KR20190030056A - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
KR20190030056A
KR20190030056A KR1020170117296A KR20170117296A KR20190030056A KR 20190030056 A KR20190030056 A KR 20190030056A KR 1020170117296 A KR1020170117296 A KR 1020170117296A KR 20170117296 A KR20170117296 A KR 20170117296A KR 20190030056 A KR20190030056 A KR 20190030056A
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KR
South Korea
Prior art keywords
spring
resonance spring
resonance
casing
piston
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KR1020170117296A
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Korean (ko)
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KR101981098B1 (en
Inventor
이종구
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엘지전자 주식회사
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Priority to KR1020170117296A priority Critical patent/KR101981098B1/en
Publication of KR20190030056A publication Critical patent/KR20190030056A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons

Abstract

The present invention relates to a linear compressor, comprising: a casing; A drive unit including a motor reciprocating in the casing and a stator for forming a movement of the motor by interaction with the motor; A compression chamber in which a compression chamber is formed in the casing and a piston which is coupled to the muffler and reciprocates inside the cylinder and compresses the fluid received in the cylinder; And a resonance spring positioned between the stator and the cover member for supporting the compression unit and forming a resonance motion of the piston, wherein the resonance spring has a constant effective number of turns per angle with respect to the center .

Description

[0001] LINEAR COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a linear compressor for compressing fluid by linear reciprocating motion of a vibrating body.

The compressor can be divided into a rotary type and a reciprocating type according to a method of compressing a refrigerant. Refers to a device that receives power from a power generating device such as a motor or turbine and compresses operating fluid such as air or refrigerant. Compressors are widely applied to industrial and household appliances, especially refrigeration cycle devices.

There are two types of compressors: a reciprocating compressor in which a compression chamber is formed between the piston and the cylinder and the piston reciprocates linearly to compress the fluid, a rotary compressor for compressing the fluid by eccentrically rotating rollers in the cylinder, And a scroll compressor in which a pair of scrolls is rotated to compress the fluid.

In recent years, the use of a linear compressor linear compressor using a linear reciprocating motion without using a crankshaft among reciprocating compressors has been increasing. The linear compressor has a merit that the efficiency of the compressor is improved and the structure is relatively simple since there is little mechanical loss in converting the rotational motion into the linear reciprocating motion.

In the linear compressor, a cylinder is disposed in a casing forming a closed space to form a compression chamber, and a piston covering the compression chamber reciprocates within the cylinder. In the linear compressor, the fluid in the closed space is sucked into the compression chamber in the process of positioning the piston at the bottom dead center (BDC), and the fluid in the compression chamber in the process of positioning the piston at the top dead center (TDC) The process of being compressed and discharged is repeated.

The linear compressor is provided with a compression unit and a drive unit, respectively, and the compression unit performs a process of compressing and discharging the refrigerant while resonating by the resonance spring through the motion generated in the drive unit.

In the linear compressor, the piston reciprocates at a high speed in the cylinder by the resonance spring while sucking the refrigerant into the casing through the suction pipe, and then is discharged from the compression space by the advancing movement of the piston and moves to the condenser through the discharge pipe A series of processes are repeatedly performed.

The conventional linear compressor generally includes a resonance spring composed of a general compressed coil having a circular cross section as shown in Patent Document 1 (Korean Patent Laid-Open Publication No. KR10-2016-0024217). In this case, a force such as a lateral force or a torsional moment is generated due to the expansion and contraction movement of the resonance spring, which hinders stable operation of the compressor. In addition, it is possible to lower the lateral force of the resonance spring by increasing the elastic modulus by disposing a plurality of resonance springs in parallel in the circumferential direction, but there is a limit, and friction loss and abrasion occur in a specific region of the cylinder during reciprocation of the piston . Accordingly, there is a need for a compressor that can stably drive by reducing the lateral force generated by the resonance spring when reciprocating the piston.

Korean Patent Publication No. KR10-2016-0024217

SUMMARY OF THE INVENTION It is an object of the present invention to provide a structure of a compressor capable of stably driving by reducing lateral force generated upon expansion and contraction of a resonance spring.

Another object of the present invention is to provide a structure of a linear compressor in which a resonance spring has a certain effective number of turns so as to secure rigidity in a direction of expansion and contraction and reduce lateral force.

Another object of the present invention is to provide a linear compressor capable of reducing the length of the resonance spring in the direction of expansion and contraction and reducing the number of resonance springs installed in the compressor through securing the rigidity of the resonance spring, Structure.

According to another aspect of the present invention, there is provided a linear compressor including: a casing; A drive unit including a motor reciprocating in the casing and a stator for forming a movement of the motor by interaction with the motor; A compression chamber in which a compression chamber is formed in the casing and a piston which is coupled to the muffler and reciprocates inside the cylinder and compresses the fluid received in the cylinder; And a resonance spring positioned between the stator and the cover member for supporting the compression unit and forming a resonance motion of the piston, wherein the resonance spring has a constant effective number of turns per angle with respect to the center So that the occurrence of lateral force can be reduced even when the resonance spring is compressed.

According to an example of the present invention, the resonance spring may have a rectangular cross section.

In addition, the resonance spring may have a circular cross section.

According to an example of the present invention, the resonance spring includes: a first portion formed at both end portions; And a second portion formed to be bent between the first portion and contacting the first portion at regular intervals.

At this time, the second portion may be formed to be bent a plurality of times.

According to an embodiment of the present invention, the resonance spring includes: a stator cover coupled to the stator; a first spring that supports a surface of the spring support member, respectively; And a second spring for supporting a space between the other surface of the spring support member and the cover member coupled to the inner rear end of the casing.

At this time, the center portions of the first spring and the second spring may be formed in the same line.

In addition, the first spring and the second spring may be disposed at a predetermined interval with respect to the center of the piston.

According to an embodiment of the present invention, the spring support member may include a resonance spring guide member protruding from one surface of the spring support member and extending along the longitudinal direction of the resonance spring to restrict a lateral movement of the resonance spring .

According to an embodiment of the present invention, the resonance spring guide member may include one end connected to the inner side surface of the casing and extending toward the resonance spring and then bent to extend along the longitudinal direction of the resonance spring .

At this time, the resonance spring guide member may surround the outer shape of the resonance spring, and may be separated from the resonance spring by a predetermined distance.

By reducing the lateral force of the resonance spring, the linear compressor having the above-described structure can reduce friction and wear with respect to a specific portion that may occur during driving of the compressor, thereby enabling stable driving.

In addition, the number of effective turns per angle of the resonance spring is set to be constant so as to have a high rigidity in the longitudinal direction with respect to the same size, thereby ensuring rigidity in the direction of expansion and contraction as well as securing of lateral rigidity.

Further, by reducing the number of the resonance springs mounted on the compressor through the resonance spring having a structure capable of ensuring sufficient elongation and lateral rigidity in comparison with the same radius and length, the internal space of the compressor can be easily secured.

1 is a sectional view showing a state of a linear compressor according to the present invention;
2 is a conceptual view showing an example of a longitudinal cross section of a resonance spring;
3 (a) and 3 (b) are conceptual views showing longitudinal sections of a resonance spring according to the present invention.
4A is a cross-sectional view of a linear compressor showing another embodiment of a linear compressor.
4B is a perspective view of a spring supporting member;
5 is a cross-sectional view showing still another embodiment of a linear compressor;

Hereinafter, a linear compressor according to the present invention will be described in detail with reference to the drawings.

As used herein, the singular forms "a", "an" and "the" include plural referents unless the context clearly dictates otherwise.

In the following description of the embodiments of the present invention, a detailed description of related arts will be omitted when it is determined that the gist of the embodiments disclosed herein may be obscured.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory and are intended to provide further explanation of the invention as claimed. It should be understood that it includes water and alternatives.

1 is a view showing a state of a linear compressor according to the present invention.

The linear compressor 100 includes a casing 110, a frame 120, a drive unit 130, and a compression unit 140.

A frame 120 is installed in the inner space 101 of the casing 110 forming the closed space. A driving unit 130 is coupled to the frame 120 and the driving unit 130 is coupled to a compression unit 140 for sucking and compressing the refrigerant. The compression unit 140 is coupled to and supported by the frame 120 together with the drive unit 130.

The casing 110 includes a shell 111 having both ends opened and formed into a substantially cylindrical shape in a substantially transverse direction, a first shell cover 112 coupled to the rear side of the shell 111, and a second shell cover 112 coupled to the front side, And a shell cover 113. The first shell cover 112 is disposed on the right side of the shell 111 and the second shell cover 113 is disposed on the left side of the shell 111 Can be combined. In addition, the first shell cover 112 and the second shell cover 113 may form a part of the shell 111.

The inner diameter of the casing 110 may be variously formed according to the size of the drive unit 130. However, in the linear compressor 100 according to the present embodiment, the oil bearing is eliminated, The inner diameter of the casing 110 is minimized so that the flange portion 122 of the frame 120 to be described later is not in contact with the inner circumferential surface of the casing 110 because the oil is not required to be filled in the space 101 As shown in FIG.

The first shell cover 112 is coupled to the rear side of the casing 110. A suction port 114 is formed in the first shell cover 112 and a suction pipe SP can be inserted and coupled.

The second shell cover 113 is formed with a discharge port 115 through which the refrigerant is discharged to the outside from the discharge space 102 and a discharge pipe DP can be connected to the outside of the discharge port 115.

The frame 120 may be connected to and supported by the other end of the support spring 150, which is positioned such that one end of the frame 120 is fixed to the casing 110. As shown in FIG. 1, the support spring 150 may be formed of a leaf spring.

The driving unit 130 may generate a reciprocating motion of the linear compressor 100 according to the present invention and may include a stator 131 and a mover 132. The stator 131 may be coupled to the frame 120. The stator 131 may include an outer stator 131a disposed to surround the compression unit 140 and an inner stator 131b spaced to the inside of the outer stator 131a and surrounding the compression unit 140 . The muver 132 may be positioned between the outer stator 131a and the inner stator 131b.

A winding coil 133 may be mounted on the outer stator 131a, and the permanent magnet may be provided on the mover 132. When a current is applied to the drive unit 130, a flux can be formed in the stator 131 by the winding coil 133, and the interaction between the magnetic flux formed by the application of the current and the magnetic flux formed by the permanent magnet The movement of the mover 132 can be formed.

The compression unit 140 is configured to suck and compress and discharge the refrigerant in the suction space 101. The compression unit 140 can be located in the center of the casing 110 to the inside of the inner stator 131b and includes a cylinder 141 and a piston 142. The cylinder 141 can be supported by the frame 120 to form the compression chamber P. The cylinder 141 may have a cylindrical shape with one end thereof opened. A discharge valve 141a and a discharge cover 143 may be mounted on the other end of the cylinder 141. [

A discharge space 102 may be formed between the discharge valve 141a and the discharge cover 143. That is, the discharge valve 141a can form a space in which the compression chamber P and the discharge cover 143 are separated from each other.

The plurality of discharge covers 143 may be overlapped with each other, and a plurality of discharge spaces 102 may be formed. A discharge tube 144 extending to communicate the discharge port 115 and the discharge space 102 with each other may be provided in the casing 110.

The piston 142 is inserted into one open end of the cylinder 141 to seal the compression chamber P. The piston 142 is connected to the above-described mover 132 and can reciprocate with the mover 132. The inner stator 131b and the cylinder 141 may be positioned between the mover 132 and the piston 142 and the mover 132 and the piston 142 may be arranged to bypass the cylinder 141 and the inner stator 131b And can be coupled to each other by a separate connecting member 145 formed.

The piston 142 is formed with a suction port 142a that hermetically seals the compression chamber P and penetrates one end thereof. The refrigerant in the suction space 101 flows through the inner space of the piston 142 in this embodiment and is sucked into the compression chamber P between the piston 142 and the cylinder 141 through the suction port 142a, . A suction valve (not shown) that opens and closes the suction port 142a may be mounted on the end surface of the piston 142 adjacent to the compression chamber P. The suction valve (not shown) can be operated by elastic deformation. That is, the suction valve (not shown) may be elastically deformed to open the suction port 142a by the pressure of the refrigerant flowing through the suction port 142a toward the compression chamber P.

The linear compressor (100) according to the present invention may further include a resonance spring (160). The resonance spring 160 functions to amplify the vibration realized by the reciprocating movement of the mover 132 and the piston 142 and effectively compress the refrigerant. The spring supporting member 146 may be coupled to the connecting member 145 connecting the piston 132 and the piston 142 to reciprocate integrally.

One end of the resonance spring 160 according to the present invention is fixed to the spring support member 146 and the other end of the resonance spring 160 can be fixedly coupled to the stator cover 147 or the cover member 148 . As shown in Fig. 1, a plurality of resonance springs 160 may be disposed on both sides of the spring support member 146, with the spring support member 146 therebetween.

The resonance spring 160 includes a first spring 161 that supports one side of the stator cover 147 and one side of the spring support member 146 and a second spring 161 that supports the other side of the spring support member 146, And a second spring 162 for supporting a space between the cover member 148 and the inner rear end of the cover member 148.

The first spring 161 and the second spring 162 may be formed so that the center portions thereof are formed on the same line. Similarly, the first spring 161 and the second spring 162 may be composed of a plurality of at least one or more, and may be disposed at regular intervals with respect to the center of the piston 142. For example, the first spring 161 and the second spring 162 may be disposed at intervals of 120 degrees with respect to the center of the piston 142.

The first spring 161 and the second spring 162 constituting the resonance spring 160 have first portions 161a and 162a formed at both ends thereof and first and second portions 161b and 162b formed between the first portions 161a and 162a And second portions 161b and 162b formed to be bent.

The first portions 161a and 162a are formed at both ends of the resonance spring 160 in contact with the stator cover 147 and the cover member 148 via the spring support member 146, The second portions 161b and 162b are portions formed to be bent between the first portions 161a and 162a and may be formed to be bent a plurality of times.

The first portions 161a and 162a and the second portions 161b and 162b may be formed to be in contact with each other at regular intervals along the circumferential direction.

When the piston 142 vibrates with respect to the cylinder 141, the resonance spring 160 vibrates with a predetermined spring constant to enable the resonance of the compression unit 140 to be realized.

The resonance spring 160 according to the present invention is configured to have a certain effective number of turns based on the center, and when the resonance spring 160 is sectioned in parallel to the central axis, the number of effective turns formed on both sides is the same . A detailed description thereof will be described later.

The linear compressor 100 is operated as follows.

First, when a current is applied to the drive unit 130, a magnetic flux can be formed in the stator 131. By the electromagnetic force generated by the magnetic fluxes formed in the stator 131, the movers 132 having the permanent magnets can be linearly reciprocated.

During reciprocation of the mover 132, the piston 142 connected to the mover 132 may be reciprocated. The piston 142 reciprocating within the cylinder 141 repeats the movement of increasing and decreasing the volume of the compression chamber P.

When the piston 142 is moved while increasing the volume of the compression chamber P, the pressure inside the compression chamber P decreases. Accordingly, the suction valve (not shown) mounted on the piston 142 is opened, and the refrigerant staying in the suction space 101 can be sucked into the compression chamber P. [ This suction stroke is continued until the piston 142 reaches the bottom dead center (BDC) by maximally increasing the volume of the compression chamber P.

The piston 142, which has reached the bottom dead center, performs the compression stroke while reducing the volume of the compression chamber P. The compression stroke is performed while moving the piston 142 to a top dead center (TDC), which reduces the volume of the compression chamber P to a minimum. At the time of the compression stroke, the pressure inside the compression chamber (P) increases, and the refrigerant sucked can be compressed. When the pressure in the compression chamber P reaches a predetermined pressure, the discharge valve 141a mounted on the cylinder 141 is opened and the refrigerant is discharged into the discharge space 102. [

The refrigerant in the suction space 101 flowing into the suction port 114 is sucked into the compression chamber P and compressed so that the discharge space 102, the discharge tube 144, And the discharge port 115 to the outside of the compressor. During the reciprocating motion of the piston 142, the resonance spring 160 is compressed and tensioned according to the number of vibrations of the piston 142, so that a resonance phenomenon can be caused and the compressor operation can be performed efficiently compared with the applied electric energy.

On the other hand, in the linear compressor 100, oil is separately used for lubrication and cooling between the fixed body including the cylinder 141 and the stator 131 and the vibrator including the muffler 132 and the piston 142 Oil-less type. In this oilless type linear compressor 100, a gas bearing may be formed for lubrication and cooling of the friction surface between the cylinder 141 and the piston 142. That is, a part of the refrigerant is supplied from the discharge space 102 to the outer peripheral surface of the piston 142 by the bearing passage 121 formed in the frame 120, so that the gas bearing film can be formed.

FIG. 2 is a view showing an example of a longitudinal section of a resonance spring, and FIGS. 3 (a) and 3 (b) are longitudinal sectional views of a resonance spring according to the present invention.

As shown in FIG. 2, the resonance spring 160 is configured so that the effective turns (effective turns) of the left and right compression coils are different from each other when the longitudinal cross section of the resonance spring 160 is viewed. The compression coil includes a valid turn serving to provide a uniform elastic force in the longitudinal direction and a right upper end and a lower end of the compression coil that does not serve to maintain uniform longitudinal stiffness. If the number of effective turns of the compression coils on the left and right sides is different from each other, the side force of the resonance spring 160 is relatively larger, so that it may act as a load of the bearing or wear due to friction with the compression unit due to lateral movement .

Thus, it is required that the resonance spring has the same effective number of turns to ensure not only the rigidity in the direction of expansion and contraction but also the reduction of the side force, thereby blocking the resonance spring 160 from coming into contact with the compression unit.

The resonance spring 160 according to the present invention is configured to have a constant effective number of turns per angle with respect to the center in order to reduce a side force.

Here, the side force refers to a force generated in a direction perpendicular to the axial direction with respect to the central axis of the resonance spring 160 when the resonance spring 160 is expanded or contracted. The side force is generated when the plate (not shown) supporting the resonance spring 160 is not in a horizontal state. As a result, a moment is generated in the plate (not shown) do. As a result of this inclination, a component force F in a direction perpendicular to the axial direction is generated in the resonance spring 160. This component force can be defined as a lateral force. That is, the resonance spring 160 generates not only the force in the direction of expansion and contraction but also the lateral force generated in the direction perpendicular to the expansion and contraction direction.

As shown in FIGS. 3A and 3B, the resonance spring 160 according to the present invention is configured such that the effective windings are formed at regular intervals and the resonance spring 160, which is formed on the left side and the right side, Since the number of effective turns of the spring 160 is constant, the lateral force generated according to the direction of expansion and contraction can be reduced.

At both ends in the axial direction of the resonance spring 160, a tight contact portion is formed to be in contact with the stator cover or the spring support member, respectively, and an effective turn portion is formed between the tight contact portions. The effective turn portion is formed to have a constant wave cross-sectional shape, and the effective turn portion may be configured to maintain a state in which a part of the adjacent wire rods in the axial direction is in contact with each other. The effective turn portion has at least one upper pitch point and a lower pitch point per turn per turn. The effective turn portion may have a wave shape having a valley (an upper pitch point) positioned to bend toward the cover member 148 and a floor (a lower pitch point) positioned to bend toward the stator cover 147. Further, the upper pitch point and the lower pitch point of the neighboring wire rods of the valid turn portion may be maintained in contact with each other.

The resonance spring 160 according to the present invention is capable of securing sufficient longitudinal strength over the same length as compared with the general resonance spring 160 and reduces the generation of the lateral force. Therefore, the resonance spring 160 Can be reduced and the length thereof can be shortened, so that the space occupied in the compressor can be reduced and the compressor can be made more compact.

The resonance spring 160 according to the present invention is formed such that the effective windings are spaced apart from each other at regular angular intervals based on the center of the effective windings rather than having the same interval between the windings of the compression coils. The number of effective turns per angle is made equal.

For example, the resonance spring 160 may refer to a wave spring and may have a predetermined effective turn number and rigidity regardless of its radial directionality, and may be linearly or surface-contacted at constant angular intervals.

3 (a) and 3 (b), the resonance spring 160 according to the present invention has a circular cross section or a rectangular cross section when the resonance spring 160 is cut in the longitudinal direction .

In particular, in the case of forming a rectangular cross-section, the axial contact between the windings is made at a constant angular interval with respect to the center, so that the axial vibration of the resonance spring can be more stably performed despite the drive of the compressor .

Since the side force of the resonance spring 160 acts as a load of a bearing (not shown) positioned inside the compressor, the wear of the compressor due to friction with the compression unit adversely affects the reliability of the compressor. Thus, the present invention is configured to reduce the lateral force while ensuring sufficient rigidity of the resonance spring 160 in the expansion and contraction direction.

4A is a sectional view of a linear compressor 200 showing another embodiment of the present invention, and Fig. 4B is a perspective view showing a spring support member 246. Fig.

The linear compressor 200 according to the present embodiment may further include a casing 210, a frame 220, a drive unit 230, a compression unit 240 and a resonance spring 260.

The resonance spring 260 functions to amplify the vibration realized by the reciprocating motion of the mover 232 and the piston 242 to effectively perform compression of the refrigerant and to connect the mover 232 and the piston 242 The spring member 246 is coupled to the connecting member 245 so that the spring member 246 can reciprocate integrally.

The linear compressor 200 according to the present embodiment is provided with a resonance spring guide member 260 which is capable of preventing lateral movement (movement toward the center direction) of the resonance spring 260 and restricting friction with the compression unit 240, (249).

The resonance spring guide member 249 may be formed so as to protrude from the front and rear surfaces of the spring support member 246 toward the stator cover 247 and the cover member 248, respectively. The maximum compression distance of the resonance spring guide member 249 is considered so that the resonance spring guide member 249 does not collide with the stator cover 247 and the cover member 248 when the resonance spring 260 is compressed. You will be able to set the length.

The resonance spring guide member 249 may be configured to accommodate the resonance spring 260 so as to correspond to the external shape of the resonance spring 260. Accordingly, the resonance spring 260 is spaced apart from the adjacent resonance spring 260 by a predetermined distance.

4B, the resonance spring supporter 246b protrudes from the resonance spring guide member 249, and the resonance spring supporter 246b may be formed so that the end of the resonance spring 260 is inserted. The resonance spring guide member 249 may be formed to protrude from the inside of the resonance spring support member 246b on one side of the resonance spring guide member 249. [ Although not shown in the figure, a plurality of resonance spring guide members 249 are formed on both sides of the spring support member 246 so as to correspond to the number of the resonance springs.

The resonance spring guide member 249 may be formed on the inner surface of the casing 210 so as to limit the lateral movement of the resonance spring 260.

5 is a cross-sectional view showing another embodiment of the linear compressor 300. As shown in Fig.

The linear compressor 300 has a structure including the casing 310, the frame 320, the drive unit 330, the compression unit 340, and the resonance spring 360, As described above.

However, the linear compressor 300 according to the present invention may be configured so that one resonance spring 360 having a large diameter is disposed between the stator cover 347 and the cover member 348 . At this time, the resonance spring 360 is configured so as to have a constant effective number of turns per angle with respect to the center in order to reduce the side force. When the longitudinal cross section of the resonance spring 360 is viewed, And the number of effective turns of the compression coil on the right side is the same as that described above. Due to the structural characteristics of the resonance spring 360, it is also possible to implement a compressor including one resonance spring 360 instead of a plurality of resonance springs 360, since generation of a lateral force can be restricted even when the compressor is driven.

It is to be understood that the present invention is not limited to the above-described embodiments, and various modifications may be made without departing from the scope of the present invention as set forth in the following claims It will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the scope of the present invention.

100: Linear compressor 110: Casing
111: shell 112: first shell cover
113: second shell cover 115: discharge port
120: frame 130: drive unit
140: compression unit 148: cover member
147: stator cover 160: resonance spring
245: connecting member 246: spring supporting member
249: Resonance spring guide member

Claims (14)

  1. Casing;
    A drive unit including a motor reciprocating in the casing and a stator for forming a movement of the motor by interaction with the motor;
    A compression chamber in which a compression chamber is formed in the casing and a piston which is coupled to the muffler and reciprocates inside the cylinder and compresses the fluid received in the cylinder; And
    And a resonance spring that forms a resonance motion of the piston,
    Wherein the resonance spring comprises a compression coil spring having the same number of effective turns on both sides of the center in the axial direction.
  2. The method according to claim 1,
    The resonance spring has tight contact portions on both ends in the axial direction, and effective turn portions are formed between the tight contact portions,
    Wherein the effective turn portion has a wave cross-sectional shape.
  3. 3. The method of claim 2,
    Wherein the effective turn portion is formed so as to maintain a state in which a part of the wire members neighboring in the axial direction are in contact with each other.
  4. The method of claim 3,
    Wherein the effective turn portion is formed so as to maintain a state in which a part of the wire members neighboring in the axial direction are in contact with each other.
  5. 5. The method of claim 4,
    Wherein the effective turn portion is formed to have at least one upper pitch point and a lower pitch point per turn,
    And an upper pitch point and a lower pitch point of the adjacent wire rods are formed to be in contact with each other.
  6. The method according to claim 1,
    Wherein the resonance spring has a rectangular cross section.
  7. The method according to claim 1,
    Wherein the resonance spring has a circular cross-section.
  8. The method according to claim 1,
    The resonance spring includes:
    A first portion formed at both end portions; And
    And a second portion formed to be bent between the first portion and the second portion.
  9. 9. The method of claim 8,
    And the second portion is formed so as to bend a plurality of times with respect to one turn.
  10. The method according to claim 1,
    The resonance spring includes:
    A stator cover coupled to the stator, and a first spring for supporting one surface of a spring support member fixed to one side of the compression unit, respectively; And
    And a second spring for supporting between the other surface of the spring support member and the cover member engaged with the inner rear end of the casing.
  11. 11. The method of claim 10,
    And the center portions of the first spring and the second spring are formed on the same line.
  12. The method according to claim 1,
    And a resonance spring guide member protruding from one surface of the spring support member fixed to one side of the compression unit and extending along the longitudinal direction of the resonance spring to limit the movement of the resonance spring in the lateral direction Linear compressors.
  13. 13. The method of claim 12,
    Wherein one end of the resonance spring guide member is coupled to an inner surface of the casing and extends toward the resonance spring and then is bent so as to extend along the longitudinal direction of the resonance spring.
  14. 13. The method of claim 12,
    Wherein the resonance spring guide member surrounds the outer shape of the resonance spring and is separated from the resonance spring by a predetermined distance.
KR1020170117296A 2017-09-13 2017-09-13 Linear compressor KR101981098B1 (en)

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KR101981098B1 KR101981098B1 (en) 2019-05-22

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20020091410A (en) * 2001-05-30 2002-12-06 주식회사 엘지이아이 Inner stator assembly fixing structure for reciprocal compressor
JP2003184745A (en) * 2001-12-12 2003-07-03 Matsushita Electric Ind Co Ltd Linear compressor
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20020091410A (en) * 2001-05-30 2002-12-06 주식회사 엘지이아이 Inner stator assembly fixing structure for reciprocal compressor
JP2003184745A (en) * 2001-12-12 2003-07-03 Matsushita Electric Ind Co Ltd Linear compressor
KR20160024217A (en) 2014-08-25 2016-03-04 엘지전자 주식회사 Linear compressor

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