Silencer structure and compressor

Abstract

The embodiment of the utility model 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 airflow can be changed, and therefore the direct blowing impact force of high-pressure refrigerant airflow on the rotor is effectively improved.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to a muffler structure and a compressor. Background Technology

[0002] Currently, compressors typically have a muffler installed outside the upper bearing structure, with the muffler's exhaust port located at the top. However, with the increasing demand for miniaturization of compressors, in related technologies, during top exhaust, due to the low overall height of the compressor, the airflow tends to blow directly onto the rotor, which can lead to axial pulsation excitation and weaken the rotor's stability during operation. Utility Model Content

[0003] The present invention aims to at least solve the technical problem of weak rotor stability during the operation of miniaturized compressors 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] A second aspect of this utility model provides a compressor.

[0006] To achieve the above objectives, embodiments of this utility model provide a muffler structure, comprising: a bottom cover structure, the bottom cover structure including a first side and a second side opposite to each other, the wall surface of the first side being used to abut against the flange portion of the upper bearing structure of the compressor; a boss structure disposed on the bottom cover structure, the boss structure protruding in a direction from the first side of the bottom cover structure toward the second side, the boss structure including a connected end and a transition portion, the transition portion being connected to the bottom cover structure, the end having an opening adapted to fit the cylindrical portion of the upper bearing structure; the transition portion including a plurality of convex portions arranged circumferentially spaced along 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 arranged adjacent to each other in the circumferential direction of the bottom cover structure, and a first exhaust hole being formed between adjacent first bosses and second bosses.

[0007] The muffler structure proposed in this utility model includes a connected bottom cover structure and a boss structure. The boss structure is located 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 achieve the connection of the muffler structure. Specifically, the boss structure protrudes towards the side away from the upper bearing structure. The boss structure includes an end with an opening and a transition portion for connecting the end and the bottom cover structure. The transition portion is provided with a first boss and a second boss with different protrusion heights and arranged adjacent to each other. That is, the first boss and the second boss are axially distanced from the bottom cover structure, and there is a height difference between the first boss and the second boss with different protrusion heights. A first exhaust hole is formed at the junction of the two bosses. Under the action of the first exhaust hole, the airflow is ensured to be discharged along a tangential path, changing the impact direction of the airflow, thereby effectively improving the direct impact force of the high-pressure refrigerant airflow on the rotor, reducing the axial pulsation excitation borne by the rotor shaft system, and improving the operating stability and reliability of the compressor.

[0008] By forming exhaust regions on one or more convex sections and setting exhaust holes on some convex sections, the spatial advantage of the convex sections is utilized to allow airflow to be discharged tangentially, reducing the direct impact of airflow on the rotor, reducing vibration and impact force, improving the flexibility and controllability of airflow guidance, and helping to finely adjust the reduction of noise and vibration.

[0009] It should be added that the opening of the first exhaust port, by facing the top of the low platform, utilizes the spatial layout of the boss to guide the airflow in 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 to the outer wall of the second boss through the first exhaust hole.

[0011] In this technical solution, by limiting the height 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, thus forming a stepped asymmetrical boss structure.

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

[0013] By setting a second exhaust port on the side wall of the lower boss in the first and second bosses, the airflow is ensured to be discharged along different paths at the top and side wall of the lower boss under the action of the first and second exhaust ports, respectively. This reduces the concentration of sound waves and changes the impact direction of the airflow, thereby effectively improving the direct impact force of the high-pressure refrigerant airflow on the rotor, reducing the axial pulsation excitation borne by the rotor shaft system, and improving the operating stability and reliability of the compressor.

[0014] Furthermore, by providing a second exhaust port on the lower second boss, a first exhaust port and a second exhaust port can be provided on the top and side wall of the second boss respectively, which can effectively reduce the direct impact on the rotor and reduce vibration and noise.

[0015] In some technical solutions, the first vent and the second vent may optionally be located on the same protrusion.

[0016] By setting different exhaust ports (i.e., the first exhaust port and the second exhaust port) on the same convex part, the structural layout is simplified, manufacturing and assembly are facilitated, structural complexity is reduced, production efficiency is improved, costs are reduced, and the rationality and effectiveness of the exhaust path are ensured.

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

[0018] By ensuring that the opening direction of the exhaust holes located on the same convex part is consistent, the two exhaust holes discharge airflow in the same direction, ensuring the uniformity and coordination of the airflow path, reducing the deflection or dispersion of airflow during the discharge process, reducing the complexity of turbulence and noise sources, and thus enhancing the noise reduction effect.

[0019] In some technical solutions, optionally, multiple convex portions are provided with first vent holes, and the opening direction of the multiple first vent holes is the same circumferential direction.

[0020] By restricting the opening direction of the first exhaust holes on multiple convex bulges to the same circumferential direction, a consistent exhaust path is formed, which helps to reduce the deflection and turbulence of airflow during the exhaust process, reduce sound wave interference, and improve the noise reduction effect.

[0021] In some technical solutions, optionally, the opening end face of the first vent is a plane, and the angle between the normal 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 limiting the opening end face of the first exhaust port to a plane and limiting the opening direction of the first exhaust port, that is, the angle between the opening end face and the plane where the bottom cover structure is located, the tangential momentum can be enhanced, the broadband noise suppression can be improved, and the secondary noise energy can be weakened, thereby improving the compressor's energy efficiency.

[0023] In some technical solutions, optionally, a guide channel is also included, disposed on the second boss; wherein one end of the guide channel extends to the first exhaust port.

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

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

[0026] In this technical solution, by limiting the ratio of the total opening area of ​​the exhaust port to the opening area of ​​the opening, the total opening area is the sum of the opening areas of all first exhaust ports and all second exhaust ports, and the opening area of ​​the opening is the upper bearing exhaust port. By limiting the ratio of the total opening area of ​​the exhaust port to the opening area of ​​the opening to be between 0.5 and 2.5, the balance between airflow 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 vent and the wall 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 of the first side of the bottom cover structure.

[0028] In this technical solution, the lower edge height of the first exhaust port is limited, i.e., the axial distance is constrained. The maximum axial distance from the end (top of the boss) to the first side (the contact surface between the bottom cover and the bearing flange) is the total height H of the boss. H1 is the minimum axial distance from the first exhaust port to the second side (the mating surface between the bottom cover and the compressor housing). By limiting H1 to ≥ 1 / 3H, it is ensured that after the airflow is discharged from the first exhaust port, there is enough space (≥ H / 3) to complete the expansion and deceleration before reaching the second side, thus avoiding shock wave noise. At the same time, it also prolongs the residence time of the airflow in the silencer cavity and increases the proportion of tangential momentum.

[0029] In some technical solutions, optionally, on 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 at the end is also a circular hole. By limiting the radial dimension of the first vent 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 of the bottom cover structure (which mates with the bearing); the maximum radial dimension of the first vent hole is B, that is, the maximum span of the vent hole in the radial direction of the bottom cover (such as the diameter of the circular hole, the width of the rectangular hole, etc.). Through the above limitation, the first vent hole can be kept within the annular area of ​​the bottom cover, ensuring that the minimum distance between the edge of the vent hole and the outer circle of the bottom cover is not less than (R1-R2-B) / 2, preventing cracks from occurring during stamping or casting; and also reserving an annular area.

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

[0032] In this technical solution, the bottom cover structure and the boss structure 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, it also improves the sealing performance, eliminates the risk of interface leakage, and has strong pressure resistance.

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

[0034] In this technical solution, the surfaces of the end and bottom cover structures of the muffler structure are defined, that is, the end plane is designed to be parallel or at a small angle to the bottom cover plane. When designed to be parallel, the jet direction of the exhaust port is strictly parallel to the bottom cover plane, the tangential velocity component accounts for a high proportion, the axial impact is reduced, the flow channel has no abrupt change, and the total pressure loss is small. In addition, the parallel plane eliminates oblique reflection of sound waves in the cavity and reduces standing wave energy.

[0035] In some technical solutions, optionally, the bottom cover structure is provided with a connecting hole, and the projection of the connecting hole and the projection of the convex part do not overlap on the cross-section of the bottom cover structure.

[0036] In this technical solution, connecting holes are provided on the bottom cover structure as holes for bolt fixing or connection with external components. Multiple connecting holes are distributed circumferentially. The convex part is a protruding structure on the bottom cover structure. In the cross-sectional projection of the bottom cover structure, the connecting holes and the convex part do not overlap. This further limits the distance between their edges to ≥1.5mm, ensuring no area overlap. The non-overlapping projection avoids stress superposition between the hole edge and the root of the convex part, reducing the maximum stress and improving fatigue life.

[0037] An embodiment of the second aspect of this application provides a compressor, including: 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 to accommodate a crankshaft; and any of the above-mentioned muffler structures being sleeved outside the cylindrical portion.

[0038] The compressor provided in this application includes an upper bearing structure and a muffler structure. By integrating the muffler structure with the upper bearing structure, a synergistic improvement in 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 structure is fixed to the flange part by bolts to form a rigid-flexible coupling system.

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

[0040] In some technical solutions, optionally, the wall surface of 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 contacting the wall of the first side of the muffler structure with the flange of the upper bearing structure, the amplitude of the vibration transfer function can be reduced, and the axial vibration of the rotor can also be reduced.

[0042] Additional aspects and advantages of this invention will become apparent in the description that follows, or may be learned by practice of this invention. Attached Figure Description

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

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

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

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

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

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

[0049] Figure 7A schematic diagram of the structure of a compressor according to an embodiment of the present invention is shown;

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

[0051] in, Figures 1 to 8 The correspondence between the reference numerals and component names in the attached drawings 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: Protrusion; 1052: First boss; 1054: Second boss; 106: First exhaust port; 1082: Guide groove; 110: Second exhaust port;

[0053] 200: Compressor; 202: Upper bearing structure; 2022: Flange section; 2024: Cylinder section. Detailed Implementation

[0054] To better understand the above-mentioned objectives, features, and advantages of the embodiments of this utility model, the embodiments of this utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0055] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, embodiments of the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0056] The following reference Figures 1 to 8 Some embodiments according to the present invention are described.

[0057] like Figure 1 and Figure 8 As shown, this embodiment provides a muffler structure 100, including a connected bottom cover structure 102 and a boss structure 104, as follows. Figure 4As shown, the boss structure 104 provides 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 muffler structure 100. Specifically, the boss structure 104 protrudes towards the side away from the upper bearing structure 202. The boss structure 104 includes an end 1042 with an opening 1046 and a transition portion 1044 for connecting the end 1042 and the bottom cover structure 102. The transition portion 1044 is provided with a plurality of protrusions 1048. At least one protrusion 1048 is provided with a first exhaust hole 106. Since the first exhaust hole 106 is formed by the first boss 1052 and the second boss 1054, at least one protrusion 1048 includes a first boss 1052 and a second boss 1054, and the protrusion height is... The first boss 1052 and the second boss 1054, which are different but adjacent to each other, have different axial distances from the bottom cover structure 102 and different protrusion heights. A first exhaust hole 106 is formed at the junction of the two bosses. Under the action of the first exhaust hole 106, the airflow is ensured to be discharged along the tangential path, and the impact direction of the airflow is changed. This effectively improves the direct impact force of the high-pressure refrigerant airflow on the rotor, reduces the axial pulsation excitation borne by the rotor shaft system, and improves the operating stability and reliability of the compressor.

[0058] It should be added that the opening of the first exhaust port 106, by facing the top or side wall of the lower platform, utilizes the spatial layout of the boss to guide the airflow in a tangential direction, thereby reducing impact and vibration.

[0059] 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, a rigid seal can be achieved to prevent high-pressure refrigerant from leaking into the bearing cavity. The wall surface of the second side 1024 is clearance-fitted with the housing of the compressor 200 to compensate for thermal expansion differences and avoid structural jamming at high temperatures.

[0060] The boss structure 104 is mainly used for airflow guidance. The opening 1046 at the end 1042 is adapted to the cylindrical part 2024 of the upper bearing structure 202, so that the muffler structure 100 and the upper bearing structure 202 are relatively stationary, eliminating the relative displacement caused by speed fluctuations and reducing friction noise.

[0061] Regarding the first protrusion 1052 and the second protrusion 1054, the first protrusion 1052 serves as the main airflow guiding surface, and the second protrusion 1054 serves as the reflecting surface. The height difference forms a sudden change zone in acoustic impedance, reflecting sound waves of a specific frequency, thereby reducing airflow speed and turbulence.

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

[0063] The first exhaust port 106 is located at the misaligned junction of adjacent high and low protrusions. Under the action of the first exhaust port 106, the airflow can be tangentially guided to avoid the refrigerant directly rushing into the main casing of the compressor 200 to form standing wave resonance and reduce secondary noise.

[0064] Furthermore, the first exhaust port 106 has a converging and expanding Laval nozzle shape, and the exhaust direction is at an angle of 45°±5° with the center line of the muffler.

[0065] In some embodiments, the boss structure 104 optionally includes a plurality of protrusions 1048, and at least one protrusion 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 protrusion 1048 includes a first boss 1052 and a second boss 1054. By providing a first exhaust hole 106 on one or more protrusions 1048, the airflow can be dispersed during exhaust, thereby improving the stability of the compressor 200 operation.

[0066] It should be added that by uniformly arranging multiple convex portions 1048 in the circumference of the bottom cover structure 102, forming an exhaust area on one or more convex portions 1048, and setting exhaust holes on some convex portions 1048, the spatial advantage of the convex portions is utilized to allow the airflow to be discharged in the tangential direction, reducing the direct impact of airflow on the rotor, reducing vibration and impact force, improving the flexibility and controllability of airflow guidance, and helping to finely adjust the reduction of noise and vibration.

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

[0068] In summary, this solution fully utilizes a multi-point, multi-angle exhaust strategy to effectively disperse airflow, reduce sound wave superposition and resonance, and improve noise reduction. Simultaneously, the arrangement of multiple exhaust ports also helps to smoothly guide airflow, reducing the impact of direct airflow onto the rotor and improving vibration and energy efficiency.

[0069] Furthermore, a first vent hole 106 is provided on one of the protruding portions 1048, and a first vent hole 106 may be provided on some of the protruding portions 1048.

[0070] It can be understood that the convex portion 1048 is an independent protruding unit distributed circumferentially along the bottom cover structure 102, and each convex portion 1048 includes a combination structure of a first boss 1052 and a second boss 1054.

[0071] The spacing angle between adjacent convex hulls 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] In summary, the muffler structure 100 provided in this application achieves the comprehensive goals of noise reduction, vibration reduction, and efficiency improvement within a compact space through the hierarchical airflow guidance of the two bosses of varying heights and the tangential exhaust direction of the first exhaust port 106.

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

[0074] The gas flows along the following path: high-pressure gas on the first side 1022 of the bottom cover structure 102 → inner wall (guide surface) of the first boss 1052 → first exhaust port 106 (main jet) → outer wall (reflective surface) of the second boss 1054 → enters the compressor 200 cavity.

[0075] The inner wall of the first protrusion 1052 can serve as a gas acceleration zone, the first exhaust port 106 can serve as a supersonic jet throat, and the outer wall of the second protrusion 1054 serves as an impact diffusion and vortex generation zone.

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

[0077] When the jet from the first exhaust port 106 impacts the outer wall of the second protrusion 1054, it generates broadband noise.

[0078] The height difference between the high and low bosses causes a time difference in the arrival of airflow pulses at the rotor, which can disrupt the coherence of certain orders, such as 4th and 8th order noise, to reduce the fundamental frequency amplitude.

[0079] In some embodiments, optionally, a second exhaust port is provided on the side wall of the lower boss in the first boss 1052 and the second boss 1054. Under the action of the first exhaust port 106 and the second exhaust port, the airflow is ensured to be discharged along different paths at the top and side wall of the lower boss, respectively, reducing sound wave concentration and changing the impact direction of the airflow. This effectively improves the direct impact force of the high-pressure refrigerant airflow on the rotor, reduces the axial pulsation excitation borne by the rotor shaft system, and improves the operating stability and reliability of the compressor.

[0080] In some embodiments, alternatively, different exhaust holes (i.e., the first exhaust hole 106 and the second exhaust hole 110) are provided on the same convex portion 1048 to simplify the structural layout, facilitate manufacturing and assembly, reduce structural complexity, improve production efficiency, reduce costs, and at the same time ensure the rationality and effectiveness of the exhaust path.

[0081] Furthermore, by setting multiple exhaust holes on the same convex portion 1048, the airflow can be discharged along different angles or paths through reasonable arrangement, reducing airflow impact and turbulence, improving the distribution and uniformity of airflow, reducing the source of noise generation, and improving the noise reduction effect.

[0082] It is important to emphasize that by arranging multiple exhaust holes on the same convex portion 1048, airflow can be released simultaneously at different locations, reducing the superposition and reflection of sound waves, thereby lowering the sound pressure level, enhancing noise reduction capabilities, and improving noise problems in specific frequency bands.

[0083] In general, by setting multiple exhaust holes on the same convex hull, different exhaust angles (such as along the tangent, sideways, etc.) can be designed to adjust the direction of airflow, reduce the impact on the rotor and shaft system, reduce vibration and axial pulsation, and improve the smoothness and reliability of compressor operation.

[0084] In some embodiments, optionally, by restricting the opening direction of the exhaust holes located on the same protrusion 1048 to be consistent, the two exhaust holes discharge airflow in the same direction, ensuring the uniformity and coordination of the airflow path, reducing the deflection or dispersion of airflow during discharge, reducing the complexity of turbulence and noise sources, thereby enhancing the noise reduction effect.

[0085] It is understandable that a unified exhaust direction helps the coherent superposition of sound waves, avoids resonance or noise amplification caused by the mutual interference of sound waves from different directions, and improves the frequency response of noise, especially achieving more significant noise suppression in the target frequency band (e.g., 500Hz to 3150Hz).

[0086] The same opening direction facilitates airflow to exit along a predetermined path, reduces airflow turbulence and pressure fluctuations near the exhaust port, reduces vibration and rotor impact caused by airflow, and improves the smoothness of compressor operation.

[0087] In some embodiments, the opening direction of the first exhaust holes 106 on the plurality of protrusions is optionally restricted to the same circumferential direction to form a consistent exhaust path, which helps to reduce the deflection and turbulence of the airflow during the exhaust process, reduce sound wave interference, and improve the noise reduction effect.

[0088] The airflow is discharged along the same circumference, allowing it to be discharged smoothly along a predetermined path, reducing turbulence and pressure fluctuations, lowering vibration and impact forces, mitigating axial pulsation of the rotor shaft system, and improving the stability and reliability of the system.

[0089] In some embodiments, the opening end face of the first exhaust port 106 may be restricted to a plane, and the opening direction of the first exhaust port 106 may be restricted, i.e., the angle between the opening end face and the plane where the bottom cover structure 102 is located, which can enhance tangential momentum, suppress broadband noise, especially reduce secondary noise energy, and improve the energy efficiency of the compressor 200.

[0090] Furthermore, the outlet section of the first exhaust port 106 is a flat geometric surface (not curved or stepped), and the angle between the normal of the opening end face and the plane of the bottom cover structure 102 is ≤45°, with the normal pointing in the direction of airflow discharge.

[0091] It is understandable that the planar end face and the outer wall of the second protrusion 1054 form a sharp-edge guide structure, which utilizes the Coanda effect to make the high-speed airflow flow closely along the wall, thereby increasing the proportion of the tangential velocity component.

[0092] When the included angle is 45°, the normal velocity component of the airflow is the same as the tangential velocity component, and the tangential momentum accounts for 50%.

[0093] By limiting the included angle to ≤45°, the airflow direction is ensured to deviate from the rotor axis (offset angle ≥45°), thus reducing the axial impact force, reducing the airflow impact energy density, and reducing secondary noise.

[0094] In some embodiments, optionally, a guide groove 1082 is provided on the second boss 1054, one end of the guide 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 coupling with the first exhaust hole 106, that is, the inlet end face of the guide groove 1082 is coplanar with the outlet of the first exhaust hole 106 or there is a small excessive misalignment, a continuous guide channel is formed.

[0095] High-pressure gas is accelerated through the first exhaust port 106 and can be further regulated by the flow guide groove 1082. The specific regulation is achieved by the shape of the flow guide groove 1082, such as gradually narrowing the groove width to increase the flow velocity, using curvature to induce swirling flow, forming a spiral flow. Furthermore, microgrooves can be set on the groove wall to reduce turbulence intensity and pressure loss.

[0096] It is understandable that by setting the guide groove 1082, the airflow path can be extended, so that the airflow from adjacent exhaust holes reaches the rotor at different times.

[0097] In some embodiments, optionally, such as Figure 2 and Figure 3 As shown, one or more second exhaust holes 110 are provided on the surface of the guide groove 1082, specifically, as... Figure 2 As shown, multiple second exhaust holes 110 can be distributed along the length of the guide groove 1082. Under the action of the second exhaust holes 110, secondary exhaust can be achieved. The gas flowing out through the second exhaust holes 110 has a low flow velocity, which replenishes tangential momentum and avoids flow separation.

[0098] With a second vent 110 provided, such as Figure 3 As shown, the second exhaust port 110 is a round hole.

[0099] It is understandable that the velocity difference between the outlet jet of the second exhaust port 110 and the main airflow creates shear layer instability, which breaks large-scale vortices into smaller vortices, thereby reducing turbulence noise energy.

[0100] Furthermore, the axis of the second exhaust port 110 forms an angle of 10° to 30° with the normal of the bottom surface of the guide groove 1082, guiding the airflow to diffuse downstream. The inlet end of the second exhaust port 110 smoothly transitions with the curved surface of the guide groove 1082, and the outlet end is connected to the cavity of the compressor 200.

[0101] In some embodiments, optionally, the area of ​​the first exhaust hole 106 and the total opening area of ​​the second exhaust hole 110 located on the same protrusion 1048 are limited. The area of ​​the first exhaust hole 106 is the effective flow area of ​​a single first exhaust hole 106, which is typically rectangular or elliptical. The total opening area of ​​the second exhaust hole 110 is the sum of the areas of all second exhaust holes 110 on the guide groove 1082, which is typically multiple holes. By limiting the area of ​​the first exhaust hole 106 to be greater than the total opening area of ​​the second exhaust hole 110, most of the airflow is discharged through the larger first exhaust hole 106, and a small portion of the airflow is discharged through the smaller second exhaust hole 110. The large area of ​​the first exhaust hole 106 reduces the jet flow pressure and also reduces the vibration acceleration of the shell surface. The multi-hole layout of the second exhaust hole 110 avoids local stress concentration and extends the fatigue life of the shell.

[0102] Furthermore, the ratio of the area of ​​the first exhaust port 106 to the total opening area of ​​the second exhaust port 110 is between 1.5 and 3.0. If the ratio is too low, the proportion of secondary airflow is too high, the tangential momentum is insufficient, and the rotor vibration increases. If the ratio is too high, the risk of main airflow blockage increases and pressure loss increases.

[0103] The orifice shape of the first exhaust port 106 is preferably rectangular or elliptical to suppress flow separation; the orifice shape of the second exhaust port 110 can be elongated or circular to improve the guidance of low-speed airflow.

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

[0105] It is understandable that if the ratio is too small, less than 0.5, the exhaust area will be insufficient, the back pressure will increase, and the compressor's power consumption will increase by 200. If the ratio is too large, greater than 2.5, the flow rate will be insufficient. The low flow rate will lead to a thicker boundary layer, greater turbulence intensity, and increased pressure loss.

[0106] In some embodiments, optionally, when only the first exhaust port 106 is provided, by limiting the ratio of the total opening area of ​​all the first exhaust ports 106 to the opening area of ​​the opening 1046, the airflow distribution and the balance of the system back pressure can be ensured by limiting the ratio of the total opening area of ​​the exhaust ports to the opening area of ​​the opening 1046 to between 0.5 and 2.5.

[0107] It is understandable that if the ratio is too small, less than 0.5, the exhaust area will be insufficient, the back pressure will increase, and the compressor's power consumption will increase by 200. If the ratio is too large, greater than 2.5, the flow rate will be insufficient. The low flow rate will lead to a thicker boundary layer, greater turbulence intensity, and increased pressure loss.

[0108] When the compressor 200 operates at high speeds, such as above 6000 rpm, the ratio can be controlled between 0.8 and 1.2 to suppress high-frequency noise. When the compressor 200 operates at low speeds, such as below 3000 rpm, the ratio can be controlled between 1.5 and 2.0 to enhance low-frequency sound absorption.

[0109] In some embodiments, optionally, such as Figure 5As shown, 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) is the total height H of the boss. 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 H = 1 / 3H, it is ensured that after the airflow 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 noise; at the same time, it also extends the residence time of the airflow in the silencing cavity and increases the proportion of tangential momentum.

[0110] If the distance is too small, that is, when H1 < H / 3, the high-speed airflow 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 the noise reduction effect is weakened.

[0111] Furthermore, when applied to a short compressor 200, for example, H = 6 mm and H1 ≥ 2 mm, a micro-hole array (pore 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. Among them, 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 airflow 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, the bottom cover structure 102 and the boss structure 104 can be integrally machined to ensure the integrity of the structure, eliminate bolt / welding connections, and reduce stress concentration; at the same time, it also improves the sealing performance, eliminates the risk of interface leakage, and has strong pressure resistance.

[0115] Furthermore, the first vent 106 is punched simultaneously with the bottom cover using a punching process.

[0116] In some embodiments, the surfaces of the end 1042 of the muffler structure 100 and the bottom cover structure 102 are optionally defined, that is, the plane of the end 1042 is designed to be parallel to or at a small angle to the plane of the bottom cover. When designed to be parallel, the jet direction of the exhaust port is strictly parallel to the plane of the bottom cover, the tangential velocity component accounts for a higher proportion, the axial impact is reduced, there is no abrupt change in the flow channel, and the total pressure loss is smaller. In addition, the parallel planes eliminate oblique reflections of sound waves in the cavity and reduce standing wave energy.

[0117] When the small angle design is used, the slight tilt can induce the airflow to spiral upward, prolong the residence time, and improve the heat exchange efficiency; at the same time, the small angle design breaks the symmetry, and the broadband noise OA value is further reduced.

[0118] In some embodiments, optionally, connecting holes 103 are provided on the bottom cover structure 102 as holes for bolt fixing or connection with external components. Multiple connecting holes 103 are circumferentially distributed, and the protruding portion 1048 is a protruding structure on the bottom cover structure 102. In the cross-sectional projection of the bottom cover structure 102, the connecting holes 103 and the protruding portion 1048 do not overlap, further limiting the distance between their edges to ≥1.5mm, ensuring no area overlap. The non-overlapping projection avoids stress superposition between the hole edge and the root of the protruding portion, reducing the maximum stress and improving fatigue life.

[0119] It is understandable that the bolt preload is uniformly transmitted through the non-overlapping area, resulting in less fluctuation in contact pressure. At the same time, the non-overlapping design ensures continuous contact of the flange face, thereby reducing the leakage rate.

[0120] Among them, the connecting holes 103 are distributed on the outer ring, and the convex bulges 1048 are concentrated on the inner ring, with radial spacing to avoid projection interference.

[0121] Furthermore, the connecting hole 103 and the convex portion 1048 are not in the same radial direction.

[0122] like Figure 7 and Figure 8As shown, an embodiment of the second aspect of this application provides a compressor 200, including an upper bearing structure 202 and a muffler structure 100. By integrating the muffler structure 100 with the upper bearing structure 202, a synergistic improvement in 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 of the above-mentioned muffler structures 100, it has the beneficial effects of any of the above-mentioned muffler structures 100, which will not be elaborated here.

[0124] Furthermore, by bringing the wall of the first side 1022 of the muffler structure 100 into contact with the flange 2022 of the upper bearing structure 202, the amplitude of the vibration transfer function can be reduced, and the axial vibration of the rotor can also be reduced.

[0125] In one 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 is fixed to the muffler by bolts. The muffler housing has a convex structure, forming a sound-absorbing cavity with the interior. The muffler bottom cover (i.e., bottom cover structure 102) has several bolt holes (i.e., connection holes 103). The muffler top cover (i.e., boss structure 104) has bearing mating holes (i.e., openings 1046). The top cover and the bottom cover are connected to form a similar convex structure. The muffler guide groove 1082 is a platform structure formed when the exhaust hole is processed by stamping, casting or other methods. Its upper edge is connected to the lower edge of the muffler exhaust hole (i.e., the first exhaust hole 106). The exhaust hole is provided on the side of the top convex bulge of the muffler. The exhaust hole includes the first exhaust hole 106, which is located on the side of the high platform (i.e., the first protrusion 1052) and blows air towards the top of the low platform (i.e., the second protrusion 1054). The exhaust hole includes the second exhaust hole 110, which is located on the side of the low platform and the number N1≥1.

[0126] like Figure 1 , Figure 4 , Figure 5 and Figure 6As shown, an exhaust port is provided on the side of the top convex bulge of the muffler; the exhaust port includes a first exhaust port 106, the convex bulge includes high and low platforms, the first exhaust port 106 is located on the side of the high platform and blows air towards the top of the low platform; a guide groove 1082 is provided on the top of the low platform; the exhaust port includes a second exhaust port 110, the second exhaust port 110 is located on the side of the low platform, and the number of second exhaust ports 110 N2≥1; there are multiple convex bulges (i.e., convex bulge parts 1048), and at least one convex bulge is provided with an exhaust port; the overall height of the muffler 2≤H≤30mm, the height H1 between the lower edge of the exhaust port and the bottom cover is ≥1 / 3H; the total area S of the exhaust ports of the muffler and the area S0 of the bearing exhaust ports satisfy 0.5≤S / S0≤2.5; the ratio of the area S1 of the first exhaust port to the area S2 of the second exhaust port of each convex bulge satisfies S1 / S2>1; as Figure 6 As shown, the muffler exhaust port is located at the junction of the top surface and the bottom cover. The angle between the normal of the exhaust port and the line connecting the center of the muffler is 0° < α < 180°. The width B of the first exhaust port of the muffler is ≤ muffler radius R1 - mating hole radius R2. The number of muffler flaps in the radial direction N1 ≥ 1, and the angle between the exhaust ports satisfies α1 > 0°. The angle between the normal of the first exhaust port of the muffler bulge and the horizontal line is -45° ≤ α2 ≤ 45°. The shape of the muffler exhaust port can be, but is not limited to, square, elliptical, circular, crescent-shaped, etc.

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

[0128] Furthermore, the muffler of this embodiment can improve the uniformity of airflow distribution and tangential exhaust efficiency, thereby mitigating the noise degradation caused by gas impact.

[0129] Specifically, optimizing the airflow direction of the silencer to a tangential direction effectively reduces the direct impact force of the high-pressure refrigerant airflow on the rotor, thus reducing the axial pulsation excitation experienced by the rotor shaft system. This design not only significantly improves the operational stability and reliability of the compressor but also features simple implementation and strong process compatibility, achieving efficient noise reduction and performance optimization without increasing additional manufacturing costs. Furthermore, while ensuring technical effectiveness, this solution also considers production efficiency and overall cost-effectiveness, possessing broad application prospects and market competitiveness.

[0130] In this utility model, 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 "multiple" refers to two or more unless otherwise explicitly defined. The terms "install," "connect," "join," and "fix" should be interpreted broadly. For example, "connect" can be a fixed connection, a detachable connection, or an integral connection; "join" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0131] In the description of this utility model, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or unit referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0132] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0133] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A silencer structure, characterized in that, include: A bottom cover structure, the bottom cover structure including a first side and a second side opposite to each other, the wall of the first side being used to abut against the flange portion of the upper bearing structure of the compressor; A boss structure is provided on the bottom cover structure, and the boss structure protrudes in a direction from the first side of the bottom cover structure toward the second side. The boss structure includes a connected end and a transition portion. The transition portion is connected to the bottom cover structure. The end is provided with an opening for fitting with the cylindrical portion of the upper bearing structure. The transition portion includes a plurality of protrusions spaced apart circumferentially along the bottom cover structure. At least one of the protrusions includes a first boss and a second boss at a different axial distance from the bottom cover structure. At least one first boss and at least one second boss are arranged adjacent to each other in the circumferential direction of the bottom cover structure, and a first vent hole is formed between adjacent first bosses and second bosses.

2. The silencer structure according to claim 1, characterized in that, 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; In this process, 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, Also includes: The second vent is located on the side wall of the one of the first boss and the second boss that is axially farther from the bottom cover structure; Wherein, at least one of the convex portions is provided with the first vent hole, and at least one of the convex portions is provided with the second vent hole on the second protrusion.

4. The muffler structure according to claim 3, characterized in that, The first vent and the second vent are located on the same protrusion.

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

6. The silencer structure according to claim 1, characterized in that, The plurality of the protruding portions are provided with the first exhaust holes, and the opening direction of the plurality of the first exhaust holes is the same circumferential direction.

7. The silencer structure according to claim 1, characterized in that, The opening end face of the first vent is a plane, and the angle between the normal of the opening end face and the plane where the bottom cover structure is located is no greater than 45°.

8. The silencer structure according to claim 1, characterized in that, Also includes: A flow guide channel is provided on the second boss; One end of the guide groove extends to the first exhaust port.

9. The muffler structure according to any one of claims 3 to 5, characterized in that, The ratio of the total opening area of ​​the first vent and the second vent to the opening area of ​​the opening is 0.5 to 2.

5.

10. The muffler 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 vent hole and the wall 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 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, On 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 vent 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 muffler 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 muffler structure according to any one of claims 1 to 8, characterized in that, The plane where the end is located is parallel to or at an angle less than a preset angle to the plane where the bottom cover structure is located.

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

15. A compressor, characterized in that, include: 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 to accommodate a crankshaft; The muffler structure as described in any one of claims 1 to 14 is sleeved outside the cylindrical portion.

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

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