Silencer structure and compressor

Abstract

The embodiment of the invention provides a silencer structure and a compressor, the silencer structure comprises a bottom cover structure, the bottom cover structure comprises a first side and a second side which are opposite to each other, and the wall surface of the first side is used for abutting against a flange part of an upper bearing structure of the compressor; the boss structure is arranged on the bottom cover structure; the transition part comprises a plurality of convex hull parts which are arranged at intervals in the circumferential direction of the bottom cover structure, at least one convex hull part comprises a first boss and a second boss which have different axial distances from the bottom cover structure, and the at least one first boss and the at least one second boss are adjacently arranged in the circumferential direction of the bottom cover structure; and a first exhaust hole is formed between the adjacent first boss and second boss. According to the technical scheme, under the action of the first exhaust holes, the impact direction of the airflow can be changed, and therefore the direct blowing impact force of the high-pressure refrigerant airflow on the rotor is effectively improved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular, to a muffler structure and a compressor. Background Art

[0002] Currently, a muffler is usually arranged 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 pulsation 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 structure.

[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 structure, including: a bottom cover structure, the bottom cover structure including opposite first and second sides, the wall surface of the first side being adapted to abut against the flange portion of the upper bearing structure of the compressor; a boss structure arranged on the bottom cover structure, and the boss structure protruding in a direction from the first side of the bottom cover structure towards the second side, the boss structure including a connected end portion and a transition portion, the transition portion being connected to the bottom cover structure, and the end portion being provided with an opening adapted to the cylindrical portion of the upper bearing structure; the transition portion including a plurality of convex portions arranged at intervals along the circumferential direction of the bottom cover structure, at least one convex portion including a first boss and a second boss with different axial distances from the bottom cover structure, at least one first boss and at least one second boss being adjacent to each other in the circumferential direction of the bottom cover structure, and a first exhaust hole being formed between the adjacent first boss and second boss.

[0007] According to the muffler structure proposed by the present invention, it includes a bottom cover structure and a boss structure connected to each other. The boss structure is arranged on the second side of the bottom cover structure, and the first side of the bottom cover structure can cooperate with the upper bearing structure to realize the connection of the muffler structure. Specifically, the boss structure protrudes toward the side away from the upper bearing structure. The boss structure includes an end portion provided with an opening and a transition portion for connecting the end portion and the bottom cover structure. The transition portion is provided with a first boss and a second boss that are adjacent to each other and have different protruding heights, that is, the axial distances of the first boss and the second boss from the bottom cover structure are different, and there is a height difference between the first boss and the second boss with different protruding heights. A first exhaust hole will be formed at the junction of the two bosses. Under the action of the first exhaust hole, it is ensured that the air flow is discharged along the tangential path, changing the impact direction of the air flow, thereby effectively improving the direct blowing impact force of the high-pressure refrigerant air flow on the rotor, reducing the axial pulsating excitation borne by the rotor shafting, and enhancing the operation stability and reliability of the compressor.

[0008] By forming an exhaust area on one or more convex portions, arranging exhaust holes on some convex portions, and utilizing the spatial advantage of the convex portions, the air flow is discharged along the tangential direction, reducing the direct impact of the air flow on the rotor, reducing vibration and impact force, improving the flexibility and controllability of air flow guidance, and contributing to the delicate adjustment of noise and vibration mitigation.

[0009] It should be added that the opening of the first exhaust hole, by facing the top of the low platform and utilizing the spatial layout of the boss, guides the air flow into a tangential direction, reducing impact and vibration.

[0010] In some technical solutions, optionally, the minimum axial distance between the first boss and the bottom cover structure is not less than the maximum axial distance between the second boss and the bottom cover structure; wherein, the gas on the first side of the bottom cover structure flows from the inner wall of the first boss through the first exhaust hole to the outer wall of the second boss.

[0011] In this technical solution, by limiting the heights of the first boss and the second boss, the minimum vertical distance from the bottom of the first boss to the bottom cover structure is not less than the maximum vertical distance from the top of the second boss to the bottom cover structure, forming a stepped asymmetric boss structure.

[0012] In some technical solutions, optionally, it further includes: a second exhaust hole provided on the side wall of the one with a smaller axial distance from the bottom cover structure among the first boss and the second boss; wherein, at least one convex portion is provided with a first exhaust hole, and at least one second boss of the convex portion is provided with a second exhaust hole.

[0013] By providing a second exhaust hole on the side wall of the lower one of the first boss and the second boss, under the action of the first exhaust hole and the second exhaust hole, on the top and side wall of the lower boss respectively, it is ensured that the air flow is discharged along different paths, reducing the concentration of sound waves, changing the impact direction of the air flow, thereby effectively improving the direct blowing impact force of the high-pressure refrigerant air flow on the rotor, reducing the axial pulsating excitation borne by the rotor shafting, and enhancing the operation stability and reliability of the compressor.

[0014] Furthermore, by providing a second exhaust hole on the lower second boss, it is possible to provide a first exhaust hole and a second exhaust hole on the top and side wall of the second boss respectively, effectively reducing the direct impact on the rotor and reducing vibration and noise.

[0015] In some technical solutions, optionally, the first exhaust hole and the second exhaust hole are provided on the same convex portion.

[0016] Setting different exhaust holes (i.e., the first exhaust hole and the second exhaust hole) on the same convex portion simplifies the structural layout, facilitates manufacturing and assembly, reduces structural complexity, improves production efficiency, reduces costs, and at the same time ensures the rationality and effectiveness of the exhaust path.

[0017] In some technical solutions, optionally, the opening direction of the first exhaust hole provided on the same convex portion is the same as the opening direction of the second exhaust hole.

[0018] By restricting the opening directions of the exhaust holes on the same convex portion to be the same, enabling the two exhaust holes to discharge the air flow in the same direction, ensuring the unity and coordination of the air flow path, reducing the deflection or dispersion of the air flow during the discharge process, reducing the complexity of turbulence and noise sources, thereby enhancing the noise reduction effect.

[0019] In some technical solutions, optionally, the first exhaust holes are provided on multiple convex portions, and the opening directions of the multiple first exhaust holes are in the same circumferential direction.

[0020] By restricting the opening directions of the first exhaust holes on multiple convex portions to be in the same circumferential direction, forming a consistent exhaust path, it helps to reduce the deflection and turbulence of the air flow during the discharge process, reduce the sound wave interference, and improve the noise reduction effect.

[0021] In some technical solutions, optionally, 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 and the plane where the bottom cover structure is located is not greater than 45°.

[0022] In this technical solution, by restricting the opening end face of the first exhaust hole to be a plane and restricting the opening direction of the first exhaust hole, that is, the included angle between the opening end face and the plane where the bottom cover structure is located, the tangential momentum can be strengthened, the broadband noise can be suppressed, especially the secondary noise energy can be weakened, and the energy efficiency of the compressor can be improved.

[0023] In some technical solutions, optionally, it further includes: a diversion groove provided on the second boss; wherein one end of the diversion groove extends to the first exhaust hole.

[0024] In this technical solution, by providing a diversion groove on the second boss, one end of the diversion groove is seamlessly connected to the outlet edge of the first exhaust hole, and the other end extends towards the end of the second boss. Through coupling with the first exhaust hole, that is, the inlet end face of the diversion groove is coplanar with the outlet of the first exhaust hole or there is a small excessive misalignment, a continuous diversion channel is formed.

[0025] In some technical solutions, optionally, the ratio of the total opening area of the first exhaust hole and the second exhaust hole to the opening area of the opening is 0.5 - 2.5.

[0026] In this technical solution, by limiting the ratio of the total opening area of the exhaust holes to the opening area of the opening, the total opening area is the sum of the opening areas of all the first exhaust holes and all the second exhaust holes, and the opening area of the opening is the upper bearing exhaust hole. By restricting the ratio of the total opening area of the exhaust holes to the opening area of the opening to be between 0.5 and 2.5, the balance of air flow distribution and system back pressure can be ensured.

[0027] In some technical solutions, optionally, in the axial direction of the opening, the minimum distance between the first exhaust hole and the wall surface of the second side of the bottom cover structure is not less than 1 / 3 of the maximum distance between the end and the wall surface of the first side of the bottom cover structure.

[0028] In this technical solution, by restricting the lower edge height of the first exhaust hole, that is, the axial distance constraint, wherein the maximum axial distance from the end (the top of the boss) to the first side (the contact surface between the bottom cover and the bearing flange), that is, the total height H of the boss, and H1 is the minimum axial distance from the first exhaust hole to the second side (the mating surface between the bottom cover and the compressor housing). By restricting H1 ≥ 1 / 3H, it is ensured that after the air flow is discharged from the first exhaust hole, there is enough space (≥ H / 3) to complete expansion and deceleration before reaching the second side, avoiding shock noise; at the same time, it also prolongs the residence time of the air flow in the silencing chamber and increases the proportion of tangential momentum.

[0029] In some technical solutions, optionally, in the cross-section of the bottom cover structure, the projection of the outer edge of the bottom cover structure is circular, and the projection of the inner edge of the opening is circular; wherein the maximum dimension of the first exhaust hole in the radial direction of the bottom cover structure is not greater than the difference between the radius of the bottom cover structure and the radius of the opening.

[0030] In this technical solution, the bottom cover structure is disc-shaped, and the opening provided at the end is also a circular hole. By restricting the radial dimension of the first exhaust hole, B ≤ R1 - R2, where the radius of the outer circle of the bottom cover structure is R1, that is, the circular projection radius of the outer edge of the bottom cover structure; the radius of the inner circle of the opening is R2, that is, the circular projection radius of the central opening (for bearing fit) of the bottom cover structure; the maximum radial dimension of the first exhaust hole is B, that is, the maximum span of the exhaust hole in the radial direction of the bottom cover (such as the diameter of a circular hole, the width of a rectangular hole, etc.). Through the above restrictions, the first exhaust hole can be ensured not to exceed the annular area of the bottom cover, and the minimum distance from the edge of the exhaust hole to the outer circle of the bottom cover is not less than (R1 - R2 - B) / 2, preventing cracks from occurring during stamping or casting; at the same time, an annular area is reserved.

[0031] In some technical solutions, optionally, the bottom cover structure and the boss structure are integrally formed.

[0032] In this technical solution, by integrally processing and forming the bottom cover structure and the boss structure, the integrity of the structure can be guaranteed, bolt / welding connections can be eliminated, and stress concentration can be reduced; 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.

[0033] In some technical solutions, optionally, the plane where the end is located is parallel to the plane where the bottom cover structure is located or the included angle is less than a preset angle.

[0034] In this technical solution, by defining the surface of the end of the muffler structure and the bottom cover structure, that is, the end plane is parallel / small included angle design with the bottom cover plane. When the parallel design is adopted, it is ensured that the jet direction of the exhaust hole is strictly parallel to the bottom cover plane, the tangential velocity component accounts for a relatively high proportion, the axial impact is reduced, there is no sudden change in the flow channel, and the total pressure loss is small. In addition, the parallel planes eliminate the obliquely reflected sound waves in the cavity and reduce the standing wave energy.

[0035] In some technical solutions, optionally, connection holes are provided on the bottom cover structure, and in the cross-section of the bottom cover structure, the projection of the connection holes does not overlap with the projection of the convex part.

[0036] In this technical solution, by providing connection holes on the bottom cover structure as the hole positions for bolt fixation or connection with external components, multiple connection holes are circumferentially distributed, and the convex part is a convex structure on the bottom cover structure. In the cross-section projection of the bottom cover structure, the connection holes do 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 the stress superposition between the hole edge and the root of the convex part, reduces the maximum stress, and also improves the fatigue life.

[0037] 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 portion and a cylindrical portion protruding from the flange portion, and the cylindrical portion is hollow for accommodating a crankshaft; any one of the above muffler structures, sleeved outside the cylindrical portion.

[0038] The compressor provided according to the present application includes an upper bearing structure and a muffler structure. By integrating the muffler structure with the upper bearing structure, the synergistic improvement of aerodynamic performance, noise reduction effect and mechanical reliability is achieved. The upper bearing structure includes a flange portion and a cylindrical portion, which is used to support the crankshaft and transmit loads. The muffler structure is fixed to the flange portion by bolts to form a rigid-flexible coupling system.

[0039] Since the compressor includes any one of the above muffler structures, it has the beneficial effects of any one of the above muffler structures, which will not be elaborated here.

[0040] In some technical solutions, optionally, the wall surface on the first side of the muffler structure is in surface contact with the flange portion of the upper bearing structure.

[0041] In this technical solution, by making the wall surface on the first side of the muffler structure in surface contact with the flange portion of the upper bearing structure, the amplitude of the vibration transfer function can be reduced, and at the same time, the axial vibration of the rotor can also be reduced.

[0042] The additional aspects and advantages of the present invention will become apparent in the following description section or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Figure 1 The structural schematic diagram of the muffler structure according to an embodiment of the present invention is shown;

[0044] Figure 2 The structural schematic diagram of the muffler structure according to an embodiment of the present invention is shown;

[0045] Figure 3 The structural schematic diagram of the muffler structure according to an embodiment of the present invention is shown;

[0046] Figure 4 The structural schematic diagram of the muffler structure according to an embodiment of the present invention is shown;

[0047] Figure 5 The structural schematic diagram of the muffler structure according to an embodiment of the present invention is shown;

[0048] Figure 6 The structural schematic diagram of the muffler structure according to an embodiment of the present invention is shown;

[0049] Figure 7 The structural schematic diagram of the compressor according to an embodiment of the present invention is shown;

[0050] Figure 8 The structural schematic diagram of a compressor according to an embodiment of the present invention is shown.

[0051] Wherein, Figures 1 to 8 The corresponding relationship between the reference numerals and the component names in the figure is as follows:

[0052] 100: muffler structure; 102: bottom cover structure; 1022: first side; 1024: second side; 103: connecting hole; 104: boss structure; 1042: end; 1044: transition part; 1046: opening; 1048: convex part; 1052: first boss; 1054: second boss; 106: first exhaust hole; 1082: diversion groove; 110: second exhaust hole;

[0053] 200: compressor; 202: upper bearing structure; 2022: flange part; 2024: cylinder part. Specific embodiments

[0054] In order 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 embodiments. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments may be combined with each other.

[0055] Many specific details are set forth in the following description in order to provide a thorough understanding of the present application. However, the embodiments of the present invention may be implemented 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.

[0056] The following refers to Figures 1 to 8 Describe some embodiments according to the present invention.

[0057] As Figure 1 and Figure 8 shown, this embodiment provides a muffler structure 100, including a connected bottom cover structure 102 and a boss structure 104, as Figure 4As shown, the boss structure 104 is provided on the second side 1024 of the bottom cover structure 102. The first side 1022 of the bottom cover structure 102 can cooperate with the upper bearing structure 202 to achieve the connection of the silencer structure 100. Specifically, the boss structure 104 protrudes toward the side away from the upper bearing structure 202. The boss structure 104 includes an end 1042 provided with an opening 1046, and a transition portion 1044 for connecting the end 1042 and the bottom cover structure 102. A plurality of boss portions 1048 are provided on the transition portion 1044. At least one boss portion 1048 is provided with a first exhaust hole 106. Since the first exhaust hole 106 is formed by a first boss 1052 and a second boss 1054, at least one boss portion 1048 includes a first boss 1052 and a second boss 1054. The first boss 1052 and the second boss 1054 with different protruding heights are arranged adjacent to each other, that is, the axial distances of the first boss 1052 and the second boss 1054 from the bottom cover structure 102 are different. There is a height difference between the first boss 1052 and the second boss 1054 with different protruding heights. A first exhaust hole 106 will be formed at the junction of the two bosses. Under the action of the first exhaust hole 106, it is ensured that the air flow is discharged along the tangential path, changing the impact direction of the air flow, so as to effectively improve the direct blowing impact force of the high-pressure refrigerant air flow on the rotor, reduce the axial pulsating excitation borne by the rotor shafting, and improve the operation stability and reliability of the compressor.

[0058] It should be added that the opening of the first exhaust hole 106 guides the air flow into a tangential direction by facing the top or side wall of the low platform, taking advantage of the spatial layout of the boss, reducing the impact and vibration.

[0059] Among them, the bottom cover structure 102 abuts against the flange portion 2022 of the upper bearing structure 202 through the wall surface of the first side 1022. After connection, rigid sealing can be achieved to prevent high-pressure refrigerant from leaking into the bearing cavity. The wall surface of the second side 1024 has a clearance fit with the housing of the compressor 200 to compensate for the difference in thermal expansion and avoid structural jamming at high temperatures.

[0060] The boss structure 104 is mainly used for air flow guidance. The opening 1046 located at the end 1042 is adapted to the cylindrical portion 2024 of the upper bearing structure 202, so that the silencer structure 100 and the upper bearing structure 202 are relatively stationary, eliminating the relative displacement caused by rotational speed fluctuations and reducing frictional abnormal sounds.

[0061] For the first boss 1052 and the second boss 1054, the first boss 1052 serves as the main air flow guiding surface, and the second boss 1054 serves as the reflecting surface. An acoustic impedance mutation region is formed through the height difference to reflect specific frequency sound waves, thereby reducing the air flow velocity and turbulence.

[0062] Furthermore, micro-vortex grooves can be provided on the surface of the first boss 1052 to induce the airflow to form Coanda effect wall attachment flow.

[0063] The first exhaust hole 106 is located at the misaligned joint of adjacent high and low bosses, and can tangentially guide the airflow under the action of the first exhaust hole 106, avoiding the refrigerant directly hitting the main housing of the compressor 200 to form standing wave resonance and reducing secondary noise.

[0064] Furthermore, the hole shape of the first exhaust hole 106 is a converging-diverging Laval nozzle, and the exhaust direction forms an angle of 45° ± 5° with the center line of the muffler.

[0065] In some embodiments, optionally, the boss structure 104 includes a plurality of boss portions 1048, and a first exhaust hole 106 is provided on at least one boss portion 1048. Since the first exhaust hole 106 is formed by the first boss 1052 and the second boss 1054, at least one boss portion 1048 includes a first boss 1052 and a second boss 1054. By providing the first exhaust hole 106 on one or more boss portions 1048, the dispersion of the airflow can be achieved during exhaust, thereby improving the operating stability of the compressor 200.

[0066] It should be added that by uniformly arranging a plurality of boss portions 1048 in the circumferential direction of the bottom cover structure 102, an exhaust area is formed on one or more boss portions 1048, and exhaust holes are provided on some of the boss portions 1048. Utilizing the spatial advantage of the bosses, the airflow is discharged along the tangential direction, reducing the airflow directly hitting the rotor, lowering vibration and impact force, improving the flexibility and controllability of the airflow guiding, and contributing to the delicate adjustment of the reduction of noise and vibration.

[0067] In addition, by providing a second exhaust hole 110 on the lower second boss 1054 of the boss portion 1048, an additional exhaust path is provided. The multi-path exhaust enhances the dispersion of the airflow, helps to reduce local pressure concentration, reduces noise and vibration, and simultaneously improves the refrigerant discharge path.

[0068] Generally speaking, the present solution makes full use of the multi-point and multi-angle exhaust strategy of the space, effectively disperses the airflow, reduces the superposition and resonance of sound waves, and improves the noise reduction effect. At the same time, the arrangement of multiple exhaust holes also helps the smooth guiding of the airflow, reduces the impact of directly hitting the rotor, and improves the vibration and energy efficiency performance.

[0069] Furthermore, a first exhaust hole 106 is provided on one boss portion 1048, and a first exhaust hole 106 can be provided on some of the plurality of boss portions 1048.

[0070] It can be understood that the convex hull parts 1048 are independent convex units distributed at intervals along the circumferential direction of the bottom cover structure 102, and each convex hull part 1048 includes a combined structure of a first convex platform 1052 and a second convex platform 1054.

[0071] The spacing angle between adjacent convex hull parts 1048 is θ = 360° / N (N is the total number of convex hulls). For example, when N = 6, θ = 60°, forming a periodic asymmetric layout.

[0072] Generally speaking, the muffler structure 100 provided by the present application ensures the comprehensive goals of noise reduction, vibration reduction, and efficiency improvement in a compact space through the hierarchical diversion of the high and low convex platforms and the tangential exhaust direction of the first exhaust hole 106.

[0073] In some embodiments, optionally, by limiting the heights of the first convex platform 1052 and the second convex platform 1054, the minimum vertical distance from the bottom of the first convex platform 1052 to the bottom cover structure 102 is not less than the maximum vertical distance from the top of the second convex platform 1054 to the bottom cover structure, forming a stepped asymmetric convex platform structure 104. On this basis, by providing a second exhaust hole 110 on the lower second convex platform 1054, the first exhaust hole 106 and the second exhaust hole 110 can be respectively provided on the top and side wall of the second convex platform 1054, which can effectively reduce the direct impact on the rotor and reduce vibration and noise.

[0074] The path of the gas during flow is as follows: high-pressure gas on the first side 1022 of the bottom cover structure 102 → the inner wall (diversion surface) of the first convex platform 1052 → the first exhaust hole 106 (main jet) → the outer wall (reflection surface) of the second convex platform 1054 → enter the cavity of the compressor 200.

[0075] Among them, the inner wall of the first convex platform 1052 can be used as a gas acceleration area, the first exhaust hole 106 can be used as a supersonic jet throat, and the outer wall of the second convex platform 1054 can be used as an impact diffusion and vortex generation area.

[0076] When the gas flows from the first convex platform 1052 to the second convex platform 1054, the flow cross-sectional area suddenly increases. According to Bernoulli's principle, the flow velocity can be reduced, and at the same time, the static pressure is restored to reduce the total pressure loss.

[0077] When the jet of the first exhaust hole 106 impacts the outer wall of the second convex platform 1054, broadband noise is excited.

[0078] The height difference between the high and low convex platforms causes a time difference in the arrival of the gas flow pulse at the rotor, which can destroy the coherence of specific orders, such as the 4th and 8th order noises, to reduce the fundamental frequency amplitude.

[0079] In some embodiments, optionally, a second exhaust hole is provided on the side wall of the lower one of the first boss 1052 and the second boss 1054. Under the action of the first exhaust hole 106 and the second exhaust hole, respectively at the top and the side wall of the lower boss, it is ensured that the air flow is discharged along different paths, reducing the concentration of sound waves, changing the impact direction of the air flow, thus effectively improving the direct blowing impact force of the high-pressure refrigerant flow on the rotor, reducing the axial pulsating excitation borne by the rotor shafting, and enhancing the operation stability and reliability of the compressor.

[0080] In some embodiments, optionally, different exhaust holes (i.e., the first exhaust hole 106 and the second exhaust hole 110) are provided in the same convex part 1048, simplifying the structural layout, facilitating manufacturing and assembly, reducing structural complexity, improving production efficiency, reducing costs, and at the same time ensuring the rationality and effectiveness of the exhaust path.

[0081] In addition, by providing multiple exhaust holes on the same convex part 1048, through reasonable layout, the air flow can be discharged along different angles or paths, reducing air flow impact and turbulence, improving the distribution and uniformity of the air flow, reducing the source of noise generation, and enhancing the noise reduction effect.

[0082] It should be emphasized that arranging multiple exhaust holes on the same convex part 1048 can release the air flow at different positions simultaneously, reducing the superposition and reflection of sound waves, thereby reducing the sound pressure level, enhancing the noise reduction ability, and improving the noise problem in a specific frequency band.

[0083] Generally speaking, by providing multiple exhaust holes on the same convex part, different exhaust angles (such as along the tangent, lateral, etc.) can be designed to adjust the direction of the air flow, reduce the impact on the rotor and the shafting, reduce vibration and axial pulsation, and improve the operation smoothness and reliability of the compressor.

[0084] In some embodiments, optionally, by restricting the opening directions of the exhaust holes located on the same convex part 1048 to be the same, the two exhaust holes discharge the air flow along the same direction, ensuring the unity and coordination of the air flow path, reducing the deflection or dispersion of the air flow during the discharge process, reducing the complexity of turbulence and noise sources, and thus enhancing the noise reduction effect.

[0085] It can be understood that the unified exhaust direction contributes to the coherent superposition of sound waves, avoiding resonance or noise amplification caused by the mutual interference of sound waves in different directions, improving the frequency response of the noise, especially achieving more significant noise suppression in the target frequency band (for example, 500 Hz to 3150 Hz).

[0086] The same opening direction facilitates the discharge of the air flow along a predetermined path, reducing the turbulence and pressure fluctuation of the air flow near the exhaust hole, reducing the vibration and rotor impact force caused by the air flow, and improving the operation smoothness of the compressor.

[0087] In some embodiments, optionally, the opening directions of the first exhaust holes 106 on the plurality of convex hull portions are restricted to the same circumferential direction, forming a consistent exhaust path, which helps to reduce the deflection and turbulence of the air flow during the exhaust process, reduce the acoustic wave interference, and improve the noise reduction effect.

[0088] The air flow is discharged along the same circumferential direction, so that the air flow is smoothly discharged along a predetermined path, reducing turbulence and pressure fluctuations, reducing vibration and impact force, reducing the axial pulsation of the rotor shafting, and improving the stability and reliability of the system.

[0089] In some embodiments, optionally, the opening end face of the first exhaust hole 106 is restricted to be a plane, and the opening direction of the first exhaust hole 106, that is, the included angle between the opening end face and the plane where the bottom cover structure 102 is located, can strengthen the tangential momentum and broadband noise suppression, especially weaken the secondary noise energy, and improve the energy efficiency of the compressor 200.

[0090] Furthermore, the outlet section of the first exhaust hole 106 is a flat geometric surface (not a curved surface or a stepped shape), and the included angle between the normal line of the opening end face and the plane of the bottom cover structure 102 is ≤ 45°, and the normal line points to the air flow discharge direction.

[0091] It can be understood that the flat end face and the outer wall of the second boss 1054 form a sharp-edge guiding structure, and the Coanda effect is used to make the high-speed air flow flow closely along the wall surface, thereby increasing the proportion of the tangential velocity component.

[0092] When the included angle is 45°, the normal velocity component and the tangential velocity component of the air flow are the same, and at this time, the proportion of the tangential momentum reaches 50%.

[0093] By restricting the included angle ≤ 45°, it is ensured that the air flow direction deviates from the rotor axis (the offset angle ≥ 45°), the axial impact force is reduced, the air flow impact energy density is reduced, and the secondary noise is reduced.

[0094] In some embodiments, optionally, a flow guiding groove 1082 is provided on the second boss 1054. One end of the flow guiding groove 1082 is seamlessly connected to the outlet edge of the first exhaust hole 106, and the other end extends to the end of the second boss 1054. Through the coupling with the first exhaust hole 106, that is, the inlet end face of the flow guiding groove 1082 and the outlet of the first exhaust hole 106 are coplanar or there is a small excessive misalignment, a continuous flow guiding channel is formed.

[0095] The high-pressure gas is accelerated by the first exhaust hole 106, and secondary regulation can be achieved under the action of the flow guiding groove 1082. The specific regulation is achieved through the shape of the flow guiding groove 1082. For example, the groove width is tapered to increase the flow velocity, and the curvature is used to induce swirl to form a spiral flow. Further, micro-grooves can be provided on the groove wall to reduce the turbulence intensity and pressure loss.

[0096] It can be understood that by setting the flow guiding groove 1082, the airflow path can be extended, so that the time for the airflow of adjacent exhaust holes to reach the rotor is different.

[0097] In some embodiments, optionally, as Figure 2 and Figure 3 shown, one or more second exhaust holes 110 are arranged on the surface of the flow guiding groove 1082. Specifically, as Figure 2 shown, a plurality of second exhaust holes 110 can be distributed along the groove length direction of the flow guiding groove 1082. Under the action of the second exhaust holes 110, secondary exhaust can be realized. The gas flow rate flowing out through the second exhaust holes 110 is relatively low, which can supplement the tangential momentum and avoid flow separation.

[0098] In the case of setting one second exhaust hole 110, as Figure 3 shown, the second exhaust hole 110 is a round hole.

[0099] It can be understood that the outlet jet of the second exhaust hole 110 forms a velocity difference with the main air flow, generating shear layer instability and breaking large-scale vortices into small vortices, thereby reducing the turbulent noise energy.

[0100] Furthermore, the included angle between the axis of the second exhaust hole 110 and the normal line of the bottom surface of the flow guiding groove 1082 is 10° - 30°, guiding the air flow to diffuse downstream. The inlet end of the second exhaust hole 110 is smoothly transitioned with the curved surface of the flow guiding groove 1082, and the outlet end is communicated with the cavity of the compressor 200.

[0101] In some embodiments, optionally, the hole area of the first exhaust hole 106 and the total opening area of the second exhaust holes 110 located on the same convex hull part 1048 are limited. The hole area of the first exhaust hole 106 is the effective flow area of a single first exhaust hole 106, usually rectangular or quasi-elliptical. The total opening area of the second exhaust holes 110 is the sum of the areas of all the second exhaust holes 110 on the flow guiding groove 1082, usually multiple holes. By restricting the hole area of the first exhaust hole 106 to be larger than the total opening area of the second exhaust holes 110, most of the air flow is discharged through the larger first exhaust hole 106, and a small part of the air flow is discharged through the smaller second exhaust holes 110. The large area of the first exhaust hole 106 reduces the jet dynamic pressure and also reduces the vibration acceleration of the shell surface. The second exhaust holes 110 avoid local stress concentration through a porous layout and extend the fatigue life of the shell.

[0102] Furthermore, the ratio of the hole area of the first exhaust hole 106 to the total opening area of the second exhaust holes 110 is between 1.5 and 3.0. If the ratio is too low, the proportion of the secondary air flow is too high, the tangential momentum is insufficient, and the rotor vibration increases. If the ratio is too high, the risk of main air flow congestion rises and the pressure loss increases.

[0103] The hole shape of the first exhaust hole 106 is preferably rectangular or quasi-elliptical to suppress flow separation; the hole shape of the second exhaust hole 110 can be strip-shaped or circular to improve the directivity of the low-speed air flow.

[0104] In some embodiments, optionally, the ratio of the total opening area of the exhaust holes to the opening area of the opening 1046 is limited. The total opening area is the sum of the opening areas of all the first exhaust holes 106 and all the second exhaust holes 110, and the opening area of the opening 1046 is the upper bearing exhaust hole. By restricting the ratio of the total opening area of the exhaust holes to the opening area of the opening 1046 to be between 0.5 and 2.5, the balance of air flow distribution and system back pressure can be ensured.

[0105] It can be understood that if the ratio is too small, less than 0.5, the exhaust area is insufficient and the back pressure increases, which will increase the power consumption of the compressor 200. If the ratio is too large, greater than 2.5, the flow velocity is insufficient, the low flow velocity leads to the thickening of the boundary layer and a large turbulence intensity, increasing the pressure loss.

[0106] In some embodiments, optionally, when only the first exhaust holes 106 are provided, by limiting the ratio of the total opening area of all the first exhaust holes 106 to the opening area of the opening 1046, and restricting the ratio of the total opening area of the exhaust holes to the opening area of the opening 1046 to be between 0.5 and 2.5, the balance of air flow distribution and system back pressure can be ensured.

[0107] It can be understood that if the ratio is too small, less than 0.5, the exhaust area is insufficient and the back pressure increases, which will increase the power consumption of the compressor 200. If the ratio is too large, greater than 2.5, the flow velocity is insufficient, the low flow velocity leads to the thickening of the boundary layer and a large turbulence intensity, increasing the pressure loss.

[0108] When the rotational speed corresponding to the main operating conditions of the compressor 200 is a high rotational speed, for example, greater than 6000 rpm, the ratio can be controlled between 0.8 and 1.2 to suppress high-frequency noise; when the rotational speed corresponding to the main operating conditions of the compressor 200 is a low rotational speed, for example, less than 3000 rpm, the ratio can be controlled between 1.5 and 2.0 to enhance low-frequency sound absorption.

[0109] In some embodiments, optionally, as Figure 5As shown in the figure, the height of the lower edge of the first exhaust hole 106 is restricted, that is, the axial distance is constrained. Among them, the maximum axial distance from the end 1042 (the top of the boss) to the first side 1022 (the contact surface between the bottom cover and the bearing flange), that is, the total height H of the boss, and H1 is the minimum axial distance from the first exhaust hole 106 to the second side 1024 (the mating surface between the bottom cover and the compressor 200 housing). By restricting H1≥1 / 3H, it is ensured that after the air flow is discharged from the first exhaust hole 106, there is enough space (≥H / 3) to complete expansion and deceleration before reaching the second side 1024, avoiding shock wave noise; at the same time, it also prolongs the residence time of the air flow in the sound-absorbing cavity and increases the proportion of tangential momentum.

[0110] If the distance is too small, that is, when H1<H / 3, the high-speed air flow directly impacts the wall surface of the second side 1024, and the turbulence intensity will increase. If the distance is too large, the first-order standing wave frequency is lower than 500 Hz, avoiding the main noise frequency band (500 Hz - 4000 Hz), and weakening the noise reduction effect;

[0111] Furthermore, when applied to a short compressor 200, for example, H = 6 mm and H1≥2 mm, a micro-hole array (hole diameter ≤1 mm) needs to be used to maintain the flow rate; when applied to a tall compressor 200, for example, H = 18 mm and H1≥6 mm, a single large hole can be set to optimize the processability.

[0112] In some embodiments, optionally, the bottom cover structure 102 is in a disc shape, and the opening 1046 provided at the end 1042 is also a circular hole. By restricting the radial dimension of the first exhaust hole 106, as Figure 5 and Figure 6 shown, B≤R1 - R2, where, the radius of the outer circle of the bottom cover structure 102 is R1, that is, the circular projection radius of the outer edge of the bottom cover structure 102; the radius of the inner circle of the opening 1046 is R2, that is, the circular projection radius of the central opening 1046 (mating with the bearing) of the bottom cover structure 102; the maximum radial dimension of the first exhaust hole 106 is B, that is, the maximum span of the exhaust hole in the radial direction of the bottom cover (such as the diameter of a circular hole, the width of a rectangular hole, etc.). Through the above restrictions, it can be ensured that the first exhaust hole 106 does not exceed the annular area of the bottom cover, ensuring that the minimum distance from the edge of the exhaust hole to the outer circle of the bottom cover is ≥(R1 - R2 - B) / 2, preventing cracks during stamping or casting; at the same time, an annular area is reserved.

[0113] It should be added that the radial span of the first exhaust hole 106 is restricted, forcing the air flow to be discharged tangentially, reducing the risk of directly blowing the rotor, increasing the proportion of tangential momentum, and reducing the axial vibration of the rotor.

[0114] In some embodiments, optionally, the bottom cover structure 102 and the boss structure 104 are integrally processed and formed, which can ensure the integrity of the structure, eliminate bolt / welding connections, and reduce 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.

[0115] Further, the first exhaust hole 106 is synchronously blanked with the bottom cover by using a punching process.

[0116] In some embodiments, optionally, the end 1042 of the silencer structure 100 and the surface of the bottom cover structure 102 are defined, that is, the end 1042 plane is parallel / a small included angle design with the bottom cover plane. When the parallel design is adopted, it is ensured that the jet direction of the exhaust hole is strictly parallel to the bottom cover plane, the tangential velocity component accounts for a relatively high proportion, the axial impact is reduced, there is no sudden change in the flow channel, and the total pressure loss is small. In addition, the parallel planes eliminate the obliquely reflected sound waves in the cavity and reduce the standing wave energy.

[0117] When the small included angle design is adopted, the slight inclination can induce the air flow to spiral upward, prolong the residence time, and improve the heat exchange efficiency; at the same time, the small included angle design destroys the symmetry, and the OA value of the broadband noise is additionally reduced.

[0118] In some embodiments, optionally, connection holes 103 are provided on the bottom cover structure 102 as hole positions for bolt fixation or connection with external components. The plurality of connection holes 103 are circumferentially distributed, and the convex part 1048 is a raised structure on the bottom cover structure 102. In the cross-sectional projection of the bottom cover structure 102, the connection holes 103 do not overlap with the convex part 1048. 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 root, reduces the maximum stress, and also improves the fatigue life.

[0119] 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.

[0120] Among them, the connection holes 103 are distributed in the outer circle, and the convex part 1048 is concentrated in the inner circle, with a radial distance to avoid projection interference.

[0121] Further, the connection holes 103 and the convex part 1048 are not in the same radial direction.

[0122] Such as Figure 7 and Figure 8As shown in the figure, an embodiment of the second aspect of the present application provides a compressor 200, which includes an upper bearing structure 202 and a muffler structure 100. By integrating the muffler structure 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 structure 100 is fixed to the flange portion 2022 by bolts to form a rigid-flexible coupling system.

[0123] Since the compressor 200 includes any one of the above muffler structures 100, it has the beneficial effects of any one of the above muffler structures 100, which will not be elaborated here.

[0124] Furthermore, by making the wall surface of the first side 1022 of the muffler structure 100 in surface contact with the flange portion 2022 surface of the upper bearing structure 202, the amplitude of the vibration transfer function can be reduced, and at the same time, the axial vibration of the rotor can also be reduced.

[0125] In a specific embodiment, a muffler structure for a compressor is provided. The muffler is an exhaust noise reduction structure for a rotary compressor, and the upper bearing and the muffler are fixed by bolts. Among them, the muffler housing is a convex structure, which forms a muffler cavity inside; the muffler bottom cover (i.e., the bottom cover structure 102), on which several bolt holes (i.e., connection holes 103) are provided; the muffler top cover (i.e., the boss structure 104); the bearing mating hole (i.e., the opening 1046); the top cover and the bottom cover are connected to form a similar convex structure; the muffler diversion groove 1082 is a platform structure formed when processing exhaust holes by stamping, casting, etc., and its upper edge is connected to the lower edge of the muffler exhaust hole (i.e., the first exhaust hole 106); exhaust holes are provided on the side of the convex part at the top of the muffler. The exhaust holes include a first exhaust hole 106, which is arranged on the side of a high platform (i.e., the first boss 1052), and the first exhaust hole 106 blows air towards the top of a low platform (i.e., the second boss 1054); the exhaust holes include a second exhaust hole 110, which is arranged on the side of the low platform, and the number N1≥1.

[0126] Such as Figure 1 、 Figure 4 、 Figure 5 and Figure 6As shown in the figure, exhaust holes are provided on the side of the convex hull at the top of the silencer; the exhaust holes include a first exhaust hole 106, the convex hull includes a high-low platform, the first exhaust hole 106 is provided on the side of the high platform, and the first exhaust hole 106 blows air towards the top of the low platform; a flow guiding groove 1082 is provided on the top of the low platform; the exhaust holes include a second exhaust hole 110, the second exhaust hole 110 is provided on the side of the low platform, and the number N2 of the second exhaust holes 110 is N2≥1; the number of convex hulls (i.e., convex hull part 1048) is multiple, and exhaust holes are provided on at least one convex hull; the overall height H of the silencer satisfies 2≤H≤30mm, and the height H1 of the lower edge of the exhaust hole from the bottom cover satisfies H1≥1 / 3H; the total area S of the exhaust holes of the silencer and the area S0 of the bearing exhaust holes satisfy 0.5≤S / S0≤2.5; the ratio of the area S1 of the first exhaust hole to the area S2 of the second exhaust hole of each convex hull satisfies S1 / S2>1; as Figure 6 As shown in the figure, the position of the exhaust hole of the silencer is located at the junction of the top surface and the bottom cover, and the angle α between the normal line of the exhaust hole and the center connection line of the silencer satisfies 0°<α<180°; the width B of the first exhaust hole of the silencer satisfies B≤the radius R1 of the silencer - the radius R2 of the mating hole; the number N1 of the petal types of the silencer in the radial direction is N1≥1, and the angle between the exhaust holes satisfies α1>0°; the angle α2 between the normal line of the first exhaust hole of the convex hull of the silencer and the horizontal line satisfies -45°≤α2≤45°; the shape of the exhaust hole of the silencer can be but is not limited to: square, quasi-elliptical, circular, crescent-shaped, etc.

[0127] Through the above specific embodiments, the noise in the frequency band of 500Hz to 3150Hz can be effectively improved, and the overall OA value is improved by more than 3dB; the tangential exhaust can improve the impact force of the direct blowing on the rotor, and the overall axial vibration is improved significantly; the discharged refrigerant is filtered through the motor winding, which can improve the problem of the deterioration of the direct blowing of the refrigerant and oil spill; due to the change in the flow direction of the discharged refrigerant, the heat dissipation efficiency of the motor is improved and the energy efficiency is increased; compared with the conventional radial side exhaust, the problem of secondary noise generated by the direct impact on the main housing can be improved, and the flow-induced noise of the secondary disturbance of the motor rotor to the high-pressure exhaust refrigerant can be reduced.

[0128] In addition, the silencer of this embodiment can improve the uniformity of the air flow distribution and the tangential exhaust efficiency, and improve the problem of noise deterioration caused by the gas impact force.

[0129] Specifically, the air flow direction of the silencer is optimized to the tangential direction, so as to effectively improve the direct blowing impact force of the high-pressure refrigerant air flow on the rotor and reduce the axial pulsating excitation borne by the rotor shafting. This design scheme can not only significantly improve the operation stability and reliability of the compressor, but also has the characteristics of simple implementation and strong process compatibility, and can achieve high-efficiency noise reduction and performance optimization without increasing additional manufacturing costs. In addition, while ensuring the technical effect, this scheme takes into account the production efficiency and overall cost performance, and has broad application prospects and market competitiveness.

[0130] In the present invention, the terms "first", "second", and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term "plural" means two or more, unless otherwise clearly defined. The terms "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.

[0131] 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. Therefore, it should not be construed as a limitation to the present invention.

[0132] In the description of this specification, the description of the terms "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 any one or more embodiments or examples in a suitable manner.

[0133] 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 changes and modifications. Any modification, equivalent replacement, improvement, 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 structure, characterized in that, Comprising: A bottom cover structure, the bottom cover structure including opposite first and second sides, the wall surface of the first side being adapted to abut against the flange portion of the upper bearing structure of the compressor; A boss structure provided on the bottom cover structure, and the boss structure protruding in a direction from the first side of the bottom cover structure towards the second side, the boss structure including a connected end portion and a transition portion, the transition portion being connected to the bottom cover structure, and the end portion being provided with an opening adapted to fit with the cylindrical portion of the upper bearing structure; The transition portion includes a plurality of convex portions arranged at intervals in the circumferential direction of the bottom cover structure, at least one of the convex portions including a first boss and a second boss having different axial distances from the bottom cover structure, at least one of the first bosses and at least one of the second bosses being adjacent to each other in the circumferential direction of the bottom cover structure, and a first exhaust hole being formed between the adjacent first boss and the second boss.

2. The silencer structure according to claim 1, wherein, The minimum axial distance between the first boss and the bottom cover structure is not less than the maximum axial distance between the second boss and the bottom cover structure; Wherein, the gas on the first side of the bottom cover structure flows from the inner wall of the first boss through the first exhaust hole to the outer wall of the second boss.

3. The silencer structure according to claim 2, characterized in that, Further comprising: A second exhaust hole provided on the side wall of one of the first boss and the second boss having a smaller axial distance from the bottom cover structure; Wherein, the first exhaust hole is provided on at least one of the convex portions, and the second exhaust hole is provided on the second boss of at least one of the convex portions.

4. The silencer structure according to claim 3, characterized in that, The first exhaust hole and the second exhaust hole are provided on the same convex portion.

5. The muffler structure according to claim 3, characterized in that, The opening direction of the first exhaust hole provided on the same convex portion is the same as the opening direction of the second exhaust hole.

6. The muffler structure according to claim 1, characterized in that, The first exhaust holes are provided on a plurality of the convex portions, and the opening directions of the plurality of first exhaust holes are in the same circumferential direction.

7. The silencer structure 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 and the plane where the bottom cover structure is located is not greater than 45°.

8. The silencer structure according to claim 1, wherein, Further comprising: A flow guiding groove provided on the second boss; Wherein, one end of the flow guiding groove extends to the first exhaust hole.

9. The silencer structure according to any one of claims 3 to 5, characterized in that, The ratio of the total opening area of the first exhaust hole and the second exhaust hole to the opening area of the opening is 0.5 - 2.

5.

10. The silencer structure according to any one of claims 1 to 8, characterized in that, In the axial direction of the opening, the minimum distance between the first exhaust hole and the wall surface of the second side of the bottom cover structure is not less than 1 / 3 of the maximum distance between the end portion and the wall surface of the first side of the bottom cover structure.

11. The muffler structure according to any one of claims 1 to 8, characterized in that, In the cross-section of the bottom cover structure, the projection of the outer edge of the bottom cover structure is circular, and the projection of the inner edge of the opening is circular; Wherein, the maximum dimension of the first exhaust hole in the radial direction of the bottom cover structure is not greater than the difference between the radius of the bottom cover structure and the radius of the opening.

12. The silencer structure according to any one of claims 1 to 8, characterized in that, The bottom cover structure and the boss structure are integrally formed.

13. The silencer structure according to any one of claims 1 to 8, characterized in that, The plane where the end portion is located is parallel to the plane where the bottom cover structure is located or the included angle is less than a preset angle.

14. The silencer structure according to any one of claims 1 to 8, characterized in that, The bottom cover structure is provided with a connection hole, and in the cross-section of the bottom cover structure, the projection of the connection hole does not overlap with the projection of the convex portion.

15. A compressor, characterized in that, Comprising: Upper bearing structure, the upper bearing structure includes a flange portion and a cylindrical portion protruding from the flange portion, and the cylindrical portion is hollow for accommodating a crankshaft; The muffler structure according to any one of claims 1 to 14 is sleeved outside the cylindrical portion.

16. The compressor according to claim 15, wherein The wall surface on the first side of the muffler structure is in surface contact with the flange portion of the upper bearing structure.

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