KR102233621B1 - A linear compressor - Google Patents

Abstract

The present invention relates to a linear compressor.
A linear compressor according to an embodiment of the present invention includes a shell provided with a discharge unit; A cylinder provided inside the shell and forming a compression space for a refrigerant; A frame fixing the cylinder to the shell; A piston provided so as to reciprocate in the axial direction inside the cylinder; A discharge valve provided on one side of the cylinder and selectively discharging the refrigerant compressed in the compression space of the refrigerant; A discharge cover coupled to the frame and having a resonance chamber for reducing pulsation of the refrigerant discharged through the discharge valve; A first spring coupled to the discharge valve to provide a restoring force to the discharge valve; And a damping device installed on one side of the first spring and distributing a force acting on the discharge valve when the piston operates abnormally.

Description

Linear compressor {A linear compressor}

The present invention relates to a linear compressor.

The cooling system is a system that circulates a refrigerant to generate cool air, and repeatedly performs compression, condensation, expansion, and evaporation processes of the refrigerant. To this end, the cooling system includes a compressor, a condenser, an expansion device and an evaporator. In addition, the cooling system may be installed in a refrigerator or air conditioner as a home appliance.

In general, a compressor is a mechanical device that receives power from a power generating device such as an electric motor or a turbine and compresses air, refrigerant or other various operating gases to increase pressure. Is being used.

If these compressors are classified largely, a reciprocating compressor that compresses the refrigerant while the piston linearly reciprocates inside the cylinder by forming a compression space through which the working gas is sucked and discharged between the piston and the cylinder. ), and a compression space in which working gas is sucked and discharged between the eccentrically rotated roller and the cylinder is formed, and the roller is rotated eccentrically along the inner wall of the cylinder to compress the refrigerant, and a rotary compressor and orbiting scroll A compressed space through which the working gas is sucked and discharged is formed between the scroll and the fixed scroll, and the orbiting scroll may be divided into a scroll compressor that compresses the refrigerant while rotating along the fixed scroll.

Recently, among the reciprocating compressors, a number of linear compressors having a simple structure have been developed, in particular, by allowing a piston to be directly connected to a driving motor for reciprocating linear motion, thereby improving compression efficiency without mechanical loss due to motion conversion and having a simple structure.

In general, a linear compressor is configured to suck a refrigerant, compress it, and discharge it while a piston moves in a reciprocating linear motion inside a cylinder by a linear motor in a sealed shell.

The linear motor is configured such that a permanent magnet is positioned between the inner stator and the outer stator, and the permanent magnet is driven to linearly reciprocate by mutual electromagnetic force between the permanent magnet and the inner (or outer) stator. In addition, as the permanent magnet is driven while being connected to the piston, the piston sucks and compresses the refrigerant while reciprocating and linearly moving inside the cylinder, and then discharged.

In connection with the conventional linear compressor, the present applicant has filed a patent application (hereinafter, prior literature) and has been registered.

[Prior literature]

1. Registration No. 10-1307688, Registration Date: September 5, 2013, Invention Title: Linear Compressor

The linear compressor according to the prior document includes a shell 110 for accommodating a plurality of components. The height of the shell 110 in the vertical direction is formed somewhat higher, as shown in FIG. 2 of the prior literature.

In addition, an oil supply assembly 900 capable of supplying oil between the cylinder 200 and the piston 300 is provided inside the shell 110.

Meanwhile, when a linear compressor is provided in a refrigerator, the linear compressor may be installed in a machine room provided below the rear of the refrigerator.

Recently, increasing the internal storage space of refrigerators has become a major concern of consumers. In order to increase the internal storage space of the refrigerator, it is necessary to reduce the volume of the machine room, and reducing the size of the linear compressor has become a major issue in order to reduce the volume of the machine room.

However, since the linear compressor disclosed in the prior literature occupies a relatively large volume, there is a problem that is not suitable for a refrigerator for increasing an internal storage space.

In order to reduce the size of the linear compressor, it is necessary to make the main components of the compressor small, but in this case, a problem of deteriorating the performance of the compressor may occur.

In order to compensate for the problem of deteriorating the performance of the compressor, it may be considered to increase the operating frequency of the compressor. However, as the operating frequency of the compressor increases, the frictional force caused by oil circulating inside the compressor increases, resulting in a problem that the performance of the compressor decreases.

On the other hand, the prior document discloses an idea in which a discharge valve spring supporting a discharge valve is constituted by a coil spring. When a coil spring is applied to the discharge valve spring, a phenomenon in which the discharge valve rotates with respect to the coil spring occurs, thereby causing abrasion of the discharge valve.

The present invention has been proposed to solve this problem, and an object of the present invention is to provide a linear compressor capable of reducing wear of a discharge valve.

A linear compressor according to an embodiment of the present invention includes a shell provided with a discharge unit; A cylinder provided inside the shell and forming a compression space for a refrigerant; A frame fixing the cylinder to the shell; A piston provided so as to reciprocate in the axial direction inside the cylinder; A discharge valve provided on one side of the cylinder and selectively discharging the refrigerant compressed in the compression space of the refrigerant; A discharge cover coupled to the frame and having a resonance chamber for reducing pulsation of the refrigerant discharged through the discharge valve; A first spring coupled to the discharge valve to provide a restoring force to the discharge valve; And a damping device installed on one side of the first spring and distributing a force acting on the discharge valve when the piston operates abnormally.

Further, the damping device includes a second spring.

In addition, a stopper coupled to the first spring and limiting an opening amount of the discharge valve is further included.

In addition, the stopper is characterized in that it is installed between the first spring and the second spring.

In addition, a first spacer installed between the first spring and the stopper to separate the first spring and the stopper is further included.

In addition, a second spacer seated on the discharge cover to support the damping device is further included, and the second spacer separates the damping device from the discharge cover.

Further, the first spring or the second spring includes a leaf spring.

In addition, the elastic modulus of the second spring is formed larger than the elastic modulus of the first spring, and when the piston operates normally, the deformation of the second spring is limited, and when the piston operates abnormally, the second It is characterized in that the deformation of the spring is made.

In addition, the stopper includes a stopper body capable of supporting the first spring; And a guide protrusion protruding from the stopper body and movably coupled along a guide groove of the discharge cover.

Further, the damping device includes a plurality of springs.

In addition, a spacer installed between the plurality of springs and the first spring to separate the plurality of springs from the first spring; And a damping mounting part seated on the discharge cover and on which the plurality of springs are installed.

In addition, a fastening member for coupling the first spring and the plurality of springs and spacers is further included.

In the linear compressor according to another aspect, the shell is provided with a discharge unit; A cylinder provided inside the shell and forming a compression space for a refrigerant; A piston provided so as to reciprocate in the front-rear direction within the cylinder; A discharge valve provided on one side of the cylinder and selectively discharging the refrigerant compressed in the compression space of the refrigerant; A discharge cover having a resonance chamber for reducing pulsation of the refrigerant discharged through the discharge valve; A first spring coupled to the discharge valve to provide a restoring force to the discharge valve; A stopper coupled to the first spring to limit the amount of deformation of the first spring; And a second spring coupled to the stopper and guiding the movement of the stopper.

In addition, the first spring is coupled to the rear of the stopper, and the second spring is coupled to the front of the stopper.

In addition, the stopper includes a stopper body capable of supporting the first spring; And a first protrusion protruding from one surface of the stopper body to support the second spring.

In addition, the stopper further includes a second protrusion protruding from the first protruding part and inserted into the insertion hole of the second spring.

In addition, when the refrigerant is discharged from the compression space, the first spring is deformed forward so that the discharge valve is movable forward, and when an abnormal operation in which the piston collides with the discharge valve, the stopper moves forward. To be movable, the second spring is characterized in that it is deformed forward.

According to the present invention, by reducing the size of the compressor including internal parts, the size of the machine room of the refrigerator can be reduced, and accordingly, the internal storage space of the refrigerator can be increased.

In addition, by increasing the operating frequency of the compressor, it is possible to prevent deterioration of performance due to smaller internal parts, and by applying a gas bearing between the cylinder and the piston, there is an advantage in that it is possible to reduce the frictional force that may be generated by the oil.

In addition, it is possible to stably operate the discharge valve for selectively discharging the high-pressure gas compressed in the compression chamber, and reduce the wear of the discharge valve by reducing the amount of impact that may occur during the operation of the discharge valve. As a result, it is possible to prevent foreign matters that may occur due to wear of the discharge valve from acting on the gas bearing.

In addition, since the opening amount of the discharge valve is limited by the stopper and the time for closing the discharge valve is shortened, there is an effect that responsiveness for the operation of the discharge valve can be improved.

In addition, a first valve spring supporting the discharge valve and a second valve spring coupled to the front of the stopper are provided to stably support the discharge valve, and when an emergency situation occurs due to a control error of the compressor, for example, For example, when the piston and the discharge valve collide, the stopper moves by the second valve spring, thereby preventing the discharge valve from being worn or damaged by the collision.

In addition, a first valve spring supporting a discharge valve and a plurality of second valve springs spaced apart from the first valve spring are provided, and when the emergency situation occurs, the discharge valve by the plurality of second valve springs By sufficiently moving in the direction in which is opened, it is possible to prevent the discharge valve from being worn or damaged by the collision.

Further, by configuring the resonance chamber in the discharge cover, it is possible to reduce the pulsation of the discharge gas and reduce noise generation.

In addition, by providing a plurality of filter devices inside the compressor, there is an advantage in that it is possible to prevent foreign matter or oil from being contained in the compressed gas (or discharge gas) flowing from the nozzle part of the cylinder to the outside of the piston.

As a result, by preventing the nozzle portion of the cylinder from being clogged, the gas bearing can be effectively operated between the cylinder and the piston, thereby preventing the cylinder and the piston from being worn.

1 is a cross-sectional view showing the configuration of a linear compressor according to a first embodiment of the present invention.
2 is a cross-sectional view showing the configuration of a suction muffler according to the first embodiment of the present invention.
3 is a cross-sectional view showing a peripheral configuration of a discharge cover and a discharge valve according to a first embodiment of the present invention.
4 is an exploded perspective view showing the configuration of a cylinder and a frame according to a first embodiment of the present invention.
5 is a cross-sectional view showing a combination of a cylinder and a piston according to a first embodiment of the present invention.
6 is an exploded perspective view showing the configuration of a cylinder according to the first embodiment of the present invention.
7 is an enlarged cross-sectional view of “A” in FIG. 5.
8 is a perspective view showing a discharge valve assembly coupled to a discharge cover according to a first embodiment of the present invention.
9 is an exploded perspective view of a discharge cover and a discharge valve assembly according to the first embodiment of the present invention.
10 is a view showing the configuration of a stopper according to the first embodiment of the present invention.
11 is a view showing the operation of the discharge valve assembly according to the first embodiment of the present invention.
12 is a cross-sectional view showing the flow of refrigerant in the linear compressor according to the first embodiment of the present invention.
13 is a cross-sectional view showing an operation of the discharge valve assembly when the linear compressor according to the first embodiment of the present invention is operated.
14 is a cross-sectional view showing the configuration of a discharge valve assembly according to a second embodiment of the present invention.
15 is a view showing the operation of the discharge valve assembly according to the second embodiment of the present invention.

Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. However, the spirit of the present invention is not limited to the presented embodiments, and those skilled in the art who understand the spirit of the present invention will be able to easily propose other embodiments within the scope of the same idea.

1 is a cross-sectional view showing the configuration of a linear compressor according to a first embodiment of the present invention.

1, a linear compressor 100 according to a first embodiment of the present invention includes a shell 101 having a substantially cylindrical shape, a first cover 102 coupled to one side of the shell 101, and the other side. It includes a second cover 103 that is coupled to. For example, the linear compressor 100 is laid in a horizontal direction, the first cover 102 is on the right side of the shell 101, and the second cover 103 is on the left side of the shell 101. Can be combined.

In a broader sense, the first cover 102 and the second cover 103 can be understood as one configuration of the shell 101.

The linear compressor 100 is provided with a driving force to the cylinder 120 provided inside the shell 101, the piston 130 and the piston 130 reciprocating and linearly moving inside the cylinder 120 A motor assembly 140 is included as a linear motor.

When the motor assembly 140 is driven, the piston 130 may reciprocate at high speed. The operating frequency of the linear compressor 100 according to the present embodiment is approximately 100 Hz.

In detail, the linear compressor 100 includes a suction unit 104 through which refrigerant is introduced and a discharge unit 105 through which the refrigerant compressed in the cylinder 120 is discharged. The suction unit 104 may be coupled to the first cover 102, and the discharge unit 105 may be coupled to the second cover 103.

The refrigerant sucked through the suction part 104 flows into the piston 130 through the suction muffler 150. In the process of passing the refrigerant through the suction muffler 150, noise may be reduced. The suction muffler 150 is configured by combining a first muffler 151 and a second muffler 153. At least a portion of the suction muffler 150 is located inside the piston 130.

The piston 130 includes a substantially cylindrical piston body 131 and a piston flange portion 132 extending radially from the piston body 131. The piston body 131 reciprocates within the cylinder 120, and the piston flange portion 132 may reciprocate outside the cylinder 120.

The piston 130 may be made of a non-magnetic aluminum material (aluminum or aluminum alloy). Since the piston 130 is made of an aluminum material, the magnetic flux generated by the motor assembly 140 is transmitted to the piston 130 to prevent leakage to the outside of the piston 130. In addition, the piston 130 may be formed by a forging method.

Meanwhile, the cylinder 120 may be made of a non-magnetic aluminum material (aluminum or aluminum alloy). In addition, the material composition ratio of the cylinder 120 and the piston 130, that is, the type and composition ratio may be the same.

Since the cylinder 120 is made of an aluminum material, the magnetic flux generated by the motor assembly 140 is transmitted to the cylinder 120 to prevent leakage to the outside of the cylinder 120. In addition, the cylinder 120 may be formed by an extrusion rod processing method.

In addition, since the piston 130 and the cylinder 120 are made of the same material (aluminum), the coefficients of thermal expansion are the same. During the operation of the linear compressor 100, a high temperature (about 100°C) environment is created inside the shell 100, and the piston 130 and the cylinder 120 have the same coefficient of thermal expansion, so that the piston 130 And the cylinder 120 can be thermally deformed by the same amount.

As a result, since the piston 130 and the cylinder 120 are thermally deformed in different sizes or directions, it is possible to prevent interference between the piston 130 and the cylinder 120 during movement of the piston 130. have.

The cylinder 120 is configured to receive at least a portion of the suction muffler 150 and at least a portion of the piston 130.

Inside the cylinder 120, a compression space P in which the refrigerant is compressed by the piston 130 is formed. In addition, a suction hole 133 for introducing a refrigerant into the compression space P is formed in a front portion of the piston 130, and the suction hole 133 is selectively disposed in front of the suction hole 133. An opening intake valve 135 is provided. A fastening hole through which a predetermined fastening member is coupled is formed in an approximately central portion of the suction valve 135.

In front of the compression space P, a discharge cover 200 forming a discharge space or discharge flow path of the refrigerant discharged from the compression space P and the discharge cover 200 are coupled to the compressed space P A discharge valve assembly for selectively discharging the refrigerant compressed in is provided.

The discharge valve assembly includes a discharge valve 220 that is opened when the pressure in the compression space P is greater than or equal to the discharge pressure to flow the refrigerant into the discharge space of the discharge cover 200, the discharge valve 220, and A plurality of valve springs 230 and 270 provided between the discharge cover 200 to impart an elastic force in the axial direction, and a stopper 240 for limiting an opening amount or an opening degree of the discharge valve 220 are included.

In the plurality of valve springs 230 and 270, a first spring 230 installed between the discharge valve 220 and the stopper 240 and a second "damping device" installed in front of the stopper 240 A spring 270 is included. The first spring 230 may be installed on one side of the stopper 240, and the second spring 270 may be spaced apart from the first spring 230 and installed on the other side of the stopper 240. In other words, the stopper 240 may be installed between the first spring 230 and the second spring 270.

The plurality of valve springs 230 and 270 may include, for example, a plate spring.

Here, the compression space P is understood as a space formed between the intake valve 135 and the discharge valve 220. In addition, the suction valve 135 may be formed on one side of the compression space P, and the discharge valve 220 may be provided on the other side of the compression space P, that is, on the opposite side of the suction valve 135. have.

In addition, the "axial direction" may be understood as a direction in which the piston 130 reciprocates, that is, a transverse direction in FIG. 1. In the "axial direction", a direction from the suction part 104 toward the discharge part 105, that is, a direction in which the refrigerant flows, is defined as "front", and the opposite direction is defined as "rear".

On the other hand, the "radial direction" is a direction perpendicular to the direction in which the piston 130 reciprocates, and can be understood as the vertical direction of FIG. 1.

In the course of the piston 130 reciprocating and linear movement inside the cylinder 120, when the pressure in the compression space P is lower than the discharge pressure and less than the suction pressure, the suction valve 135 is opened and the refrigerant Is sucked into the compression space (P). On the other hand, when the pressure in the compression space P is equal to or higher than the suction pressure, the refrigerant in the compression space P is compressed while the suction valve 135 is closed.

On the other hand, when the pressure in the compression space P is greater than or equal to the discharge pressure, the first spring 230 is deformed to open the discharge valve 220, and the refrigerant is discharged from the compression space P, It is discharged to the discharge space of the discharge cover 200. When the discharge of the refrigerant is completed, the first spring 230 provides a restoring force to the discharge valve 220 so that the discharge valve 220 is closed.

In addition, the refrigerant flowing through the discharge space of the discharge cover 200 flows into the roof pipe 165. The roof pipe 165 is coupled to the discharge cover 200 and extends to the discharge part 105, and guides the compressed refrigerant in the discharge space to the discharge part 105. For example, the roof pipe 165 has a shape wound in a predetermined direction and extends roundly, and is coupled to the discharge part 105.

The linear compressor 100 further includes a frame 110. The frame 110 is configured to fix the cylinder 120 and may be fastened to the cylinder 120 by a separate fastening member. The frame 110 is disposed to surround the cylinder 120. That is, the cylinder 120 may be positioned to be received inside the frame 110. In addition, the discharge cover 200 may be coupled to the front surface of the frame 110.

On the other hand, at least some of the gas refrigerant of the high pressure discharged through the open discharge valve 220 through the space of the portion where the cylinder 120 and the frame 110 are coupled to the outer circumferential surface of the cylinder 120 It can be fluid.

In addition, the refrigerant is introduced into the cylinder 120 through a gas inlet portion 122 (see FIG. 7) and a nozzle portion 123 (see FIG. 7) formed in the cylinder 120. The introduced refrigerant may flow into the space between the piston 130 and the cylinder 120 so that the outer circumferential surface of the piston 130 is spaced apart from the inner circumferential surface of the cylinder 120. Accordingly, the introduced refrigerant may function as a “gas bearing” that reduces friction with the cylinder 120 during the reciprocating movement of the piston 130. That is, this embodiment does not employ oil bearings.

In the motor assembly 140, outer stators 141, 143, and 145 are fixed to the frame 110 and disposed to surround the cylinder 120, and an inner stator 148 that is spaced apart from the inner stator 141, 143, and 145. ) And a permanent magnet 146 positioned in the space between the outer stator 141, 143, and 145 and the inner stator 148.

The permanent magnet 146 may linearly reciprocate by mutual electromagnetic force between the outer stator 141, 143, and 145 and the inner stator 148. In addition, the permanent magnet 146 may be composed of a single magnet having one pole, or may be configured by combining a plurality of magnets having three poles.

The permanent magnet 146 may be coupled to the piston 130 by a connection member 138. In detail, the connection member 138 may be coupled to the piston flange portion 132 to extend by bending toward the permanent magnet 146. As the permanent magnet 146 reciprocates, the piston 130 may reciprocate together with the permanent magnet 146 in the axial direction.

Further, the motor assembly 140 further includes a fixing member 147 for fixing the permanent magnet 146 to the connection member 138. The fixing member 147 may be formed by mixing glass fiber or carbon fiber and resin. The fixing member 147 is provided to surround the inner and outer sides of the permanent magnet 146, so that the permanent magnet 146 and the connection member 138 may be firmly maintained in a coupled state.

The outer stator (141,143,145) includes coil winding bodies (143,145) and a stator core (141).

The coil winding bodies 143 and 145 include a bobbin 143 and a coil 145 wound in the circumferential direction of the bobbin 143. The cross section of the coil 145 may have a polygonal shape, and for example, may have a hexagonal shape.

The stator core 141 is configured by stacking a plurality of laminations in a circumferential direction, and may be disposed to surround the coil winding bodies 143 and 145.

A stator cover 149 is provided on one side of the outer stator 141, 143, and 145. One side of the outer stator 141, 143, and 145 may be supported by the frame 110, and the other side may be supported by the stator cover 149.

The inner stator 148 is fixed to the outer periphery of the frame 110. In addition, the inner stator 148 is configured by stacking a plurality of laminations from the outside of the frame 110 in the circumferential direction.

The linear compressor 100 further includes a supporter 137 supporting the piston 130 and a back cover 170 spring-coupled to the supporter 137.

The supporter 137 is coupled to the piston flange portion 132 and the connection member 138 by a predetermined fastening member.

In front of the back cover 170, a suction guide part 155 is coupled. The suction guide part 155 guides the refrigerant sucked through the suction part 104 to flow into the suction muffler 150.

The linear compressor 100 includes a plurality of springs 176 whose natural frequencies are adjusted so that the piston 130 can perform resonant motion.

The plurality of springs 176 include a first spring supported between the supporter 137 and the stator cover 149 and a second spring supported between the supporter 137 and the back cover 170 do.

The linear compressor 100 further includes leaf springs 172 and 174 provided on both sides of the shell 101 so that the internal components of the compressor 100 are supported by the shell 101.

The leaf springs 172 and 174 include a first leaf spring 172 coupled to the first cover 102 and a second leaf spring 174 coupled to the second cover 103. As an example, the first plate spring 172 may be fitted into a portion where the shell 101 and the first cover 102 are coupled, and the second plate spring 174 is 2 The cover 103 may be arranged to be fitted to a portion to which it is coupled.

2 is a cross-sectional view showing the configuration of a suction muffler according to the first embodiment of the present invention.

Referring to FIG. 2, in a suction muffler 150 according to an embodiment of the present invention, a first muffler 151, a second muffler 153 coupled to the first muffler 151, and the first muffler ( A first filter 310 supported by the 151 and the second muffler 153 is included.

The first muffler 151 and the second muffler 153 have a flow space portion through which a refrigerant flows. In detail, the first muffler 151 extends from the inside of the suction part 104 toward the discharge part 105, and at least a portion of the first muffler 151 is inside the suction guide part 155 Is extended to. In addition, the second muffler 153 extends from the first muffler 151 to the inside of the piston body 131.

The first filter 310 is understood as a configuration installed in the flow space to filter foreign matter. Since the first filter 310 is made of a material having magnetic properties, it is possible to easily filter foreign matter contained in the refrigerant, particularly metal dirt. For example, the first filter 310 may be made of stainless steel, and thus may have a predetermined magnetic property and a rust phenomenon may be prevented.

As another example, the first filter 310 may be coated with a magnetic material or configured to attach a magnet to the surface of the first filter 310.

The first filter 310 may be configured in a mesh type having a plurality of filter holes, and may have a substantially disk shape. In addition, the filter hole may have a diameter or width less than or equal to a predetermined size. For example, the predetermined size may be about 25 μm.

The first muffler 151 and the second muffler 153 may be assembled by a press-fitting method. In addition, the first filter 310 may be assembled by being fitted into a press-fit portion of the first muffler 151 and the second muffler 153.

For example, one of the first muffler 151 and the second muffler 153 may have a groove portion, and the other may include a protrusion into which the groove portion is inserted. When both side portions of the first filter 310 are interposed between the groove portion and the protrusion portion, the first filter 310 may be supported by the first and second mufflers 151 and 153.

In detail, while the first filter 310 is positioned between the first and second mufflers 151 and 153, the first muffler 151 and the second muffler 153 move in a direction closer to each other and press fit. Then, both side portions of the first filter 310 may be fitted and fixed between the groove portion and the protrusion portion.

In this way, since the first filter 310 is provided to the suction muffler 150, foreign substances having a predetermined size or more among the refrigerant sucked through the suction unit 104 may be filtered by the first filter 310. . Therefore, foreign matters are contained in the refrigerant acting as a gas bearing between the piston 130 and the cylinder 120, and it is possible to prevent the foreign matter from flowing into the cylinder 120.

In addition, since the first filter 310 is firmly fixed to the press-fit portion of the first and second mufflers 151 and 153, separation from the suction muffler 150 can be prevented.

3 is a cross-sectional view showing the peripheral configuration of a discharge cover and a discharge valve according to a first embodiment of the present invention, and FIG. 4 is an exploded perspective view showing the configuration of a cylinder and a frame according to the first embodiment of the present invention.

3 and 4, the linear compressor 100 according to the first embodiment of the present invention further includes a discharge valve 220 that is selectively opened to discharge the refrigerant compressed in the compression space P. Included.

A rear surface of the discharge valve 220 may be installed to be in contact with a front portion of the cylinder 120. When the rear surface of the discharge valve 220 is in contact with the front portion of the cylinder 120, the refrigerant in the compression space P is compressed. And, when the pressure of the compression space (P) is greater than the discharge pressure, the rear surface of the discharge valve 220 is separated from the front portion of the cylinder 120 to open the discharge valve 220, The compressed refrigerant is discharged through the spaced space.

In the linear compressor 100, a first spring 230 coupled to the front of the discharge valve 220 to elastically support the discharge valve 220, and a deformation amount of the first spring 230 is less than or equal to a set amount. A stopper 240 limited to and a second spring 270 coupled to the stopper 240 to guide the movement of the stopper 240 during abnormal operation of the compressor 100 are included.

The discharge valve 220 is provided with an insertion protrusion 222 coupled to the first spring 230. Further, the stopper 240 includes protrusions 246 and 247 coupled to the second spring 270.

The elastic modulus K2 of the second spring 270 may be larger than the elastic modulus K1 of the first spring 230. Therefore, during normal operation of the compressor 100, that is, when the discharge valve 220 is normally opened or closed, the first spring 230 may be deformed and the second spring 270 may not be deformed. have.

In detail, when the pressure in the compression space P is greater than or equal to the discharge pressure, and when the discharge valve 220 is opened, the first spring 230 has a forward-deformed movement, and in this process, the stopper Reference numeral 240 interferes with the first spring 230 in front of the first spring 230 to prevent excessive deformation of the first spring 230.

On the other hand, when a control error of the compressor 100 occurs, abnormal operation may be performed. The abnormal operation includes an abnormal operation of the piston 130. For example, when the piston 130 moves forward excessively and collides with the discharge valve 220 with a force greater than or equal to a set force, the stopper ( 240) can move forward. Accordingly, an impact applied to the discharge valve 220 can be alleviated.

The linear compressor 100 includes a plurality of spacers 250 and 260 for providing a space for deformation of the valve springs 230 and 270. In the plurality of spacers 250 and 260, a first spacer 250 installed between the first spring 230 and the stopper 240 and a second spacer installed in front of the second spring 270 ( 260) are included.

The first spacer 250 may secure a space in which the first spring 230 can be deformed by separating the first spring 230 from the stopper 240 by a set distance. The set distance may be determined by an adjustable thickness of the first spacer 250.

The second spacer 260 is located between the second spring 270 and the discharge cover 200, so that the second spring 270 is spaced apart from the discharge cover 200 to be stably supported. do. In addition, the second spacer 260 secures a space in which the second spring 270 can be deformed.

The linear compressor 100 includes a second filter 320 provided between the frame 110 and the cylinder 120 to filter the high-pressure gas refrigerant discharged through the discharge valve 220. The second filter 320 may be located at a portion or a coupling surface where the frame 110 and the cylinder 120 are coupled.

In detail, the cylinder 120 includes a cylinder body 121 having a substantially cylindrical shape and a cylinder flange portion 125 extending radially from the cylinder body 121.

The cylinder body 121 includes a gas inlet 122 through which the discharged gas refrigerant is introduced. The gas inlet 122 may be formed to be recessed in a substantially circular shape along the outer circumferential surface of the cylinder body 121.

In addition, a plurality of gas inlets 122 may be provided. The plurality of gas inlet portions 122 include gas inlet portions 122a, 122b (see FIG. 6) located on one side from the central portion in the axial direction of the cylinder body 121 and a gas inlet portion positioned on the other side from the central portion in the axial direction. (122c, see Fig. 6) is included.

The cylinder flange portion 125 is provided with a fastening portion 126 coupled to the frame 110. The fastening part 126 may be configured to protrude outward from the outer circumferential surface of the cylinder flange part 125. The fastening part 126 may be coupled to the cylinder fastening hole 118 of the frame 110 by a predetermined fastening member.

The cylinder flange portion 125 includes a seating surface 127 that is seated on the frame 110. The seating surface 127 may be a rear portion of the cylinder flange portion 125 extending in the radial direction from the cylinder body 121.

The frame 110 includes a frame body 111 surrounding the cylinder body 121 and a cover coupling portion 115 extending in a radial direction of the frame body 111 and coupled to the discharge cover 200. Is included.

In the cover coupling part 115, a plurality of cover fastening holes 116 into which a fastening member coupled to the discharge cover 200 is inserted, and a plurality of cylinders into which a fastening member coupled to the cylinder flange 125 is inserted. Fastening holes 118 are formed. The cylinder fastening hole 118 is formed at a slightly recessed position from the cover coupling part 115.

The frame 110 is provided with a recessed portion 117 that is recessed rearward from the cover coupling portion 115 and into which the cylinder flange portion 125 is inserted. That is, the depression 117 may be disposed to surround the outer circumferential surface of the cylinder flange 125. The depressed depth of the depressed portion 117 may correspond to a front and rear width of the cylinder flange portion 125.

A predetermined refrigerant flow space may be formed between the inner circumferential surface of the depression 117 and the outer circumferential surface of the cylinder flange 125. The high-pressure gas refrigerant discharged from the discharge valve 220 may flow toward the outer peripheral surface of the cylinder body 121 through the refrigerant flow space. The second filter 320 may be installed in the refrigerant flow space to filter the refrigerant.

In detail, a seating portion provided stepwisely is formed at a rear end of the recessed portion 117, and a ring-shaped second filter 320 may be seated in the seating portion.

In a state in which the second filter 320 is seated on the seating portion, when the cylinder 120 is coupled to the frame 110, the cylinder flange 125 is in front of the second filter 320 The second filter 320 is pressed. That is, the second filter 320 may be interposed and fixed between the seating portion of the frame 110 and the seating surface 127 of the cylinder flange portion 125.

The second filter 320 blocks foreign substances from flowing into the gas inlet 122 of the cylinder 120 from among the high-pressure gas refrigerant discharged through the open discharge valve 220, and contains oil contained in the refrigerant. It can be configured to adsorb.

For example, the second filter 320 may include a nonwoven fabric or an adsorption fabric made of polyethylene terephthalate (PET) fibers. The PET has the advantage of excellent heat resistance and mechanical strength. In addition, it is possible to block foreign substances of 2 μm or more in the refrigerant.

The high-pressure gas refrigerant passing through the flow space between the inner circumferential surface of the depression 117 and the outer circumferential surface of the cylinder flange 125 passes through the second filter 320, and in this process, the refrigerant is filtered. I can.

5 is a cross-sectional view showing a combination of a cylinder and a piston according to a first embodiment of the present invention, FIG. 6 is an exploded perspective view showing the configuration of a cylinder according to the first embodiment of the present invention, and FIG. It is an enlarged cross-sectional view of "A".

5 to 7, the cylinder 120 according to the first embodiment of the present invention has a substantially cylindrical shape and forms a first body end 121a and a second body end 121b ( 121) and a cylinder flange portion 125 extending radially outward from the second body end portion 121b of the cylinder body 121.

The first body end 121a and the second body end 121b form both ends of the cylinder body 121 with respect to the central portion 121c in the axial direction of the cylinder body 121.

The cylinder body 121 is provided with a plurality of gas inlet portions 122 through which at least a portion of the refrigerant of the high-pressure gas discharged through the discharge valve 220 flows. A third filter 330 as a “filter member” may be disposed in the plurality of gas inlets 122.

The plurality of gas inlets 122 are configured to be depressed by a predetermined depth and width from the outer circumferential surface of the cylinder body 121. The refrigerant may be introduced into the cylinder body 121 through the plurality of gas inlet portions 122 and nozzle portions 123.

In addition, the introduced refrigerant is located between the outer circumferential surface of the piston 130 and the inner circumferential surface of the cylinder 120, and functions as a gas bearing for the movement of the piston 130. That is, by the pressure of the introduced refrigerant, the outer circumferential surface of the piston 130 is kept spaced apart from the inner circumferential surface of the cylinder 120.

The plurality of gas inlets 122 include a first gas inlet 122a and a second gas inlet 122b positioned at one side from the axial center 121c of the cylinder body 121, and the shaft A third gas inlet 122c positioned on the other side from the direction central portion 121c is included.

The first and second gas inlets 122a and 122b are located closer to the second body end 121b with respect to the axial central portion 121c of the cylinder body 121, and the third gas inlet portion 122c may be positioned closer to the first body end 121a with respect to the central portion 121c in the axial direction of the cylinder body 121.

That is, the plurality of gas inlets 122 are arranged in an asymmetrical number with respect to the central portion 121c in the axial direction of the cylinder body 121.

Referring to FIG. 1, the internal pressure of the cylinder 120 is more on the side of the second body end 121b close to the discharge side of the compressed refrigerant compared to the side of the first body end 121a close to the suction side of the refrigerant. Since it is formed high, more gas inlet portions 122 are formed on the side of the second body end 121b to enhance the function of the gas bearing, and relatively few gas inlet portions 122 are formed on the side of the first body end 121a. ) Can be formed.

The cylinder body 121 further includes a nozzle part 123 extending from the plurality of gas inlet parts 122 in a direction of the inner circumferential surface of the cylinder body 121. The nozzle part 123 is formed to have a smaller width or size than the gas inlet part 122.

A plurality of nozzle portions 123 may be formed along the gas inlet portion 122 extending in a circular shape. In addition, the plurality of nozzle units 123 are disposed to be spaced apart from each other.

The nozzle part 123 includes an inlet part 123a connected to the gas inlet part 122 and an outlet part 123b connected to an inner circumferential surface of the cylinder body 121. The nozzle part 123 is formed to have a predetermined length from the inlet part 123a toward the outlet part 123b.

The refrigerant introduced into the gas inlet part 122 is filtered by the third filter 330 and then flows to the inlet part 123a of the nozzle part 123, and the cylinder along the nozzle part 123 It flows in the direction of the inner circumferential surface of (120). Then, the refrigerant flows into the inner space of the cylinder 120 through the outlet part 123b.

The piston 130 moves away from the inner circumferential surface of the cylinder 120 by the pressure of the refrigerant discharged from the outlet part 123b, that is, rises from the inner circumferential surface of the cylinder 120. That is, the pressure of the refrigerant supplied to the inside of the cylinder 120 provides a levitation force or a levitation pressure to the piston 130.

The depth and width of the plurality of gas inlets 122 and the length L of the nozzle part 123 are determined by the stiffness of the cylinder 120, the amount of the third filter 330, or the nozzle An appropriate size may be determined in consideration of the size of the pressure drop of the refrigerant passing through the unit 123.

For example, when the depth and width of the plurality of gas inlets 122 are too large or the length of the nozzle unit 123 is too small, the stiffness of the cylinder 120 may be weakened. On the other hand, if the depth and width of the plurality of gas inlets 122 are too small, the amount of the third filter 330 that can be installed in the gas inlet 122 may be too small.

In addition, when the length of the nozzle part 123 is too large, the pressure drop of the refrigerant passing through the nozzle part 123 becomes too large, so that a sufficient function as a gas bearing cannot be performed.

The diameter of the inlet part 123a of the nozzle part 123 is larger than the diameter of the outlet part 123b. Based on the flow direction of the refrigerant, the flow cross-sectional area of the nozzle part 123 is gradually smaller as it goes from the inlet part 123a to the outlet part 123b.

In detail, when the diameter of the nozzle part 123 is too large, the amount of refrigerant flowing into the nozzle part 123 among the high-pressure gas refrigerant discharged through the discharge valve 220 becomes too large, resulting in a loss of flow rate of the compressor. There is a problem that becomes large. On the other hand, when the diameter of the nozzle part 123 is too small, the pressure drop in the nozzle part 123 increases, and there is a problem that the performance as a gas bearing decreases.

Therefore, in this embodiment, the diameter of the inlet part 123a of the nozzle part 123 is relatively large to reduce the pressure drop of the refrigerant flowing into the nozzle part 123, and the diameter of the outlet part 123b By forming relatively small, it is characterized in that it is possible to adjust the inflow amount of the gas bearing through the nozzle unit 123 to a predetermined value or less.

The third filter 330 blocks foreign substances of a predetermined size or more from flowing into the cylinder 120 and absorbs oil contained in the refrigerant. Here, the predetermined size may be 1 μm.

The third filter 330 includes a thread wound around the gas inlet 122. In detail, the thread is made of polyethylene terephthalate (PET) material and may have a predetermined thickness or diameter.

The thickness or diameter of the thread may be determined to be an appropriate value in consideration of the strength of the thread. If the thickness or diameter of the thread is too small, the strength of the thread becomes too weak and can be easily broken. If the thickness or diameter of the thread is too large, the thread is wound. In this case, there is a problem in that the air gap in the gas inlet 122 is too large to reduce the filtering effect of foreign matter.

For example, the thickness or diameter of the thread is formed in a unit of several hundred μm, and the thread may be formed by combining a number of strands with a spun thread of several tens of μm.

The thread is wound a plurality of times and the end thereof is configured to be fixed with a knot. The number of times the thread is wound may be appropriately selected in consideration of the degree of pressure drop of the gas refrigerant and the filtering effect of foreign matter. If the number of windings is too large, the pressure drop of the gas refrigerant becomes too large, and if the number of windings is too small, filtering of foreign matter may not be performed well.

In addition, the tension force wound around the thread is formed in an appropriate size in consideration of the degree of deformation of the cylinder 120 and the fixing force of the thread. If the tension is too large, deformation of the cylinder 120 may be caused, and if the tension is too small, the thread may not be well fixed to the gas inlet 122.

8 is a perspective view showing a discharge valve assembly coupled to a discharge cover according to a first embodiment of the present invention, and FIG. 9 is an exploded perspective view of a discharge cover and discharge valve assembly according to the first embodiment of the present invention, and FIG. 10 Is a view showing the configuration of the stopper according to the first embodiment of the present invention, Figure 11 is a view showing the operation of the discharge valve assembly according to the first embodiment of the present invention.

8 to 11, in the linear compressor 100 according to the first embodiment of the present invention, it is coupled to the front of the frame 110 and forms a discharge passage for the refrigerant discharged from the compression space (P). A discharge cover 200 is included.

The discharge cover 200 includes a cover body 200a forming a discharge passage for the refrigerant discharged through the discharge valve 220, and the frame 110 extending radially outward from the cover body 200a. A frame coupling portion 201 coupled to the pipe connection portion 201 and a pipe connection portion 202 for discharging the refrigerant through the discharge passage of the discharge body 200a to the outside of the discharge cover 200 are included. The frame coupling part 201 forms a rear surface of the discharge cover 200, and the pipe connection part 202 may be connected to the roof pipe 165.

A discharge valve assembly may be installed on the discharge cover 200. The discharge valve assembly includes a discharge valve 220, first and second springs 230 and 270, a stopper 240, and first and second spacers 250 and 260.

In detail, the cover body 200a of the discharge cover 200 includes a plurality of stepped portions 203 and 205 stepped forward from the frame coupling portion 201. In the plurality of stepped portions 203 and 205, a first stepped portion 203 formed to be recessed rearward from the frame coupling portion 201 and the first stepped portion 203 toward the resonance chamber 212 A second stepped portion 205 formed to be further recessed is included.

The cover body 200a further includes a step connection portion 203a extending radially inward from the first step portion 203 and connected to the second step portion 205. That is, the cover body 200a is configured to extend from the first step portion 203 in an inner radial direction and then further depress rearward to form the second step portion 205.

The first stepped portion 203 includes a discharge hole 204 for guiding the refrigerant through the discharge passage of the cover body 200a to the pipe connection part 202 and discharging it from the discharge cover 200 do. The discharge hole 204 is formed through at least a portion of the first stepped portion 203. The refrigerant discharged through the discharge valve 220 may flow to the pipe connection part 202 through the discharge hole 204.

The cover body 200a further includes a resonance chamber 212 that is further depressed from the second stepped portion 205 and forms a space portion for reducing the pulsation of the refrigerant. A plurality of resonance chambers 212 may be formed. In addition, at least a portion of the refrigerant discharged through the discharge valve 220 may flow in the space portion of the resonance chamber 212.

The cover body 200a further includes a seating portion 210 that partitions the plurality of resonance chambers 212 and supports the second spacers 260. The plurality of resonance chambers 212 are further depressed forward from the seating portion 210 and may be formed at positions spaced apart from each other by the seating portion 210.

A first guide groove 206 is formed in the cover body 200a as a "guide flow path" that guides at least a portion of the refrigerant discharged through the discharge valve 220 to the plurality of resonance chambers 212. The first guide groove 206 extends forward from the step connection portion 203a toward the second step portion 205. In addition, the first guide groove 206 may be formed by cutting at least a portion of the stepped connection portion 203a and the second stepped portion 205.

A plurality of first guide grooves 206 may be formed, corresponding to the number of the plurality of resonance chambers 212. The plurality of first guide grooves 206 may be formed to be spaced apart from each other.

At least a portion of the refrigerant discharged through the open discharge valve 220 flows into the plurality of resonance chambers 212 along the first guide groove 206, thereby occurring during the refrigerant flow process during the operation of the compressor. It is possible to reduce the pulsation to be performed.

A second guide groove 207 is formed in the cover body 200a to guide the coupling of the stopper 240. The second guide groove 207 guides the coupling of the guide protrusion 243 of the stopper 240. In addition, the second guide groove 207 may be formed by cutting at least a portion of the step connection portion 203a and the second step portion 205.

A plurality of second guide grooves 207 may be formed, corresponding to the number of guide protrusions 243 of the stopper 240. The plurality of second guide grooves 207 may be formed to be spaced apart from each other.

The discharge valve 220 includes a valve body 221 selectively in close contact with the front surface of the cylinder flange 125 of the cylinder 120 and a valve depression 223 that is recessed forward from the valve body 221. Is included. The valve depression 223 is a "interference prevention" that prevents at least a part of the piston 130 from interfering with the discharge valve 220 while the piston 130 is moved forward to compress the refrigerant. It is understood as "home". Here, at least a portion of the piston 130 includes a fastening member for fastening the suction valve 135 to the piston 130.

The discharge valve 220 further includes an insertion protrusion 222 protruding forward from the valve body 221 and coupled to the first spring 230. The insertion protrusion 222 may be coupled to a first insertion hole 232 formed in the first spring 230.

The cross-sectional shape of the insertion protrusion 222 and the first insertion hole 232 may have a non-circular shape. For example, the cross-sectional shape may be a polygon. Therefore, when the discharge valve 220 performs an opening/closing action in a state in which the insertion protrusion 222 is inserted into the first insertion hole 232, it is possible to prevent the discharge valve 220 from rotating itself. I can. As a result, it is possible to prevent the discharge valve 220 from being unstable, and in particular, in the case of a linear compressor using a gas bearing rather than an oil bearing as in this embodiment, it is expected that the discharge valve is lubricated by oil. Since it is difficult to do, the effect of reducing the abrasion of the discharge valve due to unstable behavior appears.

The first spring 230 includes a plate spring, and may have a substantially disk shape.

In detail, the first spring 230 is configured to be coupled to the front of the discharge valve 220 to enable elastic movement of the discharge valve 220. In the first spring 230, a first spring body 231 having a plurality of cutouts and an insertion protrusion 222 of the discharge valve 220 is formed in an approximately central portion of the first spring body 231 A first insertion hole 232 to be inserted is included.

The plurality of cutouts are configured to have a spiral, and the first spring 230 may be elastically deformed by the plurality of cutouts.

The first spring 230 includes a spring depression 233 that is depressed from an outer circumferential surface of the first spring body 231. The spring depression 233 guides the position of the guide protrusion 243 of the stopper 240.

The stopper 240 is installed in front of the first spring 230.

In detail, the stopper 240 includes a stopper body 241 that limits the amount of deformation of the first spring 230 during the deformation process of the first spring 230. The stopper body 241 has a substantially disk shape, and when the first spring 230 is deformed by a predetermined amount or more, it may be installed at a position that may interfere with the first spring 230.

The stopper 240 further includes a valve avoidance hole 242 penetrating through the stopper body 241. The valve avoidance hole 242 penetrates substantially from the center of the stopper body 241 to prevent the stopper body 241 from interfering with the insertion protrusion 222 of the discharge valve 220. That is, when the insertion protrusion 222 moves forward while the discharge valve 220 is opened, the stopper body 241 does not interfere with the insertion protrusion 222, the valve avoidance hole 242. Provides an interference avoidance space.

The stopper 240 further includes a guide protrusion 243 protruding rearward from the rear surface of the stopper body 241 to guide the connection with the discharge cover 200. When the stopper 240 is coupled to the discharge cover 200, the guide protrusion 243 moves into the cover body 200a along the second guide groove 207.

The guide protrusion 243 may be coupled to the spring depression 233 of the first spring 230 and the spacer groove 252 of the first spacer 250. Accordingly, the first spring 230, the stopper 240, and the first spacer 250 may be stably coupled.

For example, the stopper 240 may be fixed by press-fitting into the second guide groove 207 while the guide protrusion 243 is coupled to the spring depression 233 and the spacer groove 252. have. Therefore, the stopper 240 can be stably coupled to the discharge cover 200 without a separate fastening member.

The first spacer 250 may be interposed between the first spring 230 and the stopper 240 so that the first spring 230 is spaced apart from the stopper 240.

In detail, the first spacer 250 has a first spacer body 251 having an approximately ring shape and a position of the guide protrusion 243 of the stopper 240 by being depressed from the outer peripheral surface of the first spacer body 251 It includes a spacer groove 252 to guide the.

In front of the stopper 240, a second spring 270 that guides the movement of the stopper 240 during emergency operation of the compressor 100 is included. The second spring 270 is configured to elastically support the stopper 240.

In the second spring 270, a second spring body 271 having a substantially disk shape and a second insertion hole 272 that penetrates into the substantially central portion of the second spring body 271 and is coupled to the stopper 240 This includes. The second insertion hole 272 may have a non-circular shape, for example, a polygonal shape, similar to the shape of the first insertion hole 232 of the first spring 230.

The stopper 240 includes protrusions 246 and 247 protruding forward from the front surface of the stopper body 241. The protrusions 246 and 247 include a first protrusion 246 protruding forward from the stopper body 241 and a second protrusion 247 protruding further forward from the first protrusion 246.

The first protrusion 246 functions as a support device for the second spring 270, and the second protrusion 247 is inserted into the second insertion hole 272 of the second spring 270 It can function as a device.

In detail, the diameter of the second protrusion 247 is formed such that it can be inserted into the second insertion hole 272 of the second spring 270. And, the diameter of the first protrusion 246 is formed larger than the second insertion hole 272 of the second spring 270, the first protrusion 246 is the rear of the second spring 270 It is configured to support the second spring 270 in.

11 shows a state in which the second spring 270 is deformed and guides the movement of the stopper 240 during emergency operation of the compressor 100.

In detail, the emergency operation of the compressor 100 includes, for example, an operation in which the piston 130 and the discharge valve 220 collide due to a control error of the compressor. In this case, the force or load F acting on the discharge valve 220 is a force or load acting on the discharge valve 220 during normal operation of the compressor 100, that is, a force acting by the discharge refrigerant. Or it can be formed larger than the load.

Therefore, when the compressor 100 is in an emergency operation, the second spring 270 is deformed so that the stopper 240 moves forward, so that the force or load applied to the discharge valve 220 is applied to the stopper ( 240) and the second spring 270. As a result, it is possible to reduce the wear of the discharge valve 220.

The elastic modulus of the second spring 270 is greater than that of the first spring 230. Accordingly, during the process of opening and closing the discharge valve 220 during normal operation of the compressor 100, the second spring 270 may not be deformed. On the other hand, when an excessive force or load is applied to the discharge valve 220 during abnormal operation of the compressor 100, the second spring 270 may be deformed to guide the movement of the stopper 240. .

The second spacer 260 is mounted on the mounting portion 210 of the cover body 200a and configured to support the second spring 270. That is, the second spacer 260 is positioned between the seating portion 210 and the second spring 270 so that the second spring 270 can be spaced apart from the seating portion 210. . When the second spring 270 is deformed, a space between the second spring 270 and the seating part 210 may provide a space in which the second spring 270 can be deformed.

The second spacer 260 includes a second spacer body 261 supporting the front surface of the second spring 270 and having a hollow disk shape, and an edge protruding rearward along the circumference of the spacer body 261 Part 262 is included. The rim portion 262 is configured to surround the outer circumferential surface of the second spring 270 and supports the second spring 270.

When the stopper 240 is press-fitted to the discharge cover 200, the second spring 270 and the second spacer 260 may be provided with a seating portion 210 of the discharge cover 200 and the stopper. It can be stably supported among 240.

12 is a cross-sectional view showing the flow of refrigerant in the linear compressor according to the first embodiment of the present invention, and FIG. 13 is a cross-sectional view showing the action of the discharge valve assembly when operating the linear compressor according to the first embodiment of the present invention. .

12 and 13, the refrigerant flows into the shell 101 through the suction part 104 and flows into the suction muffler 150 through the suction guide part 155.

Then, the refrigerant flows into the second muffler 153 via the first muffler 151 of the suction muffler 150 and flows into the piston 130. In this process, the suction noise of the refrigerant can be reduced.

Meanwhile, the refrigerant may filter foreign matter having a predetermined size (25 μm) or more while passing through the first filter 310 provided to the suction muffler 150.

When the suction valve 135 is opened, the refrigerant passing through the suction muffler 150 and present in the piston 130 is sucked into the compression space P through the suction hole 133.

When the refrigerant pressure in the compression space (P) exceeds the discharge pressure, the discharge valve 220 is opened, and the refrigerant is discharged to the discharge space of the discharge cover 200 through the opened discharge valve 220, and the discharge cover It flows to the discharge part 105 through the loop pipe 165 coupled to the 200, and is discharged to the outside of the compressor 100.

When the discharge valve 220 is opened, the first spring 230 may be elastically deformed forward, and the stopper 240 may prevent the first spring 230 from being deformed more than a set amount. have.

In particular, as in the present embodiment, when the linear compressor 100 is operated at a high frequency, the degree of opening of the discharge valve 220, that is, the movement distance of the discharge valve 220 increases. Accordingly, when the discharge valve 220 is closed, the amount of impact applied to the discharge valve 220 increases, and thus the amount of wear of the discharge valve 220 may increase. In particular, when oil is not used and gas bearings are applied, this wear phenomenon can be increased.

Therefore, in this embodiment, the discharge valve 220 is elastically supported by the first spring 230, and the discharge valve 220 is opened by installing a stopper 240 on one side of the valve spring 230. The amount or degree of opening can be limited.

On the other hand, at least some of the refrigerants present in the discharge space of the discharge cover 200 are space existing between the cylinder 120 and the frame 110, that is, the inner circumferential surface of the depression 117 of the frame 110, Through a flow space formed between the outer circumferential surface of the cylinder flange 125 of the cylinder 120, it may flow toward the outer circumferential surface of the cylinder body 121.

At this time, the refrigerant may pass through the second filter 320 interposed between the seating surface 127 of the cylinder flange 125 and the seating portion 113 of the frame 110, and in this process, a predetermined size Foreign matter (2μm) or more can be filtered. In addition, the oil of the refrigerant may be adsorbed to the second filter 320.

The refrigerant that has passed through the second filter 320 is introduced into a plurality of gas inlet portions 122 formed on the outer circumferential surface of the cylinder body 121. In addition, while the refrigerant passes through the third filter 330 provided in the gas inlet 122, foreign matters of a predetermined size (1 μm) or more contained in the refrigerant may be filtered, and oil contained in the refrigerant may be adsorbed. have.

The refrigerant that has passed through the third filter 330 is introduced into the cylinder 120 through the nozzle unit 123 and is located between the inner circumferential surface of the cylinder 120 and the outer circumferential surface of the piston 130, and the piston ( 130) acts to be spaced apart from the inner circumferential surface of the cylinder 120 (gas bearing).

At this time, the diameter of the inlet part 123a of the nozzle part 123 is larger than the diameter of the outlet part 123b, and accordingly, the refrigerant flow cross-sectional area in the nozzle part 123 based on the flow direction of the refrigerant is It gradually decreases. As an example, the diameter of the inlet portion 123a may have a value equal to or greater than twice the diameter of the outlet portion 123b.

In this way, the high-pressure gas refrigerant is bypassed into the inside of the cylinder 120 to act as a bearing for the piston 130 that reciprocates, thereby reducing wear between the piston 130 and the cylinder 120. . In addition, by not using oil for bearings, even if the compressor 100 is operated at high speed, friction loss due to oil may not be generated.

In addition, by providing a plurality of filters on the path of the refrigerant flowing inside the compressor 100, foreign matter contained in the refrigerant can be removed, and accordingly, the reliability of the refrigerant serving as a gas bearing can be improved. Accordingly, it is possible to prevent the occurrence of wear on the piston 130 or the cylinder 120 due to foreign substances contained in the refrigerant.

In addition, by removing the oil contained in the refrigerant by the plurality of filters, it is possible to prevent the occurrence of friction loss due to the oil. Since the first filter 310, the second filter 320, and the third filter 330 filter refrigerant to serve as a gas bearing, they may be collectively referred to as a “refrigerant filter device”.

Meanwhile, when the compressor 100 operates abnormally due to a control error of the compressor 100 during the normal operation of the compressor 100 as shown in FIG. 13, the second spring 270 is deformed. The stopper 240 may move forward (see FIG. 11).

In detail, a phenomenon in which the reciprocating piston 130 collides with the discharge valve 220 may occur due to a control error of the compressor 100. In this case, the force applied to the discharge valve 220 may be greater than the force applied to the discharge valve 220 when the discharge valve 220 is normally opened as described in FIG. 12.

In this case, the second spring 270 may be deformed together with the first spring 230. In addition, by the deformation of the second spring 270, the stopper 240 may move forward.

Accordingly, the force applied to the discharge valve 220 may be absorbed by the second spring 270 and the stopper 240. As a result, it is possible to prevent abrasion of the discharge valve 220.

Hereinafter, a second embodiment of the present invention will be described. In this embodiment, since there is a difference in the structure of the discharge valve assembly compared to the first embodiment, the difference will be mainly described, and the description of the first embodiment and reference numerals are used for other parts.

14 is a cross-sectional view showing the configuration of a discharge valve assembly according to the second embodiment of the present invention, and FIG. 15 is a view showing the operation of the discharge valve assembly according to the second embodiment of the present invention.

14, in the discharge valve assembly according to the second embodiment of the present invention, a discharge valve 220 having an insertion protrusion 222, and an insertion coupled to the insertion protrusion 222 of the discharge valve 220 A first spring 430 having a ball and providing a restoring force to the discharge valve 220 and a damping device 432, 434, and 436 spaced apart from the first spring 430 are included.

The discharge valve assembly further includes a spacer 450 that separates the first spring 430 from the damping devices 432, 434, and 436.

The damping devices 432, 434 and 436 include a plurality of springs. The plurality of springs include a second spring 432, a third spring 434 and a fourth spring 436. The second, third, and fourth springs 432, 434, and 436 may be coupled to each other to be arranged side by side in the front and rear directions.

The first spring 430 guides the opening of the discharge valve 220 while being deformed forward when the compressor 100 is normally operated, that is, when the compressed refrigerant is discharged from the compression space P. In addition, when the discharge of the compressed refrigerant is completed, a restoring force is provided to the discharge valve 220 to guide the closing of the discharge valve 220.

The damping devices 432, 434, 436, when abnormal operation of the compressor 100 occurs, for example, when a reciprocating piston 130 collides with the discharge valve 220 due to a control error of the compressor 100 , Is configured to absorb an impact force acting on the discharge valve 220.

The elastic modulus of the second to fourth springs 432, 434 and 436 constituting the damping devices 432, 434, and 436 is formed larger than that of the first spring 430. During normal operation of the compressor 100, the first spring 430 may be deformed, but the second to fourth springs 432, 434, and 436 may not be deformed. In addition, leaf springs may be included in the first to fourth springs 430, 432, 434, and 436.

The linear compressor 100 further includes a damping mounting portion 460 on which the damping devices 432, 434, and 436 are mounted. The damping mounting part 460 is mounted on the mounting part 210 of the discharge cover 200 described in the first embodiment to support the damping devices 432, 434, and 436.

The linear compressor 100 further includes a fastening member 480 for fixing the first spring 430 and the damping devices 432, 434, 436 to the damping mounting part 460. The fastening member 480 may pass through the first spring 430, the spacer 450 and the damping devices 432, 434, 436, and may be coupled to the damping mounting part 460.

Referring to FIG. 15, when a force (F) greater than a set force is applied to the discharge valve 220 during an abnormal operation of the compressor 100, an excessive forward deformation may occur in the first spring 430. have.

In addition, the first spring 430 may pressurize the damping devices 432, 434, and 436, and in this process, the second to fourth springs 432, 434, and 436 may be deformed forward.

In this way, when the second to fourth springs 432, 434, and 436 are deformed, the force acting on the discharge valve 220 may be transmitted to the damping devices 432, 434, and 436.

That is, the force acting on the discharge valve 220 may be absorbed by the damping devices 432, 434, and 436, and thus, abrasion of the discharge valve 220 may be prevented. As a result, it is possible to prevent a foreign material caused by abrasion of the discharge valve 220 from acting on the nozzle part 123 of the cylinder 120 and adversely affecting the gas bearing.

100: linear compressor 101: shell
110: frame 111: frame body
115: cover coupling portion 117: recessed portion
120: cylinder 121: cylinder body
122: gas inlet 123: nozzle part
123a: inlet part 123b: outlet part
125: cylinder flange portion 127: seating surface
130: piston 140: motor assembly
150: suction muffler 165: roof pipe
171,172: leaf spring 200: discharge cover
204: discharge hole 210: seating portion
212: resonance chamber 220: discharge valve
230: first spring 240: stopper
250: first spacer 260: second spacer
270: second spring 310: first filter
320: second filter 330: third filter

Claims (17)

A shell provided with a discharge unit;
A cylinder provided inside the shell and forming a compression space for a refrigerant;
A frame fixing the cylinder to the shell;
A piston provided so as to reciprocate in the axial direction inside the cylinder;
A discharge valve provided on one side of the cylinder and selectively discharging the refrigerant compressed in the compression space of the refrigerant;
A discharge cover coupled to the frame and having a seating portion forming a resonance chamber for reducing pulsation of the refrigerant discharged through the discharge valve;
A first spring coupled to the discharge valve to provide a restoring force to the discharge valve;
A damping device installed on one side of the first spring and distributing a force acting on the discharge valve when the piston operates abnormally; And
It is seated on the seating portion, and includes a support structure for fixing and supporting the damping device,
The damping device includes a leaf spring having a helical cutout,
The leaf spring is spaced apart from the first spring and has a greater modulus of elasticity than the first spring,
The support structure is a linear compressor that separates the leaf spring from the seating portion and forms a space in which the leaf spring can be deformed forward. delete The method of claim 1,
A linear compressor coupled to the first spring and further comprising a stopper for limiting an opening amount of the discharge valve. The method of claim 3,
The leaf spring of the damping device is defined as a second spring,
The stopper is a linear compressor, characterized in that installed between the first spring and the second spring. The method of claim 3,
The linear compressor further comprises a first spacer installed between the first spring and the stopper to separate the first spring from the stopper. The method of claim 1,
The support structure,
And a second spacer in the shape of a hollow disk for supporting the damping device,
The second spacer,
A second spacer body having the hollow disk shape; And
A linear compressor that protrudes rearward along a circumference of the second spacer body and includes an edge portion surrounding an outer circumferential surface of the leaf spring. The method of claim 1,
A linear compressor including a leaf spring in the first spring. The method of claim 1,
When the piston operates normally, deformation of the leaf spring of the damping device is limited, and when the piston operates abnormally, the leaf spring of the damping device is deformed. The method of claim 3,
In the stopper,
A stopper body capable of supporting the first spring; And
A linear compressor comprising a guide protrusion protruding from the stopper body and movably coupled along a guide groove of the discharge cover. The method of claim 1,
A linear compressor having a plurality of leaf springs of the damping device. The method of claim 10,
And a spacer installed between the plurality of leaf springs and the first spring to separate the plurality of springs from the first spring,
The support structure includes a damping mounting portion for fixing the plurality of leaf springs and the spacer. The method of claim 11,
A linear compressor further comprising a fastening member for coupling the first spring, the plurality of leaf springs, and the spacer to the damping mounting portion. A shell provided with a discharge unit;
A cylinder provided inside the shell and forming a compression space for a refrigerant;
A piston provided so as to reciprocate in the front-rear direction within the cylinder;
A discharge valve provided on one side of the cylinder and selectively discharging the refrigerant compressed in the compression space of the refrigerant;
A discharge cover having a seating portion forming a resonance chamber for reducing pulsation of the refrigerant discharged through the discharge valve;
A first spring coupled to the discharge valve to provide a restoring force to the discharge valve;
A stopper coupled to the first spring to limit the amount of deformation of the first spring;
A ring-shaped first spacer installed between the stopper and the first spring;
A second spring coupled to the stopper, guiding the movement of the stopper, and having a greater modulus of elasticity than the first spring; And
A linear compressor that is seated on the seating portion to support the second spring so as to be spaced apart from the discharge cover, and includes a second spacer having a hollow disk shape. The method of claim 13,
The first spring is coupled to the rear of the stopper, and the second spring is coupled to the front of the stopper. The method of claim 13,
In the stopper,
A stopper body capable of supporting the first spring;
A linear compressor including a first protrusion protruding from one surface of the stopper body to support the second spring. The method of claim 15,
In the stopper,
The linear compressor further includes a second protrusion protruding from the first protrusion and inserted into the insertion hole of the second spring. The method of claim 13,
When the refrigerant is discharged from the compression space, the first spring is deformed forward so that the discharge valve is movable forward,
When the piston collides with the discharge valve in an abnormal operation, the second spring is deformed forward so that the stopper can move forward.

Images