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; partition plate structures matched with the structures of the first convex hull parts are arranged in the first boss structures, and partition plate exhaust holes are formed in the partition plate structures; the second boss structure comprises a plurality of second convex hull parts which are arranged in the circumferential direction, and second exhaust holes are formed in the second convex hull parts; the first bottom cover and the second bottom cover are arranged in a stacked mode, and the first boss structure is located in the second silencer. According to the technical scheme, through cooperation of the first silencer and the second silencer, under the action of the partition plate structure, multi-frequency-band noise absorption and suppression can be effectively achieved.

Description

Technical Field

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

[0002] Currently, a muffler is usually provided outside the upper bearing structure of a compressor, and the exhaust holes of the muffler 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 top exhaust process, due to the relatively low overall height of the compressor, the air flow is likely to directly blow the rotor, which may cause axial pulsating excitation, resulting in weak stability of the rotor during operation. Summary of the Invention

[0003] The present invention aims to at least solve the technical problem of 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 muffler 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 muffler assembly, including: a first muffler, the first muffler 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 muffler, disposed on the second side of the first muffler, the second muffler 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, a partition structure adapted to the structure of the plurality of first convex portions is provided in the first boss structure, partition exhaust holes are provided on the partition structure, and at least one first exhaust hole is provided on the first convex portion; 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 muffler.

[0007] According to the muffler assembly proposed by the present invention, through the cooperation of the boss structures of the inner and outer two-layer mufflers, namely the first muffler and the second muffler, a partition structure is provided in the first muffler located inside, which can effectively achieve multi-band noise absorption and suppression, especially excellent in medium and low frequency and high frequency noise control.

[0008] Specifically, the first muffler, as the inner-layer 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 a plurality of 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 the plurality of 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] It should be emphasized that the partition structure is adapted to the shape of the first convex portion to form a partition chamber, blocking the sound wave propagation path. Through partition and multiple reflections of sound waves, the sound wave attenuation is enhanced, especially for suppressing specific frequency bands of noise. By arranging the partition exhaust holes on the partition, it is used to adjust the path and speed of the air flow passing through the partition, control the air flow, avoid the generation of noise caused by the direct passage of the air flow, optimize the interaction between the air flow and the sound wave, and improve the noise reduction effect.

[0011] In some technical solutions, optionally, the ratio range of the axial distance between the partition structure and the first bottom cover to the axial dimension of the first muffler is 0.3 to 0.7.

[0012] In this technical solution, the axial distance (H1) between the partition structure and the first bottom cover, that is, the distance between the partition structure and the first bottom cover along the axial direction (usually the air flow direction) within the first boss structure, represents the installation position height of the partition in the inner-layer muffler. The axial dimension (H2) of the first muffler, that is, the length or height of the first muffler as a whole along the axial direction. By setting the ratio range of the two, that is, the ratio of H1 / H2 is 0.3 to 0.7, that is, the axial distance of the partition structure from the first bottom cover accounts for 30% to 70% of the axial dimension of the first muffler.

[0013] 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 0.6.

[0014] In this technical solution, the axial dimension of the first muffler, that is, the length or height of the inner-layer muffler (the first muffler) measured along the axial direction, and the axial dimension of the second muffler, that is, the length or height of the outer-layer muffler (the second muffler) along the axial direction. By restricting the ratio range of the two to 0.3 to 0.6, that is, the axial dimension of the inner-layer muffler is 30% to 60% of the outer-layer muffler, so this ratio ensures that the inner-layer muffler (the first muffler) has a certain size difference relative to the outer-layer muffler (the second muffler), forming a multi-level spatial layout.

[0015] In some technical solutions, optionally, the opening end face of the first exhaust hole is a flat surface, 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 flat surface, 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°.

[0016] 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 flat surface, 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 the generation of air flow disturbance and eddy current. On the one hand, by keeping the opening end face flat, the air flow passes smoothly, reducing the disturbance and eddy current of the air flow at the outlet of the exhaust hole, and reducing the noise caused by the 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 the manufacturing efficiency and assembly accuracy.

[0017] 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 hole connected to the second exhaust hole is 0.5 to 1.5.

[0018] In this technical solution, by limiting the ratio of the areas of the second exhaust hole and the bearing exhaust hole, 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 hole is the area of the bearing exhaust hole connected to the second exhaust hole. By restricting the ratio range of the two to 0.5 ≤ S / S0 ≤ 1.5, it ensures the reasonable distribution of the air flow in the exhaust path, ensuring both sufficient flow rate of the exhaust hole and avoiding excessive congestion or insufficient air flow.

[0019] 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.

[0020] In this technical solution, by integrally processing and forming the bottom cover structure and the boss structure. 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 strong.

[0021] 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.

[0022] 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 of the first bottom cover (i.e., the plane perpendicular to the axial direction), the projected area of the connection holes and the projected area of the first convex part do not intersect; similarly, in the cross-section of the second bottom cover, the projection of the connection holes does not overlap with the projection of the second convex part either. Through the above limitations, the projection of the connection holes and the convex part do not overlap, ensuring that when the air flow passes through the connection holes, 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 holes and the convex projection helps to reduce local vibration and resonance points of the structure and reduce noise amplification.

[0023] In some technical solutions, optionally, the second exhaust hole is provided in one of the second convex parts with the largest internal cavity volume among the multiple second convex parts.

[0024] For the muffler structure, the second muffler includes multiple second convex parts, and each second convex part has a certain internal cavity volume. By arranging the second exhaust hole in one of the second convex parts with the largest internal cavity volume, the relatively large cavity space can be effectively utilized, reducing the air flow resistance and discharging the gas smoothly.

[0025] 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 one of the above muffler assemblies, sleeved outside the cylindrical part.

[0026] 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 achieved. 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.

[0027] Since the compressor includes any one of the above muffler assemblies, it has the beneficial effects of any one of the above muffler assemblies, which will not be elaborated here.

[0028] In some technical solutions, optionally, a bearing exhaust hole is provided on the flange part of the upper bearing structure. When the muffler assembly is connected to the flange part, the included angle range between the plane passing through the axis of the bearing exhaust hole and the axis of the cylindrical part and the plane passing through the axis of the first exhaust hole and the axis of the cylindrical part is 60° to 90°.

[0029] By arranging the bearing exhaust hole on the flange part of the upper bearing structure, after the silencer 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 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 rationally utilizing the space.

[0032] In some technical solutions, optionally, the included angle range between the plane passing through the axis of the bearing exhaust hole and the axis of the cylinder part and the plane passing through the axis of the partition exhaust hole and the axis of the cylinder part is 270° - 330°.

[0033] This solution restricts the position of the bearing exhaust hole. The plane formed by the axis of the bearing exhaust hole and the axis of the cylinder part represents the spatial positioning of the exhaust direction of the bearing exhaust hole, and the plane formed by the axis of the partition exhaust hole and the axis of the cylinder part represents the spatial positioning of the exhaust direction of the partition exhaust hole. By restricting the included angle between the two planes to 270° - 330°, the exhaust direction of the partition exhaust hole has a certain angular deviation relative to the exhaust direction of the bearing exhaust hole, and the included angle is between 270° and 330°.

[0034] It can be understood that the included angle of 270° - 330° makes the exhaust directions of the two exhaust holes neither completely the same nor directly facing each other, avoiding the direct superposition of sound waves, reducing noise resonance and superposition effects. The included angle promotes the multi-directional scattering of sound waves between the exhaust holes, enhancing the reflection and attenuation effects of sound waves inside the silencer.

[0035] Generally speaking, by designing the included angle between the exhaust direction planes of the bearing exhaust hole and the partition exhaust hole to be 270° - 330°, effective dispersion of acoustics and air flow discharge is achieved. It not only avoids the direct superposition of sound waves and air flow, but also optimizes the structural space layout, contributing to improving the noise reduction performance and mechanical stability of the overall silencer.

[0036] The additional aspects and advantages of the present invention will become apparent in the following description section or be learned through the practice of the present invention. Brief Description of the Drawings

[0037] Figure 1 Shows a schematic structural diagram of a silencer component according to an embodiment of the present invention;

[0038] Figure 2 Shows a schematic structural diagram of a silencer component according to an embodiment of the present invention;

[0039] Figure 3 Shows a schematic structural diagram of a silencer component according to an embodiment of the present invention;

[0040] Figure 4Shows a schematic structural diagram of a muffler assembly according to an embodiment of the present invention;

[0041] Figure 5 Shows a schematic structural diagram of an upper bearing structure according to an embodiment of the present invention;

[0042] Figure 6 Shows a schematic structural diagram of a compressor according to an embodiment of the present invention;

[0043] Figure 7 Shows a schematic structural diagram of a muffler assembly according to an embodiment of the present invention;

[0044] Figure 8 Shows a schematic diagram of the relationship curve of the transmission loss of the muffler assembly in this embodiment;

[0045] Figure 9 Shows a schematic diagram of the average sound attenuation of the muffler assembly at 4000 Hz in this embodiment.

[0046] Among them, Figures 1 to 7 The corresponding relationship between the reference numerals and the component names in the figure is as follows:

[0047] 100: Muffler assembly;

[0048] 102: First muffler; 1022: First bottom cover; 1024: First boss structure; 104: First convex part; 1042: Partition structure; 1044: Partition exhaust hole; 106: First exhaust hole;

[0049] 110: Second muffler; 1122: Second bottom cover; 1124: Second boss structure; 114: Second exhaust hole; 116: Second convex part;

[0050] 122: First side; 124: Second side;

[0051] 132: Connection hole;

[0052] 200: Compressor; 202: Upper bearing structure; 2022: Flange part; 2023: Bearing exhaust hole; 2024: Cylindrical part. Detailed implementation manners

[0053] 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 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.

[0054] 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 to the limitations of the specific embodiments disclosed below.

[0055] Reference is now made to Figures 1 to 9 Describe some embodiments in accordance with the present invention.

[0056] As Figure 1 and Figure 5 As shown, the present embodiment provides a muffler assembly 100. Through the cooperation of the boss structures of the inner and outer two-layer mufflers, namely the first muffler 102 and the second muffler 110, the noise absorption and suppression in multiple frequency bands are effectively realized, especially excellent in the control of medium and low frequency and high frequency noises.

[0057] 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.

[0058] 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.

[0059] It should be emphasized that the partition structure 1042 is adapted to the shape of the first convex portion 104 to form a partition chamber, blocking the sound wave propagation path. Through the partition and multiple reflections of sound waves, the sound wave attenuation is enhanced, especially for the noise in a specific frequency band. By providing the partition exhaust holes 1044 on the partition, it is used to adjust the path and speed of the air flow passing through the partition, control the air flow, avoid the generation of noise caused by the direct passage of the air flow, optimize the interaction between the air flow and the sound wave, and improve the sound absorption effect.

[0060] The second muffler 110, as the outer-layer muffler, 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-layer structure, ensuring that the air flow passes between the outer-layer bosses. The second boss structure 1124 cooperates with the first boss structure 1024 to form an outer-layer acoustic impedance structure, reflecting and scattering the outer-layer noise.

[0061] By providing a plurality of circumferentially arranged second convex portions on the second convex platform 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.

[0062] By restricting the relative positional relationship between the first convex platform 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 convex platform structure 1024 is located inside the second muffler 110, a stepped structure of inner and outer layers is formed, effectively blocking the transmission of noise in different frequency bands. For example, the inner first convex platform structure 1024 mainly targets medium and low frequencies, while the outer second convex platform structure 1124 targets high frequencies.

[0063] 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 petal shapes of the first convex portions 104 is the same as the circumferential distribution trend of the petal shapes of the second convex portions 116; wherein, the petal shape of the first convex portion 104 provided with the first exhaust hole is the same as the petal shape of the second convex portion 116 provided with the second exhaust hole.

[0064] 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 circumferential distribution law of the petal shapes of the convex portions is also the same, that is, the circumferential distribution trend of the petal shapes is the same. It can be understood that the circumferential distribution trend of the petal shapes is the change trend of the projected area of each convex portion on the plane where the bottom cover is located, and the change trend remains consistent. On this basis, by restricting the petal shape of the first convex portion 104 provided with the first exhaust hole to be the same as the petal shape of the second convex portion 116 provided with the second exhaust hole, reasonable guidance of the air flow can be achieved.

[0065] In some embodiments, optionally, as Figure 1 and Figure 2 shown, the axial distance (H1) between the partition structure 1042 and the first bottom cover 1022, that is, the distance between the partition structure 1042 and the first bottom cover 1022 along the axial direction (usually the air flow direction) inside the first convex platform structure 1024, represents the installation position height of the partition in the inner muffler, and the axial dimension (H2) of the first muffler 102, that is, the overall length or height of the first muffler 102 along the axial direction. By controlling the ratio range of the two, that is, the ratio of H1 / H2 is between 0.3 and 0.7, that is, the axial distance from the partition structure 1042 to the first bottom cover 1022 accounts for 30% to 70% of the axial dimension of the first muffler 102.

[0066] It can be understood that the partition structure 1042 is arranged at a position slightly forward or slightly backward in the middle (within the range of 30% to 70%) of the axial dimension of the first muffler 102, which is beneficial to forming multiple acoustic impedance surfaces, increasing the reflection and absorption paths of sound waves, enabling the sound waves to have a longer propagation path before and after passing through the partition, and enhancing the multiple reflection and attenuation effects of sound waves.

[0067] If the partition structure 1042 is not too close (the ratio is too small), it can avoid the direct penetration of sound waves and affect the sound absorption effect; nor is it too far (the ratio is too large), otherwise it will weaken the acoustic function of the partition.

[0068] In some embodiments, optionally, as Figure 1 、 Figure 2 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 along the axis, and the axial dimension H3 of the second muffler 110, that is, the length or height of the outer muffler (the second muffler 110) along the axis. By restricting the ratio range of the two to 0.3 to 0.6, that is, the axial dimension of the inner muffler is 30% to 60% of the outer muffler, this ratio ensures that the inner muffler (the first muffler 102) has a certain size 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, mainly playing a role in local sound absorption and reflection, suitable for absorbing high-frequency noise and reducing the noise transmission near the exhaust port. If the ratio is large, that is, close to 0.6, the inner muffler is longer, which can form a more complex acoustic path and enhance the attenuation effect on medium and low-frequency noise.

[0070] By restricting the ratio to be between 0.3 and 0.6, it can not only ensure that the inner structure has sufficient length (to achieve effective acoustic effects), but also will not cause the structure to be 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 gas flow is smooth and uniform when passing through, reducing the generation of air flow disturbance and eddy current. On the one hand, by keeping the opening end face flat, the air flow passes smoothly, reducing the disturbance and eddy current at the outlet of the exhaust hole, and reducing the noise caused by the 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 the manufacturing efficiency and assembly accuracy.

[0072] Meanwhile, 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 limited to be between 0° and 90°. At the two extreme positions, the included angle is 0°, the opening face 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 face of the exhaust hole is perpendicular to the bottom cover plane, and the air flow is discharged vertically. By limiting 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, avoid the reverse or excessive deviation of the air flow, and thus optimize the exhaust path.

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

[0074] In some embodiments, optionally, the areas of the second exhaust hole 114 and the bearing exhaust hole 2023 are proportionally 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 hole 2023 is the area of the bearing exhaust hole 2023 connected to the second exhaust hole 114. By limiting the ratio range of the two to be 0.5 ≤ S / S0 ≤ 1.5, it is ensured that the distribution of the air flow in the exhaust path is reasonable, which not only ensures sufficient flow rate of the exhaust hole but also avoids excessive congestion or insufficient air flow.

[0075] Generally speaking, by limiting the ratio range of the two to be 0.5 to 1.5, a reasonable proportional relationship is maintained between the total opening area of the second exhaust hole 114 and the area of the bearing exhaust hole 2023, which not only ensures the exhaust flow rate but also optimizes the acoustic effect and mechanical performance.

[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, so as to ensure the integrity of the structure, eliminate bolt / welding connections, and reduce stress concentration.

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

[0078] In some embodiments, optionally, as Figure 2 and Figure 4As shown, the connecting 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. In the cross-section of the first bottom cover 1022 (i.e., the plane perpendicular to the axial direction), the projection area of the connecting hole 132 and the projection area of the first convex hull portion 104 have no intersection; similarly, in the cross-section of the second bottom cover 1122, the projection of the connecting hole 132 and the projection of the second convex hull portion do not overlap either. Through the above limitations, the projection of the connecting hole 132 and the convex hull portion do not overlap, ensuring that when the air flow passes through the connecting hole 132, it will not directly pass through the acoustic reflection area inside the convex hull, reducing acoustic interference and the complexity of the noise propagation path. In addition, avoiding the overlap of the connecting hole 132 and the convex hull 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 connecting hole 132 in the cross-sections of the first bottom cover 1022 and the second bottom cover 1122 to not overlap with the projection of the corresponding convex hull portion, 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 connecting holes 132 on the bottom cover structure as the hole positions for bolt fixation or connection to external components, the multiple connecting holes 132 are circumferentially distributed, and the convex hull portion is a raised structure on the bottom cover structure. In the cross-section projection of the bottom cover structure, the connecting hole 132 and the convex hull portion do not overlap. Further, the distance between their edges is restricted to be ≥1.5 mm to ensure no area overlap. The non-overlapping projection avoids the stress superposition between the hole edge and the convex hull 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 connecting holes 132 are distributed in the outer circle, and the convex hull portions 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 silencer structure, the second silencer includes a plurality of second convex hull portions 116, and each second convex hull portion 116 has a certain internal cavity volume. By arranging the second exhaust hole 114 in one of the second convex hull portions 116 with the largest internal cavity volume, the larger cavity space can be effectively utilized to reduce the air flow resistance, discharge the gas smoothly. In addition, the large cavity can play a role in buffering and absorbing sound waves, improving the silencing effect, reducing noise rebound and resonance, and thus helping to evenly distribute the exhaust pressure to ensure the overall performance stability of the silencer.

[0085] As Figure 5 and Figure 6 shown, an embodiment of the second aspect of the present application provides a compressor 200, including 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, forming a rigid-flexible coupling system.

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

[0087] Furthermore, as Figure 2 and Figure 5 shown, a bearing exhaust hole 2023 is provided on the flange portion 2022 of the upper bearing structure 202. After the muffler 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 the conflict or interference between the exhaust pipe and the bearing and the cylinder body, and reasonably utilizing the space.

[0088] 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 sound absorption 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 in a limited space, and avoiding the conflict between the exhaust pipe and other mechanical structures.

[0089] 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 of the bearing exhaust hole 2023 and the axis of the cylinder portion 2024 to be between 60° and 90°.

[0090] Furthermore, as Figure 4 and Figure 5The position of the second exhaust hole 114 is restricted. Specifically, the plane formed by the axis of the bearing exhaust hole 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 hole 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 hole 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 hole 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.

[0091] 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 wave scattering blind area caused by too large a difference in the exhaust hole directions, 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 hole 2023, and is beneficial to the compact utilization of the internal space of the compressor 200.

[0092] Furthermore, the included angle between the two planes is defined as 0°, that is, the two planes are coplanar, which is more conducive to the smooth exhaust.

[0093] Furthermore, as Figure 1 and Figure 5 shown, the position of the bearing exhaust hole 2023 is restricted. The plane formed by the axis of the bearing exhaust hole 2023 and the axis of the cylinder part 2024 represents the spatial positioning of the exhaust direction of the bearing exhaust hole 2023, and the plane formed by the axis of the partition exhaust hole 1044 and the axis of the cylinder part 2024 represents the spatial positioning of the exhaust direction of the partition exhaust hole 1044. By restricting the included angle θ formed by the two planes to 270° to 330°, the exhaust direction of the partition exhaust hole 1044 has a certain angular deviation relative to the exhaust direction of the bearing exhaust hole 2023, and the included angle is between 270° and 330°.

[0094] It can be understood that the included angle of 270° to 330° makes the exhaust directions of the two exhaust holes neither completely the same nor directly facing each other, avoiding the direct superposition of sound waves, reducing the noise resonance and superposition effect, and the included angle promotes the multi-directional scattering of sound waves between the exhaust holes, enhancing the reflection and attenuation effect of sound waves inside the muffler.

[0095] Generally speaking, by designing the included angle between the exhaust direction planes of the bearing exhaust hole 2023 and the partition exhaust hole 1044 to be 270° - 330°, the effective dispersion of acoustics and airflow emissions is achieved. This not only avoids the direct superposition of sound waves and airflow but also optimizes the structural space layout, contributing to improving the noise reduction performance and mechanical stability of the overall muffler.

[0096] In a specific embodiment, a double-layer muffler is provided. The muffler includes a first muffler and a second muffler, and an inner partition provided in the first muffler. The first muffler is the inner-layer muffler. The first muffler is provided with an inner partition (i.e., the partition structure), and the inner partition is provided with exhaust holes (i.e., the partition exhaust holes). The included angle between the exhaust holes and the bearing exhaust port is θ, satisfying 270° ≤ θ ≤ 330°. The height of the inner partition is H1, and the height of the first muffler is H2. The ratio of the height of the inner partition to the height of the first muffler satisfies 0.3 ≤ H1 / H2 ≤ 0.7. An exhaust outlet is provided on the first muffler. The included angle θ1 between the exhaust port and the bearing exhaust port is as Figure 7 shown, satisfying 60° ≤ θ1 ≤ 90°, and the exhaust mode is upward exhaust. A second muffler is provided outside the first muffler. The second muffler is the outer-layer muffler. The second muffler includes a plurality of convex structures. The convex structures are provided with exhaust holes. The included angle θ2 between the exhaust holes and the exhaust valve plate satisfies 0° ≤ θ2 ≤ 30°, and the exhaust mode of the exhaust holes is upward exhaust. Further, θ2 = 0°. The height of the second muffler is H3. The ratio of the height of the first muffler to the height of the second muffler satisfies 0.3 ≤ H2 / H3 ≤ 0.6. The total area S of the exhaust holes of the second muffler and the area S0 of the bearing exhaust holes satisfy 0.5 ≤ S / S0 ≤ 1.5. The design of the inner partition is beneficial to reducing high-frequency airflow noise problems below 1500 Hz and above 2500 Hz, and is beneficial to realizing the silent design of the compressor.

[0097] As Figure 8 shown, it is the transfer loss simulation curve of different positions of the exhaust holes of the inner partition of the double-layer muffler. Different hole positions opened on the inner partition (i.e., the partition structure) have a greater impact on the sound attenuation of the transfer loss. Therefore, the transfer loss simulation results of different positions of the inner partition are compared. When the included angle between the opening position of the inner partition and the bearing exhaust hole position is 270° ≤ θ ≤ 330° (i.e., Figure 8 the inner partition S5 in the figure), the sound attenuation is significantly improved at high frequencies below 1500 Hz and above 2500 Hz. In addition, the convex parts on the inner-layer muffler of the double-layer muffler are named sequentially according to the circumference. The one with the largest projected area is taken as S1, and they are named S2, S3, S4, and S5 in clockwise order according to the direction as Figure 4 shown. Similarly, for the outer-layer muffler, the one with the largest projected area is also taken as S1, and the rest are named S2, S3, S4, and S5 in clockwise order. On this basis, Figure 8The specific structures represented by the four curves are as follows: Inner layer S2 - Outer layer S1: Exhaust holes are provided on the convex part of S1 in the outer muffler, and exhaust holes are also provided on the convex part of the inner layer S2; Inner partition S3: Exhaust holes are provided within the area corresponding to S3 on the inner partition; Inner partition S4: Exhaust holes are provided within the area corresponding to S4 on the inner partition; Inner partition S5: Exhaust holes are provided within the area corresponding to S5 on the inner partition.

[0098] Figure 9 It is a comparison chart of the average sound attenuation of different exhaust positions of the inner partition. When the included angle between the opening position of the inner partition and the exhaust hole position of the bearing is 270° ≤ θ ≤ 330° (inner partition S5), the average sound attenuation at 4000 Hz increases by 2.6 dB.

[0099] In the present invention, the terms "first", "second", and "third" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance; the term "plural" means two or more, unless otherwise clearly defined. Terms such as "installed", "connected", "joined", "fixed", etc. should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "joined" 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.

[0100] 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, should not be construed as a limitation to the present invention.

[0101] 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 instance. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0102] The above are only the preferred embodiments of the present invention and are not used to limit the present invention. For those skilled in the art, the present invention can have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included within 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 first convex portions circumferentially arranged, a partition structure adapted to the structures of the plurality of first convex portions is provided inside the first boss structure, partition exhaust holes are provided on the partition structure, and at least one first exhaust hole is provided on the first convex portion; The second boss structure includes a plurality of second convex portions circumferentially arranged, 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 muffler assembly according to claim 1, wherein The ratio range of the axial distance between the partition structure and the first bottom cover to the axial dimension of the first muffler is 0.3 to 0.

7.

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

6.

4. The silencer assembly according to claim 1, characterized in that, The opening end face of the first exhaust hole is a plane, and the included 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 included 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°.

5. The silencer assembly according to any one of claims 1 to 4, characterized in that, The ratio of the total opening area of the second exhaust holes to the opening area of the bearing exhaust holes 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 the cross-section of the first bottom cover, the projection of the connection hole does not overlap with the projection of the first convex portion. 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 portion.

8. The silencer assembly according to any one of claims 1 to 4, characterized in that, The second exhaust hole is provided on the 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 is sleeved outside the cylindrical portion.

10. The compressor according to claim 9, wherein Bearing exhaust holes are provided on the flange portion of the upper bearing structure. 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 hole 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°.

11. The compressor according to claim 10, characterized in that, The included angle range between the plane passing through the axis of the bearing exhaust hole and the axis of the cylindrical portion and the plane passing through the axis of the partition exhaust hole and the axis of the cylindrical portion is 270° to 330°.

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