CN214959227U

CN214959227U - Motor and compressor comprising same

Info

Publication number: CN214959227U
Application number: CN202120373397.4U
Authority: CN
Inventors: 洪彦杓; 崔基喆
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2020-05-13
Filing date: 2021-02-10
Publication date: 2021-11-30
Anticipated expiration: 2031-02-10
Also published as: KR102399507B1; KR20210138898A

Abstract

The utility model provides a motor reaches compressor including it. According to the utility model discloses a motor of an aspect, characterized in that includes: a stator including a yoke, and a first tooth portion and a second tooth portion that protrude from an inner surface of the yoke toward an inner side of the yoke and face each other; a first coil and a second coil wound around the first tooth portion and the second tooth portion, respectively; and a magnet disposed between the first tooth portion and the second tooth portion and reciprocating in the axial direction, wherein the stator includes a plurality of core plates stacked in the axial direction, the magnet includes a first surface facing the first tooth portion and a second surface facing the second tooth portion, one axial side of the first surface and the other axial side of the second surface have a first polarity, and the other axial side of the first surface and one axial side of the second surface have a second polarity different from the first polarity. According to the utility model discloses a motor can improve the space efficiency nature and the manufacturing ease of compressor to can reduce the manufacturing cost of compressor.

Description

Motor and compressor comprising same

Technical Field

The utility model relates to a motor reaches compressor including it. And more particularly, to a motor applied to a linear compressor compressing a refrigerant by a linear reciprocating motion of a piston and a linear compressor including the same.

Background

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

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

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

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

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

A compression unit and a driving unit (motor) are respectively provided inside the linear compressor, and the compression unit is moved by the resonance of the resonance spring by the movement of the driving unit, and compresses and discharges the refrigerant.

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

On the other hand, the motor of the conventional linear compressor is disposed outside the cylinder tube, and therefore, there is a problem that space efficiency is lowered.

In addition, since the structure of the motor of the conventional linear compressor is complicated, there is a problem in that the manufacturing cost is increased.

Further, since core plates (core plates) of a stator of a conventional linear compressor are stacked in a radial direction, there is a problem in that manufacturing is difficult.

Documents of the prior art

Patent document

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

SUMMERY OF THE UTILITY MODEL

The utility model aims to solve the problem that a motor that can improve space efficiency nature and including its compressor is provided.

Another object of the present invention is to provide a motor and a compressor including the same, which can reduce manufacturing costs.

Further, an object of the present invention is to provide a motor and a compressor including the same, which can improve the ease of manufacturing.

In order to achieve the above object, according to an aspect of the present invention, a motor includes: a stator including a yoke and first and second teeth portions protruding from an inner side surface of the yoke toward an inner side of the yoke and facing each other; first and second coils wound around the first and second teeth, respectively; and a magnet disposed between the first tooth portion and the second tooth portion and reciprocating in an axial direction.

At this time, the stator may include a plurality of core plates stacked in an axial direction, and the magnet may include: a first surface opposite the first tooth; and a second surface that is opposite to the second tooth, one side in the axial direction of the first surface and the other side in the axial direction of the second surface may have a first polarity, and the other side in the axial direction of the first surface and the one side in the axial direction of the second surface may have a second polarity different from the first polarity.

That is, since the core plates of the stator are stacked in the axial direction, the ease of manufacturing can be improved.

In addition, the manufacturing cost can be reduced by reducing the motor configuration.

In addition, the length of the magnet in the axial direction may be formed to be greater than the length of the stator in the axial direction.

The length of the magnet in the axial direction may be two or more times the length of the stator in the axial direction.

In addition, the magnet may be formed in a flat plate shape.

In addition, first direction lengths of the first tooth portion and the second tooth portion perpendicular to the axial direction may correspond to the first direction lengths of the magnets, respectively.

In addition, the first coil and the second coil may be wound in the same direction as each other.

In addition, the yoke may be formed in a closed curve shape on a plane perpendicular to the axial direction.

In order to achieve the above object, according to an aspect of the present invention (aspect), a compressor includes: a cylinder barrel; a piston disposed inside the cylinder and reciprocating in an axial direction; a stator including a yoke and first and second teeth portions that protrude from an inner surface of the yoke toward an inner side of the yoke and face each other, the stator being disposed behind the piston; first and second coils wound around the first and second teeth, respectively; a magnet disposed between the first tooth portion and the second tooth portion and reciprocating in an axial direction; and a connection member, one side of which is connected to the piston and the other side of which is connected to the magnet.

That is, since the stator is disposed behind the piston, space efficiency can be improved.

At this time, the stator may include a plurality of core plates stacked in an axial direction, and the magnet may include: a first surface opposite the first tooth; and a second surface opposite to the second tooth, one side of the first surface in the axial direction and the other side of the second surface in the axial direction may have a first polarity, and the other side of the first surface and one side of the second surface may have a second polarity different from the first polarity.

In addition, the magnet may be formed in a flat plate shape.

In addition, the winding directions of the first coil and the second coil may be the same as each other.

In addition, the piston may include: a guide portion disposed inside the cylinder; and a head portion disposed in front of the guide portion, wherein one side of the connection member may be connected to a central region of the head portion, and the other side of the connection member may be connected to a front surface of the magnet.

In addition, the connection member may be formed of an elastic material.

Further, the stator may be disposed rearward of the cylinder.

In addition, it may include: a housing for accommodating the cylinder; and an elastic member for connecting the back surface of the magnet and the inner surface of the case.

Further, the outer side surface of the stator may be disposed at a position further outward than the outer side surface of the cylinder.

In addition, an inner area of the first and second teeth may be formed to be larger than an area for winding the first and second coils.

Through the utility model discloses, can provide a motor that can improve space efficiency nature and including its compressor.

In addition, the present invention can provide a motor and a compressor including the same, which can reduce manufacturing costs.

Further, according to the present invention, a motor and a compressor including the same, which can improve the ease of manufacturing, can be provided.

Drawings

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

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

Fig. 3 is a perspective view of a motor according to an embodiment of the present invention.

Fig. 4 is a perspective view of a magnet according to an embodiment of the present invention.

Fig. 5 is a plan view of a motor according to an embodiment of the present invention.

Fig. 6 and 7 are sectional views of a motor according to an embodiment of the present invention.

Fig. 8 to 10 are operation diagrams of a motor according to an embodiment of the present invention.

Fig. 11 is a graph showing the magnitude of the voltage induced in the coil with respect to the position of the magnet according to an embodiment of the present invention.

Description of the reference numerals

100: the compressor 101: accommodation space

102: suction space 103: compression space

104: discharge space 110: casing (casting)

111: housing (shell) 112: first case cover

113: second housing cover 114: suction tube

115: discharge pipe 115 a: circulation pipe

117: support spring 117 a: support bracket

117 b: first support guide 117 c: support cover

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

118: the elastic member 120: frame structure

121: main body portion 122: first flange part

130: the motor 131: stator

131 a: core plate 131 b: magnetic yoke

132: tooth portion 132 a: first tooth part

132 b: second tooth 133: coil

133 a: first coil 133 b: second coil

135: magnet 140: cylinder barrel

141: second flange portion 142: gas inlet

150: piston 151: head part

152: guide portion 153: third flange part

154: suction port 155: suction valve

170: discharge valve assembly 171: discharge valve

172: valve spring 180: discharge cap assembly

181: first discharge cap 182: second discharge cap

183: third discharge cap 200: connecting member

Detailed Description

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

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

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

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

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

At the lower side of the housing 111, a leg 20 may be coupled. The leg 20 may be coupled to a base of a product on which the linear compressor 100 is provided. For example, the product may include a refrigerator and the base may include a base of a machine compartment of the refrigerator. As another example, the product may include an outdoor unit of an air conditioner, and the base may include a base of the outdoor unit.

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

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

On the outer surface of the housing 111, a terminal (terminal)30 may be provided. The connection terminal 30 can supply an external power to the motor 130 of the linear compressor 100. Specifically, the connection terminal 30 may be connected to a lead wire of the coil 133.

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

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

housing covers

112, 113.

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

The linear compressor 100 may include a plurality of

pipes

114, 115, 40, and the plurality of

pipes

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

The plurality of

tubes

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

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

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

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

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

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

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

Fig. 2 is a sectional view for explaining the structure of the compressor 100. Fig. 3 is a perspective view of a motor according to an embodiment of the present invention. Fig. 4 is a perspective view of a magnet according to an embodiment of the present invention. Fig. 5 is a plan view of a motor according to an embodiment of the present invention. Fig. 6 and 7 are sectional views of a motor according to an embodiment of the present invention.

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

Referring to fig. 2 to 7, the compressor 100 may include: a housing 110; and a main body accommodated inside the case 110. The main body of the compressor 100 may include: a frame 120; a cylinder 140 fixed to the frame 120; a piston 150 linearly reciprocating inside the cylinder 140; a motor 130 fixed to the frame 120 and providing a driving force to the piston 150, and the like. Here, the cylinder 140 and the piston 150 may be referred to as

compression units

140 and 150.

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

The main body of the compressor 100 may be elastically supported by a support spring 117 and an elastic member 118 provided inside the casing 110. The support spring 117 may support the front of the main body. The support spring 117 may include a plate spring. The elastic member 118 may support the rear of the main body. The elastic member 118 may include a plate spring. The support spring 117 and the elastic member 118 may support a plurality of internal parts of the body of the compressor 100 while being capable of absorbing vibration and impact generated as the piston 150 reciprocates.

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

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

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

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

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

The rear side of the main body of the compressor 100 may be elastically supported by the elastic member 118 in the radial direction of the first housing cover 112.

The elastic member 118 may include a circular plate spring.

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

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

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

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

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

The frame 120 may include: a body 121 for supporting the outer circumferential surface of the cylinder 140; and a first flange portion 122 connected to one side of the body portion 121. The frame 120 may be elastically supported to the housing 11 by the first and second support springs 116 and 117 together with the cylinder 140.

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

A cylinder 140 may be coupled to an inner circumferential surface of the body 121. For example, the cylinder 140 may be press-fitted (press-fitting) and fixed to the inner circumferential surface of the body portion 121.

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

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

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

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

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

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

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

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

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

The gas inlets 142 may be formed in plural numbers independently, or the inlets may be formed in annular grooves, and the outlets may be formed in plural numbers at regular intervals along the annular grooves. The gas inlet 142 may be formed only on the front side with respect to the axial center of the cylinder 140. In addition, the gas inlet 142 may be formed on the rear side with respect to the axial center of the cylinder 140 in consideration of the drooping of the piston 150.

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

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

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

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

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

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

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

The piston 150 may include a third flange portion 153. The third flange 153 may be bent outward from the rear of the guide portion 152.

The piston 150 may be coupled to a Magnet (Magnet) 135. The magnet 135 may reciprocate in the front-rear direction as the piston 150 moves. The magnet 135 may be connected with the piston 150 via a connection member 200. The magnet 135 may be referred to as a "mover". The magnet 135 may reciprocate in the axial direction. The front surface of the magnet 135 may be connected with the connection member 200. The back of the magnet 135 may be connected to the elastic member 118. The magnet 135 may be disposed rearward of the piston 150. The magnet 135 may be disposed rearward of the cylinder 140. The magnet 135 may be disposed within the stator 131. The magnet 135 may face the coil 133. The magnet 135 may be disposed between the teeth 132. Specifically, the magnet 135 may be disposed between the first tooth portion 132a and the second tooth portion 132 b.

The coupling member 200 may couple the piston 150 and the magnet 135. One end of the connection member 200 may be connected to the piston 150. One end of the connection member 200 may be connected to the head 151. One end of the connection member 200 may be connected to a central region of the head 151. The other end of the connection member 200 may be connected to the magnet 135. The other end of the connection member 200 may be connected to the front surface of the magnet 135. The connection member 200 may be formed in a cylindrical shape. The connection member 200 may be formed of a material having elasticity. The connection member 200 may be referred to as a "flexible rod". The coupling member 200 may reciprocate the piston 150 in the axial direction in accordance with the movement of the magnet 135 in the axial direction.

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

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

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

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

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

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

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

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

Further, between the discharge cap assembly 180 and the frame 120, there may be provided: a gasket 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 may be arranged such that a plurality of discharge caps are in communication with each other in sequence. In the case where the discharge cap assembly 180 is composed of a plurality of discharge caps, the discharge space 104 may include a plurality of space portions partitioned by the respective discharge caps. The plurality of space portions may be arranged along the front-rear direction and communicate with each other.

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

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

The motor 130 may include: a stator 131 disposed inside the housing 110; a coil 133 wound around the stator 131; and a magnet 135 disposed inside the stator 131 and facing the coil 133.

The stator 131 may be disposed inside the housing 110. The stator 131 may be disposed behind the cylinder 140. The stator 131 may be disposed behind the piston 150. The outer side surface of the stator 131 may be disposed further outward than the outer side surface of the cylinder 140. The stator 131 may overlap (overlap) the cylinder 140 in the axial direction. The stator 131 may overlap the piston 150 in the axial direction. This can improve the space efficiency of the compressor 100.

The stator 131 may include a plurality of core plates 131a stacked in the axial direction. Since the plurality of core plates 131a are stacked in the axial direction, the stator 131 can be easily stacked. This can improve the ease of manufacture. The stator 131 may include a yoke 131b and a tooth portion 132. In contrast, in the stator 131, a plurality of lamination sheets (lamination blocks) may be stacked in the axial direction, or a plurality of lamination blocks (lamination blocks) may be stacked in the axial direction.

The yoke 131b may be formed in a circular band shape. The yoke 131b may be formed in a closed curve shape on a plane perpendicular to the axial direction. The yoke 131b may be formed in an O-shape.

The tooth portion 132 may protrude from an inner side surface of the yoke 131b toward an inner side of the yoke 131 b. The coil 133 may be wound around the tooth 132. The teeth 132 may include a first tooth 132a and a second tooth 132b opposite to each other. A gap g may be formed between the first tooth portion 132a and the second tooth portion 132 b. The magnet 135 may be disposed between the first tooth portion 132a and the second tooth portion 132 b. The first coil 133a may be wound around the first tooth 132 a. The second coil 133b may be wound around the second tooth portion 132 b. The inner side areas of the first and

second tooth portions

132a and 132b may be formed to be larger than the areas for winding the first and

second coils

133a and 133 b.

The coil 133 may be wound around the tooth 132. The cross section of the coil 133 may be formed in a circular or polygonal shape, and may have a hexagonal shape, for example. The coil 133 may include: a first coil 133a wound around the first tooth 132 a; and a second coil 133b wound around the second tooth portion 132 b. The magnet 135 may be disposed between the first coil 133a and the second coil 133 b. The first and

second coils

133a and 133b may be wound in the same direction as each other.

The axial length of the magnet 135 may be formed to be greater than the axial length of the stator 131. Specifically, the length of the magnet 135 in the axial direction may be formed to be greater than the length of the yoke 131b of the stator 131 in the axial direction. For example, the axial length of the magnet 135 may be more than twice the axial length of the stator 131. The magnet 135 may be formed in a flat plate shape. The length of the magnet 135 in the first direction perpendicular to the axial direction may correspond to the length of the first tooth portion 132a and the second tooth portion 132b in the first direction.

The magnet 135 may include: a first surface 135a facing the first tooth 132 a; and a second surface 135b facing the second tooth 132 b. One axial side 135aa of the first surface 135a of the magnet 135 and the other axial side 135bb of the second surface 135b of the magnet 135 may have a first polarity. For example, one axial side 135aa of the first surface 135a of the magnet 135 and the other axial side 135bb of the second surface 135b of the magnet 135 may be N-poles. The axially other side 135ab of the first surface 135a of the magnet 135 and the axially one side 135ba of the second surface 135b of the magnet 135 may have a second polarity different from the first polarity. For example, the other axial side 135ab of the first surface 135a of the magnet 135 and the one axial side 135ba of the second surface 135b of the magnet 135 may be S-poles. When a current is applied to the motor 130, a magnetic flux (magnetic flux) is formed in the winding coil 133, and the magnet 135 can be moved by generating an electromagnetic force by an interaction between the magnetic flux formed in the coil 133 and the magnetic flux formed by the magnet 135. Further, the piston 150 connected to the connecting member 200 reciprocates in the axial direction integrally with the magnet 135 while the magnet 135 reciprocates in the axial direction.

On the other hand, the motor 130 and the

compression units

140, 150 may be supported by the support spring 117 and the elastic member 118 in the axial direction.

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

The elastic member 118 may be a coil spring extending in the axial direction. Both end portions of the elastic member 118 may be connected to the vibration body and the fixed body, respectively. For example, one end of the elastic member 118 may be connected with the magnet 135, and the other end thereof may be connected with the housing 110. Therefore, the elastic member 118 can be elastically deformed between the vibrator that generates vibration at one end portion of the elastic member 118 and the fixed body that is fixed to the other end portion of the elastic member 118.

The natural frequency of the elastic member 118 may be designed to coincide with the resonant frequency of the magnet 135 and the piston 150 when the compressor 100 is operated, thereby enabling the reciprocation of the piston 150 to be increased.

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

Referring to fig. 2 to 10, the operating state of the compressor 100 is as follows.

First, when a current is applied to the motor 130, a magnetic flux can be formed in the stator 131 by the current flowing through the coil 133. The magnetic flux formed at the stator 131 generates an electromagnetic force, and the magnet 135 linearly reciprocates due to the generated electromagnetic force. Such an electromagnetic force is alternately generated in a direction (forward direction) in which the piston 150 faces a Top Dead Center (TDC) when a compression stroke is performed, and in a direction (backward direction) in which the piston 150 faces a Bottom Dead Center (BDC) when an intake stroke is performed. That is, the motor 130 can generate a force, that is, a thrust force, for moving the magnet 135 and the piston 150 in the moving direction.

For example, referring to fig. 8, if current is applied to the first and

second coils

133a and 133b, the second tooth portion 132b will assume the N-pole, and the first tooth portion 132a will assume the S-pole. At this time, one axial side 135aa of the first surface 135a receives an attractive force, the other axial side 135ab of the first surface 135a receives a repulsive force (repulsive force), one axial side 135ba of the second surface 135b receives an attractive force, and the other axial side 135bb of the second surface 135b receives a repulsive force, so that the magnet 135 moves forward.

Referring to fig. 9, if current is applied to the first and

second coils

133a and 133b in the opposite direction to fig. 8, the first tooth 132a will assume the N-pole and the second tooth 132b will assume the S-pole. At this time, one side 135aa in the axial direction of the first surface 135a receives a repulsive force, the other side 135ab in the axial direction of the first surface 135a receives an attractive force, one side 135ba in the axial direction of the second surface 135b receives a repulsive force, and the other side 135bb in the axial direction of the second surface 135b receives an attractive force, so that the magnet 135 moves toward the rear.

In addition, referring to fig. 10, if current is applied to the first and

second coils

133a and 133b in the same direction as fig. 8, the second tooth portion 132b will assume the N-pole, and the first tooth portion 132a will assume the S-pole. At this time, the one axial side 135aa of the first surface 135a receives an attractive force, the other axial side 135ab of the first surface 135a receives a repulsive force, the one axial side 135ba of the second surface 135b receives an attractive force, and the other axial side 135bb of the second surface 135b receives a repulsive force, so that the magnet 135 is moved again toward the front.

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

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

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

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

In one embodiment of the present invention, a case where the elastic member 118 functions as a mechanical resonance spring is described as an example, and in contrast to this, the elastic member 118 may not function as a mechanical resonance spring. At this time, the magnet 135 may be controlled so as not to deviate from the magnetic attraction range, and resonance may be performed by a center force (Centering force) in the reciprocating direction between the stator 131 and the magnet 135.

When the magnet 135 is moved in a direction away from the teeth 132 by a Magnetic force, the magnet 135 receives a central force in a direction close to the teeth 132, that is, a reciprocating direction returning to the gap g side where the Magnetic energy (Magnetic resistance) is low, which is called a Magnetic Resonance Spring (Magnetic Resonance Spring), and the magnet 135 can perform a resonant motion by the Magnetic Resonance Spring. Accordingly, the magnet 135 of the motor 130 can perform a resonant motion without a mechanical resonant spring, thereby reducing the size of the motor 130 and the weight thereof, and reducing the number of parts to save the manufacturing cost.

For example, as shown in fig. 8, when the magnet 135 moves forward by the magnetic force, a reciprocating central force F1 is accumulated between the magnet 135 and the tooth 132, and the reciprocating central force F1 is a force that returns the magnet 135 toward the side where the magnetic energy (magnetic potential energy or magnetic resistance) is low, that is, toward the gap g direction or the rear.

At this time, when the direction of the current applied to the magnet 135 is switched, the magnet 135 is moved backward by the magnetic force toward the gap g or backward generated by the coil 133 and the accumulated reciprocation direction center force F1, and the boundary surface between the magnetic poles can be restored to the central region of the gap g as shown in fig. 9.

At this time, the magnet 135 passes through the central region of the gap g by the inertial force and the magnetic force, and further moves toward the rear. At this time, as shown in fig. 10, when a current is applied to the coil 133 in the opposite direction to fig. 9, the same magnetic poles as in fig. 8 are formed in the teeth 132, and thus an attractive force and a repulsive force in the same direction as in fig. 8 are formed in each region of the magnet 135, so that the magnet 135 can move forward.

At this time, the reciprocation direction center force F2 is accumulated between the tooth 132 and the magnet 135, and therefore, the magnet 135 can repeat a series of reciprocating motions intended to move forward by the force and the magnetic force in the gap g direction, as in the case of including the mechanical resonance spring.

Referring to fig. 11, the magnitude (V) of the voltage induced by the coil 133 is maintained relatively flat with respect to the position of the magnet 135. For example, it can be confirmed that: the voltage induced in the coil 133 remains above 60 as the magnet 135 is moved in the axial direction in the range between-6 nm and 6 nm. That is, the motor 130 may be composed of only one stator 131 and one magnet 135, and thus, manufacturing costs of the motor 130 may be reduced and manufacturing easiness may be improved. In addition, the piston 150 can be reciprocated at a high speed by a simple structure of the motor 130.

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

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

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

Claims

1. A motor, comprising:

a stator including a yoke, and a first tooth portion and a second tooth portion that protrude from an inner surface of the yoke toward an inner side of the yoke and face each other;

a first coil and a second coil wound around the first tooth portion and the second tooth portion, respectively; and

a magnet disposed between the first tooth portion and the second tooth portion and reciprocating in an axial direction,

the stator is provided with a plurality of core plates stacked in an axial direction,

the magnet includes: a first surface opposite the first tooth; and a second surface opposite the second tooth,

one side in the axial direction of the first surface and the other side in the axial direction of the second surface have a first polarity,

the other side in the axial direction of the first surface and the one side in the axial direction of the second surface have a second polarity different from the first polarity.

2. The motor of claim 1,

the length of the magnet in the axial direction is formed to be greater than the length of the stator in the axial direction.

3. The motor of claim 2,

the length of the magnet in the axial direction is more than twice as long as the length of the stator in the axial direction.

4. The motor of claim 1,

the magnet is formed in a flat plate shape.

5. The motor of claim 1,

first direction lengths of the first tooth portion and the second tooth portion perpendicular to the axial direction correspond to the first direction lengths of the magnet, respectively.

6. The motor of claim 1,

the first coil and the second coil are wound in the same direction as each other.

7. The motor of claim 1,

the yoke is formed in a closed curve shape on a plane perpendicular to the axial direction.

8. A compressor, comprising:

a cylinder barrel;

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

a stator including a yoke, and a first tooth portion and a second tooth portion that protrude from an inner surface of the yoke toward an inner side of the yoke and face each other, the stator being disposed behind the piston;

a first coil and a second coil wound around the first tooth portion and the second tooth portion, respectively;

a magnet disposed between the first tooth portion and the second tooth portion and reciprocating in an axial direction; and

a connection member having one side connected to the piston and the other side connected to the magnet,

9. The compressor of claim 8,

10. The compressor of claim 9,