CN113250938A

CN113250938A - Compressor

Info

Publication number: CN113250938A
Application number: CN202011442723.9A
Authority: CN
Inventors: 金泳成; 俞善准; 金炯锡; 朴真成
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2020-02-12
Filing date: 2020-12-08
Publication date: 2021-08-13
Anticipated expiration: 2040-12-08
Also published as: KR20210102645A; CN113250938B; KR102390579B1

Abstract

The invention provides a compressor. A compressor according to an aspect of the present invention is a compressor that compresses a refrigerant sucked into a cylinder tube and discharges the refrigerant, and includes: a cylinder barrel of a cylindrical shape; a piston disposed inside the cylinder and reciprocating in an axial direction; and a bush (push) press-fitted to an inner surface of the cylinder, wherein a difference between an outer diameter of the bush and an inner diameter of the cylinder is 80 μm to 120 μm before the bush is press-fitted to the cylinder.

Description

Compressor

Technical Field

The present invention relates to a compressor. And more particularly, to a linear compressor compressing a refrigerant by a linear reciprocating motion of a piston.

Background

Generally, a compressor is a device that receives power from a power generation device such as a motor or a turbine and compresses a working fluid such as air or a refrigerant. Specifically, compressors have been widely used in the entire industry or household electrical appliances, particularly in vapor compression refrigeration cycles (hereinafter, referred to as "refrigeration cycles") and the like.

Such compressors may be classified into a Reciprocating compressor (Reciprocating compressor), a Rotary compressor (Rotary compressor), and a Scroll compressor (Scroll compressor) according to a manner of compressing a refrigerant.

The reciprocating compressor is a type in which a compression space is formed between a piston and a cylinder and fluid is compressed by a linear reciprocating motion of the piston; the rotary compressor is a system for compressing a fluid by a roller (roller) eccentrically rotating inside a cylinder tube; a scroll compressor is a system in which a pair of scrolls formed in a spiral shape are engaged and rotated to compress a fluid.

Recently, among reciprocating compressors, Linear compressors (Linear compressors) using Linear reciprocating motion without using a crankshaft are increasingly used. In the case of the linear compressor, since mechanical loss generated when converting a rotational motion into a linear reciprocating motion is small, there are advantages in that the efficiency of the compressor is improved and the structure is simple.

In the linear compressor, a cylinder tube is located inside a casing for forming a closed space to form a compression chamber, and a piston for covering the compression chamber reciprocates inside the cylinder tube. The linear compressor will repeatedly perform the following process: the fluid in the hermetic space is sucked into the compression chamber during the piston is located at the Bottom Dead Center (BDC), and the fluid in the compression chamber is compressed and discharged during the piston is located at the Top Dead Center (TDC).

The linear compressor is provided with a compression unit and a driving unit, respectively, and the compression unit is moved by a resonance spring to perform a resonance motion by a movement generated in the driving unit, and compresses and discharges a refrigerant.

The piston of the linear compressor will repeat a series of processes as follows: the refrigerant is sucked into the interior of the casing through the suction pipe while reciprocating at a high speed in the interior of the cylinder by the resonance spring, and then discharged from the compression space by the forward movement of the piston, and then moved to the condenser through the discharge pipe.

On the other hand, the linear compressor can be classified into an oil lubrication type linear compressor and a gas lubrication type linear compressor according to a lubrication method.

The oil-lubricated linear compressor is configured such that a predetermined amount of oil is stored in a casing, and a space between a cylinder tube and a piston is lubricated by the oil.

In contrast, the gas lubrication type linear compressor is configured such that a part of the refrigerant discharged from the compression space is guided between the cylinder tube and the piston without storing oil in the casing, and thereby the cylinder tube and the piston are lubricated by the gas pressure of the refrigerant.

In the oil-lubricated linear compressor, since oil having a relatively low temperature is supplied between the cylinder tube and the piston, overheating of the cylinder tube and the piston due to heat of the motor, heat of compression, or the like can be suppressed. Accordingly, the oil-lubricated linear compressor can prevent the refrigerant passing through the suction flow path of the piston from being sucked into the compression chamber of the cylinder tube and heated to increase the specific volume (specific volume), thereby preventing the occurrence of suction loss in advance.

However, in the oil-lubricated linear compressor, when the oil discharged to the refrigeration cycle apparatus together with the refrigerant is not smoothly recovered to the compressor, an oil shortage phenomenon may occur inside the casing of the compressor, and such an oil shortage phenomenon occurring inside the casing may become a cause of lowering the reliability of the compressor.

In contrast, the gas lubrication type linear compressor can be miniaturized compared to the oil lubrication type linear compressor, and since the space between the cylinder tube and the piston is lubricated by the refrigerant, there is an advantage in that the reliability of the compressor is not lowered by the lack of oil.

On the other hand, when the engine is operated at a high temperature of 100 ℃ or higher, the distance between the piston and the cylinder is shortened, and there is a problem that the piston and the cylinder collide with each other.

Documents of the prior art

Patent document

Patent document 1: korean granted patent publication No. 10-1484324B (Notice date: 2015.01.20)

Disclosure of Invention

The problem to be solved by the present invention is to provide a compressor capable of preventing collision between a piston and a cylinder by maintaining a distance between the piston and the cylinder.

In order to achieve the above object, according to one aspect of the present invention (aspect), a compressor for compressing a refrigerant sucked into a cylinder tube and discharging the compressed refrigerant includes: a cylinder barrel of a cylindrical shape; a piston disposed inside the cylinder and reciprocating in an axial direction; and a bush (push) press-fitted to an inner surface of the cylinder, wherein a difference between an outer diameter of the bush and an inner diameter of the cylinder is 80 μm to 120 μm before the bush is press-fitted to the cylinder.

Thus, the collision between the piston and the cylinder can be prevented by maintaining the distance between the piston and the cylinder.

Before the bush is press-fitted into the cylinder, a difference between an outer diameter of the bush and an inner diameter of the cylinder may be 80 μm to 90 μm.

In addition, an indentation belt may be formed between the bushing and the cylinder, and the compressor may satisfy the following formula 1, δ_T＝δ_TD+δ_EDβ, wherein δ_TRepresenting the total deformation, δ, of the internal diameter of the bushing_TDRepresents the amount of thermal deformation, δ, of the bushing_EDRepresents the elastic deformation amount of the bush, and β represents the elastic deformation coefficient of the bush.

In addition, the liner may have a linear expansion coefficient larger than that of the cylinder tube.

In addition, the yield strength (yield strength) of the bushing may be greater than the yield strength of the cylinder barrel.

Further, the difference between the inner diameter of the bushing and the outer diameter of the piston may be 5 μm or more at a temperature of 100 ℃.

In addition, the piston and the bushing may be formed of different materials from each other.

In addition, the bushing may be formed of a cast iron material, and the piston may be formed of an aluminum material.

In addition, the cylinder may be formed of an aluminum material, and the bushing may be formed of a cast iron material.

The cylinder tube may be formed of an Al-Mg-Si-based aluminum alloy.

In order to achieve the above object, according to one aspect of the present invention (aspect), a compressor for compressing a refrigerant sucked into a cylinder tube and discharging the compressed refrigerant includes: a cylinder barrel of a cylindrical shape; and a bush (push) press-fitted to an inner surface of the cylinder, wherein a difference between an outer diameter of the bush and an inner diameter of the cylinder is 80 μm to 120 μm before the bush is press-fitted to the cylinder.

In addition, an indentation belt may be formed between the bushing and the cylinder, and the compressor may satisfy the following formula 1, δ_T＝δ_TD+δ_EDβ, wherein δ_TIs the total deformation, δ, of the internal diameter of the bushing_TDIs referred to the amount of thermal deformation, δ, of the bushing_EDRefers to the amount of elastic deformation of the bushing, and β refers to the coefficient of elastic deformation of the bushing.

Additionally, the bushing may have a yield strength greater than a yield strength of the cylinder barrel.

The cylinder tube may be formed of an Al-Mg-Si-based aluminum alloy.

In order to achieve the above object, according to one aspect of the present invention (aspect), a compressor for compressing a refrigerant sucked into a cylinder tube and discharging the compressed refrigerant includes: a cylinder barrel of a cylindrical shape; a piston disposed in the cylinder and reciprocating in an axial direction; and a bush (push) press-fitted to an inner side surface of the cylinder, a press-fitting band being formed between the bush and the cylinder, and the compressor satisfying the following formula 1, δ_T＝δ_TD+δ_EDβ, wherein δ_TIs the total deformation, δ, of the internal diameter of the bushing_TDIs referred to the amount of thermal deformation, δ, of the bushing_EDRefers to the amount of elastic deformation of the bushing, and β refers to the coefficient of elastic deformation of the bushing.

Further, before the bush is press-fitted into the cylinder, a difference between an outer diameter of the bush and an inner diameter of the cylinder may be 80 μm to 120 μm.

According to the present invention, it is possible to provide a compressor capable of preventing collision between a piston and a cylinder by maintaining a distance between the piston and the cylinder.

Drawings

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

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

Fig. 3 is a sectional view showing a part of the structure of a compressor according to an embodiment of the present invention.

Fig. 4 is an enlarged view of a portion a of fig. 3.

Fig. 5 is a sectional view of a bushing and a cylinder of a compressor according to an embodiment of the present invention.

FIG. 6 is a graph showing the clearance between the cylinder and the piston based on temperature in accordance with one embodiment of the present invention.

Fig. 7 is a graph showing the amount of thermal deformation of the inner diameter of the bush based on the thickness of the press-fit band according to the embodiment of the present invention.

Fig. 8 is a graph showing the linear expansion coefficient of the liner based on the thickness of the press-in band according to the embodiment of the present invention.

Description of the reference numerals

100: the compressor 101: accommodation space

102: suction space 103: compression space

104: discharge space 110: casing (casting)

111: housing (shell) 112: first case cover

113: second housing cover 114: suction tube

115: discharge pipe 115 a: circulation pipe

116: first support spring 116 a: suction guide

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

117: second support spring 117 a: support bracket

117 b: first support guide 117 c: support cover

117 d: second support guide 117 e: third supporting and guiding member

118: resonant spring 118 a: a first resonant spring

118 b: second resonant spring 119: spring support

119 a: main body portion 119 b: second joint part

119 c: the support portion 120: frame structure

121: main body portion 122: first flange part

123: rear cover 123 a: support bracket

130: the driving unit 131: outer stator

132: coil wound body 132 a: bobbin

132 b: coil 133: stator core

134: inner stator 135: moving member (mover)

136: magnet frame 136 a: a first combining part

137: stator cover 140: cylinder barrel

141: second flange portion 142: gas inlet

150: piston 151: head part

152: guide portion 153: third flange part

154: suction port 155: suction valve

160: the muffler unit 161: suction muffler

161 a: fourth flange portion 162: internal guide

170: discharge valve assembly 171: discharge valve

172: valve spring 180: discharge cap assembly

181: first discharge cap 182: second discharge cap

183: third discharge cap 200: bush (push)

210: press-in band

Detailed Description

Hereinafter, embodiments disclosed in this specification (discloser) will be described in detail with reference to the drawings, and the same or similar constituent elements are given the same reference numerals regardless of the drawing numbers, and repeated description thereof will be omitted.

In describing the embodiments disclosed in the present specification, if a certain component is referred to as being "connected" or "coupled" to another component, it is understood that the component may be directly connected or coupled to the other component, but other components may be present therebetween.

In the description of the embodiments disclosed in the present specification, when it is determined that a specific description of a related known technique would make the gist of the embodiments disclosed in the present specification unclear, a detailed description thereof will be omitted. Further, the drawings are provided for the convenience of understanding the embodiments disclosed in the present specification, the technical idea disclosed in the present specification is not limited to the drawings, and the present invention includes all modifications, equivalents and alternatives made within the technical idea and technical scope of the present invention.

On the other hand, the term of the specification (disabler) may be replaced with the term of document, specification, description, or the like.

Referring to fig. 1, a linear compressor 100 according to an embodiment of the present invention may include: a housing 111; and case covers 112, 113 joined to the case 111. Broadly speaking, it is understood that the housing covers 112, 113 are one component of the housing 111.

At the lower side of the housing 111, a leg 20 may be coupled. The leg 20 may be coupled to a base of a product on which the linear compressor 100 is provided. For example, the product may include a refrigerator and the base may include a base of a machine compartment 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 housing 111 may have a substantially cylindrical shape, and may be laid laterally or longitudinally. With reference to fig. 1, the housing 111 may extend long in the lateral direction and have a lower height in the radial direction. That is, the linear compressor 100 may have a low height, and thus, for example, when the linear compressor 100 is provided at a base of a machine room of a refrigerator, there is an advantage in that the height of the machine room may be reduced.

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

On the outer surface of the housing 111, a terminal (terminal)30 may be provided. The connection terminal 30 can supply an external power to the driving unit 130 of the linear compressor 100. Specifically, the connection terminal 30 may be connected to a lead wire of the coil 132 b.

On the outside of the connection terminal 30, a bracket 31 may be provided. The bracket 31 may include: a plurality of brackets surrounding the wire terminals 30. The bracket 31 may perform a function of protecting the connection terminal 30 from an external impact or the like.

Both side portions of the case 111 may be opened. Housing covers 112 and 113 may be coupled to both side portions of the open housing 111. Specifically, the housing covers 112, 113 may include: a first housing cover 112 coupled to one side portion of the housing 111 having an opening; and a second housing cover 113 coupled to the other side portion of the housing 111, which is open. The inner space of the housing 111 can be sealed by

housing covers

112, 113.

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

The linear compressor 100 may include a plurality of

pipes

114, 115, 40, and the plurality of

pipes

114, 115, 40 may be provided at the casing 111 or the casing covers 112, 113 and may be capable of sucking, discharging, or injecting a refrigerant.

The plurality of

tubes

114, 115, 40 may include: a suction pipe 114 for flowing the refrigerant into the inside of the linear compressor 100; a discharge pipe 115 for discharging the compressed refrigerant from the linear compressor 100; and a supplementary pipe 40 for supplementing the refrigerant to the linear compressor 100.

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

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

The supplementary pipe 40 may be coupled to an outer circumferential surface of the housing 111. An operator may inject the refrigerant into the linear compressor 100 through the supplementary pipe 40.

The supplemental tube 40 may be coupled to the housing 111 at a different height than the discharge tube 115 to avoid interference with the discharge tube 115. Here, the height is understood to be a distance in the vertical direction starting from the leg portion 20. The discharge pipe 115 and the replenishment pipe 40 are coupled to the outer peripheral surface of the housing 111 at different heights, thereby achieving convenience in operation.

At least a part of the second housing cover 113 may be disposed adjacent to the inner circumferential surface of the housing 111 corresponding to the position for coupling the supplementary pipe 40. In other words, at least a portion of the second housing cover 113 may function as resistance to the refrigerant injected through the supplementary pipe 40.

Therefore, the flow path of the refrigerant flowing in via the supplementary tube 40 is formed such that the size of the flow path becomes small by the second housing cover 113 in the process of entering the inner space of the housing 111 and becomes large again after passing through the second housing cover 113, from the viewpoint of the flow path of the refrigerant. In this process, the pressure of the refrigerant is reduced, and the refrigerant is vaporized, and in this process, oil contained in the refrigerant can be separated. Therefore, the refrigerant from which the oil is separated flows into the piston 150, and the compression performance of the refrigerant can be improved. The oil component is understood to be working oil present in the cooling system.

Fig. 2 is a sectional view for explaining the structure of the compressor 100.

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

The linear compressor may be a constituent element of a refrigeration cycle, and the fluid to be compressed in the linear compressor may be a refrigerant circulating in the refrigeration cycle. The refrigeration cycle may include a condenser, an expansion device, an evaporator, and the like, in addition to the compressor. The linear compressor may be used as one component of a cooling system of a refrigerator, but is not limited thereto and may be widely used throughout the entire industry.

Referring to fig. 2, the compressor 100 may include: a housing 110; and a main body accommodated inside the case 110. The main body of the compressor 100 may include: a frame 120; a cylinder 140 fixed to the frame 120; a piston 150 linearly reciprocating inside the cylinder 140; a driving unit 130 fixed to the frame 120 and providing a driving force to the piston 150, and the like. Here, the cylinder 140 and the piston 150 may be referred to as

compression units

140 and 150.

The compressor 100 may include: a bearing unit for reducing friction between the cylinder 140 and the piston 150. The bearing unit may be an oil bearing or a gas bearing. Alternatively, a mechanical bearing may be used as the bearing unit.

The main body of the compressor 100 may be elastically supported by support springs 116 and 117, and the support springs 116 and 117 are disposed at both ends of the inner side of the casing 110. The support springs 116, 117 may include: a first support spring 116 supporting the rear of the main body; and a second support spring 117 supporting the front of the main body. The support springs 116, 117 may comprise leaf springs. The support springs 116 and 117 may support various internal parts of the body of the compressor 100 while being capable of absorbing vibration and impact generated as the piston 150 reciprocates.

The case 110 may form a closed space. The enclosed space may include: an accommodating space 101 for accommodating a sucked refrigerant; a suction space 102 in which a refrigerant before compression is filled; a compression space 103 for compressing a refrigerant; and a discharge space 104 in which the compressed refrigerant is filled.

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

The housing 110 may include: a housing 111 having both ends opened and formed in a substantially cylindrical shape elongated in the lateral direction; a first housing cover 112 coupled to a rear side of the housing 111; and a second housing cover 113 coupled to the front side of the housing 111. Here, the front side refers to a direction in which the compressed refrigerant is discharged as the left side in the drawing; the rear side refers to a direction in which the refrigerant flows in, which is the right side of the drawing. In addition, the first housing cover 112 or the second housing cover 113 may be formed integrally with the housing 111.

The housing 110 may be formed of a thermally conductive material. This enables heat generated in the internal space of the housing 110 to be quickly released to the outside.

The first casing cover 112 may be coupled to the casing 111 in such a manner as to seal the rear side of the casing 111, and the suction pipe 114 may be inserted into and coupled to the center of the first casing cover 112.

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

The first support spring 116 may include a circular plate spring. The edge portion of the first support spring 116 may be elastically supported in the front direction with respect to the rear cover 123 by the support bracket 123 a. The central portion of the first support spring 116, which forms the opening, may be supported in the rear direction with respect to the first casing cover 112 by the suction guide 116 a.

A through flow path may be formed inside the suction guide 116 a. The suction guide 116a may be formed in a cylindrical shape. A central opening portion of the first support spring 116 may be coupled to an outer circumferential surface of a front side of the suction guide 116a, and a rear side end portion of the suction guide 116a may be supported by the first case cover 112. At this time, an additional suction side support member 116b may be provided between the suction guide 116a and the inner side surface of the first housing cover 112.

The rear side of the suction guide 116a may communicate with the suction pipe 114, and the refrigerant sucked through the suction pipe 114 may pass through the suction guide 116a and smoothly flow into a muffler unit 160, which will be described later.

Between the suction guide 116a and the suction side support member 116b, a damping member 116c may be disposed. The damping member 116c may be formed of a rubber material or the like. This can block transmission of vibration, which may occur during suction of the refrigerant through the suction pipe 114, to the first housing cover 112.

The second housing cover 113 may be coupled to the housing 111 in such a manner as to seal the front side of the housing 111, and the discharge pipe 115 may be inserted through the circulation pipe 115a and coupled to the second housing cover 113. The refrigerant discharged from the compression space 103 may pass through the discharge cap assembly 180 and then be discharged to the refrigeration cycle through the circulation pipe 115a and the discharge pipe 115.

The front side of the main body of the compressor 100 may be elastically supported by the second supporting springs 117 in a radial direction of the casing 111 or the second casing cover 113.

The second support spring 117 may include a circular plate spring. The central portion of the second support spring 117, in which the opening is formed, may be supported in the rear direction with respect to the discharge cap assembly 180 by the first support guide 117 b. The edge of the second support spring 117 may be supported by the support bracket 117a in a forward direction with respect to the inner surface of the housing 111 or the inner circumferential surface of the housing 111 adjacent to the second housing cover 113.

Unlike fig. 2, the edge of the second supporting spring 117 may be supported in a forward direction with respect to the inner surface of the housing 111 or the inner circumferential surface of the housing 111 adjacent to the second housing cover 113 by an additional bracket (not shown) coupled to the second housing cover 113.

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

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

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

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

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

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

The bearing inlet groove 125a may be recessed by a predetermined depth in the axial direction, and the bearing communication hole 125b may be a hole having a cross-sectional area smaller than that of the bearing inlet groove 125a and inclined toward the inner circumferential surface of the body portion 121. The gas groove 125c may be formed in an annular shape having a predetermined depth and an axial length on the inner circumferential surface of the body portion 121. In contrast, the gas groove 125c may be formed in the outer peripheral surface of the cylinder tube 140 that contacts the inner peripheral surface of the body 121, or may be formed in the entire inner peripheral surface of the body 121 and the outer peripheral surface of the cylinder tube 140.

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

On the other hand, the frame 120 and the cylinder 140 may be formed of aluminum or an aluminum alloy.

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

The cylinder 140 may include: and a second flange 141 disposed at a front end thereof. The second flange portion 141 may be bent toward the outside of the cylinder 140. The second flange portion 141 may extend in the outer circumferential direction of the cylinder 140. The second flange portion 141 of the cylinder 140 may be coupled with the frame 120. For example, a flange groove corresponding to the second flange portion 141 of the cylinder 140 may be formed at the front side end portion of the frame 120, and the second flange portion 141 of the cylinder 140 may be inserted into the flange groove and coupled by a coupling member.

On the other hand, a gas bearing member may be provided which can lubricate the space between the cylinder 140 and the piston 150 by supplying the discharged gas to the space between the outer circumferential surface of the piston 150 and the outer circumferential surface of the cylinder 140. The spit gas between the cylinder 140 and the piston 150 provides a levitation force to the piston 150, thereby enabling reduction of friction generated between the piston 150 and the cylinder 140.

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

The gas inflow port 142 may be formed to have a wide inlet and a fine through hole at an outlet, thereby functioning as a nozzle. A filter (not shown) for blocking inflow of foreign substances may be additionally provided at an inlet portion of the gas inlet 142. The filter may be a mesh filter made of metal, or may be formed by winding a member such as a thin wire.

The gas inlet 142 may be formed in plurality independently, or the inlet may be formed in a ring-shaped groove, and the outlet may be formed in plurality at regular intervals along the ring-shaped groove. The gas inlet 142 may be formed only on the front side with respect to the axial center of the cylinder 140. In addition, the gas inlet 142 may be formed on the rear side with respect to the axial center of the cylinder 140 in consideration of the drooping of the piston 150.

The piston 150 is inserted into an open end portion formed at the rear of the cylinder 140 and is disposed to close the rear of the compression space 103.

The piston 150 may include a head 151 and a guide portion 152. The head 151 may be formed in a disc shape. The head 151 may be partially open. The header 151 may divide the compression space 103. The guide portion 152 may extend rearward from an outer circumferential surface of the head portion 151. The guide portion 152 may be formed in a cylindrical shape. The guide 152 may be hollow inside, and a front portion thereof may be sealed by the head 151. The guide portion 152 may be opened at the rear thereof and connected to the muffler unit 160. The head 151 may be an additional member combined with the guide 152. Unlike this, the head 151 and the guide 152 may be formed in one body.

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

The suction port 154 may extend in the axial direction of the piston 150. The suction port 154 may be formed to be inclined with respect to the axial direction of the piston 150. For example, the suction port 154 may extend to be inclined with respect to a direction that is farther from the center axis toward the rear of the piston 150.

The suction port 154 may be formed in a circular shape in cross section. The inner diameter of the suction port 154 may be formed to be fixed. In contrast, the suction port 154 may be formed as an elongated hole whose opening extends along the radial direction of the head 151, and whose inner diameter gradually increases toward the rear.

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

A suction valve 155 for selectively opening and closing a suction port 154 may be installed at a head 151 of the piston 150 adjacent to the compression space 103. The suction valve 155 can be actuated by elastic deformation to open or close the suction port 154. That is, the suction valve 155 may be elastically deformed to open the suction port 154 by the pressure of the refrigerant flowing to the compression space 103 through the suction port 154.

The piston 150 may be connected with the moving member 135. The moving member 135 may reciprocate in the front-rear direction as the piston 150 moves. Between the moving member 135 and the piston 150, an inner stator 134 and a cylinder 140 may be disposed. The mover 135 and the piston 150 may be connected to each other via a magnet frame 136, the magnet frame 136 being formed to bypass the cylinder 140 and the inner stator 134 toward the rear.

The muffler unit 160 may be combined with the rear of the piston 150 so as to attenuate noise generated during the suction of the refrigerant into the piston 150. The refrigerant sucked through the suction pipe 114 may pass through the muffler unit 160 and flow to the suction space 102 inside the piston 150.

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

The suction muffler 161 may be positioned at the rear of the piston 150, a rear side opening of the suction muffler 161 may be disposed adjacent to the suction pipe 114, and a front side end of the suction muffler 161 may be combined with the rear of the piston 150. The suction muffler 161 forms a flow path in the axial direction, and thereby can guide the refrigerant in the accommodating space 101 to the suction space 102 inside the piston 150.

A plurality of noise spaces partitioned by baffles (baffles) may be formed inside the suction muffler 161. The suction muffler 161 may be formed by coupling two or more members to each other, and for example, a plurality of noise spaces may be formed by pressing and coupling the second suction muffler to the inside of the first suction muffler. In addition, the suction muffler 161 may be formed of a plastic material in consideration of weight and insulation.

One side of the inner guide 162 may communicate with the noise space of the suction muffler 161, and the other side thereof may be deeply inserted into the interior of the piston 150. The inner guide 162 may be formed in a pipe (pipe) shape. Both ends of the inner guide 162 may have the same inner diameter. The inner guide 162 may be formed in a cylindrical shape. In contrast, the inner guide 162 may have a larger inner diameter at a front end on the discharge side than at a rear end on the opposite side.

The suction muffler 161 and the inner guide 162 may be provided in various shapes, by which the pressure of the refrigerant passing through the muffler unit 160 can be adjusted. The suction muffler 161 and the inner guide 162 may also be formed in one body.

The discharge valve assembly 170 may include: a discharge valve 171; and a valve spring 172 that is provided on the front side of the discharge valve 171 and elastically supports the discharge valve 171. The discharge valve assembly 170 may selectively discharge the refrigerant compressed in the compression space 103. Here, the compression space 103 refers to a space formed between the suction valve 155 and the discharge valve 171.

The discharge valve 171 may be configured to be supported on the front surface of the cylinder 140. The discharge valve 171 can selectively open and close the front opening of the cylinder 140. The discharge valve 171 may be actuated by elastic deformation, and thus may be able to open or close the compression space 103. The discharge valve 171 is elastically deformed by the pressure of the refrigerant flowing through the compression space 103 to the discharge space 104, thereby opening the compression space 103. For example, the compression space 103 may be kept in a sealed state in a state where the discharge valve 171 is supported on the front surface of the cylinder 140, and the compressed refrigerant in the compression space 103 may be discharged toward an opened space in a state where the discharge valve 171 is spaced apart from the front surface of the cylinder 140.

The valve spring 172 may be disposed between the discharge valve 171 and the discharge cap assembly 180, and provide an elastic force in the axial direction. The valve spring 172 may be a compression coil spring, or a plate spring may be used in consideration of space occupation or reliability.

When the pressure in the compression space 103 is equal to or higher than the discharge pressure, the valve spring 172 deforms forward, thereby opening the discharge valve 171, and the refrigerant can be discharged from the compression space 103 and toward the first discharge space 104a of the discharge cap assembly 180. When the discharge of the refrigerant is finished, the valve spring 172 provides a restoring force to the discharge valve 171, thereby closing the discharge valve 171.

Hereinafter, a process in which the refrigerant flows into the compression space 103 through the suction valve 155 and the refrigerant in the compression space 103 is discharged to the discharge space 104 through the discharge valve 171 will be described, specifically, as follows.

When the pressure in the compression space 103 becomes equal to or lower than a predetermined suction pressure while the piston 150 is linearly reciprocating inside the cylinder 140, the suction valve 155 is opened, and the refrigerant is sucked into the compression space 103. On the contrary, if the pressure of the compression space 103 exceeds the preset suction pressure, the refrigerant of the compression space 103 is compressed in a state where the suction valve 155 is closed.

On the other hand, when the pressure in the compression space 103 becomes equal to or higher than the preset discharge pressure, the valve spring 172 deforms forward, thereby opening the discharge valve 171 connected thereto, and the refrigerant is discharged from the compression space 103 toward the discharge space 104 of the discharge cap assembly 180. When the discharge of the refrigerant is completed, the valve spring 172 applies a restoring force to the discharge valve 171, whereby the discharge valve 171 is closed, and the front of the compression space 103 is sealed.

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

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

The discharge cap assembly 180 may be formed of a heat conductive material. Therefore, when the high-temperature refrigerant flows into the discharge cap assembly 180, the heat of the refrigerant is transmitted to the casing 110 via the discharge cap assembly 180 and is released to the outside of the compressor.

The discharge cap assembly 180 may be formed of one discharge cap, or a plurality of discharge caps may be arranged to communicate with each other in sequence. When the discharge cap assembly 180 is formed of a plurality of discharge caps, the discharge space 104 may include a plurality of space portions partitioned by the respective discharge caps. The plurality of space portions may be arranged along the front-rear direction and communicate with each other.

For example, in the case where there are three discharge caps, the discharge space 104 may include: a first discharge space 104a formed between the first discharge cap 181 coupled to the front side of the frame 120 and the frame 120; a second discharge space 104b which communicates with the first discharge space 104a and is formed between the first discharge cap 181 and the second discharge cap 182 coupled to the front side of the first discharge cap 181; and a third discharge space 104c which communicates with the second discharge space 104b and is formed between the third discharge cap 183 and the second discharge cap 182 which are coupled to the front side of the second discharge cap 182.

The first discharge space 104a can selectively communicate with the compression space 103 through the discharge valve 171, the second discharge space 104b can communicate with the first discharge space 104a, and the third discharge space 104c can communicate with the second discharge space 104 b. Thus, the refrigerant discharged from the compression space 103 is discharged to the outside of the casing 110 through the circulation pipe 115a and the discharge pipe 115 communicating with the third discharge cap 183 while the discharge noise thereof is attenuated as it passes through the first discharge space 104a, the second discharge space 104b, and the third discharge space 104c in this order.

The driving unit 130 may include: an outer stator (out stator)131 configured to surround the body portion 121 of the frame 120 between the housing 111 and the frame 120; an inner stator (inner stator)134 configured to surround the cylinder 140 between the outer stator 131 and the cylinder 140; and a mover 135 disposed between the outer stator 131 and the inner stator 134.

The outer stator 131 may be coupled to the rear of the first flange portion 122 of the frame 120, and the inner stator 134 may be coupled to the outer circumferential surface of the body portion 121 of the frame 120. Also, the inner stator 134 may be disposed to be spaced toward the inside of the outer stator 131, and the moving element 135 may be disposed in a space between the outer stator 131 and the inner stator 134.

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

The outer stator 131 may include: a coil wound body 132 surrounding the axial direction along the circumferential direction; and a stator core 133 laminated so as to surround the coil wound body 132. The coil wound body 132 may include: a bobbin (bobbin)132a having a hollow cylindrical shape inside; and a coil 132b wound in the circumferential direction of the bobbin 132 a. The cross section of the coil 132b may be formed in a circular or polygonal shape, and may be, for example, a hexagonal shape. The stator core 133 may be formed by radially laminating a plurality of laminated plates (lamination sheets), or may be formed by laminating a plurality of laminated blocks (lamination blocks) in the circumferential direction.

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

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

One side of the moving member 135 may be supported in combination with the magnet frame 136. The magnet frame 136 may have a substantially cylindrical shape and be configured to be inserted into a space between the outer stator 131 and the inner stator 134. Also, the magnet frame 136 may be provided to be coupled to a rear side of the piston 150 and to move together with the piston 150.

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

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

When a current is applied to the driving unit 130, a magnetic flux (magnetic flux) is formed on the winding coil, and an electromagnetic force is generated by an interaction between the magnetic flux of the winding coil formed on the outer stator 131 and a magnetic flux formed by the permanent magnet of the mover 135, thereby enabling the mover 135 to move. Further, the piston 150 connected to the magnet frame 136 reciprocates in the axial direction integrally with the moving member 135 while the moving member 135 reciprocates in the axial direction.

On the other hand, the driving unit 130 and the compressing

units

140 and 150 may be supported by the supporting

springs

116 and 117 and the resonant spring 118 in the axial direction.

The resonant spring 118 can achieve effective compression of the refrigerant by increasing vibration generated by the reciprocating motion of the mover 135 and the piston 150. Specifically, the piston 150 may be moved in resonance by adjusting the resonance spring 118 to a vibration frequency corresponding to the natural vibration frequency of the piston 150. In addition, the resonant spring 118 can stably move the piston 150, thereby reducing the occurrence of vibration and noise.

The resonant spring 118 may be a coil spring extending in the axial direction. Both end portions of the resonance spring 118 may be connected to the vibration body and the fixed body, respectively. For example, one end portion of the resonant spring 118 may be connected with the magnet frame 136, and the other end portion thereof may be connected with the rear cover 123. Therefore, the resonance spring 118 is elastically deformable between the vibrator that generates vibration at one end portion of the resonance spring 118 and the fixed body that is fixed to the other end portion of the resonance spring 118.

The natural frequency of the resonant spring 118 may be designed to coincide with the resonant frequency of the mover 135 and the piston 150 when the compressor 100 is operated, thereby enabling the reciprocating motion of the piston 150 to be increased. However, here, the rear cover 123 provided as a fixed body is elastically supported by the housing 110 by the first support spring 116, and thus is strictly speaking not fixed.

The resonant springs 118 may include a first resonant spring 118a and a second resonant spring 118b, and the first resonant spring 118a is supported at a rear side and the second resonant spring 118b is supported at a front side with reference to the spring supporter 119.

The spring support 119 may include: a main body portion 119a surrounding the suction muffler 161; a second coupling portion 119b bent inward in the radial direction from the front of the body portion 119 a; and a support portion 119c bent radially outward from the rear of the body portion 119 a.

The front surface of the second coupling portion 119b of the spring support 119 may be supported by the first coupling portion 136a of the magnet frame 136. The inner diameter of the second coupling portion 119b of the spring supporter 119 may surround the outer diameter of the suction muffler 161. For example, the second coupling portion 119b of the spring supporter 119, the first coupling portion 136a of the magnet frame 136, and the third flange portion 153 of the piston 150 may be integrally coupled by a mechanical coupling member after being sequentially disposed. At this time, as previously described, the fourth flange portion 161a of the suction muffler 161 may be disposed between the third flange portion 153 of the piston 150 and the first coupling portion 136a of the magnet frame 136 and fixed together.

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

A plurality of first resonance springs 118a and a plurality of second resonance springs 118b may be arranged along the circumferential direction of the center axis. The first resonant spring 118a and the second resonant spring 118b may be arranged in parallel along the axial direction or may be arranged to be offset from each other. The first resonant spring 118a and the second resonant spring 118b may be arranged at a predetermined interval along the radiation direction of the central axis. For example, the first resonant spring 118a and the second resonant spring 118b are provided in three, respectively, and are arranged at intervals of 120 degrees along the radiation direction of the central axis.

The compressor 100 may include a plurality of sealing members: a plurality of the sealing members serves to increase coupling force between the frame 120 and a plurality of components of the circumference thereof.

For example, the plurality of sealing members may include: a first sealing member provided at a portion where the frame 120 and the discharge cap assembly 180 are coupled to each other, and inserted into an installation groove provided at a front end of the frame 120; and a second sealing member which is provided at a portion where the frame 120 and the cylinder 140 are combined, and is inserted into a setting groove provided at an outer side surface of the cylinder 140. The second sealing member serves to prevent the refrigerant in the gas groove 125c formed between the inner circumferential surface of the frame 120 and the outer circumferential surface of the cylinder 140 from leaking to the outside, and can increase the coupling force between the frame 120 and the cylinder 140. The plurality of sealing members may further include a third sealing member which is provided at a portion where the frame 120 and the inner stator 134 are combined and is inserted into a setting groove provided at an outer side surface of the frame 120. Here, the first to third sealing members may have a ring shape.

The operating state of the linear compressor 100 described above is as follows.

First, if a current is applied to the driving unit 130, a magnetic flux may be formed at the outer stator 131 due to the current flowing through the coil 132 b. The magnetic flux formed at the outer stator 131 generates an electromagnetic force, and the moving member 135 provided with the permanent magnet linearly reciprocates due to the generated electromagnetic force. Such an electromagnetic force is alternately generated in a direction (forward direction) in which the piston 150 faces a Top Dead Center (TDC) when a compression stroke is performed, and in a direction (backward direction) in which the piston 150 faces a Bottom Dead Center (BDC) when an intake stroke is performed. That is, the driving unit 130 may generate a force pushing the moving member 135 and the piston 150 toward the moving direction, i.e., a thrust force.

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

If the piston 150 moves in a direction (rearward direction) in which the volume of the compression space 103 increases, the pressure of the compression space 103 may decrease. At this time, the suction valve 155 installed in front of the piston 150 is opened, and thus the refrigerant staying in the suction space 102 is sucked into the compression space 103 along the suction port 154. Such a suction stroke may be performed until the piston 150 increases the volume of the compression space 103 to the maximum and is located at the bottom dead center.

The piston 150 reaching the bottom dead center switches its moving direction and moves toward a direction (forward direction) in which the volume of the compression space 103 is reduced while performing a compression stroke. When the compression stroke is performed, the pressure of the compression space 103 is increased, and thus the sucked refrigerant is compressed. When the pressure in the compression space 103 reaches the set pressure, the discharge valve 171 is pushed out by the pressure in the compression space 103 to open the cylinder tube 140, and the refrigerant can be discharged into the discharge space 104 through the partitioned space. Such a compression stroke may be continuously performed until the piston 150 moves to the top dead center where the volume of the compression space 103 is minimized.

While the suction stroke and the compression stroke of the piston 150 are repeated, the refrigerant flowing into the receiving space 101 inside the compressor 100 via the suction pipe 114 may sequentially pass through the suction guide 116a, the suction muffler 161, and the inner guide 162 and flow into the suction space 102 inside the piston 150, and the refrigerant of the suction space 102 may flow into the compression space 103 inside the cylinder 140 when the piston 150 performs the suction stroke. A flow in which the refrigerant of the compression space 103 is compressed and discharged to the discharge space 104, and then discharged to the outside of the compressor 100 through the circulation pipe 115a and the discharge pipe 115 is formed during the compression stroke of the piston 150.

Fig. 3 is a sectional view showing a part of the structure of a compressor according to an embodiment of the present invention. Fig. 4 is an enlarged view of a portion a of fig. 3. Fig. 5 is a sectional view of a bushing and a cylinder of a compressor according to an embodiment of the present invention. FIG. 6 is a graph showing the clearance between the cylinder and the piston based on temperature in accordance with one embodiment of the present invention. Fig. 7 is a graph showing the amount of thermal deformation of the inner diameter of the bush based on the thickness of the press-fit band according to the embodiment of the present invention. Fig. 8 is a graph showing the linear expansion coefficient of the liner based on the thickness of the press-in band according to the embodiment of the present invention.

The compressor 100 according to the embodiment of the present invention may include the cylinder 140, the piston 150, and the bush (bush)200, but some of the components may be omitted, and additional components may not be excluded.

The compressor 100 may include a cylinder 140. The cylinder 140 may be formed in a cylindrical shape. The cylinder 140 may be formed in a cylindrical shape with its front and rear opened. The cylinder 140 may be formed to extend in the axial direction. The cylinder 140 may be fixed to the frame 120. The cylinder 140 may have a gas inlet 142 formed therein. A piston 150 may be disposed within the cylinder 140. A bushing 200 may be disposed inside the cylinder 140. A bushing 200 may be disposed between the cylinder 140 and the piston 150. The bush 200 may be press-coupled to the inner side surface of the cylinder 140. The inner diameter of the cylinder 140 may be smaller than the outer diameter of the bushing 200 before the bushing 200 is press-fitted into the cylinder 140.

The compressor 100 may include a piston 150. The piston 150 may be disposed in the cylinder 140. The piston 150 may be disposed within the cylinder 140. The outer side of the piston 150 and the inner side of the cylinder 140 may be spaced apart from each other. A gap d may be formed between the outer side surface of the piston 150 and the inner side surface of the cylinder 140. Here, the clearance d between the inner surface of the cylinder 140 and the outer surface of the piston 150 may be a difference between the inner diameter of the cylinder 140 and the outer diameter of the piston 150.

The compressor 100 may include a bushing 200. The bushing 200 may be disposed within the cylinder 140. The bushing 200 may be disposed between the cylinder 140 and the piston 150. The bush 200 may be coupled to the inner side surface of the cylinder 140. The bush 200 may be press-coupled to the inner side surface of the cylinder 140. The outer diameter of the bushing 200 may be formed to be larger than the inner diameter of the cylinder 140 before the bushing 200 is press-fitted into the cylinder 140. Thus, when the bush 200 is press-fitted and coupled to the inner surface of the cylinder 140, the press-fitting band 210 can be formed between the bush 200 and the cylinder 140.

The piston 150 and the bushing 200 may be formed of different materials from each other. For example, the piston 150 may be formed of an aluminum material, and the bushing 200 may be formed of a cast iron material, so that wear resistance between the piston 150 and the bushing 200 can be improved. In this case, since the linear expansion coefficient of the piston 150 is larger than that of the bushing 200, in the case where the temperature rises due to the reciprocating motion of the piston 150 in the axial direction, the gap d between the piston 150 and the bushing 200 may be reduced.

In an embodiment of the present invention, since the press-in band 210 is formed between the bushing 200 and the cylinder 140, the compressor 100 may satisfy the following equation 1.

[ equation 1]

δ_T＝δ_TD+δ_EDβ

Here, δ_TMay refer to the total amount of deformation, δ, of the inner diameter of bushing 200_TDMay refer to the amount of thermal deformation, δ, of the bushing 200_EDMay refer to the amount of elastic deformation of the bushing 200, and β may refer to the elastic deformation coefficient of the bushing 200.

That is, by increasing the elastic deformation amount of the bush 200 and the elastic deformation coefficient of the bush 200, the total deformation amount of the inner diameter of the bush 200 is increased, and thus the gap d between the piston 150 and the bush 200 can be prevented from being decreased.

Here, the elastic deformation coefficient β of the bushing 200 may satisfy the following formula 2.

[ formula 2]

Here, β may refer to an elastic deformation coefficient, Y, of the bushing 200_cMay refer to the yield strength, Y, of the cylinder 140_bMay refer to the yield strength, C, of the bushing 200_cMay refer to the linear expansion coefficient, C, of the cylinder 140_bMay refer to the linear expansion coefficient of the bushing 200.

That is, the elastic deformation coefficient of the bushing 200 may be inversely proportional to the yield strength of the cylinder 140, and may be proportional to the yield strength of the bushing 200, and may be proportional to the linear expansion coefficient of the cylinder 140, and may be proportional to the linear expansion coefficient of the bushing 200.

In other words, by reducing the yield strength of the cylinder 140, increasing the yield strength of the bushing 200, increasing the linear expansion coefficient of the cylinder 140, and increasing the linear expansion coefficient of the bushing 200, the clearance d between the piston 150 and the bushing 200 can be prevented from being reduced even during operation at a high temperature of 100 ℃. Accordingly, collision between the piston 150 and the cylinder 140 can be prevented.

For example, the liner 200 may have a coefficient of linear expansion greater than that of the cylinder tube 140. Additionally, the yield strength of the bushing 200 may be greater than the yield strength of the cylinder barrel 140.

The cylinder 140 and the bush 200 may be formed of different materials from each other. For example, the liner 200 may be formed of a cast iron material, and the cylinder 140 may be formed of an aluminum material, so that the wear resistance between the liner 200 and the cylinder 140 can be improved. In this case, the cylinder tube 140 may be made of Al-Mg-Si based aluminum alloy. Thus, even during operation at a high temperature of 100 ℃ or higher, the clearance d between the bush 200 and the piston 150 can be maintained at a predetermined distance or more, and collision between the bush 200 and the piston 150 can be prevented.

In the case where the clearance d between the bushing 200 and the piston 150 is excessively small, collision between these constituents may occur, and in the case where the clearance d between the bushing 200 and the piston 150 is excessively large, compression efficiency of the compressor 100 may be reduced. Referring to fig. 6, at normal temperature, the gap d between the bushing 200 and the piston 150 may be 10 μm. Further, the difference between the inner diameter of the bushing 200 and the outer diameter of the piston 150, i.e., the clearance d between the bushing 200 and the piston 150, may be 5 μm or more at a temperature of 100 ℃. Thereby, not only the compression efficiency of the compressor 100 can be improved, but also collision between the bushing 200 and the piston 150 can be prevented.

Before the bush 200 is press-fitted into the cylinder 140, if the difference between the outer diameter of the bush 200 and the inner diameter of the cylinder 140, that is, the thickness of the press-fitting band 210 is small, the amount of thermal deformation of the inner diameter of the bush 200 may be reduced. In contrast, in the case where the thickness of the press-in band 210 is large, the plastic deformation region becomes large, and the amount of thermal deformation of the inner diameter of the bush 200 may increase.

Specifically, referring to fig. 7 and 8, when the thickness of the press-in tape 210 is 120 μm, it can be confirmed that: the linear expansion coefficient of the liner 200 is raised to the vicinity of 17.5, and the amount of thermal deformation of the liner 200 is between 30 μm and 35 μm. In addition, when the thickness of the press-in tape 210 was 80 μm, it was confirmed that: the linear expansion coefficient of the bushing 200 is increased to 18 to 19, and the amount of thermal deformation of the bushing 200 is 30 to 35 μm. In contrast, in the case where the thickness of the press-in band 210 is less than 80 μm, it can be confirmed that the amount of thermal deformation of the bush 200 is reduced to between 20 μm and 25 μm.

That is, before the bush 200 is press-fitted into the cylinder 140, the difference between the outer diameter of the bush 200 and the outer diameter of the cylinder 140, that is, the thickness of the press-fitting band 210 may be 80 μm to 120 μm. Preferably, the difference between the size of the outer diameter of the bushing 200 and the size of the outer diameter of the cylinder 140 may be 80 μm to 90 μm before the bushing 200 is press-fitted into the cylinder 140. Thus, the total amount of deformation of the inner diameter of the bush 200 is increased, thereby preventing the clearance d between the piston 150 and the bush 200 from decreasing.

Any one or other embodiments of the specification set forth above are not intended to be exclusive or exhaustive of each other. The respective constituent elements or functions of any one of the embodiments or the other embodiments of the present invention described above may be used in combination or combined.

For example, this means that the a configuration described in a specific embodiment and/or drawing and the B configuration described in other embodiment and/or drawing can be combined. That is, even if the combination between the components is not directly described, it means that the combination is possible unless it is explicitly stated that the combination is impossible.

The above detailed description is, therefore, not to be taken in a limiting sense, and is to be construed as exemplary in all aspects. The scope of the invention should be determined by reasonable interpretation of the appended claims and all changes which come within the equivalent scope of the invention should be construed as falling within the scope of the invention.

Claims

1. A compressor for compressing a refrigerant sucked into a cylinder tube and discharging the refrigerant, comprising:

a cylinder barrel of a cylindrical shape;

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

a bushing press-fitted into the inner surface of the cylinder,

before the bush is press-fitted into the cylinder, a difference between an outer diameter of the bush and an inner diameter of the cylinder is 80 μm to 120 μm.

2. The compressor of claim 1,

before the bush is press-fitted into the cylinder, a difference between an outer diameter of the bush and an inner diameter of the cylinder is 80 μm to 90 μm.

3. The compressor of claim 1,

a press-in band is formed between the bush and the cylinder,

the compressor satisfies the following formula,

[ equation 1]

δ_T＝δ_TD+δ_EDβ

Wherein, delta_TIs the total deformation, δ, of the internal diameter of the bushing_TDIs referred to the amount of thermal deformation, δ, of the bushing_EDRefers to the amount of elastic deformation of the bushing, and β refers to the coefficient of elastic deformation of the bushing.

4. The compressor of claim 1,

the linear expansion coefficient of the bushing is greater than that of the cylinder barrel.

5. The compressor of claim 1,

the yield strength of the bushing is greater than the yield strength of the cylinder barrel.

6. The compressor of claim 1,

the difference between the inner diameter of the bushing and the outer diameter of the piston is 5 [ mu ] m or more at a temperature of 100 ℃.

7. The compressor of claim 1,

the piston and the bushing are formed of different materials from each other.

8. The compressor of claim 1,

the bushing is formed of a cast iron material, and the piston is formed of an aluminum material.

9. The compressor of claim 1,

the cylinder barrel is made of aluminum, and the lining is made of cast iron.

10. The compressor of claim 9,

the cylinder barrel is formed of an Al-Mg-Si series aluminum alloy.