Compressor

Abstract

Disclosed is a compressor comprising: a shell providing a space therein and including a suction port through which a refrigerant flows in; a cylinder disposed inside the shell; a piston that reciprocates relative to the cylinder and includes a cylindrical piston body and a piston head disposed at one end of the piston body and having a through-hole; and a suction muffler which is disposed in the inner space of the piston and in which the refrigerant that flows in through the suction port and passes through the through-hole of the piston flows. The suction muffler comprises: a suction part including an inlet of the suction muffler and a cylindrical first housing that has a space therein; a connection part including a connection pipe that is disposed inside the first housing; and a discharge part including a discharge pipe that is disposed inside the piston. The outer circumference of the discharge pipe is spaced apart from the inner circumference of the piston and a first resonator is formed between the discharge pipe and the piston, and the outer circumference of the connection pipe is spaced apart from the inner circumference of the first housing and a second resonator is formed between the connection pipe and the first housing.

Description

compressor

[0001] The present disclosure relates to a compressor, and more particularly to a compressor having a suction muffler.

[0002] A compressor is a device that compresses refrigerant using driving force generated by an electric motor or similar device. It is widely used not only in home appliances like refrigerators and air conditioners, but also across industries. Depending on their operating principles, these compressors can be categorized into reciprocating, rotary, and scroll compressors. Among these, linear compressors, which utilize linear motors to reciprocate pistons in a linear motion, are widely adopted due to their simple structure and high efficiency.

[0003] Technologies have been developed for linear compressors to reduce suction path noise and maintain a stable suction pressure of the refrigerant by arranging a suction muffler inside the piston. For example, prior art documents 1 (KR20220098553A) and 2 (KR20180079026A) disclose structures in which a muffler is arranged inside the piston and its shape is varied to simultaneously reduce noise in both high- and low-frequency bands. In addition, prior art document 3 (KR20160136823A) proposes a technology to secure structural stability by improving the bonding strength between the suction guide and the back cover.

[0004] The mufflers disclosed in the above-mentioned prior documents are based on a diffuser-type muffler structure. A diffuser-type muffler is a structure that forms a diffuser structure within a flow path to reduce the flow velocity while restoring the static pressure, and at the same time induce reflection and interference of sound waves, thereby selectively attenuating noise of a specific frequency. Unlike a general buffer chamber or a simple tubular muffler, a diffuser-type muffler has the advantage of being able to effectively utilize acoustic resonance characteristics while minimizing fluid dynamic loss. Accordingly, it is being usefully applied as a structure that can control suction noise while efficiently utilizing the internal space of a compressor.

[0005] However, conventional technology has limitations in reducing noise simply by modifying multiple mufflers or flow path shapes. Furthermore, suction efficiency has been limited due to the ineffective utilization of the resonance phenomenon of refrigerant flow. In particular, the air space formed within the muffler or piston often serves merely as a buffer, limiting flow noise suppression and resulting in pressure loss during suction.

[0006] The present disclosure aims to solve the above-mentioned and other problems.

[0007] Another object may be to provide a compressor having a suction muffler that reduces noise across various frequency bands.

[0008] Another purpose may be to provide a suction muffler that reduces noise generated from a compressor unit or a home appliance such as a refrigerator equipped with a compressor.

[0009] Another purpose may be to provide a suction muffler that reduces noise generated in a cavity within the shell of a compressor or in a cavity of a refrigerator having a compressor.

[0010] Another purpose may be to provide a muffler that reduces noise in a band between two specific frequencies, rather than just reducing noise at a specific frequency.

[0011] Another purpose may be to provide a suction muffler in which a resonator is formed not only through the discharge portion of the suction muffler but also through the structure of the connecting portion connecting the suction portion and the discharge portion.

[0012] Another purpose may be to provide a suction muffler in which a resonator is formed in the space inside the connection portion, the space between the connection portion and the discharge portion, and the space between the connection portion and the suction portion through the structure of the connection portion connecting the suction portion and the discharge portion as well as the discharge portion of the suction muffler.

[0013] Another purpose may be to provide a suction muffler that reduces noise at the loudest frequency in the compressor.

[0014] Another purpose may be to provide a compressor whose noise is not amplified by the suction muffler.

[0015] Another purpose may be to provide a compressor that reduces noise caused by resonance of the compressor shell.

[0016] Another purpose may be to provide a compressor that can improve driving performance.

[0017] Another purpose may be to provide a compressor that can improve refrigerant inlet efficiency.

[0018] The tasks of the present invention are not limited to the tasks mentioned above, and other tasks not mentioned will be clearly understood by those skilled in the art from the description below.

[0019] According to one aspect of the present disclosure for achieving the above-described purpose, a compressor including a suction muffler is provided.

[0020] The compressor includes: a shell providing a space therein; a cylinder disposed inside the shell; a piston reciprocating with respect to the cylinder; and a suction muffler.

[0021] The above shell includes an inlet through which refrigerant is introduced.

[0022] The above piston includes a cylindrical piston body and a piston head disposed at one end of the piston body and having a through hole.

[0023] The above suction muffler is arranged in the internal space of the piston. The suction muffler allows refrigerant to flow between the suction port and the hole of the piston.

[0024] The above suction muffler may include: a suction portion, a connection portion, and a discharge portion.

[0025] The above suction unit may include an inlet of the suction muffler and a cylindrical first housing having a space inside.

[0026] The above connecting portion may include a connecting tube disposed inside the first housing.

[0027] The above discharge unit may include a discharge pipe disposed inside the piston.

[0028] The outer circumference of the discharge tube may be spaced apart from the inner circumference of the piston so that a first resonator may be formed between the discharge tube and the piston.

[0029] The outer perimeter of the connecting tube may be spaced apart from the inner perimeter of the first housing so that a second resonator may be formed between the connecting tube and the first housing.

[0030] The above discharge portion may further include a first extension portion extending radially outward from the discharge tube.

[0031] The first expansion portion may be spaced apart from the piston so that an inlet of the first resonator may be formed between the first expansion portion and the piston.

[0032] The above connecting portion may include an inlet of the second resonator penetrating the connecting tube in a radial direction.

[0033] The volume of the first resonator may be larger than the volume of the second resonator.

[0034] The discharge portion may include: a second housing having a diameter larger than the discharge pipe and positioned upstream of the discharge pipe; and a first extension pipe extending upstream from the discharge pipe, positioned inside the second housing, and having an outer diameter smaller than the inner diameter of the second housing.

[0035] A third resonator may be formed between the second housing and the first extension tube.

[0036] The volume of the third resonator may be smaller than the volume of the first resonator and the volume of the second resonator.

[0037] The above connecting portion may further include a neck provided at a downstream end of the above connecting portion and into which the first extension pipe is inserted.

[0038] The inner diameter of the neck may be larger than the outer diameter of the first extension tube and smaller than the inner diameter of the second housing so that an inlet of the third resonator is formed between the neck and the first extension tube.

[0039] The above connecting portion may further include a second extension portion extending radially outward from the downstream end of the connecting pipe and connected to the neck.

[0040] The second extension section may be arranged on the outside of the first extension tube, so that a fourth resonator may be formed between the first extension tube and the second extension section.

[0041] The upstream end of the first extension pipe and the downstream end of the connection pipe may be spaced apart from each other by a distance smaller than the length of the second extension portion to form an inlet of the fourth resonator.

[0042] The area of ​​the entrance of the third resonator may be smaller than the area of ​​the entrance of the fourth resonator.

[0043] The volume of the fourth resonator may be smaller than the volume of the first resonator and the volume of the second resonator.

[0044] The above connecting portion may further include a supporter extending radially outward from an end of the connecting tube and contacting the inner side of the first housing.

[0045] The above suction unit may further include a suction guide forming an inlet of the above suction unit.

[0046] The above suction guide is arranged on the inside of the first housing, extends downstream from the first housing, and can be inclined so that its diameter becomes smaller as it goes downstream.

[0047] The above suction portion may include a ring-shaped outer ring positioned radially outside the downstream end of the suction guide and protruding downstream from the suction guide.

[0048] The outer ring may be spaced radially inward from the first housing, so that a fifth resonator may be formed between the outer ring and the first housing.

[0049] The above suction unit may further include a ring-shaped inner ring provided at the downstream end of the suction guide.

[0050] The inner ring and the outer ring may be spaced apart from each other in the radial direction to form a sixth resonator therebetween.

[0051] The above supporter can be extended upstream to form a space on the inside.

[0052] The above outer ring and the above inner ring are inserted into the inner space of the supporter and can be spaced apart from the supporter and the connecting pipe.

[0053] The above suction guide can be curved and inclined.

[0054] The inner diameter of the downstream end of the above suction guide, the inner diameter of the above connecting pipe, and the inner diameter of the upstream end of the above discharge pipe may be the same.

[0055] The inner diameter of the above suction guide, the inner diameter of the above connecting pipe, and the inner diameter of the above discharge pipe may be 7 mm or more.

[0056] The above first extension portion may have a cylindrical shape extending radially outward from the discharge pipe and extending downstream from the outer end.

[0057] The above discharge portion may further include a second extension pipe extending downstream from the discharge pipe and positioned inside the first extension portion.

[0058] The second extension pipe and the first extension portion may be spaced apart from each other in the radial direction to form a seventh resonator therebetween.

[0059] The length of the second extension pipe extending downstream may be shorter than the length of the first extension portion.

[0060] The inner surface of the above discharge pipe may be inclined so that the diameter increases from the upstream side to the downstream side.

[0061] According to one aspect of the present disclosure for achieving the above-described object, a compressor includes a shell providing a space therein and including a suction port through which refrigerant is introduced; a cylinder disposed inside the shell; a piston including a cylindrical piston body and a piston head disposed at one end of the piston body and having a through hole, the piston reciprocating with respect to the cylinder; and a suction muffler disposed in an inner space of the piston and allowing refrigerant to flow through the suction port and the through hole of the piston. The suction muffler includes: a suction portion including an inlet of the suction muffler and a cylindrical first housing having a space therein; a connection portion including a connection pipe disposed inside the first housing; and a discharge portion including a discharge pipe disposed inside the piston and a first extension portion extending radially outward from the discharge pipe. An outer diameter of the discharge pipe is smaller than an inner diameter of the piston so that a first resonator is formed between the discharge pipe and the piston. The first extension portion is spaced apart from the piston, such that an inlet of the first resonator is formed between the first extension portion and the piston. The outer diameter of the connection tube is smaller than the inner diameter of the first housing, such that a second resonator is formed between the connection tube and the first housing. The connection portion includes an inlet of the second resonator that radially penetrates the connection tube.

[0062] According to one aspect of the present disclosure for achieving the above-described object, a compressor includes a shell providing a space therein and including an intake port through which refrigerant is introduced; a cylinder disposed inside the shell; a piston including a cylindrical piston body and a piston head disposed at one end of the piston body and having a through hole, the piston reciprocating with respect to the cylinder; and a suction muffler disposed in the inner space of the piston and allowing refrigerant to flow between the intake port and the through hole of the piston. The suction muffler includes: a suction portion including an inlet of the suction muffler and a cylindrical first housing having a space therein; a discharge portion including a second housing connected to the first housing and a discharge pipe extending from the second housing toward a downstream side of the flow of the refrigerant; and a connection portion including a supporter in contact with the first housing, an extension portion in contact with the second housing, and a connection pipe extending between the supporter and the extension portion. The connecting tube is spaced inwardly from the first housing and includes a radially penetrating inlet, so that a resonator is formed between the connecting tube and the first housing.

[0063] Specific details of other embodiments are included in the detailed description and drawings.

[0064] According to at least one of the embodiments of the present disclosure, a compressor having a suction muffler that reduces noise in various frequency bands can be provided.

[0065] According to at least one of the embodiments of the present disclosure, a suction muffler that reduces noise generated from a compressor unit or a home appliance such as a refrigerator equipped with a compressor can be provided.

[0066] According to at least one of the embodiments of the present disclosure, a suction muffler can be provided that reduces noise generated in a cavity inside a shell of a compressor or a cavity of a refrigerator having a compressor.

[0067] According to at least one of the embodiments of the present disclosure, it is possible to provide a suction muffler that reduces not only noise at a specific frequency, but also noise in a band between two specific frequencies.

[0068] According to at least one of the embodiments of the present disclosure, a suction muffler can be provided in which a resonator is formed through the structure of a connection portion connecting the suction portion and the discharge portion as well as the discharge portion of the suction muffler.

[0069] According to at least one of the embodiments of the present disclosure, a suction muffler can be provided in which a resonator is formed in a space inside the connection portion, a space between the connection portion and the discharge portion, and a space between the connection portion and the suction portion through a structure of a connection portion connecting the suction portion and the discharge portion as well as the discharge portion of the suction muffler.

[0070] According to at least one of the embodiments of the present disclosure, a suction muffler can be provided that reduces noise at a frequency at which noise level is the loudest in a compressor.

[0071] According to at least one of the embodiments of the present disclosure, a compressor whose noise is not amplified by a suction muffler can be provided.

[0072] According to at least one of the embodiments of the present disclosure, a compressor can be provided that reduces noise caused by resonance of a compressor shell.

[0073] According to at least one of the embodiments of the present disclosure, a compressor capable of improving driving performance can be provided.

[0074] According to at least one of the embodiments of the present disclosure, a compressor capable of improving refrigerant inflow efficiency can be provided.

[0075] FIG. 1 is a cross-sectional view of a compressor according to one embodiment of the present disclosure.

[0076] Figure 2 is a perspective view of the compressor illustrated in Figure 1.

[0077] Figure 3 is an exploded view of the compressor illustrated in Figure 2.

[0078] Figure 4 is a drawing and graph for explaining a 1 / 4 wave field, which is a type of resonator.

[0079] Figure 5 is a drawing and graph for explaining a Helmholtz resonator, which is a type of resonator.

[0080] Figures 6 and 7 are drawings and graphs for explaining the superposition of transmission losses through an array of resonators.

[0081] Figure 8 is an enlarged view of the piston and suction muffler shown in Figure 1.

[0082] FIG. 9 is a graph showing the noise of a compressor equipped with a conventional suction muffler and a compressor according to an embodiment of the present disclosure.

[0083] Figure 10 is a graph showing the noise of a conventional compressor unit equipped with a suction muffler and a refrigerator equipped with a compressor according to an embodiment of the present disclosure.

[0084] Fig. 11 is a graph showing the insertion loss of a suction muffler applied to a conventional compressor and a suction muffler of a compressor according to one embodiment of the present disclosure.

[0085] Figure 12 is a graph showing the results of an insertion loss experiment of a suction muffler applied to a conventional compressor.

[0086] Figure 13 is a drawing for explaining the pressure drop according to the shape of the suction muffler.

[0087] Figure 14 is a drawing for explaining the pressure drop according to the shape of the inlet of the suction muffler.

[0088] Figures 15 and 16 are graphs and drawings for explaining the pressure drop according to the shape of the outlet of the suction muffler.

[0089] Figure 17 is a graph showing the inner diameter and pressure drop of a suction muffler.

[0090] Figure 18 is a graph showing the slope and pressure drop of the suction muffler.

[0091] Hereinafter, embodiments disclosed in this specification will be described in detail with reference to the attached drawings. Regardless of the drawing numbers, identical or similar components are given the same reference numbers and redundant descriptions thereof will be omitted.

[0092] The suffixes "module" and "part" used for components in the following description are given or used interchangeably only for the convenience of writing specifications, and do not have distinct meanings or roles in themselves.

[0093] In addition, when describing the embodiments disclosed in this specification, if it is determined that a detailed description of a related known technology may obscure the gist of the embodiments disclosed in this specification, the detailed description thereof will be omitted. In addition, the attached drawings are only intended to facilitate easy understanding of the embodiments disclosed in this specification, and the technical ideas disclosed in this specification are not limited by the attached drawings, and should be understood to include all modifications, equivalents, and substitutes included in the spirit and technical scope of the present disclosure.

[0094] Terms that include ordinal numbers, such as first, second, etc., may be used to describe various components, but the components are not limited by these terms. These terms are used solely to distinguish one component from another.

[0095] When a component is referred to as being "connected" or "connected" to another component, it should be understood that it may be directly connected or connected to that other component, but that there may be other components intervening. Conversely, when a component is referred to as being "directly connected" or "connected" to another component, it should be understood that there are no other components intervening.

[0096] Singular expressions include plural expressions unless the context clearly indicates otherwise.

[0097] Referring to FIG. 1, a compressor (10) according to one embodiment of the present disclosure may be installed in a refrigerator (1). The compressor (10) may be placed in a machine room of the refrigerator (1). That is, the refrigerator (1) includes a storage room for storing food and a machine room in which components of a refrigeration cycle are placed, and the refrigeration cycle may include a compressor (10).

[0098] Alternatively, the compressor (10) according to one embodiment of the present disclosure may be installed in other products such as air conditioners.

[0099] The compressor (10) may include a shell (100). The shell (100) may provide a space therein. Components of the compressor (10), such as a cylinder (120), a piston (130), a motor assembly (20), and a suction muffler (30), may be installed in the internal space of the shell (100).

[0100] The shell (100) may include a first shell (101) and a second shell (102) that are coupled to each other. A cylinder (120), a piston (130), a motor assembly (20), a muffler (30), etc. may be installed inside the first shell (100), and the first shell (101) and the second shell (102) may be coupled.

[0101] A suction port (103) may be formed in the shell (100). A compressor suction pipe (104) may be connected to the suction port (103). Refrigerant flowing through the compressor suction pipe (104) may be introduced into the interior of the compressor (10) through the suction port (103).

[0102] A compressor discharge pipe (106) can be connected to the shell (100). Refrigerant introduced into the compressor (10) can be compressed by the compressor (10) and discharged through the compressor discharge pipe (106).

[0103] The compressor (10) may be a linear compressor. The compressor (10) may include a cylinder (120) and a piston (130) that reciprocates with respect to the cylinder (120). The cylinder (120) may have a cylindrical shape having a space inside. One side of the cylinder (120) is open so that the piston (130) can be inserted therein.

[0104] The piston (130) is arranged at least partially within the internal space of the cylinder (120), and the remaining portion is arranged outside the cylinder (120) through an open side, and can reciprocate. The piston (130) can reciprocate linearly within the internal space of the cylinder (120).

[0105] The piston (130) may have a cylindrical shape with a space inside.

[0106] The compressor (10) may include a suction muffler (30). The suction muffler (30) may be disposed at least partially inside the piston (130).

[0107] When the piston (130) moves in the direction of being withdrawn through the open side of the cylinder (120), the space (123) between the piston (130) and the cylinder (120) expands, and the internal pressure may be lowered. When the pressure of the cylinder (120) is lowered, the refrigerant flowing into the interior of the compressor (10) may pass through the suction muffler (30) and flow into the space (123) between the piston (130) and the cylinder (120). As the refrigerant passes through the suction muffler (270), noise of various frequencies may be reduced. A detailed description of the suction muffler (270) and noise reduction will be described later.

[0108] As the piston (130) moves in the direction of being drawn into the cylinder (120), the space between the piston (130) and the cylinder (120) is reduced, and the refrigerant introduced into the space can be compressed.

[0109] The other side of the cylinder (120) may be opened. A discharge valve assembly (140) may be arranged on the opened other side of the cylinder (120). The discharge valve assembly (140) may open and close the opened other side of the cylinder (120). The discharge valve assembly (140) may open and close the cylinder (120) depending on the pressure of the internal space (123) of the cylinder (120).

[0110] The discharge valve assembly (140) may include a discharge valve (142) that opens and closes the cylinder (120), a discharge cover (141) that accommodates the discharge valve (142), and a spring (144) connected to the discharge valve (142). One end of the spring (144) may be connected to the discharge valve (142), and the other end may be connected to the discharge cover (141).

[0111] If the pressure in the internal space (123) of the cylinder (120) is higher than the set pressure, the discharge valve (142) opens, and if it is lower than the set pressure, the discharge valve (142) can close the cylinder (120).

[0112] The compressor (10) may include a discharge muffler (150). The discharge muffler (150) may surround a discharge cover (141). When the discharge valve (142) is opened, the refrigerant in the cylinder (120) may pass through the discharge cover (141) and flow into the discharge muffler (150). The discharge muffler (150) may reduce the flow noise of the compressed refrigerant and the opening and closing noise of the discharge valve (142).

[0113] The compressor (10) may include a loop pipe (105) connected to a discharge muffler (150). The loop pipe (105) may be flexibly movable within the shell (100). The loop pipe (105) may connect the discharge muffler (150) and the compressor discharge pipe (106). The refrigerant of the discharge muffler (150) may be guided to the compressor discharge pipe (106) through the loop pipe (105) and discharged to the outside.

[0114] The compressor (10) may include a frame (110) that supports a cylinder (120). The frame (110) may secure the cylinder (120) to the shell (100). The frame (110) may be formed integrally with the cylinder (120) or may be combined with the cylinder (120) to secure the cylinder (120) to the shell (100).

[0115] The discharge cover (141) and discharge muffler (450) can be fixed to the frame (110).

[0116] The compressor (10) may include a motor assembly (20) that provides power to the piston (130). The motor assembly (20) may provide power to cause the piston (130) to perform a linear reciprocating motion.

[0117] The motor assembly (20) may include a stator (210, 220) fixed to a frame (110) and a permanent magnet (230) that moves linearly with respect to the stator (210, 220). The stator (210, 220) may be fixed to the frame (110).

[0118] The stator (210, 220) may include an outer stator (210) arranged to surround the cylinder (120) and an inner stator (220) arranged spaced apart from the inner side of the outer stator (210). The outer stator (210) and the inner stator (220) may be fixed to the frame (110).

[0119] The permanent magnet (230) can be positioned in the space between the outer stator (210) and the inner stator (220). The permanent magnet (230) can move in a straight line back and forth by mutual electromagnetic force with the stator (210, 220).

[0120] The permanent magnet (230) may be composed of a single magnet having one pole, or may be composed of a combination of multiple magnets having three poles.

[0121] The permanent magnet (230) can be coupled to the piston (130) by a connecting member (138). The connecting member (138) can extend from one end of the piston (130) to the permanent magnet (130). As the permanent magnet (230) moves linearly, the piston (130) can reciprocate linearly together with the permanent magnet (230).

[0122] The outer stator (210) may include a coil winding (213, 215) and a stator core (211). The coil winding (213, 215) may include a bobbin (213) and a coil (215) wound on the bobbin (213). The stator core (211) may be arranged to surround the coil winding (213, 215).

[0123] When current is applied to the motor assembly (200), current flows through the coil (215), and a magnetic flux is formed around the coil (215) due to the current flowing through the coil (215), and the magnetic flux flows while forming a closed circuit along the outer stator (210) and the inner stator (220). The magnetic flux flowing along the outer stator (210) and the inner stator (220) and the magnetic flux of the permanent magnet (230) interact with each other, and a force that moves the permanent magnet (230) can be generated.

[0124] A stator cover (240) is arranged on one side of the outer stator (210). One side of the outer stator (210) may be supported by the frame (110), and the other side may be supported by the stator cover (240).

[0125] The inner stator (220) can be fixed to the outer periphery of the cylinder (120).

[0126] The compressor (10) may include a piston supporter (160) that supports the piston (130). The piston supporter (160) may be coupled to the outside of the connecting member (138). The piston supporter (160) may move together with the piston (130).

[0127] The compressor (10) may include a back cover (180). The back cover (180) may be coupled to a stator cover (240).

[0128] The back cover (180) may be placed at the rear of the piston supporter (160). The back cover (180) may surround at least a portion of the suction muffler (30).

[0129] Here, 'rear' may mean upstream in the direction of flow of the refrigerant in the suction muffler (30). Also, downstream in the direction of flow of the refrigerant may be referred to as 'front'.

[0130] The compressor (10) may further include a suction guide device (not shown) coupled to the back cover (180). The suction guide device is coupled to the back cover (180) and extends rearward, and may be positioned to move closer to the suction muffler (30) or further away from the suction muffler (30) during the reciprocating linear movement of the piston (130) and the suction muffler (30).

[0131] Alternatively, as illustrated in FIG. 1, the compressor (10) may not be provided with a separate suction guide device that guides the refrigerant to flow into the suction muffler (30). Even without the suction guide device, the refrigerant can flow smoothly into the suction muffler (30).

[0132] The compressor (10) may include a plurality of springs (172, 178) connected to the piston supporter (160). The springs (172, 178) may include a first spring (172) provided between the piston supporter (160) and the stator cover (240) and a second spring (178) provided between the piston supporter (160) and the back cover (180). The first springs (172) and the second springs (178) are each provided in plurality so that the piston supporter (160) can be arranged along the circumferential direction.

[0133] Oil can be stored on the inner bottom surface of the shell (100). An oil supply device (190) for pumping oil into the interior of the shell (100) can be provided. The oil supply device (190) can be placed at the lower part of the inner space of the shell (100). The oil supply device (160) can be operated by vibration generated as the piston (130) reciprocates and linearly moves, thereby pumping oil upward.

[0134] The compressor (10) may further include an oil supply pipe (195) that guides the flow of oil from the oil supply device (190) to the cylinder (120). The oil supply pipe (195) may extend from the oil supply device (190) to the space (123) between the cylinder (120) and the piston (130).

[0135] Oil pumped from the oil supply device (190) is supplied to the space (123) between the cylinder (120) and the piston (130) through the oil supply pipe (195), so that cooling and lubrication can be performed.

[0136] Referring to FIGS. 2 and 3, the suction muffler (30) may include a suction portion (40) and a discharge portion (60). The refrigerant may be sucked into the interior of the suction muffler (30) through the suction portion (40). The refrigerant introduced into the suction muffler (30) may be discharged to the exterior of the suction muffler (30) through the discharge portion (60).

[0137] The suction unit (40) may include a cylindrical first housing (42).

[0138] The suction portion (40) may include a suction guide (41) forming an inlet (410) of a suction muffler. The suction guide (41) may be provided at the upstream end of the first housing (42).

[0139] The suction guide (41) can extend in the direction of refrigerant flow. The suction guide (41) can be placed inside the first housing (42).

[0140] The suction guide (41) may be inclined so that the radius becomes narrower as it goes downstream. The suction guide (41) may be inclined in a curved manner.

[0141] The discharge unit (60) may include a discharge pipe (61). The discharge pipe (61) may have a cylindrical shape. The discharge pipe (61) may have a cylindrical shape with a length longer than a diameter.

[0142] The discharge tube (61) may be arranged inside the piston (130). The outer circumference of the discharge tube (61) may be spaced apart from the inner circumference of the piston (130). A space (31, see FIG. 8) may be formed between the discharge tube (61) and the piston. The space (31) may be a resonator that reduces noise. Hereinafter, the space is referred to as a first resonator (31).

[0143] The discharge unit (60) may include a second housing (65). The second housing (65) may be arranged on the upstream side of the discharge pipe (61) in the refrigerant flow direction.

[0144] The second housing (65) may have a cylindrical shape. A space (33, see FIG. 8) may be formed inside the second housing (65), and the space (33) is also referred to as a third resonator (33). A detailed description of the third resonator will be described later with reference to FIG. 8.

[0145] The discharge pipe (61) can extend downstream of the refrigerant flow from the second housing (65). The discharge pipe (61) can be inclined so that its diameter increases toward the downstream side.

[0146] A reinforcing rib (69) may be provided between the discharge pipe (61) and the second housing (65). A plurality of reinforcing ribs (69) may be provided, and the plurality of reinforcing ribs (69) may be arranged along the circumferential direction.

[0147] The second housing (65) can be connected to the first housing (42) of the suction unit (40). The suction unit (40) and the discharge unit (60) can be coupled to each other. The first housing (42) and the second housing (65) can be coupled to each other.

[0148] The suction portion (40) may include a flange (465) provided at the downstream end of the first housing (42), and the discharge portion (60) may include a flange (645) provided at the upstream end of the second housing (65).

[0149] The discharge portion (60) may include an insert portion (64) extending upstream of the refrigerant flow from the second housing (65). The suction portion (40) may include a receiving portion (46) provided at the downstream end of the first housing (42).

[0150] The detailed structure of the combination of the suction part (40) and the discharge part (60) is described later with reference to FIG. 8.

[0151] The discharge portion (60) may include a first expansion portion (66) arranged on the downstream side of the refrigerant flow. The expansion portion (66) may be arranged on the downstream side of the discharge pipe (61).

[0152] The first expansion portion (66) may extend radially outward from the discharge pipe (61). The first expansion portion (66) may extend radially outward from the discharge pipe (61) and may extend downstream. The first expansion portion (66) may have a cylindrical shape. The first expansion portion (66) may be a cylindrical shape with a diameter greater than a length.

[0153] The suction muffler (30) may include a connecting portion (50). The connecting portion (50) may connect the suction portion (40) and the discharge portion (60). The connecting portion (50) may connect the inlet (410) of the suction muffler (30) and the discharge pipe (61).

[0154] The connecting portion (50) may be arranged between the inlet (410) of the suction muffler (30) and the discharge pipe (61). The connecting portion (50) may extend between the inlet (410) of the suction muffler (30) and the discharge pipe (61). The connecting portion (50) may be spaced apart from the inlet (410) of the suction muffler (30) and the discharge pipe (61).

[0155] The connecting portion (50) may include a connecting tube (52) disposed inside the first housing (42). The connecting tube (52) may have a cylindrical shape. The connecting tube (52) may have a cylindrical shape with a length longer than a diameter.

[0156] The outer diameter of the connecting tube (52) may be smaller than the inner diameter of the first housing (62). The outer circumference of the connecting tube (52) may be spaced apart from the inner circumference of the first housing (62) so that a space (32, see FIG. 8) may be formed between the connecting tube (52) and the first housing (42). The space (32) may be a resonator that reduces noise. Hereinafter, the space (32) is referred to as a second resonator (32).

[0157] The connecting portion (50) may include a hole (321) that radially penetrates the connecting tube (52). The hole (321) may form an inlet of the second resonator (32). Hereinafter, the hole (321) is also referred to as an inlet of the second resonator (32).

[0158] The connecting portion (50) may include a supporter (51). The supporter (51) may support the connecting portion (50) from the suction portion (40).

[0159] The supporter (51) may be placed on the upstream side of the connecting pipe (52). The supporter (51) may extend from the upstream end of the connecting pipe (52).

[0160] The supporter (51) may be formed in a cylindrical shape. The supporter (51) may be in a cylindrical shape with a diameter greater than the length.

[0161] The supporter (51) may have a cylindrical shape extending from the connecting pipe (52). The supporter (51) may have a diameter larger than the diameter of the connecting pipe (52). The supporter (51) may have an outer diameter larger than the outer diameter of the connecting pipe (52). The supporter (51) may have an inner diameter larger than the inner diameter of the connecting pipe (52) (see FIG. 8).

[0162] The supporter (51) can be inserted into the interior of the first housing (42). The supporter (51) can be in contact with the first housing (42). The outer circumference of the supporter (51) can be in contact with the inner circumference of the first housing (42).

[0163] The connecting portion (50) may include a second extension portion (54). The second extension portion (54) may support the connecting portion (50) from the discharge portion (60).

[0164] The second extension (54) may be positioned on the downstream side of the connecting pipe (52). The second extension (54) may extend from the downstream end of the connecting pipe (52).

[0165] The second expansion portion (54) may be formed in a cylindrical shape. It may be a cylindrical shape with a diameter larger than the length of the second expansion portion (54).

[0166] A space (34) is formed inside the second expansion portion (54), and the space (34) is called a fourth resonator (34). A detailed description of the fourth resonator (34) will be described later with reference to FIG. 8.

[0167] The second expansion portion (54) may have a cylindrical shape extending from the connecting tube (52). The second expansion portion (54) may have a diameter larger than the diameter of the connecting tube (52). The second expansion portion (54) may have an inner diameter larger than the inner diameter of the connecting tube (52) (see FIG. 8). The second expansion portion (54) may have an outer diameter larger than the outer diameter of the connecting tube (52).

[0168] The second extension (54) can be inserted into the interior of the second housing (65). The second extension (54) can be in contact with the second housing (65). The outer circumference of the second extension (54) can be in contact with the inner circumference of the second housing (65).

[0169] The second resonator (32, see FIG. 8) can be defined by the outer circumference of the connecting tube (52), the inner circumference of the first housing (42), the supporter (51), and the extension (54).

[0170] The second extension (54) can be connected to the neck (53) described later.

[0171] The connecting portion (50) may include a neck (53) provided at the downstream end of the connecting portion (50). The neck (53) may protrude downstream from the second extension portion (54). The neck (53) may be ring-shaped or cylindrical. The neck (53) may be ring-shaped with a diameter greater than its length.

[0172] A first extension pipe (63) described later in the discharge portion (60) can be inserted into the inner side of the neck (53). The neck (53) can be spaced outward from the first extension pipe (63) to form an inlet of the third resonator (33).

[0173] The connecting portion (50) may include a reinforcing rib (59) protruding outward from the connecting pipe (52). The reinforcing rib (59) may extend along the length of the connecting pipe (52). The reinforcing rib (59) may connect the supporter (51) and the connecting pipe (52). The reinforcing rib (59) may connect the second expansion portion (54) and the connecting pipe (52).

[0174] Hereinafter, the noise reduction principle of the diffuser type muffler will be explained with reference to FIGS. 4 to 7.

[0175] Figure 4 illustrates a quarter-wavelength tube. As illustrated in Figure 4(a), a lateral channel (302) extending from a main channel (301) and having a closed end is formed. This structure is generally called a "quarter-wavelength tube" or "resonator" and is used to selectively attenuate sound waves of a specific frequency transmitted along the main channel (301). The lateral channel (302) may extend laterally from the main channel (301) or may extend parallel to the main channel.

[0176] When the length of the lateral vortex (302) is L, resonance occurs at a frequency expressed by the following equation.

[0177]

[0178] Here, fr is called the "resonant frequency." When a sound wave of this frequency propagates along the main channel, some of its energy flows into the lateral channels, is reflected at the ends, and returns with its phase reversed. As a result, destructive interference occurs between the incident sound wave and the reflected wave, which leads to the attenuation (attenuation) of sound pressure energy rather than its amplification.

[0179] As illustrated in Fig. 4(b), transmission loss is maximized at the resonant frequency fr, which means that the corresponding frequency component propagating along the main path is substantially blocked. This loss peak occurs repeatedly at odd multiples of c / 4L.

[0180] Meanwhile, when the cross-sectional area of ​​the main duct (301) is S1 and the cross-sectional area of ​​the side duct (302) is S2, the cross-sectional area ratio (S2 / S1) affects the strength and bandwidth of the damping effect of the resonator, and by adjusting this, the noise suppression characteristics of a specific frequency band can be precisely controlled.

[0181] Fig. 5 is a drawing illustrating a noise reduction structure utilizing the principle of a Helmholtz resonator. A neck (304), which is a narrow passage connected from a main passage (303), is formed, and an expansion space (305) having a relatively large volume is provided at the end of this neck (304). At this time, the neck (304) forms the entrance to the expansion space (305), and its length is referred to as L. This structure is acoustically classified as a Helmholtz resonator, and can attenuate sound pressure energy by inducing a resonance phenomenon for sound waves of a specific frequency.

[0182] The resonant frequency fr of a Helmholtz resonator is expressed as follows:

[0183]

[0184] Here, c represents the speed of sound, S represents the cross-sectional area of ​​the neck (304), L represents the length of the neck, and V represents the volume of the expansion space (305).

[0185] The above frequency fr is the 'resonant frequency'. When sound waves of that frequency are transmitted along the main passage (303), some of them flow into the expansion space (305) through the neck (304) and cause resonance. At this time, when the sound waves generated by resonance are reflected again and become phase opposite to the incident wave, the frequency component causes destructive interference within the main passage and is attenuated. This does not amplify energy through resonance, but acts in the direction of absorbing and extinguishing the energy of a specific frequency component.

[0186] Figure 5(b) is a graph depicting transmission loss along the frequency axis, showing a distinct peak at the resonant frequency fr, where transmission loss is maximized. This is a characteristic of Helmholtz resonators, demonstrating that they can achieve highly effective noise suppression within a narrow frequency band.

[0187] Figure 6 is a drawing for explaining the principle of attenuating noise over a wide frequency range by arranging multiple resonators having different resonant frequencies and overlapping multiple transmission loss bands.

[0188] As illustrated in Fig. 6(a), multiple resonators are connected in parallel along the main path, and each resonator is designed to have a different length Li. Accordingly, each resonator has a different resonant frequency fi, and in the drawing, for example, the resonators corresponding to i = 1, 2, 3, and 4 are indicated to have resonant frequencies of 257 Hz, 297 Hz, 361 Hz, and 413 Hz, respectively.

[0189] Figure 6(b) is a graph depicting the transmission loss characteristics of individual resonators and the overall transmission loss characteristics when all of them are arranged along the frequency axis. While individual resonators form peaks at their respective resonant frequencies, their overlapping arrangements result in high transmission loss characteristics across a wide frequency band, from 250 Hz to 500 Hz or higher. This structure demonstrates that it is not limited to a specific single-frequency attenuation, but is effective for multi-band or broadband noise reduction.

[0190] Fig. 7 is a drawing for explaining that the superposition effect of transmission loss can be maximized by spacing out multiple resonators (HR1, HR2) each having a resonant frequency on the main filament and optimally setting the spacing between them.

[0191] As illustrated in Fig. 7(a), HR1 and HR2 are noise reduction means each having a Helmholtz resonator structure, and are sequentially connected along the main flow path. At this time, by appropriately adjusting the spacing L between the resonators, the damping effects of the two resonators can be designed to overlap in the frequency domain.

[0192] As mentioned above, the resonant frequency depends on the physical structure of the resonator (speed of sound, cross-sectional area of ​​the neck, volume of the resonant space, and length of the neck).

[0193] To superimpose the attenuation characteristics of these two resonators, it is crucial to establish a positional relationship where the reflected waves from the two resonators can interfere with each other on the main channel. To achieve this, the center-to-center distance L between the resonators can be optimally determined using the following formula.

[0194]

[0195]

[0196] f HR1 , f HR2 is the resonant frequency of HR1 and HR2, f m is the overlap center frequency between HR1 and HR2, which means the point where the frequency bands of the two resonators overlap most effectively.

[0197] L opt The attenuation effect is maximized when the phase is reversed at that frequency (1 / 4 wavelength interval).

[0198] P1 to P4 shown in Fig. 7(a) represent pressure observation points on the main euro, and P1 and P2 correspond to pressures at the front and rear positions of HR1, and P3 and P4 correspond to pressures at the front and rear positions of HR2, respectively.

[0199] These points are used as reference points to visually assess the acoustic pressure distribution before and after the resonator, or to interpret the interference characteristics of reflected waves between resonators. For example, if the distance between P2 and P3 is L, and the structure is designed such that the reflected wave reverses its phase as it travels this distance, superposition loss can be maximized.

[0200] Figure 7(b) is a graph comparing the transmission loss when only a single resonator is applied to HR1 and HR2, and when two resonators are arranged (Lined array). HR1 and HR2 show transmission loss peaks at different frequencies, and when two resonators are arranged, they overlap, showing an improvement in transmission loss over a wide frequency range. In particular, L derived from the above formula opt When applied (Lined array), a broadband attenuation performance superior to the individual performance of the two resonators can be realized.

[0201] Hereinafter, a suction muffler (30) according to an embodiment of the present disclosure will be described with reference to FIG. 8. Referring to FIG. 8, a compressor (10) may include a suction muffler (30). The suction muffler (30) may reduce noise of the compressor (10). The suction muffler (30) may include a diffuser-type muffler structure. The suction muffler (30) may form a diffuser-type muffler structure together with a piston (130).

[0202] The piston (130) may have a cylindrical shape having a space inside. The piston (130) may include a cylindrical piston body (136) and a piston head (131) arranged at one end of the piston body (136). The piston head (131) may cover one side of the internal space of the piston body (136). The piston head (131) may be located at the front end of the piston body (136).

[0203] A discharge port (132) is formed in the piston head (131) so that the refrigerant that has passed through the suction muffler (30) can be discharged to the outside of the piston (130). The refrigerant discharged through the discharge port (132) of the piston (130) flows into the space (123) between the piston (130) and the cylinder (120) and can be compressed by the piston (130).

[0204] The piston (130) may include a check valve (133) that opens and closes the discharge port (132). The check valve (133) may be fastened to the outside of the piston head (131) by a fastening member (134).

[0205] The check valve (133) may be made of a flexible material. The check valve (133) may cover the discharge port (132).

[0206] When the piston (130) moves backward, the internal pressure of the space (123) between the piston (130) and the cylinder (120) decreases, and the check valve (134) opens, allowing the refrigerant passing through the suction muffler (30) to flow into the internal space (123) of the cylinder (120).

[0207] When the piston (130) moves forward and enters the cylinder (120), the pressure in the space (123) between the piston (130) and the cylinder (120) increases, the check valve (134) closes, and the refrigerant introduced into the space (123) can be compressed.

[0208] The piston (130) may include a flange (137) coupled with a connecting member (138). The flange (137) may be located at the rear end of the piston body (136). The flange (137) may be coupled with a piston supporter (160).

[0209] <1st resonator (31)>

[0210] The suction muffler (30) may include a discharge portion (60). The discharge portion (60) may include a discharge pipe (61). The discharge pipe (61) may have a cylindrical shape. The discharge pipe (61) may have a cylindrical shape with a length longer than a diameter.

[0211] The discharge tube (61) may be arranged inside the piston (130). The outer circumference of the discharge tube (61) may be spaced apart from the inner circumference of the piston (130). A space (31) may be formed between the discharge tube (61) and the piston. The space (31) may be a resonator for reducing noise. Hereinafter, the space is referred to as a first resonator (31). The first resonator (31) may be a Helmholtz resonator.

[0212] The discharge portion (60) may include a first expansion portion (66) arranged on the downstream side of the refrigerant flow. The expansion portion (66) may be arranged on the downstream side of the discharge pipe (61).

[0213] The first expansion portion (66) may extend radially outward from the discharge pipe (61). The first expansion portion (66) may extend radially outward from the discharge pipe (61) and may extend downstream. The first expansion portion (66) may have a cylindrical shape. The first expansion portion (66) may be a cylindrical shape with a diameter greater than a length.

[0214] The first expansion portion (66) can be spaced apart from the piston (130). The interior of the discharge portion (60) and the first resonator (31) can be communicated through the gap (g) between the first expansion portion (66) and the piston (130). The spaced portion between the first expansion portion (66) and the piston (130) is referred to as the inlet (311) of the first resonator (31).

[0215] The outer circumference of the first extension (66) may be spaced inward from the piston body (130). The outer diameter (r2) of the first extension (66) may be smaller than the inner diameter (r1) of the piston body (130).

[0216] The downstream end of the first extension (66) can be spaced apart from the piston head (131).

[0217] <Second resonator (32)>

[0218] The suction muffler (30) may include a suction portion (40) and a connecting portion (50). The suction portion (40) may include a cylindrical first housing (42), and the connecting portion (50) may include a connecting tube (52) disposed inside the first housing (42). The outer diameter of the connecting tube (52) may be smaller than the inner diameter of the first housing (62). The outer circumference of the connecting tube (52) may be spaced apart from the inner circumference of the first housing (62), so that a space (32) may be formed between the connecting tube (52) and the first housing (42). The space (32) may be a resonator that reduces noise. Hereinafter, the space (32) is referred to as a second resonator (32). The second resonator (32) may be a Helmholtz resonator.

[0219] The connecting portion (50) may include a hole (321) that radially penetrates the connecting tube (52). The hole (321) may form an inlet of the second resonator (32). Hereinafter, the hole (321) is also referred to as an inlet of the second resonator (32).

[0220] The discharge unit (60) may include a second housing (65). The second housing (65) may be arranged on the upstream side of the discharge pipe (61) in the refrigerant flow direction.

[0221] The connecting portion (50) may include a second extension portion (54). The second extension portion (54) may support the connecting portion (50) from the discharge portion (60).

[0222] The second extension (54) may be positioned on the downstream side of the connecting pipe (52). The second extension (54) may extend from the downstream end of the connecting pipe (52).

[0223] The second expansion portion (54) may be formed in a cylindrical shape. It may be a cylindrical shape with a diameter greater than the length of the second expansion portion (54). The second expansion portion (54) may have an outer diameter greater than the outer diameter of the connecting pipe (52).

[0224] The second extension (54) can be inserted into the interior of the second housing (65). The second extension (54) can be in contact with the second housing (65). The outer circumference of the second extension (54) can be in contact with the inner circumference of the second housing (65).

[0225] The space of the second resonator (32) can be defined by the outer circumference of the connecting tube (52), the inner circumference of the first housing (42), the supporter (51), and the extension (54).

[0226] <Third Resonator (33)>

[0227] The second housing (65) may have a cylindrical shape. The second housing (65) may have a larger diameter than the discharge pipe (61). The second housing (65) may have an inner diameter larger than the outer diameter of the discharge pipe (61).

[0228] The discharge portion (60) may include a first extension pipe (63) extending from the discharge pipe (61). The first extension pipe may extend from the discharge pipe (61) to the upstream side of the refrigerant flow.

[0229] The first extension pipe (63) may be arranged inside the second housing (65). The first extension pipe (63) may be spaced inward from the second housing (65). The diameter of the first extension pipe (63) may be smaller than the diameter of the second housing (65). The outer diameter of the first extension pipe (63) may be smaller than the inner diameter of the second housing (65).

[0230] A space (33) may be formed between the second housing (65) and the first extension tube (63), and the space (33) may also be referred to as a third resonator (33). The third resonator (33) may be a Helmholtz resonator.

[0231] The connecting portion (50) may include a neck (53) provided at the downstream end of the connecting portion (50). The neck (53) may protrude downstream from the second extension portion (54). The neck (53) may be ring-shaped or cylindrical. The neck (53) may be ring-shaped with a diameter greater than its length.

[0232] A first extension pipe (63) described later in the discharge portion (60) can be inserted into the inner side of the neck (53). The neck (53) can be spaced outward from the first extension pipe (63) to form an inlet of the third resonator (33).

[0233] <4th resonator (34)>

[0234] The second expansion portion (54) may be a cylindrical shape extended from the connecting tube (52). The second expansion portion (54) may have a diameter larger than the diameter of the connecting tube (52). The second expansion portion (54) may have an inner diameter larger than the inner diameter of the connecting tube (52).

[0235] The first extension pipe (63) can be inserted into the inside of the second extension part (54). The upstream part of the first extension pipe (63) can be placed inside the second extension part (54).

[0236] A space (34) is formed between the first extension tube (63) and the second extension part (54), and the space (34) is called a fourth resonator (34). The fourth resonator (34) may be a Helmholtz resonator.

[0237] The first extension pipe (63) may be spaced inward from the second extension portion (54). The outer diameter of the first extension pipe (63) may be smaller than the inner diameter of the second extension portion (54).

[0238] The first extension pipe (63) may be spaced apart from the connection portion (50). The first extension pipe (63) may be spaced apart from the connection portion (52) and / or the second extension portion (54). The first extension pipe (63) may be spaced downstream from the connection portion (52) and / or the second extension portion (54).

[0239] The first extension tube (63) and the connecting portion (54) can be spaced apart from each other to form an entrance to the fourth resonator (34).

[0240] <5th resonator (35)>

[0241] The suction portion (40) may include a suction guide (41) forming an inlet (410) of the suction muffler (30). The suction guide (41) may be provided at the upstream end of the first housing (42).

[0242] The suction guide (41) may extend in the direction of refrigerant flow. The suction guide (41) may extend downstream in the direction of refrigerant flow. The suction guide (41) may be arranged inside the first housing (42).

[0243] The suction guide (41) may be inclined so that the radius becomes narrower as it goes downstream. The suction guide (41) may be inclined in a curved manner.

[0244] The suction portion (40) may include an outer ring (415) protruding from the suction guide (41). The outer ring (415) may protrude downstream from the suction guide (41).

[0245] The outer ring (415) may have a ring shape. The outer ring (415) may have a cylindrical shape with a diameter greater than the length.

[0246] The outer ring (415) may be placed on the inside of the first housing (42). The outer ring (415) may be spaced inward from the first housing (42). The space between the outer ring (415) and the first housing (42) may be referred to as a fifth resonator (35). The fifth resonator (35) may be a 1 / 4 wavelength field.

[0247] The outer diameter of the outer ring (415) may be smaller than the inner diameter of the first housing (42).

[0248] The outer ring (415) can be inserted into the connecting portion (50). The outer ring (415) can be inserted into the inner space of the supporter (51). The downstream end of the outer ring (415) can be located downstream of the upstream end of the supporter (51).

[0249] The outer ring (415) can be spaced apart from the connecting portion (50). The outer ring (415) can be spaced radially inward from the supporter (51).

[0250] The outer ring (415) may be spaced upstream from the connecting portion (50). The outer ring (415) may be spaced upstream from the supporter (51) and / or the connecting pipe (52).

[0251] <6th resonator (36)>

[0252] The outer ring (415) can be positioned radially outside the downstream end of the suction guide (41).

[0253] The suction portion (40) may include an inner ring (416) extending downstream from the suction guide (41). The inner ring (416) may extend from the downstream end of the suction guide (41).

[0254] The inner ring (416) may be placed on the inner side of the outer ring (415). The inner ring (416) may be spaced inward from the outer ring (415). A space (36) may be formed between the spaced inner ring (416) and the outer ring (415), and the space (36) may be referred to as a sixth resonator (36). The sixth resonator (36) may be a 1 / 4 wavelength field.

[0255] The inner ring (416) may be spaced apart from the connecting portion (50). The inner ring (416) may be spaced upstream from the connecting portion (50). The inner ring (416) may be spaced upstream from the supporter (51) and / or the connecting pipe (52).

[0256] The downstream end of the inner ring (416) may be positioned at the same position in the longitudinal direction of the suction muffler as the downstream end of the outer ring (415). Alternatively, the outer ring (415) may be further extended downstream.

[0257] The inner ring (416) can be inserted into the connecting portion (50). The inner ring (416) can be inserted into the inner space of the supporter (51). The downstream end of the inner ring (416) can be located downstream of the upstream end of the supporter (51).

[0258] <7th Resonator (37)>

[0259] The discharge portion (60) may further include a second extension pipe (67). The second extension pipe (67) may extend downstream from the discharge pipe (61).

[0260] The second extension pipe (67) may have a ring shape. The second extension pipe (67) may have a cylindrical shape with a diameter greater than its length.

[0261] The second extension tube (67) may be arranged inside the first extension section (66). The second extension tube (67) may be spaced inward from the first extension section (66). The space between the second extension tube (67) and the first extension section (66) may be referred to as a seventh resonator (37). The seventh resonator (37) may be a 1 / 4 wave field.

[0262] The outer diameter of the second extension pipe (67) may be smaller than the inner diameter of the first extension part (66).

[0263] The second extension pipe (67) can be spaced apart from the piston head (131). The second extension pipe (67) can be spaced upstream from the piston head (131).

[0264] The length of the second extension pipe (67) may be shorter than the length of the first extension portion (66). The downstream end of the second extension pipe (57) may be located upstream of the downstream end of the first extension portion (66).

[0265]

[0266] Meanwhile, the first extension portion (63) can form an inlet (62) of the discharge portion (60). The first extension portion (66) can form an outlet (68) of the discharge portion (60). The outlet (68) of the discharge portion (60) can also be referred to as an outlet (68) of the suction muffler (30).

[0267] The inner diameter of the downstream end of the suction guide (41), the inner diameter of the connecting pipe (52), and the inner diameter (D1) of the upstream end of the discharge pipe (61) may be the same.

[0268] The discharge pipe (61) may be inclined so that its diameter increases from the inlet (62) toward the outlet (68). The inner diameter (D2) of the downstream end of the discharge pipe may be larger than the inner diameter (D1) of the upstream end of the discharge pipe (61).

[0269] A detailed description of the diameter and inclination of the discharge pipe (61) will be described later with reference to Fig. 18.

[0270] Meanwhile, the second housing (65) can be connected to the first housing (42) of the suction unit (40). The suction unit (40) and the discharge unit (60) can be coupled to each other. The first housing (42) and the second housing (65) can be coupled to each other.

[0271] The suction portion (40) may include a flange (465) provided at the downstream end of the first housing (42), and the discharge portion (60) may include a flange (645) provided at the upstream end of the second housing (65). The flange (465) of the suction portion (40) and the flange (645) of the discharge portion (60) may be coupled to each other.

[0272] The discharge portion (60) may include an insert portion (64) extending upstream of the refrigerant flow from the second housing (65). The insert portion (64) may protrude upstream from the flange (645). The insert portion (64) may have a ring shape.

[0273] The suction portion (40) may include a receiving portion (46) provided at the downstream end of the first housing (42). The receiving portion (46) may be recessed outward from the inner periphery of the first housing (42).

[0274] The insertion part (64) can be inserted into the receiving part (46). When the insertion part (64) is inserted into the receiving part (46), the flange (645) of the discharge part (60) and the flange (465) of the suction part (40) can come into contact.

[0275] Meanwhile, the supporter (51) can be inserted into the interior of the first housing (42). The supporter (51) can be in contact with the first housing (42). The outer circumference of the supporter (51) can be in contact with the inner circumference of the first housing (42). The first housing (42) can include a step portion (45) on the inner circumference, and the position of the connection portion (50) with respect to the suction portion (40) can be set by the step portion (45).

[0276] Hereinafter, with reference to FIGS. 8 to 12, the problems of the conventional diffuser-type muffler and the effect of the suction muffler (30) according to the present disclosure will be described.

[0277] The y-axis of Figures 9 and 10 represents the sound pressure level (SPL), and the unit is dBA (decibels A-weighted). SPL is an index that converts sound pressure into a logarithmic scale to quantify the size of sound, allowing for an objective comparison of the intensity of sound perceived by humans.

[0278] In particular, dBA is a sound pressure level that applies the A-weighting that reflects human hearing sensitivity. It is a value measured by emphasizing the mid- and high-frequency range (especially 500 Hz to 6 kHz) to which people are relatively sensitive, and attenuating the low-frequency and ultra-high-frequency range. Since it is measured similarly to the actual auditory noise level, it is the most widely used standard when measuring noise in home appliances or living environments.

[0279] Therefore, a lower SPL [dBA] value in this figure means that the actual perceived noise at that frequency has been reduced, and the reduction in SPL in a specific band is directly related to the noise reduction effect felt by the consumer while the refrigerator is operating.

[0280] Fig. 9 shows the noise (91, 92) of a compressor using a conventional diffuser-type muffler and the noise (93) of a compressor equipped with a suction muffler according to the present disclosure, and Fig. 10 shows the noise (1001) of a refrigerator equipped with a compressor using a conventional diffuser-type muffler and the noise (1002) of a refrigerator (1) equipped with a compressor (10) equipped with a suction muffler according to the present disclosure. ㅇ shows the insertion loss (1101, 1102) of a conventional diffuser-type muffler and the insertion loss (1103) of a suction muffler (30) according to the present disclosure, and Fig. 12 is a graph showing the experimental results for the insertion loss of a conventional diffuser-type muffler.

[0281] <Problems of conventional technology and effects of the first and second resonators (31, 32)>

[0282] Referring to Fig. 9, it can be seen that the noise of a compressor equipped with a conventional diffuser-type muffler is louder in the 400 Hz to 800 Hz band (9a) compared to other bands. The noise in this band may be generated from a cavity inside the compressor shell (100).

[0283] For example, the noise (91) of a compressor equipped with a conventional first diffuser-type muffler is louder than other bands in the range of 400 Hz to 600 Hz, and the noise (92) of a compressor equipped with a conventional second diffuser-type muffler is louder than other bands in the range of 800 Hz.

[0284] Referring to Fig. 10, the noise of a refrigerator equipped with a compressor (1001) having a conventional diffuser-type muffler is louder in the band (10a) of 400 Hz to 1000 Hz than in other bands.

[0285] Referring to FIGS. 8 to 10, the resonant frequency of the first resonator (31) may be lower than the resonant frequency of the second resonator (32). For example, the resonant frequency of the first resonator (31) may be in the range of 300 Hz to 500 Hz, and the resonant frequency of the second resonator (32) may be in the range of 500 Hz to 800 Hz. For example, the resonant frequency of the first resonator (31) may be 400 Hz, and the resonant frequency of the second resonator (32) may be 600 Hz.

[0286] The volume of the first resonator (31) may be larger than the volume of the second resonator (32). The length of the discharge tube (61) may be longer than the length of the connecting tube (52).

[0287] The length of the first extension (66) forming the entrance (311) of the first resonator (31) may be longer than the thickness of the connecting tube (52) forming the length of the entrance of the second resonator (312).

[0288] The distance between the inlet (311) of the first resonator (31) and the inlet of the second resonator (312) can be set based on the resonant frequency of the first resonator (31), the resonant frequency of the second resonator, and the speed of sound. The speed of sound can be determined depending on the type and temperature of the refrigerant.

[0289] For example, if the known frequency of the first resonator (31) is 400 Hz and the resonant frequency of the second resonator (32) is 600 Hz, the optimal distance (L) between the inlet (311) of the first resonator (31) and the inlet (321) of the second resonator (32) depending on the type and temperature of the refrigerant opt ) are as shown in the table below. In the past, R-134a was widely used in refrigerators, and recently, R-600a is the most widely used refrigerant for refrigerators.

[0290] Refrigerant temperature (℃)Speed ​​of sound (m / s)Optimal distance (mm)R-134a018596.41019099.020195101.6R-600a0200104.210210109.420220114.6

[0291] For example, the distance (L) between the inlet (311) of the first resonator (31) and the inlet (321) of the second resonator (32) may be in the range of 95 mm to 115 mm. For example, the distance (L) may be 110 mm.

[0292] Fig. 11 is a graph showing the insertion loss (1101, 1102) of a conventional muffler and the insertion loss (1103) of a suction muffler (30) of the present disclosure, where the x-axis represents frequency and the y-axis represents insertion loss. The insertion loss is a value expressed in dB units as a difference in sound level depending on whether a muffler is installed, and a larger value means a better noise reduction effect.

[0293] As shown in the graph, when the suction muffler (30) of the present invention was applied (1103), the insertion loss was improved across the entire band compared to the prior art (1101, 1102).

[0294] For example, the insertion loss of the suction muffler (30) in the 400 Hz to 800 Hz band (11a) is improved compared to the conventional muffler (1101, 1102).

[0295] This shows the effect of the first resonator (31), the second resonator (32) and the superposition of the two resonators described above.

[0296] <Problems with conventional technology and the effect of the third resonator (33)>

[0297] Referring to Fig. 9, it can be seen that the noise of the compressor (10) is loud in the band (9b) including 5 kHz. The noise in the 5 kHz band may correspond to the main noise generated when the compressor (10) compresses the refrigerant. For example, it may be noise generated by the reciprocating motion of the piston (130) and the closing and opening of valves such as the check valve (133).

[0298] The suction muffler (30) of the present disclosure may include a third resonator (33) to improve the main noise of the compressor (10).

[0299] The resonant frequency of the third resonator (33) may be greater than the resonant frequencies of the first resonator (31) and the second resonator (32). The volume of the third resonator (33) may be smaller than the volume of the first resonator (31) and / or the volume of the second resonator (32).

[0300] For example, the resonant frequency of the third resonator (33) may be within the range of 4 KHz to 6.3 KHz. For example, the resonant frequency of the third resonator (33) may be 5 KHz.

[0301] Referring to Fig. 11, in the case of the suction muffler (30) according to the embodiment of the present disclosure (1101), the insertion loss has a large value in the 5 KHz band (11d). Therefore, when the suction muffler (30) is applied, noise in the 5 KHz band (11d) can be reduced.

[0302] This shows the effect of the third resonator (33) described above.

[0303] In the case of conventional mufflers (1102, 1103), it can be seen that the insertion loss is large in the 5 kHz band (11d). However, in the case of conventional mufflers, although noise in the 5 kHz band (11d) can be reduced, there is a problem in that noise in other bands cannot be reduced. For example, as described above with reference to FIG. 9, conventional mufflers have a problem in that they cannot reduce noise in the 400 Hz to 800 Hz band.

[0304] As shown in Fig. 11, the suction muffler (30) of the present disclosure comprises first and second resonators (31, 32) through a structural change of the muffler, and also has a third resonator (33) having a resonant frequency in the 5 kHz band, thereby reducing noise in the 400 Hz to 800 Hz band (11a) while also reducing noise in the 5 kHz band (11d).

[0305] <Problems of conventional technology and the effects of the 4th and 5th resonators (34, 35)>

[0306] Referring to Fig. 11, in the case of the conventional muffler of the second case (1102), the insertion loss shows a negative value in the band of 1500 Hz to 2000 Hz (11b) and the band of 2500 Hz (11c). The conventional muffler of the second case has the characteristic of having more resonators than the conventional muffler of the first case.

[0307] Figure 12 shows another experimental result for the insertion loss of the conventional muffler of the second case above. In this case, the insertion loss is negative in the bands of 1100 Hz to 1700 Hz and 2500 Hz.

[0308] That is, in the case of a conventional muffler (1102), the insertion loss may be negative in the 1100 Hz to 2000 Hz band and the 2500 Hz band.

[0309] When insertion loss is negative, this indicates that the muffler actually increased noise in a specific frequency band. In other words, the sound pressure level after insertion of the muffler is higher than before, indicating that the resonator or flow path structure has acted to amplify the corresponding frequency component.

[0310] This phenomenon can occur when the resonator's position or design frequency is inappropriate, or when the conditions for reflected wave interference between resonators are not optimally aligned. In particular, when the reflected wave is out of phase with the incident wave (constructive interference), certain frequency components are amplified, resulting in worsened noise.

[0311] Therefore, simply increasing the number of resonators in a muffler cannot guarantee effectiveness, and optimal placement based on the design frequency and spacing of the resonators and fluid flow characteristics must be considered. The suction muffler (30) according to one embodiment of the present disclosure is designed to improve these aspects and secure a stable positive insertion loss across the entire frequency band.

[0312] The resonant frequency of the fourth resonator (34) can be within the range of 1100 Hz to 2000 Hz.

[0313] The volume of the fourth resonator (34) may be smaller than the volume of the first resonator (31) and the volume of the second resonator (32).

[0314] The resonant frequency of the fifth resonator (35) may be within the range of 2400 Hz to 2600 Hz. For example, the resonant frequency of the fifth resonator (35) may be 2500 Hz.

[0315] Referring to Fig. 11, in the case of the suction muffler of the present disclosure (1103), it can be seen that the insertion loss is positive in the band (11b) of 1100 Hz to 2000 Hz and the band (11c) of 2500 Hz. This is an effect according to the arrangement of the 4th and 5th resonators (34, 35) and other resonators.

[0316] <Problems of conventional technology and the effects of the 6th and 7th resonators (36, 37)>

[0317] Referring to Fig. 9, it can be seen that the noise level of the conventional compressor (91, 92) is high in the 8 KHz to 10 KHz band (9c). The noise in this band may be due to vibration of the shell (100) of the compressor (10).

[0318] The resonant frequency of the sixth resonator (36) may be 8 KHz.

[0319] The resonant frequency of the seventh resonator (37) may be 10 KHz.

[0320] Referring to Fig. 11, the insertion loss of the suction muffler (30) in the 8 KHz to 10 KHz band (11e) is improved compared to the conventional muffler (1101, 1102). This indicates the effect of the 6th and 7th resonators (36, 37).

[0321] Hereinafter, with reference to FIGS. 13 to 18, a structure for minimizing the problem of reduced compression performance while reducing noise will be described.

[0322] Referring to Figure 13, when a fluid passes through the interior of a compressor or other device, a pressure drop (ΔP) occurs depending on the shape of the structure. In general, the pressure drop is divided into viscous loss in the laminar flow region and inertial loss in the turbulent flow region, and can be expressed as follows.

[0323]

[0324] Here, DP is the pressure drop, Q is the volume flow rate, μ is the viscosity of the fluid, ρ is the density of the fluid, K L is the laminar loss coefficient (or viscous loss coefficient), K T means the turbulence loss coefficient.

[0325] In this formula, the laminar and turbulent loss coefficients are determined solely by the geometry of the structure, regardless of the fluid properties. For example, rapid contractions or expansions of the flow path, bends, the shape of the inlet, and the presence of obstacles increase the loss associated with the flow, thus increasing the corresponding coefficients.

[0326] That is, regardless of the type of fluid in the same structure, the laminar and turbulent loss coefficients are the same, reflecting the pressure resistance characteristics of the structure. Therefore, pressure loss can be minimized through shape optimization.

[0327] For example, a straight, smooth pipe has low resistance. In contrast, a pipe with a sharp constriction, a sharp inlet, or a 90-degree bend has high resistance.

[0328] Figure 14 illustrates the difference in viscous loss coefficients depending on the inlet shape. Figure 14(a) is a reentrant shape with an inlet protruding inward, and due to significant flow separation and vortex generation, the viscous loss coefficient is very high at approximately 0.8. In the sharp-edged shape of Figure 14(b), the flow contracts rapidly along the sharp edge, resulting in a loss of around 0.5 in the viscous loss coefficient.

[0329] In contrast, the Slightly Rounded shape in Fig. 14(c) has a gentle inlet boundary, which reduces flow separation and reduces loss with a viscous loss coefficient of 0.2. In particular, Fig. 14(d) is a Well-Rounded shape with sufficient curvature at the inlet, which ensures smooth fluid transition and maintains stable flow. The loss coefficient at this time is approximately 0.04, the lowest among the four.

[0330] Figure 15 is a graph showing how the loss coefficient (K) changes according to the geometric variables of the inlet shape, such as the radius of curvature ratio (r / d) and the inlet length ratio (L / d), when a fluid is introduced. Each curve in the graph reflects a different inlet length ratio or inlet angle, with the lowest curve representing a curved inlet. In common, the loss coefficient starts at 0.5 at points where the value of r / d or L / d is 0. This represents the loss coefficient when the inlet has a sharp-edged structure.

[0331] As shown in the graph, the loss coefficient decreases rapidly as the radius of curvature ratio (r / d) increases, while extending the inlet length alone has a relatively limited effect on reducing loss. This suggests that, at the same starting point, the well-rounded structure has a greater effect on reducing flow loss than the angled structure, effectively stabilizing the flow.

[0332] Therefore, the present invention has a significant technical difference in that it is designed to enable smooth suction of fluid without structural interference and minimize pressure drop due to viscous loss by adopting a curvature structure with a sufficiently secured r / d value for the inlet shape, i.e., a well-rounded shape.

[0333] Referring to FIGS. 8, 14, and 15, the suction muffler (30) has a well-rounded suction guide (41) structure as illustrated in FIG. 14(d). The suction guide (41) may be curved and inclined. The curvature radius ratio of the suction guide (41) may be greater than 0.2.

[0334] This minimizes flow separation upon fluid inflow and significantly reduces pressure drop due to viscosity loss. Even when applied in conjunction with the noise-reducing structure within the muffler, this design provides a significant differentiating factor, as it minimizes suction resistance upon refrigerant inflow.

[0335] In addition, the suction performance can be improved even without having a suction guide provided separately from the suction muffler through the suction guide structure.

[0336] Figure 16 shows the viscosity loss coefficient (K) depending on the difference in the exit shape through which the fluid exits the flow path. L ) is a drawing showing the effect on the structure. Figures 16(a) to 16(d) represent reentrant, sharp-edged, slightly-rounded, and well-rounded structures, respectively, and the exit loss coefficient is commonly maintained at about 1.0 in all shapes. This is because the fluid flow at the exit end freely diffuses into the atmosphere or expansion space, and the pressure loss is determined by the change in flow rate and the flow rate conservation condition rather than the structural shape.

[0337] Referring to Fig. 8, the suction muffler of the present disclosure may have a reentrant or sharp-edged structure among the outlet shapes illustrated in Fig. 16. For example, a first expansion portion (66) is provided at the downstream end of the discharge pipe (61), which forms the inlet of the first resonator and simultaneously exhibits a sharp-edged outlet structure. However, the position is the terminal end of the suction path and the section where the refrigerant flows into the resonator, and the presence of the expansion space causes the flow rate to drop rapidly, and the effect on the pressure drop is minimal.

[0338] In addition, the first extension pipe (67) extending from the discharge pipe (61) forms a seventh resonator (37) between itself and the first expansion portion (66), and the inlet of the resonator may be configured in a reentrant shape. Since this is also a structure in which the fluid flows into a rapidly expandable space, the loss coefficient is maintained at a certain level regardless of the shape, as illustrated in Fig. 16(a), and no substantial pressure drop problem occurs.

[0339] Therefore, in this disclosure, it can be seen that even if a reentrant or sharp-edged structure is applied to the exit shape, it does not significantly affect the pressure loss in the entire flow system, and it is an effective design that can structurally induce smooth refrigerant inflow.

[0340] Figure 17 is a graph showing how the pressure drop within the main channel changes depending on the inner diameter of the main channel, and shows the pressure drop values ​​when the refrigerant mass flow rate (mdot) is 2 g / s and 3 g / s, respectively. The pressure drop is calculated according to the following empirical formula, and the pressure drop increases exponentially as the inner diameter decreases.

[0341] In particular, when the inner diameter is 6 mm or less, the pressure drop exceeds 1000 Pa when the mass flow rate is 2 g / s, which may negatively affect compressor performance. Generally, when the pressure drop exceeds 1000 Pa, the overall compression performance may decrease by approximately 1% or more.

[0342] Accordingly, in the present invention, by setting the inner diameter of the main flow path to at least 7 mm, the pressure drop is maintained at 1000 Pa or less even when the mass flow rate is 3 g / s, thereby minimizing the performance degradation of the compressor even if a muffler structure is added.

[0343] Referring to FIG. 8, the main flow path of the present invention includes a discharge pipe (61) and a connection pipe (52), and the suction side of the main flow path is formed by the downstream end of the suction guide (41) or the inner ring (416).

[0344] The inner diameter (D1) of the upstream side of the discharge pipe (61) and the inner diameter (D1) of the connecting pipe (52) may each be set to 7 mm or more. In addition, the inner diameter of the downstream end of the suction guide (41) or the inner ring (416) may also be set to 7 mm or more.

[0345] The inner diameter (D1) of the upstream side of the discharge pipe (61) and the inner diameter (D1) of the connecting pipe (52) may be formed to be identical to each other. The inner diameter of the downstream end of the suction guide (41) or the inner ring (416) may also be formed to be identical to or continuous with the inner diameter of the connecting pipe (52).

[0346] Through this design, the suction muffler of the present disclosure can effectively combine the damping performance generated by the resonator structure while minimizing the loss of refrigerant flow, thereby simultaneously securing refrigerant efficiency and noise reduction performance of the entire system.

[0347] Figure 18 is a graph showing the change in the pressure loss coefficient (ζ) according to the expansion angle (θ) in a diffusion-type flow path, and shows how the loss coefficient changes according to the area ratio (n=A2 / A1=D2^2 / D1^2) under the condition that the Reynolds number is 10000 or more.

[0348] According to the graph, regardless of the value of n, the loss coefficient remains almost constant or decreases slightly when the expansion angle is within the range of 5° to 10°. When n is 4 or greater, the loss coefficient tends to increase rapidly from an expansion angle of 10°. In addition, when n is 2, the loss coefficient remains almost constant or decreases slightly when the expansion angle is within the range of 5° to 15°, and the loss coefficient tends to increase from an expansion angle of 15°.

[0349] In the present invention, the expansion angle of the discharge pipe (61) was designed in consideration of such flow characteristics.

[0350] Referring to Fig. 8, the inner surface of the discharge pipe (61) may be inclined so that the diameter increases from the upstream side to the downstream side. The discharge pipe (61) is connected to the connecting pipe (52) and may have a diffusion structure that gradually expands from the upstream side inner diameter (D1) to the downstream side inner diameter (D2).

[0351] For example, the inclination angle of the discharge pipe (61) can be set within a range of 5° or more and 10° or less. For example, the inclination angle of the discharge pipe (61) can be 10°.

[0352] Alternatively, the ratio of the downstream area to the upstream area of ​​the discharge pipe (61) may be 2. This corresponds to a region in which the sensitivity of the loss coefficient is relatively low and controllable on the graph of Fig. 18. At this time, the inclination angle of the discharge pipe (61) may be 5° or more and 15° or less. For example, setting the angle to 10° minimizes the loss coefficient while facilitating structural implementation and enabling stable flow path formation even within a miniaturized suction muffler.

[0353] This minimizes diffusion loss that may occur as the refrigerant flows along the expansion section, and simultaneously ensures stability and efficiency of the refrigerant intake flow.

[0354] Accordingly, the present invention provides the advantage of suppressing unnecessary pressure loss within the suction passage and securing both suction efficiency and consistency of refrigerant flow by setting the expansion angle of the discharge pipe to the minimum point of the loss coefficient.

[0355] Any or all of the embodiments of the present disclosure described above are not mutually exclusive or distinct. Any or all of the embodiments of the present disclosure described above may have their respective components or functions combined or used together.

[0356] For example, it means that a configuration A described in a particular embodiment and / or drawing can be combined with a configuration B described in another embodiment and / or drawing. That is, even if a combination between configurations is not directly described, it means that a combination is possible, except in cases where a combination is described as impossible.

[0357] The above detailed description should not be construed as limiting in any respect and should be considered illustrative only. The scope of the present invention should be determined by a reasonable interpretation of the appended claims, and all modifications within the equivalent scope of the present invention are intended to be included within the scope of the present invention.

Claims

1. A shell providing space inside and including an inlet through which refrigerant flows; A cylinder placed inside the above shell; A piston comprising a cylindrical piston body and a piston head disposed at one end of the piston body and having a through hole, the piston reciprocating with respect to the cylinder; and A suction muffler is disposed in the internal space of the piston and allows refrigerant to flow between the suction port and the bore of the piston, The above suction muffler: A suction unit including an inlet of the above suction muffler and a cylindrical first housing having a space inside; A connecting portion including a connecting tube disposed inside the first housing; and It includes a discharge unit including a discharge pipe disposed inside the piston, The outer circumference of the discharge tube is spaced apart from the inner circumference of the piston, so that a first resonator is formed between the discharge tube and the piston, A compressor in which the outer circumference of the connecting pipe is spaced apart from the inner circumference of the first housing, so that a second resonator is formed between the connecting pipe and the first housing.

2. In paragraph 1, The discharge portion further includes a first extension portion extending radially outward from the discharge pipe, A compressor wherein the first expansion portion is spaced apart from the piston and an inlet of the first resonator is formed between the first expansion portion and the piston.

3. In paragraph 1, A compressor wherein the connecting portion includes an inlet of the second resonator penetrating the connecting tube in a radial direction.

4. In paragraph 1, A compressor wherein the volume of the first resonator is greater than the volume of the second resonator.

5. In paragraph 1, The above discharge part: A second housing having a diameter larger than the discharge pipe and located upstream of the discharge pipe; and A first extension pipe extending upstream from the discharge pipe, disposed inside the second housing, and having an outer diameter smaller than the inner diameter of the second housing, A compressor in which a third resonator is formed between the second housing and the first extension pipe.

6. In paragraph 5, A compressor wherein the volume of the third resonator is smaller than the volume of the first resonator and the volume of the second resonator.

7. In paragraph 5, The above connecting portion further includes a neck provided at the downstream end of the above connecting portion and into which the first extension pipe is inserted, A compressor in which the inner diameter of the neck is larger than the outer diameter of the first extension tube and smaller than the inner diameter of the second housing so that an inlet of the third resonator is formed between the neck and the first extension tube.

8. In paragraph 7, The above connecting portion further includes a second extension portion extending radially outward from the downstream end of the connecting pipe and connected to the neck, A compressor in which the second extension section is arranged on the outside of the first extension pipe, and a fourth resonator is formed between the first extension pipe and the second extension section.

9. In paragraph 8, A compressor in which the upstream end of the first extension pipe and the downstream end of the connection pipe are spaced apart from each other by a distance smaller than the length of the second extension portion to form the inlet of the fourth resonator.

10. In paragraph 9, A compressor in which the area of ​​the inlet of the third resonator is smaller than the area of ​​the inlet of the fourth resonator.

11. In paragraph 8, A compressor wherein the volume of the fourth resonator is smaller than the volume of the first resonator and the volume of the second resonator.

12. In paragraph 1, A compressor wherein the connecting portion further includes a supporter extending radially outward from an end of the connecting tube and contacting the inner side of the first housing.

13. In paragraph 12, The above suction part further includes a suction guide forming an inlet of the above suction part, A compressor in which the suction guide is arranged on the inside of the first housing, extends downstream from the first housing, and is inclined so that the diameter becomes smaller as it goes downstream.

14. In paragraph 13, The above suction portion includes a ring-shaped outer ring positioned radially outside the downstream end of the suction guide and protruding downstream from the suction guide, A compressor in which the outer ring is spaced radially inward from the first housing, so that a fifth resonator is formed between the outer ring and the first housing.

15. In paragraph 14, The above suction unit further includes a ring-shaped inner ring provided at the downstream end of the suction guide, A compressor in which the inner ring and the outer ring are spaced apart from each other in the radial direction to form a sixth resonator therebetween.

16. In paragraph 15, The above supporter extends upstream to form a space on the inside, A compressor in which the outer ring and the inner ring are inserted into the inner space of the supporter and are spaced apart from the supporter and the connecting pipe.

17. In paragraph 13, The above suction guide is a compressor with a curved slope.

18. In paragraph 13, A compressor in which the inner diameter of the downstream end of the above suction guide, the inner diameter of the above connecting pipe, and the inner diameter of the upstream end of the above discharge pipe are the same.

19. In paragraph 18, A compressor in which the inner diameter of the above suction guide, the inner diameter of the above connecting pipe, and the inner diameter of the above discharge pipe are 7 mm or more.

20. In the second paragraph, A compressor having a cylindrical shape in which the first expansion portion extends radially outward from the discharge pipe and extends downstream from the outer end.

21. In paragraph 20, The above discharge portion further includes a second extension pipe extending downstream from the discharge pipe and positioned inside the first extension portion, The second extension pipe and the first extension portion are spaced apart from each other in the radial direction to form a seventh resonator therebetween, A compressor in which the length of the second extension pipe extending downstream is shorter than the length of the first extension section.

22. In paragraph 1, A compressor in which the inner surface of the discharge pipe is inclined so that the diameter increases from the upstream side to the downstream side.

23. A shell providing space inside and including an inlet for introducing refrigerant; A cylinder placed inside the above shell; A piston comprising a cylindrical piston body and a piston head disposed at one end of the piston body and having a through hole, the piston reciprocating with respect to the cylinder; and A suction muffler is disposed in the internal space of the piston and allows refrigerant to flow between the suction port and the bore of the piston, The above suction muffler: A suction unit including an inlet of the above suction muffler and a cylindrical first housing having a space inside; A connecting portion including a connecting tube disposed inside the first housing; and It includes a discharge tube arranged inside the piston and a discharge portion including a first extension extending radially outward from the discharge tube, The outer diameter of the discharge pipe is smaller than the inner diameter of the piston so that a first resonator is formed between the discharge pipe and the piston, The first expansion portion is spaced apart from the piston, and an inlet of the first resonator is formed between the first expansion portion and the piston, The outer diameter of the connecting tube is smaller than the inner diameter of the first housing so that a second resonator is formed between the connecting tube and the first housing, A compressor wherein the connecting portion includes an inlet of the second resonator penetrating the connecting tube in a radial direction.

24. A shell providing space inside and including an inlet for introducing refrigerant; A cylinder placed inside the above shell; A piston comprising a cylindrical piston body and a piston head disposed at one end of the piston body and having a through hole, the piston reciprocating with respect to the cylinder; and A suction muffler is disposed in the internal space of the piston and allows refrigerant to flow between the suction port and the bore of the piston, The above suction muffler: A suction unit including an inlet of the above suction muffler and a cylindrical first housing having a space inside; A discharge unit including a second housing connected to the first housing and a discharge pipe extending downstream of the flow of the refrigerant from the second housing; and A connecting portion including a supporter in contact with the first housing, an extension portion in contact with the second housing, and a connecting pipe extending between the supporter and the extension portion, A compressor in which the connecting tube is spaced inwardly from the first housing and includes an inlet penetrating radially, so that a resonator is formed between the connecting tube and the first housing.

Images