Reciprocating compressor

Abstract

Disclosed is a reciprocating compressor. The reciprocating compressor can include a housing, a drive motor, a drive shaft, a piston, a cylinder, and a suction muffler, and a suction passage of the suction muffler can be formed with a valley in which a cross-sectional area of the suction passage is reduced. Thereby, it is possible to save manufacturing costs of the suction muffler by simplifying a structure of the suction muffler, and it is possible to effectively attenuate vibrations and / or noises from the suction muffler by sufficiently securing a muffling space while simplifying the structure of the suction muffler, and it is possible to further effectively attenuate the vibrations and / or the noises from the suction muffler by utilizing the valley.

Description

Technical Field

[0001] This utility model relates to a reciprocating compressor. Background Technology

[0002] Compressors can be classified into various types, such as rotary compressors, scroll compressors, and reciprocating compressors, based on their compression method and the type of refrigerant used. A reciprocating compressor compresses the refrigerant while a piston reciprocates within a cylinder.

[0003] Reciprocating compressors can be classified into vibratory and coupled types based on the piston's driving method. A vibratory reciprocating compressor compresses the refrigerant by having the piston connected to the moving part of a reciprocating motor and vibrating while simultaneously reciprocating within the cylinder. A coupled reciprocating compressor compresses the refrigerant by having the piston connected to the rotating shaft of a rotary motor and reciprocating within the cylinder.

[0004] In a vibratory reciprocating compressor, the suction side and discharge side can be arranged on one side with the piston as the center, or they can be arranged on both sides respectively. However, in the case of a connected reciprocating compressor, in most cases, the suction side and discharge side are arranged on one side of the piston simultaneously. This utility model relates to a connected reciprocating compressor. Hereinafter, a reciprocating compressor can be defined as a connected reciprocating compressor.

[0005] In a reciprocating compressor, the intake muffler and the exhaust muffler can be installed separately, or they can be bundled into a single assembly. This embodiment focuses on an example where the intake muffler and the exhaust muffler are installed separately, but the same principle applies to cases where the intake muffler and the exhaust muffler are combined into one unit.

[0006] Patent Document 1 (Korean Patent Publication No. 10-2016-0055499) discloses a reciprocating compressor with an intake muffler and an exhaust muffler integrated into a single muffler assembly. In this case, the shape of the muffler assembly is relatively complex, potentially increasing manufacturing costs. Furthermore, in Patent Document 1, the intake muffler is small, limiting its effectiveness in attenuating intake noise. This limitation becomes more pronounced as the reciprocating compressor is miniaturized.

[0007] Patent document 2 (Korean Patent Publication No. 10-2020-0132420) discloses a reciprocating compressor with separate intake and exhaust silencers. In this case, since the internal flow path of the intake silencer is formed in a straight line shape, there are limitations in effectively attenuating intake noise.

[0008] Furthermore, in Patent Document 2, because the intake port is simply formed through the muffler body, the intake volume cannot be sufficiently ensured, thus limiting its ability to improve compressor performance. Patent Document 1 also suffers from this limitation.

[0009] Furthermore, in Patent Documents 1 and 2, the gap between the oil pipe that injects oil into the internal space of the casing and the outer peripheral surface of the muffler facing the oil pipe becomes narrower. Therefore, a large amount of oil injected through the oil pipe will collide with the muffler and flow back to the oil pipe side. Utility Model Content

[0010] The purpose of this invention is to provide a reciprocating compressor that can save manufacturing costs by simplifying the structure of the intake muffler.

[0011] Another objective of this invention is to provide a reciprocating compressor that can effectively attenuate vibration and / or noise by simplifying the structure of the intake muffler while ensuring sufficient silencing space.

[0012] Another objective of this invention is to provide a reciprocating compressor capable of further effectively attenuating vibration and / or noise by forming internal flow paths of the intake muffler in various ways.

[0013] Another objective of this invention is to provide a reciprocating compressor that can improve compressor performance by increasing the amount of refrigerant drawn in through the intake port of the intake muffler.

[0014] Another objective of this invention is to provide a reciprocating compressor capable of suppressing the backflow of oil injected into the internal space of the housing via the oil pipe by widening the gap between the oil pipe and the intake muffler facing the oil pipe.

[0015] To achieve the objectives of this invention, a reciprocating compressor comprising a housing, a drive motor, a drive shaft, a piston, a cylinder, and an intake muffler can be provided. The drive motor can be disposed within the internal space of the housing. The drive shaft can be coupled to the rotor of the drive motor. The piston can be coupled to the drive shaft and reciprocate. The piston can be reciprocally inserted into the cylinder, and the cylinder, together with the piston, forms a compression chamber. The intake muffler can include a muffler inlet opening into the internal space of the housing, a muffler outlet opening into the intake side of the compression chamber, a silencing space disposed between the muffler inlet and the muffler outlet, and an intake passage connecting the muffler inlet and the muffler outlet across the silencing space. The intake passage can form a valley with a reduced cross-sectional area. Therefore, the manufacturing cost of the intake muffler can be saved by simplifying its structure. The vibration and / or noise at the intake muffler can be effectively attenuated by ensuring sufficient silencing space while simplifying its structure. The vibration and / or noise at the intake muffler can be further attenuated by utilizing the valley section.

[0016] As an example, the intake passage can be formed by a partition wall extending from the inner side of the intake muffler. The valley can be formed by a portion of the partition wall protruding in a direction intersecting the length direction of the intake passage. Thus, the valley can be shaped like a neck portion, thereby effectively attenuating vibrations and / or noise generated during refrigerant intake.

[0017] For example, the valley can be formed as a part of the partition wall with a curved protrusion. This allows for easy formation of valleys, thereby reducing refrigerant flow resistance.

[0018] Specifically, the valley can be formed symmetrically with respect to the centerline passing through the center of the valley. This minimizes the flow resistance of the refrigerant through the valley, thereby minimizing refrigerant intake losses caused by the valley.

[0019] As another example, the intake passage can be formed between a first partition wall and a second partition wall facing each other. The valley can be formed by a portion of the first partition wall protruding toward the second partition wall. This allows for easy formation of the valley, thereby reducing the flow resistance of the refrigerant.

[0020] For example, the first partition wall can be formed on a side more adjacent to the muffler inlet than the second partition wall. The valley can be formed in an arc shape. Thus, the suction flow path at the valley can be formed in the positive direction of the refrigerant flow, thereby further reducing the refrigerant flow resistance.

[0021] Furthermore, the second partition wall can be formed as a straight line in the valley. This allows the intake refrigerant to move slowly along the inner surface of the first partition wall, thereby further effectively attenuating vibrations and / or noise at the valley.

[0022] Furthermore, the second partition wall can be formed in the valley as a curved surface convex in a direction corresponding to the first partition wall. The curvature of the second partition wall can be less than that of the first partition wall. This reduces the flow resistance of the refrigerant and allows a valley to be formed in the middle of the suction passage, thereby further reducing refrigerant intake losses.

[0023] As another example, the anechoic spaces can be configured in multiples. The valleys can be formed between the multiple anechoic spaces. Thus, refrigerant whose vibration and / or noise are initially attenuated via the front anechoic spaces can pass through the valleys, thereby improving the vibration and / or noise attenuation effect while minimizing the flow resistance caused by the valleys.

[0024] For example, the plurality of silencing spaces may include: a first silencing space communicating with the muffler inlet; and a second silencing space separated from the first silencing space by the intake passage and communicating with the muffler outlet. The valley may be formed to be more adjacent to the intake and outlet of the second silencing space than the intake and outlet of the first silencing space. Thus, the valley can be located as downstream as possible from the intake passage, based on the refrigerant intake direction, thereby further reducing the flow resistance at the intake passage.

[0025] As another example, the intake passage may include: an inlet passage connected to the muffler inlet; and an outlet passage connected to the muffler outlet. The cross-sectional area of ​​the inlet passage may be configured such that at least a portion of it decreases in size as it approaches the outlet passage. This allows the intake refrigerant to move rapidly from the inlet passage to the outlet passage.

[0026] For example, the inlet passage can extend in the same direction as the muffler inlet. The outlet passage can extend in the same direction as the muffler outlet. The inlet passage and the outlet passage can be formed at right angles to each other. Thus, at least a portion of the outlet passage can be formed between the two side partition walls, thereby minimizing the path length of the outlet passage.

[0027] As another example, a filter receiving groove can be formed around the muffler outlet. A filter element that filters out foreign matter from the refrigerant passing through the intake passage can be inserted into the filter receiving groove. This prevents foreign matter mixed in with the intake refrigerant from flowing into the compression chamber of the cylinder.

[0028] As another example, the muffler inlet may include: a suction port connected to the suction passage; and a refrigerant trapping section disposed between the internal space of the housing and the suction port. The cross-sectional area of ​​the refrigerant trapping section may be larger than the cross-sectional area of ​​the suction port. Therefore, by increasing the amount of refrigerant drawn into the compression chamber through the increased suction port, the compressor performance can be improved.

[0029] As an example, the refrigerant trapping section can be recessed to a predetermined depth on the outer side of the inner circumferential surface facing the housing towards the inner side of the drive motor. The intake port can be formed through the inner circumferential surface of the refrigerant trapping section. This ensures a proper intake passage while maximizing the volume of the muffler inlet, including the refrigerant trapping section, thereby increasing the refrigerant intake capacity.

[0030] Furthermore, the cross-sectional area of ​​the refrigerant trap can be formed symmetrically with respect to the centerline passing through the center of the refrigerant trap along the axial direction. This allows for an increase in the volume of the refrigerant trap while minimizing the flow resistance of the refrigerant at the trap, thereby enabling the refrigerant to move smoothly towards the suction passage.

[0031] As another example, an oil pipe can be connected to the housing. An oil damping section with a predetermined depth can be formed on the outer surface of the intake muffler facing the oil pipe. This allows for the suppression of backflow of oil injected into the interior space of the housing via the oil pipe by widening the gap between the oil pipe and the intake muffler facing the oil pipe.

[0032] As an example, the two sides and top surface of the oil damping section can be blocked, while its bottom surface can be open. This allows oil to flow smoothly along the oil damping section to the oil storage space of the outer casing, effectively suppressing the backflow of injected oil into the oil pipe.

[0033] In addition, the inner surface of the oil damping section facing the oil pipe can be formed flat or curved.

[0034] To achieve the objective of this invention, a reciprocating compressor comprising a housing, a drive motor, a drive shaft, a piston, a cylinder, and an intake muffler can be provided. The drive motor can be disposed within the internal space of the housing. The drive shaft can be coupled to the rotor of the drive motor. The piston can be coupled to the drive shaft and reciprocate. The piston can be reciprocally inserted into the cylinder, and the cylinder, together with the piston, forms a compression chamber. The intake muffler can include a muffler inlet opening into the internal space of the housing, a muffler outlet opening into the intake side of the compression chamber, a silencing space disposed between the muffler inlet and the muffler outlet, and an intake passage connecting the muffler inlet and the muffler outlet across the silencing space. The intake passage can include an inlet passage portion connected to the muffler inlet and an outlet passage portion connected to the muffler outlet. The cross-sectional area of ​​the inlet passage portion can be formed such that at least a portion gradually decreases towards the outlet passage portion. Thus, refrigerant can be rapidly moved from the inlet passage portion to the outlet passage portion.

[0035] For example, the inlet passage can extend in the same direction as the muffler inlet. The outlet passage can extend in the same direction as the muffler outlet. The inlet passage and the outlet passage can be formed at right angles to each other. Thus, at least a portion of the outlet passage can be formed between the two side partition walls, thereby minimizing the path length of the outlet passage. Attached Figure Description

[0036] Figure 1 This is a perspective view showing the interior of the housing of the reciprocating compressor of this embodiment.

[0037] Figure 2 Viewed from the front Figure 1 A cross-sectional view of the interior of a reciprocating compressor.

[0038] Figure 3 View from the top Figure 1 A top view of the interior of a reciprocating compressor.

[0039] Figure 4 This is a perspective view of the inhalation muffler of this embodiment from the front.

[0040] Figure 5 It is Figure 4 A three-dimensional view of the intake muffler broken down and viewed from the front.

[0041] Figure 6 It is Figure 4 A three-dimensional view of the intake muffler as broken down and viewed from the back.

[0042] Figure 7 It is Figure 4 The intake muffler assembly is shown in the front view.

[0043] Figure 8 yes Figure 7 Sectional view along line “VIII-VIII”.

[0044] Figure 9 yes Figure 7 A cross-sectional view along the "IX-IX" line.

[0045] Figure 10 It is shown in Figure 4 A cross-sectional view of an embodiment in which the intake pipe is inserted into the intake of the muffler.

[0046] Figure 11 It is Figure 4 A portion of the intake muffler is broken and shown in the front view.

[0047] Figure 12 This is a front view showing a broken section of another embodiment of the muffler inlet.

[0048] Figure 13 This is a front view showing the inhalation pathway of this embodiment.

[0049] Figure 14 This is a graph illustrating the noise reduction effect of the inhalation muffler in this embodiment.

[0050] Figure 15 This is a schematic diagram illustrating another embodiment of the inhalation pathway.

[0051] Figure 16 This is a perspective view showing the oil damping section of this embodiment.

[0052] Figure 17 yes Figure 16 Sectional view along line “XVII-XVII”.

[0053] Figures 18 to 20 This is a schematic diagram showing another embodiment of the oil damping unit. Detailed Implementation

[0054] The reciprocating compressor of this invention will now be described in detail based on an embodiment shown in the accompanying drawings. As described above, the intake muffler and discharge muffler of the reciprocating compressor can be connected to each other to form a muffler assembly, or the intake muffler and discharge muffler can be set up independently. This embodiment focuses on a reciprocating compressor in which the intake muffler and discharge muffler are set up independently. However, it is not limited to this and can also be applied to a reciprocating compressor in which the intake muffler and discharge muffler are connected to each other.

[0055] Furthermore, with the piston as the center, the compression chamber side is defined as the front, and the opposite side as the rear, and will be explained accordingly. Similarly, for the muffler assembly, the side facing the outer casing is defined as the front, and the side facing away from the outer casing is defined as the rear, and will be explained accordingly.

[0056] In addition, below, the radial side of the rotation axis in the inner circumferential surface of the lower shell will be defined as the side surface, the eccentric side of the rotation axis in the inner circumferential surface of the upper shell will be defined as the top surface, and the lower end side of the rotation axis in the inner circumferential surface of the lower shell will be defined as the bottom surface, and will be explained accordingly.

[0057] Figure 1 This is a perspective view showing the interior of the housing of the reciprocating compressor of this embodiment. Figure 2 Viewed from the front Figure 1 A cross-sectional view of the interior of a reciprocating compressor. Figure 3 View from the top Figure 1 A top view of the interior of a reciprocating compressor.

[0058] Reference Figures 1 to 3 The reciprocating compressor of this embodiment may include a housing 110, an electric motor 120 disposed in the internal space 110a of the housing 110 and providing driving force, a compression unit 130 receiving driving force from the electric motor 120 and compressing refrigerant, an intake and discharge unit 140 guiding refrigerant into the compression chamber 130a and discharging the compressed refrigerant, and a vibration damping unit 150 buffering the impact generated when the housing 110 and the compressor body C collide. The housing 110 may form the appearance of the compressor, and it can be understood that the electric motor 120, the compression unit 130, the intake and discharge unit 140, and the vibration damping unit 150 form the compressor body.

[0059] The housing 110 may include a lower housing 111 and an upper housing 112. The lower housing 111 may be combined with the upper housing 112 to form a sealed internal space 110a. The internal space 110a of the housing 110 may accommodate an electric motor 120, a compressor 130, an intake / exhaust section 140, and a vibration damping section 150. However, in the case of a small reciprocating compressor, the electric motor 120, the compressor 130, the intake / exhaust section 140, and the vibration damping section 150 may be arranged adjacent to the inner circumferential surface of the housing. The housing 110 may be formed of a lightweight aluminum alloy (hereinafter simply referred to as aluminum) with high thermal conductivity.

[0060] The lower outer casing 111 can be formed into a generally hemispherical shape. A suction pipe 115 for drawing in refrigerant, a discharge pipe 116 for discharging refrigerant, and an oil pipe 117 for injecting oil can be respectively connected through and incorporated into the lower outer casing 111. These suction pipes 115, discharge pipes 116, and oil pipes 117 can be respectively incorporated into the lower outer casing 111 by insert die casting.

[0061] The upper outer shell 112 may have the same topography as the lower outer shell 111 and be approximately hemispherical. The upper outer shell 112 may be attached to the lower outer shell 111 on the upper side of the lower outer shell 111 and form the internal space 110a of the outer shell 110 described above.

[0062] Reference Figures 1 to 3 In this embodiment, the electric unit (or drive motor) 120 may include a stator 121 and a rotor 122. The stator 121 may be elastically supported in the internal space 110a of the housing 110, that is, the bottom surface of the lower housing 111, and the rotor 122 may be rotatably disposed inside the stator 121.

[0063] The stator 121 may include a stator core 1211 and a stator coil 1212.

[0064] With the stator core 1211 axially and radially spaced on the inner surface of the housing 110, the lower end of the stator core 1211 can be elastically supported on the bottom surface of the housing 110 by a support spring 123. This prevents vibrations generated during operation from being directly transmitted to the housing 110.

[0065] The stator coil 1212 can be wound inside the stator core 1211. As described above, if a voltage is applied from the outside, the stator coil 1212 will generate an electromagnetic force and perform electromagnetic interaction with the stator core 1211 and the rotor 122. As a result, the electric motor 120 generates a driving force for reciprocating the compression unit 130.

[0066] The rotor 122 may include a rotor core 1221 and a magnet 1222.

[0067] The rotor core 1221 can be formed in a generally cylindrical shape and rotatably disposed inside the stator core 1211. A drive shaft 125 can be pressed into the center of the rotor core 1221.

[0068] Magnets 1222 can be formed of permanent magnets and can be inserted into rotor core 1221 at equal intervals along the circumferential direction of rotor core 1221. Thus, rotor 122 rotates through electromagnetic interaction with stator core 1211 and stator coil 1212. While drive shaft 125 rotates together with rotor 122, the rotational force of electric motor 120 is transmitted to compression unit 130 through connecting rod 126.

[0069] Reference Figures 1 to 3 In this embodiment, the compression unit 130 may include a cylinder body 131 and a piston 132. The cylinder body 131 is elastically supported on the outer shell 110, and the piston 132 is connected to the drive shaft 125 via a connecting rod 126 and moves relative to the cylinder body 131.

[0070] The cylinder body 131 can be disposed on one axial side of the electric unit 120, such as the upper side. The cylinder body 131 can be fastened to the stator 121 by stator fastening bolts (not shown), and can be elastically supported together with the stator 121 of the electric unit 120 on the lower housing 111.

[0071] The cylinder body 131 of this embodiment may include a frame portion 1311, a fixing protrusion 1312 connected to the stator 121 of the electric unit 120, a bearing portion 1313 supporting the drive shaft 125, and a cylinder portion (cylinder barrel) 1315 forming the compression chamber 130a.

[0072] The frame portion 1311 can be formed into a flat plate shape that extends laterally, or it can be formed into a radial plate shape by reducing the weight of a portion of the edge except for the corners.

[0073] The fixing protrusion 1312 may be formed on the edge of the frame portion 1311. For example, the fixing protrusion 1312 may be formed by protruding downward from the edge of the frame portion 1311 toward the electric part 120. A fastening hole 1312a may be formed in the fixing protrusion 1312 for the stator fastening bolt (not shown) and the rear shock absorber 152 described later.

[0074] The bearing portion 1313 can be formed extending axially from the center portion of the frame portion 1311 to both sides. A bearing hole 1313a can be formed through the bearing portion 1313 axially to allow the drive shaft 125 to pass through. Thus, the drive shaft 125 can be inserted into the bearing portion 1313 and supported radially, and can also be placed at the upper end of the bearing portion 1313 and supported axially.

[0075] The cylinder section (hereinafter referred to as cylinder) 1314 can be formed radially eccentrically from one side edge of the frame section 1311. The cylinder 1314 can be radially penetrated and a piston 132 connected to the connecting rod 126 can be inserted into the inner opening end, and a valve assembly 141 forming the intake and exhaust section 140 described later can be installed at the outer opening end.

[0076] In this embodiment, the piston 132 can have an opening on the side (rear side) facing the connecting rod 126, and its opposite side (front side) facing away from the connecting rod 126 can be flattened into a closed shape. Thus, the connecting rod 126 is inserted into and rotatably coupled to the piston 132 on its rear side, and the front side of the piston 132, together with the valve assembly 141 described later, forms a compression chamber 130a inside the cylinder 1314.

[0077] Reference Figures 1 to 3The intake and exhaust section 140 of this embodiment may include a valve assembly 141, an intake muffler 142, and an exhaust muffler 143. The valve assembly 141 is a component for opening and closing the compression chamber 130a of the cylinder body 131, the intake muffler 142 is a component for reducing the intake noise of refrigerant drawn into the compression chamber 130a, and the exhaust muffler 143 is a component for reducing the exhaust noise of refrigerant discharged from the compression chamber 130a.

[0078] Valve assembly 141 may be provided with an intake valve (not shown) and an exhaust valve (not shown) and is attached to the end of cylinder body 131. The intake valve and exhaust valve may be provided separately, but they can also typically be formed together on the same valve plate. The intake valve may be configured to open and close in the direction of piston 132, and conversely, the exhaust valve may be configured to open and close in the opposite direction to the intake valve. Thus, a separate retainer may not be provided for the intake valve, while a retainer may be provided for the exhaust valve to limit the opening amount of the exhaust valve.

[0079] The intake muffler 142 may have an internal intake space, with its inlet indirectly connected to the intake pipe 115 and its outlet directly connected to the intake side of the valve assembly 141. Thus, refrigerant can be drawn into the compression chamber 130a of the cylinder 1314 via the intake muffler 142. At this time, pressure pulsations and / or intake noise generated during refrigerant intake can be canceled or attenuated by the intake muffler 142. The intake muffler 142 will be described again later along with the intake pipe 115 and the oil pipe 117.

[0080] The discharge muffler 143 may have a discharge space inside, the inlet of which is connected to the discharge side of the valve assembly 141, and the outlet of the discharge space is directly connected to the discharge pipe 116 through the annular pipe 118. Thus, a low-pressure compressor can be formed in which the refrigerant compressed in the compression chamber 130a can be discharged directly to the outside of the compressor through the annular pipe 118 and the discharge pipe 116 without passing through the internal space 110a of the outer casing 110.

[0081] Reference Figures 1 to 3 In this embodiment, the damping parts 150 can be respectively disposed on both sides of the piston 132 in the reciprocating direction, including a front damper 151 and a rear damper 152. These front dampers 151 and rear dampers 152 can be formed of elastic materials such as rubber.

[0082] The front shock absorber 151 can be configured to surround the upper side of the cylinder block 131 and the valve assembly 141; in other words, it can be configured to surround the upper front corner of the cylinder block 131 and / or the valve assembly 141. Thus, the front shock absorber 151 can effectively suppress or buffer the impact caused by the collision between the compression section 130 and the intake / exhaust section 400 and the housing 110 during compressor operation.

[0083] The rear shock absorber 152 can be disposed on the upper rear side of the cylinder block 131; in other words, it can be disposed between the two rear corners and / or the two corners of the cylinder block 131. Thus, the rear shock absorber 152 can effectively suppress or buffer the impact caused by the collision between the housing 110 and the compression section 130 when the compressor is driven.

[0084] In the attached drawing, the reference numerals 110b are for illustrative purposes only, 1421 is the muffler inlet, 1422 is the muffler outlet, 1423 is the muffler space, 1425 is the front cover, 1426 is the back cover, and 1429 is the oil vibration damping section.

[0085] The reciprocating compressor of this embodiment, as described above, operates in the following manner.

[0086] That is, if power is applied to the electric motor 120, the rotor 122 will rotate. If the rotor 122 rotates, the drive shaft 125 coupled to the rotor 122 will rotate, and at the same time, the rotational force will be transmitted to the piston 132 through the connecting rod 126. The piston 132 reciprocates relative to the cylinder 1314 in the front-rear direction through the connecting rod 126.

[0087] For example, if the piston 132 retracts in the cylinder 1314 (intake stroke), the volume of the compression chamber 130a will increase. As a result, the refrigerant that fills the internal space 110a of the housing 110 via the intake pipe 115 will be drawn into the compression chamber 130a via the intake space of the intake muffler 142 and the intake valve of the valve assembly 141.

[0088] Conversely, if the piston 132 advances in the cylinder 1314 (discharge stroke), the volume of the compression chamber 130a decreases. As a result, the refrigerant filling the compression chamber 130a is compressed and discharged through the discharge valve of the valve assembly 141 to the discharge space of the discharge muffler 143. This refrigerant is then discharged into the refrigeration cycle through the annular pipe 118 and the discharge pipe 116, and the aforementioned series of processes is repeated.

[0089] In this case, forming the suction inlet of the suction muffler 142 as large as possible can help increase the amount of refrigerant drawn in. However, when the suction inlet is formed to directly penetrate one side of the suction muffler 142, the size of the suction inlet is limited due to the internal flow path of the suction muffler 142. In the case of the suction muffler 142 applied to a small reciprocating compressor, this makes it more difficult to enlarge the suction inlet.

[0090] Furthermore, forming the internal volume of the suction muffler 142 as large as possible is beneficial for attenuating vibration and / or noise. However, in the case of small reciprocating compressors with a small gap between the inner circumferential surface of the housing 110 and the outer circumferential surface of the compressor body C, it is difficult to ensure sufficient space for the suction muffler 142 between the inner circumferential surface of the housing 110 and the outer circumferential surface of the compressor body C. Considering this, instead of reducing the internal volume of the suction muffler 142, the internal flow path of the suction muffler 142 can be formed in a complex manner. However, forming a complex internal flow path for the suction muffler 142 not only makes the manufacture of the suction muffler 142 more difficult and increases its manufacturing cost, but also increases the flow resistance at the suction muffler 142, and causes the intake refrigerant to overheat due to the delayed intake of the refrigerant, resulting in intake losses.

[0091] Furthermore, as the internal volume of the intake muffler 142 increases, it gets closer to the inner circumferential surface of the outer casing 110. In this case, the oil pipe 117 cannot be adequately separated from the intake muffler 142. Therefore, when oil is injected, the oil will collide with the intake muffler and flow back into the oil pipe 117, making it impossible to inject oil smoothly.

[0092] Therefore, in this embodiment, similar to the refrigerant trapping section 1421a, a refrigerant trapping section 1421a wider than the suction port 1421b can be provided on the front side of the suction port, thereby increasing the amount of refrigerant drawn in without increasing the size of the suction port 1421b. This allows for improved compressor performance by increasing the suction volume of the reciprocating compressor.

[0093] Furthermore, in this embodiment, the internal flow path of the intake muffler 142 can be simplified by appropriately forming the internal flow path, while simultaneously maximizing the internal volume of the intake muffler 142. This allows the intake muffler 142 to be applied not only to medium and large reciprocating compressors but also to small reciprocating compressors, thereby facilitating manufacturing, reducing manufacturing costs, while simultaneously increasing the internal volume and improving vibration and / or noise attenuation.

[0094] In addition, in this embodiment, the gap between the intake muffler 142 and the oil pipe 117 can be sufficiently separated, so that even if the oil injected into the oil storage space 110b of the housing 110 via the oil pipe 117 collides with the intake muffler 142, the backflow of the oil via the oil pipe 117 can be suppressed.

[0095] Figure 4 This is a perspective view of the intake muffler of this embodiment, viewed from the front. Figure 5 It is Figure 4 A three-dimensional view of the intake muffler broken down and viewed from the front. Figure 6 It is Figure 4 A three-dimensional view of the intake muffler disassembled and viewed from the back. Figure 7 It is Figure 4 The intake muffler assembly is shown in the front view. Figure 8 yes Figure 7 Sectional view along line "VIII-VIII", Figure 9 yes Figure 7 A cross-sectional view along the "IX-IX" line. Figure 10 This is a cross-sectional view showing an embodiment where the suction tube is inserted into the muffler inlet.

[0096] Reference Figures 4 to 9 In this embodiment, the intake muffler 142 can be divided into a muffler body 142a and a muffler fixing part 142b based on its external shape. The muffler body 142a is the part that reduces the vibration and / or noise of the intake refrigerant, and the muffler fixing part 142b is the part that connects the intake muffler 142 to the compression part.

[0097] The muffler body 142a and the muffler fixing part 142b can be formed as a single unit. For example, the muffler fixing part 142b can extend from the upper center of the muffler body 142a toward the suction valve part of the valve assembly 141. Thus, the muffler body 142a can be fixed to the compressor body C by the muffler fixing part 142b.

[0098] In this configuration, a muffler inlet 1421, a muffler space 1423, and a suction passage 1424 (described later) can be formed inside the muffler body 142a, and a muffler outlet 1422 (described later) can be formed inside the muffler fixing portion 142b. Thus, refrigerant flowing into the internal space 110a of the housing 110 can sequentially pass through the muffler body 142a and the muffler fixing portion 142b and be drawn into the compression chamber.

[0099] Additionally, the muffler body 142a may form a sound-absorbing space 1423, which will be described later, inside it, and it may typically be formed with a plurality of covers 1425, 1426. For example, the muffler body 142a may be formed with a first cover (hereinafter, front cover) 1425 facing the inner peripheral surface of the housing 110 and a second cover (hereinafter, back cover) 1426 facing the outer peripheral surface of the compressor body C.

[0100] Reference Figures 4 to 6The front cover 1425 and the back cover 1426 can be formed along the inner circumferential surface of the outer casing 110. For example, the outer side of the front cover 1425 (the front side facing the inner circumferential surface of the outer casing) can be formed into an arc shape along the inner circumferential surface of the outer casing 110 when projected axially, and the outer side of the back cover 1426 (the rear side facing the compressor body) can be formed into a generally wedge-shaped cross-section shape along the outer circumferential surface of the compressor body (e.g., the stator core) C when projected axially. As a result, the muffler body 142a can extend relatively long on both sides in the circumferential direction with the front end face of the cylinder 1314 as the center, thereby forming a sound-absorbing space 1423 at both ends of the muffler body 142a that is relatively wider than the central part of the muffler body 142a. As a result, the sound-absorbing space 1423 of the intake muffler 142 can be enlarged as a whole.

[0101] Additionally, sealing protrusions 1425a and 1426a may be formed along the edge on at least one side of the inner surface of the front cover 1425 (the rear side facing the back cover) and the inner surface of the back cover 1426 (the front side facing the front cover). For example, the sealing protrusions 1425a and 1426a may be formed on the inner surfaces of the front cover 1425 and the back cover 1426 respectively, corresponding to each other, or they may be formed only on the inner surface of the front cover 1425 or only on the inner surface of the back cover 1426. In this case, the front end faces of the sealing protrusions 1425a and 1426a may engage with the inner surfaces of the covers 1426 and 1425 facing them respectively to form a protrusion and a groove for a concave-convex engagement; or, a protrusion and a groove may be formed on the front end faces of the sealing protrusions 1425a and 1426a facing each other to engage with each other for a concave-convex engagement. This embodiment shows an example in which sealing protrusions 1425a and 1426a are formed on the inner side of the front cover 1425 and the inner side of the back cover 1426 in a corresponding manner. Hereinafter, the front sealing protrusion 1425a of the front cover 1425 and the back sealing protrusion 1426a of the back cover 1426 will be collectively referred to as sealing protrusions and will be described.

[0102] Furthermore, partition walls 1425b and 1426b extending from the sealing protrusions 1425a and 1426a may be formed on at least one side of the inner surface of the front cover 1425 and the inner surface of the back cover 1426. The internal space of the muffler body 142a can be formed by the partition walls 1425b and 1426b to create at least one or more sound-absorbing spaces 1423. For example, the partition walls 1425b and 1426b may be formed on the inner surface of the front cover 1425 and the inner surface of the back cover 1426 respectively, or they may be formed only on the inner surface of the front cover 1425 or only on the inner surface of the back cover 1426. In this case, protrusions and grooves may be formed on the front end faces and inner surfaces facing them, or on the front end faces of the partition walls 1425b and 1426b facing each other, respectively, to mesh and engage with each other. This embodiment shows an example in which partition walls 1425b and 1426b are formed on the inner side of the front cover 1425 and the inner side of the back cover 1426 in a corresponding manner. As a result, the silencing space 1423 and the intake passage 1424, which will be described later, can be easily formed inside the muffler body 142a.

[0103] Reference Figures 5 to 8 In this embodiment, the intake muffler 142 can be divided into a muffler inlet 1421, a muffler outlet 1422, a muffler space 1423, and an intake passage 1424 based on its internal shape. The muffler inlet 1421 is the part that guides the intake refrigerant into the muffler space 1423. The muffler outlet 1422 is the part that guides the refrigerant through the muffler space 1423 into the cylinder 1314 of the compressor section 130. The muffler space 1423 is the part that attenuates the vibration and / or noise of the intake refrigerant. The intake passage 1424 is the part that guides the intake refrigerant through the muffler inlet 1421 into the muffler space 1423 and simultaneously guides the refrigerant through the muffler space 1423 to the muffler outlet 1422. Therefore, refrigerant can be drawn from the muffler inlet 1421 to the silencing space 1423 via the intake passage 1424, and after vibration and / or noise are attenuated, it can be drawn into the compression chamber 130a of the cylinder 1314 via the muffler outlet 1422. Conversely, when refrigerant is drawn in, noise generated in the intake valve section of the valve assembly 141, etc., can be moved in reverse order to the various parts of the muffler body 142a described above and attenuated simultaneously. Hereinafter, the description will be based on the path of refrigerant intake.

[0104] Reference Figures 7 to 9In this embodiment, the muffler inlet 1421 can be formed as a cover penetrating at least one side of the front cover 1425 and the back cover 1426 forming the muffler body 142a. For example, the muffler inlet 1421 can be formed to penetrate the front cover 1425, the back cover 1426, or both. In this embodiment, the muffler inlet 1421 can be formed as a tunnel shape penetrating the lower half of the front cover 1425 and deeply recessed into the inner side of the back cover 1426. This increases the volume of the muffler inlet 1421, allowing refrigerant drawn into the internal space 110a of the housing 110 to move rapidly into the muffler 142, thus increasing the refrigerant intake.

[0105] Specifically, the muffler inlet 1421 may include a refrigerant trapping section 1421a and a suction port 1421b. The refrigerant trapping section 1421a is the part that traps the refrigerant drawn into the internal space 110a of the housing 110 and guides it to the suction port 1421b side. The suction port 1421b is the part that guides the refrigerant trapped in the refrigerant trapping section 1421a into the suction passage 1424.

[0106] For example, the refrigerant trapping section 1421a can be formed such that the front of the muffler body section 142a facing the inner side of the lower outer casing 111 is recessed to a predetermined depth towards the back of the compressor body C. In this case, the front cover 1425 forming the front of the refrigerant trapping section 1421a can be penetrated and opened, the back cover 1426 forming the back of the refrigerant trapping section 1421a can be sealed, and the front cover 1425 and the back cover 1426 forming the inner circumferential surface between the front and back of the refrigerant trapping section 1421a can be formed as a whole in a sealed shape, or formed as a part of which is open and the suction port 1421b described later is formed in said part. Thus, the refrigerant drawn into the internal space 110a of the outer casing 110 passes through the front of the opening of the muffler inlet 1421, that is, the front of the refrigerant trapping section 1421a, and is trapped in the refrigerant trapping section 1421a, and then moves into the interior of the muffler body 142a through the suction port 1421b.

[0107] In this case, the cross-sectional area of ​​the refrigerant trapping section 1421a can be formed to be greater than or equal to the cross-sectional area of ​​the suction port 1421b. Preferably, the cross-sectional area of ​​the refrigerant trapping section 1421a can be formed to be greater than the cross-sectional area of ​​the suction port (or suction passage) 1421b. As a result, the refrigerant drawn into the internal space 110a of the housing 110 can move smoothly towards the wider muffler inlet 1421 and then move to the suction passage 1424 side, thereby correspondingly increasing the suction volume.

[0108] Although not shown in the figure, as described above, the muffler inlet 1421 can also be formed as a recess in the side of the muffler body 142a at a predetermined depth. In this case, the refrigerant trapping section 1421a can be recessed in the sealing protrusions 1425a and 1426a forming the side of the muffler body 142a at a predetermined depth, and the suction port 1421b can penetrate through the back of the refrigerant trapping section 1421a and communicate with the suction passage 1424. In this case, the cross-sectional area of ​​the refrigerant trapping section 1421a can also be formed to be larger than the cross-sectional area of ​​the suction port (or suction passage) 1421b.

[0109] The refrigerant trapping section 1421a can be formed such that its cross-sectional area is larger than that of the suction pipe 115. As a result, the refrigerant trapping section 1421a can be formed as wide as possible, and the refrigerant drawn into the internal space 110a of the outer casing 110 can flow rapidly into the interior of the suction muffler 142 through the refrigerant trapping section 1421a, thereby increasing the refrigerant intake.

[0110] In this case, the refrigerant trap 1421a can be separated from the end of the suction pipe 115. For example, as Figure 9 As shown, the end of the suction pipe 115 can communicate with the internal space 110a of the housing 110 outside the refrigerant collection section 1421a. As a result, a portion of the refrigerant flowing into the internal space 110a of the housing 110 can diffuse into the internal space 110a of the housing 110, thereby enabling the heat generated in the internal space 110a of the housing 110 to be dissipated rapidly.

[0111] In this case, the refrigerant trapping section 1421a can be formed wider than the suction pipe 115 at the end facing the suction pipe 115. In other words, the refrigerant trapping section 1421a can be formed with a cross-sectional area wider than the suction pipe 115 at a position where at least a portion overlaps with the suction pipe 115 in the radial direction. As a result, the refrigerant drawn into the internal space 110a of the housing 110 via the suction pipe 115 can be trapped in the refrigerant trapping section 1421a and rapidly drawn into the compression chamber 130a, thereby increasing the refrigerant intake.

[0112] On the other hand, the refrigerant trapping section 1421a may also overlap with the end of the suction pipe 115. For example, as Figure 10As shown, the end of the suction pipe 115 can also be inserted into the refrigerant trapping section 1421a at a predetermined depth and communicate with the internal space 110a of the housing 110. In other words, as described above, the cross-sectional area (e.g., inner diameter) of the refrigerant trapping section 1421a can be formed to be larger than the cross-sectional area (e.g., outer diameter) of the suction pipe 115, and a gap for refrigerant movement can be formed between the inner circumferential surface of the refrigerant trapping section 1421a and the outer circumferential surface of the suction pipe 115. Thus, most of the refrigerant drawn into the internal space 110a of the housing 110 can flow directly into the refrigerant trapping section 1421a without passing through the internal space 110a of the housing 110, while further increasing the refrigerant intake to the compression chamber 130a. In this case, a portion of the refrigerant flowing into the refrigerant trapping section 1421a can flow out into the internal space 110a of the housing 110, thereby dissipating heat from the internal space 110a of the housing 110.

[0113] Reference Figures 4 to 7 A first oil-blocking portion 1421d may be formed around the periphery of the muffler inlet 1421 of the refrigerant collection section 1421a. For example, the first oil-blocking portion 1421d may be formed to surround the upper periphery of the muffler inlet 1421. As a result, oil that has splashed in the internal space 110a of the housing 110 can be effectively prevented from flowing into the interior of the intake muffler 142 through the muffler inlet 1421.

[0114] In this case, the first oil-blocking portion 1421d can be formed in a dome shape, so that the lower side of the muffler inlet 1421 is open, and the height of the first oil-blocking portion 1421d can be formed to be lower than or equal to the height of the first volume portion 1423c described later. Thus, even if the compressor is miniaturized, it is possible to suppress the collision between a part of the muffler body portion 142a and the inner peripheral surface of the housing 110.

[0115] In addition, the refrigerant trapping section 1421a can be formed into a circular cross-section shape when projected from the front, or it can be formed into an angular shape with curved edges, such as a quadrilateral or a triangle. Figure 11 This is a front view showing a broken section of the intake muffler. Figure 12 This is a front view showing a broken section of another embodiment of the muffler inlet.

[0116] like Figure 11As shown, the refrigerant trapping section 1421a can be formed symmetrically with respect to the centerline (first centerline) CL1 passing through its center along the axial direction. For example, the refrigerant trapping section 1421a can be formed into a quadrilateral cross-section shape with its inner circumferential surface exhibiting angular curves when projected from the front. In other words, the cross-sectional area of ​​the refrigerant trapping section 1421a can be formed symmetrically with respect to the first centerline CL1. This allows for an increase in the volume of the refrigerant trapping section 1421a while minimizing the flow resistance of the refrigerant at this section, thereby enabling the refrigerant to move smoothly toward the suction passage 1424.

[0117] like Figure 12 As shown, the refrigerant trapping section 1421a can also be formed asymmetrically with respect to the first centerline CL1. For example, the refrigerant trapping section 1421a can be formed such that a portion of its inner circumferential surface is inclined when projected from the front. In other words, the cross-sectional area of ​​the refrigerant trapping section 1421a can be formed asymmetrically with respect to the first centerline CL1. Thus, while forming an intake guide surface 1421c with an enlarged cross-sectional area closer to the intake port 1421b, it also allows the refrigerant to move more smoothly to the intake passage 1424 side.

[0118] Although not shown, the refrigerant trap 1421a may also be formed as a suction guide hole. For example, the suction guide hole may also be formed through the front and back sides of the suction muffler 142. In this case, the suction guide hole may also be formed with the same shape and / or standard as the refrigerant trap 1421a described above.

[0119] Reference Figures 4 to 9 As described above, the suction port 1421b can be formed through the inner peripheral surface of the refrigerant trapping section 1421a toward the inlet passage section 1424a (described later). Thus, refrigerant flowing into the interior of the refrigerant trapping section 1421a can move along the inner peripheral surface of the refrigerant trapping section 1421a, bend through the suction port 1421b, and flow into the suction passage 1424 (described later). This ensures the suction passage 1424 is secure while simultaneously forming the muffler inlet 1421, including the refrigerant trapping section 1421a, as wide as possible, thereby increasing the refrigerant intake volume.

[0120] For example, the intake port 1421b can be formed through the lower half of the refrigerant trapping section 1421a in a circumferential direction. Thus, the muffler inlet 1421 can be formed as close as possible to the edge of the intake muffler 142, while simplifying the structure of the silencing space 1423 and ensuring the volume of the silencing space 1423 as wide as possible, thereby improving the attenuation effect of vibration and / or noise.

[0121] As described above, the suction port 1421b can be narrower than the refrigerant trapping section 1421a and the inlet passage section 1424a. For example, the cross-sectional area of ​​the suction port 1421b can be formed to be approximately half or less than the maximum cross-sectional area of ​​the refrigerant trapping section 1421a and / or the inlet passage section 1424a. This increases the refrigerant flow velocity at the suction port 1421b, allowing the refrigerant trapped in the refrigerant trapping section 1421a to move rapidly to the inlet passage section 1424a side via the narrower suction port 1421b.

[0122] Furthermore, the suction port 1421b can be formed at the lowermost end of the suction passage 1424 connected to the suction port 1421b; in other words, it can be formed on the upper side above the end of the inlet passage 1424a. This reduces suction loss by suppressing the backflow of oil from the inlet passage 1424a to the suction port 1421b.

[0123] Reference Figure 13 As described above, the muffler outlet 1422 of this embodiment can be formed to penetrate the interior of the muffler fixing portion 142b extending from the muffler body portion 142a.

[0124] In this case, a filter member 1422b can be provided at the muffler outlet 1422. For example, a filter receiving groove 1422a can be formed at the muffler outlet 1422, which is connected to the outlet passage portion 1424b of the intake passage 1424, and a filter member 1422b, such as a mesh screen, can be inserted into the filter receiving groove 1422a. As a result, foreign matter mixed with the intake refrigerant can be trapped by the filter member 1422b, thereby preventing the foreign matter from flowing into the compression chamber 130a of the cylinder 1314.

[0125] Although not shown in the figure, the filter component 1422b may also be disposed inside the silencer outlet 1422 or on the outlet side of the silencer outlet 1422 facing the valve assembly 141.

[0126] Reference Figures 4 to 13 In this embodiment, the anechoic space 1423, formed between the muffler inlet 1421 and the muffler outlet 1422, can be formed by a single anechoic space 1423 or by a plurality of anechoic spaces 1423. For example, if the anechoic space 1423 is formed by a single space, one anechoic space 1423 can be connected in the middle of the intake passage 1424 described later. Conversely, if there are a plurality of anechoic spaces 1423, these plurality of anechoic spaces 1423 can be connected in series with each other, or they can be connected in parallel through the intake passage 1424 described later. This embodiment shows an example of a plurality of anechoic spaces 1423 connected in parallel through the intake passage 1424 described later.

[0127] Specifically, the anechoic space 1423 can be formed inside the muffler body 142a, as described above, between the inner surfaces of the front cover 1425 and / or the inner surfaces of the back cover 1426 facing each other. For example, the anechoic space 1423 can be formed as a plurality of anechoic spaces 1423 by protruding partition walls 1425b and 1426b on the front cover 1425 and the back cover 1426, respectively. These plurality of anechoic spaces 1423 may pass through the middle of the partition walls 1425b and 1426b between the two sides of the partition walls 1425b and 1426b and communicate with the intake passage 1424 and / or the anechoic space 1423 described later. One end of the partition walls 1425b and 1426b may also be separated from the inner peripheral surface of the respective sealing protrusions 1425a and 1426a extending along the edge of the front cover 1425 and / or the back cover 1426 and communicate with the intake passage 1424 and / or another anechoic space 1423 described later, or may be connected by combining the former and the latter. This embodiment shows an example in which the sealing protrusions 1425a and 1426a of the cover 1425 and 1426, which are separated from the end of the partition walls 1425b and 1426b and communicate with the intake passage 1424 and / or another anechoic space 1423 described later, while passing through the middle of a portion of the partition walls 1425b and 1426b.

[0128] For example, a plurality of silencing spaces 1423 can be formed by two silencing spaces 1423, and the two silencing spaces 1423 can be connected in parallel through the suction flow path 1422d described later. In other words, in this embodiment, the first silencing space 1423a can be connected to the inlet passage 1424a of the suction passage 1424 described later through the first inlet / outlet 1424c described later, and the second silencing space 1423b can be connected to the outlet passage 1424b of the suction passage 1424 described later through the second inlet / outlet 1424d described later. Thus, the intake refrigerant flowing into the interior of the intake silencer 142 through the silencer inlet 1421 can attenuate vibration and / or noise while passing through the respective silencing spaces 1423a, 1423b and the suction passage 1424.

[0129] Refer again Figure 13 The first anechoic space 1423a can be separated from the intake passage 1424 by the first partition wall 1427a, which will be described later. For example, the first anechoic space 1423a can be formed in the space between the inner peripheral surfaces of the sealing protrusions 1425a and 1426a and the inner surface of the first partition wall 1427a, which will be described later. Thus, the first anechoic space 1423a can be formed on one side of the intake passage 1424 in the circumferential direction.

[0130] Additionally, a first volume portion 1423c, forming part of the first anechoic space 1423a, can be formed on its front side. For example, the first volume portion 1423c can be formed protruding from the front side of the front cover 1425 toward the inner peripheral surface of the outer casing 110. Thus, the internal volume of the first anechoic space 1423a can be increased by the internal volume of the first volume portion 1423c, thereby further effectively attenuating the vibration and / or noise of the intake refrigerant.

[0131] In this case, such as Figures 4 to 7 As shown, a first oil drain hole 1428a communicating with the first silencing space 1423a may be formed on the lower side of the first volume portion 1423c. For example, the first oil drain hole 1428a may be formed to communicate with the inlet passage portion 1424a of the suction passage 1424 (described later) on the lower side below the first volume portion 1423c. Thus, when the compressor is running, before the oil flowing down from the front of the front cover 1425 flows into the first oil drain hole 1428a, it can fall from the lower edge of the first volume portion 1423c into the oil storage space 110b of the outer casing 110 and be recovered. Thus, it is possible to prevent oil from flowing from the outside of the suction muffler 142 through the inside, i.e., the suction passage 1424, into the first silencing space 1423a via the first oil drain hole 1428a.

[0132] The first oil drain hole 1428a can be formed as a side end adjacent to the muffler inlet 1421 in the inlet passage portion 1424a of the suction passage 1424. For example, the bottom-side sealing protrusions 1425a and 1426a of the inlet passage portion 1424a formed on the lower side of the first silencing space 1423a can be formed to slope downwards towards the muffler inlet 1421. The first oil drain hole 1428a can be formed to communicate with a relatively low portion of the inlet passage portion 1424a of the suction passage 1424, in other words, to communicate with the side inlet passage portion 1424a adjacent to the muffler inlet 1421. Thus, the oil filtered by the first silencing space 1423a and / or the suction passage 1424 will not remain in the inlet passage portion 1424a of the suction passage 1424, but can be smoothly recovered to the oil storage space 110b of the housing 110 via the first oil drain hole 1428a.

[0133] In this case, a second oil-blocking portion 1428b can be formed around the first oil drain hole 1428a. For example, the second oil-blocking portion 1428b can be formed to be disposed between the lower end of the first volume portion 1423c and the first oil drain hole 1428a and to surround the upper half of the first oil drain hole 1428a. This further effectively prevents oil from flowing into the first silencing space 1423a through the first oil drain hole 1428a.

[0134] Here, the bottom surface of the second oil-blocking portion 1428b facing the outer casing 110 can be formed into an open dome shape, and the height of the second oil-blocking portion 1428b can be formed to be lower than or equal to the height of the first volume portion 1423c. Thus, even if the compressor is miniaturized, it is possible to suppress the collision between a part of the muffler body portion 142a and the inner peripheral surface of the outer casing 110a.

[0135] Refer again Figure 11 and Figure 13 The second anechoic space 1423b can be separated from the intake passage 1424 via the second partition wall 1427b, which will be described later. For example, the second anechoic space 1423b can be formed as the space between the inner peripheral surfaces of the sealing protrusions 1425a and 1426a and the inner surface of the second partition wall 1427b, which will be described later. Thus, the second anechoic space 1423b can be formed on the other side of the circumferential direction of the intake passage 1424.

[0136] Furthermore, the second anechoic space 1423b may have a second volume portion 1423d forming part of the second anechoic space 1423b on its front side. For example, the second volume portion 1423d may be formed protruding from the other side of the front of the front cover 1425 toward the inner peripheral surface of the outer casing 110. As a result, the internal volume of the second anechoic space 1423b can be increased by the internal volume of the second volume portion 1423d, thereby further effectively attenuating the vibration and / or noise of the intake refrigerant.

[0137] In this case, such as Figures 4 to 7 As shown, a second oil drain hole 1428c can be formed in the lower half of the second anechoic space 1423b. For example, the second oil drain hole 1428c can be formed to penetrate the bottom surface of the front cover 1425 facing the bottom surface of the housing 110; in other words, it penetrates and connects to the bottom surface of the second volume portion 1423d. Therefore, when the compressor is running, the oil flowing down from the front of the front cover 1425 can fall off at the lower corner of the second volume portion 1423d and be collected in the oil storage space 110b of the housing 110 before flowing into the second oil drain hole 1428c. This prevents oil from flowing from the outside of the suction muffler 142 into the inside, i.e., into the second anechoic space 1423b, via the second oil drain hole 1428c.

[0138] The second oil drain hole 1428c can be formed at the side end of the second silencing space 1423b adjacent to the outlet passage portion 1424b of the suction passage 1424 (described later). For example, the lower end of the muffler body portion 142a (the bottom surface of the second silencing space) can be inclined such that the end is closer to the muffler inlet 1421 along the circumferential direction from the muffler outlet 1422 and further away from the bottom surface of the housing 110. Therefore, the second oil drain hole 1428c can be formed at a relatively low height portion of the second volume portion (i.e., the second silencing space) 1423d, in other words, it is formed to communicate with the side of the second volume portion 1423d adjacent to the muffler outlet 1422. Thus, the oil filtered in the second silencing space 1423b will not remain in the second silencing space 1423b, but can be smoothly recovered to the oil storage space 110a of the housing 110 via the second oil drain hole 1428c.

[0139] In this case, a third oil-blocking portion 1428d surrounding the periphery of the second oil drain hole 1428c can be formed on the bottom surface of the front cover 1425. This further effectively prevents oil from flowing into the second silencing space 1423b via the second oil drain hole 1428c.

[0140] The bottom surface of the third oil-blocking portion 1428d facing the bottom surface of the outer casing 110 can be formed into an open dome shape, and the height of the third oil-blocking portion 1428d can be formed to be lower than or equal to the lowest point of the front cover 1425, based on the bottom surface of the outer casing 110. This suppresses interference with peripheral components including the annular tube 118.

[0141] Refer again Figure 13 In this embodiment, the intake passage 1424 can be inside the intake muffler 142. In other words, it can be formed as a partition wall 1427a, 1427b between the front cover 1425 and the back cover 1426 that form the muffler body 142a, or it can be formed to penetrate the interior of the front cover 1425 and / or the interior of the back cover 1426. This embodiment shows the former case, that is, an example in which the intake passage 1424 is formed as a partition wall 1427a, 1427b between the front cover 1425 and the back cover 1426.

[0142] For example, a front partition wall 1425b protruding towards the inner peripheral surface of the back cover 1426 at a predetermined height can be formed on the inner peripheral surface of the front cover 1425, and a back partition wall 1426b protruding towards the inner peripheral surface of the front cover 1425 at a predetermined height and engaging with the front partition wall 1425b can be formed on the inner peripheral surface of the back cover 1426. Thus, the internal space of the intake muffler 142 can be divided into a plurality of spaces by the front partition wall 1425b and the back partition wall 1426b.

[0143] In this case, the front partition wall 1425b can be formed by a first front partition wall 1425b and a second front partition wall 1425b separated by a circumferential direction, and the back partition wall 1426b can be formed by a first back partition wall 1426b1 and a second back partition wall 1426b2 separated by a circumferential direction and respectively corresponding to the first front partition wall 1425b1 and the second front partition wall 1425b2. Hereinafter, the first front partition wall 1425b1 and the first back partition wall 1426b1 will be combined and defined as the first partition wall 1427a, and the second front partition wall 1425b2 and the second back partition wall 1426b2 will be combined and defined as the second partition wall 1427b, and will be described.

[0144] The first partition wall 1427a and the second partition wall 1427b can be separated by a predetermined interval along the circumferential direction. In other words, the first partition wall 1427a can be formed on one side of the circumferential direction adjacent to the muffler inlet 1421, and the second partition wall 1427b can be formed on the other side of the circumferential direction relatively far from the muffler inlet 1421. Thus, an intake passage 1424 connecting the muffler inlet 1421 and the muffler outlet 1422 can be formed between the front cover 1425 and the back cover 1426 through the first partition wall 1427a and the second partition wall 1427b.

[0145] Specifically, as described above, at least a portion of the inhalation passage 1424 may be formed between the first partition wall 1427a and the second partition wall 1427b, and may include an inlet passage 1424a, an outlet passage 1424b, a first inlet / outlet 1424c, a second inlet / outlet 1424d, and a valley 1424e. The inlet passage 1424a is adjacent to and connected to the muffler inlet 1421, the outlet passage 1424b is adjacent to and connected to the muffler outlet 1422, the first inlet / outlet 1424c is the part in the middle of the inlet passage 1424a that communicates with the first anechoic space 1423a, the second inlet / outlet 1424d is the part in the middle of the outlet passage 1424b that communicates with the second anechoic space 1423b, and the valley 1424e is the part located between the first inlet / outlet 1424c and the second inlet / outlet 1424d that improves the attenuation effect of vibration and / or noise.

[0146] In this embodiment, the inlet passage portion 1424a can be formed extending circumferentially near the lower end of the first partition wall 1427a surrounding the muffler inlet 1421 and the muffler body portion 142a. For example, the inlet passage portion 1424a can be formed between the first partition wall 1427a and the bottom-side sealing protrusions 1425a and 1426a of the muffler body portion 142a facing the first partition wall 1427a axially. Thus, the inlet passage portion 1424a can be formed by a single partition wall 1427a, and the manufacturing process of the inlet passage portion 1424a can be simplified.

[0147] As described above, one end of the inlet passage 1424a communicates with the inner circumferential surface of the refrigerant trapping section 1421a through a circumferentially penetrating suction port 1421b in the lower half of the muffler inlet 1421. Thus, the refrigerant flowing into the interior of the muffler inlet 1421 can bend and move towards the inlet passage 1424a within the muffler inlet 1421.

[0148] In this case, as described above, the inlet passage 1424a can be formed to be smaller than the refrigerant trapping section 1421a and larger than the suction port 1421b. For example, the inlet side cross-sectional area of ​​the inlet passage 1424a can be formed to be smaller than the cross-sectional area of ​​the refrigerant trapping section 1421a and larger than the cross-sectional area of ​​the suction port 1421b. Thus, while the internal volume of the first anechoic space 1423a connected to the inlet passage 1424a can be formed as wide as possible, the volume of the muffler inlet 1421 can be formed as large as possible, thereby increasing the intake volume to the muffler body 142a.

[0149] Furthermore, the inlet passage 1424a can be formed to gradually narrow from the end that contacts the muffler inlet 1421 towards the end that contacts the outlet passage 1424b. For example, in the inlet passage 1424a, as described above, as the bottom-side sealing protrusions 1425a and 1426a of the muffler body 142a, which forms the inlet passage 1424a together with the first partition wall 1427a, are formed to slope upwards towards the muffler outlet 1422, the cross-sectional area of ​​the inlet passage 1424a can be formed to be narrower towards the outlet passage 1424b. As a result, the refrigerant can be rapidly moved from the inlet passage 1424a to the outlet passage 1424b.

[0150] In this embodiment, the outlet passage 1424b can be formed by extending substantially axially from the end of the inlet passage 1424a toward the muffler outlet 1422. For example, the first partition wall 1427a forming one side of the outlet passage 1424b can be bent at approximately a right angle at the end of the inlet passage 1424a and extend axially toward the periphery of the muffler outlet 1422, while the second partition wall 1427b forming the other side of the outlet passage 1424b can extend axially toward the muffler outlet 1422 from the bottom-side sealing protrusions 1425a and 1426a. Thus, at least a portion of the outlet passage 1424b can be formed between the first partition wall 1427a and the second partition wall 1427b, thereby minimizing the path length of the outlet passage 1424b.

[0151] In this case, one end of the first partition wall 1427a forming one side of the outlet passage 1424b can extend from the inner peripheral surface of the top surface-side sealing protrusions 1425a and 1426a that form the upper side of the muffler body 142a around the muffler outlet 1422. One end of the second partition wall 1427b forming the other side of the outlet passage 1424b can be separated from the inner peripheral surface of the top surface-side sealing protrusions 1425a and 1426a described above, forming the second inlet / outlet 1424d described later. Thus, the first anechoic space 1423a and the second anechoic space 1423b can be separated by the first partition wall 1427a forming the outlet passage 1424b.

[0152] In this embodiment, the first inlet / outlet portion 1424c can be formed in the middle of the inlet passage portion 1424a or at the end of the inlet passage portion 1424a connected to the outlet passage portion 1424b. For example, the first inlet / outlet portion 1424c can be formed to cut through the middle portion of the first partition wall 1427a, or it can be formed to cut off the space between the inlet passage portion 1424a and the outlet passage portion 1424b. In the former case, the intake refrigerant can be moved quickly to the first anechoic space 1423a, and in the latter case, the path length of the inlet passage portion 1424a can be shortened while allowing most of the intake refrigerant to pass through the first anechoic space 1423a. This embodiment shows the latter case, that is, an example where the first inlet / outlet portion 1424c is formed at the end of the inlet passage portion 1424a.

[0153] In this embodiment, the second inlet / outlet portion 1424d can be formed in the middle of the outlet passage portion 1424b, or it can be formed at the end of the outlet passage portion 1424b connected to the muffler outlet 1422. For example, the second inlet / outlet portion 1424d can be formed to cut through the middle portion of the second partition wall 1427b, or it can be formed to cut off the space between the second partition wall 1427b and the muffler outlet 1422. In the former case, the drawn-in refrigerant can move rapidly to the second anechoic space 1423b, and in the latter case, the flow resistance between the second anechoic space 1423b and the muffler outlet 1422 can be reduced and the amount of refrigerant drawn in can be increased. This embodiment shows the latter case, that is, an example in which the second inlet / outlet portion 1424d is formed at the end of the outlet passage portion 1424d.

[0154] Reference Figure 5 , Figure 6 as well as Figure 13 In this embodiment, the valley portion 1424e can protrude from the middle of the suction passage 1424 described above in a direction intersecting the length direction (or travel direction) of the suction passage 1424. Thus, the valley portion 1424e can form a neck portion, thereby effectively attenuating vibrations and / or noise generated during refrigerant intake.

[0155] For example, the valley 13424e can be formed in the middle of the inlet passage 1424a, or in the middle of the outlet passage 1424b, or between the inlet passage 1424a and the outlet passage 1424b. In other words, the valley 1424e, based on the refrigerant's suction path (or the direction of travel of the suction passage), can be formed on the upstream side above the first inlet / outlet 1424c, or on the downstream side below the second inlet / outlet 1424d, or between the first inlet / outlet 1424c and the second inlet / outlet 1424d. This embodiment shows an example where the valley 1424e is formed between the first inlet / outlet 1424c and the second inlet / outlet 1424d. Thus, refrigerant whose vibration and / or noise are initially attenuated while passing through the first anechoic space 1423a can pass through the valley 1424e, thereby improving the vibration and / or noise attenuation effect while minimizing the flow resistance caused by the valley 1424e.

[0156] In this case, the valley 1424e can be formed between the first inlet / outlet 1424c and the second inlet / outlet 1424d, and can be formed closer to the second inlet / outlet 1424d than the first inlet / outlet 1424c. For example, a portion of the valley 1424e can be formed to overlap with the second inlet / outlet 1424d. Thus, the valley 1424e can be located as downstream as possible from the intake passage 1424 with reference to the refrigerant intake direction, thereby further reducing the flow resistance at the intake passage 1424.

[0157] Specifically, in the valley portion 1424e, at least one of the first partition wall 1427a and the second partition wall 1427b forming the outlet passage portion 1424b can protrude toward the opposite partition wall. For example, in the valley portion 1424e, the first partition wall 1427a can protrude toward the second partition wall 1427b, or the second partition wall 1427b can protrude toward the first partition wall 1427a, or the first partition wall 1427a and the second partition wall 1427b can protrude toward each other.

[0158] Here, when the first partition wall 1427a protrudes towards the second partition wall 1427b, the valley 1424e can protrude in the positive direction of the refrigerant flow direction and minimize the flow resistance caused by the valley 1424e. When the second partition wall 1427b protrudes towards the first partition wall 1427a, the valley 1424e can protrude in the opposite direction of the refrigerant flow direction and maximize the change in flow characteristics at the valley 1424e. When the two partition walls 1427a and 1427b protrude towards each other, the two situations described above can be appropriately combined. This embodiment shows an example where the first partition wall 1427a protrudes towards the second partition wall 1427b.

[0159] Furthermore, the valley 1424e can be formed as a line or as a curved surface. In the former case, a sound-absorbing space can be formed within the intake passage 1424 by forming multiple valleys 1424e. In the latter case, the flow resistance of the intake refrigerant caused by the valley 1424e can be reduced as much as possible. This embodiment shows an example of the latter, that is, the valley 1424e is formed as a curved surface.

[0160] For example, in the valley 1424e, the first partition wall 1427a can be formed as a curved protrusion toward the second partition wall 1427b. In other words, the first partition wall 1427a forming one side of the valley 1424e can be formed as a semicircular or nearly semicircular protrusion toward the second partition wall 1427b, while the second partition wall 1427b forming the other side of the valley 1424e can be formed as a straight line. Thus, the cross-sectional area of ​​the valley 1424e can be configured such that, along the refrigerant flow path, it narrows sharply from one end of the valley 1424e closer to the center, and then widens sharply from the center closer to the other end of the valley 1424e. This allows the drawn-in refrigerant to move slowly along the inner surface of the first partition wall 1427a, thereby further effectively attenuating vibrations and / or noise at the valley 1424e.

[0161] In this case, the valley 1424e can be formed symmetrically with reference to the second centerline CL2 passing through the center of the valley 1424e. In other words, the cross-sectional area of ​​the suction passage 1424 at both ends of the valley 1424e can be formed to be the same. As a result, the refrigerant suction loss caused by the valley 1424e can be minimized by reducing the flow resistance of the refrigerant through the valley 1424e as much as possible.

[0162] Figure 14 This is a graph illustrating the noise reduction effect of the inhalation muffler in this embodiment. (Refer to...) Figure 14 It can be confirmed that the inhalation muffler 142 of this embodiment improves the noise attenuation effect compared to existing inhalation mufflers (e.g., Patent Document 1). In particular, it can be confirmed that the noise attenuation effect in the low-frequency band (800-1.6kHz) is further improved. It can be confirmed that the valley 1424e is formed as a curved surface in the middle of the inhalation passage 1424, thereby improving the noise attenuation characteristics.

[0163] Figure 15 This is a schematic diagram illustrating another embodiment of the inhalation pathway. (Refer to...) Figure 15 Both sides of the valley 1424e can also be formed as curved surfaces. For example, the second partition wall 1427b can also be formed as a curved surface like the first partition wall 1427a. In this case, the curvature R2 of the second partition wall 1427b can be formed to be equal to or less than the curvature R1 of the first partition wall 1427a. As a result, the flow resistance of the refrigerant is reduced, and a valley 1424e can be formed in the middle of the suction passage 1424, thereby further reducing the refrigerant suction loss.

[0164] Figure 16 This is a perspective view showing the oil damping section of this embodiment. Figure 17 It is shown Figure 16 Sectional view along line "XVII-XVII", Figures 18 to 20 This is a schematic diagram showing another embodiment of the oil damping unit.

[0165] Refer again Figures 4 to 8 An oil damping portion 1429 can be formed on the outer surface of the front cover 1425. For example, the oil damping portion 1429 can be formed at the opposite end of the muffler inlet 1421 at both ends in the circumferential direction of the front cover 1425; in other words, it can be formed at a position where at least a portion of it overlaps radially with the oil pipe 117 on the second silencing space 1423b side. Thus, the oil damping portion 1429 can not only be formed to face the oil pipe 117 radially, but the muffler inlet 1421 and the oil damping portion 1429 can also be formed as large and deep as possible.

[0166] In this case, the cross-sectional area of ​​the oil damping section 1429 can be formed to be greater than or equal to the cross-sectional area of ​​the oil pipe 117. For example, the cross-sectional area of ​​the oil damping section 1429 can be formed to be greater than the cross-sectional area of ​​the oil pipe 117. Thus, while the oil pipe 117 can be accommodated in the circumferential and axial directions of the oil damping section 1429, almost the majority of the oil injected through the oil pipe 117 can interact with the oil damping section 1429, thereby effectively suppressing backflow of oil in the oil pipe 117 that becomes blocked after oil injection when the compressor is installed.

[0167] Specifically, the oil damping portion 1429 can be recessed towards the back cover 1426 at a predetermined depth, similar to the muffler inlet 1421. For example, the oil damping portion 1429 can be formed to protrude further towards the inner side of the back cover 1426 than the inner side of the front cover 1425 forming the second anechoic space 1423b, except for the portion where the oil damping portion 1429 is formed. Thus, with the outer peripheral surface of the front cover 1425 as a reference, the inner side (bottom surface) 1429a of the oil damping portion 1429 facing the inner peripheral surface of the outer casing 110 can be recessed to a depth that overlaps with at least a portion of the second anechoic space 1423b in the circumferential direction.

[0168] The inner peripheral surface of the oil damping section 1429 can be formed in a closed or open shape. In other words, the inner peripheral surface of the oil damping section 1429 can be formed in a circular shape, and the lower end can be formed in an open arc shape. In the former case, the volume of the noise reduction space 1423 caused by the oil damping section 1429 can be ensured to be as wide as possible by forming the cross-sectional area of ​​the oil damping section 1429 as possible. In the latter case, with the lower half of the inner peripheral surface of the oil damping section 1429 opening towards the bottom surface of the outer casing 110, oil will flow smoothly through the oil damping section 1429 to the oil storage space 110b of the outer casing 110. As a result, the backflow of oil injected into the internal space 110a of the outer casing 110 towards the oil pipe 117 can be effectively suppressed. This embodiment illustrates the latter case, where the top surface 1429b and the two side surfaces 1429c of the oil damping section 1429 are blocked and the bottom surface 1429d is open.

[0169] Reference Figure 16 In this embodiment, the oil damping section 1429 can be formed in an arc shape, and the two side surfaces 1429c in the circumferential direction of the oil damping section 1429 can be formed in parallel. As a result, the oil colliding with the oil damping section 1429 can flow smoothly into the oil storage space 110b of the outer casing 110, while minimizing the cross-sectional area of ​​the oil damping section 1429 as much as possible and ensuring the volume of the noise reduction space 1423 as wide as possible.

[0170] The depth D of the oil damping portion 1429 can be formed to be less than or equal to the radial width L of the second anechoic space 1423b, which is defined as the interval between the inner side of the front cover 1425 and the inner side of the back cover 1426 at the location where the oil damping portion 1429 is formed. For example, the depth D of the oil damping portion 1429 can be formed to be less than the radial width L of the second anechoic space 1423b. As a result, the interval between the inner circumferential surface of the housing 110 and the outer side of the intake muffler 142 facing the inner circumferential surface of the housing 110 can be separated by the depth D of the oil damping portion 1429, thereby effectively suppressing the backflow of oil through the oil pipe 117. At the same time, the reduction in the internal volume of the second anechoic space 1423b can be minimized as much as possible, thereby improving the noise and / or vibration attenuation effect.

[0171] In this case, the end of the oil pipe 117 may not be inserted into the interior of the oil damping section 1429. It can be configured to face the oil damping section 1429 radially from its exterior. Alternatively, the end of the oil pipe 117 may be inserted into the interior of the oil damping section 1429. In the former case, when the compressor body C vibrates, it is possible to prevent the suction muffler 142 and the oil pipe 117 from colliding while maximizing the gap G between the oil damping section 1429 and the oil pipe 117. In the latter case, the oil pipe 117 can be inserted as deeply as possible into the internal space 110a of the housing 110, thereby improving the assembly reliability of the oil pipe 117. This embodiment illustrates the former case, where the end of the oil pipe 117 is positioned outside the oil damping section 1429.

[0172] Reference Figure 17 The inner surface 1429a of the oil damping section 1429 facing the oil pipe 117 can be formed flat. For example, the inner surface 1429a of the oil damping section 1429 can be formed into a flat plate shape. Thus, the oil damping section 1429 can be easily formed while appropriately maintaining the gap G between the oil damping section 1429 and the oil pipe 117, thereby suppressing oil backflow.

[0173] Reference Figure 18 and Figure 19 The inner surface 1429a of the oil damping section 1429 facing the oil pipe 117 can also be formed as a curved surface. In this case, the inner surface 1429a of the oil damping section 1429 can be formed to allow the oil at the oil damping section 1429 to spread wider according to the curved surface shape, and the depth D of the oil damping section 1429 can also be formed deeper.

[0174] In other words, such as Figure 18 As shown, when the inner side 1429a of the oil damping part 1429 protrudes and bends toward the inner peripheral surface of the outer casing 110, the edge of the oil damping part 1429 can be formed to be deeper than the center, so that the oil can spread rapidly toward the edge of the oil damping part 1429, flow smoothly and be quickly injected into the oil storage space 110b of the outer casing 110.

[0175] On the contrary, such as Figure 19 As shown, when the oil damping section 1429 is recessed and bent away from the inner peripheral surface of the housing 110, the inner side surface (bottom surface) 1429a of the oil damping section 1429 facing the oil pipe 117 can be formed to be deeper and wider to ensure the gap G between the oil damping section 1429 and the oil pipe 117, thereby effectively suppressing oil backflow into the oil pipe 117.

[0176] Reference Figure 20The width of the upper end and the width of the lower end of the oil damping section 1429 can also be different. For example, the oil damping section 1429 can be formed into an arc shape, and the two side surfaces 1429c in the circumferential direction of the oil damping section 1429 can also be formed to become wider closer to the lower end. As a result, while the bottom surface 1429d of the opening end of the oil damping section 1429 can be formed to be wider, the oil that collides with the inner side surface (bottom surface) 1429a of the oil damping section 1429 can flow more smoothly towards the oil storage space 110b of the outer casing 110 and be injected into the oil storage space 110b more quickly.

[0177] In this way, a sound-absorbing space and an intake passage can be formed by creating interlocking partition walls on the front and back covers of the intake muffler, thereby simplifying the structure of the intake muffler and saving manufacturing costs.

[0178] Additionally, a silencing space can be created by forming interlocking partition walls on the front and back covers of the intake muffler, thereby simplifying the structure of the intake muffler while ensuring sufficient silencing space. This effectively attenuates vibrations and / or noise at the intake muffler.

[0179] In addition, the intake passage can be formed by forming interlocking partition walls on the front and back covers of the intake muffler, and the shape of the intake passage can be varied by forming a valley in the middle of the intake passage, thereby further effectively attenuating vibration and / or noise at the intake muffler.

[0180] Furthermore, a refrigerant trapping section wider than the cross-sectional area of ​​the suction inlet can be formed upstream of the inlet that forms the suction muffler, thereby increasing the amount of refrigerant drawn in through the suction inlet. This increases the amount of refrigerant drawn into the compression chamber while simultaneously improving compressor performance.

[0181] Additionally, the gap between the oil pipe and the intake muffler facing the oil pipe can be widened by forming an oil damping section on the outer side of the intake muffler facing the oil pipe. This allows for rapid and easy oil injection by suppressing backflow of oil injected into the internal space of the casing via the oil pipe.

Claims

1. A reciprocating compressor, characterized in that, include: shell; A drive motor is located within the interior space of the housing; A drive shaft, which is connected to the rotor of the drive motor; The piston is coupled to the drive shaft and reciprocates. A cylinder, wherein the piston is reciprocally inserted into the cylinder, and the cylinder and the piston together form a compression chamber; as well as The intake muffler includes a muffler inlet opening into the internal space of the housing, a muffler outlet opening into the intake side of the compression chamber, a silencing space disposed between the muffler inlet and the muffler outlet, and an intake passage connecting the muffler inlet and the muffler outlet through the silencing space. The inhalation passage forms a valley with a smaller cross-sectional area.

2. The reciprocating compressor according to claim 1, characterized in that, The intake passage is formed by a partition wall extending from the inner side of the intake muffler. The valley is formed by a portion of the partition wall protruding in a direction that intersects the length direction of the inhalation passage.

3. The reciprocating compressor according to claim 2, characterized in that, The valley is a part of the partition wall that is formed by a curved protrusion.

4. The reciprocating compressor according to claim 3, characterized in that, The valley is formed symmetrically with respect to the center line passing through the center of the valley.

5. The reciprocating compressor according to claim 1, characterized in that, The inhalation passage is formed between a first partition wall and a second partition wall that face each other. The valley is formed by a portion of the first partition wall protruding toward the second partition wall.

6. The reciprocating compressor according to claim 5, characterized in that, The first partition wall is formed on the side that is more adjacent to the muffler inlet than the second partition wall. The valley is formed by protruding in an arc shape.

7. The reciprocating compressor according to claim 5, characterized in that, The second partition wall forms a straight line in the valley, or The second partition wall is formed in the valley as a curved surface that protrudes in a direction corresponding to the first partition wall, and the curvature of the second partition wall is less than that of the first partition wall.

8. The reciprocating compressor according to claim 1, characterized in that, The anechoic spaces are configured in multiple ways. The valley is formed between a plurality of the anechoic spaces.

9. The reciprocating compressor according to claim 8, characterized in that, The plurality of said anechoic spaces include: The first anechoic space is connected to the inlet of the silencer; and The second anechoic space is separated from the first anechoic space by the intake passage and is connected to the muffler outlet; The valley is formed to be more adjacent to the entrance / exit of the second anechoic space than the entrance / exit of the first anechoic space.

10. The reciprocating compressor according to claim 1, characterized in that, The inhalation pathway includes: The inlet passage is connected to the inlet of the muffler; and The outlet passage is connected to the outlet of the muffler; The cross-sectional area of ​​the inlet passage is such that at least a portion of it becomes smaller as it approaches the outlet passage.

11. The reciprocating compressor according to claim 10, characterized in that, The inlet passage extends in the same direction as the muffler inlet. The outlet passage extends in the same direction as the muffler outlet. The inlet passage and the outlet passage are formed by bending at right angles to each other.

12. The reciprocating compressor according to any one of claims 1 to 11, characterized in that, The silencer inlet includes: Inhalation port, connected to the inhalation passage; and A refrigerant trap is disposed between the internal space of the housing and the suction port; The cross-sectional area of ​​the refrigerant trap is larger than the cross-sectional area of ​​the suction port.

13. The reciprocating compressor according to any one of claims 1 to 11, characterized in that, An oil pipe is connected to the outer casing and penetrates the outer casing. An oil damping section with a pre-set depth is formed on the outer side of the intake muffler facing the oil pipe.

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