Air intake muffler and compressor

Abstract

The utility model provides an air suction silencer and compressor. Air suction silencer includes: first cover body has air inlet channel structure and air outlet channel structure, air inlet channel structure and air outlet channel structure all are located on the outer surface of first cover body, and at least part air inlet channel structure extends along the surface of first cover body, first cover body covers and sets up on second cover body to enclose the sound attenuation chamber between both, first cover body still has the air inlet hole of setting in the end of air inlet channel structure, air inlet channel structure communicates with sound attenuation chamber through air inlet hole, air inlet hole is close to the edge of first cover body relative to the center of first cover body and is located in the intermediate region of first cover body's first side, the baffle is arranged in sound attenuation chamber to make sound attenuation chamber form air inlet chamber and air outlet chamber, air inlet chamber communicates with air inlet hole, and air outlet chamber communicates with air outlet channel structure. The utility model solves the problem that the air suction silencer in the prior art has insufficient high frequency sound attenuation capacity.

Description

Technical Field

[0001] This utility model relates to the field of noise reduction equipment technology, specifically to an intake silencer and a compressor. Background Technology

[0002] With the rapid development of the automotive industry and consumers' increasing emphasis on in-car comfort, the market demand for car refrigerators, as an important appliance for enhancing the driving experience, is growing year by year. However, the noise generated by the compressor of a car refrigerator during operation, especially high-frequency noise, has become a major pain point for user experience. High-frequency noise is typically concentrated in the 3500-4500Hz range, which falls precisely within the sensitive hearing range of the human ear. Prolonged exposure to high-frequency noise can not only cause auditory fatigue but also psychological discomfort, severely impacting the comfort of the ride. In existing technologies, the design of intake mufflers generally employs deflectors or complex internal channels to guide airflow and achieve noise reduction. However, these traditional designs are insufficient in their high-frequency noise reduction capabilities, failing to meet user needs.

[0003] In other words, existing intake silencers have insufficient high-frequency noise reduction capabilities. Utility Model Content

[0004] The main purpose of this utility model is to provide an intake muffler and a compressor to solve the problem of insufficient high-frequency noise reduction capability of the intake muffler in the prior art.

[0005] To achieve the above objectives, according to one aspect of the present invention, an intake muffler is provided, comprising: a first cover having an air inlet channel structure and an air outlet channel structure, both of which are located on the outer surface of the first cover, and at least a portion of the air inlet channel structure extends along the surface of the first cover; a second cover, the first cover being disposed on the second cover to form a muffler cavity between the two, the first cover also having an air inlet hole disposed at the end of the air inlet channel structure, the air inlet channel structure communicating with the muffler cavity through the air inlet hole, the air inlet hole being disposed near the edge of the first cover relative to the center of the first cover, and the air inlet hole being located in the middle region of a first side of the first cover; and a partition disposed in the muffler cavity to form an air inlet cavity and an air outlet cavity, the air inlet cavity communicating with the air inlet hole, and the air outlet cavity communicating with the air outlet channel structure.

[0006] Furthermore, the first cover has a body, and an air intake channel structure is disposed on the outer surface of the body and forms an air intake channel between the two. The end of the air intake channel structure away from the air intake hole has an inlet and extends to the edge of the second side of the first cover.

[0007] Furthermore, the first cover also has an air outlet, and the air outlet cavity is connected to the air outlet channel structure through the air outlet. The air outlet and the air outlet channel structure are set close to the center of the first cover relative to the edge of the first cover. The extension direction of the air outlet channel structure is different from the extension direction of the air inlet channel structure.

[0008] Furthermore, the extension direction of the air outlet channel structure is perpendicular to the body of the first cover; and / or, the extension direction of the air outlet channel structure is perpendicular to the extension direction of the air inlet channel structure.

[0009] Furthermore, one or more oil drain ports are provided on the side surface of the second cover away from the first cover. When there are multiple oil drain ports, at least two of the multiple oil drain ports are respectively provided at two corners on the same side of the second cover, and oil drain ports are provided in both the air inlet chamber and the air outlet chamber.

[0010] Furthermore, the partition is disposed on at least one of the first cover and the second cover, and the first cover or the second cover without the partition has a positioning structure for engaging with the edge of the partition, the positioning structure being a positioning rib or a positioning groove.

[0011] Furthermore, a partition is provided on the second cover, and the first cover has a positioning structure, which includes two positioning ribs. The two positioning ribs are spaced apart and form a snap-fit ​​gap, and the edge of the partition extends into the snap-fit ​​gap.

[0012] Furthermore, the positioning rib protrudes from the opening of the first cover at the edge facing the second cover, and the height of the positioning rib in the direction perpendicular to the first cover is within the range of greater than or equal to 0.5 mm and less than or equal to 2 mm; and / or, the partition protrudes from the opening of the second cover at the edge facing the first cover, and the protrusion height of the partition is greater than 0 mm and less than or equal to 2 mm.

[0013] Furthermore, the intake muffler also includes a flow channel structure located in the exhaust chamber. One end of the flow channel structure passes through the partition and communicates with the intake chamber, while the other end of the flow channel structure communicates with the exhaust chamber.

[0014] Furthermore, the partition has a connecting hole or a connecting notch, one end of the flow channel structure is connected to the connecting hole or the connecting notch, and when the partition has a connecting notch, the connecting notch is formed at the corner of the partition; and / or, the diameter or side length of the flow channel structure along the cross section perpendicular to it is greater than or equal to 2 mm and less than or equal to 4 mm.

[0015] Furthermore, the flow channel structure includes a flow guide rib and a flow guide plate. The flow guide rib is disposed on the surface of the first cover facing the second cover. The flow guide plate is connected to the partition and the inner wall of the second cover. The flow guide plate is open on the side facing the first cover, so that after the first cover and the second cover are assembled, the flow guide rib, the inner surface of the first cover, the flow guide plate and the inner wall of the second cover together form the channel part of the flow channel structure.

[0016] Furthermore, the air outlet channel structure is located in the middle region along the length of the first cover, the air inlet end of the air outlet channel structure extends into the interior of the first cover, and the distance D between the air inlet end of the air outlet channel structure and the inner wall surface of the first cover is greater than or equal to 3 mm and less than or equal to 8 mm.

[0017] Furthermore, the height H1 of the first cover is less than the height H2 of the second cover; and / or, the ratio between the cavity height H of the intake muffler and the length L of the intake muffler is greater than or equal to 0.25 and less than or equal to 0.6; and / or, the ratio between the volume of the intake chamber and the volume of the exhaust chamber is greater than or equal to 0.3 and less than or equal to 0.7; and / or, the air inlet is a circular or polygonal hole, and the diameter or side length of the air inlet is greater than or equal to 2 mm and less than or equal to 4 mm.

[0018] According to another aspect of the present invention, a compressor is provided, comprising: a compressor housing, wherein a motor is disposed in the compressor housing; and the aforementioned intake muffler, wherein the intake muffler is disposed in the compressor housing and located on one side of the motor.

[0019] Furthermore, the intake muffler has a first side and a second side arranged opposite to each other. The first side of the intake muffler has an oil drain port. The first side of the intake muffler is arranged closer to the motor than the second side of the intake muffler. The flow channel structure of the intake muffler is located on the first side of the intake muffler.

[0020] According to the technical solution of this utility model, the intake muffler includes a first cover, a second cover, and a partition. The first cover has an air inlet channel structure and an air outlet channel structure, both of which are located on the outer surface of the first cover, and at least a portion of the air inlet channel structure extends along the surface of the first cover. The first cover is placed on the second cover to form a muffler cavity between the two. The first cover also has an air inlet hole located at the end of the air inlet channel structure. The air inlet channel structure communicates with the muffler cavity through the air inlet hole. The air inlet hole is located near the edge of the first cover relative to the center of the first cover, and is located in the middle area of ​​the first side of the first cover. The partition is placed in the muffler cavity to form an air inlet cavity and an air outlet cavity. The air inlet cavity communicates with the air inlet hole, and the air outlet cavity communicates with the air outlet channel structure.

[0021] By arranging the intake and exhaust channels on the outer surface of the first cover, and planning at least part of the intake channel to extend along the surface of the first cover, this design avoids the construction of complex internal channels, simplifies the structure of the intake muffler, reduces manufacturing costs, and also makes assembly easier. By setting the intake port closer to the edge of the first cover than its center, and placing it in the middle region of the first side of the first cover, the intake port is located in the modal vibration node region of the acoustic cavity. This effectively suppresses sound wave reflection and resonance in the high-frequency range (e.g., 3500~4500Hz), significantly improving the high-frequency noise reduction performance and alleviating the noise problem of the vehicle refrigerator compressor in the high-frequency range. Dividing the muffler cavity into an intake and exhaust cavity by a partition not only optimizes the airflow path and reduces eddies and energy loss within the muffler cavity, but also enables the muffler to effectively reduce noise in the space-constrained vehicle environment. The proximity of the intake port to the edge further optimizes the airflow distribution, reduces direct impact on the compressor's interior, and lowers noise generation.

[0022] In summary, the intake muffler of this application can significantly improve operating noise and reduce the impact on user comfort without sacrificing the performance of the vehicle refrigerator compressor, thus enhancing the overall user experience of the vehicle refrigerator. It not only effectively solves the problem of poor high-frequency noise reduction in existing technologies, but also achieves a balance between cost, space, and performance through structural optimization. Attached Figure Description

[0023] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0024] Figure 1 A schematic diagram of the intake silencer of one alternative embodiment of the present invention is shown;

[0025] Figure 2 It shows Figure 1 Exploded view of the intake muffler in the middle;

[0026] Figure 3 It shows Figure 1 A bottom view of the first cover of the intake muffler;

[0027] Figure 4 It shows Figure 1 Top view of the second cover of the intake muffler;

[0028] Figure 5 It shows Figure 1 A partial cross-sectional view of the first cover of the intake muffler in the middle;

[0029] Figure 6 A comparison diagram of transmission loss between an optional embodiment of the present invention's intake muffler and a prior art intake muffler is shown.

[0030] Figure 7 A schematic diagram of the compressor according to an alternative embodiment of the present invention is shown.

[0031] The above figures include the following reference numerals:

[0032] 100. Intake silencer; 110. First cover; 111. Body; 112. Intake channel structure; 113. Exhaust channel structure; 114. Intake hole; 115. First side of the first cover; 116. Exhaust port; 117. Positioning rib; 118. Guide rib; 119. Second side of the first cover; 120. Second cover; 121. Oil drain port; 122. Partition plate; 1221. Connecting notch; 123. Guide plate; 140. Intake chamber; 150. Exhaust chamber; 160. First side of the intake silencer; 170. Second side of the intake silencer; 200. Compressor housing; 300. Motor. Detailed Implementation

[0033] It should be noted that, where there is no conflict, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0034] It should be noted that, unless otherwise specified, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0035] In this utility model, unless otherwise stated, directional terms such as "upper," "lower," "top," and "bottom" are generally used in relation to the direction shown in the accompanying drawings, or in relation to the vertical, perpendicular, or gravitational direction of the component itself; similarly, for ease of understanding and description, "inner" and "outer" refer to the inner and outer contours of each component itself, but the above directional terms are not used to limit this utility model.

[0036] In order to solve the problem of insufficient high-frequency noise reduction capability of the existing intake muffler 100, this utility model provides an intake muffler 100 and a compressor.

[0037] like Figures 1 to 6As shown, the intake muffler 100 includes a first cover 110, a second cover 120, and a partition 122. The first cover 110 has an intake channel structure 112 and an exhaust channel structure 113, both of which are located on the outer surface of the first cover 110, and at least a portion of the intake channel structure 112 extends along the surface of the first cover 110. The first cover 110 covers the second cover 120 to form a muffler cavity between them. The first cover 110 also has a partition 122. An air inlet 114 is located at the end of the air channel structure 112. The air inlet structure 112 is connected to the silencing cavity through the air inlet 114. The air inlet 114 is located near the edge of the first cover 110 relative to the center of the first cover 110, and the air inlet 114 is located in the middle area of ​​the first side 115 of the first cover. A partition 122 is disposed in the silencing cavity so that the silencing cavity forms an air inlet cavity 140 and an air outlet cavity 150. The air inlet cavity 140 is connected to the air inlet 114, and the air outlet cavity 150 is connected to the air outlet channel structure 113.

[0038] By arranging the air intake channel structure 112 and the air outlet channel structure 113 on the outer surface of the first cover 110, and planning at least a portion of the air intake channel structure 112 to extend along the surface of the first cover 110, this design avoids the construction of complex internal channels, simplifies the structure of the intake muffler 100, reduces manufacturing costs, and also makes assembly easier. By setting the air intake hole 114 near the edge of the first cover 110 relative to the center of the first cover 110, and with the air intake hole 114 located in the middle region of the first side 115 of the first cover, the location of the air intake hole 114 is situated in the modal vibration node region of the acoustic cavity. This effectively suppresses sound wave reflection and resonance in the high-frequency range (e.g., 3500~4500Hz), thereby significantly improving the noise reduction performance in the high-frequency range and improving the noise problem of the vehicle refrigerator compressor in the high-frequency range. The muffler cavity is divided into an intake cavity 140 and an exhaust cavity 150 by a partition 122. This not only optimizes the airflow path and reduces turbulence and energy loss within the muffler cavity, but also enables the muffler to effectively reduce noise in the space-constrained vehicle environment. The placement of the intake port 114 near the edge further optimizes the airflow distribution, reduces direct impact on the compressor's interior, and lowers noise levels.

[0039] In summary, the intake muffler 100 of this application can significantly improve operating noise and reduce the impact on user comfort without sacrificing the performance of the vehicle refrigerator compressor, thereby enhancing the overall user experience of the vehicle refrigerator. It not only effectively solves the problem of poor high-frequency noise reduction in existing technologies, but also achieves a balance between cost, space, and performance through structural optimization.

[0040] like Figure 6 As shown, Figure 6A comparison diagram of the transmission loss of the intake silencer 100 of this application and the intake silencer 100 in the prior art is shown. As can be seen from the figure, by moving the air inlet 114 to the middle area of ​​the first side 115 of the first cover, this application effectively suppresses sound wave reflection and resonance in the 3500~4500Hz frequency band, compared with the existing one which is set in the middle, thereby significantly improving the noise reduction performance in the high frequency band.

[0041] In one alternative embodiment of this application, reference is made to Figure 1 As shown, the height H1 of the first cover 110 is less than the height H2 of the second cover 120. In the space-constrained vehicle environment, this high-low cover design can make more rational use of the space around the compressor, reduce the volume of the intake muffler 100, avoid interference with other vehicle components, and ensure the freedom and safety of installation of the compressor and its accessories in confined spaces. The higher design of the second cover 120 can increase the volume of the muffler cavity, which is beneficial for the multiple reflections and attenuation of sound waves, especially in the high-frequency noise reduction effect. At the same time, it simplifies the overall structure of the intake muffler 100, avoids the need for complex internal components, and thus reduces manufacturing costs. Furthermore, this design makes it easier to assemble the intake muffler 100 onto the compressor, reducing the complexity and time required for assembly. It should be noted that the height H1 of the first cover 110 refers to the height of the main body 111.

[0042] Of course, in other optional embodiments not shown in the figures of this application, the height H1 of the first cover 110 is equal to or greater than the height H2 of the second cover 120, and can be adjusted according to actual application requirements.

[0043] like Figure 1 As shown, the ratio between the cavity height H and the length L of the intake muffler 100 is greater than or equal to 0.25 and less than or equal to 0.6. By controlling the ratio between the height and length of the intake muffler 100, the internal acoustic environment of the intake muffler 100 can be adjusted to conform to a specific acoustic cavity modal distribution. When this ratio is within a specific range, the intake muffler 100 can effectively utilize its internal acoustic characteristics, especially for high-frequency noise in the 3500~4500Hz range, achieving better absorption and reduction, and significantly improving the sound quality during compressor operation. By effectively controlling noise, especially high-frequency noise that the human ear is sensitive to, this design can significantly reduce user auditory fatigue and improve riding comfort. Under this height-to-length ratio constraint, the structural design of the intake muffler 100 can better prevent lubricating oil from splashing and backflowing during compressor operation. The muffler is tall enough in the vertical direction to effectively prevent lubricating oil from rising to the air inlet 114, while the length control helps to form a stable and continuous airflow channel, reducing the risk of oil being carried into the compressor by airflow vortex.

[0044] This application stipulates that the ratio between the cavity height H and the length L of the intake muffler 100 is greater than or equal to 0.25 and less than or equal to 0.6. Compared to intake mufflers 100 with excessively long or high proportions, this design ensures that the intake muffler 100 maintains a compact overall structure while meeting noise reduction performance requirements. This not only saves space and reduces the impact on the layout of surrounding components, but also reduces material consumption and production costs.

[0045] In a specific embodiment of this application, the ratio of the cavity height H of the intake muffler 100 to the length L of the intake muffler 100 is H / L = 0.38.

[0046] In addition, in the vehicle environment, compressors often face complex operating conditions such as bumps and tilts. The intake muffler 100 with this design ratio can maintain a stable noise reduction effect and reliable oil management under various conditions, which enhances the operating stability and reliability of the compressor system, especially in application scenarios with limited space and harsh operating conditions.

[0047] like Figure 2 and Figure 5As shown, the first cover 110 has a body 111, and an air intake channel structure 112 is disposed on the outer surface of the body 111, forming an air intake channel between the two. That is, the inner wall of the air intake channel structure 112 and the outer surface of the body 111 form an air intake channel. The end of the air intake channel structure 112 away from the air intake hole 114 has an inlet and extends to the edge of the second side 119 of the first cover. The first side 115 of the first cover is adjacent to the second side 119 of the first cover. The air intake channel structure 112 and the body 111 are integrally formed. By disposing of the air intake channel structure 112 on the outer surface of the body 111 of the first cover 110 and forming an air intake channel, the airflow can be effectively guided and controlled. The intake passage structure 112 has an inlet at one end away from the intake port 114, extending to the edge of the body 111. This arrangement allows the airflow to be pre-regulated by the intake passage before entering the silencer chamber, reducing turbulence and noise generated by the direct impact of the airflow on the inside of the silencer chamber, thereby improving the absorption and attenuation capability of the intake silencer 100 for high-frequency noise. The inlet of the intake passage structure 112, being away from the intake port 114 and extending to the edge of the body 111, forms a physical barrier during compressor operation, effectively preventing lubricating oil from entering the intake passage structure 112 through splashing. Furthermore, the lubricating oil tends to flow along the outer surface of the first cover 110. This design helps guide the oil back to the oil sump at the bottom of the compressor, preventing oil from entering the interior of the intake silencer 100 and improving the reliability of the intake silencer 100. Compact structure and cost savings: The external design of the air intake channel structure 112 and its integration with the body 111 of the first cover 110 avoids the construction of complex internal channels, simplifies the structure of the intake muffler 100, and helps to achieve efficient noise reduction within a limited vehicle space. At the same time, this design reduces the amount of materials used and lowers manufacturing costs.

[0048] Furthermore, the arrangement of the intake channel structure 112 makes it easier to form during the production process, reducing manufacturing difficulty. At the same time, this design makes the assembly process of the intake muffler 100 and the compressor more intuitive and convenient, reducing the possibility of assembly errors and improving assembly efficiency.

[0049] In addition, the design of the air intake channel structure 112 extending to the edge of the body 111 can optimize the distribution of airflow before entering the silencer cavity, reduce airflow turbulence, and help form a more stable and smooth airflow, reducing additional noise caused by irregular airflow and further improving the efficiency of the intake silencer 100.

[0050] In an optional embodiment of this application, the air intake channel structure 112 may be a ring-shaped structure or other semi-enclosed anti-splash structure, which can be adjusted according to implementation requirements.

[0051] In one optional embodiment of this application, the air inlet 114 is a circular hole with a diameter greater than or equal to 2 mm and less than or equal to 4 mm. This design optimizes the shape and size of the air inlet 114, reducing turbulence and noise during airflow while ensuring sufficient gas throughput to maintain compressor operating efficiency. This dimensional control facilitates effective reflection and absorption of sound waves within the cavity of the intake silencer 100, especially at high frequencies, achieving excellent noise reduction. The circular hole design also simplifies the manufacturing process, reduces production costs, and facilitates cleaning, preventing oil accumulation and blockage, thus ensuring long-term operational stability and ease of maintenance.

[0052] In another optional embodiment of this application, the air inlet 114 is a polygonal hole with a side length greater than or equal to 2 mm and less than or equal to 4 mm. By rationally planning the shape and size of the air inlet 114, it is beneficial to ensure the reliability of its use, guarantee that the gas in the air intake channel structure 112 can stably enter the air intake chamber 140 through the air inlet 114, ensure stable airflow, and guarantee the noise reduction effect. The shape and size of the air inlet 114 can be reasonably adjusted according to actual needs, and this application does not impose any limitations.

[0053] like Figure 3 and Figure 5 As shown, the first cover 110 also has an air outlet 116. The air outlet chamber 150 is connected to the air outlet channel structure 113 through the air outlet 116. The air outlet 116 and the air outlet channel structure 113 are positioned close to the center of the first cover 110 relative to its edge. The extension direction of the air outlet channel structure 113 is different from the extension direction of the air inlet channel structure 112. Positioning the air outlet 116 and the air outlet channel structure 113 close to the center of the first cover 110 reduces turbulence at the air outlet 116 compared to positioning them at the edge, ensuring smooth gas flow and reducing additional noise generation during the outflow process. By designing the extension direction of the air outlet channel structure 113 to differ from that of the air inlet channel structure 112, direct collision between the intake and exhaust airflows can be avoided, reducing acoustic resonance generated during airflow ingress and egress, and further improving the noise reduction performance of the intake silencer 100 in the high-frequency range. At the same time, this design helps to balance the overall structure of the intake muffler 100, while making full use of the limited space to ensure the freedom and stability of the intake muffler 100 in the compact vehicle environment.

[0054] Specifically, the extension direction of the air outlet channel structure 113 is perpendicular to the body 111 of the first cover 110, and the extension direction of the air outlet channel structure 113 is perpendicular to the extension direction of the air inlet channel structure 112. The air outlet channel structure 113 is located in the middle region along the length of the first cover 110. The air inlet end of the air outlet channel structure 113 extends into the interior of the first cover 110, and the distance D between the air inlet end of the air outlet channel structure 113 and the inner wall surface of the first cover 110 is greater than or equal to 3 mm and less than or equal to 8 mm. By planning the extension direction of the air outlet channel structure 113 to be perpendicular to the body 111 of the first cover 110 and perpendicular to the extension direction of the air inlet channel structure 112, this design can effectively guide the airflow to enter from the side of the first cover 110 and then flow vertically upward or downward, avoiding direct collision between the intake and exhaust airflows, reducing airflow turbulence and eddy current generation, thereby reducing flow noise and improving the overall cooling efficiency of the muffler.

[0055] In the embodiments of this application, the air outlet channel structure 113 is located in the middle region along the length of the first cover 110, and its air inlet extends into the interior of the first cover 110, with the distance D from the inner wall surface controlled between 3mm and 8mm. That is, the height of the air inlet protruding from the inner wall surface of the first cover 110 is between 3mm and 8mm. This layout ensures the longest possible airflow path within the silencing cavity, increasing the number of sound wave reflections and the contact area of ​​the silencing material. Especially for high-frequency noise, it significantly improves the silencing effect and reduces user auditory fatigue. The vertical arrangement of the air outlet channel structure 113 and its position close to the center of the first cover 110 help maintain the overall structural balance of the intake muffler 100, reducing the risk of structural deformation or damage due to bumps and vibrations in a vehicle environment. Simultaneously, this layout fully utilizes the internal space of the intake muffler 100, adapting to the compact installation environment of the vehicle refrigerator compressor. Furthermore, it prevents the airflow from carrying refrigerant oil out of the intake muffler 100 and into the compressor cylinder, ensuring the stability of the compressor's operation.

[0056] In one optional embodiment of this application, the cross-section of the air outlet channel structure 113 along its extension direction is circular, with a diameter greater than or equal to 2 mm and less than or equal to 4 mm. This arrangement effectively smooths the airflow, reduces turbulence and vortices, thereby reducing flow noise and ensuring the high-frequency noise suppression capability of the intake silencer 100. The circular cross-section enhances the uniformity of the air outlet channel structure 113, prevents the formation of dead airflow angles, reduces airflow resistance, and improves gas flow efficiency. Precise control of the diameter ensures sufficient flow while avoiding additional sound wave reflection caused by an excessively large channel, achieving a balance between noise reduction and airflow.

[0057] Of course, in other alternative embodiments of the application, the cross section of the air outlet channel structure 113 along its extension direction can also be set as a polygon, which can be set according to the actual situation, and this application does not impose any restrictions.

[0058] In one optional embodiment of this application, the length of the air outlet structure 113 in the direction perpendicular to the first cover 110 is greater than 5 mm. By planning the length of the air outlet structure 113, the situation where the outlet of the air outlet structure 113 is too close to the wall of the first cover 110, causing airflow vortices, is avoided, thus preventing energy loss.

[0059] like Figure 4 As shown, one or more oil drain ports 121 are provided on the side surface of the second cover 120 away from the first cover 110. When there are multiple oil drain ports 121, at least two of the multiple oil drain ports 121 are respectively provided at two corners on the same side of the second cover 120, and oil drain ports 121 are provided in both the air inlet chamber 140 and the air outlet chamber 150.

[0060] In a specific embodiment of this application, there are two oil drain ports 121. The two oil drain ports 121 are respectively located at two corners on the same side of the second cover 120, and oil drain ports 121 are correspondingly provided in both the air inlet chamber 140 and the air outlet chamber 150. The intake muffler 100 has a first side and a second side arranged opposite to each other. The first side 160 of the intake muffler has an oil drain port 121, and the first side 160 of the intake muffler is located closer to the motor 300 than the second side 170 of the intake muffler. That is, the oil drain port 121 is located on the side of the intake muffler 100 closer to the motor 300. The oil drain ports 121 located at the corners utilize gravity, which can more effectively guide the lubricating oil out of the intake muffler 100, preventing oil from remaining inside the intake muffler 100 and affecting the purity of the airflow and the heat exchange efficiency of the system. By positioning the oil drain port 121 close to the motor 300, even under complex operating conditions such as vehicle tilting or bumping, it ensures that lubricating oil will not flow back into the intake chamber 140 or exhaust chamber 150, preventing oil from being sucked into the compressor cylinder, ensuring stable operation of the compressor's lubrication system, and avoiding system failure. Simultaneously, ensuring that the oil drain port 121 on the intake muffler 100 is always on the side away from the high oil level in the compressor oil sump effectively avoids the risk of oil backflow caused by compressor tilting under complex road conditions, significantly improving the reliability of compressor operation. By providing oil drain ports 121 in both the intake chamber 140 and the exhaust chamber 150, tiny oil droplets carried in by the airflow can be promptly removed, reducing the possibility of oil accumulation in the intake muffler 100, preventing oil clogging of the airflow channel, maintaining the long-term operating efficiency of the muffler, and thus ensuring the noise reduction effect.

[0061] In a specific embodiment of this application, the two oil drain ports 121 are located at the lowest point in the width direction of the second cover 120, and the two oil drain ports 121 are the same size. The oil drain ports 121 are circular and the diameter of the oil drain ports 121 is in the range of greater than or equal to 0.5 mm and less than or equal to 1.5 mm.

[0062] Specifically, a partition 122 is disposed on at least one of the first cover 110 and the second cover 120, and the first cover 110 or the second cover 120 without a partition 122 has a positioning structure for engaging with the edge of the partition 122. The positioning structure is a positioning rib 117 or a positioning groove. After the first cover 110 and the second cover 120 are connected, the edge of the partition 122 engages with the positioning structure to form an air inlet chamber 140 and an air outlet chamber 150.

[0063] In a specific embodiment of this application, a partition 122 is provided on the second cover 120. The partition 122 extends to the bottom of the second cover 120 from the side away from the first cover 110. The first cover 110 has a positioning structure, which includes two positioning ribs 117. The two positioning ribs 117 are spaced apart and form a snap-fit ​​gap. The partition 122 extends into the snap-fit ​​gap toward the edge of the first cover 110. By extending the partition 122 into the snap-fit ​​gap of the first cover 110, precise alignment and firm fixation between the second cover 120 and the first cover 110 are achieved, ensuring a stable connection between the two parts under complex working conditions and avoiding airflow leakage and increased noise caused by relative movement. At the same time, the partition 122 extending to the bottom combines with the positioning ribs 117 of the first cover 110 to form a structure that isolates the air intake chamber 140 and the air outlet chamber 150, while also forming a reinforcing structure. This improves the overall strength and deformation resistance of the intake muffler 100, ensuring durability and reliability in the vehicle environment. The snap-fit ​​gap and the fit between the baffle 122 simplify the assembly process of the intake muffler 100, eliminating the need for additional fasteners, reducing assembly difficulty and time, and reducing production costs.

[0064] like Figure 5 As shown, two positioning ribs 117 are arranged parallel and spaced apart. The edge of the positioning rib 117 facing the second cover 120 protrudes from the opening of the first cover 110. The height of the positioning rib 117 in the direction perpendicular to the first cover 110 is greater than or equal to 0.5 mm and less than or equal to 2 mm. This arrangement provides a space for the edge of the partition 122 to accommodate the two ribs, ensuring a stable fit. At the same time, this arrangement provides alignment for the installation of the first cover 110 and the second cover 120, ensuring precise alignment during assembly, avoiding airtightness problems caused by component misalignment, and enhancing the structural stability and assembly efficiency of the intake muffler 100.

[0065] Specifically, the height of the positioning rib 117 is controlled within a specific range, ensuring sufficient positioning support while avoiding excessive increase in the thickness of the first cover 110. This optimizes the layout of the intake muffler 100 within a compact space, allowing it to adapt to the space constraints of the vehicle refrigerator compressor. The protruding design of the positioning rib 117 simplifies the assembly process between the second cover 120 and the first cover 110, avoiding the need for additional fasteners, reducing assembly difficulty and time, and also reducing production costs and potential maintenance complexity.

[0066] In a specific embodiment of this application, the edge of the partition 122 facing the first cover 110 protrudes from the opening of the second cover 120, and the protrusion height of the partition 122 is greater than 0 mm and less than or equal to 2 mm. That is, the height of the partition 122 protruding from the opening of the second cover 120 is within the range of greater than 0 mm and less than or equal to 2 mm. The protruding design of the partition 122 ensures precise alignment between the second cover 120 and the first cover 110 during assembly. The controlled protrusion height enhances the stability of the connection, effectively prevents relative displacement during operation, and ensures the overall airtightness of the intake muffler 100.

[0067] In an optional embodiment of this application, the partition 122 is connected to the two positioning ribs 117 by nesting, snap-fitting, or bonding. Through the cooperation of the partition 122 and the two positioning ribs 117, the partition 122 can divide the silencing cavity into an air inlet cavity 140 and an air outlet cavity 150, ensuring the reliability of the two cavities.

[0068] In an optional embodiment of this application, the ratio of the volume of the inlet chamber 140 to the volume of the outlet chamber 150 is greater than or equal to 0.3 and less than or equal to 0.7. This configuration, where the volume of the outlet chamber 150 is larger than that of the inlet chamber 140, optimizes the propagation path of sound waves within the silencer cavity, effectively absorbing sound waves of specific frequencies, particularly high-frequency noise in the 3500-4500Hz range, achieving better noise reduction. Simultaneously, it helps maintain airflow balance during the inlet and outlet processes, avoiding additional noise and pressure fluctuations caused by airflow imbalance, thus improving the stability of compressor operation. A reasonable volume ratio maximizes the acoustic performance of the silencer, significantly enhancing its ability to suppress high-frequency noise by adjusting the reflection and interference of internal sound waves.

[0069] In a specific embodiment of this application, the ratio of the volume of the air inlet chamber 140 to the volume of the air outlet chamber 150 is 0.5.

[0070] In the specific embodiments of this application, the thickness of the partition 122 is greater than or equal to 0.5 mm and less than or equal to 1.5 mm. By rationally planning the thickness of the partition 122, on the one hand, the dimensional rationality of the partition 122 can be ensured, thus guaranteeing structural strength. On the other hand, it avoids the partition 122 occupying too much space in the silencing cavity, ensuring that the silencing cavity has a sufficiently large gas flow space.

[0071] In a specific embodiment of this application, the intake muffler 100 further includes a flow guide channel structure. The two ends of the flow guide channel structure are respectively connected to the intake chamber 140 and the exhaust chamber 150. The flow guide channel structure is located in the exhaust chamber 150. One end of the flow guide channel structure passes through the partition 122 and communicates with the intake chamber 140, while the other end communicates with the exhaust chamber 150. The partition 122 has a communication notch 1221. One end of the flow guide channel structure communicates with the communication notch 1221. When the partition 122 has the communication notch 1221, the communication notch 1221 is formed at the corner of the partition 122, and the communication notch 1221 is located on one side edge of the partition 122 near the first cover 110. Gas entering the intake chamber 140 can only enter the exhaust chamber 150 through the flow guide channel structure, and then exit the intake muffler 100 through the exhaust channel structure 113.

[0072] The presence of the flow guide channel structure precisely controls the airflow path from the inlet chamber 140 to the outlet chamber 150, preventing irregular diffusion of airflow within the chamber, effectively reducing turbulence and improving airflow smoothness. Through the ingenious combination of the connecting notch 1221 and the flow guide channel structure, the principles of sound wave reflection and interference can be utilized to further reduce noise at specific frequencies, especially in the 3500~4500Hz high-frequency range, improving the overall noise reduction efficiency of the muffler. The connecting notch 1221, designed at the corner of the partition 122 and close to the first cover 110, helps prevent lubricating oil from accumulating or flowing back inside the chamber, reducing the possibility of accidental oil entry into the compressor cylinder and ensuring normal lubrication and stable operation of the compressor. The combined design of the flow guide channel structure and the connecting notch 1221 of the partition 122 takes into account the space limitations of the vehicle refrigerator compressor, achieving a compact structure while ensuring necessary acoustic performance, adapting to the usage requirements of the complex vehicle environment.

[0073] In an optional embodiment not shown in the figures of this application, the partition 122 has a connecting hole, one end of the flow channel structure is connected to the connecting hole, and the connecting hole is located on the side of the partition 122 near the first cover 110.

[0074] In a specific embodiment of this application, the flow guide channel structure is circular along a cross-section perpendicular to it, and the diameter of the flow guide channel structure along the cross-section perpendicular to it is greater than or equal to 2 mm and less than or equal to 4 mm. By rationally planning the shape and size of the flow guide channel structure, it is beneficial to ensure the flow guiding effect, ensuring that the gas in the intake chamber 140 can stably enter the exhaust chamber 150 through the flow guide channel structure, further ensuring the noise reduction effect of the intake muffler 100.

[0075] In an optional embodiment not shown in the figures of this application, the flow channel structure is polygonal along a cross section perpendicular to it, with the side length of the polygon being greater than or equal to 2 mm and less than or equal to 4 mm.

[0076] like Figure 3 and Figure 4 As shown, the flow channel structure includes a flow guide rib 118 and a flow guide plate 123. The flow guide rib 118 is disposed on the surface of the first cover 110 facing the second cover 120. The flow guide plate 123 is connected to the inner wall of the partition 122 and the second cover 120, and the flow guide plate 123 is open on the side facing the first cover 110, so that after the first cover 110 and the second cover 120 are assembled, the flow guide rib 118, the inner surface of the first cover 110, the flow guide plate 123, and the inner wall of the second cover 120 together form the channel portion of the flow channel structure. The extension direction of the flow channel structure is perpendicular to the partition 122. The combined use of the flow guide rib 118 and the flow guide plate 123 can accurately guide the airflow direction, reduce turbulence in the airflow inside the muffler, thereby improving the aerodynamic performance and noise reduction effect of the muffler. The design of the flow channel structure can control the propagation path of sound waves within the cavity. By utilizing multiple reflections and interferences of sound waves, it effectively reduces sound at specific frequencies, with a particularly significant suppression effect on high-frequency noise. The open design of the flow guide plate 123 and the layout of the flow guide ribs 118 together form a protective mechanism, effectively preventing lubricating oil from splashing into the intake channel structure 112, thus preventing oil from entering the compressor and affecting its performance and lifespan. Through the combination of the flow guide ribs 118 and the flow guide plate 123, the structural layout is optimized, ensuring both noise reduction and rational space utilization, adapting to the compact space requirements of the vehicle refrigerator compressor. This design simplifies the assembly process of the intake muffler 100. The cooperation between the flow guide ribs 118 and the flow guide plate 123 requires no additional fasteners, making assembly simpler and faster, reducing production costs and improving manufacturing efficiency.

[0077] Specifically, the end of the guide plate 123 is integrally formed with the partition plate 122, and the side of the partition plate 122 facing the first cover 110 is set higher than the guide plate 123. The end of the guide rib 118 is connected to the end of a positioning rib 117, and the two are integrally formed. This arrangement simplifies the structure of the intake muffler 100, increases the volume of the intake chamber 140 and the exhaust chamber 150, and ensures that after the first cover 110 and the second cover 120 are assembled, the intake chamber 140 and the exhaust chamber 150 are connected only through the guide channel structure, thus ensuring the stability of the airflow.

[0078] In one optional embodiment of this application, both the first cover 110 and the second cover 120 are made of PBT. The first cover 110 and the second cover 120 are snap-fitted or welded together. The wall thickness of the first cover 110 and the second cover 120 is greater than or equal to 1 mm and less than or equal to 2 mm. PBT has high strength and rigidity, and also exhibits good impact toughness. The wall thickness of the first cover 110 and the second cover 120 is carefully planned to ensure both overall structural strength and lightweight design.

[0079] like Figure 7 As shown, this application also provides a compressor, which includes a compressor housing 200 and the aforementioned suction silencer 100. A motor 300 is disposed within the compressor housing 200; the suction silencer 100 is disposed within the compressor housing 200 and located to one side of the motor 300. The suction silencer 100 has a first side and a second side arranged opposite to each other. The first side 160 of the suction silencer has an oil drain port 121, which is positioned closer to the motor 300 than the second side 170. The flow guide channel structure of the suction silencer 100 is located on the first side 160. Thus, even when the compressor is in the worst tilting condition, due to the layout of the oil drain port 121 of the suction silencer 100 offset to the side of the motor 300, the oil drain port 121 is close to the center of the compressor core and is always on the side away from the high oil level in the compressor oil sump. This effectively avoids the risk of oil backflow caused by compressor tilting under complex road conditions, significantly improving the operational reliability of the compressor. Meanwhile, the layout design of the airflow guide channel structure located on the first side, close to the motor 300, can more accurately control the direction of airflow. By guiding the airflow through a preset path, it reduces turbulence and impact of the airflow inside the compressor housing 200, thereby reducing operating noise and improving acoustic performance.

[0080] In other alternative embodiments of this application, the flow channel structure is located on the side of the intake muffler 100 near the motor 300, or on the side of the intake muffler 100 near the compressor housing 200. The position of the flow channel structure can be adjusted according to the actual situation.

[0081] In an optional embodiment of this application, the length L and width W of the intake muffler 100 can be set according to actual needs, and the shape of the intake muffler 100 can be set to be similar to that of the compressor housing 200 and the motor 300. The safe distance between the intake muffler 100 and the compressor housing 200 and other components on the compressor housing 200 is more than 5 mm, and the safe distance between the intake muffler 100 and the motor 300 is more than 2 mm, thereby avoiding interference between the intake muffler 100 and the compressor housing 200 and the motor 300, and ensuring the working stability of the compressor housing 200 and the motor 300.

[0082] Obviously, the embodiments described above are only some, not all, of the embodiments of this utility model. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without inventive effort should fall within the scope of protection of this utility model.

[0083] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0084] It should be noted that the terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in sequences other than those illustrated or described herein.

[0085] The above description is merely a preferred embodiment of this utility model and is not intended to limit the 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. An intake silencer, characterized in that, include: A first cover (110) has an air intake channel structure (112) and an air outlet channel structure (113), both of which are located on the outer surface of the first cover (110), and at least a portion of the air intake channel structure (112) extends along the surface of the first cover (110). The second cover (120) is covered by the first cover (110) to form a sound-absorbing cavity between the two. The first cover (110) also has an air inlet (114) disposed at the end of the air inlet channel structure (112). The air inlet channel structure (112) is connected to the sound-absorbing cavity through the air inlet (114). The air inlet (114) is disposed near the edge of the first cover (110) relative to the center of the first cover (110), and the air inlet (114) is located in the middle region of the first side (115) of the first cover. A partition (122) is disposed in the silencing cavity so that the silencing cavity forms an air inlet cavity (140) and an air outlet cavity (150). The air inlet cavity (140) is connected to the air inlet hole (114), and the air outlet cavity (150) is connected to the air outlet channel structure (113).

2. The intake silencer according to claim 1, characterized in that, The first cover (110) has a body (111), and the air intake channel structure (112) is disposed on the outer surface of the body (111) and forms an air intake channel between the two. The end of the air intake channel structure (112) away from the air intake hole (114) has an inlet and extends to the edge of the second side (119) of the first cover.

3. The intake silencer according to claim 1, characterized in that, The first cover (110) also has an air outlet (116), and the air outlet cavity (150) is connected to the air outlet channel structure (113) through the air outlet (116). The air outlet (116) and the air outlet channel structure (113) are arranged close to the center of the first cover (110) relative to the edge of the first cover (110). The extension direction of the air outlet channel structure (113) is different from the extension direction of the air inlet channel structure (112).

4. The intake silencer according to claim 3, characterized in that, The air outlet channel structure (113) extends perpendicularly to the body (111) of the first cover (110); and / or, The extension direction of the exhaust channel structure (113) is perpendicular to the extension direction of the intake channel structure (112).

5. The intake silencer according to claim 1, characterized in that, The second cover (120) has one or more oil drain ports (121) on the side surface away from the first cover (110). When there are multiple oil drain ports (121), at least two of the multiple oil drain ports (121) are respectively located at two corners on the same side of the second cover (120), and the oil drain ports (121) are correspondingly provided in the air inlet chamber (140) and the air outlet chamber (150).

6. The intake silencer according to claim 1, characterized in that, The partition (122) is disposed on at least one of the first cover (110) and the second cover (120), and the first cover (110) or the second cover (120) without the partition (122) has a positioning structure for engaging with the edge of the partition (122), the positioning structure being a positioning rib (117) or a positioning groove.

7. The intake silencer according to claim 6, characterized in that, The second cover (120) is provided with the partition (122), and the first cover (110) has the positioning structure, which includes two positioning ribs (117). The two positioning ribs (117) are spaced apart and form a snap-fit ​​gap. The edge of the partition (122) extends into the snap-fit ​​gap.

8. The intake silencer according to claim 7, characterized in that, The positioning rib (117) protrudes from the opening of the first cover (110) at its edge facing the second cover (120), and the height of the positioning rib (117) in the direction perpendicular to the first cover (110) is greater than or equal to 0.5 mm and less than or equal to 2 mm; and / or, The partition (122) protrudes from the opening of the second cover (120) on the side facing the first cover (110), and the protrusion height of the partition (122) is greater than 0 mm and less than or equal to 2 mm.

9. The intake silencer according to claim 1, characterized in that, The intake silencer also includes a flow channel structure, which is located in the exhaust chamber (150). One end of the flow channel structure passes through the partition (122) and communicates with the intake chamber (140), while the other end of the flow channel structure communicates with the exhaust chamber (150).

10. The intake silencer according to claim 9, characterized in that, The partition (122) has a connecting hole or a connecting notch (1221), one end of the flow channel structure is connected to the connecting hole or the connecting notch (1221), and when the partition (122) has the connecting notch (1221), the connecting notch (1221) is formed at the corner of the partition (122); and / or, The diameter or side length of the flow channel structure along the cross section perpendicular to it is greater than or equal to 2 mm and less than or equal to 4 mm.

11. The intake silencer according to claim 9, characterized in that, The flow channel structure includes a flow guide rib (118) and a flow guide plate (123). The flow guide rib (118) is disposed on the surface of the first cover (110) facing the second cover (120). The flow guide plate (123) is connected to the partition (122) and the inner wall of the second cover (120). The flow guide plate (123) is open on the side facing the first cover (110) so that after the first cover (110) and the second cover (120) are assembled, the flow guide rib (118), the inner surface of the first cover (110), the flow guide plate (123) and the inner wall of the second cover (120) together form the channel portion of the flow channel structure.

12. The intake silencer according to claim 1, characterized in that, The air outlet channel structure (113) is located in the middle region along the length of the first cover (110). The air inlet end of the air outlet channel structure (113) extends into the interior of the first cover (110), and the distance D between the air inlet end of the air outlet channel structure (113) and the inner wall surface of the first cover (110) is greater than or equal to 3 mm and less than or equal to 8 mm.

13. The intake muffler according to any one of claims 1 to 12, characterized in that, The height H1 of the first cover (110) is less than the height H2 of the second cover (120); and / or, The ratio between the cavity height H of the intake muffler and the length L of the intake muffler is greater than or equal to 0.25 and less than or equal to 0.6, and / or The ratio of the volume of the air inlet chamber (140) to the volume of the air outlet chamber (150) is greater than or equal to 0.3 and less than or equal to 0.7; and / or, The air inlet (114) is a circular or polygonal hole, and the diameter or side length of the air inlet (114) is greater than or equal to 2 mm and less than or equal to 4 mm.

14. A compressor, characterized in that, include: A compressor housing (200) is provided with a motor (300). The intake muffler (100) according to any one of claims 1 to 13, wherein the intake muffler (100) is disposed in the compressor housing (200) and located on one side of the motor (300).

15. The compressor according to claim 14, characterized in that, The intake muffler (100) has a first side and a second side arranged opposite to each other. The first side (160) of the intake muffler has an oil drain port (121). The first side (160) of the intake muffler is arranged close to the motor (300) relative to the second side (170) of the intake muffler. The flow channel structure of the intake muffler (100) is located on the first side (160) of the intake muffler.

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