Linear compressor

Abstract

A linear compressor according to the present invention may comprise: a discharge valve for discharging a compressed high-pressure refrigerant; a discharge cover assembly for forming a discharge chamber for the refrigerant discharged through the discharge valve; a frame for supporting the discharge cover assembly; and a cylinder which is supported inside the frame and into which a piston reciprocating in the axial direction is inserted. An embodiment may comprise: a valve spring which supports the discharge valve and reciprocates in the axial direction; a spring bracket which supports the valve spring and is fastened to the discharge cover assembly; and a damping member which is placed on the spring bracket and dampens the vibrations of the valve spring.

Description

Linear compressor

[0001] The present invention relates to a linear compressor.

[0002] In a reciprocating compressor, a compression space for compressing the working gas is formed between the piston and the cylinder, and the piston compresses the refrigerant introduced into the compression space as it moves in a straight line back and forth inside the cylinder.

[0003] Recently, among the aforementioned reciprocating compressors, many linear compressors have been developed that are simple in structure and can improve compression efficiency without mechanical losses occurring when converting the motor's rotational motion into linear motion, by directly connecting the piston to a drive motor that performs reciprocating linear motion.

[0004] Generally, a linear compressor is configured such that a piston moves in a reciprocating linear motion inside a cylinder driven by a linear motor within a sealed shell, drawing in and compressing refrigerant, and then discharging it.

[0005] The high-temperature refrigerant compressed in the compression space of the cylinder can flow toward the discharge cover via the discharge valve. The discharge cover is coupled to a frame supporting the cylinder and can form a discharge chamber through which the high-temperature discharge gas flows.

[0006] The discharge valve described above can repeatedly open and close. When the discharge valve is closed, a tapping sound may be generated. When the discharge valve is closed, the cylinder may be struck. The tapping sound may be generated in correspondence with the movement frequency of the piston. The tapping sound of the discharge valve may cause deterioration of the linear compressor. The tapping sound may cause vibration noise.

[0007] The present invention aims to propose a linear compressor capable of reducing vibration transmission by providing a damping member in the transmission path of the discharge valve.

[0008] The present invention aims to propose a linear compressor that performs a vibration reduction function directly in a vibration path passing through a valve spring supporting the discharge valve.

[0009] The present invention aims to propose a linear compressor that provides a damping member on a path passing through the discharge side of the linear compressor, through which the torn sound of the discharge valve is mainly transmitted.

[0010] The present invention aims to propose a linear compressor that can be used for a long time by providing a damping member with high heat resistance and oil resistance as a damping member inside the linear compressor.

[0011] The present invention aims to propose a linear compressor that firmly supports a damping member to prevent performance degradation of the damping member and improve production yield.

[0012] An embodiment of the present invention may include: a discharge valve for discharging a compressed high-pressure refrigerant; a discharge cover assembly for forming a discharge chamber for the refrigerant discharged through the discharge valve; a frame for supporting the discharge cover assembly; and a cylinder supported inside the frame and into which a piston that reciprocates in the axial direction is inserted.

[0013] An embodiment may include a valve spring that supports the discharge valve and reciprocates in the axial direction; a spring bracket that supports the valve spring and is fastened to the discharge cover assembly; and a damping member that rests on the spring bracket and reduces vibration of the valve spring.

[0014] The damping member may be provided in front of the valve spring. The damping member may contact the front surface of the valve spring. The damping member may be aligned vertically with the outer circumference of the valve spring.

[0015] The damping member may have a thickness of 0.5 to 1 mm in the axial direction. A damping cover for fixing the damping member may be provided at the front of the damping member.

[0016] The above discharge cover assembly may include a first discharge cover forming a first discharge chamber for refrigerant, and a second discharge cover coupled to the first discharge cover and forming a discharge chamber for refrigerant discharged from the first discharge chamber.

[0017] The first discharge cover may include an inner wall defining the first discharge chamber, an outer wall defining the discharge chamber of the second discharge cover, and a connecting rib connecting the inner wall and the inner surface of the outer wall in a radial direction.

[0018] The damping cover can be axially fixed to at least one of the inner wall or the connecting rib.

[0019] The damping cover may be placed in front of the damping member. The damping cover and the damping member may come into contact with each other. The damping cover may cover the entire damping member. The damping cover and the valve spring may not come into contact. The position of the damping cover may be supported by the inner surface of the spring bracket and / or the damping member.

[0020] The above spring bracket or the above damping cover may be made of plastic.

[0021] The embodiment may include a weight reduction portion provided on the outer surface of the damping cover. The embodiment may include a weight reduction corresponding portion provided on the inner surface of the spring bracket in correspondence with the weight reduction portion.

[0022] The above-mentioned weight loss portion may include two consecutive contraction portions. An embodiment may include contraction portions provided at both ends of the above-mentioned weight loss corresponding portion.

[0023] The above weight loss portions may be provided in three equal intervals in the circumferential direction.

[0024] The radial inner end of the damping member may be located within the fixed portion area of ​​the valve spring.

[0025] An embodiment may include a sealing recess that accommodates a first valve sealing member on the outer surface of the spring bracket. An embodiment may include a deformation recess provided on the outer surface of the spring bracket. An embodiment may include a second valve sealing member provided at the contact portion between the rear end of the spring bracket and the cylinder.

[0026] The first valve sealing member may have a dominant vibration-noise reduction among vibration-noise reduction and thermal insulation. The second valve sealing member may have a dominant thermal insulation among vibration-noise reduction and thermal insulation.

[0027] The above damping member may be made of FKM. The above damping member may be made of HNBR.

[0028] An embodiment may include a discharge valve assembly for controlling the discharge of compressed high-pressure refrigerant; a discharge cover assembly for forming a discharge chamber for the refrigerant discharged through the discharge valve assembly; and a frame for supporting the discharge cover assembly.

[0029] An embodiment may include a cylinder into which a piston that reciprocates axially is inserted, supported inside the frame. An embodiment may include a damping member adjacent to the discharge valve assembly to reduce noise generated by the cylinder.

[0030] The above discharge valve assembly may include: a discharge valve; a valve spring that supports the discharge valve and reciprocates in the axial direction; a spring bracket that supports the valve spring and is fastened to the discharge cover assembly; and a damping member that is fastened to the spring bracket and reduces vibration of the valve spring.

[0031] The above damping member can be fixed in position by a damping cover made of the same material as the spring bracket.

[0032] An embodiment may include a damping member that is fixed to the discharge valve assembly and dampens the transmission of tapping sounds generated in the discharge valve and the cylinder to the discharge cover assembly. The damping member may have the shape of a ring.

[0033] According to an embodiment of the present invention, a damping member is provided in the transmission path of the discharge valve to reduce vibration transmitted to the discharge cover side.

[0034] The present invention can directly perform vibration reduction in the vibration transmission path by having a damping member contact and support the valve spring that supports the discharge valve.

[0035] The present invention can reduce vibration and noise transmitted to the discharge cover by providing a damping member on the sound transmission path passing through the discharge side of a linear compressor.

[0036] The present invention enables the linear compressor to be operated reliably for a long time by applying FKM, which has high heat resistance and oil resistance, as a damping member.

[0037] The present invention can maximize the action of the damping member by firmly supporting the damping member.

[0038] The present invention allows sufficient elastic deformation to occur when the damping cover and spring bracket supporting the damping member are fastened together. Accordingly, damage during the fastening of parts can be prevented, and the production yield of good products can be improved.

[0039] FIG. 1 is a cross-sectional view of a linear compressor according to a first embodiment.

[0040] FIG. 2 is a cross-sectional view taken along 2-2 of FIG. 1.

[0041] FIG. 3 is a cross-sectional view taken along 2-2 of FIG. 1, assuming a linear compressor of the second embodiment.

[0042] FIG. 4 is an enlarged view of the periphery of the discharge valve assembly in FIG. 3.

[0043] FIG. 5 is a cross-sectional view of a discharge valve assembly.

[0044] FIG. 6 is a drawing illustrating the fastening of a damping cover.

[0045] FIG. 7 is a perspective view of a damping cover.

[0046] FIG. 8 is a perspective view of a damping member.

[0047] FIG. 9 is an effect graph comparing a second embodiment with a damping member and a control example without a damping member.

[0048] Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that in assigning reference numerals to the components of each drawing, the same components are given the same reference numeral whenever possible, even if they are shown in different drawings. Furthermore, in describing the embodiments of the present invention, if it is determined that a detailed description of related known components or functions would hinder understanding of the embodiments of the present invention, such detailed description is omitted.

[0049] In addition, terms such as first, second, A, B, (a), (b), etc., may be used when describing the components of the embodiments of the present invention. These terms are intended only to distinguish the components from other components, and the essence, order, or sequence of the components is not limited by the terms. Where it is stated that a component is "connected," "combined," or "connected" to another component, it should be understood that the component may be directly connected or connected to the other component, but that another component may also be "connected," "combined," or "connected" between each component.

[0050] <1st Embodiment>

[0051] FIG. 1 is a cross-sectional view of a linear compressor according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along 2-2 of FIG. 1.

[0052] Referring to FIGS. 1 and 2, a linear compressor (10) according to an embodiment of the present invention may include a shell (11) and a first shell cover (12) and a second shell cover (13) coupled to both sides of the shell (11). In a broad sense, the first shell cover (12) and the second shell cover (13) may be understood as components of the shell (11).

[0053] The shell (11) has a roughly cylindrical shape and can be arranged in a horizontally lying position or in an axially lying position. Based on FIG. 1, the shell (11) is extended horizontally and may have a somewhat lower height in the radial direction.

[0054] Since the linear compressor (10) can have a low height, for example, when the linear compressor (10) is installed on the base of the machine room of a refrigerator, there is an advantage that the height of the machine room can be reduced.

[0055] The above linear compressor (10) may include a plurality of pipes that are provided in the shell (11) or shell cover (12, 13) and can suck in, discharge, or inject refrigerant.

[0056] The plurality of pipes may include a suction pipe (14) that allows the refrigerant to be sucked into the interior of the linear compressor (10). The suction pipe (14) may be connected to the first shell cover (12). The refrigerant may be sucked into the interior of the linear compressor (10) along the axial direction through the suction pipe (14).

[0057] The plurality of pipes may further include a discharge pipe (not shown) for allowing compressed refrigerant to be discharged from the linear compressor (10) and a process pipe (not shown) for replenishing refrigerant to the linear compressor (10). For example, the discharge pipe and the process pipe may be connected to the outer surface of the shell (11).

[0058] Support devices (20, 90) that support the main body of the linear compressor (10) may be included on both sides of the shell (11). The support devices (20, 90) may include a first support device (20) that is coupled to the first shell cover (12) and elastically supports the main body of the linear compressor (10).

[0059] Here, the main body of the compressor refers to a component provided inside the shell (11), and may include, for example, a drive unit that reciprocates back and forth and a support unit that supports the drive unit. The drive unit may include a piston (70), a permanent magnet (45), a supporter (33), and an intake muffler (25), etc. And, the support unit may include a resonant spring (30), a rear cover (31), a stator cover (32), a first support device (20), and a second support device (90), etc.

[0060] The first support device (20) may include a support bracket (21a) communicating with the suction pipe (14) and a support spring (21b) coupled to the support bracket (21a) and supported by the rear cover (31).

[0061] The above support device may include a second support device (90) that is coupled to the second shell cover (13) and supports the discharge cover assembly.

[0062] The linear compressor (10) may include a frame (50) provided inside the compressor shell (11) and a cylinder (60) inserted inside the frame (50). The cylinder (60) and the frame (50) may be made of a metal material, for example, aluminum or an aluminum alloy.

[0063] The above linear compressor (10) includes a piston (70) that moves in a reciprocating linear motion inside the cylinder (60). The piston (70) can move in an axial direction.

[0064] The above linear compressor (10) may further include a suction muffler (25) coupled to the piston (70) to reduce noise generated from the refrigerant sucked through the suction pipe (14).

[0065] The refrigerant sucked in through the suction pipe (14) flows into the interior of the piston (70) via the suction muffler (25). For example, as the refrigerant passes through the suction muffler (25), the flow noise of the refrigerant can be reduced. The suction muffler (25) may be composed of a plurality of mufflers combined.

[0066] The above linear compressor (10) may include a motor assembly (41, 43, 45) as a linear motor that provides driving force to the piston (70).

[0067] The motor assembly may include an outer stator (41) fixed to the frame (50) and arranged to surround the cylinder (60), an inner stator (43) spaced apart from the inner side of the outer stator (41), and a permanent magnet (45) located in the space between the outer stator (41) and the inner stator (43).

[0068] A stator cover (32) is provided on one side of the outer stator (41). That is, one side of the outer stator (41) is supported by the frame (50), and the other side can be supported by the stator cover (32).

[0069] The permanent magnet (45) can move in a linear reciprocating motion due to the mutual electromagnetic force between the outer stator (41) and the inner stator (43). The permanent magnet (45) may be composed of a single magnet having one pole or may be composed of a plurality of magnets having three poles combined.

[0070] The above permanent magnet (45) can be installed in a magnet frame (46). The magnet frame (46) has a roughly cylindrical shape and can be positioned to be inserted into the space between the outer stator (41) and the inner stator (43).

[0071] The magnet frame (46) is coupled to the piston (70), and when the permanent magnet (45) reciprocates, the piston (70) can reciprocate in the axial direction together with the permanent magnet (45).

[0072] The linear compressor (10) may further include a supporter (33) that supports the piston (70). The supporter (33) is coupled to the rear side of the piston (730), and the muffler (25) may be positioned to pass through the inside thereof. The piston (70), the magnet frame (46), and the supporter (33) may be connected by a fastening member.

[0073] The linear compressor (10) may include a rear cover (31) that is coupled to the stator cover (32), extends rearward, and is supported by a first support device (20). The rear cover (31) may be spring-supported by the supporter (33).

[0074] The rear cover (31) may include a plurality of support legs that are coupled to the rear of the stator cover (32).

[0075] The linear compressor (10) may include an inlet guide (23) coupled to the rear cover (31) to guide the inflow of refrigerant into the intake muffler (25). At least a portion of the inlet guide (23) may be inserted into the inside of the intake muffler (25).

[0076] The above linear compressor (10) may further include a plurality of resonant springs (30) each having an adjusted natural frequency so that the piston (70) can resonate.

[0077] The plurality of resonant springs (30) may include a plurality of first resonant springs supported between the supporter (33) and the stator cover (32), and a plurality of second resonant springs supported between the supporter (33) and the rear cover (31). Through the action of the plurality of resonant springs (30), stable movement of the drive unit reciprocating inside the linear compressor (10) is performed, and vibration or noise generation due to the movement of the drive unit can be reduced.

[0078] The frame (50) is understood as a configuration for fixing the cylinder (60), and, for example, the cylinder (60) can be pressed into the inside of the frame (50). The frame (50) can be arranged to surround the cylinder (60).

[0079] The above frame (50) has a hollow cylindrical shape and includes a frame body (51) that forms a space into which the cylinder (60) is inserted, and a frame flange (52) that extends radially from the front part of the frame body (51).

[0080] A cylinder sealing member (82) may be provided between the frame (50) and the cylinder (60). By means of the cylinder sealing member (82), the adhesion force may be increased during the press-fitting process between the frame (50) and the cylinder (60).

[0081] The cylinder sealing member (82) has a ring shape and can be installed on the inner surface of the frame (50) on which the flange (62) of the cylinder (60) is seated.

[0082] The above frame (50) may have a bearing channel (58) formed therein that extends axially from the frame flange (52) toward the frame body. A refrigerant acting as a gas bearing among the compressed discharge gas may flow through the bearing channel (58).

[0083] The refrigerant acting as the gas bearing is supplied between the cylinder body (61) and the piston (70) of the cylinder (60) to cause the piston (70) to float inside the cylinder (60).

[0084] Defines the direction.

[0085] "Axial direction" can be understood as the direction in which the piston (70) reciprocates, i.e., the up-and-down direction in FIG. 2. Among the "axial directions," the direction from the piston (70) toward the compression space (P) of the cylinder (60), i.e., the direction in which the refrigerant flows, is defined as "forward," and the opposite direction is defined as "rear." When the piston (70) moves forward, the compression space (P) is reduced, and when it moves rearward, the compression space (P) can be expanded.

[0086] On the other hand, "radial direction" is a direction perpendicular to the direction in which the piston (70) reciprocates, and can be understood as the horizontal direction of FIG. 2.

[0087] A compression space (P) in which refrigerant is compressed by the piston (70) may be formed inside the cylinder (60). An intake port for introducing refrigerant into the compression space (P) is formed at the front of the piston (70), and an intake valve (75) for selectively opening the intake port may be provided in front of the intake port.

[0088] The above suction port may be provided in multiple numbers. The multiple suction ports are spaced apart in the circumferential direction of the piston (70), and refrigerant is introduced into the compression space (P) through the multiple suction ports. The suction valve (75) may be connected to the front of the piston (70) by a fastening member (78), such as a screw or a bolt.

[0089] In front of the compression space (P), a discharge cover assembly (100, 200, 300) forming a discharge space for the refrigerant discharged from the compression space (P) may be provided. The discharge cover assembly (100, 200, 300) may be positioned in front of the frame (50).

[0090] The above discharge cover assembly may include a first discharge cover (100) and a second discharge cover (200) supported on the front of the frame (50). The first discharge cover (100) may be positioned inside the second discharge cover (200).

[0091] For example, the first discharge cover (100) can be press-fitted and fixed to the second discharge cover (200). The cover flange (not shown) of the first discharge cover (100) can be press-fitted into the inner circumference of the cover flange (not shown) of the second discharge cover (200). By press-fitting the first discharge cover (100) into the second discharge cover (200), the first and second discharge covers (100, 200) can be firmly fixed.

[0092] The internal space of the first discharge cover (100) and the internal space of the second discharge cover (200) can form a discharge path (also referred to as a "discharge room") for the refrigerant discharged from the compression space (P). For example, the refrigerant discharged from the compression space (P) can flow through the internal space of the first discharge cover (100), be discharged from the first discharge cover (100), and flow into the internal space of the second discharge cover (200).

[0093] The refrigerant flowing through the discharge chamber of the first discharge cover (100) and the discharge chamber of the second discharge cover (200) can be in a high-temperature gaseous state. The high-temperature heat can be transferred to the frame (50) supporting the first and second discharge covers (100, 200).

[0094] If high-temperature heat is excessively transferred to the frame (50), that heat becomes a factor that raises the temperature (suction temperature) of the refrigerant sucked into the compression space (P) of the cylinder.

[0095] If the above suction temperature increases, the volume of refrigerant per unit mass, that is, the specific volume of the refrigerant, increases, causing a decrease in volumetric efficiency, and consequently, a problem may arise in which the compression efficiency of the compressor decreases.

[0096] To prevent such problems, the first discharge cover (100) and the second discharge cover (200) according to an embodiment of the present invention may be composed of a material having a low heat transfer coefficient. The material having a low heat transfer coefficient may be a non-metallic material.

[0097] The first discharge cover (100) and the second discharge cover (200) may include plastic.

[0098] The first discharge cover (100) and the second discharge cover (200) may be made of the same plastic material, for example, polyamide (PA66) as a type of heat-resistant engineering plastic.

[0099] By making the first discharge cover (100) of the above-mentioned first discharge cover (100) of a plastic material, the amount of high-temperature heat within the first discharge cover (100) that is directly transferred to the frame (50) supporting the first discharge cover (100) or transferred to the second discharge cover (200) that is press-fitted to the first discharge cover (100) can be reduced.

[0100] By making the second discharge cover (200) of the above-mentioned second discharge cover (200) of a plastic material, the amount of high-temperature heat within the second discharge cover (200) that is directly transferred to the frame (50) supporting the second discharge cover (200) or transferred to the first discharge cover (100) that is press-fitted to the second discharge cover (200) can be reduced.

[0101] Ultimately, it is possible to prevent excessive transfer of high-temperature heat from the refrigerant present in the discharge chamber within the first and second discharge covers (100, 200) to the frame (50). Accordingly, the suction temperature of the refrigerant can be reduced and the compression efficiency of the compressor can be improved.

[0102] Since the first and second discharge covers (100, 200) are made of a relatively lightweight plastic material, there is a possibility that vibration and noise may occur in the first and second discharge covers (100, 200) due to the high-pressure refrigerant discharged from the compression space (P).

[0103] To prevent such problems, the discharge cover assembly according to the present embodiment may include a damping member (180) for reducing vibration of the first and second covers (100, 200).

[0104] The damping member (180) is mounted in the recess of the first discharge cover (100), and the inner wall of the second discharge cover (200) may be configured to support or press the damping member (180).

[0105] The damping member (180) can offset the magnitude of vibration and noise transmitted from one of the first and second discharge covers (100, 200) to the other. In particular, when the discharge valve (191) is turned on and off, the effect of reducing the magnitude of the valve tapping sound that is frictionally applied to the cylinder (60) can be expected.

[0106] In a structure in which the damping member (180) is mounted on the recess (140) of the first discharge cover (100), the recess (140) and the damping member (180) form a flow path through which refrigerant flows, and the flow path can be understood as defining a pulsation path to reduce pulsation that occurs when high-pressure discharge gas flows.

[0107] The above discharge cover assembly may include a third discharge cover (300) that supports the second discharge cover (200).

[0108] The third discharge cover (300) may have a roughly ring shape and be positioned to surround the rear portion of the second discharge cover (200). The third discharge cover (300) may support the cover flange (250) of the second discharge cover (200).

[0109] The third discharge cover (300) can be supported on the front of the frame (50).

[0110] The third discharge cover (300) is fastened to the frame flange (52) by a fastening member (not shown), and the front surface of the frame flange (52) can come into surface contact with the rear surface of the third discharge cover (300).

[0111] A frame fastening hole (55) into which the fastening member is inserted may be formed in the frame flange (52). Multiple frame fastening holes (55) may be formed. A cover fastening hole (335) may be formed in the third discharge cover (300) at a position corresponding to the frame fastening hole (55).

[0112] The above fastening member can be fastened to the frame fastening hole (55) and the cover fastening hole (335) to fix the frame (50) and the third discharge cover (300).

[0113] The third discharge cover (300) may be made of a material different from the first discharge cover (100) and the second discharge cover (200). The third discharge cover (300) may be made of a material having greater strength than the first discharge cover (100) and the second discharge cover (200).

[0114] The third discharge cover (300) may be made of a metal material, for example, aluminum. Since the third discharge cover (300) is connected to the frame (50) by the fastening member, a failure in connection may occur if the amount of deformation increases due to high heat. Therefore, the third discharge cover (300) may be made of a metal material so that the amount of thermal deformation is not large.

[0115] A frame sealing member (81) capable of increasing bonding strength and preventing refrigerant leakage may be provided at the portion where the second discharge cover (200) and the frame (50) are in surface contact. The frame sealing member (81) has a ring shape and may be installed between the rear surface of the second discharge cover (200) and the front surface of the frame (50).

[0116] The discharge cover assembly may include a discharge valve assembly (190). The discharge valve assembly may include a discharge valve (191) and a spring assembly (193, 195) that provides elastic force to the discharge valve (191) in a direction that brings it into close contact with the front end of the cylinder (60).

[0117] The above spring assembly (193, 195) may include a valve spring (193) composed of a leaf spring and a spring bracket (195) that surrounds the edge of the valve spring (193) to support the valve spring (193).

[0118] The discharge valve (191) is coupled to the central part of the valve spring (193). When the discharge valve (191) is opened, the refrigerant compressed in the compression space (P) of the cylinder (60) is discharged and flows into the internal space of the first discharge cover (100). When the discharge of the refrigerant is completed, the discharge valve (191) can be closed by the restoring force of the valve spring (193).

[0119] The above spring bracket (195) can be seated on the inner surface of the first discharge cover (100).

[0120] A sealing bracket (197) may be installed around the front end of the cylinder (60). For example, the sealing bracket (197) may have a ring shape. The sealing bracket (197) may be seated on the front flange of the cylinder (60) and supported on the rear of the spring bracket (195).

[0121] A bracket sealing member (83) may be provided between the sealing bracket (197) and the flange of the cylinder (60). The bracket sealing member (83) is provided on the contact surface between the sealing bracket (197) and the flange of the cylinder (60), and can prevent refrigerant from leaking through the space between the cylinder (60) and the spring assembly (193, 195).

[0122]

[0123] <2nd Example>

[0124] A second embodiment of the present invention is characterized in that the discharge valve assembly (190) is improved compared to the first embodiment. Other descriptions may be applied to the second embodiment as well. Unless otherwise noted, the description of the first embodiment may be applied to the second embodiment as is.

[0125] FIG. 3 is a cross-sectional view of a linear compressor of the second embodiment taken along 2-2 of FIG. 1. FIG. 4 is an enlarged view of the periphery of the discharge valve assembly in FIG. 3.

[0126] Refer to Figs. 3 and 4.

[0127] The discharge valve assembly (190) can be fixed between the cylinder (60) and the first discharge cover (100). The discharge valve assembly (190) can be fixed axially between the cylinder (60) and the first discharge cover (100). The discharge valve assembly (190) can be fixed radially (radially) to the first discharge cover.

[0128] The discharge valve assembly may include a spring bracket (195) that secures the valve spring (192). The spring bracket (195) may be provided in a roughly ring shape.

[0129] The outer surface of the spring bracket (195) may be provided with a sealing recess (195a) that accommodates a first valve sealing member (401). The first valve sealing member may seal the space between the outer surface of the spring bracket (195) and the inner surface of the outer wall (111). The first valve sealing member (401) may perform the function of sealing to block leakage of refrigerant. The first valve sealing member (401) may perform the function of damping vibration and noise. The first valve sealing member (401) may be made of rubber.

[0130] A deformation recess (195c) may be provided on the outer surface of the spring bracket (195) behind the sealing recess (195a). The spring bracket (195) can be easily deformed by the deformation recess (195c). The deformation recess (195c) can increase the elasticity of the spring bracket. The deformation recess (195c) can adjust the elastic modulus (k) of the spring bracket. The spring bracket can be more elastically deformed by the deformation recess (195c). For example, the spring bracket (195) can be elastically deformed when a valve spring (193) and / or a damping member (40) and / or a damping cover (41) is inserted.

[0131] The spring bracket (195) may be made of plastic. The spring bracket (195) may be made of polyamide (e.g., PA66) that can be used under high pressure and high temperature conditions. Since the spring bracket uses a high-rigidity material, it may be susceptible to deformation.

[0132] A second valve sealing member (402) may be provided at the contact portion between the rear end of the spring bracket (195) and the cylinder (60). The second valve sealing member may seal the space between the rear surface of the spring bracket (195) and the front surface of the cylinder (60). The second valve sealing member (402) may perform the function of sealing to block leakage of refrigerant. The second valve sealing member (402) may perform the function of insulation to prevent high heat from the discharge valve assembly from being transferred to the cylinder. The second valve sealing member (402) may be made of rubber.

[0133] The first valve sealing member may be located in front of the second valve sealing member.

[0134] The inner surface of the spring bracket (195) may be provided with a spring recess (195b) into which the valve spring (193) is inserted. The valve spring may be fitted into the spring recess (195b). The discharge valve (191) may be supported by the valve spring. The discharge valve may vibrate in the forward and backward directions under the influence of the spring constant of the valve spring.

[0135] A damping member (40) may be provided in front of the valve spring. The damping member may have a ring shape. The damping member may be made of rubber capable of exerting sufficient damping force. The damping member may use FKM (Fluorine Kautschuk Material, fluorocarbon-based fluoroelastomer). The damping member may be made of fluororubber. Fluororubber has the advantage of not requiring organic compounding agents due to the stable chemical structure of carbon and fluorine. Fluororubber has the advantage of having a wide operating temperature range from -20 to 250 degrees Celsius. In particular, fluororubber has the advantage of being able to be used stably under high-temperature conditions where high-temperature and high-pressure refrigerants flow. Fluororubber has the advantage of good fire resistance due to the stable structure of fluorine and carbon.

[0136] Hydrogenated Nitrile Butadiene Rubber (HNBR) can be used as the material for the above damping member. Compared to FKM, the above hydrogenated nitrile rubber has the disadvantage of a narrow heat resistance range of -20 to 150 degrees Celsius, and the disadvantage of requiring the addition of organic compounding agents to compensate for heat resistance and ozone resistance. The above hydrogenated nitrile rubber has the advantage of being cheaper than FKM.

[0137] The damping member (40) can be aligned vertically with the outer circumference of the valve spring. The damping member can be placed in front of the valve spring. The damping member and the valve spring can come into axial contact with each other. A large amount of vibration from the valve spring can be transmitted to the damping member. The damping member can perform a damping action against vibration noise transmitted to it.

[0138] The damping member may have a thickness sufficient to obtain adequate damping performance. The damping member may have a thickness of 0.5 to 1.5 mm in the axial direction. The cross-section of the ring of the damping member may have an axial size smaller than its radial size.

[0139] A damping cover (41) that maintains the installation position of the damping member (40) may be provided. The damping cover may have a roughly ring shape. The damping cover (41) may be placed in front of the damping member (40). The damping cover and the damping member may come into contact with each other. The damping cover may cover the entire damping member. The front end of the damping cover may be supported by the connecting rib (136) and / or the inner wall (130). The position of the damping cover may be supported by the inner surface of the spring bracket, the damping member, and the first discharge cover.

[0140] With the above discharge valve assembly inserted, the damping member can be supported in an axial position by the valve spring and the damping cover. The damping cover can be pressed against the connecting rib (136) and / or the inner wall (130) to fix the damping member.

[0141] The operation of the above damping member is explained.

[0142] The discharge valve may vibrate. A tapping sound may occur as a result of the discharge valve (191) coming into contact with the cylinder (60). The vibration noise generated from the discharge valve (191) may be transmitted to the valve spring (193). The vibration noise of the valve spring may be damped by the damping of the damping member. The vibration of the valve spring may be transmitted to the first discharge cover after being damped by the damping member. The noise vibration transmitted to the first discharge cover may be reduced.

[0143] Figure 5 is a cross-sectional view of a discharge valve assembly.

[0144] Refer to FIG. 5. The valve spring (193) may have a shape in which at least two spiral branches extend. The valve spring may move axially. While the valve spring is moving, the damping cover (41) and the valve spring (193) may not come into contact. To this end, the damping member (40) may provide a sufficient gap in the axial direction.

[0145] The radial outer end of the damping member may be positioned inwardly to the radial outer end of the valve spring. The radial inner end of the damping member may be located within the area of ​​the fixed part of the valve spring. The radial inner end of the damping member may reach the boundary between the fixed part of the valve spring and the movable part of the valve spring. Accordingly, wear of the damping member can be prevented. Accordingly, reliability regarding vibration noise reduction can be improved. The spacing between the radial inner ends of the damping member may be 32-34 mm.

[0146] The fixed portion of the valve spring may refer to the part of the valve spring that is fixed to the spring bracket and does not move in the axial direction. The movable portion of the valve spring may refer to the part of the valve spring that moves in the axial direction together with the discharge valve.

[0147] FIG. 6 is a drawing illustrating the fastening of a damping cover. FIG. 7 is a perspective view of a damping cover. FIG. 8 is a perspective view of a damping member.

[0148] Refer to FIGS. 6 to 8.

[0149] The damping cover (41) may be made of a polyamide (e.g., PA66) that can be used under high pressure and high temperature conditions. Since the damping cover uses a high-rigidity material, it may be susceptible to deformation. Both the damping cover and the spring bracket may be susceptible to deformation. Consequently, the two members may be damaged when pressed together. After being pressed together, if the residual stress increases, it may cause permanent deformation and fracture. To prevent this, the damping cover and the spring bracket may further include certain configurations.

[0150] The damping cover and the spring bracket can both be provided in an approximate ring shape.

[0151] The damping cover may have a reduction portion along the circumferential direction of the ring. The reduction portion may be a portion where the thickness of the ring decreases in the radial direction. The reduction portion may have the same thickness in the axial direction. The reduction portion may be provided at equal intervals along the circumferential direction of the ring. The reduction portion may be provided in three places. The spring constant during deformation of the damping cover can be adjusted by the reduction portion.

[0152] The above-mentioned weight reduction portion may include a first contraction portion (41d) and a second contraction portion (41e). The first contraction portion may be provided to contract toward the center from the radial outer surface of the damping cover. The first contraction portion (41d) and the second contraction portion (41e) may be continuous with each other.

[0153] Even if the damping cover is deformed by the aforementioned weight reduction part, it can undergo elastic deformation and minimize the occurrence of residual stress.

[0154] The above spring bracket may have a weight loss corresponding portion along the circumferential direction of the ring. The weight loss corresponding portion may correspond to the weight loss portion. The weight loss corresponding portion may be a portion where the thickness of the ring expands in the radial direction. The weight loss corresponding portion may have the same thickness in the axial direction. The weight loss corresponding portion may be provided at equal intervals along the circumferential direction of the ring. The weight loss corresponding portion may be provided in three places.

[0155] The above weight loss corresponding part may include a first extension part (195d) and a second extension part (195e). The first extension part may be provided to extend toward the center from the radial inner surface of the spring bracket. The first extension part (195d) and the second extension part (195e) may be continuous with each other.

[0156] The above-mentioned weight loss corresponding portion corresponds to the above-mentioned weight loss portion, allowing the damping cover to be deformed and pressed into the spring bracket. Contraction portions (195f) may be provided at both ends of the above-mentioned weight loss corresponding portion. The contraction portion (195f) may be a portion where the thickness of the spring bracket contracts. The contraction portion (195f) may perform the same function as the contraction portion of the corresponding cover. The spring constant during deformation of the spring bracket can be adjusted by the above-mentioned weight loss corresponding portion and the above-mentioned contraction portion (195f).

[0157] The spring bracket can be elastically deformed by the above-mentioned contraction portion (195f), and the occurrence of residual stress can be minimized.

[0158] When the damping cover is pressed into the spring bracket, the elastic deformation of each member can be smoothed and the occurrence of residual stress can be minimized.

[0159] FIG. 9 is an effect graph comparing the second embodiment with a damping member and the control example without a damping member. The control example was tested twice, and the second embodiment was tested once.

[0160] Refer to Fig. 9. Based on the vibration measured at the discharge cover, it can be seen that the vibration is reduced by 1.2 dB across all frequencies. In particular, it can be seen that the vibration noise reduction effect is significant at the representative vibration frequencies of the linear compressor, namely 800 Hz, 2.5 kHz, and 4 kHz.

[0161] The linear compressor according to an embodiment of the present invention can reduce the transmission of vibration noise and other noises generated at the discharge valve to the discharge cover. Accordingly, there is great potential for industrial application.

Claims

1. A discharge valve for discharging compressed high-pressure refrigerant; A discharge cover assembly forming a discharge chamber for the refrigerant discharged through the above discharge valve; A frame supporting the above discharge cover assembly; A cylinder into which a piston that reciprocates in the axial direction is inserted, supported inside the above frame; A valve spring that supports the discharge valve and reciprocates in the axial direction; The spring bracket that supports the valve spring and is fastened to the discharge cover assembly; and A linear compressor comprising a damping member that is placed on the spring bracket and reduces vibration of the valve spring.

2. In Paragraph 1, The damping member is provided in front of the valve spring. The above damping member contacts the front surface of the valve spring, and A linear compressor satisfying at least one of the following: the damping member is aligned vertically with the outer circumference of the valve spring.

3. In Paragraph 1, The above damping member is a linear compressor having a thickness of 0.5 to 1 mm in the axial direction.

4. In Paragraph 1, A linear compressor provided with a damping cover that fixes the damping member in front of the damping member.

5. In Paragraph 4, The above discharge cover assembly includes a first discharge cover forming a first discharge chamber for refrigerant, and a second discharge cover coupled to the first discharge cover and forming a discharge chamber for refrigerant discharged from the first discharge chamber. The first discharge cover comprises an inner wall defining the first discharge chamber, an outer wall defining the discharge chamber of the second discharge cover, and a connecting rib connecting the inner wall and the inner surface of the outer wall in a radial direction. The above damping cover is a linear compressor axially fixed to at least one of the inner wall or the connecting rib.

6. In Paragraph 4, The above damping cover is placed in front of the above damping member. The above damping cover and the above damping member are in contact with each other. The above damping cover covers all of the above damping members. The above damping cover and the above valve spring do not come into contact, and A linear compressor satisfying at least one of the conditions that the damping cover is positioned by the inner surface of the spring bracket and / or by a damping member.

7. In Paragraph 4, The above spring bracket or the above damping cover is a linear compressor made of plastic.

8. In Paragraph 7, A weight-reducing portion provided on the outer surface of the above damping cover, and A linear compressor comprising a weight loss corresponding portion provided on the inner surface of the spring bracket in correspondence with the weight loss portion.

9. In Paragraph 8, The above-mentioned weight loss portion is a linear compressor comprising two consecutive contraction sections.

10. In Paragraph 8, A linear compressor comprising a contraction section provided at both ends of the above-mentioned weight loss corresponding section.

11. In Paragraph 8, The above weight loss portion is a linear compressor provided with three equal intervals in the circumferential direction.

12. In Paragraph 1, A linear compressor in which the radial inner end of the damping member is located within the fixed portion area of ​​the valve spring.

13. In Paragraph 1, A sealing recess that accommodates a first valve sealing member on the outer surface of the above spring bracket; A deformation recess provided on the outer surface of the above spring bracket; and A linear compressor comprising at least one of a second valve sealing member provided at the contact portion between the rear end of the spring bracket and the cylinder.

14. In Paragraph 13, The above-mentioned first valve sealing member is one in which vibration noise reduction is dominant among vibration noise reduction and thermal insulation, or The above-mentioned second valve sealing member is a linear compressor that satisfies at least one of vibration noise reduction and thermal insulation, wherein thermal insulation is dominant.

15. In Paragraph 1, The above damping member is a linear compressor made of FKM or HNBR.

16. A discharge valve assembly for controlling the discharge of compressed high-pressure refrigerant; A discharge cover assembly forming a discharge chamber for the refrigerant discharged through the above discharge valve assembly; A frame supporting the above discharge cover assembly; A cylinder into which a piston that reciprocates axially is inserted, supported inside the above frame; and A linear compressor comprising a damping member adjacent to the discharge valve assembly for reducing noise generated by the cylinder.

17. In Paragraph 16, The above discharge valve assembly is, Discharge valve; A valve spring that supports the discharge valve and reciprocates in the axial direction; The spring bracket that supports the valve spring and is fastened to the discharge cover assembly; A linear compressor comprising a damping member that is fastened to the spring bracket and reduces vibration of the valve spring.

18. In Paragraph 17, The above damping member is a linear compressor whose position is fixed by a damping cover made of the same material as the spring bracket.

19. A discharge valve assembly including a discharge valve for controlling the discharge of compressed high-pressure refrigerant; A discharge cover assembly forming a discharge chamber for the refrigerant discharged through the above discharge valve assembly; A frame supporting the above discharge cover assembly; and It includes a cylinder into which a piston that reciprocates in the axial direction is inserted, which is supported inside the above frame, and A linear compressor comprising a damping member fixed to the discharge valve assembly and damping the transmission of tapping sounds generated in the discharge valve and the cylinder to the discharge cover assembly.

20. In Paragraph 19, The above damping member is a linear compressor having the shape of a ring.

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