Silencer assembly and compressor

Abstract

The embodiment of the invention provides a silencer assembly and a compressor, and the silencer assembly comprises a first silencer which comprises a first bottom cover and a first boss structure protruding from the first side of the first bottom cover to the second side of the first bottom cover; the second silencer is arranged on the second side of the first silencer, and the second silencer comprises a second bottom cover and a second boss structure protruding in the direction from the first side of the second bottom cover to the second side of the second bottom cover; the first boss structure comprises a plurality of first bosses and second bosses which are arranged in the circumferential direction, the minimum axial distance between the first bosses and the first bottom cover is larger than the minimum axial distance between the second bosses and the first bottom cover, and first exhaust holes are formed in the second bosses; the second boss structure comprises a plurality of second convex hull parts arranged in the circumferential direction, and second exhaust holes are formed in the second convex hull parts. In the technical scheme of the invention, through the cooperation of the inner and outer layers of silencers, namely the first silencer and the second silencer, the multi-band noise absorption and suppression can be effectively realized.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and more particularly, to a silencer assembly and a compressor. Background Art

[0002] Currently, a silencer is usually arranged outside the upper bearing structure of a compressor, and the exhaust holes of the silencer are arranged at the top. However, with the continuous improvement of the demand for miniaturization of the compressor volume, in the related art, during the process of top exhaust, due to the relatively low overall height of the compressor, the air flow is likely to directly blow the rotor, which will cause axial pulsating excitation and make the stability of the rotor during operation relatively weak. Summary of the Invention

[0003] The present invention aims to at least solve the technical problem of relatively weak rotor stability during the operation of a miniaturized compressor in the prior art or related technologies.

[0004] In view of this, an embodiment of the first aspect of the present invention provides a silencer assembly.

[0005] An embodiment of the second aspect of the present invention provides a compressor.

[0006] To achieve the above object, an embodiment of the present invention provides a silencer assembly, including: a first silencer, the first silencer including a first bottom cover and a first boss structure protruding from the first side of the first bottom cover towards the second side; a second silencer, arranged on the second side of the first silencer, the second silencer including a second bottom cover and a second boss structure protruding from the first side of the second bottom cover towards the second side; the first boss structure includes a plurality of first convex portions arranged circumferentially, the first convex portion including a first boss and a second boss, the minimum axial distance between the first boss and the first bottom cover is greater than the minimum axial distance between the second boss and the first bottom cover, and at least one first exhaust hole is provided on the second boss; the second boss structure includes a plurality of second convex portions arranged circumferentially, and at least one second exhaust hole is provided on at least one of the second convex portions; wherein, the first bottom cover and the second bottom cover are stacked, and the first boss structure is located inside the second silencer.

[0007] According to the silencer assembly proposed by the present invention, through the cooperation of the boss structures of the inner and outer two-layer silencers, namely the first silencer and the second silencer, the absorption and suppression of multi-band noise are effectively realized, and it is particularly excellent in the control of medium and low frequency and high frequency noise.

[0008] Specifically, the first muffler, as the inner muffler, includes a first bottom cover and a first boss structure. The first bottom cover serves as the basis and support surface of the structure, providing fixation and support for the first boss structure while ensuring the stability of the air flow direction. The first boss structure protrudes from the first side of the first bottom cover towards the second side, and can form multiple first convex portions, increasing the reflection path of sound waves inside the boss and enhancing the sound absorption effect, so as to serve as an acoustic impedance structure for sound wave reflection and absorption.

[0009] By restricting the circumferential distribution of multiple first convex portions on the first boss structure, the path complexity of sound waves is increased, and the sound absorption area and reflection effect are improved.

[0010] Among them, the first convex portion includes a first boss and a second boss with different heights, forming a multi-level acoustic impedance structure to optimize the reflection, scattering and absorption of sound waves. By arranging one or more first exhaust holes on the lower second boss, that is, the minimum axial distance between the first boss and the first bottom cover is greater than the minimum axial distance between the second boss and the first bottom cover, and at least one first exhaust hole is provided on the second boss. The first exhaust hole, as the outlet of the exhaust air flow, is arranged on the lower second boss, which is beneficial to guiding the exhaust air flow to discharge from the lower area of the inner muffler, forming a controlled air flow path. Local pressure changes and turbulence are generated around the exhaust hole for sound waves, enhancing the scattering and attenuation effects of sound waves, especially effective for medium and low frequency noises.

[0011] The lower position of the second boss forms a stepped structure. Arranging the first exhaust hole here helps sound waves to be repeatedly reflected between the stepped bosses, extending the propagation path of sound waves and enhancing the sound absorption effect.

[0012] In some technical solutions, optionally, the ratio range of the minimum axial distance between the second boss and the first bottom cover to the minimum axial distance between the first boss and the first bottom cover is 0.35 - 0.9.

[0013] In this technical solution, the minimum axial distance (H2) between the first boss and the first bottom cover is the shortest distance measured axially from the first bottom cover to the first boss (the higher protruding part) in the inner muffler, that is, the height or protruding degree of the first boss. The minimum axial distance (H1) between the second boss and the first bottom cover is the shortest distance measured axially from the first bottom cover to the second boss (the lower protruding part) in the inner muffler, that is, the height of the second boss.

[0014] By controlling the ratio range of the two, that is, the ratio of H1 / H2 is between 0.35 - 0.9, that is, the height of the second boss is 35% to 90% of the height of the first boss, and controlling the ratio of H1 to H2, the inner muffler forms an obvious stepped boss structure, thereby generating multiple acoustic wave reflection interfaces, increasing the propagation path and reflection times of sound waves in the muffler, and enhancing the sound absorption effect.

[0015] In some technical solutions, optionally, the ratio range of the axial dimension of the first muffler to the axial dimension of the second muffler is 0.3 to 0.76.

[0016] In this technical solution, the axial dimension of the first muffler, that is, the length or height of the inner muffler (the first muffler) measured along the axis, and the axial dimension of the second muffler, that is, the length or height of the outer muffler (the second muffler) along the axis. By restricting the ratio range of the two to 0.3 to 0.76, that is, the axial dimension of the inner muffler is 30% to 76% of the outer muffler, this ratio ensures that the inner muffler (the first muffler) has a certain dimensional difference relative to the outer muffler (the second muffler), forming a multi-level spatial layout.

[0017] In some technical solutions, optionally, the opening end face of the first exhaust hole is a plane, and the angle between the normal line of the opening end face of the first exhaust hole and the plane where the first bottom cover is located is not greater than 90°; and / or the opening end face of the second exhaust hole is a plane, and the angle between the normal line of the opening end face of the second exhaust hole and the plane where the second bottom cover is located is not greater than 90°.

[0018] In this technical solution, by restricting the opening end faces of the first exhaust hole and the second exhaust hole, and restricting the orientation of the first exhaust hole, that is, the opening end face is a plane, so that the opening end face of the exhaust hole is a flat plane, ensuring that the exhaust air flow is smooth and uniform when passing through, reducing air flow disturbance and vortex generation. On the one hand, by keeping the opening end face flat, the air flow passes smoothly, reducing the disturbance and vortex of the air flow at the outlet of the exhaust hole, reducing the noise caused by air flow impact. On the other hand, the flat end face is convenient for processing and manufacturing (such as stamping, milling), ensuring the flatness of the exhaust hole end face, facilitating sealing and assembly, and improving manufacturing efficiency and assembly accuracy.

[0019] In some technical solutions, optionally, the ratio of the total opening area of the second exhaust hole to the opening area of the bearing exhaust port connected to the second exhaust hole is 0.5 to 1.5.

[0020] In this technical solution, by restricting the ratio of the areas of the second exhaust hole and the bearing exhaust port, where the total opening area (S) of the second exhaust hole is the sum of the total cross-sectional areas of all the second exhaust holes, and the opening area (S0) of the bearing exhaust port is the area of the bearing exhaust port connected to the second exhaust hole. By restricting the ratio range of the two to 0.5 ≤ S / S0 ≤ 1.5, it ensures that the air flow distribution in the exhaust path is reasonable, ensuring both sufficient flow of the exhaust hole and avoiding excessive congestion or insufficient air flow.

[0021] In some technical solutions, optionally, the first bottom cover and the first boss structure are integrally formed; and / or the second bottom cover and the second boss structure are integrally formed.

[0022] In this technical solution, the bottom cover structure and the boss structure are integrally processed and formed. Specifically, the first bottom cover and the first boss structure can be integrally formed, and the second bottom cover and the second boss structure can also be integrally formed, thereby ensuring the integrity of the structure, eliminating bolt / welding connections, and reducing stress concentration. At the same time, the sealing performance is also improved, there is no risk of interface leakage, and the pressure resistance ability is relatively strong.

[0023] In some technical solutions, optionally, connection holes are provided on the first bottom cover and the second bottom cover. In the cross-section of the first bottom cover, the projection of the connection hole does not overlap with the projection of the first convex part. In the cross-section of the second bottom cover, the projection of the connection hole does not overlap with the projection of the second convex part.

[0024] In this technical solution, the connection holes are located on the first bottom cover and the second bottom cover and are used to connect the first bottom cover to the upper bearing structure. In the cross-section (i.e., the plane perpendicular to the axial direction) of the first bottom cover, the projection area of the connection hole and the projection area of the first convex part have no intersection. Similarly, in the cross-section of the second bottom cover, the projection of the connection hole does not overlap with the projection of the second convex part. Through the above limitations, the projection of the connection hole and the convex part do not overlap, ensuring that when the air flow passes through the connection hole, it will not directly pass through the acoustic reflection area inside the convex part, reducing acoustic interference and the complexity of the noise propagation path. In addition, avoiding the overlap of the connection hole and the convex projection helps to reduce local vibration and resonance points of the structure and reduce noise amplification.

[0025] In some technical solutions, optionally, the second exhaust hole is provided in the second boss part with the largest inner cavity volume among the plurality of second boss parts.

[0026] For the muffler structure, the second muffler includes a plurality of second boss parts, and each second boss part has a certain inner cavity volume. By arranging the second exhaust hole in the second boss part with the largest inner cavity volume, the relatively large cavity space can be effectively utilized, the air flow resistance can be reduced, and the gas can be discharged smoothly.

[0027] An embodiment of the second aspect of the present application provides a compressor, including: an upper bearing structure, the upper bearing structure includes a flange part and a cylindrical part protruding from the flange part, and the cylindrical part is hollow for accommodating a crankshaft; any of the above muffler assemblies, sleeved outside the cylindrical part.

[0028] According to the compressor provided by the present application, including an upper bearing structure and a muffler assembly, by integrating the muffler assembly with the upper bearing structure, the coordinated improvement of aerodynamic performance, noise reduction effect and mechanical reliability is realized. The upper bearing structure includes a flange part and a cylindrical part, which are used to support the crankshaft and transmit loads. The muffler assembly is fixed to the flange part by bolts to form a rigid-flexible coupling system.

[0029] Since the compressor includes any one of the above muffler components, it has the beneficial effects of any one of the above muffler components, which will not be elaborated here.

[0030] In some technical solutions, optionally, the cylinder part includes a first shaft part and a second shaft part. The first shaft part is connected to the flange part, and the outer diameter of the first shaft part is larger than that of the second shaft part. Wherein, the minimum axial distance between the second boss and the first bottom cover is not greater than the axial dimension of the first shaft part.

[0031] In this technical solution, the cylinder part includes at least two parts, namely a first shaft part and a second shaft part. Among them, the first shaft part is connected to the flange part and has a larger outer diameter, playing a role of support and connection. The second shaft part has a smaller outer diameter and is located adjacent to the first shaft part.

[0032] By restricting the lengths of the second boss and the first shaft part, specifically, the minimum axial distance between the second boss and the first bottom cover, that is, the minimum axial distance from the second boss to the first bottom cover in the inner muffler, and the axial dimension of the first shaft part, that is, the axial length of the first shaft part. By making the outer diameter of the first shaft part larger, sufficient mechanical strength and an installation base are provided to support the flange part and related components. The second shaft part has a smaller outer diameter, which is convenient for cooperation with the crankshaft or other mechanical components, improving the compactness and coordination of the overall structure.

[0033] In some technical solutions, optionally, a bearing exhaust port is provided on the flange part of the upper bearing structure. When the muffler component is connected to the flange part, the included angle range between the plane passing through the axis of the bearing exhaust port and the axis of the cylinder part and the plane passing through the axis of the first exhaust hole and the axis of the cylinder part is 60° - 90°.

[0034] By providing the bearing exhaust port on the flange part of the upper bearing structure, after the muffler component is connected to the flange part, the exhaust direction of the exhaust hole is opposite to the axis of the cylinder part. By restricting the included angle range between the exhaust direction (axis) of the exhaust hole and the axis of the cylinder part in space to be 60° - 90°, it is ensured that the exhaust flow deviates from the axis of the cylinder part at a certain angle, avoiding conflicts or interferences between the exhaust pipe and the bearing and the cylinder body, and reasonably utilizing the space.

[0035] The additional aspects and advantages of the present invention will become apparent in the following description part or be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 Shows a schematic structural diagram of a muffler component according to an embodiment of the present invention;

[0037] Figure 2 Shows a schematic structural diagram of a muffler component according to an embodiment of the present invention;

[0038] Figure 3Shows a schematic structural diagram of a muffler assembly according to an embodiment of the present invention;

[0039] Figure 4 Shows a schematic structural diagram of a muffler assembly according to an embodiment of the present invention;

[0040] Figure 5 Shows a schematic structural diagram of an upper bearing structure according to an embodiment of the present invention;

[0041] Figure 6 Shows a schematic structural diagram of a compressor according to an embodiment of the present invention;

[0042] Figure 7 Shows a schematic diagram of the relationship curve between the heights of the first boss and the second boss and the transmission loss in this embodiment;

[0043] Figure 8 Shows a schematic diagram of the average sound attenuation of the heights of the first boss and the second boss below 4000 Hz in this embodiment.

[0044] Among them, Figures 1 to 6 The corresponding relationship between the reference numerals and the component names in the figure is:

[0045] 100: Muffler assembly;

[0046] 102: First muffler; 1022: First bottom cover; 1024: First boss structure; 104: First convex part; 1042: First boss; 1044: Second boss; 106: First exhaust hole;

[0047] 110: Second muffler; 1122: Second bottom cover; 1124: Second boss structure; 114: Second exhaust hole; 116: Second convex part;

[0048] 122: First side; 124: Second side;

[0049] 132: Connecting hole;

[0050] 200: Compressor; 202: Upper bearing structure; 2022: Flange part; 2023: Bearing exhaust port; 2024: Cylindrical part; 2026: First shaft part; 2028: Second shaft part. Detailed implementation manners

[0051] In order to be able to more clearly understand the above-mentioned objects, features and advantages of the embodiments of the present invention, the embodiments of the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

[0052] In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. However, embodiments of the present invention may be practiced in other ways different from those described herein. Therefore, the scope of protection of the present application is not limited by the limitations of the specific embodiments disclosed below.

[0053] Reference is made below Figures 1 to 8 to describe some embodiments in accordance with the present invention.

[0054] As Figure 1 and Figure 5 shown, this embodiment provides a muffler assembly 100. Through the cooperation of the boss structures of the inner and outer two layers of mufflers, namely the first muffler 102 and the second muffler 110, effective absorption and suppression of noise in multiple frequency bands are achieved, especially excellent performance in medium and low frequency and high frequency noise control.

[0055] Specifically, the first muffler 102, as the inner layer muffler, includes a first bottom cover 1022 and a first boss structure 1024. The first bottom cover 1022 serves as the basis and support surface of the structure, providing fixation and support for the first boss structure 1024, and at the same time ensuring the stability of the air flow guidance. The first boss structure 1024 protrudes from the first side 122 of the first bottom cover 1022 towards the second side 124, and can form a plurality of first convex portions 104, increasing the reflection path of sound waves inside the boss, enhancing the sound absorption effect, and serving as an acoustic impedance structure for sound wave reflection and absorption.

[0056] By restricting the circumferential distribution of the plurality of first convex portions 104 on the first boss structure 1024, the complexity of the sound wave path is increased, and the sound absorption area and reflection effect are improved.

[0057] Among them, the first convex portion 104 includes a first boss 1042 and a second boss 1044 with different heights, forming a multi-level acoustic impedance structure to optimize the reflection, scattering and absorption of sound waves. By providing one or more first exhaust holes 106 on the lower second boss 1044, that is, the minimum axial distance between the first boss 1042 and the first bottom cover 1022 is greater than the minimum axial distance between the second boss 1044 and the first bottom cover 1022, and at least one first exhaust hole 106 is provided on the second boss 1044. The first exhaust hole 106 serves as the outlet of the exhaust air flow. Being provided on the lower second boss 1044 is conducive to guiding the exhaust air flow to discharge from the lower area of the inner layer muffler, forming a controlled air flow path. Sound waves generate local pressure changes and turbulence around the exhaust hole, enhancing the scattering and attenuation effects of sound waves, especially effective for medium and low frequency noise.

[0058] The lower position of the second boss 1044 forms a stepped structure. Setting the first exhaust hole 106 here helps sound waves to be repeatedly reflected between the stepped bosses, extending the sound wave propagation path and enhancing the sound absorption effect.

[0059] The second muffler 110 serves as an outer muffler and includes a second bottom cover 1122 and a second boss structure 1124 protruding from the first side 122 of the second bottom cover 1122. Among them, the second bottom cover 1122 serves as the support and sealing surface of the outer structure to ensure that the air flow passes between the outer bosses. The second boss structure 1124 cooperates with the first boss structure 1024 to form an acoustic impedance structure on the outer layer, reflecting and scattering the outer noise.

[0060] By providing a plurality of circumferentially arranged second convex portions on the second boss structure 1124, multi-angle sound wave reflection and scattering paths are provided. At the same time, by providing second exhaust holes 114 on the second convex portions, the discharge path of the exhaust air flow is controlled, and the frequency and intensity of the exhaust noise are adjusted.

[0061] By restricting the relative positional relationship between the first boss structure 1024 and the second muffler 110, that is, the first bottom cover 1022 and the second bottom cover 1122 are stacked, and the first boss structure 1024 is located inside the second muffler 110, a stepped structure of the inner and outer layers is formed, effectively blocking the transmission of noise in different frequency bands. For example, the first boss structure 1024 on the inner layer mainly targets medium and low frequencies, while the second boss structure 1124 on the outer layer targets high frequencies.

[0062] In some embodiments, optionally, the number of the first convex portions 104 is the same as the number of the second convex portions 116, and the circumferential distribution trend of the lobe shapes of the first convex portions 104 is the same as the circumferential distribution trend of the lobe shapes of the second convex portions 116; among them, the lobe shape of the first convex portion 104 provided with the first exhaust hole is the same as the lobe shape of the second convex portion 116 provided with the second exhaust hole.

[0063] By respectively providing corresponding exhaust holes on the convex portions in two adjacent mufflers. Specifically, the number of the first convex portions 104 is the same as the number of the second convex portions 116, and the distribution law of the lobe shapes of the convex portions in the circumferential direction is also consistent, that is, the circumferential distribution trend of the lobe shapes is the same. It can be understood that the circumferential distribution trend of the lobe shapes is the change trend of the projected area corresponding to each convex portion on the plane where the bottom cover is located, and the change trend remains consistent. On this basis, by restricting the lobe shape of the first convex portion 104 provided with the first exhaust hole to be the same as the lobe shape of the second convex portion 116 provided with the second exhaust hole, reasonable guidance of the air flow can be achieved.

[0064] In some embodiments, optionally, as Figure 1As shown, the minimum axial distance (H2) between the first boss 1042 and the first bottom cover 1022 is the shortest distance measured axially from the first bottom cover 1022 to the first boss 1042 (the higher protruding part) in the inner muffler, that is, the height or protruding degree of the first boss 1042. The minimum axial distance (H1) between the second boss 1044 and the first bottom cover 1022 is the shortest distance measured axially from the first bottom cover 1022 to the second boss 1044 (the lower protruding part) in the inner muffler, that is, the height of the second boss 1044.

[0065] By controlling the ratio range of the two, that is, the ratio of H1 / H2 is between 0.35 and 0.9, that is, the height of the second boss 1044 is 35% to 90% of the height of the first boss 1042, the ratio of H1 to H2 is controlled, and the inner muffler forms an obvious stepped boss structure, thereby generating multiple acoustic reflection interfaces, increasing the propagation path and reflection times of sound waves in the muffler, and improving the sound absorption effect.

[0066] In addition, the lower second boss 1044 (H1) acts as an intermediate reflection surface and acts together with the higher first boss 1042 (H2) to form acoustic impedance surfaces of different heights, enhancing the reflection and absorption capabilities of sound waves of different frequencies. By limiting the ratio range to 0.35 - 0.9, it can be ensured that the second boss 1044 is neither too low (to avoid weakening the sound absorption effect) nor too high (to prevent structural congestion or airflow obstruction), achieving the best acoustic adjustment.

[0067] Among them, when the position of the second boss 1044 is relatively low, exhaust holes are provided on the second boss 1044 to ensure smooth airflow discharge without being blocked by the first boss 1042.

[0068] In some embodiments, optionally, as Figure 1 and Figure 3 shown, the axial dimension of the first muffler 102, that is, the length or height H2 of the inner muffler (the first muffler 102) measured axially, and the axial dimension H3 of the second muffler 110, that is, the axial length or height of the outer muffler (the second muffler 110). By limiting the ratio range of the two to 0.3 - 0.76, that is, the axial dimension of the inner muffler is 30% to 76% of the outer muffler, this ratio ensures that the inner muffler (the first muffler 102) has a certain dimensional difference relative to the outer muffler (the second muffler 110), forming a multi-level spatial layout.

[0069] If the ratio is small, that is, close to 0.3, the inner muffler is shorter and mainly plays a role in local sound absorption and reflection, suitable for absorbing high-frequency noise and reducing noise transmission near the exhaust port. If the ratio is large, that is, close to 0.76, the inner muffler is longer and can form a more complex acoustic path, enhancing the attenuation effect on medium and low-frequency noise.

[0070] By restricting the retention ratio to be between 0.3 and 0.76, it can not only ensure that the inner structure has sufficient length (to achieve effective acoustic effects), but also prevent the structure from being too heavy or difficult to manufacture due to excessive size.

[0071] In some embodiments, optionally, the opening end faces of the first exhaust hole 106 and the second exhaust hole 114 are restricted, and the orientation of the first exhaust hole 106 is restricted, that is, the opening end face is a plane, so that the opening end face of the exhaust hole is a flat plane, ensuring that the exhaust air flow is smooth and uniform when passing through, reducing air flow disturbance and vortex generation. On the one hand, by keeping the opening end face flat, the air flow passes smoothly, reducing the disturbance and vortex at the outlet of the exhaust hole, and reducing the noise caused by air flow impact. On the other hand, the flat end face is convenient for processing and manufacturing (such as stamping, milling), ensuring that the end face of the exhaust hole is flat, facilitating sealing and assembly, and improving manufacturing efficiency and assembly accuracy.

[0072] At the same time, the included angle range between the opening direction of the exhaust hole (i.e., the normal direction of the opening end face) and the plane where the bottom cover is located is restricted to be between 0° and 90°. At the two extreme positions, the included angle is 0°, the opening surface of the exhaust hole is parallel to the bottom cover plane, and the air flow is discharged along the parallel direction. The included angle is 90°, the opening surface of the exhaust hole is perpendicular to the bottom cover plane, and the air flow is discharged vertically. By restricting the included angle range, a certain deviation is allowed, but not exceeding 90°, which helps to guide the exhaust air flow to flow out along the predetermined direction, avoiding reverse air flow or excessive deviation, and thus optimizing the exhaust path.

[0073] It can be understood that the first exhaust hole 106 can exhaust air from the top or the side. Similarly, the second exhaust hole 114 can exhaust air from the top or the side.

[0074] In some embodiments, optionally, the ratio of the areas of the second exhaust hole 114 and the bearing exhaust port 2023 is limited. Among them, the total opening area (S) of the second exhaust hole 114 is the sum of the total cross-sectional areas of all the second exhaust holes 114, and the opening area (S0) of the bearing exhaust port 2023 is the area of the bearing exhaust port 2023 connected to the second exhaust hole 114. By restricting the ratio range between the two to be 0.5 ≤ S / S0 ≤ 1.5, it ensures that the air flow is reasonably distributed in the exhaust path, ensuring sufficient air flow in the exhaust hole while avoiding excessive congestion or insufficient air flow.

[0075] Generally speaking, by restricting the ratio range between the two to be 0.5 to 1.5, it ensures a reasonable proportional relationship between the total opening area of the second exhaust hole 114 and the area of the bearing exhaust port 2023, ensuring both the exhaust flow rate and optimizing the acoustic effects and mechanical properties.

[0076] In some embodiments, optionally, the bottom cover structure and the boss structure are integrally processed and formed. Specifically, the first bottom cover 1022 and the first boss structure 1024 can be integrally formed, and the second bottom cover 1122 and the second boss structure 1124 can also be integrally formed, thereby ensuring the integrity of the structure, eliminating bolt / welding connections, and reducing stress concentration.

[0077] Furthermore, the first exhaust hole 106 and the second exhaust hole 114 are synchronously blanked with the bottom cover using a punching process.

[0078] In some embodiments, optionally, as Figure 2 and Figure 4 shown, the connection holes 132 are located on the first bottom cover 1022 and the second bottom cover 1122, and are used to connect the first bottom cover 1022 to the upper bearing structure 202. On the cross-section of the first bottom cover 1022 (i.e., the plane perpendicular to the axial direction), the projection area of the connection hole 132 has no intersection with the projection area of the first convex part 104; on the cross-section of the second bottom cover 1122, similarly, the projection of the connection hole 132 does not overlap with the projection of the second convex part. Through the above limitations, the projection of the connection hole 132 does not overlap with the convex part, ensuring that when the air flow passes through the connection hole 132, it will not directly pass through the acoustic reflection area inside the convex part, reducing acoustic interference and the complexity of the noise propagation path. In addition, avoiding the overlap of the connection hole 132 and the convex part projection helps to reduce local vibration and resonance points of the structure and reduce noise amplification.

[0079] Generally speaking, by restricting the projection area of the connection hole 132 within the cross-sections of the first bottom cover 1022 and the second bottom cover 1122 and not overlapping with the corresponding convex part projection, it helps to optimize the air flow path, reduce noise and vibration, improve the structural layout, and simplify the manufacturing process.

[0080] In addition, by providing the connection holes 132 on the bottom cover structure as the hole positions for bolt fixation or connection with external components, the multiple connection holes 132 are circumferentially distributed, and the convex part is a raised structure on the bottom cover structure. In the cross-section projection of the bottom cover structure, the connection hole 132 does not overlap with the convex part. Further, the distance between the edges of the two is restricted to be ≥ 1.5 mm to ensure no area overlap. The non-overlapping projection avoids stress superposition between the hole edge and the convex root, reduces the maximum stress, and also improves the fatigue life.

[0081] It can be understood that the bolt pre-tightening force is evenly transmitted through the non-overlapping area, and the contact pressure fluctuation is small. At the same time, the non-overlapping design ensures continuous contact of the flange surface to reduce the leakage rate.

[0082] Among them, the connection holes 132 are distributed in the outer circle, and the convex parts are concentrated in the inner circle, with a radial distance to avoid projection interference.

[0083] Furthermore, the connecting hole 132 and the convex hull portion are not in the same radial direction.

[0084] In some embodiments, optionally, for the muffler structure, the second muffler includes a plurality of second convex hull portions 116, each of which has a certain inner cavity volume. By arranging the second exhaust hole 114 in one of the second convex hull portions 116 with the largest inner cavity volume, the relatively large cavity space can be effectively utilized, the air flow resistance can be reduced, and the gas can be discharged smoothly. In addition, the large cavity can play a role in buffering and absorbing sound waves, improving the muffling effect, reducing noise rebound and resonance, thereby helping to evenly distribute the exhaust pressure and ensuring the stable overall performance of the muffler.

[0085] As Figure 5 and Figure 6 As shown, an embodiment of the second aspect of the present application provides a compressor 200, which includes an upper bearing structure 202 and a muffler assembly 100. By integrating the muffler assembly 100 with the upper bearing structure 202, the coordinated improvement of aerodynamic performance, noise reduction effect and mechanical reliability is achieved. The upper bearing structure 202 includes a flange portion 2022 and a cylinder portion 2024, which are used to support the crankshaft and transmit loads. The muffler assembly 100 is fixed to the flange portion 2022 by bolts to form a rigid-flexible coupling system.

[0086] Since the compressor 200 includes any one of the above-mentioned muffler assemblies 100, it has the beneficial effects of any one of the above-mentioned muffler assemblies 100, which will not be elaborated here.

[0087] Furthermore, the cylinder portion 2024 at least includes two parts, a first shaft portion 2026 and a second shaft portion 2028. Among them, the first shaft portion 2026 is connected to the flange portion 2022 and has a relatively large outer diameter, which plays a role in support and connection. The second shaft portion 2028 has a relatively small outer diameter and is located adjacent to the first shaft portion 2026.

[0088] As Figure 1 and Figure 5 As shown, by restricting the lengths of the second boss 1044 and the first shaft portion 2026, specifically, the minimum axial distance (H1) between the second boss 1044 and the first bottom cover 1022, that is, the minimum axial distance from the second boss 1044 to the first bottom cover 1022 in the inner muffler, and the axial dimension (H) of the first shaft portion 2026, that is, the axial length of the first shaft portion 2026. By restricting H1≤H, the first shaft portion 2026 has a relatively large outer diameter, providing sufficient mechanical strength and an installation base to support the flange portion 2022 and related components. The second shaft portion 2028 has a relatively small outer diameter, which is convenient for cooperation with the crankshaft or other mechanical components, improving the compactness and coordination of the overall structure.

[0089] The axial distance between the second boss 1044 and the first bottom cover 1022 is not greater than the axial dimension of the first shaft portion 2026, ensuring that the inner structure of the silencer (the second boss 1044) is within the range of the first shaft portion 2026, avoiding the boss structure exceeding the support range of the cylinder portion 2024 and improving the structural stability.

[0090] It can be understood that the axial dimension of the second boss 1044 of the silencer is limited by the length of the first shaft portion 2026, ensuring that the inner silencer is within the allowable range of the mechanical structure and avoiding installation difficulties or a decline in acoustic performance due to the excessive length of the silencer structure.

[0091] Generally speaking, the relatively large outer diameter of the first shaft portion 2026 ensures mechanical support and connection strength; the relatively small outer diameter of the second shaft portion 2028 achieves a compact structure. The axial distance between the second boss 1044 and the first bottom cover 1022 is not greater than the axial dimension of the first shaft portion 2026, ensuring that the size of the inner structure of the silencer is controlled, adapting to the mechanical structure, and enhancing the overall stability and noise reduction performance.

[0092] Furthermore, as Figure 2 and Figure 5 shown, the bearing exhaust port 2023 is provided on the flange portion 2022 of the upper bearing structure 202. After the silencer assembly 100 is connected to the flange portion 2022, the exhaust direction of the exhaust hole is opposite to the axis of the cylinder portion 2024. By restricting the included angle range between the exhaust direction (axis) of the exhaust hole and the axis of the cylinder portion 2024 in space to 60° - 90°, it is ensured that the exhaust flow deviates from the axis of the cylinder portion 2024 at a certain angle, avoiding conflicts or interferences between the exhaust pipe and the bearing and the cylinder body, and rationally utilizing the space.

[0093] In this embodiment, when the included angle is close to 90°, the scattering and attenuation of the exhaust sound wave can be improved, which helps to generate strong scattering and reflection of the sound wave at the exhaust hole, enhancing the silencing effect. By restricting the above angle range, the exhaust sound wave is deviated from the main axis of the cylinder body, reducing the direct transmission of noise along the axis to the external environment and improving the noise reduction performance. In addition, through the angle restriction, it can be ensured that no excessive turbulence or vibration is generated when the air flow is discharged, reducing the noise and vibration caused by the air flow, deflecting the exhaust direction reasonably within the limited space, and avoiding conflicts between the exhaust pipe and other mechanical structures.

[0094] Generally speaking, this design effectively optimizes the spatial layout of the exhaust path, enhances the scattering and attenuation of the exhaust sound wave, and significantly improves the noise control effect by controlling the included angle between the exhaust axis passing through the bearing exhaust port 2023 and the axis of the cylinder portion 2024 to be between 60° and 90°.

[0095] Furthermore, as Figure 4 and Figure 5The position of the second exhaust hole 114 is restricted as shown. Specifically, the plane formed by the axis of the bearing exhaust port 2023 and the axis of the cylinder part 2024 is mainly used to define the spatial orientation of the exhaust direction of the bearing exhaust port 2023, and the plane formed by the axis of the second exhaust hole 114 and the axis of the cylinder part 2024 is mainly used to define the spatial orientation of the exhaust direction of the second exhaust hole 114. By restricting the included angle between the two planes, that is, the included angle is 0° to 30°, it means that the exhaust direction of the second exhaust hole 114 is relatively close to the exhaust direction of the bearing exhaust port 2023, ensuring that the exhaust direction of the second exhaust hole 114 is basically the same as or slightly deviated from the direction of the bearing exhaust port 2023, which is beneficial to the smooth connection of the exhaust flow and the flow field coordination, reduces the conflict and disturbance of the exhaust flow in the flow direction, and maintains the stability of the air flow.

[0096] By restricting the included angle between the two planes to 0° to 30°, it helps the sound waves to propagate along similar paths, facilitates the design of the acoustic structure of the muffler for effective attenuation and absorption, avoids the acoustic scattering blind area caused by too large a difference in the directions of the exhaust holes, and improves the overall noise reduction effect. In addition, it can also simplify the exhaust pipe design, facilitate the connection and installation of the muffler assembly 100 and the bearing exhaust port 2023, and is beneficial to the compact utilization of the internal space of the compressor 200.

[0097] Furthermore, the included angle between the two planes is defined as 0°, that is, the two planes are coplanar, which is more beneficial to the smooth exhaust.

[0098] In a specific embodiment, a double-layer muffler and its rotary compressor 200 are provided, including a pump body structure and a muffler disposed in a sealed housing. The muffler includes a first muffler 102 and a second muffler 110. The first muffler 102 is an inner-layer muffler. The first muffler 102 includes at least one convex hull height reduction (i.e., the second boss 1044). The inner-layer muffler exhaust hole (i.e., the first exhaust hole 106) is located at the position of the reduced convex hull. The exhaust mode is upward exhaust at the top or lateral exhaust. The included angle between the exhaust hole position and the bearing exhaust port 2023 is θ1, satisfying 60° ≤ θ1 ≤ 90°. The reduced convex hull height of the first muffler 102 is H1, and the height of the first muffler 102 is H2, satisfying 0.35 ≤ H1 / H2 ≤ 0.9. At the same time, the height of the first muffler 102 should be matched with the stepped journal of the bearing (i.e., the upper bearing structure 202), and the height H of the wide part of the journal (i.e., the first shaft part 2026) satisfies H2 ≤ H. The double-layer muffler includes a second muffler 110. The second muffler 110 is an outer-layer muffler. The convex hull of the second muffler 110 (i.e., the second boss structure 1124) is provided with an exhaust hole (i.e., the second exhaust hole 114). The exhaust hole is upward or lateral exhaust, and the included angle with the bearing exhaust port is θ2, satisfying 0° ≤ θ2 ≤ 30°. Further, θ2 = 0°. The height of the second muffler is H3, and the ratio of the height of the first muffler to the height of the second muffler is 0.3 ≤ H2 / H3 ≤ 0.76. The area of the exhaust hole of the second muffler is S, and the area of the bearing exhaust port is S0, satisfying 0.5 ≤ S / S0 ≤ 1.5. The double-layer muffler can effectively improve the noise reduction amount in the frequency bands below 1500 Hz and above 3000 Hz, which is beneficial to reducing the exhaust noise of the compressor.

[0099] In addition, a stepped convex hull structure is provided in the inner layer of the double-layer muffler, and the exhaust hole is arranged on the reduced convex hull structure. The larger the ratio of the convex hull height H2 of the inner-layer muffler to the reduced convex hull height H1, the better the noise reduction effect. It can solve the problems of medium and low-frequency air flow noise below 1500 Hz and high-frequency air flow noise above 3000 Hz at most. The noise reduction amount is increased by 3.6 dB, and the noise reduction effect is excellent. The inner-layer muffler can be completed by stamping processing, and the manufacturability is good.

[0100] Figure 7 and Figure 8 In, A represents a muffler with the same height of the first boss and the second boss of the first muffler, that is, a muffler with a uniform height. Specifically, the heights of the first boss and the second boss are both 7.5 mm. B represents a first muffler with the height of the first boss being 14 mm and the height of the second boss being 7.5 mm. C represents a first muffler with the height of the first boss being 11 mm and the height of the second boss being 7.5 mm. D represents a first muffler with the height of the first boss being 9.5 mm and the height of the second boss being 7.5 mm. As Figure 7The figure shows the relationship curve between the different inner muffler heights H2 of the convex hull reduced double-layer muffler and the transmission loss. From Figure 7 it can be seen that when the convex hull height is reduced to 7.5 mm, the transmission loss increases with the increase of the inner muffler height H2, and the noise reduction amount increases, which can solve the problems of medium and low frequency air flow noise below 1500 Hz and high frequency air flow noise above 3000 Hz. Figure 8 The figure shows the comparison of the average noise reduction amount below 4000 Hz of inner mufflers with different heights. When the inner height H2 gradually increases, the average noise reduction amount also increases accordingly. Compared with the inner muffler with a uniform height, the average noise reduction amount can be increased by 3.6 dB.

[0101] In the present invention, the terms "first", "second", "third" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance; the term "plurality" means two or more, unless otherwise clearly defined. Terms such as "installed", "connected", "connected to", "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "connected" can be a direct connection or an indirect connection through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0102] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "left", "right", "front", "rear", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or unit referred to must have a specific direction, be constructed and operated in a specific orientation, and therefore cannot be construed as a limitation of the present invention.

[0103] In the description of this specification, the description of terms such as "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0104] The above is only the preferred embodiment of the present invention and is not used to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A muffler assembly, characterized in that, Comprising: A first muffler, the first muffler including a first bottom cover and a first boss structure protruding from a first side of the first bottom cover towards a second side; A second muffler, disposed on a second side of the first muffler, the second muffler including a second bottom cover and a second boss structure protruding from a first side of the second bottom cover towards a second side; The first boss structure includes a plurality of circumferentially arranged first convex portions, the first convex portion includes a first boss and a second boss, a minimum axial distance between the first boss and the first bottom cover is greater than a minimum axial distance between the second boss and the first bottom cover, and at least one first exhaust hole is provided on the second boss; The second boss structure includes a plurality of circumferentially arranged second convex portions, and at least one second exhaust hole is provided on at least one of the second convex portions; Wherein, the first bottom cover and the second bottom cover are stacked, and the first boss structure is located inside the second muffler.

2. The silencer assembly according to claim 1, characterized in that, A ratio range of a minimum axial distance between the second boss and the first bottom cover to a minimum axial distance between the first boss and the first bottom cover is 0.35 to 0.

9.

3. The silencer component according to claim 1, wherein A ratio range of an axial dimension of the first muffler to an axial dimension of the second muffler is 0.3 to 0.

76.

4. The silencer assembly according to claim 1, wherein, An opening end face of the first exhaust hole is a plane, and an included angle between a normal line of the opening end face of the first exhaust hole and a plane where the first bottom cover is located is not greater than 90°; and / or An opening end face of the second exhaust hole is a plane, and an included angle between a normal line of the opening end face of the second exhaust hole and a plane where the second bottom cover is located is not greater than 90°.

5. The silencer assembly according to any one of claims 1 to 4, characterized in that, A ratio of a total opening area of the second exhaust holes to an opening area of a bearing exhaust port communicating with the second exhaust holes is 0.5 to 1.

5.

6. The silencer assembly according to any one of claims 1 to 4, characterized in that, The first bottom cover and the first boss structure are integrally formed; and / or the second bottom cover and the second boss structure are integrally formed.

7. The silencer assembly according to any one of claims 1 to 4, characterized in that, Connection holes are provided on the first bottom cover and the second bottom cover. In a cross-section of the first bottom cover, a projection of the connection hole does not overlap with a projection of the first convex portion. In a cross-section of the second bottom cover, a projection of the connection hole does not overlap with a projection of the second convex portion.

8. The silencer assembly according to any one of claims 1 to 4, characterized in that, The second exhaust hole is provided in a second convex portion with the largest inner cavity volume among the plurality of second convex portions.

9. A compressor, characterized in that, Comprising: An upper bearing structure, the upper bearing structure including a flange portion and a cylindrical portion protruding from the flange portion, the cylindrical portion being hollow for accommodating a crankshaft; The muffler assembly according to any one of claims 1 to 8, sleeved outside the cylindrical portion.

10. The compressor according to claim 9, characterized in that, The cylindrical portion includes a first shaft portion and a second shaft portion, the first shaft portion is connected to the flange portion, and an outer diameter of the first shaft portion is greater than an outer diameter of the second shaft portion; Wherein, a minimum axial distance between the second boss and the first bottom cover is not greater than an axial dimension of the first shaft portion.

11. The compressor according to claim 10, characterized in that, The flange portion of the upper bearing structure is provided with a bearing exhaust port. When the muffler assembly is connected to the flange portion, the included angle range between the plane passing through the axis of the bearing exhaust port and the axis of the cylindrical portion and the plane passing through the axis of the first exhaust hole and the axis of the cylindrical portion is 60° to 90°.

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