KR20200127463A - Linear compressor - Google Patents

Abstract

The present invention relates to a linear compressor for reducing noise generated through a suction valve formed of a plurality of blades having different stiffness. According to the idea of the present invention, the linear compressor includes a cylinder, a piston, a suction valve, and a valve fastening member. In addition, the suction valve includes a fixing part and a plurality of blades extending radially from the fixing part and deformed forward in an axial direction to open a suction port. In addition, the plurality of blades include a first blade and a second blade with lower rigidity or low stiffness than the first blade.

Description

Linear compressor {LINEAR COMPRESSOR}

The present invention relates to a linear compressor.

In general, a compressor is a mechanical device that receives power from a power generating device such as an electric motor or a turbine and compresses air, refrigerant or other various working fluids to increase pressure. It is widely used throughout.

The compressor is classified into a reciprocating compressor, a rotary compressor, and a scroll compressor according to a compression method of a working fluid.

Specifically, the reciprocating compressor includes a cylinder and a piston provided in the cylinder to enable linear reciprocating motion. Further, a compression space is formed between the piston head and the cylinder, and as the compression space is increased or decreased by the linear reciprocating motion of the piston, the working fluid in the compression space is compressed at high temperature and high pressure.

In addition, the rotary compressor includes a cylinder and a roller that rotates eccentrically within the cylinder. In addition, while the roller rotates eccentrically inside the cylinder, the working fluid supplied to the compression space is compressed at high temperature and high pressure.

In addition, the scroll compressor includes a fixed scroll and an orbiting scroll rotating around the fixed scroll. And, while the orbiting scroll rotates, the working fluid supplied to the compression space is compressed at high temperature and high pressure.

Recently, among the reciprocating compressors, development of a linear compressor in which a piston is directly connected to a linear motor for linear reciprocating motion has been actively made.

Specifically, the linear compressor is configured such that a piston in a sealed shell makes a linear reciprocating motion in a cylinder by a linear motor, suctioning and compressing the refrigerant into a compression space, and then discharging it. Accordingly, the piston is provided with a suction hole through which the refrigerant flows into the compression space and a suction valve opening and closing the suction hole.

In connection with such a linear compressor, the present applicant has filed a patent application (hereinafter, Prior Document 1) and registered.

1.Publication number: 10-2017-0124905 (Publication date: November 13, 2017)

2. Title of invention: linear compressor

The prior document 1 discloses the shape of the suction valve, and the suction valve is provided with a plurality of blades. Such a wing is provided to correspond to each suction hole so that each suction hole can be opened and closed.

At this time, there is a problem in that a predetermined noise is generated by the impact of the blade opening and closing the suction hole. In particular, there is a problem in that a plurality of wings simultaneously open and close the suction hole, and considerable noise is generated.

Such noise corresponds to a main noise source when the compressor is driven, and thus causes great inconvenience to users who use the compressor and devices equipped with the compressor.

The present invention has been proposed to solve this problem, and an object of the present invention is to provide a linear compressor that reduces noise generated through a suction valve formed of a plurality of blades having different stiffness.

In particular, as the plurality of blades are formed to have different thicknesses, lengths or widths, an object thereof is to provide a linear compressor including suction valves having different rigidities.

In addition, an object of the present invention is to provide a linear compressor in which noise is effectively reduced by variously changing the number of the plurality of blades and the suction holes opened and closed by the plurality of blades.

The compressor according to the idea of the present invention is characterized in that it includes a suction valve provided with blades having different stiffness.

The compressor according to the idea of the present invention includes a cylinder forming a compression space, a piston reciprocating in an axial direction to vary the volume of the compression space, and having a suction port for supplying a refrigerant to the compression space, and the suction port. A suction valve disposed on a front surface of the piston forming the compression space to open and close, and a valve fastening member passing through the suction valve and inserted into the front surface of the piston to fasten the suction valve to the piston are included.

And, the suction valve, the fixing portion in close contact with the front surface of the piston by the valve fastening member and extending radially from the fixing portion, deformed axially forward from the front of the piston to open the suction port Includes multiple wings.

In addition, the plurality of wings includes a first wing and a second wing formed with lower rigidity or low stiffness than that of the first wing.

In detail, the second wing may be 1) further extended in the radial direction, 2) thinner in the axial direction, or 3) narrower in the circumferential direction than the first wing.

In this case, the suction port includes a plurality of suction holes centered on a virtual pitch circle formed on the front surface of the piston and spaced apart in a circumferential direction along the pitch circle.

That is, the plurality of suction holes are respectively formed along the circumference of one circle (pitch circle).

According to the present invention, there is an advantage in that the plurality of blades provided in the suction valve are provided with different stiffness, so that noise generated when opening and closing the suction hole due to the refrigerant flow can be reduced.

In addition, as the plurality of blades are provided with different thicknesses, lengths, or widths, suction valves having different rigidities may be formed. Accordingly, there is an advantage in that the impact sound between the suction valve and the piston can be reduced and noise can be reduced.

In detail, since the blades having different stiffness have different strain or response rates, the suction hole may be opened and closed at different timings according to the flow of the refrigerant. Accordingly, there is an advantage that the impact of the front surface of the blade and the piston is generated at different timings and noise can be reduced.

In addition, since the plurality of blades and suction holes opened and closed by the plurality of blades are provided in various numbers, noise can be effectively reduced according to the design.

1 is a view showing a linear compressor according to an embodiment of the present invention.
2 is an exploded view of a shell and a shell cover of a linear compressor according to an embodiment of the present invention.
3 is an exploded view showing the configuration of a linear compressor according to an embodiment of the present invention.
4 is a cross-sectional view taken along line IV-IV' of FIG. 1.
5 and 6 are views showing a piston and a suction valve of a linear compressor according to a first embodiment of the present invention.
7 is a front view of a piston of a linear compressor according to a first embodiment of the present invention.
8 to 10 are views showing various intake valves of the linear compressor according to the first embodiment of the present invention.
11 and 12 are views showing a piston and a suction valve of a linear compressor according to a second embodiment of the present invention.
13 is a front view of a piston of a linear compressor according to a second embodiment of the present invention.
14 to 16 are views showing various intake valves of a linear compressor according to a second embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail through exemplary drawings. In adding reference numerals to elements of each drawing, it should be noted that the same elements are assigned the same numerals as possible even if they are indicated on different drawings. In addition, in describing an embodiment of the present invention, when it is determined that a detailed description of a related known configuration or function interferes with an understanding of the embodiment of the present invention, the detailed description thereof will be omitted.

In addition, in describing the constituent elements of an embodiment of the present invention, terms such as first, second, A, B, (a), and (b) may be used. These terms are only used to distinguish the component from other components, and the nature, order, or order of the component is not limited by the term. When 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 another component between each component It should be understood that may be “connected”, “coupled” or “connected”.

FIG. 1 is a view showing a linear compressor according to an embodiment of the present invention, and FIG. 2 is an exploded view showing a shell and a shell cover of a linear compressor according to an embodiment of the present invention.

1 and 2, a compressor 10 according to an 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 and 103 can be understood as one configuration of the shell 101.

A leg 50 may be coupled to the lower side of the shell 101. The leg 50 may be coupled to a base of a product on which the 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 an approximately cylindrical shape and may be laid in a horizontal direction or laid in an axial direction. Referring to FIG. 1, the shell 101 extends long in the horizontal direction and may have a slightly lower height in the radial direction. That is, since the compressor 10 may have a low height, when the compressor 10 is installed on the machine room base of a refrigerator, there is an advantage that the height of the machine room can be reduced.

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

Outside of the terminal 108, a bracket 109 is installed. 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 impact.

Both sides of the shell 101 are configured to be opened. 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 include a first shell cover 102 coupled to an opened side of the shell 101 and a second shell cover 103 coupled to the opened other side of the shell 101. ) Is included. 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 on the right side of the compressor 10, and the second shell cover 103 may be located on the left side of the compressor 10. In other words, the first and second shell covers 102 and 103 may be disposed to face each other.

The compressor 10 further includes a plurality of pipes 104, 105, and 106 provided in the shell 101 or the shell covers 102, 103 and capable of sucking, discharging or injecting a refrigerant.

In the plurality of pipes 104, 105, 106, a suction pipe 104 through which refrigerant is sucked into the inside of the compressor 10, a discharge pipe 105 through which the compressed refrigerant is discharged from the compressor 10, and a refrigerant are provided. A process pipe 106 for replenishing the compressor 10 is included.

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

The discharge pipe 105 may be coupled to the outer peripheral 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 closer to the second shell cover 103 than the first shell cover 102.

The process pipe 106 may be coupled to the outer peripheral surface of the shell 101. The operator may inject the refrigerant into the compressor 10 through the process pipe 106.

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 (or radial 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, operation convenience can be achieved.

At least a portion of the second shell cover 103 may be positioned adjacent to the inner circumferential surface of the shell 101 corresponding to the point where 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, in terms of the flow path of the refrigerant, the size of the flow path of the refrigerant 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 through it. And is formed to grow again. In this process, the pressure of the refrigerant is reduced, so that the refrigerant can be vaporized, and in this process, the oil contained in the refrigerant can be separated. Accordingly, as the refrigerant from which oil is separated flows into the piston 130 (refer to FIG. 3), the compression performance of the refrigerant may be improved. The oil can be understood as the hydraulic oil present in the cooling system.

On the inner surface of the first shell cover 102, a cover support portion 102a is provided. A second support device 185 to be described later may be coupled to the cover support part 102a. The cover support part 102a and the second support device 185 may be understood as a device for supporting the main body of the compressor 10. Here, the main body of the compressor means a component provided inside the shell 101, and may include, for example, a driving part for back and forth reciprocating motion and a support part supporting the driving part. The driving unit may include components such as a piston 130, a magnet frame 138, a permanent magnet 146, a supporter 137, and a suction muffler 150 to be described later. In addition, the support may include components such as resonance springs 176a and 176b, rear cover 170, stator cover 149, a first support device 165 and a second support device 185 to be described later. .

A stopper 102b may be provided on the inner side of the first shell cover 102. The stopper 102b is understood as a configuration that prevents the main body of the compressor, particularly the motor assembly 140, from being damaged by colliding with the shell 101 due to vibration or shock generated during transport of the compressor 10. . The stopper 102b is located adjacent to the rear cover 170 to be described later, and when shaking occurs in the compressor 10, the rear cover 170 interferes with the stopper 102b, thereby the motor assembly It is possible to prevent the transmission of the impact to the 140.

On the inner circumferential surface of the shell 101, a spring fastening portion 101a may be provided. For example, the spring fastening part 101a may be disposed at a position adjacent to the second shell cover 103. The spring fastening portion 101a may be coupled to the first support spring 166 of the first support device 165 to be described later. As the spring fastening portion 101a and the first support device 165 are coupled, the main body of the compressor can be stably supported inside the shell 101.

3 is an exploded view showing the configuration of a linear compressor according to an embodiment of the present invention, and FIG. 4 is a cross-sectional view taken along line IV-IV' of FIG. 1.

3 and 4, in the compressor 10 according to the embodiment of the present invention, a cylinder 120 provided inside the shell 101 and a reciprocating linear motion within the cylinder 120 A motor assembly 140 is included as a linear motor that provides driving force to the piston 130 and the piston 130. When the motor assembly 140 is driven, the piston 130 may reciprocate in the axial direction.

The compressor 10 further includes a suction muffler 150 connected to the piston 130 and configured 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, while the refrigerant passes 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 151, 152, and 153 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. In addition, the third muffler 153 may accommodate the second muffler 152 therein and may extend to the rear of the first muffler 151. From the viewpoint 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.

A muffler filter (not shown) may be positioned at an interface where the first muffler 151 and the second muffler 152 are coupled. For example, the muffler filter may have a circular shape, and an outer peripheral portion of the muffler filter may be supported between the first and second mufflers 151 and 152.

Hereinafter, for convenience of description, a 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. 4. 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". For example, 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 reciprocates, and can be understood as the vertical direction of FIG. 4.

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 reciprocates within the cylinder 120, and the piston flange 132 reciprocates outside the cylinder 120.

The cylinder 120 is configured to receive at least a portion of the first muffler 151 and at least a portion of the piston body 131.

Inside the cylinder 120, a compression space P in which the refrigerant is compressed by the piston 130 is formed. In addition, a suction port 133 for introducing a refrigerant into the compression space P is formed on the front surface of the piston body 131.

In addition, the compressor 10 includes a suction valve 200 selectively opening the suction port 133 and a valve fastening member 134 penetrating the suction valve 200 and inserted into the piston 130 More included. This will be described in detail after FIG. 5.

In addition, the compressor 10 includes a discharge cover 160 and discharge valve assemblies 161 and 163. The discharge cover 160 is installed in front of the compression space P to form a discharge space 160a of the refrigerant discharged from the compression space P. The discharge space 160a includes a plurality of spaces partitioned by the inner wall of the discharge cover 160. The plurality of space portions are disposed in a front-rear direction and may communicate with each other.

The discharge valve assemblies 161 and 163 are coupled to the discharge cover 160 and selectively discharge the refrigerant compressed in the compression space P. The discharge valve assemblies 161 and 163 are opened when the pressure in the compression space P is equal to or higher than the discharge pressure, and discharge with the discharge valve 161 and the discharge valve 161 for introducing the refrigerant into the discharge space 160a. A spring assembly 163 is provided between the covers 160 to provide an elastic force in the axial direction.

The spring assembly 163 includes a valve spring 163a and a spring support part 163b for supporting the valve spring 163a to the discharge cover 160. For example, the valve spring 163a may include a leaf spring. In addition, the spring support part 163b may be injection-molded integrally with the valve spring 163a by an injection process.

The discharge valve 161 is coupled to the valve spring 163a, and a rear part or a rear surface of the discharge valve 161 is positioned to be supported on the front surface of the cylinder 120. When the discharge valve 161 is supported on the front surface of the cylinder 120, the compression space P is maintained in a closed state, and when the discharge valve 161 is separated from the front surface of the cylinder 120, the compression The space P is opened so that the compressed refrigerant inside the compressed space P may be discharged.

That is, the compression space P is understood as a space formed between the suction valve 200 and the discharge valve 161. In addition, the suction valve 200 is formed on one side of the compression space P, and the discharge valve 161 is provided on the other side of the compression space P, that is, on the opposite side of the suction valve 200 Can be.

In the course of the piston 130 reciprocating and linear movement inside the cylinder 120, when the pressure in the compression space P becomes less than or equal to the suction pressure, the suction valve 200 is opened so that the refrigerant is transferred to the compressed space ( P) is inhaled. On the other hand, when the pressure in the compression space P is equal to or higher than the suction pressure, the refrigerant in the compression space P is compressed while the suction valve 200 is closed.

On the other hand, when the pressure in the compression space (P) becomes more than the discharge pressure, the valve spring (163a) is deformed forward to open the discharge valve (161), and the refrigerant is discharged from the compression space (P). , It is discharged to the discharge space of the discharge cover 160. When the discharge of the refrigerant is completed, the valve spring 163a provides a restoring force to the discharge valve 161 so that the discharge valve 161 is closed.

In addition, a cover pipe 162a is coupled to the discharge cover 160 to discharge the refrigerant flowing through the discharge space 160a of the discharge cover 160. For example, the cover pipe 162a may be made of a metal material.

In addition, a roof pipe 162b is further coupled to the cover pipe 162a to transfer the refrigerant flowing through the cover pipe 162a to the discharge pipe 105. One side of the roof pipe 162b may be coupled to the cover pipe 162a, and the other side may be coupled to the discharge pipe 105.

The roof pipe 162b is made of a flexible material, and may be formed relatively long. In addition, the roof pipe 162b extends roundly along the inner circumferential surface of the shell 101 from the cover pipe 162a, and may be coupled to the discharge pipe 105. For example, the roof pipe 162b may have a wound shape.

The compressor 10 further includes a frame 110. The frame 110 is understood as a configuration for fixing the cylinder 120. As an example, the cylinder 120 may be press-fit into the frame 110. The cylinder 120 and the frame 110 may be made of aluminum or aluminum alloy.

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. In addition, the discharge cover 160 may be coupled to the front surface of the frame 110 by a fastening member.

The motor assembly 140 includes an outer stator 141 fixed to the frame 110 and disposed to surround the cylinder 120, and an inner stator 148 disposed to be 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 force between 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 may be configured by combining a plurality of magnets having three poles.

The permanent magnet 146 may be installed on 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.

In detail, based on the cross-sectional view of FIG. 4, the magnet frame 138 is coupled to the piston flange 132 and extends in an outer radial direction and may be bent forward. 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 together with the permanent magnet 146 in the axial direction.

The outer stator 141 includes coil winding bodies 141b, 141c and 141d and a stator core 141a. The coil winding bodies 141b, 141c, and 141d include a bobbin 141b and a coil 141c wound in the circumferential direction of the bobbin. Further, the coil winding bodies 141b, 141c, and 141d further include a terminal portion 141d for guiding a power line connected to the coil 141c to be drawn out or exposed to the outside of the outer stator 141. The terminal portion 141d may be disposed to be inserted into a terminal insertion portion provided in the frame 110.

The stator core 141a includes a plurality of core blocks configured by stacking a plurality of laminations in a circumferential direction. The plurality of core blocks may be disposed to surround at least a portion of the coil winding bodies 141b, 141c, and 141d.

A stator cover 149 is provided on 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 may be supported by the stator cover 149.

The stator cover 149 and the frame 110 are fastened by a cover fastening member 149a. The cover fastening member 149a penetrates through the stator cover 149 and extends forward toward the frame 110 and may be coupled to a fastening hole provided in the frame 110.

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

The 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 disposed inside the supporter 137 so that the suction muffler 150 penetrates. The piston flange 132, the magnet frame 138, and the supporter 137 may be fastened by a fastening member.

A 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.

The compressor 10 further includes a rear cover 170 coupled to the stator cover 149 and extending rearwardly, and supported by a second support device 185.

In detail, the rear cover 170 includes three support legs, and the three support legs may be coupled to the rear surface of the stator cover 149. A spacer 181 may be interposed between the three support legs and the rear surface of the stator cover 149. By adjusting the thickness of the spacer 181, a distance from the stator cover 149 to the rear end of the rear cover 170 may be determined. In addition, the rear cover 170 may be spring supported by the supporter 137.

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

The compressor 10 further includes a plurality of resonance springs 176a and 176b whose natural frequencies are adjusted so that the piston 130 can perform resonance motion.

In the plurality of resonance springs (176a, 176b), a first resonance spring (176a) supported between the supporter 137 and the stator cover 149, and between the supporter 137 and the rear cover 170 A second resonant spring 176b supported is included. By the action of the plurality of resonant springs 176a and 176b, a stable movement of the driving unit reciprocating inside the compressor 10 is performed, and generation of vibration or noise caused by the movement of the driving unit may be reduced.

The supporter 137 includes a first spring support part 137a coupled to the first resonance spring 176a.

The compressor 10 includes a plurality of sealing members 127, 128, 129a, and 129b for increasing the coupling force between the frame 110 and parts around the frame 110.

In detail, the plurality of sealing members 127, 128, 129a and 129b includes a first sealing member 127 provided at a portion where the frame 110 and the discharge cover 160 are coupled. The first sealing member 127 may be disposed in the first installation groove of the frame 110.

The plurality of sealing members 127, 128, 129a, and 129b further includes a second sealing member 128 provided at a portion where the frame 110 and the cylinder 120 are coupled. The second sealing member 128 may be disposed in the second installation groove of the frame 110.

The plurality of sealing members 127, 128, 129a and 129b further includes a third sealing member 129a provided between the cylinder 120 and the frame 110. The third sealing member 129a may be disposed in a cylinder groove formed at a rear portion of the cylinder 120. The third sealing member (129a) prevents the refrigerant in the gas pocket formed between the inner circumferential surface of the frame and the outer circumferential surface of the cylinder from leaking to the outside, and increases the coupling force between the frame 110 and the cylinder 120 Can be done.

The plurality of sealing members 127, 128, 129a, and 129b further include a fourth sealing member 129b provided at a portion where the frame 110 and the inner stator 148 are coupled. The fourth sealing member 129b may be disposed in the third installation groove of the frame 110. The first to fourth sealing members 127, 128, 129a, and 129b may have a ring shape.

The compressor 10 further includes a first support device 165 coupled to the discharge cover 160 and supporting one side of the main body of the compressor 10. The first support device 165 is disposed adjacent to the second shell cover 103 to elastically support the main body of the compressor 10. In detail, the first support device 165 includes a first support spring 166. The first support spring 166 may be coupled to the spring fastening portion 101a described in FIG. 2.

The compressor 10 further includes a second support device 185 coupled to the rear cover 170 and supporting the other side of the main body of the compressor 10. The second support device 185 may be coupled to the first shell cover 102 to elastically support the main body of the compressor 10. In detail, the second support device 185 includes a second support spring 186. The second support spring 186 may be coupled to the cover support part 102a described in FIG. 2.

The cylinder 120 includes a cylinder body 121 extending in the axial direction and a cylinder flange 122 provided outside the front portion of the cylinder body 121. The cylinder body 121 has a cylindrical shape having a central axis in the axial direction, and is inserted into the frame 110. Accordingly, the outer circumferential surface of the cylinder body 121 may be positioned to face the inner circumferential surface of the frame 110.

A gas inlet 126 through which at least some of the refrigerants discharged through the discharge valve 161 is introduced is formed in the cylinder body 121. The at least part of the refrigerant is understood as a refrigerant used as a gas bearing between the piston 130 and the cylinder 120.

The refrigerant used as the gas bearing is between the inner circumferential surface of the frame 110 and the outer circumferential surface of the cylinder 120 via a gas hole 114 formed in the frame 110 as shown in FIG. 4. Flows into the formed gas pockets. In addition, the refrigerant in the gas pocket may flow to the gas inlet 126.

In detail, the gas inlet 126 may be configured to be recessed radially inward from the outer peripheral surface of the cylinder body 121. Further, the gas inlet 126 may be configured to have a circular shape along the outer circumferential surface of the cylinder body 121 with respect to an axial central axis. A plurality of gas inlet portions 126 may be provided. For example, two gas inlet portions 126 may be provided.

The cylinder body 121 includes a cylinder nozzle 125 extending radially inward from the gas inlet 126. The cylinder nozzle 125 may extend to an inner circumferential surface of the cylinder body 121.

The refrigerant that has passed through the gas inlet 126 is introduced into the space between the inner peripheral surface of the cylinder body 121 and the outer peripheral surface of the piston body 131 through the cylinder nozzle 125. This refrigerant provides a levitation force to the piston 130 to perform the function of a gas bearing for the piston 130.

5 and 6 are views showing a piston and a suction valve of a linear compressor according to a first embodiment of the present invention.

5 and 6, the piston 130 has a substantially cylindrical shape, the piston body 131 extending in the front and rear direction, and the piston extending radially outward from the piston body 131 A flange 132 is included.

A first piston groove 136a is formed on the outer peripheral surface of the piston body 131. The first piston groove 136a may be located in front of the piston body 131 in the radial direction of the center line. The first piston groove 136a may be understood as a configuration provided to guide smooth flow of the refrigerant gas flowing through the cylinder nozzle 125 and prevent pressure loss.

In addition, a second piston groove 136b is formed on the outer peripheral surface of the piston body 131. The second piston groove 136b may be located at the rear of the piston body 131 in the radial direction of the center line. That is, the second piston groove 136b may be understood to be disposed between the first piston groove 136a and the piston flange 132.

In addition, the second piston groove 136b may be understood as a "discharge guide groove" that guides the refrigerant gas used to float the piston 130 to be discharged to the outside of the cylinder 120. The refrigerant gas is discharged to the outside of the cylinder 120 through the second piston groove 136b, so that the refrigerant gas used in the gas bearing passes through the front of the piston body 131 to the compressed space P. It can prevent re-entry.

The piston flange 132 includes a flange body 132a extending radially outward from the rear portion of the piston body 131 and a piston fastening portion 132b further extending radially outward from the flange body 132a. Is included.

The piston fastening part 132b includes a piston fastening hole 132c to which a predetermined fastening member is coupled. The fastening member may pass through the piston fastening hole 132c and be coupled to the magnet frame 138 and the supporter 137. In addition, the plurality of piston fastening parts 132b may be provided, and the plurality of piston fastening parts 132b may be spaced apart from each other and disposed on the outer circumferential surface of the flange body 132a.

The rear portion of the piston body 131 is opened, so that the refrigerant can be sucked. At least a portion of the suction muffler 150 may be inserted into the piston body 131 through a rear portion of the opened piston body 131.

As described above, the piston 130 is provided so as to reciprocate in the axial direction, that is, the front-rear direction within the cylinder 120. In particular, it may be understood that the piston 130 reciprocates in the axial direction to change the volume of the compression space P.

At this time, the piston 130 may also be understood as a configuration forming the compression space (P). In detail, the axial front surface (131a) of the piston (130) forms the compression space (P). That is, the front surface 131a is reciprocated by the axial reciprocating movement of the piston 130 and the volume of the compression space P may be varied.

A suction port 133 for supplying a refrigerant to the compression space P is formed on the front surface 131a. The suction port 133 may be understood as a hole formed in the axial front of the piston 130 to guide the refrigerant to the compression space P.

In addition, a fastening hole 131b for coupling the suction valve 200 and the piston 130 is formed on the front surface 131a. The fastening hole 131b may be understood as a hole into which the valve fastening member 134 is inserted.

The fastening hole 131b is located in the center of the front surface 131a, and the suction port 133 is located outside the fastening hole 131b. In detail, the suction port 133 includes a plurality of suction holes, and the plurality of suction holes may be disposed to surround the fastening hole 131b.

The suction valve 200 is disposed on the front surface 131a to open and close the suction port 133. In detail, the suction valve 200 may be coupled to the piston 130 by the valve fastening member 134. At this time, a part of the suction valve 200 is in close contact with the front surface 131a by the valve fastening member 134, and this is referred to as a fixing part 202.

The fixing part 202 is provided with a coupling hole 204 through which the valve fastening member 134 passes. The coupling hole 204 may be sequentially disposed in the axial direction with the fastening hole 131b to form one hole. In addition, as shown in FIG. 6 to 5, the valve fastening member 134 passes through the coupling hole 204 and is inserted into the fastening hole 131b.

In addition, the suction valve 200 includes a plurality of blades 210 and 220 extending radially from the fixing part 202 to open the suction port 133. In this case, the plurality of blades 210 and 220 may be understood as the rest of the suction valve 200 rather than the fixing part 202. That is, the suction valve 200 is divided into the fixing part 202 and the plurality of blades.

In addition, the plurality of blades 210 and 220 correspond to a portion that is deformed from the front surface of the piston 130 to the front in the axial direction. That is, as the plurality of wings 210 and 220 are deformed, the suction port 133 may be opened.

At this time, the compressor 10 according to the idea of the present invention includes a plurality of blades 210 and 220 having different rigidities or low stiffness. In general, stiffness represents the degree to which a material resists elastic deformation when it undergoes elastic deformation. That is, the plurality of wings 210 and 220 are deformed differently from each other, and the suction port 133 may be opened.

The plurality of wings includes a first wing 210 and a second wing 220 formed with a lower rigidity or low stiffness than the first wing 210. In this case, the low stiffness corresponds to a relative value, and a reference value may not exist. In other words, the low rigidity corresponds to an example of the expression that the first wing 210 and the second wing 220 have different rigidities.

Accordingly, the second blade 220 can be more easily deformed than the first blade 220 by the same external force, in detail, the pressure of the refrigerant. That is, it can be said that the second wing 220 has a higher strain rate or better response rate than the second wing 220.

As a result, the first wing 220 and the second wing 220 may open the suction port 133 with a time difference. In detail, the second wing 220 may open the suction port 133 faster than the first wing 210 and close the suction port later.

Such stiffness is proportional to the width (width) and thickness of the wing, and inversely proportional to the length. At this time, the width of the blade corresponds to the circumferential length, the thickness of the blade corresponds to the axial length, and the length of the blade corresponds to the radial length. Accordingly, as the width and thickness of the blade increases, the mass increases and the rigidity increases. On the other hand, as the length of the blade increases, it moves away from the fixing part 202 and receives a larger moment, thereby reducing stiffness.

Accordingly, the second blade 220 may have a width extending in the circumferential direction or a thickness extending in the axial direction smaller than that of the first blade 210, or may have a length extending in the radial direction longer. This will be described later in detail with reference to FIGS. 8 to 10.

7 is a front view of a piston of a linear compressor according to a first embodiment of the present invention.

As shown in FIG. 7, a virtual pitch circle (pc) may be formed on the front surface 131a of the piston 130. At this time, the pitch circle (pc) means a circle passing through the center of each hole. In addition, the fastening hole 131b is disposed in the center of the pitch circle pc.

The suction port 133 includes a plurality of suction holes formed centered on the pitch circle (pc). In other words, the pitch circle (pc) corresponds to a circle extending the center of the plurality of suction holes. Since the pitch circle (pc) is provided as a circle having the same radial diameter, it can be understood that the plurality of suction holes are spaced apart by the same distance from the fastening hole (131b).

In addition, the plurality of suction holes are disposed to be spaced apart in the circumferential direction along the pitch circle (pc). For example, in the plurality of suction holes, a first suction hole (133a) and a second suction hole (133b) and a third suction hole (133c) respectively formed on both sides of the circumferential direction of the first suction hole (133a) This includes. That is, along the pitch circle pc, the second suction hole 133b, the first suction hole 133a, and the third suction hole 133c are sequentially disposed.

At this time, the first suction hole (133a) is disposed adjacent to the second suction hole (133b) and the circumferential direction than the third suction hole (133c). That is, the plurality of suction holes are disposed to be spaced apart at different intervals in the circumferential direction.

In particular, the plurality of suction holes may be formed in a plurality of pairs. The suction holes formed in pairs are located closer to each other in the circumferential direction than the other suction holes. That is, the first suction hole (133a) and the second suction hole (133b) may be understood as a pair. In addition, the third suction hole (133c) and the fourth suction hole (133d) is provided closest to the circumferential direction, the third suction hole (133c) and the fourth suction hole (133d) will be understood as a pair. I can.

At this time, the pair of suction holes are simultaneously opened and closed by one wing. In other words, a single wing can open and close a pair of suction holes. Accordingly, as one blade is deformed, a pair of suction holes are opened, and a refrigerant may flow through the pair of suction holes.

In detail, the first suction hole 133a and the second suction hole 133b are simultaneously opened and closed by either the first blade 210 or the second blade 220. In this case, the third suction hole 133c may be opened and closed by the other one of the first wing 210 and the second wing 220. That is, the third suction hole 133c may be opened and closed by a blade different from the first suction hole 133a and the second suction hole 133b.

It may be understood that the third suction hole 133c is opened and closed separately from the first suction hole 133a and the second suction hole 133b. Separately opened and closed can be understood as being opened or closed at different times.

In the above, a common part of the compressor according to the idea of the present invention has been described. Accordingly, the above description is cited for each embodiment, and redundant descriptions are omitted. Hereinafter, it will be described in detail for each embodiment.

The suction valve 200 of the linear compressor according to the first embodiment of the present invention includes a plurality of the first blades 210 and the second blades 220, respectively. In addition, the first wing 210 and the second wing 220 are alternately arranged in the circumferential direction. That is, the first wing 210 and the second wing 220 may be provided in the same number.

5 and 6, the suction valve 200 includes four blades. In detail, the suction valve 200 includes two first blades 210 and two second blades 220. Accordingly, it can be seen that the two first blades 210 and the two second blades 220 extend radially opposite to each other around the fixing part 202.

However, this is exemplary, and the suction valve 200 may include four or more blades. For example, six blades may be included in the suction valve 200, and three of the first blades 210 and the second blades 220 may be included.

As described above, one wing can open and close a pair of suction holes. Accordingly, referring to FIGS. 5 to 7, eight suction holes may be included in the suction port 133. In addition, it can be understood that the suction port 133 has four pairs of suction holes. In addition, it can be seen that any two pairs of suction holes are opened and closed by the first wing 210, and the remaining two pairs of suction holes are opened and closed by the second wing 220.

Hereinafter, a suction valve provided with a plurality of blades having different stiffness will be described in detail as an example.

8 to 10 are views showing various intake valves of the linear compressor according to the first embodiment of the present invention. For convenience of explanation, in FIGS. 8 to 10, a pitch line and a suction hole together with the suction valve are illustrated by a chain line and a dotted line, respectively.

As described above, the second wing 220 is 1) the thickness extending in the axial direction is smaller than the first wing 210, 2) the length extending in the radial direction is long, or 3) the width extending in the circumferential direction It can be formed small.

In FIG. 8, a case of 1), a case of 2) in FIG. 9, and a case of 3) in FIG. 10 are shown. For common configurations, the same reference numerals are used, and the contents described above are cited. For different configurations, a, b, and c are assigned to the reference numerals, respectively, and the differences will be described.

As shown in FIG. 8, the suction valve 200a includes a first blade 210a having a first thickness t1 and a second blade 220a having a second thickness t2. In addition, the first thickness t1 is formed to be thicker than the second thickness t2 (t1>t2). As described above, the thickness corresponds to the axial length.

Further, the suction valve 200a includes a step 212 formed between the fixing part 204 and the first blade 210a. In other words, the first wing (210a) is formed thicker than the fixing portion (204). In particular, the fixing part 204 may be formed to have the same thickness as the second wing 220a.

At this time, the fixing part 204 is shown as a part in close contact with the front surface 131a by the head of the valve fastening member 134. In detail, the fixing part 204 is shown as a concentric circle having a larger diameter than the coupling hole 204. In addition, a portion other than the fixing portion 204 may be defined as a wing, or a wing may be defined based on the stepped portion 212. It may be difficult to clearly distinguish between the fixing part 204 and the blade as a part of the suction valve 200a.

In addition, the suction valve 200a may form a step difference between the second blade 220a and the fixing part 204. That is, the fixing part 204 and the first wing 210a may be formed to have the same thickness, and the second wing 220a may be formed to be thinner.

In this case, it is assumed that the external conditions of the first wing 210a and the second wing 220a except for the thickness are the same. Accordingly, it can be understood that the thicker first wing 210a is provided with high rigidity compared to the second wing 220a. Accordingly, the first wing 210a may open the suction port 133 later than the second wing 220a and close the suction port 133 faster.

As shown in FIG. 9, the suction valve 200b includes a first wing 210b having a first length L1 and a second wing 220b having a second length L2. In addition, the first length L1 is formed to be shorter than the second length L2 (L1<L2).

As described above, the length corresponds to the radial length. In detail, it may be defined as the maximum length in the radial direction from the center of the coupling hole 204. That is, the second wing 220b is formed to extend longer in the radial direction from the fixing part 202 than the first wing 210b.

In particular, the first wing (210b) and the second wing (220b) is formed to extend more radially outward than the pitch circle (pc) so as to cover the suction port 133. In this case, it may be understood that the second wing 220b extends further outward in the radial direction of the pitch circle pc than the first wing 210b.

In this case, it is assumed that the external conditions of the first wing 210b and the second wing 220b except for the length are the same. Accordingly, it can be understood that the second wing 220b formed longer is provided with lower rigidity compared to the first wing 210b. Accordingly, the second blade 220b may open the suction port 133 faster than the first blade 210b and close the suction port 133 later.

As shown in FIG. 10, the suction valve 200c includes a first wing 210c having a first width W1 and a second wing 220c having a second width W2. In addition, the first width W1 is formed larger than the second width W2 (W1>W2).

As described above, the width corresponds to the length in the circumferential direction. In detail, it may be defined as a length covering the circumference of the pitch circle (pc). That is, the first wing 210c is formed to cover a wider circumference of the pitch circle pc than the second wing 220c.

In particular, the first wing (210b) and the second wing (220b) are formed gradually wider in the circumferential direction toward the outer side in the radial direction from the fixing portion 202. At this time, it can be understood that the first wing 210c gradually widens in the circumferential direction at a larger ratio than the second wing 220c.

In this case, it is assumed that the external conditions of the first wing 210c and the second wing 220c are the same except for the width. Accordingly, it may be understood that the first wing 210c formed wider is provided with high rigidity compared to the second wing 220c. Accordingly, the first wing 210a may open the suction port 133 later than the second wing 220a and close the suction port 133 faster.

In FIGS. 8 to 10, thickness, length, and width were respectively illustrated and described. However, such an embodiment may be selectively used together and is not limited to one.

For example, the second wing may have a smaller width and thickness than the first wing. In addition, the second wing may have a narrower width and longer length than the first wing. In addition, the second wing may be formed to be thinner and longer in length than the first wing. In addition, the second wing may have a smaller width and thickness than the first wing, and may have a longer length.

11 and 12 are views showing a piston and a suction valve of a linear compressor according to a second embodiment of the present invention, and FIG. 13 is a front view showing a piston of a linear compressor according to a second embodiment of the present invention. to be.

In the suction valve 300 of the linear compressor according to the second embodiment of the present invention, the first blade 310 and the second blade 320 are provided in different numbers. That is, the suction valve 200 according to the first embodiment has an even number of blades, but the suction valve 300 according to the second embodiment has an odd number of blades. Hereinafter, only differences from the first embodiment will be described in detail, and the above description is cited for common parts.

For example, the suction valve 300 may have three blades, and may include one first blade 310 and two second blades 320. Also, one second wing 320 and two first wings 310 may be provided.

In addition, the first wing 310 and the second wing 320 may be provided in plurality, respectively. 11 and 12, the suction valve 300 includes five blades. In detail, the suction valve 300 includes two first blades 310 and three second blades 320. In addition, the suction valve 300 may include three first blades 310 and two second blades 320.

However, this is exemplary, and the suction valve 200 may include five or more blades. For example, the suction valve 200 includes seven blades, and the first blade 210 and the second blade 220 may be included in each of three or four.

As described above, one wing can open and close a pair of suction holes. Accordingly, referring to FIG. 13, 10 suction holes may be included in the suction port 133. In addition, it can be understood that the suction port 133 has 5 pairs of suction holes.

At this time, as described in FIG. 7, the suction port 133 includes a first suction hole 133a, a second suction hole 133b, and a third suction hole 133c. In addition, in FIG. 13 rather than FIG. 7, the circumferential separation distance between the first suction hole 133a and the third suction hole 133c is shortened. This can be understood as a natural result as the number of suction holes increases.

14 to 16 are views showing various intake valves of a linear compressor according to a second embodiment of the present invention. For convenience of explanation, in FIGS. 14 to 16, a pitch line and a suction hole together with the suction valve are illustrated by a dashed line and a dotted line, respectively.

As described above, the second wing 220 is 1) the thickness extending in the axial direction is smaller than the first wing 210, 2) the length extending in the radial direction is long, or 3) the width extending in the circumferential direction It can be formed small.

In FIG. 14, a case of 1), a case of 2) in FIG. 15, and a case of 3) in FIG. 16 are shown. For common configurations, the same reference numerals are used, and the contents described above are cited. For different configurations, a, b, and c are assigned to the reference numerals, respectively, and the differences will be described.

As shown in FIG. 14, the suction valve 300a includes a first blade 310a having a first thickness t1 and a second blade 320a having a second thickness t2. In addition, the first thickness t1 is formed to be thicker than the second thickness t2 (t1>t2). As described above, the thickness corresponds to the axial length.

Further, the suction valve 300a includes a step 312 formed between the fixing part 204 and the first blade 310a. In other words, the first wing 310a is formed thicker than the fixing part 204. In particular, the fixing part 204 may be formed to have the same thickness as the second wing 320a.

In this case, it is assumed that the external conditions of the first wing 310a and the second wing 320a excluding the thickness are the same. Accordingly, it can be understood that the thicker first wing 310a is provided with high rigidity compared to the second wing 320a. Accordingly, the first wing 310a may open the suction port 133 later than the second wing 320a and close the suction port 133 faster.

Further, the suction valve 300a is provided with three first blades 310a and two second blades 320a. At this time, the number of the first wing (310a) and the second wing (320a) may be provided differently depending on the design. As the suction valve 300a has more of the first blades 310a having relatively high rigidity, stability may be achieved.

As shown in FIG. 15, the suction valve 300b includes a first wing 310b having a first length L1 and a second wing 320b having a second length L2. In addition, the first length L1 is formed to be shorter than the second length L2 (L1<L2).

As described above, the length corresponds to the radial length. In detail, it may be defined as the maximum length in the radial direction from the center of the coupling hole 204. That is, the second wing 320b is formed to extend longer in the radial direction from the fixing part 202 than the first wing 310b.

In particular, the first wing 310b and the second wing 320b are formed to extend more radially outward than the pitch circle pc so as to cover the suction port 133. In this case, it may be understood that the second wing 320b extends further outward in the radial direction of the pitch circle pc than the first wing 310b.

In this case, it is assumed that the external conditions of the first wing 310b and the second wing 320b are the same except for the length. Accordingly, it can be understood that the second wing 320b formed longer than that of the first wing 310b is provided with lower rigidity. Accordingly, the second wing 320b may open the suction port 133 faster than the first wing 310b and close the suction port 133 later.

In addition, the intake valve 300b is provided with three second blades 320b and two first blades 310b. That is, as the suction valve 300b has more of the second blades 320b having relatively low rigidity, a large amount of refrigerant flow can be secured.

As shown in FIG. 16, the suction valve 300c includes a first wing 310c having a first width W1 and a second wing 320c having a second width W2. In addition, the first width W1 is formed larger than the second width W2 (W1>W2).

As described above, the width corresponds to the length in the circumferential direction. In detail, it may be defined as a length covering the circumference of the pitch circle (pc). That is, the first wing 310c is formed to cover a wider circumference of the pitch circle pc than the second wing 320c.

In particular, the first wing 310b and the second wing 320b are formed to be wider in the circumferential direction toward the outer side in the radial direction from the fixing part 202. In this case, it can be understood that the first wing 310c gradually widens in the circumferential direction at a larger ratio than the second wing 320c.

In this case, it is assumed that the external conditions of the first wing 310c and the second wing 320c are the same except for the width. Accordingly, it can be understood that the first wing 310c formed wider is provided with high rigidity compared to the second wing 320c. Accordingly, the first wing 310a may open the suction port 133 later than the second wing 320a and close the suction port 133 faster.

In FIGS. 14 to 16, the thickness, length, and width were respectively illustrated and described. However, such an embodiment may be selectively used together and is not limited to one.

In addition, as in the first and second embodiments, the number of blades and suction holes may be formed differently according to design. As described above, since a plurality of wings having different stiffnesses are provided, impact sound is generated at a time difference, thereby effectively reducing noise.

10: compressor 130: piston
133: suction hole 134: valve fastening member
200: suction valve 202: fixed part
210, 310: first wing 220, 320: second wing
pc: pitch line T: thickness (length in axial direction)
L: Length (radial length) W: Width or width (circumferential length)

Claims (20)

A cylinder forming a compression space;
A piston reciprocating in the axial direction to change the volume of the compression space and having a suction port for supplying a refrigerant to the compression space;
A suction valve disposed in front of the piston forming the compression space to open and close the suction port; And
A valve fastening member penetrating the suction valve and inserted into the front surface of the piston so as to fasten the suction valve to the piston,
In the suction valve,
A fixing part in close contact with the front surface of the piston by the valve fastening member; And
It includes a plurality of blades extending radially from the fixing part and deforming axially forward from the front surface of the piston to open the suction port,
In the plurality of wings,
First wing; And
A linear compressor comprising: a second blade formed with lower rigidity or low stiffness than the first blade. The method of claim 1,
In the suction port,
A linear compressor comprising a plurality of suction holes centered on an imaginary pitch circle formed on the front surface of the piston and spaced apart in a circumferential direction along the pitch circle. The method of claim 2,
In the plurality of suction holes,
A first suction hole; And
It includes a second suction hole and a third suction hole respectively formed on both sides of the circumferential direction of the first suction hole,
The first suction hole is a linear compressor, characterized in that disposed adjacent to the second suction hole in the circumferential direction than the third suction hole. The method of claim 3,
The first suction hole and the second suction hole are simultaneously opened and closed by any one of the first blade and the second blade,
And the third suction hole is opened and closed separately from the first suction hole and the second suction hole by the other one of the first blade and the second blade. The method of claim 1,
The second blade is a linear compressor, characterized in that formed to have a smaller thickness in the axial direction than the first blade. The method of claim 5,
In the suction valve,
And a step portion formed between the fixed portion and the first wing so that the first wing is formed thicker in the axial direction than the fixed portion. The method of claim 1,
The second blade is a linear compressor, characterized in that extending longer in the radial direction from the fixed part than the first blade. The method of claim 7,
The suction port includes a plurality of suction holes formed centered on a virtual pitch circle formed on the front surface of the piston,
The linear compressor, characterized in that the first blade and the second blade are formed to extend radially outwardly than the pitch circle so as to cover the plurality of suction holes. The method of claim 1,
The first blade is a linear compressor, characterized in that formed wider in the circumferential direction than the second blade. The method of claim 9,
The first blade and the second blade are formed to be gradually wider in the circumferential direction toward the outer side in the radial direction from the fixed part. The method of claim 1,
The suction port includes a plurality of suction holes formed centered on a virtual pitch circle formed on the front surface of the piston,
The linear compressor, characterized in that the first blade is formed to cover a circumference of the pitch circle wider than that of the second blade. The method of claim 1,
The second blade is a linear compressor, characterized in that the circumferential width or axial thickness is smaller or the radial length is formed longer than that of the first blade. The method of claim 1,
The linear compressor, characterized in that the first blade and the second blade are provided in different numbers. The method of claim 13,
The linear compressor, characterized in that the first blade and the second blade is provided in plurality, respectively. The method of claim 1,
The suction port includes suction holes formed in a plurality of pairs,
The linear compressor, characterized in that the first blade and the second blade open and close a pair of different suction holes, respectively. A cylinder forming a compression space;
A piston reciprocating in the axial direction to change the volume of the compression space;
A suction port formed in front of the piston in the axial direction to guide the refrigerant to the compression space; And
A suction valve coupled to the axial front surface of the piston and extending in a radial direction to open and close the suction port is included,
In the suction port,
It includes a plurality of suction holes arranged to be spaced apart in a circumferential direction along the pitch circle, centered on a virtual pitch circle formed on the front surface of the piston,
In the plurality of wings,
First wing; And
And a second blade having at least one of a width extending in a circumferential direction, a length extending in a radial direction, and a thickness extending in an axial direction different from the first blade with respect to the pitch circle Linear compressor. The method of claim 16,
Each of the first wing and the second wing is provided in plurality,
The first blade and the second blade are arranged alternately in a circumferential direction. The method of claim 16,
Each of the first wing and the second wing is provided in plurality,
The linear compressor, characterized in that the first blade and the second blade are provided in different numbers. The method of claim 16,
The suction valve further includes a fixing part that is in close contact with the front surface of the piston corresponding to the center of the pitch circle,
The plurality of wing portions, characterized in that the linear compressor, characterized in that extending so that the width in the circumferential direction widens radially outward from the fixed portion. The method of claim 16,
The second blade is a linear compressor, characterized in that a width extending in a circumferential direction or a thickness extending in an axial direction is smaller than that of the first blade, or a length extending in a radial direction is longer.

Images