CN213684425U

CN213684425U - Compressor

Info

Publication number: CN213684425U
Application number: CN202022080564.4U
Authority: CN
Inventors: 金光旭; 崔基喆
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2019-10-31
Filing date: 2020-09-21
Publication date: 2021-07-13
Anticipated expiration: 2030-09-21
Also published as: KR102271808B1; KR20210051735A; EP3816440A1

Abstract

The utility model discloses a compressor. The compressor includes: a compressor body including a cylinder, a piston that reciprocates in the cylinder in an axial direction of a housing, and a drive unit that drives the piston; a housing surrounding the compressor body; a first support portion that supports a suction side of the compressor main body in the casing; and a second support portion that supports the discharge side of the compressor body inside the casing. At this time, the case may be constituted by a lower shell and an upper shell fixed to the lower shell, and a separation surface of the lower shell and the upper shell fixed to each other may be formed to be inclined with respect to a horizontal center line of the case when viewed from an axial direction of the case. According to the utility model discloses a compressor, compare with prior art, can reduce the part quantity that constitutes the casing to can reduce equipment time and operation man-hour.

Description

Compressor

Technical Field

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

Background

The 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.

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.

A reciprocating compressor is a type in which a compression space for sucking and discharging a working gas is formed between a piston and a cylinder, and the piston linearly reciprocates inside the cylinder to compress a refrigerant; a rotary compressor is a system in which a compression space for sucking and discharging a working gas is formed between a roller (roller) and a cylinder, and the roller eccentrically rotates along an inner wall of the cylinder to compress a refrigerant; a scroll compressor is a system in which a compression space for sucking and discharging a working gas is formed between an orbiting scroll (orbiting scroll) and a fixed scroll (fixed scroll), and the orbiting scroll compresses a refrigerant as the fixed scroll rotates.

Recently, in the reciprocating compressor, there has been an increasing development of a linear compressor in which a piston is directly connected to a driving motor performing a reciprocating linear motion, thereby improving mechanical efficiency without a mechanical loss due to motion conversion and having a simple structure.

The present applicant has previously filed patent laid-open publication No. 10-2017-0124889 (hereinafter, referred to as "prior art"), which is a prior document.

A linear compressor as a related art includes: a main body part provided with a mechanism structure; a case (casting) for protecting the main body from the outside; and a support portion that supports the main body portion between the main body portion and the housing.

The support portion includes: a pair of support springs disposed in front and rear of the main body; and a structure for fixing a pair of the support springs.

Further, the casing includes a cylindrical shell (shell) in which a terminal for transmitting an external power source to a motor assembly of the linear compressor is provided; a socket (receptacle) formed at the end of the lead wire connected with the motor of the compressor body is fastened with the terminal inside the cylindrical shell.

In the linear compressor of such a structure, the lead wire needs to be formed in an appropriate length so as not to be disconnected not only by vibration of the compressor but also to come into contact with the cylindrical shell and the compressor body.

Also, it is necessary to confirm whether the support portion is accurately assembled with the cylindrical housing by the naked eye.

Therefore, in the conventional linear compressor, the cylindrical shell includes a portion opened at both sides in the longitudinal direction of the shell, and the casing further includes a pair of shell covers (shell covers) covering the front and rear sides in the longitudinal direction of the shell.

In the linear compressor having such a structure, after the main body of the compressor is slightly pushed into the cylindrical casing, the one-side support portion (for example, the first support portion including the plate spring) is assembled to the one-side casing cover (for example, the first casing cover), and then the first casing cover is assembled to the cylindrical casing while being pushed to the first casing cover and the compressor body.

Then, the lead wire drawn out from the motor and the socket are connected to the connection terminal located at the cylindrical casing, and thereafter, a wire processing operation is performed so that the lead wire does not come into contact with the cylindrical casing and the compressor body.

Then, the other side case cover (for example, the second case cover) is assembled to the cylindrical case, and then the case assembly is completed by welding the parting surface between the first case cover and the cylindrical case and the parting surface between the second case cover and the cylindrical case.

As described above, in the linear compressor of the related art, since two housing covers need to be separately provided for socket assembly and lead wire processing, the number of parts constituting the housing is increased, and there is a problem in that assembly time and working man-hours are increased.

In contrast, in order to reduce the assembly time and the number of operations, it has been attempted to configure the casing of the linear compressor by using two casings separated vertically, as in the case of the casing of the general hermetic compressor.

Therefore, in the case where the housing is configured by two housings separated vertically, a problem arises in quality concerning socket assembly and lead wire contact, and it is therefore difficult to configure the housing by two housings separated vertically.

Prior Art

Patent document

Patent document 1: korean laid-open patent publication 10-2017-0124889A (Kokai: 2017.11.13)

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a be provided with the compressor of the casing that constitutes is come to two shells that utilize upper and lower isolating construction.

An object of the utility model is to provide a through make upper portion shell and lower part shell have the separating plane of slope, can make binding post set up in the compressor of lower part shell.

The utility model discloses a compressor of embodiment can include: a compressor body including a cylinder, a piston that reciprocates in the cylinder in an axial direction of a housing, and a driving unit that drives the piston; a housing surrounding the compressor body; a first support portion that supports a suction side of the compressor main body inside the casing; and a second support portion that supports the discharge side of the compressor body inside the casing.

At this time, the case may be constituted by a lower shell and an upper shell fixed to the lower shell, and a separation surface of the lower shell and the upper shell fixed to each other may be formed to be inclined with respect to a horizontal center line of the case when viewed from an axial direction of the case.

The inclination angle of the separation plane may be set within a range in which the connection terminal and the PTC cap can be mounted and the second support portion can be provided.

As an example, the inclination angle of the parting plane may be formed to be 20 ° to 70 ° with respect to a horizontal center line of the housing.

The lower casing and the upper casing may be provided at both sides thereof in the axial direction of the housing, respectively, with side walls.

The side wall may replace an existing housing cover.

At least either one of both side ends of the parting surface may be located on an upper side than a horizontal center line of the housing when viewed in an axial direction of the housing.

A terminal for supplying an external power to a motor assembly of the compressor may be provided at the lower housing, and the terminal may be provided at a position of the lower housing on a side of an end of the two side ends of the separating surface where a height is relatively higher.

The first and second support portions may include plate springs, respectively.

Unlike this, the first support part may include a plate spring, and the second support part may include: an axial support unit elastically deformed in the axial direction or a direction adjacent to the axial direction; and a radial support unit that elastically deforms in a radial direction perpendicular to the axial direction or in a direction adjacent to the radial direction.

The axial supporting unit may be interposed between the compressor body and one side wall of the lower casing.

One side of the axial supporting unit may be supported by the compressor body, and the other side of the axial supporting unit may be supported by one side wall of the lower casing; one side of the radial support unit may be supported to the compressor body, and the other side of the radial support unit may be supported to the body portion of the lower casing.

The compressor body may include a discharge cap assembly. A suction pipe for sucking a refrigerant may be connected to one side of the discharge cap assembly in the axial direction, a discharge pipe for discharging the refrigerant compressed in the cylinder may be connected to the other side of the discharge cap assembly in the axial direction, and a discharge space may be formed on the other side of the discharge cap assembly in the axial direction.

The axial support means may be axially or axially adjacent to the discharge cap assembly, and the radial support means may be radially or radially adjacent to the discharge cap assembly.

Here, the discharge cap may be formed with a support unit coupling portion protruding in an axial direction, one end of the axial support unit may be seated in a groove recessed at one side of the support unit coupling portion, and the radial support unit may be seated on an outer side surface of the support unit coupling portion.

At this time, the axial supporting unit may include a coil spring (coil spring), and one end of the coil spring may be seated in a groove of the supporting unit coupling portion.

The radial support unit may include: a coupling member coupled to the compressor body; a leg portion connected to the coupling member and extending in a radial direction or a direction adjacent to the radial direction; a spring support portion provided at an end of the leg portion; and a spring supported by the spring support portion and contracted in a radial direction or a direction adjacent to the radial direction.

At this time, the spring may be disposed such that its contractible length is greater than its outer diameter.

Alternatively, the axial support unit may include a coil spring: the outer diameter of the coil spring is the same as the contractible length thereof, or the contractible length of the coil spring is smaller than the outer diameter thereof.

In addition, the radial support unit may include a coil spring that is compressed in a direction parallel to a load direction of the compressor body when viewed from an axial direction of the housing.

Here, the coil spring may be provided such that its contractible length is greater than its outer diameter.

The axial support unit may include a coil spring compressed in a direction parallel to a driving direction of the compressor body when viewed from an upper portion.

The radial support unit may include a plurality of coil springs that are compressed in a direction that is offset (inclined) by a predetermined angle from a load direction of the compressor body when viewed in an axial direction of the housing, and the plurality of coil springs may be arranged in a direction facing the load direction.

The radial support unit may include: a coupling member coupled to the compressor body; a leg portion connected to the coupling member and extending in a radial direction or a direction adjacent to the radial direction; a spring support portion provided at an end of the leg portion; and a coil spring that is supported by the spring support portion and contracts in a radial direction or a direction adjacent to the radial direction.

Here, the pair of radial support units may be formed so as to be disposed at angles facing each other with respect to the load direction.

One side of the leg portion may be connected to the coupling member, the other side of the leg portion may be branched and extended at an angle opposite to the load bearing direction, and a plurality of the spring support portions and the coil springs may be provided so as to correspond to the branched leg portions.

In the compressor of the present invention, the shell is composed of a lower shell and an upper shell, and, when viewed from the axial direction, the portions of the lower shell and the upper shell fixed to each other, that is, the parting plane, are inclined with respect to the horizontal center line of the shell, whereby it is possible to mount, to the lower shell, components such as the compressor body, the first supporting portion and the second supporting portion for supporting the compressor body, the connection terminal for supplying power to the motor assembly of the compressor body, and the like.

Therefore, the number of components constituting the housing can be reduced as compared with the related art, and the assembly time and the working man-hour can be reduced.

Drawings

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

Fig. 2 is a left side view of the compressor in fig. 1 as viewed from the discharge side.

Fig. 3 is a view showing a state in which a partition wall is omitted from the compressor of fig. 2.

Fig. 4 is a sectional view for explaining an internal structure of a compressor according to an embodiment of the present invention.

Fig. 5 is a sectional view for explaining an internal structure of a compressor according to another embodiment of the present invention.

Fig. 6 is a perspective view showing a first support spring according to an embodiment of the present invention.

Fig. 7 is a front view showing a second support spring according to an embodiment of the present invention.

Fig. 8 is a sectional view showing a coupling structure of the axial direction supporting unit.

Fig. 9 is an exploded perspective view of the second support spring.

Fig. 10 is a view showing a radial support unit according to a first embodiment of the present invention.

Fig. 11 is a view showing a modified example of the radial support unit in fig. 10.

Fig. 12 is a front view showing a second support spring for explaining a radial support unit according to a second embodiment of the present invention.

Fig. 13 is a front view showing a radial support unit according to a second embodiment of the present invention.

Fig. 14 is a front view showing a second support spring for explaining a radial support unit according to a third embodiment of the present invention.

Fig. 15A and 15B are graphs showing vibration levels based on the rigidity of the supporting spring.

Detailed Description

Hereinafter, embodiments disclosed in the present invention will be described in detail with reference to the accompanying drawings, and the same or similar constituent elements will be given the same reference numerals regardless of the figure number, and repeated description thereof will be omitted.

In describing the embodiments disclosed herein, 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. The "plurality" in the present specification may mean two or more.

In describing the embodiments disclosed in the present invention, when it is determined that a specific description of a related known technology would make the gist of the embodiments disclosed in the present invention unclear, a detailed description thereof will be omitted.

In addition, the drawings are provided to facilitate understanding of the embodiments of the present disclosure, and the technical idea of the present disclosure is not limited to the drawings, and the present disclosure includes all modifications, equivalents, and substitutes made within the technical idea and technical scope of the present disclosure.

On the other hand, the terms in the present invention may be replaced with terms such as document (document), specification (specification), description (description), and the like.

Next, a description will be given of a linear compressor according to the present invention, as an example, in which an operation of sucking and compressing a fluid while linearly reciprocating a piston and discharging the compressed fluid is performed.

The linear compressor may be a component of a refrigeration cycle, and the fluid compressed in the linear compressor may be a refrigerant circulating in the refrigeration cycle.

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

Fig. 1 is an external perspective view of a compressor according to the present invention, fig. 2 is a left side view of the compressor in fig. 1 as viewed from a discharge side, and fig. 3 is a view showing a state in which a partition wall is omitted from the compressor in fig. 2.

Referring to fig. 1 to 3, the linear compressor 100 of the present invention is provided with a casing 110 surrounding a compressor body.

The case 110 may be composed of a lower case 111 and an upper case 112 fixed to the lower case 111; a Separation Plane (SP) of the lower casing 111 and the upper casing 112 fixed to each other may be formed to be inclined with respect to a Horizontal Center Line (HCL) of the casing 110 when viewed from an axial direction of the casing 110.

The inclination angle θ of the separation plane SP with respect to the horizontal center line HCL may be set within a range in which the line terminal 30 and the PTC cap may be mounted and the second support portion may be provided.

As an example, the inclination angle θ of the separation plane SP may be formed to be 20 ° to 70 ° with respect to the horizontal center line HCL of the housing 110.

At least either one of both side ends of the separation surface SP may be located on an upper side than a horizontal center line HCL of the housing 110 when viewed in the axial direction of the housing 110.

That is, in fig. 1 to 3, the case where the right-side end portion of the both side end portions of the separation surface SP is located on the upper side of the horizontal center line HCL and the left-side end portion of the both side end portions of the separation surface SP is located on the lower side of the horizontal center line HCL has been described as an example, but the left-side end portion may be located on the upper side of the horizontal center line HCL.

A leg portion 20 may be coupled to the lower side of the lower housing 111. The leg 20 may be coupled to a base of a product for installing the linear compressor 100.

For example, the product may comprise a refrigerator and the base may comprise a machine compartment base of the refrigerator. As another example, the product may include an outdoor unit of an air conditioner, and the base may include a base of the outdoor unit.

With reference to fig. 1, the lower casing 111 extends long in the lateral direction, and a central axis of the lower casing 111 in the longitudinal direction coincides with a central axis of a compressor main body described later, and the central axis of the compressor main body coincides with central axes of a cylinder and a piston constituting the compressor main body.

A connection terminal 30 may be provided at a side of the outer surface of the lower case 111 where the height of the separation plane SP is relatively high, and a socket LW1 connected to an end of a Lead Wire (Lead Wire) LW may be connected to the connection terminal 30.

Here, it is understood that the height refers to a distance in the vertical direction starting from the leg portion 20.

The terminal 30 is a component for supplying an external power to a motor assembly (refer to the driving unit 130 of fig. 4) of the linear compressor 100. In particular, the connection terminal 30 may be connected to a lead wire of a coil (refer to 132b of fig. 4).

Outside the connection terminal 30, a PTC cap 31 for protecting the connection terminal 30 is provided.

The lower casing 111 may be provided with Side walls (Side Wall) SW1 on both sides in the axial direction of the casing 110, and the upper casing 112 may be provided with Side walls SW2 on both sides in the axial direction of the casing 110.

The side walls SW1, SW2 may replace existing housing covers. That is, the right side wall SW1 of the lower casing 111 and the right side wall SW2 of the upper casing 112 may replace an existing suction side casing cover, and the left side wall SW1 of the lower casing 111 and the left side wall SW2 of the upper casing 112 may replace an existing discharge side casing cover.

Therefore, an upper portion of the lower housing 111 facing the upper housing 112 is open, and a lower portion of the upper housing 112 facing the lower housing 111 is open.

Accordingly, when the lower shell 111 and the upper shell 112 are fixed to each other at the separation plane SP by welding or the like, the internal space of the case 110 can be sealed.

The one side wall SW1 is positioned on the suction side of the refrigerant, and for example, the right side wall SW1 with reference to fig. 1 is positioned on the suction side of the refrigerant; the other side wall SW1 is positioned on the refrigerant discharge side, and for example, the left side wall SW1 with reference to fig. 1 is positioned on the refrigerant discharge side.

The linear compressor 100 may further include a plurality of

pipes

114 and 115, and the plurality of

pipes

114 and 115 may be provided in the lower shell 111 and may be capable of sucking, discharging, and injecting a refrigerant.

The plurality of

pipes

114 and 115 include a suction pipe 114 for sucking the refrigerant into the linear compressor 100 and a discharge pipe 115 for discharging the compressed refrigerant from the linear compressor 100.

Although not shown, the compressor may further include a supplementary pipe for supplementing the refrigerant to the linear compressor 100.

The suction pipe 114 may be combined with a right side wall of the lower housing 111. The refrigerant may be sucked into the interior of the linear compressor 100 in the axial direction via the suction pipe 114.

The discharge pipe 115 may be combined with the outer circumferential surface of the lower housing 111. The refrigerant sucked through the suction pipe 114 may be compressed while flowing in the axial direction of the compressor.

The compressed refrigerant can be discharged through the discharge pipe 115. The discharge pipe 115 may be disposed closer to the left side wall than the right side wall of the lower housing 111.

Inside the lower shell 111, means for supporting the compressor body may be provided. Here, the compressor body refers to a member provided inside the casing 111, and may include, for example: a driving part reciprocating in the front-back direction; and a support portion for supporting the driving portion.

Fig. 4 is a sectional view for explaining an internal structure of the compressor 100 according to the embodiment of the present invention.

Referring to fig. 4, the compressor body includes: 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.

Also, 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 compressor body may be elastically supported by support springs 116 and 117 provided at both inner ends of the casing 110.

The support spring may be provided with: a first support spring 116 for supporting the rear (suction side) of the body; and a second support spring 117 for supporting the front (discharge side) of the body, which may be a plate spring.

In addition, the supporting

springs

116, 117 may absorb vibration and impact occurring with the reciprocation of the piston 150.

The closed space formed by the case 110 may be formed as: an accommodation space 101 for accommodating the sucked refrigerant; a suction space 102 for filling the refrigerant before being compressed; a compression space 103 for compressing a refrigerant; and a discharge space 104 for filling the compressed refrigerant.

That is, the refrigerant sucked in through 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 and discharged to the discharge space 104, and then discharged to the outside through the discharge pipe 115 connected to the front side of the casing 110.

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

In the center of the right side wall of the lower housing 111, a suction pipe 114 may be inserted and coupled.

The rear side of the compressor body is elastically supported in the radial direction by the right side wall of the lower casing 111 by the first support spring 116.

The first support spring 116 may be a circular plate spring, and an edge portion of the first support spring 116 may be supported in the front direction to the rear cover 123 by the support bracket 123 a; the opened central portion of the first support spring 116 may be supported in the rear direction by the right side wall of the lower housing 111 through the suction guide 116 a.

The suction guide 116a is formed in a cylindrical shape having a through flow path provided therein. A central opening portion of the first support spring 116 may be coupled to an outer peripheral surface of the suction guide 116a on the front side, and a rear side end portion of the suction guide 116a may be supported by a right side wall of the lower housing 111.

At this time, an additional suction side support member 116b may be interposed between the suction guide 116a and the inner side surface of the right side wall of the lower housing 111.

The suction guide 116a is communicated at the rear side with the suction pipe 114, and the refrigerant sucked through the suction pipe 114 may pass through the suction guide 116a and flow into the muffler unit 160.

A damping member 116c formed of a rubber material or the like may be provided between the suction guide 116a and the suction side support member 116 b.

This can block transmission of vibration generated during suction of the refrigerant through the suction pipe 114 to the right side wall of the lower housing 111.

The discharge pipe 115 may be inserted through the annular pipe 115a and coupled to the lower housing 111. 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 annular pipe 115a and the discharge pipe 115.

The front side of the compressor body may be elastically supported in the radial direction by the lower casing 111 or the left side wall of the lower casing 111 by the second support spring 117.

The second support spring 117 may be a circular plate spring, a central portion of the second support spring 117 having an opening may be supported in the rear direction by the discharge cap assembly 180 via the first support guide 117b, and an edge portion of the second support spring 117 may be supported in the radial direction by an inner side surface of the lower case 111 or an inner peripheral surface of the lower case 111 adjacent to a left side wall of the lower case 111 via the support bracket 117 a.

Alternatively, unlike the drawing, the edge portion of the second support spring 117 may be supported in the front direction by a bracket (not shown) on the left side wall of the lower housing 111.

The first support guides 117b may be formed in a continuous cylindrical shape having different diameters from each other, a front side of the first support guides 117b may be inserted into a central opening of the second support spring 117, and a rear side of the first support guides 117b may be inserted into a 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 117c, and a cup-shaped third support guide 117e recessed rearward may be coupled to the inner side of the left side wall of the lower housing 111, the third support guide 117e corresponding to the second support guide 117 d.

The second support guide 117d may be inserted into the inside of the third support guide 117e and supported in the axial and radial directions. At this time, a gap (gap) may be formed between the second and third support guides 117d and 117 e.

The frame 120 includes: a body 121 for supporting the outer circumferential surface of the cylinder 140; and a flange portion 122 connected to one side of the body portion 121 and supporting the driving unit 130.

Further, 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 121 may be formed in a cylindrical shape surrounding the outer peripheral surface of the cylinder tube 140, and the flange 122 may be formed to extend radially from the front end of the body 121.

A cylinder 140 may be coupled to an inner circumferential surface of the body part 121, and an inner stator 134 may be coupled to an outer circumferential surface of the body part 121.

For example, the cylinder 140 may be press-fitted (fixed) to the inner circumferential surface of the body portion 121, and the inner stator 134 may be fixed to the outer circumferential surface of the body portion 121 by a fixing ring.

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

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

The bearing inlet groove may be recessed by a predetermined depth in the axial direction, and the bearing communication hole may be a hole having a cross-sectional area smaller than that of the bearing inlet groove, and may be formed to be inclined toward the inner circumferential surface of the body portion 121.

The gas groove 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 grooves may be formed on the outer circumferential surface of the cylinder tube 140 that contacts the inner circumferential surface of the body portion 121, or may be formed on both the inner circumferential surface of the body portion 121 and the outer circumferential surface of the cylinder tube 140.

Further, a gas inlet 142 corresponding to the gas groove may be formed on the outer circumferential surface of the cylinder 140. The gas inlet 142 forms a kind of nozzle portion in 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 open, the piston 150 may be inserted through the rear end of the cylinder 140, and the front end of the cylinder 140 may be closed by the discharge valve assembly 170.

A compression space 103 may be formed in a space surrounded by the cylinder 140, the front end 151 (head) of the piston 150, and the discharge valve assembly 170.

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 is compressed as the piston 150 advances, and is discharged through the discharge valve assembly 170.

The front end of the cylinder 140 may be bent outward to form a flange 141. The flange portion 141 of the cylinder 140 may be coupled to the frame 120.

For example, a flange groove corresponding to the flange portion 141 of the cylinder 140 may be formed at the front side end portion of the frame 120, and the flange portion 141 of the cylinder 140 may be inserted into the flange groove and coupled by a mechanical coupling member.

In another aspect, there may also be provided: and a gas bearing unit which supplies the discharged gas to a gap between the outer peripheral surface of the piston 150 and the outer peripheral surface of the cylinder 140, thereby allowing gas lubrication between the cylinder 140 and the piston 150.

The spit gas between the cylinder 140 and the piston 150 can provide a floating force to the piston 150, thereby reducing friction between the piston 150 and the cylinder 140.

For example, the cylinder tube 140 may be formed with a gas inlet 142, and the gas inlet 142 communicates with a gas groove formed in the inner circumferential surface of the body portion 121 and penetrates the cylinder tube 140 in the radial direction, so that the compressed refrigerant flowing into the gas groove can be guided between the inner circumferential surface of the cylinder tube 140 and the outer circumferential surface of the piston 150.

The gas grooves may be formed on the outer circumferential surface of the cylinder 140 in consideration of convenience of processing.

The inlet of the gas inflow port 142 may be formed to be relatively wide, and the outlet of the gas inflow port 142 may be formed as a fine through-hole to function as a nozzle.

A filter (not shown) for blocking the inflow of foreign substances may be further provided at an inlet 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, the inlet of the gas inlet 142 may be formed as a circular groove, and the outlet of the gas inlet 142 may be formed in plurality at predetermined intervals along the circular groove.

The gas inlet 142 may be formed only on the front side with respect to the axial middle of the cylinder 140, or may be formed at the rear side in combination in consideration of the sagging of the piston 150.

The piston 150 is inserted into the cylinder 140 from an open end at the rear of the cylinder 140, and seals the rear of the compression space 103.

The piston 150 includes a head portion 151 that is formed in a disc shape and partitions the compression space 103, and a cylindrical guide portion 152, the guide portion 152 extending rearward from an outer circumferential surface of the head portion 151.

The head 151 is partially opened, and the guide 152 is formed to have a hollow interior. The front of the guide 152 is partially sealed by the head 151, and the rear of the guide 152 is opened and connected to the muffler unit 160.

The head part 151 and the guide part 152 may be additional members coupled to each other, or the head part 151 and the guide part 152 may be formed as one body.

Also, a suction port 154 may be formed in the head portion 151 of the piston 150, and the suction port 154 penetrates the head portion 151.

The suction port 154 is used to communicate the suction space 102 and the compression space 103 inside the piston 150.

Therefore, 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. Alternatively, 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 in a direction away from the center axis toward the rear of the piston 150.

Also, the suction port 154 is formed as a circular opening, and the inner diameter of the suction port 154 may be formed to be fixed.

Alternatively, the suction port 154 may be formed as an elongated hole-shaped opening extending in the radial direction of the head 151, or may be formed such that the inner diameter thereof gradually increases toward the rear.

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

A suction valve 155 that selectively opens and closes the suction port 154 may be installed in the head portion 151 of the piston 150 adjacent to the compression space 103.

The suction valve 155 can be actuated by elastic deformation, thereby opening or closing the suction port 154.

That is, the suction valve 155 may be elastically deformed by the pressure of the refrigerant passing through the suction port 154 and flowing to the compression space 103 to open the suction port 154.

The piston 150 is connected to a mover (mover)135, and the mover 135 can reciprocate in the front and rear directions as the piston 150 moves.

The inner stator 134 and the cylinder 140 may be located between the moving member 135 and the piston 150.

Also, 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 is combined with the rear of the piston 150, thereby being capable of attenuating noise generated in a process of sucking 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 includes: 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 coupled to the rear of the piston 150.

The suction muffler 161 may form a flow path in the axial direction, thereby being capable of guiding the refrigerant in the receiving space 101 to the suction space 102 inside the piston 150.

At this time, 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 joining two or more members to each other, and for example, a second suction muffler is press-fitted and joined to the inside of the first suction muffler, thereby forming a plurality of noise spaces. Also, the suction muffler 161 may be formed of a plastic material in consideration of the weight or insulation of the suction muffler 161.

The inner guide 162 may be a pipe shape having one side communicating with the noise space of the suction muffler 161 and the other side deeply inserted into the inside of the piston 142.

The inner guide 162 may have a cylindrical shape having the same inner diameter at both ends, and may be formed such that the inner diameter of the front end on the discharge side is larger than the inner diameter of the rear end on the opposite side in some cases.

The suction muffler 161 and the inner guide 162 may be formed in various shapes, thereby adjusting the pressure of the refrigerant passing through the muffler unit 160. Also, the suction muffler 161 and the inner guide 162 may 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 is understood to be a space formed between the suction valve 155 and the discharge valve 171.

The discharge valve 171 may be disposed to be supportable on the front surface of the cylinder 140 and installed to selectively open and close the front opening of the cylinder 140.

The discharge valve 171 can be operated by elastic deformation, thereby opening or closing the compression space 103.

The discharge valve 171 is elastically deformable so as to open the compression space 103 by the pressure of the refrigerant passing through the compression space 103 and flowing to the discharge space 104.

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 through an open space in a state where the discharge valve 171 is spaced apart from the front surface of the cylinder 140.

The valve spring 172 is disposed between the discharge valve 171 and the discharge cap assembly 180, and provides an elastic force in the axial direction.

The valve spring 172 may be a compression coil spring, and 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 is deformed forward, thereby opening the discharge valve 171, and the refrigerant can be discharged from the compression space 103 and discharged into the first discharge space of the discharge cap assembly 180.

Further, 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.

Next, 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 is equal to or higher than the preset discharge pressure, the valve spring 172 is deformed forward, and the discharge valve 171 connected thereto is opened, whereby 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 provides 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, and form a discharge space 104 for receiving the refrigerant discharged from the compression space 103. Further, the discharge cap assembly 180 may be coupled to the front of the frame 120, thereby attenuating noise generated during the discharge of the refrigerant from the compression space 103.

The discharge cap assembly 180 may receive the discharge valve assembly 170 and be coupled to a front side of the flange portion 122 of the frame 120.

For example, the discharge cap assembly 180 may be coupled to the 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 for thermal insulation; and an O-ring (O-ring) 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 a plurality of discharge caps are provided, 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 formed between the first discharge cap 181 and the frame 120, the first discharge cap 181 being coupled to a front side of the frame 120; a second discharge space formed between the second discharge cap 182 and the first discharge cap 181, the second discharge cap 182 communicating with the first discharge space and coupled to a front side of the first discharge cap 181; and a third discharge space formed between the third discharge cap 183 and the second discharge cap 182, the third discharge cap 183 communicating with the second discharge space and being coupled to the front side of the second discharge cap 182.

The first discharge space may selectively communicate with the compression space 103 through the discharge valve 171, the second discharge space may communicate with the first discharge space, and the third discharge space may communicate with the second discharge space.

Accordingly, the refrigerant discharged from the compression space 103 passes through the first discharge space, the second discharge space, and the third discharge space in this order, and the discharge noise thereof is attenuated, and is discharged to the outside of the casing 110 through the annular pipe 115a and the discharge pipe 115 communicating with the third discharge cap 183.

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 case 110 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 moving member 135 disposed between the outer stator 131 and the inner stator 134.

The outer stator 131 may be coupled to the rear of the 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 be provided with 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 includes: 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 circular or polygonal, and may be hexagonal, for example.

The stator core 133 may be formed by radially laminating a plurality of laminate sheets (lamination sheets), or may be formed by laminating a plurality of laminate blocks (lamination blocks) in the circumferential direction.

The front side of the outer stator 131 may be supported by the 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 have a disc shape whose inside is hollow, the outer stator 131 may be supported at a front surface of the stator cover 137, and the resonant spring may be supported at a rear surface of the stator cover 137.

The inner stator 134 may be formed by laminating a plurality of lamination plates on the outer circumferential surface of the body portion 121 of the frame 120 along 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 coupling portion 136a, and the coupling portion 136a may be coupled to a third flange 153 formed at the rear of the piston 150.

The 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.

A fourth flange portion 161a formed in front of the suction muffler 161 may be interposed between the third flange portion 153 of the piston 150 and the coupling portion 136a of the magnet frame 136.

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 the 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 springs in the axial direction.

The resonant spring 118 can effectively achieve compression of the refrigerant by increasing vibration generated by the reciprocating motion of the mover 135 and the piston 150.

Specifically, the piston 150 can be moved in resonance by adjusting the vibration frequency of the resonance spring 118 to the natural vibration frequency corresponding to 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 vibrating 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 can be elastically deformed between the vibrating body and the fixed body.

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, the rear cover 123, which is a fixed body, is elastically supported by the housing 110 by the first support spring 116, and is not strictly speaking fixed.

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

The spring support 119 may include: a body portion 119a surrounding the suction muffler 161; a 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 main body portion 119 a.

The front surface of the coupling portion 119b of the spring support 119 may be supported by the coupling portion 136a of the magnet frame 136.

The inner diameter of the combining portion 119b of the spring supporter 119 may surround the outer diameter of the suction muffler 161.

For example, the coupling portion 119b of the spring supporter 119, the 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 described above, the fourth flange portion 161a of the suction muffler 161 may be interposed between the third flange portion 153 of the piston 150 and the 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 support 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 central 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.

On the other hand, the compressor 100 may include a plurality of sealing members for increasing a coupling force between the frame 120 and a plurality of components at the periphery thereof.

For example, the plurality of sealing members may include: a first sealing member interposed between a portion where the frame 120 and the discharge cap assembly 180 are coupled to each other and inserted into a mounting groove provided at a front end of the frame 120; and a second sealing member provided to a portion where the frame 120 and the cylinder 140 are combined, and inserted into a mounting groove provided to an outer side surface of the cylinder 140.

The second sealing member can prevent the refrigerant of the air 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 of the frame 120 and the cylinder 140.

Also, 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 be ring-shaped.

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 can linearly reciprocate using the generated electromagnetic force.

Such an electromagnetic force is generated in both a direction (forward direction) in which the piston 150 faces a Top Dead Center (TDC) when a compression stroke is performed, and a direction (rearward 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 mover 135 and the piston 150 in 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 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, which flows into the receiving space 101 inside the compressor 100 via the suction pipe 114, flows into the suction space 102 inside the piston 150 through the suction guide 116a, the suction muffler 161, and the inner guide 162 in order, 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.

During the compression stroke of the piston 150, the refrigerant in 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 ring pipe 115a and the discharge pipe 115

Fig. 5 is a sectional view for explaining a structure of a compressor 100-1 according to another embodiment of the present invention.

Referring to fig. 5, the compressor 100-1 includes a discharge cap assembly 190 and a discharge valve assembly.

The discharge cap assembly 190 is formed with a discharge space 104 for accommodating the refrigerant discharged from the compression space 103. The discharge cap assembly 190 includes: a discharge cap 184 coupled to the front surface of the frame 120; and a discharge chamber (plenum)185 disposed inside the discharge cap 184.

The discharge cap assembly 190 may further include: a cylindrical fixing ring 186 closely attached to the inner peripheral surface of the discharge chamber 185.

The discharge valve assembly is coupled to the inside of the discharge cap assembly 190, and discharges the refrigerant compressed in the compression space 103 to the discharge space 104.

And, the discharge valve assembly may include: a discharge valve 171; and a spring assembly 175 for providing an elastic force in a direction in which the discharge valve 171 is brought into close contact with the front end of the cylinder 140.

The spring assembly 175 may include: a valve spring 172 having a plate spring form; a spring support 173 located at an edge of the valve spring 172 and supporting the valve spring 172; and a friction ring 174 fitted over an outer circumferential surface of the spring support 173.

The front center portion of the discharge valve 171 is fixed and coupled to the center of the valve spring 172. The rear surface of the discharge valve 171 is in close contact with the front surface (or the front end) of the cylinder 140 by the elastic force of the valve spring 172.

When the pressure in the compression space 103 is equal to or higher than the discharge pressure, the valve spring 172 is elastically deformed in the direction toward the discharge chamber 185.

Further, the discharge valve 171 is spaced from the distal end portion of the cylinder 140, whereby the refrigerant can be discharged from the compression space 103 toward the discharge space 104 formed inside the discharge chamber 185.

That is, when the discharge valve 171 is supported on the front surface of the cylinder 140, the compression space 103 is kept in a sealed state, and when the discharge valve 171 is spaced from the front surface of the cylinder 140, the compression space 103 is opened, and the compressed refrigerant in the compression space 103 can be discharged.

The compression space 103 may be understood as a space formed between the suction valve 155 and the discharge valve 171.

And, the suction valve 155 may be formed at one side of the compression space 103; the discharge valve 171 may be disposed at the other side of the compression space 103, i.e., at the opposite side of the suction valve 155.

When the pressure in the compression space 103 becomes equal to or lower than the suction pressure of the refrigerant while the piston 150 is linearly reciprocating inside the cylinder 140, the suction valve 155 is opened, and the refrigerant flows into the compression space 103.

Conversely, if the pressure in the compression space 103 exceeds the suction pressure of the refrigerant, the suction valve 155 is closed, and the refrigerant in the compression space 103 is compressed by the forward movement of the piston 130.

On the other hand, when the pressure in the compression space 103 is set to be higher than the pressure in the discharge space 104 (discharge pressure), the valve spring 172 is deformed forward, and the discharge valve 171 is separated from the cylinder 140.

The refrigerant in the compression space 103 is discharged into the discharge space 104 formed in the discharge chamber 185 via the space defined between the discharge valve 171 and the cylinder 140.

When the discharge of the refrigerant is completed, the valve spring 172 provides a restoring force to the discharge valve 171, and the discharge valve 171 comes into close contact with the tip of the cylinder 140 again.

In addition, the linear compressor 100-1 may further include: a loop pipe (loop pipe)115a connected to the discharge pipe 115.

The annular pipe 115a discharges the refrigerant flowing to the discharge cap assembly 190 to the outside.

At this time, one end of the ring pipe 115a is coupled to the discharge cap 184, and the other end thereof is coupled to the discharge pipe 115. At least a portion of the annular tube 115a may be formed of a flexible material and bent and extended along the inner circumferential surface of the housing 110.

In addition, the linear compressor 100-1 may further include an axial support unit 210 and a radial support unit 200 for supporting a front end portion of the compressor body.

The axial support unit 210 may be provided between the left partition wall of the lower housing 111 and the discharge cap 184 in parallel with the axial direction.

The axial support unit 210 has one end supported by a mounting groove 113a, and the other end supported by a mounting groove 184a, the mounting groove 113a being recessed from the rear toward the front of the left side wall of the lower housing 111, and the mounting groove 184a being recessed from the front toward the rear of the discharge cap 184.

The axial support unit 210 is provided so as to be able to compress and stretch in the axial direction, and is able to support a load (load) in the axial direction, thereby being able to reduce vibration.

The radial support unit 200 may be disposed between the discharge cap 184 and the housing 110 in a direction perpendicular to the axial direction.

One end of the radial support unit 200 may be supported on an outer circumferential surface of a support unit coupling portion 184b, the support unit coupling portion 184b protruding toward the front of the discharge cap 184, and the other end of the radial support unit 200 may be supported on an inner circumferential surface of the lower housing 111 or an inner circumferential surface of a left side wall of the lower housing 111.

Also, the radial direction supporting unit 200 may be configured to be able to compress and stretch in the radial direction and to be able to support a load in the vertical direction, so that vibration can be reduced.

At this time, unlike the drawing, the radial direction support unit 200 may be arranged along a direction inclined forward at a predetermined angle from a direction perpendicular to the axial direction.

That is, the radial support unit 200 may be disposed to be inclined such that the lower portion thereof is located forward of the upper portion thereof.

In addition, the radial support unit 200 may include: and a support unit arranged along a plurality of directions.

For example, the pair of radial support units 200 may be arranged in a state of being opened at an angle in a range of 90 to 120 degrees, thereby supporting the discharge cap assembly 190.

On the other hand, the left side wall of the lower housing 111 may be provided in a shape that prevents interference with the support unit 200.

In addition, the linear compressor 100-1 may include: a plurality of sealing members for increasing coupling force between the frame 120 and components around the frame 120. For example, the plurality of sealing members may have a ring shape.

Fig. 6 is a perspective view showing the first support spring 116 according to the embodiment of the present invention.

The first support spring 116 of embodiments of the present invention may be a plate spring.

Since the first supporting spring 116 supports one side of the compressor body, the drooping phenomenon can be reduced. If the droop phenomenon of the compressor body is reduced, the body and the shell 110 can be prevented from colliding during the operation of the compressor.

The first support spring 116 may be coupled to the right side wall of the lower case 111 through a suction guide 116a and a suction side support member 116 b.

The suction guide 116a is combined with the center portion of the first support spring 116, and the suction side support member 116b is combined with the rear of the suction guide 116a and fixed to the right side wall of the lower case 111.

The first supporting spring 116 is disposed with its central axis parallel to the axial direction of the compressor body, and the plate spring is installed to be disposed in a direction perpendicular to the axial direction.

From the characteristics of the plate spring, it can have a large lateral rigidity (rigidity in the direction perpendicular to the axial direction of the compressor body) and a small longitudinal rigidity (rigidity in the axial direction of the compressor body).

For example, the longitudinal stiffness of the leaf spring may be about 1:10 relative to the lateral stiffness. Here, the longitudinal rigidity refers to rigidity of the plate spring in the axial direction, and the lateral rigidity refers to rigidity of the plate spring in the width direction.

As such, the plate spring has a large lateral rigidity, and therefore may adversely affect vibration and noise characteristics. This is because the smaller the rigidity of the spring, the better the vibration and noise characteristics.

The rubber packing member is press-fitted into and bonded to the inner side of the leaf spring, but since there is no structure for preventing the leaf spring and the rubber packing member from rotating, there is a possibility that the rubber packing member rotates relative to the leaf spring.

Thereby, there is a possibility that the compressor body rotates, and vibration in the radial direction of the compressor body may become large. If the vibration in the radial direction of the compressor body becomes large, there is a risk that the compressor body collides with the casing.

Fig. 7 is a front view showing the second support spring 117 according to the embodiment of the present invention, and fig. 8 is a sectional view showing a coupling structure of the axial direction support unit 210. Fig. 9 is an exploded perspective view of the second support spring 117.

Referring to fig. 7 to 9, the second supporting spring 117 according to the embodiment of the present invention is a structure including a coil spring (coil spring). In this manner, the problem of the plate spring described above can be solved by using the coil spring.

Although the coil spring may vary depending on the design, it may generally have a characteristic of a longitudinal rigidity to a transverse rigidity of about 1:0.3 to 1: 1.2. Here, the longitudinal rigidity refers to the rigidity of the coil spring in the direction in which the coil spring is compressed, and the lateral rigidity refers to the rigidity of the coil spring in the circumferential direction.

If a plate spring is used as the second support spring 117, the lateral rigidity of the plate spring is large, and therefore, the vibration characteristics in the load direction of the compressor body are deteriorated.

However, when the coil spring is used as the second support spring 117, the coil spring has a small vertical rigidity, and therefore, the vibration characteristics in the load direction can be improved.

The second support spring 117 may include an axial support unit 210 and a radial support unit 200.

The axial support unit 210 may be disposed parallel to the axial direction between the left side wall of the lower housing 111 and the discharge cap 184.

The axial support unit 210 has one end supported by a mounting groove 113a, and the other end supported by a mounting groove 184a, the mounting groove 113a being recessed from the rear to the front of the left side wall of the lower housing 111, and the mounting groove 184a being recessed from the front to the rear of the discharge cap 184.

The axial support unit 210 is provided so as to be able to be compressed and extended in the axial direction, and is able to support a load (load) in the axial direction, thereby being able to reduce vibration.

On the other hand, the axial support unit 210 is disposed adjacent to the axial direction. For example, the light source may be disposed so as to be inclined in the vertical direction.

However, when the axial support unit 210 is inclined while being deviated from the vertical direction when viewed from the axial front, the vibration in the width direction may be deteriorated, which is not preferable.

Further, a mounting groove 184a for receiving the rear end of the axial support unit 210 may be provided in front of the discharge cap 184.

For example, the mounting groove 184a may be a groove recessed in a circular shape corresponding to the outer diameter of the rear portion of the axial support unit 210.

The mounting groove 184a may be formed on the front surface of the supporting unit coupling portion 184b protruding forward from the discharge cap 184. One end of the axial supporting unit 210 is inserted into and supported by the mounting groove 184a of the discharge cap 184, and movement in the radial direction is restricted.

A mounting groove 113a may be formed at a left side wall of the lower housing 111, and a front end of the axial support unit 210 is received behind the mounting groove 113 a.

For example, the mounting groove 113a may be a groove recessed in a circular shape corresponding to the outer diameter of the front portion of the axial support unit 210.

The axial support unit 210 may have an optimized axial length and stiffness.

The axial length and stiffness may be selected as: when compressed, the left side wall of the lower housing 111 does not collide with the discharge cap 184, and the degree of vibration can be reduced while supporting the load of the main body.

The radial support unit 200 may be disposed between the discharge cap 184 and the lower housing 111 in a direction perpendicular to the axial direction.

One end of the radial support unit 200 may be supported on the outer circumferential surface of the support unit coupling portion 184b protruding toward the front of the discharge cap 184, and the other end of the radial support unit 200 may be supported on the inner circumferential surface of the lower housing 111.

The radial support unit 200 is provided to be able to compress and stretch in the radial direction, and supports a load in the vertical direction, thereby being able to reduce vibration.

In this case, unlike the drawings, the radial support unit 200 may be arranged in a direction inclined at a predetermined angle from a direction perpendicular to the axial direction toward the front. That is, the radial support unit 200 may be disposed to be inclined such that the lower portion thereof is located forward of the upper portion thereof.

On the other hand, the radial support unit 200 may be disposed adjacent to the radial direction. For example, the inclined surface may be arranged to be inclined in the axial direction, or may be arranged to be inclined forward when viewed from the side.

However, when only one radial support unit 200 is provided, it is not preferable that the vibration in the width direction be deteriorated if the unit is disposed to be deviated from the vertical direction and inclined when viewed from the front in the axial direction.

However, when a plurality of radial support units 200 are symmetrically arranged in the width direction, such a risk can be eliminated.

In addition, the radial direction supporting unit 200 may include a plurality of supporting units arranged along a direction symmetrical with respect to the vertical direction.

For example, the pair of support units may be arranged to support the discharge cap 184 in a state of being opened at an angle in a range of 90 to 120 degrees when viewed from the axial direction.

On the other hand, the left side wall of the lower housing 111 may be formed in a shape that prevents interference with the radial direction support unit 200.

A support unit coupling portion 184b may be formed in front of the discharge cap 184, and one end of the radial support unit 200 may be coupled to the support unit coupling portion 184 b.

For example, the support unit coupling portion 184b may protrude from the front surface of the discharge cap 184 in a cylindrical shape, and the diameter of the support unit coupling portion 184b may be larger than the diameter of the axial support unit 210.

The radial support unit 200 may be provided with a pair. One end of the pair of radial support units 200 may be coupled to the outer circumferential surface of the support unit coupling portion 184b of the discharge cap 184, and the other end of the pair of radial support units 200 may be in close contact with the inner circumferential surface of the lower housing 111.

For example, the pair of radial support units 200 may be coupled to the support unit coupling portions 184b of the discharge cap 184 in a state of being opened at an angle in the range of 90 to 120 degrees.

The arrangement angle of the pair of radial support units 200 may be set so as to support a load in a vertically downward direction and to support a horizontal shaking motion.

For example, if the arrangement angle between the pair of radial support units 200 is narrowed, the load in the vertically downward direction is supported more favorably, and if the arrangement angle between the pair of radial support units 200 is widened, the wobbling in the width direction is supported more favorably.

Fig. 10 is a view showing a radial support unit 200 according to a first embodiment of the present invention.

Referring to fig. 10, the radial support unit 200 of the first embodiment may include: a leg 201 extending in a radial direction perpendicular to the axial direction; a support portion 202 supported by the support unit coupling portion 184b of the discharge cap 184; spring supports 203a and 203b and a spring 204 provided at the front end of the leg 201; and a coupling protrusion 205 coupled with the support unit coupling portion 184 b.

The leg 201 extends in the vertical direction in the axial direction when attached, and the support portion 202 extends outward from one end of the leg 201. Therefore, stable support can be achieved by increasing the support area.

Also, the supporting portion 202 may be provided in a concave curved shape corresponding to the convex curved surface of the supporting unit coupling portion 184 b. Also, a bead may be formed between the leg portion 201 and the support portion 202.

The coupling protrusion 205 may be formed on and protrude from a surface of the support portion 202 opposite to the leg portion 201, and may be formed to correspond to the shape of the coupling groove 184c to be coupled to the coupling groove 184c formed recessed in the outer circumferential surface of the support unit coupling portion 184b of the discharge cap 184. The coupling projection 205 may be detachably provided on the discharge cap 184.

Also, a vibration preventing member 202a may be provided on an inner side surface of the support portion 202, and the vibration preventing member 202a may prevent vibration and impact from being transmitted between the support portion 202 and the support unit coupling portion 184 b.

On the other hand, not only the load in the radial direction acts on the radial direction support unit 200, but also an axial force and a torsion force in the circumferential direction may act on the radial direction support unit 200.

Therefore, the combining projection 205 may be formed of a material capable of elastic deformation.

For example, the coupling protrusion 205 may be formed of a rubber material, and may be formed of a fluorine-based rubber material.

At this time, the coupling protrusion 205 and the vibration preventing member 202a may be formed in one body. For example, the coupling protrusion 205 and the vibration preventing member 202a may be injection-molded using a rubber material.

The

spring support portions

203a, 203b may be provided at the ends of the leg portions 201, and the leg portions 201 may be supported on the inner circumferential surface of the lower housing 111 when mounted.

The spring supports 203a, 203b may include: a fixed spring support portion 203a connected to the leg portion 201 and supporting one end of the spring 204; and a variable spring support portion 203b that supports the other end of the spring 204 and moves together with the contraction and extension of the spring 204.

The fixed spring support portion 203a may be formed with a support surface expanding outward from the end of the leg portion 201, thereby enabling to support one end of the spring 204.

In order to prevent the spring 204 from being detached, the fixed spring support 203a may include a fixed protrusion having an outer diameter corresponding to an inner diameter of the spring 204 and protruding in a longitudinal direction of the spring 204.

One surface of the variable spring support portion 203b supports the other end of the spring 204, and the other surface of the variable spring support portion 203b supports the inner circumferential surface of the lower housing 111.

In order to prevent the spring 204 from being detached, the variable spring support 203b may include a fixing protrusion having an outer diameter corresponding to an inner diameter of the spring 204 and protruding in a longitudinal direction of the spring 204.

The other surface of the variable spring support portion 203b supported by the lower case 111 may be formed as a curved surface, for example, a curved surface corresponding to the radius of curvature of the inner circumferential surface of the lower case 111.

On the other hand, the meaning of "fixed" in the fixed spring support 203a and the meaning of "variable" in the variable spring support 203b can be understood as relative movement.

That is, the fixed spring support portion 203a means that the fixed position is maintained with reference to the discharge cap 184 coupled to the radial support unit 200; the variable spring support portion 203b means a portion that is separated from or approaches in the radial direction with respect to the discharge cap 184.

If the movement is described with reference to the lower case 111, the case where the variable spring supporting portion 203b is provided at a predetermined position of the lower case 111 and the position of the fixed spring supporting portion 203a can be changed will be described.

The spring 204 may be a coil spring, and both ends thereof are supported by the

spring supporting portions

203a, 203 b.

However, in the radial support unit 200 of the first embodiment, there is a possibility that the spring 204 will buckle (bucking).

When a large vibration of the compressor body is generated or an external force is applied, a force exceeding a predetermined force of the spring 204 may be applied, and at this time, the spring 204 may be bent and the support function of the body may be lost.

In addition, when the length of the spring 204 is made long in order to reduce the rigidity in the gravity direction (longitudinal rigidity), there is a limit in reducing the longitudinal rigidity because the buckling resistance becomes weak.

Fig. 11 is a view showing a modified example of fig. 10.

Referring to fig. 11, the radial support unit 200-1 of the modified embodiment is for solving the problem of buckling of the spring 204, and the spring support includes not only a fixed spring support 203a and a variable spring support 203b, but also a guide 203c having one end connected to the variable spring support 203b and the other end movably inserted into the fixed spring support 203 a.

The guide portion 203c penetrates the center of the coil spring 204 and extends, and may be provided with a length greater than that when the spring 204 is relaxed. Further, the guide portion 203c may be provided so as to be movable in the contracting direction of the spring 204.

The guide portion 203c can absorb a force acting in a direction deviating from the contraction direction of the spring 204, thereby preventing the spring 204 from buckling.

However, since a torsion force in the circumferential direction also acts on the radial direction support unit 200-1, there is a possibility that the guide portion 203c may be broken in this case.

Fig. 12 is a front view showing the second support spring 117 for explaining the radial support unit 200-2 of the second embodiment of the present invention, and fig. 13 is a front view showing the radial support unit 200-2 of the second embodiment of the present invention.

Referring to fig. 12 and 13, a radial support unit 200-2 according to a second embodiment of the present invention includes two legs 201-1 opened at a predetermined angle, and the two legs 201-1 are connected from one support expansion 202-1 to both sides.

That is, unlike the first embodiment described with reference to fig. 7 to 10 in which the radial support unit 200 includes a pair of support units each having one leg 201 and disposed at a predetermined angle, the radial support unit 200-2 according to the second embodiment of the present invention is different in that two legs 201-1 are formed to extend from one support unit.

In this manner, the two leg portions 201-1 are integrated, whereby the structural rigidity can be ensured and the advantage of the assembly tolerance can be reduced.

As described above, in the case of the radial support units 200, 200-1, 200-2 described with reference to fig. 7 to 12, the radial support units are arranged so as to be spaced apart by a predetermined angle in the circumferential direction in the direction of the non-load direction of the main body.

Fig. 14 is a front view showing a radial support unit 200-3 according to a third embodiment of the present invention.

The support springs 116, 117 may be formed as a path for transmitting vibration between the compressor body and the housing 110. Therefore, in order to effectively damp the transmitted vibration, the longitudinal rigidity and the lateral rigidity of the support springs 116, 117 need to be made smaller.

The supporting force of the spring structure can be expressed by the product of the stiffness and the compressed length. Therefore, if the compressed length is made longer, the same supporting force can be maintained with less rigidity.

Referring to fig. 14, a radial support unit 200-3 of the third embodiment of the present invention is different in that only one radial support unit extending from a central axis toward a lower side of a six-point direction is provided.

The utility model discloses a second supporting spring of third embodiment not only can noise reduction and vibration through reducing vertical rigidity and horizontal rigidity, but also can support the body steadily.

When the radial direction supporting units 200, 200-1, 200-2 are arranged in a state of being opened at a prescribed angle in the circumferential direction from the vertically downward direction, there will be a limit to the reduction of the longitudinal rigidity.

Although the compression length of the spring needs to be increased in order to reduce the vertical rigidity, if the spring is disposed so as to be inclined with respect to the load direction, buckling is likely to occur if the spring length is increased.

However, when the radial direction supporting unit 200-3 is arranged in the vertically downward direction (six-point direction), since the direction of the elastic restoring force and the direction of the load are formed to coincide, the possibility of occurrence of buckling will be reduced, and the longitudinal rigidity can be reduced by increasing the compression length of the spring, and the load of the main body can be supported.

In addition, the second support spring needs to apply a support force not only to the load of the compressor body but also to a force acting in a direction deviating from the direction of the load.

To this end, the second support spring according to the third embodiment of the present invention may further include an axial support unit 210, and the axial support unit 210 may be disposed between the left side wall of the lower housing 111 and the discharge cap 184 in parallel with the axial direction.

Thus, the following steps are formed: a structure in which the load of the body part is supported by a low longitudinal rigidity of one radial support unit 200-3, and the rotation or torsion of the body part is supported by one axial support unit 210.

In addition, the axial support unit 210 may be provided such that the free length (contractible length) of the spring is less than or equal to the outer diameter of the spring, thereby enabling buckling to be prevented. This is because, in the case of the axial support unit 210, the load acts in the lateral direction of the spring.

Also, the radial direction supporting unit 200-3 may be provided such that the free length (contractible length) of the spring is greater than the outer diameter of the spring, thereby being capable of reducing the longitudinal rigidity.

In addition, the second supporting spring according to the third embodiment of the present invention employs one axial supporting unit 210 and one radial supporting unit 200-3, so that the supporting spring, which is a medium for transmitting vibration, can be minimized, and the spring having a small rigidity as described above can be used, thereby increasing the effect of reducing vibration.

Referring to fig. 15A and 15B, it can be confirmed that: difference in vibration level in the case of using springs having spring constants different from each other in structures having the same weight.

In FIG. 15A, the vibration level (Vi) is 7000N/m in spring constantBrodrion Level) of 100gal (mm/sec)²) (ii) a In FIG. 15B, the vibration Level (Vibratrion Level) is 55gal (mm/sec) with a spring constant of 4000N/m²). That is, if the spring stiffness drops from 7000 to 4000, the vibration level is almost reduced to half.

From this, it was confirmed that the vibration level becomes smaller as the rigidity of the axial support unit 210 and the radial support unit 200 is lowered.

Claims

1. A compressor, comprising:

a compressor body including a cylinder, a piston that reciprocates in the cylinder in an axial direction of a housing, and a drive unit that drives the piston;

a housing surrounding the compressor body;

a first support portion that supports a suction side of the compressor main body in the casing; and

a second support part which supports the discharge side of the compressor body in the shell,

the housing includes a lower shell and an upper shell secured to the lower shell,

the separation surfaces of the lower shell and the upper shell fixed to each other are inclined with respect to a horizontal center line of the housing when viewed from the axial direction of the housing.

2. The compressor of claim 1,

the angle of inclination of the parting plane is 20 to 70 °.

3. The compressor of claim 1,

the lower casing is provided with side walls on both sides in the axial direction of the housing,

the upper housing is provided with side walls on both sides in the axial direction of the housing.

4. The compressor of claim 3,

at least either one of both side ends of the separating surface is located on an upper side than a horizontal center line of the housing when viewed in an axial direction of the housing.

5. The compressor of claim 4,

a terminal is provided at the lower housing for providing an external power source to a motor assembly of the compressor.

6. The compressor of claim 5,

the terminal is provided at a position on the side of an end portion of the lower case located at a higher height of both side end portions of the separation surface.

7. The compressor of any one of claims 1 to 6,

the first support portion and the second support portion include plate springs, respectively.

8. The compressor of any one of claims 1 to 6,

the first support portion includes a plate spring,

the second support portion includes:

an axial support unit elastically deformed in the axial direction or a direction adjacent to the axial direction; and

and a radial support unit elastically deformed toward a radial direction perpendicular to the axial direction or a direction adjacent to the radial direction.

9. The compressor of claim 8,

the radial support unit includes a plurality of coil springs that expand and contract in a direction inclined at a predetermined angle to a load direction of the compressor body when viewed in an axial direction of the housing.

10. The compressor of claim 9,

the radial support unit includes:

a coupling member coupled to the compressor body;

a leg portion connected to the coupling member and extending in a radial direction or a direction adjacent to the radial direction; and

a spring support portion provided at an end of the leg portion,

the plurality of coil springs are supported by the spring support portion and expand and contract in a radial direction or a direction adjacent to the radial direction.