes 114, 115, 40 may include a suction pipe 114 for sucking the refrigerant into the interior of the linear compressor 100, a discharge pipe 115 for discharging the compressed refrigerant from the linear compressor 100, and a supplementary pipe 40 for supplementing the refrigerant to the linear compressor 100.

For example, the suction pipe 114 may be coupled to the first cover 112. The refrigerant may be sucked into the inside of the linear compressor 100 in the shaft direction through the suction pipe 114.

The discharge pipe 115 may be coupled to the outer circumferential surface of the case 111. The refrigerant sucked through the suction pipe 114 may be compressed while flowing in the axial direction. In addition, the compressed refrigerant may be discharged through the discharge pipe 115. The discharge pipe 115 is disposed closer to the second cover 113 than the first cover 112.

The supplementary tube 40 may be coupled to the outer circumferential surface of the case 111. A worker may inject the refrigerant into the inside of the linear compressor 100 through the supplementary pipe 40.

To avoid interference with the discharge pipe 115, the supplementary pipe 40 may be coupled at a different height from the discharge pipe 115. Here, the height is understood to be the distance in the vertical direction from the leg 20. The discharge pipe 115 and the supplementary pipe 40 are coupled to the outer circumferential surface of the housing 111 at different heights to facilitate the work.

At least a part of the second case cover 113 is provided adjacent to the inner peripheral surface of the case 111 at a position coupled to the replenishment pipe 40. In other words, at least a portion of the second case cover 113 functions as a resistance to the refrigerant injected through the supplementary tube 40.

Therefore, from the viewpoint of the flow path of the refrigerant, the size of the flow path of the refrigerant flowing in through the supplementary tube 40 becomes small by the second case cover 113 in the process of entering the inner space of the case 111, and becomes large again therethrough. In this process, the refrigerant is vaporized due to the pressure reduction of the refrigerant, and in this process, oil contained in the refrigerant is separated. Therefore, the refrigerant from which the oil is separated flows into the inside of the piston 150 to improve the compression performance of the refrigerant. Oil is understood to be hydraulic oil present in the refrigeration system.

Fig. 2 is a cross-sectional view of a compressor according to an embodiment of the present invention.

Next, a linear compressor that performs an operation of sucking a fluid and compressing the fluid by reciprocating a piston and discharging the compressed fluid will be described as an example of a compressor according to the present specification.

The linear compressor may be referred to as a constituent element of a refrigeration cycle, and the fluid compressed in the linear compressor may be a refrigerant circulating in the refrigeration cycle. The refrigeration cycle may include a condenser, an expansion device, an evaporator, and the like, in addition to the compressor. In addition, the linear compressor may be used as one configuration of a refrigeration system of a refrigerator without limitation, and may be widely used in all industries.

As shown in fig. 2, the compressor 100 may include a casing 110 and a main body received inside the casing 110. The main body of the compressor 100 may include a frame 120, a cylinder 140 fixed to the frame 120, a piston 150 reciprocating inside the cylinder 140, a driving unit 130 fixed to the frame 120 and providing a driving force to the piston, and the like. Here, the cylinder 140 and the piston 150 may also be referred to as compression units 140, 150.

The compressor 100 may include bearing means to reduce friction between the cylinder 140 and the piston 150. The bearing means may be an oil bearing or a gas bearing. In addition, a mechanical bearing may be used as the bearing means.

The main body of the compressor 100 may be elastically supported by support springs 116 and 117 provided at both ends of the inner side of the casing 110. The support springs 116, 117 may comprise a first support spring 116 at the rear of the support body and a second support spring 117 at the front of the support body. The support springs 116, 117 may comprise leaf springs. The support springs 116 and 117 support the internal components of the main body of the compressor 100 and absorb vibration and shock generated by the reciprocating motion of the piston 150.

The housing 110 may form a closed space. The closed spaces may include a receiving space 101 receiving a sucked refrigerant, a suction space 102 receiving a refrigerant before compression, a compression space 103 compressing a refrigerant, and a discharge space 104 receiving a compressed refrigerant.

The refrigerant sucked through the suction pipe 114 connected to the rear side of the casing 110 is stored in the storage space 101, and the refrigerant in the suction space 102 communicating with the storage space 101 is compressed in the compression space 103, discharged to the discharge space 104, and discharged to the outside through the discharge pipe 115 connected to the front side of the casing 110.

The housing 110 may include a case 111 opened at both ends and formed in a substantially horizontally long cylindrical shape, a first case cover 112 coupled to a rear side of the case 111, and a second case cover 113 coupled to a front side. Here, the front side may be understood as the left side of the drawing, in which the compressed refrigerant is discharged, and the rear side may be understood as the right side of the drawing, in which the refrigerant flows. In addition, the first cover 112 or the second cover 113 may be integrally formed with the case 111.

The housing 110 may be formed of a thermally conductive material. Thereby, heat generated in the inner space of the case 110 can be rapidly dissipated to the outside.

The first cover 112 is coupled to the case 111 to seal the rear side of the case 111, and a suction pipe 114 is inserted into and coupled to the center of the first cover 112.

The rear side of the main body of the compressor 100 may be elastically supported by the first support spring 116 in a radial direction of the first housing cover 112.

The first supporting spring 116 case includes a circular plate spring. The edge portion of the first support spring 116 may be elastically supported in the front direction with respect to the rear cover 123 by the support frame 123 a. The open central portion of the first support spring 116 can be supported rearward with respect to the first cover 112 by the suction guide 116 a.

The suction guide 116a may form a through flow passage therein. The suction guide 116a may be formed in a cylindrical shape. The suction guide 116a has a central opening of the first support spring 116 coupled to the front outer peripheral surface thereof, and has a rear end supported by the first cover 112. In this case, another suction-side support member 116b may be provided between the suction guide 116a and the inner surface of the first cover 112.

The suction guide 116a communicates with the suction pipe 114 at a rear side thereof, and the refrigerant sucked through the suction pipe 114 can smoothly flow into a muffler unit 160, which will be described later, through the suction guide 116 a.

The damping member 116c may be formed of a rubber material or the like between the suction guide 116a and the suction side support member 116 b. Accordingly, it is possible to block vibration, which may be generated during the suction of the refrigerant through the suction pipe 114, from being transmitted to the first cover 112.

The second cover 113 is coupled to the housing 111 to seal the front side of the housing 111, and a discharge pipe 115 is inserted through a ring pipe 115 a. The refrigerant discharged from the compression space 103 may be discharged to the refrigeration cycle through the annular tube 115a and the discharge tube 115 after passing through the discharge cap assembly 180.

The front side of the main body of the compressor 100 is elastically supported by the second support spring 117 in the radial direction of the casing 111 or the second casing cover 113.

The second support spring 117 case includes a circular plate spring. The open central portion of the second support spring 117 is supported rearward with respect to the discharge cover assembly 180 by the first support guide 117 b. The edge of the second support spring 117 may be supported forward by the support frame 117a with respect to the inner side surface of the case 111 or the inner circumferential surface of the case 111 adjacent to the second case cover 113.

Unlike fig. 2, the edge of the second supporting spring 117 may be supported forward with respect to the inner surface of the case 111 or the inner circumferential surface of the case 111 adjacent to the second case cover 113 by another holder (not shown) coupled to the second case cover 113.

The first support guide 117b may be formed in a cylindrical shape. The cross-section of the first support guide 117 may include a plurality of diameters. The front side of the first support guide 117b is inserted into the central opening of the second support spring 117, and the rear side thereof is inserted into the central opening of the discharge cover assembly 180. The support cover 117c may be coupled to a front side of the first support guide 117b via the second support spring 117. A cup-shaped second support guide 117d recessed forward may be coupled to a front side of the support cover 117 c. A cup-shaped third support guide 117e that corresponds to the second support guide 117d and is recessed rearward may be coupled to the inside of the second cover 113. The second support guide 117d may be inserted into an inner side of the third support guide 117e to be supported in an axial direction and/or a radial direction. At this time, between the second and third support guides 117d and 117e, a gap (gap) may be formed.

The frame 120 may include a body portion 121 supporting an outer circumferential surface of the cylinder 140, and a first flange portion 122 connected to one side of the body portion 121 and supporting the driving unit 130. The frame 120 may be elastically supported with respect to the housing 110 by the first and second support springs 116 and 117 together with the driving unit 130 and the cylinder 140.

The body portion 121 may surround the outer circumferential surface of the cylinder 140. The body portion 121 may be formed in a cylindrical shape. The first flange portion 122 may be formed to extend in the radial direction at the front end portion of the body portion 121.

A cylinder 140 may be coupled to an inner circumferential surface of the body portion 121. An inner stator 134 may be coupled to an outer circumferential surface of the body part 121. For example, the cylinder 140 may be press-fitted (fixed) to the inner circumferential surface of the body portion 121, and the inner stator 134 may be fixed by a separate fixing ring (not shown).

The outer stator 131 is coupled to the rear surface of the first flange 122, and the discharge cover assembly 180 is coupled to the front surface thereof. For example, the outer stator 131 and the discharge cover assembly 180 may be fixed by a mechanical coupling means.

A bearing inlet groove 125a constituting a part of the gas bearing is formed on the front surface side of the first flange 122, a bearing communication hole 125b penetrating the bearing inlet groove 125a to the inner circumferential surface of the body 121 is formed, and a gas groove 125c communicating with the bearing communication hole 125b is formed on the inner circumferential surface of the body 121.

The bearing inlet groove 125a is formed to be recessed in the axial direction at a constant depth, and the bearing communication hole 125b is a hole having a smaller cross section than the bearing inlet groove 125a and is formed to be inclined toward the inner circumferential surface of the body portion 121. The gas groove 125c is formed in an annular shape having a fixed depth and a fixed axial length on the inner circumferential surface of the body 121. In contrast, the gas groove 125c is formed on the outer circumferential surface of the cylinder 140, which is in contact with the inner circumferential surface of the body 121, or on the inner circumferential surface of the body 121 and the outer circumferential surface of the cylinder 140.

Further, a gas inlet 142 corresponding to the gas groove 125c may be formed on the outer circumferential surface of the cylinder 140. The gas inlet 142 constitutes a kind of nozzle portion in the gas bearing.

In addition, the frame 120 and the cylinder 140 may be formed of aluminum or an aluminum alloy.

The cylinder 140 may be formed in a cylindrical shape with both ends open. The piston 150 may be inserted through the rear end of the cylinder 140. The front end of the cylinder 140 may be closed by a discharge valve unit 170. A compression space 103 may be formed between the cylinder 140, the front end portion of the piston 150, and the discharge valve unit 170. The forward end of the piston 150 may be referred to herein as a head 151. The compression space 103 increases in volume when the piston 150 retreats and decreases in volume when the piston 150 advances. That is, the refrigerant flowing into the compression space 103 may be compressed as the piston 150 moves forward, and discharged through the discharge valve unit 170.

The cylinder 140 may include a second flange portion 141 provided at a front end portion. The second flange portion 141 may be bent toward the outside of the cylinder 140. The second flange portion 141 may be elongated in an outer circumferential direction of the cylinder 140. The second flange portion 141 of the cylinder 140 may be coupled to the frame 120. For example, the front end of the frame 120 may be formed with a flange groove corresponding to the second flange 141 of the cylinder 140, and the second flange 141 of the cylinder 140 may be coupled to the flange groove by a coupling member.

In addition, a gas bearing means for supplying exhaust gas through a gap between the outer circumferential surface of the piston 150 and the outer circumferential surface of the cylinder 140 to perform gas lubrication between the cylinder 140 and the piston 150 may be provided. The exhaust gas between the cylinder 140 and the piston 150 may provide an upward buoyancy to the piston 150 to reduce friction generated between the piston 150 and the cylinder 140.

For example, the cylinder 140 may include a gas flow inlet 142. The gas inlet 142 may communicate with a gas groove 125c formed in the inner circumferential surface of the body 121. The gas inlet 142 may penetrate the cylinder 140 in a radial direction. The gas inlet 142 may guide the compressed refrigerant flowing into the gas groove 125c to between an inner circumferential surface of the cylinder 140 and an outer circumferential surface of the piston 150. In contrast, the gas groove 125 may be formed on the outer circumferential surface of the cylinder 140 in consideration of convenience of processing.

The inlet of the gas inflow port 142 is relatively wide, and the outlet is formed with fine through holes to function as a nozzle. A filter (not shown) for blocking inflow of foreign matters may be additionally provided at an inlet of the gas inlet 142. The filter may be a mesh filter formed of metal, or may be formed by winding a filament or the like.

The gas inflow port 142 may be independently formed in plural, or the inlet may be formed in an annular groove along which the outlet is formed in plural at a certain interval. The gas inlet 142 may be formed only on the front side with respect to the axial middle of the cylinder 140. In contrast, the gas inlet 142 may be formed at the rear side of the cylinder 140 with respect to the axial middle of the cylinder 140 in consideration of the sinking of the piston 150.

The piston 150 is inserted from the open end at the rear of the cylinder 140 to close the rear of the compression space 103.

The piston 150 may include a head 151 and a guide 152. The head 151 may be formed in a disk shape. The head 151 may be partially open. The header 151 may divide the compression space 103. The guide 152 may be extended rearward on the outer circumferential surface of the head 151. The guide portion 152 may be formed in a cylindrical shape. The guide 152 is hollow and the front is partially sealed by the head 151. The guide 152 is open at the rear and is connectable to a muffler unit 160. The head 151 may be provided as a separate member coupled to the guide 152. Unlike this, the head 151 and the guide 152 may be integrally formed.

The piston 150 may include a suction port 154. The suction port 154 may penetrate the head 151. The suction port 154 may communicate the suction space 102 and the compression space 103 inside the piston 150. For example, the refrigerant flowing from the receiving space 101 into the suction space 102 inside the piston 150 may be sucked into the compression space 103 between the piston 150 and the cylinder 140 through the suction port 154.

The suction port 154 may be elongated in the axial direction of the piston 150. The suction port 154 may be formed obliquely in the axial direction of the piston 150. For example, the suction port 154 may be obliquely elongated in a direction away from the central axis toward the rear of the piston 150.

The cross-section of the suction port 154 may be formed in a circular shape. The inner diameter of the suction port 154 may be constant. In contrast, the suction port 154 may be formed in the form of an elongated hole whose opening extends in the radial direction of the head 151, or may be formed in the form of a hole whose inner diameter increases toward the rear.

The suction port 154 may be formed in plural in one or more directions of a radial direction and a circumferential direction of the head 151.

A suction valve 155 that can selectively open and close a suction port 154 may be mounted on a head portion 151 of the piston 150 adjacent to the compression space 103. The suction valve 155 may operate by being elastically deformed to open or close the suction port 154. That is, the suction valve 155 may be elastically deformed by the pressure of the refrigerant flowing to the compression space 103 through the suction port 154 to open the suction port 154.

The piston 150 may be coupled to the impeller 135. The pusher 135 may reciprocate in the forward and backward directions with the movement of the piston 150. Between the impeller 135 and the piston 150, an inner stator 134 and a cylinder 140 may be provided. The mover 135 and the piston 150 may be connected to each other by a magnetic frame 136 formed by roundabout the cylinder 140 and the inner stator 134 from the rear.

The muffler unit 160 is coupled to the rear of the piston 150 to reduce noise generated in a process of refrigerant being sucked into the piston 150. The refrigerant sucked through the suction pipe 114 may flow to the suction space 102 inside the piston 150 through the muffler unit 160.

The muffler unit 160 may include a suction muffler 161 communicating to the receiving space 101 of the casing 110, and an inner guide 162 connected to a front of the suction muffler 161 and guiding refrigerant to the suction port 154.

The suction muffler 161 is located behind the piston 142, and has a rear opening adjacent to the suction pipe 114, and a front end coupled to the rear of the piston 142. The suction muffler 161 forms a flow passage in the axial direction so that the refrigerant in the receiving space 101 can be guided to the suction space 102 inside the piston 150.

The inside of the suction muffler 161 may be formed of a plurality of sound deadening spaces divided by the baffle. The suction muffler 161 may be formed by coupling two or more members to each other, for example, by press-coupling a second suction muffler to the inside of a first suction muffler to form a plurality of sound deadening spaces. In addition, the suction muffler 161 may be formed of a plastic material in consideration of weight or insulation.

One side of the inner guide 162 is communicated with a sound deadening space of the suction muffler 161, and the other side thereof is deeply inserted into the interior of the piston 142. The inner guide 162 may be formed in a tubular shape. Both ends of the inner guide 162 may have the same inner diameter. The inner guide 162 may be formed in a cylindrical shape. In contrast, the inner diameter of the front end on the discharge side may be larger than the inner diameter of the rear end on the opposite side.

The suction muffler 161 and the inner guide 162 may be provided in various shapes, thereby adjusting the pressure of the refrigerant passing through the muffler unit 160. The suction muffler 161 and the inner guide 162 may also be integrally formed.

The discharge valve unit 170 may include a discharge valve 171, and an elastic member 172 provided at a front side of the discharge valve 171 and elastically supporting the discharge valve 171. The discharge valve unit 170 may selectively discharge the refrigerant compressed in the compression space 103. Here, the compression space 103 refers to a space formed between the suction valve 155 and the discharge valve 171.

The discharge valve 171 is supportably disposed in front of the cylinder 140. The discharge valve 171 selectively opens and closes the front opening of the cylinder 140. The discharge valve 171 may work by elastic deformation to open or close the compression space 103. The discharge valve 171 may be elastically deformed by the pressure of the refrigerant flowing to the compression space 104 through the compression space 103 to open the compression space 103. For example, the compression space 103 is maintained in a sealed state in a state where the discharge valve 171 is supported by the front surface of the cylinder 140, and the compressed refrigerant of the compression space 103 may be discharged to an open space in a state where the discharge valve 171 is spaced apart from the front surface of the cylinder 140.

The elastic member 172 is disposed between the discharge valve 171 and the discharge cap assembly 180 and provides elastic force in the axial direction. The elastic member 172 may use a compression coil spring, or a plate spring in consideration of space occupation or reliability.

When the pressure in the compression space 103 is higher than the discharge pressure, the elastic member 172 deforms forward to open the discharge valve 171, and the refrigerant is discharged from the compression space 103 to the first discharge space 104a of the discharge cover assembly 180. After the discharge of the refrigerant is finished, the elastic member 172 may provide a restoring force to the discharge valve 171 to close the discharge valve 171.

The process of flowing the refrigerant into the compression space 103 through the suction valve 155 and discharging the refrigerant in the compression space 103 to the discharge space 104 through the discharge valve 171 will be described as follows:

when the pressure of the compression space 103 is lower than a preset suction pressure during the reciprocating linear motion of the piston 150 inside the cylinder 140, the suction valve 155 is opened and the refrigerant is sucked into the compression space 103. In contrast, when the pressure of the compression space 103 exceeds the preset suction pharmacological agent, the refrigerant of the compression space 103 is compressed in a state where the suction valve 155 is closed.

When the pressure in the compression space 103 is higher than a predetermined discharge pressure, the elastic member 172 is deformed forward to open the discharge valve 171 connected thereto, so that the refrigerant can be discharged from the compression space 103 to the discharge space 104 of the discharge cap assembly 180. After the discharge of the refrigerant is completed, the elastic member 172 applies a restoring force to the discharge valve 171 to close the discharge valve 171, thereby sealing the front of the compression space 103.

The discharge cover assembly 180 is disposed in front of the compression space 103 to form a discharge space 104 for receiving the refrigerant discharged from the compression space 103, and coupled to the front of the frame 120 to reduce noise generated in the process of discharging the refrigerant from the compression space 103. The discharge cover assembly 180 accommodates the discharge valve unit 170 and is coupled to the front of the first flange 122 of the frame 120. For example, the discharge valve assembly 180 may be coupled to the first flange portion 122 by a mechanical coupling member.

Further, a gasket 165 for heat insulation and an O-ring (O-ring)166 for suppressing leakage of the refrigerant in the discharge space 104 may be provided between the discharge cover assembly 180 and the frame 120.

The discharge cap assembly 180 may be formed of a thermally conductive material. Therefore, when the refrigerant in a high temperature state flows into the discharge cover assembly 180, heat of the refrigerant is transferred to the casing 110 through the discharge cover assembly 180 and is emitted to the outside of the compressor.

The discharge cap assembly 180 may be formed of one discharge cap, or a plurality of discharge caps may be sequentially connected. When the discharge cover assembly 180 is composed of a plurality of discharge covers, the discharge space 104 may include a plurality of space portions divided by the plurality of discharge covers. The plurality of space portions may be provided in the front-rear direction and communicate with each other.

For example, when the number of the discharge covers is three, the discharge spaces 104 may include a first discharge space 104a formed between the first discharge cover 181 coupled to the front side of the frame 120 and the frame, a second discharge space 104b formed between the second discharge cover 182 coupled to the front side of the first discharge cover 181 and the first discharge cover 181 communicating with the first discharge space 104a, and a third discharge space 104c formed between the third discharge cover 183 coupled to the front side of the second discharge cover 182 and the second discharge cover 182 communicating with the second discharge space 104 b.

In addition, the first discharge space 104 may selectively communicate with the compression hole 103 through the discharge valve 171, the second discharge space 104b communicates with the first discharge space 104a, and the third discharge space 104c communicates with the second discharge space 104 b. Therefore, the refrigerant discharged from the compression space 103 reduces noise while passing through the first discharge space 104a, the second discharge spaces 1 to 4b, and the third discharge spaces 1 to 4c in this order, and is discharged to the outside of the casing 110 through the annular pipe 115a and the discharge pipe 115 communicating with the third discharge cover 183.

The driving unit 130 may include an outer stator 131 disposed around the body portion 121 of the frame 120 between the case 111 and the frame, an inner stator 134 disposed around the cylinder 140 between the outer stator 131 and the cylinder 140, and a propeller 135 disposed between the outer stator 131 and the inner stator 134.

The outer stator 131 may be coupled to the rear of the first flange portion 122 of the frame 120, and the inner stator 134 may be coupled to the outer circumferential surface of the body portion 121 of the frame 120. In addition, the inner stator 134 is spaced inward of the outer stator 131, and the impeller 135 may be disposed in a space between the outer stator 131 and the inner stator 134.

The outer stator 131 may be provided with winding coils, and the mover 135 may include permanent magnets. The permanent magnet may be constituted by a single magnet having one pole, or by a combination of a plurality of magnets having three poles.

The outer stator 131 may include a coil winding body 132 in a circumferential direction around the shaft direction and a stator core 133 laminated around the coil winding body 132. The coil winding body 132 may include a bobbin 132a of a hollow cylindrical shape and a coil 132b wound in a circumferential direction of the coil 132 a. The cross section of the coil 132b may be formed in a circular or polygonal shape, and an example thereof may have a hexagonal shape. The stator core 133 may be radially stacked by a plurality of lamination sheets (lamination sheets), or may be stacked in a circumferential direction by a plurality of lamination blocks (lamination blocks).

The front side of the outer stator 131 is supported by the first flange portion 122 of the frame 120, and the rear side is supported by the stator cover 137. For example, the stator cover 137 is formed in a disk shape having a front surface supported by the outer stator 131 and a rear surface supported by the resonance spring 118.

The inner stator 134 may be formed by a plurality of lamination layers laminated in a circumferential direction on an outer circumferential surface of the body part 121 of the frame 120.

One side of the mover 135 is supported in combination with the magnetic frame 136. The magnetic frame 136 has a substantially cylindrical shape and is inserted into a space between the outer stator 131 and the inner stator 134. In addition, the magnetic frame 136 may be coupled to a rear side of the piston 150 to move together with the piston 150.

For example, a rear end of the magnetic frame 136 is bent and extended radially inward to form a first coupling portion 136a, and the first coupling portion 136a is coupled to a third flange 153 formed behind the piston 150. The first coupling portion 136a of the magnetic frame 136 and the third flange portion 153 of the piston 150 may be coupled by a mechanical coupling member.

Further, a fourth flange portion 161a formed in front of the suction muffler 161 may be provided between the third flange portion 153 of the piston 150 and the first coupling portion 136a of the magnetic frame 136. Therefore, the piston 150, the muffler unit 160, and the propeller 135 linearly reciprocate together in a state of being integrated.

When a current is applied to the driving unit 130, a magnetic flux (magnetic flux) is generated in the winding coil, and an electromagnetic force is generated by an interaction between the magnetic flux generated from the winding coil of the outer stator 131 and the magnetic flux generated from the permanent magnet of the mover 135 to move the mover 135. In addition, while the pusher 135 reciprocates in the axial direction, the piston 150 connected to the magnetic frame 136 also reciprocates in the axial direction integrally with the pusher 135.

In addition, the driving unit 130 and the compressing units 140 and 150 are supported in the axial direction by the supporting springs 116 and 117 and the resonant spring 118.

The resonant spring 118 amplifies vibration generated by the reciprocating motion of the mover 135 and the piston 150, achieving effective compression of the refrigerant. Specifically, the resonant spring 118 is adjusted to a frequency corresponding to the natural frequency of the piston 150 to cause the piston 150 to perform a resonant motion. In addition, the resonant spring 118 achieves stable movement of the piston 150 to reduce generation of vibration and noise.

The resonance spring 118 may be a coil spring elongated in the axial direction. Both ends of the resonant spring 118 may be connected to the vibrating body and the fixed body, respectively. For example, one end of the resonant spring 118 is connected to the magnetic frame 136, and the other end is connected to the rear cover 123. Therefore, the resonance spring 118 is elastically deformable between the vibrating body vibrating at one end and the fixed body fixed at the other end.

The natural frequency of the resonant spring 118 is designed to coincide with the resonant frequency of the impeller 135 and the piston 150 when the compressor 100 is operated, thereby amplifying the reciprocating motion of the piston 150. However, the rear cover 123, which is a fixed body, is not rigidly fixed because it is elastically supported by the housing 110 by the first support spring 116.

The resonant springs 118 may include a first resonant spring 118a supporting a rear side and a second resonant spring 118b supporting a front side, with respect to the spring supporter 119.

The spring holder 119 may include a spring body 119a surrounding the suction muffler 161, a second coupling portion 119b bent to the inner radial direction in front of the spring body 119a, and a support portion 119c bent to the outer radial direction in rear of the spring body 119 a.

The second coupling portion 119b of the spring holder 119 may be supported at a front surface thereof by the first coupling portion 136a of the magnetic frame 136. The inner diameter of the second coupling portion 119b of the spring supporter 119 may surround the outer diameter of the suction muffler 161. For example, the second coupling portion 119b of the spring holder 119, the first coupling portion 136a of the magnetic frame 136, and the third flange portion 153 of the piston 150 are sequentially provided and then integrated by mechanical parts. At this time, as described above, the fourth flange 161a of the suction muffler 161 may be provided and fixed between the third flange 153 of the piston 150 and the first coupling portion 136a of the magnetic frame 136.

The first resonant spring 118a may be disposed between a front surface of the rear cover 123 and a rear surface of the spring supporter 119. The second resonant spring 118b may be disposed between a rear surface of the stator cover 137 and a front surface of the spring supporter 119.

A plurality of first and second resonant springs 118a and 118b may be provided along the circumferential direction of the center axis. The first and second resonant springs 118a and 118b may be disposed side by side in the axial direction or disposed to cross each other. The first and second resonant springs 118a and 118b may be disposed at a predetermined interval in a radial direction of the central axis. For example, the first and second resonant springs 118a and 118b are provided in three numbers, respectively, and are provided at intervals of 120 degrees in the radial direction of the central axis.

The compressor 100 may include a plurality of sealing members capable of increasing a coupling force between the frame 120 and peripheral members thereof.

For example, the plurality of sealing members may include a first sealing member provided at a portion where the frame 120 and the discharge cap assembly 180 are coupled and inserted into a mounting groove formed at a front end of the frame 120, and a second sealing member provided at a portion where the frame 120 and the cylinder 140 are coupled and inserted into a mounting groove formed at an outer side surface of the cylinder 140. The second sealing member prevents the refrigerant of the gas groove 125c formed between the inner circumferential surface of the frame 120 and the outer circumferential surface of the cylinder 140 from leaking to the outside, increasing the coupling force of the frame 120 and the cylinder 140. In addition, the plurality of sealing members may further include a third sealing member provided at a portion where the frame 120 and the inner stator 134 are coupled and inserted into a mounting groove formed at an outer side surface of the frame 120. Here, the first to third seal members may have a ring shape.

The operation of the linear compressor 100 as described above is as follows:

first, when a current is applied to the driving unit 130, a magnetic flux is generated in the outer stator 131 by the current flowing in the coil 132 b. The magnetic flux generated in the outer stator 131 generates an electromagnetic force, and the mover 135 having the permanent magnet can linearly reciprocate by the generated electromagnetic force. The electromagnetic force is alternately generated in a direction (forward direction) in which the piston 150 moves to a Top Dead Center (TDC) during the compression stroke, and in a direction (backward direction) in which the piston 150 moves to a Bottom Dead Center (BDC) during the intake stroke. That is, the driving unit 130 may generate a thrust force as a force pushing the mover 135 and the piston 150 to the moving direction.

The piston 150, which linearly reciprocates inside the cylinder 140, may repeatedly increase or decrease the volume of the compression space 103.

When the piston 150 moves in a direction (rear direction) to increase the volume of the compression space 103, the pressure of the compression space 103 may be reduced. Therefore, the suction valve 155 provided in front of the piston 150 is opened, and the refrigerant staying in the suction space 102 can be sucked into the compression space 103 through the suction port 154. The suction stroke may be performed until the piston 150 increases the volume of the compression space 103 to the maximum to reach the bottom dead center.

The piston 150, which reaches the bottom dead center, switches the direction of movement, and moves in a direction of reducing the volume of the compression space 103 (forward direction) to perform a compression stroke. In the compression stroke, the pressure of the compression space 103 increases to compress the sucked refrigerant. When the pressure of the compression space 103 reaches the set pressure, the discharge valve 17 is pushed out by the pressure of the compression space 103 to be opened from the cylinder 140, and the refrigerant is discharged from the discharge space 104 through the partitioned space. The compression stroke may be performed until the piston 150 reaches the top dead center where the volume of the compression space 103 becomes minimum.

By repetition of the suction stroke and the compression stroke of the piston 150, the refrigerant flowing into the receiving space 101 inside the compressor 100 through the suction pipe 114 flows into the suction space 102 inside the piston 150 through the suction guide 116a, the suction muffler 161, and the inner guide 162 in this order, and the refrigerant in the suction space 102 can flow into the compression space 103 inside the cylinder 140 during the suction stroke of the piston 150. In the compression stroke of the piston 150, after the refrigerant of the compression space 103 is compressed and discharged to the discharge space 104, a flow discharged to the outside of the compressor 100 through the ring pipe 115a and the discharge pipe 115 may be formed.

Fig. 3 is an exploded perspective view of a discharge valve unit according to an embodiment of the present invention. Fig. 4 is a plan view of an elastic member according to an embodiment of the present invention. Fig. 5 is an enlarged view of a portion a of fig. 4. Fig. 6 is an oblique view of a discharge valve according to an embodiment of the present invention. Fig. 7 to 11 are assembly process diagrams of the discharge valve unit according to an embodiment of the present invention.

As shown in fig. 3 to 11, the discharge valve unit 170 according to an embodiment of the present disclosure may include a base 171a, a coupling member 171b, and an elastic member 172, but some of them may be removed and other components may be added.

The discharge valve unit 170 may include a base 171 a. The base 171a may be disposed at one side of the combining member 171 b. The base 171a may be disposed under the combining member 171 b. The base 171a may be coupled to the lower surface of the coupling member 171 b. The upper surface of the base 171a may be combined with the lower surface of the combining member 171 b. The base 171a may be formed in a disc shape. A central portion of the base 171a may be formed to protrude upward. An upper surface of a central portion of the base 171a may be formed to protrude upward. The lower surface of the central portion of the base 171a may be concavely formed upward. The groove formed at the lower surface of the central portion of the base 171a prevents the piston 150 from colliding with the head 151 when it reaches the bottom dead center.

The base 171a may be formed of a plastic material. For example, the base 171a may be formed of a Fiber Reinforced Plastic (CF RTP) material. The base 171a may be formed by laminating a plurality of sheets (sheets) woven from fiber reinforced plastic.

The discharge valve unit 170 may include a coupling member 171 b. The coupling member 171b may be disposed at the base 171 a. The coupling member 171b may be disposed on the upper surface of the base 171 a. The lower surface of the coupling member 171b may be coupled to the upper surface of the base 171 a. The lower surface of the coupling member 171b may be compression molded to the upper surface of the base 171 a. The coupling member 171b may be formed of a metal material. The lower surface of the coupling part 171b may have roughness. A roughness may be provided on a lower surface of the combining member 171b opposite to the upper surface of the base 171 a. For example, the lower surface of the bonding member 171b may be formed with a micro-or nano-sized fine structure. The lower surface of the bonding member 171b may have roughness by a chemical method such as etching or a physical method such as scratching. Accordingly, when the coupling member 171b is compression molded at a high temperature on the base 171a, the plastic component of the base 171a is sufficiently melted into the fine structure of the lower surface of the metal coupling member 171b, so that the coupling force with respect to the coupling member 171b of the base 171a can be improved. Here, the high temperature means a temperature higher than the melting point of the resin (resi n) constituting the fiber reinforced plastic.

An upper region of the combining member 171b may have a smaller diameter than a lower region. The elastic member 172 may be coupled to the coupling member 171 b. The upper region of the combining part 171b may combine the elastic part 172.

The discharge valve unit 170 may include an elastic member 172. The elastic member 172 may be coupled to the coupling member 171 b. The elastic member 172 may be coupled to an upper region of the coupling member 171 b. The elastic member 172 may be riveted (rivet) to the coupling member 171 b.

The elastic member 172 may include a first hole 172 b. The first hole 172b may be formed at a central region of the body 172a of the elastic member 172. The first hole 172b may pass through upper and lower surfaces of the body 172a of the elastic member 172. The first hole 172b may correspond to a diameter of the coupling member 171 b. Specifically, the first hole 172b may correspond to a diameter at an upper region of the coupling member 171 b.

The resilient member 172 may include a groove 172 c. The groove 172c may be formed to be recessed outward from the inner side surface of the first hole 172 b. Thus, a space is formed between the inner surface of the first hole 172b and the coupling member 171 b. When the elastic member 172 is caulked to the coupling member 171b, the coupling member 171b is disposed in the groove 172c, so that the elastic member 172 is prevented from rotating relative to the coupling member 171 b. In the embodiment of the present specification, the cross section of the groove 172c has been described as having a "U" shape, but the shape of the groove 172c may be variously modified.

The elastic member 172 may include second holes 172d, 172e, 172 f. The second holes 172d, 172e, 172f may penetrate upper and lower surfaces of the body 172a of the elastic member 172. The second holes 172d, 172e, 172f may be formed in a spiral shape. The second apertures 172d, 172e, 172f may include a plurality of second apertures 172d, 172e, 172 f. The second holes 172d, 172e, 172f may be spaced apart. The plurality of second holes 172d, 172e, 172f may be formed quasi-symmetrically with respect to the first hole 172 b. The elastic force of the elastic member 172 may be increased by the plurality of second holes 172d, 172e, 172 f.

Next, an assembly process of the discharge valve unit 170 will be described with reference to fig. 7 to 11.

As shown in fig. 7 and 8, a plurality of sheets woven from fiber reinforced plastic are prepared, and after a metal coupling member 171b is provided thereon, the coupling member 171b is coupled to the base 171a by high-temperature compression molding.

As shown in fig. 9 to 11, after the elastic member 172 is disposed at the upper region of the combining member 171b, the elastic member 172 is riveted to the combining member 171b to dispose at least a portion of the combining member 171b in the groove 172 c.

The foregoing description of certain embodiments or other embodiments of the invention is not intended to be exhaustive or to limit the invention to the precise form disclosed. The various structures or functions of some embodiments or other embodiments of the invention described above may be combined or combined.

For example, the a configuration described in the specific embodiments and/or drawings and the B configuration described in the other embodiments and/or drawings may be combined. That is, even when the coupling between the components is not directly described, the coupling can be performed unless the coupling is explicitly described.

The foregoing detailed description is not to be taken in a limiting sense, but is made exemplary in all aspects. The scope of the invention should be determined by reasonable interpretation of the appended claims and all changes which come within the range of equivalency of the invention are intended to be embraced therein.

Claims (11)

1. A discharge valve unit comprising:

a base made of plastic;

a metal material combination component arranged on the base; and

an elastic member coupled to the coupling member;

the surface of the coupling member facing the base has roughness.

2. The discharge valve unit according to claim 1, wherein: the combination part is formed on the base in a compression molding mode.

3. The discharge valve unit according to claim 1, wherein: the base is made of CFRTP material.

4. The discharge valve unit according to claim 1, wherein: the elastic member is riveted to the coupling member.

5. The discharge valve unit according to claim 1, wherein: the elastic component comprises a first hole for combining the combining component; the diameter of the first hole corresponds to the diameter of the coupling member.

6. The discharge valve unit according to claim 5, wherein: a space is formed between the inner surface of the first hole and the coupling member.

7. The discharge valve unit according to claim 5, wherein: the elastic member includes a groove formed in a recessed manner in an inner surface of the first hole.

8. The discharge valve unit according to claim 7, wherein: the coupling member is disposed in the groove when the elastic member is riveted to the coupling member.

9. The discharge valve unit according to claim 1, wherein: the elastic member includes a body, a first hole formed in a central region of the body, and a plurality of second holes spaced apart from the first hole.

10. The discharge valve unit according to claim 9, wherein: the plurality of second holes are formed in a spiral shape; the plurality of second holes are formed symmetrically with respect to the first hole.

11. A compressor, comprising:

a frame;

a cylinder provided in the frame to form a refrigerant compression space;

a piston disposed in the cylinder and reciprocating in an axial direction; and

a discharge valve unit coupled to the frame to form a refrigerant discharge space through which the refrigerant discharged from the compression space flows;

the discharge valve unit includes a base made of a plastic material, a metal coupling member provided on the base, and an elastic member coupled to the coupling member;

the surface of the coupling member facing the base has roughness.

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