KR100848914B1 - Linear compressor - Google Patents

Abstract

A linear compressor is provided to simplify a manufacturing process by modifying the shape of a bearing. A linear compressor comprises a piston(116), a first bearing(160), and a second bearing(170). The piston reciprocates in a cylinder(111) to compress refrigerant in a compression chamber. The first bearing is installed at the cylinder to support the piston. The second bearing is installed at a compressor body to support the piston. An oil inlet port is provided at the second bearing to supply oil to the second bearing. An oil outlet port is provided at the second bearing to discharge oil from the second bearing. The oil outlet port is positioned above the center of the second bearing to preserve the oil supplied to the second bearing. A groove is formed in a contact surface of the second bearing and the piston in order to facilitate supply of oil.

Description

Linear compressor

1 is a cross-sectional view of a linear compressor according to the prior art

Figure 2 is a cross-sectional view showing the main portion of the linear compressor according to the prior art

3 is a configuration diagram showing a structure in which a piston of a linear compressor according to the prior art is supported by a bearing;

4 is a cross-sectional view showing a linear compression unit of the linear compressor according to the present invention.

Figure 5 is a schematic view showing a simplified structure for supporting both ends of the piston of the linear compressor according to the present invention applying the bonding means

6 is a cross-sectional view showing a first bearing shape of the linear compressor according to the present invention.

7 is a cross-sectional view showing a second bearing configuration of the linear compressor according to the present invention.

8 is a flowchart illustrating a method of manufacturing a linear compressor according to the present invention to which an adhesive means is applied.

9 is a flow chart showing a manufacturing method according to another embodiment of the linear compressor according to the present invention to which the adhesive means is applied.

10 is a configuration diagram briefly showing the support structure of both ends of the piston of the linear compressor according to the present invention to which the position correction member is applied.

11 is a flow chart showing a manufacturing method of the linear compressor according to the present invention to which the position correction member is applied.

12 is a flow chart showing a manufacturing method according to another embodiment of the linear compressor according to the present invention to which the position correction member is applied.

** Description of symbols for the main parts of the drawing **

110: linear compression section 112: cylinder frame

111 cylinder 114 back cover

115: suction passage 116: piston

117: discharge valve assembly 118: sealing member

121: outer stator 122: inner stator

124: coil 125: permanent magnet

126: permanent magnet frame 127: stator cover

160: first bearing 170: second bearing

172: home 174: oil inlet

176: oil discharge outlet C: center line

E: Bonding means G: Position correction member

The present invention relates to a linear compressor, and more particularly, to a linear compressor capable of increasing the compression efficiency and ensuring the reliability of the system.

In general, a linear compressor is a device that sucks and compresses a refrigerant and discharges it while linearly reciprocating a piston inside a cylinder by using a linear driving force of a linear motor.

1 is a cross-sectional view of a linear compressor according to the prior art, Figure 2 is a cross-sectional view showing the main portion of the linear compressor according to the prior art, Figure 3 shows a structure in which the piston of the linear compressor according to the prior art is supported by a bearing It is a block diagram.

As shown in FIG. 1, the linear compressor according to the related art is vibrated by a shell 2 containing oil O and a damper 3 installed inside the shell 2. And a linear compression unit 10 for compressing and discharging the refrigerant after inhaling the refrigerant.

In the shell 2, a suction pipe 4 through which the refrigerant is sucked and a discharge pipe 5 connected by the linear compression unit 10 are disposed to penetrate the shell 2.

The linear compression unit 10 is arranged such that the cylinder frame 12 with the cylinder 11, the back cover 14 with the refrigerant suction path 13, and the linear reciprocating inside the cylinder 11. And a piston (16) having a suction passage (15) formed therein so as to suck refrigerant inside, a linear motor (20) for linearly reciprocating the piston (16), and installed to open and close the front end of the cylinder (11). It comprises a discharge valve assembly 17 to which the pipe 5 is connected.

The linear motor 20 largely consists of a stator and a mover. The stator includes an outer stator 21, an inner stator 22, a bobbin 23 provided with the outer stator 21, and a coil 24 wound around the bobbin 23 to form a magnetic field. . The mover is composed of a permanent magnet 25 that is linearly moved by the magnetic force formed in the coil 24, and a permanent magnet frame 26 to which the permanent magnet 25 is fixed.

On the other hand, the cylinder frame 12 is located in front of the linear motor 20, the stator cover 27 is fixed to the rear of the linear motor 20, the outer stator 21 is fixed. The cylinder frame 12 and the stator cover 27 are fastened axially by the bolt 30 and the nut 31 so that the compressive force in the axial direction is applied to the outer stator 21.

The cylinder frame 12 is formed with a first through hole 28 into which the bolt 30 is inserted at a position spaced a predetermined angle along the circumferential direction. In addition, the stator cover 27 is formed with a second through hole 29 corresponding to the through hole and into which the bolt 30 is inserted.

In addition, the lower side of the linear compression unit 10, the lubrication / cooling of the cylinder 11 and the piston 16, to the shell 2 by using the force that the linear compression unit 10 vibrates. Oil supply means 33 for supplying the contained oil (O) to the inside of the linear compression unit 10 is provided.

The oil supply means 33 includes an oil cylinder 34 fixedly mounted to the lower side of the linear motor 20, an oil piston 35 disposed in the oil cylinder 34 so as to be linearly reciprocated, and the oil. It is composed of first and second oil springs 36 and 37 disposed inside the oil cylinder 34 so as to elastically support the piston 35.

In addition, the linear compression unit 10 is provided with an oil suction passage 38 and an oil discharge passage 39 connected to the oil cylinder 34 to allow the oil O to pass therethrough.

The oil cylinder 34 has an oil suction hole 40 formed at one side to suck the oil inside the shell 2, and an oil discharge hole 41 formed at the other side thereof to communicate with the oil suction flow path 38. do.

An oil suction cover 42 is installed between the oil cylinder 34 and the stator cover 27 to shield a part of the oil suction hole 40 and to support an end of the second oil spring 37. . The cylinder frame 12 is equipped with an oil discharge cover 43 for forming an oil passage 44 between the cylinder frame 12.

The oil piston 35 is inserted into the oil cylinder 34, and an oil flow passage 45 is formed therein. An oil suction valve 46 supported by the first oil spring 36 is mounted on the outlet side of the oil passage 45 of the oil piston 35. In addition, an oil discharge valve 47 is mounted in the oil discharge hole 41 of the oil cylinder 34.

Referring to FIG. 2, in detail, a portion in which a refrigerant gas is compressed in a linear compressor according to the related art is formed, and a compression chamber P in which a refrigerant gas is compressed is formed in the cylinder 11.

In addition, the piston 16 linearly reciprocates in the cylinder 11 to compress the refrigerant gas. In addition, the discharge valve assembly 17 is installed at one side of the cylinder 11 to discharge the refrigerant gas compressed in the compression chamber P to the outside.

At this time, the suction valve 54 is provided at one end of the piston 16 to open and close the flow of the refrigerant sucked into the compression chamber (P).

Here, the piston 16 is connected to one end of the cylindrical piston body 16a and the piston body 16a through which the refrigerant gas can flow, and a plurality of suction flow paths to allow the refrigerant gas to flow therein ( 52 is formed of a cylindrical piston head (16b) formed.

The discharge valve assembly 17 includes inner and outer discharge covers 17a and 17b installed to cover one end of the cylinder 11. A hemispherical discharge valve 17c is provided inside the inner discharge cover 17a to open and close the compression chamber P. On the other hand, the discharge valve 17c is installed to be elastically supported by a valve spring 17d installed on the inner discharge cover 17a.

Here, the suction valve 54 has a thin plate shape provided at one end of the piston 16 to open and close the suction flow path 52 of the piston. The suction valve 54 is bolted to the piston head 16b at the center thereof, and is bent in accordance with the refrigerant gas pressure of the compression chamber P based on the fixed portion. Open).

Accordingly, while the piston 16 linearly reciprocates within the cylinder 11, the refrigerant gas is sucked into the compression chamber P formed between the piston 16 and the cylinder 11, compressed, and then discharged. The process is repeated.

Specifically, as the piston 16 moves from the top dead center A to the bottom dead center C, the pressure in the compression chamber P is relatively low. Therefore, in the state where the discharge valve 17c is blocking the compression chamber P, the suction valve 54 is bent, whereby the suction flow path 52 is opened, and refrigerant gas is supplied to the compression chamber P. Flows into.

As the piston 16 moves from the bottom dead center C to the top dead center A, the pressure in the compression chamber P becomes relatively high. Therefore, in the state where the discharge valve 17c is blocking the compression chamber P, the suction valve 54 closes the suction flow path 52, and the refrigerant gas is compressed in the compression chamber P. . At this time, when the piston 16 reaches the top dead center (A), the discharge valve 17c is opened to discharge the refrigerant gas compressed in the compression chamber (P).

Meanwhile, the linear compressor according to the prior art has a structure in which two bearings support the piston 16 for reciprocating motion, as shown in FIG. 3. That is, the first bearing 60 provided in front of the piston 16 and the second bearing 70 provided slightly behind the piston 16 support the piston 16.

Here, the piston 16 reciprocates while receiving force and moment by its own weight or linear motor 20 and an elastic member. The force and the moment are absorbed by the first bearing 60 and the second bearing 70, whereby the piston 16 can move straight reciprocating straight without swinging.

By the way, based on the center of gravity of the piston 16, both the first bearing 60 and the second bearing 70 is located on one side, the distance between the first bearing 60 and the second bearing 70 Short is a problem that does not effectively support the force and moment acting on the piston (16).

The frictional loss generated on the surfaces of the first bearing 60 and the second bearing 70 greatly affects the efficiency of the linear compressor. As described above, the first bearing 60 and the second bearing 70 have one side. When gathered, the force to be supported by the two bearings 60 and 70 is large, and the friction loss accordingly becomes large. This, in turn, leads to reduced compression efficiency and lower reliability throughout the linear compressor.

In addition, disposing the first bearing 60 and the second bearing 70 at both ends of the piston 16 is not implemented until now due to the difficulty of assembly.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a linear compressor capable of increasing the compression efficiency and ensuring the reliability of the system.

In order to achieve the above object, the present invention is a reciprocating motion in the cylinder, the piston for compressing the refrigerant in the compression chamber, the compression chamber side is provided on the basis of the center of gravity of the piston, the compression chamber side shear is inclined It is provided with a linear compressor comprising a first cylinder for supporting the piston made of a non-cylindrical cylinder, and a second bearing for supporting the piston, provided on the opposite side of the compression chamber based on the center of gravity of the piston.

The second bearing may be provided with an oil inlet for supplying oil to the second bearing, and an oil discharge port for discharging oil from the second bearing.

Here, the oil discharge port is preferably provided above the center of the second bearing in order to preserve the oil supplied to the second bearing.

In addition, a groove for smoothly supplying oil may be further provided on a surface of the second bearing in contact with the piston.

On the other hand, the linear compressor according to the present invention is provided between the piston and the cylinder, and further includes a sealing member for preventing the oil supplied to the first bearing from leaking.

The sealing member is preferably made integral with the piston.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. However, the present invention is not limited to the embodiments described herein and may be embodied in other forms. Rather, the embodiments introduced herein are provided so that the disclosure may be made thorough and complete, and to fully convey the spirit of the present invention to those skilled in the art. Like numbers refer to like elements throughout.

4 is a cross-sectional view showing a linear compression unit of the linear compressor according to the present invention.

Referring to FIG. 4, the linear compressor according to the present invention reciprocates inside the cylinder 111, compresses a refrigerant in the compression chamber P (see FIG. 2), and the piston 116. It is provided on the compression chamber (P, see Fig. 2) side with respect to the center of gravity, the front end of the compression chamber (P, see Fig. 2) is made of a cylindrical shape without an inclined portion (S) to support the piston 116 A first bearing 160 and a second bearing 170 provided on an opposite side of the compression chamber P (see FIG. 2) based on the center of gravity of the piston 116 to support the piston 116. It is configured by.

The cylinder 111 is provided in the linear compression unit 110 inside the shell 2 (see FIG. 1) forming an external shape of the linear compressor. The cylinder frame 112 for supporting the cylinder 111 is provided at the front end of the linear compression unit 110. In addition, a rear cover 114 is formed at the rear end of the linear compression unit 110 to form the body of the linear compression unit 110 together with the cylinder frame 112.

A ring-shaped inner stator 122 having a plurality of laminations stacked in a circumferential direction is provided around the cylinder 111 so as to be fixed to an outer circumferential surface of the cylinder 111. In addition, the outer stator 122 is provided with a ring-shaped outer stator 121 in which a plurality of laminations are also stacked in the circumferential direction together with the coil 124 wound in the circumferential direction.

In the space between the inner stator 122 and the outer stator 121 is provided with a permanent magnet 125 that linearly reciprocates by mutual electromagnetic force between the inner stator 122 and the outer stator 121.

At this time, one end of the inner stator 122 is supported by the cylinder frame 112, and is fixed by a fixing ring (not shown) on the outer circumferential surface of the cylinder 111. One end of the outer stator 121 is also supported by the cylinder frame 112, and the other end of the outer stator 121 is supported by the stator cover 127. On the other hand, the stator cover 127 is assembled and fixed to the cylinder frame 112 with a bolt. The permanent magnet 125 is installed to be connected to the other end of the piston 116 by the permanent magnet frame 126.

When the current is supplied to the outer stator 121, the piston 116 moves to the cylinder as the permanent magnet 125 linearly reciprocates by mutual electromagnetic force between the inner stator 122 and the outer stator 121. 111) Linear reciprocating motion inside.

Here, the refrigerant is introduced into the compression chamber (P, see Fig. 2) through the suction passage 115 formed in the piston 116, the piston 116 reciprocating the inside of the cylinder 111 to the compression chamber (P, see FIG. 2) The refrigerant inside is compressed. In addition, the compressed refrigerant exits to the outside of the compression chamber P (see FIG. 2) through the discharge valve assembly 117 installed in front of the piston 116.

Meanwhile, the linear compressor according to the present invention is provided at the compression chamber P (see FIG. 2) on the basis of the center of gravity of the piston 116, and the front end of the compression chamber P (see FIG. 2) is inclined. It is formed on the opposite side of the compression chamber (P, see Fig. 2) on the basis of the center of gravity of the piston 116 and the first bearing 160 to support the piston 116 made of a cylindrical portion (S), And a second bearing 170 supporting the piston 116.

As described above, the piston 116 reciprocates while receiving a force and a moment by its own weight, a motor, a spring, or the like. The first bearing 160 and the second bearing 170 absorb the force and moment acting on the piston 116 in this way, so that the piston 116 can move straight without swinging in the cylinder 111. Play a supportive role.

As in the related art, when both the first bearing 160 and the second bearing 170 are located at one side based on the center of gravity of the piston 116, the distance between both bearings 160 and 170 is short, so that the piston 116 It does not effectively support the forces and moments acting on them. As a result, the force that the first bearing 160 and the second bearing 170 need to support increases, and thus the friction loss increases.

However, as described above, when the first bearing 160 and the second bearing 170 are disposed opposite to each other based on the center of gravity of the piston 116, the force and moment acting on the piston 116 are effectively absorbed. To support the piston 116. That is, like the linear compressor according to the present invention, when the piston 116 is disposed at both ends of the first bearing 160 and the second bearing 170, the piston 116 is supported with a relatively small force to reduce the friction loss. .

In addition, both ends of the support structure has an advantage that the bending phenomenon of the piston 116 due to the moment is significantly smaller than the existing structure has the advantage that the behavior and reliability of the piston 116 is improved.

However, in order to implement the both ends of the support structure, the center of the first bearing 160 and the center of the second bearing 170 must be positioned on the same line. This is because the piston 116 can move straight without swinging to prevent wear or breakage due to the collision with the cylinder 111, and reduce friction loss.

Figure 5 is a schematic view showing a structure of both ends of the piston of the linear compressor according to the present invention to which the adhesive means is applied, Figure 6 is a cross-sectional view showing the first bearing shape of the linear compressor according to the present invention, Figure 7 It is sectional drawing which showed the 2nd bearing structure of the linear compressor. 8 is a flowchart illustrating a manufacturing method of the linear compressor according to the present invention to which the bonding unit is applied, and FIG. 9 is a flowchart illustrating a manufacturing method according to another embodiment of the linear compressor according to the present invention to which the bonding unit is applied.

5 to 9, in the linear compressor according to the present invention, the second bearing 170 may be fixed by the bonding means E. FIG.

Although the first bearing 160 is provided between the cylinder 111 and the piston 116 in the same manner as before, the second bearing 170 has a center so that its center coincides with the center of the first bearing 160. It is important to be installed. This is because the friction loss is reduced by ensuring the straightness during the reciprocating motion of the piston 116.

Specifically, the manufacturing method of the linear compressor according to the present invention is the step of fixing the first bearing 160 on one side of the piston 116 centered on the center of gravity of the piston 116, and of the second bearing 170 Fixing the second bearing 170 to the other side of the piston 116 about the center of gravity of the piston 116 such that a center thereof is aligned with the center of the first bearing 160. It is composed.

In the fixing of the second bearing 170, the second bearing 170 is aligned so that the power loss is the smallest in the state in which the piston 116 is reciprocated, and then using the adhesive means The bearing 170 may be fixed.

Here, the first bearing 160 is provided on the compression chamber (P, see FIG. 2) on the basis of the center of gravity of the piston 116, the second bearing 170 of the piston 116 It is preferably provided on the opposite side of the compression chamber (P, see Fig. 2) on the basis of the center of gravity.

The first bearing 160 may be provided between the cylinder 111 and the piston 116 at the compression chamber P (see FIG. 2) side of the cylinder 111, that is, at the front end of the cylinder 111. Can be. In this case, the first bearing 160 has a cylindrical shape in which the front end of the compression chamber P (see FIG. 2) is not inclined.

Conventionally, when the surface in which the first bearing 160 is in contact with the cylinder 111 is wide, the front end of the first bearing 160 is the cylinder 111 to prevent damage to the inner wall of the cylinder 111. Slightly inclined to face the central axis.

That is, as shown in FIG. 6, in the conventional first bearing 60, the inclined portion S is formed at the front end of the compression chamber P (see FIG. 2). This is, after all, because the first bearing 160 and the second bearing 170 is pushed to one side of the piston 116 center of gravity, the behavior of the piston 116 was not good. Here, reference numeral 62 is a storage groove 62 for storing oil supplied to the conventional first bearing 60.

However, since the position of the second bearing 170 is moved, the posture is stabilized during the reciprocating movement of the piston 116, so that the inclined portion can be eliminated, and the first bearing has a conventional inclined portion ( It consists of a cylindrical shape without S). Of course, the first bearing 160 of the linear compressor according to the present invention also has a storage groove 162 for storing oil.

As such, when the shape of the first bearing 160 is formed in a cylindrical shape without the inclined portion S, the manufacturing process is simplified, and the piston is in contact with the cylinder 111 in a large area. Since 116 is supported, frictional losses are reduced.

On the other hand, a seating member 118 is provided at the position where the second bearing 170 has been previously positioned to prevent the supplied oil from leaking out. The oil is supplied to reduce the friction between the cylinder 111 and the piston 116. Conventionally, the space between the first bearing 160 and the second bearing 170 served as a storage groove, but in the linear compressor according to the present invention, since the second bearing 170 is moved to the opposite side, The sealing member 118 is provided to preserve the supplied oil.

The sealing member 118 is made of a separate member may be coupled to the piston 116 is pressed or fused. In addition, the sealing member 118 may be formed integrally with the piston 116.

As such, since the sealing member 118 is provided, the oil lubricated in the first bearing 160 is preserved to enable lubrication even when oil is not smoothly supplied to the first bearing 160.

Meanwhile, an oil inlet 174 for supplying oil to the second bearing 170 and an oil discharge port 176 for discharging oil from the second bearing 170 are provided in the second bearing 170. It is provided.

In the related art, since the first bearing 160 and the second bearing 170 were adjacent to each other, oil could be supplied to the first bearing 160 and the second bearing 170 simultaneously by one oil supply system. . However, in the present invention, since the first bearing 160 and the second bearing 170 are disposed at both ends of the piston 116, the oil inlet 174 and the oil discharge port 176 are separately formed in the second bearing 170, respectively. It is provided.

In this case, the oil discharge port 176 is provided above the center of the second bearing 170 in order to preserve the oil supplied to the second bearing 170. That is, the oil discharge port 176 is located in the upper portion based on the center line C of the second bearing 170, all oil does not immediately escape, and a certain amount of oil is always preserved. Therefore, even if the oil supply to the second bearing 170 is not smooth, a stable lubrication action can be made.

In addition, the linear compressor according to the present invention is provided on the surface where the second bearing 170 is in contact with the piston 116, and oil is applied to the surface where the second bearing 170 and the piston 116 are in contact. A groove 172 for smoothly supplying is further included.

The groove 172 forms a predetermined space between the second bearing 170 and the piston 116. In addition, the oil supplied from the oil inlet 174 stays in the groove 172 for a while, and the piston 116 reciprocates to the surface where the second bearing 170 and the piston 116 come into contact with each other. Spread evenly. That is, the groove 172 serves as an intermediate reservoir of oil supplied to the second bearing 170.

Meanwhile, referring to the method of manufacturing the linear compressor in detail, first, the first bearing 160 is fixed to the compression chamber P (refer to FIG. 2) (S110). In addition, the second bearing 170 is temporarily aligned on the opposite side of the position of the first bearing 160 based on the center of gravity of the piston 116 (S120). At this time, the center of the second bearing 170 does not coincide with the center of the first bearing 160.

Here, the second bearing 170 is disposed to surround one end of the piston 116 and is coupled to a frame of the linear compressor body, that is, the linear compression unit 110. Specifically, the second bearing 170 may be coupled to the back cover 114 to support the piston 116. Of course, it is understood that the member of the compressor body to which the second bearing 170 is coupled may vary depending on the product.

At this time, the second bearing 170 is not completely fixed to the back cover 114, for example, is in a state in which the fastening means (not shown), such as a bolt, is arranged in a flowable state without being fully tightened. .

Thereafter, the degree of power loss of the linear compressor in the state of reciprocating the piston 116 is measured (S130). The measurement of the power loss can be made, for example, by comparing the stroke value according to the reciprocating motion of the piston 116 with the value of the current or voltage supplied to the linear compressor.

Here, if there is a reference value of the preset power loss amount, it is compared with the measured power loss amount. At this time, in the manufacturing method of the linear compressor according to the present invention, if the measured power loss amount is less than or equal to a predetermined reference value, by applying an adhesive means (E) to the second bearing 170 to the back cover 114 Fixing step (S150).

If the measured power loss amount is greater than the preset reference value, the second bearing 170 is aligned again (S120), and the operation of measuring the power loss in the state in which the piston 116 is reciprocated is repeated (S130). do. That is, the above process is repeated until the amount of power loss is equal to or smaller than the reference value.

The reference value of the amount of power loss can be obtained experimentally and empirically for the same product, and can be obtained by measuring the case where the power loss becomes the minimum while the straightness of the piston 116 is secured.

An epoxy resin or the like may be used as an adhesive means E for fixing the second bearing 170 to the back cover 114. Epoxy resin has excellent mechanical properties such as bending strength and hardness, does not generate volatile substances and shrinkage of volume during curing, and has great adhesion to the material surface when curing.

The adhesive means (E) is applied directly without further tightening the temporarily tightening means. Specifically, the bonding means (E) is preferably applied to a wide portion to include a portion provided with the fastening means to fix the second bearing 170 to the back cover 114.

By performing the above process, the center of the first bearing 160 and the center of the second bearing 170 can be positioned on the same line to implement both end support structures.

On the other hand, looking at the manufacturing method according to another embodiment of the linear compressor according to the present invention applying the adhesive means (E), first fixing the first bearing 160 to the compression chamber (P, see Fig. 2) (S210) . Then, the second bearing 170 is temporarily aligned on the opposite side of the position of the first bearing 160 based on the center of gravity of the piston 116 (S220). At this time, the center of the second bearing 170 is not in agreement with the center of the first bearing 160.

Thereafter, the degree of power loss of the linear compressor in the state of reciprocating the piston 116 is measured (S230). At this time, a trial and error method is performed to determine the position of the second bearing 170 in which the measured amount of power loss is substantially the smallest.

That is, the second bearing 170 is aligned while changing the position, and the amount of power loss is measured at each position. If the minimum value of the measured power loss is continuously updated, and the measurement of the power loss amount is repeated, the updated minimum value will converge to a predetermined value. At this time, if the minimum value is found in the next attempt, the position is determined as the position of the second bearing 170 in which the amount of power loss is the smallest (S240), and the bonding means E is applied to fix the second bearing 170. (S250).

Of course, as the number of times of power loss measurement increases, the position of the second bearing 170 will be aligned with the center of the first bearing 160 more accurately.

The member to which the second bearing 170 is fixed, the application method of the bonding means E, and the like are the same as described above.

FIG. 10 is a schematic view showing a structure of both ends of the piston of the linear compressor according to the present invention to which the position correction member is applied. FIG. Is a flowchart illustrating a manufacturing method according to another embodiment of the linear compressor according to the present invention to which the position correction member is applied.

10 to 12, in the linear compressor according to the present invention, the second bearing 170 is fastened in a state in which the position correction member G is inserted between the second bearing 170 and the compressor body. It may be fixed by (not shown).

That is, in the manufacturing method of the linear compressor according to the present invention, the step of fixing the second bearing 170, the second bearing 170 to minimize the power loss in the state reciprocating the piston 116 After the alignment, the position correction member G is inserted between the second bearing 170 and the compressor body, and the second bearing 170 is fixed by using a fastening means (not shown).

Looking at the manufacturing method of the linear compressor in detail, first, the first bearing 160 is fixed to the compression chamber (P, see FIG. 2) (S310). Then, the second bearing 170 is temporarily aligned on the opposite side of the position of the first bearing 160 on the basis of the center of gravity of the piston 116 (S320). At this time, the center of the second bearing 170 does not coincide with the center of the first bearing 160.

Here, the second bearing 170 is disposed to surround one end of the piston 116 and is coupled to a frame of the linear compressor body, that is, the linear compression unit 110. Specifically, the second bearing 170 may be coupled to the back cover 114 to support the piston 116.

Of course, the second bearing 170 is not completely fixed to the back cover 114, and is, for example, in a state in which the fastening means (not shown) such as a bolt is completely aligned without being completely tightened. .

Thereafter, the degree of power loss of the linear compressor in the state of reciprocating the piston 116 is measured (S330).

Here, if there is a reference value of the preset power loss amount, it is compared with the measured power loss amount. As described above, the reference value may be obtained by measuring in advance the case where the power loss becomes the minimum in the state in which the straightness of the piston 116 is secured.

At this time, in the manufacturing method of the linear compressor according to the present invention, if the measured power loss amount is less than or equal to a predetermined reference value, inserting the position correction member (G) between the second bearing 170 and the compressor body, and fastening The second bearing 170 is fixed by means (not shown) (S350).

The compressor body refers to a frame constituting the linear compression unit 110, and specifically, the back cover 114 may correspond to this.

The position correction member G may be a film or the like used as a gap gauge. The position correction member G is provided to fill the gap between the contact surface of the second bearing 170 and the back cover 114 in a state in which the second bearing 170 is arranged to have the smallest power loss. will be.

If the position correction member (G) is provided between the contact surface of the second bearing 170 and the back cover 114, when the second bearing 170 is aligned in a position that can minimize the power loss, fastening means Thereby completely fixing the second bearing 170. At this time, the fastening means may be used, such as bolts and nuts.

If the measured power loss is greater than the preset reference value, the second bearing 170 is aligned again (S320), and the power loss is measured (S330) while the piston 116 is reciprocated. . That is, the above process is repeated until the amount of power loss is equal to or smaller than the reference value.

By performing the above process, the center of the first bearing 160 and the center of the second bearing 170 can be positioned on the same line to implement both ends of the support structure.

On the other hand, looking at the manufacturing method according to another embodiment of the linear compressor according to the present invention to which the position correction member (G) is applied, first fixing the first bearing 160 to the compression chamber (P, see Fig. 2) (S410) ). Then, the second bearing 170 is temporarily aligned on the opposite side of the position of the first bearing 160 on the basis of the center of gravity of the piston 116 (S420).

Thereafter, the degree of power loss of the linear compressor in the state of reciprocating the piston 116 is measured (S430). At this time, a trial and error method is performed to determine the position of the second bearing 170 in which the measured amount of power loss is substantially the smallest.

That is, the second bearing 170 is aligned while changing the position, and the amount of power loss is measured at each position. If the minimum value of the measured power loss is continuously updated, and the measurement of the power loss amount is repeated, the updated minimum value will converge to a predetermined value. At this time, if the minimum value is found in the next trial, the position is determined as the position of the second bearing 170 in which the amount of power loss is the smallest (S440), and the position correction member G is the second bearing 170 and the compressor body. In the inserted state, the fastening means is applied to fix the second bearing 170 (S450).

Of course, as the number of times of power loss measurement increases, the position of the second bearing 170 will be aligned with the center of the first bearing 160 more accurately.

The method of applying the member to which the second bearing 170 is fixed or the position correction member G is the same as described above.

On the other hand, if the present invention provides a manufacturing method according to another embodiment of the linear compressor, the second bearing 170 may be provided to be supported by a deformable support member.

That is, in the step of fixing the second bearing 170, the second bearing 170 is supported by a deformable support member, during the reciprocating movement of the piston 116, the second bearing 170 itself Is to be aligned to the optimal position.

To this end, when the second bearing 170 is fixed to a member of the compressor body to which the second bearing 170 is fixed, for example, the back cover 114 as described above, the back cover 114 has a hardness It is preferable that the organic material is formed of a material such as plastic or rubber, rather than a large metal material.

Although the above has been described with reference to a preferred embodiment of the present invention, those skilled in the art to various modifications and changes to the present invention without departing from the spirit and scope of the invention described in the claims described below You can do it. Therefore, it should be seen that all modifications included in the technical scope of the present invention are basically included in the scope of the claims of the present invention.

According to the linear compressor according to the present invention described above, the following effects are obtained.

First, since two bearings supporting the piston are disposed opposite to each other based on the center of gravity of the piston, the piston can be supported by effectively absorbing the force and moment acting on the piston.

Second, since the piston is supported by a relatively small force, there is an advantage that the friction loss is reduced.

Third, both ends of the support structure as described above has the advantage that the bending of the piston due to the moment is significantly smaller than the existing structure is improved the behavior of the piston.

Fourth, since the frictional loss of the piston is reduced and the behavior of the piston is improved, the efficiency of the compressor is improved, and the reliability of the system is secured.

Fifth, by changing the shape of the first bearing, there is an advantage that the manufacturing process is simplified and the friction loss is further reduced.

Sixth, by providing a specific structure for a smooth oil supply to the second bearing, it is possible to prevent damage or breakage of the system.

Claims (7)

A piston reciprocating inside the cylinder and compressing a refrigerant in the compression chamber; A first bearing installed in the cylinder corresponding to one side of the piston based on the center of gravity of the piston, the first bearing supporting the piston having a cylindrical end without a slanted portion; And And a second bearing installed on the compressor body corresponding to the other side based on the center of gravity of the piston to support the piston. The method of claim 1, And a oil inlet for supplying oil to the second bearing, and an oil discharge port for discharging oil from the second bearing. The method of claim 2, The oil discharge port is a linear compressor, characterized in that provided above the center of the second bearing, in order to preserve the oil supplied to the second bearing. The method of claim 1, The second compressor is provided on the surface in contact with the piston, the linear compressor further comprises a groove for smoothly supplying oil to the surface in contact with the second bearing and the piston. The method of claim 1, And a sealing member provided between the piston and the cylinder to prevent leakage of the oil supplied to the first bearing. The method of claim 5, wherein And said sealing member is formed integrally with said piston. A piston reciprocating inside the cylinder and compressing a refrigerant in the compression chamber; A first bearing installed in the cylinder corresponding to one side of the piston based on the center of gravity of the piston to support the piston; A second bearing installed on the compressor body corresponding to the other side based on the center of gravity of the piston to support the piston; And And a groove provided on a surface of the second bearing in contact with the piston and for smoothly supplying oil to a surface of the second bearing in contact with the piston.

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