Air suction silencer and compressor

Abstract

The utility model discloses an air suction silencer and a compressor, the air suction silencer comprises: a housing assembly, which is internally provided with a cavity and is provided with an air suction port and an air exhaust port; the through pipeline is arranged in the cavity, and the two ends of the through pipeline communicate with the air suction port and the air exhaust port correspondingly; wherein the inner wall of at least one part of the through pipeline is arranged to be of a wave-shaped structure which fluctuates in the air suction direction. According to the embodiment of the utility model, the through pipeline communicated with the air suction port and the air exhaust port respectively is arranged in the air suction silencer, and the design of the wave-shaped structure enables refrigerant gas to be separated from the wall surface when flowing to the wave crest and wave trough areas, and then the refrigerant gas is combined with the wall surface again in the wave trough and wave crest areas to form a backflow area; the boundary layer is damaged due to the existence of the backflow area, the refrigerant disturbance capacity is enhanced, the heat exchange performance is enhanced, the air suction overheating of the air suction silencer is effectively reduced, and the air suction efficiency is further improved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, and particularly relates to a suction muffler and a compressor. Background Art

[0002] In a refrigeration system, a suction muffler is a key component. It can not only reduce the noise generated when the compressor sucks air, but also optimize the heat exchange efficiency of the system to a certain extent. However, in the current design technology of suction mufflers, most suction mufflers only focus on the silencing effect and ignore other performances of the suction muffler, especially the heat insulation performance.

[0003] The heat insulation performance refers to the ability of a material or structure to resist heat transfer. In the application scenario of a suction muffler, good heat insulation performance is crucial for maintaining the efficient and stable operation of the compressor system. However, the traditional design of suction mufflers often fails to fully consider this point. During the operation of the compressor, the heat generated is easily used to heat the suction muffler, resulting in too high a suction temperature and reduced suction efficiency. Summary of the Utility Model

[0004] The purpose of the utility model is to provide a suction muffler and a compressor, aiming to solve the problem of overheating of the suction muffler during the operation of the compressor in the prior art.

[0005] The utility model provides a suction muffler, which comprises: a housing assembly, a cavity is arranged inside the housing assembly, and a suction port and an exhaust port are arranged on the housing assembly;

[0006] A through pipe is arranged in the cavity, and both ends of the through pipe are respectively communicated with the suction port and the exhaust port;

[0007] Wherein, at least a part of the inner wall of the through pipe is arranged as a wavy structure that fluctuates along the suction direction.

[0008] Optionally, the through pipe comprises a first through pipe and a second through pipe communicated with the first through pipe. The first through pipe is close to the suction port, the second through pipe is close to the exhaust port, and the wavy structure is arranged on the inner wall of the first through pipe.

[0009] Optionally, a plurality of sound-absorbing holes are arranged on the pipe wall of the second through pipe.

[0010] Optionally, the distance between two longitudinally adjacent sound-absorbing holes ranges from 1 to 3 mm, and the distance between two transversely adjacent sound-absorbing holes ranges from 0.5 to 1.0 mm.

[0011] Optionally, the aperture of the sound-absorbing hole ranges from 0.4 to 1.0 mm.

[0012] Optionally, the cross-sections of the first through pipe and the second through pipe are both rectangular. The sound absorption holes are arranged on four side walls of the second through pipe. Each side wall is provided with multiple rows and multiple columns of the sound absorption holes, and the sound absorption holes on two opposite side walls are symmetrically arranged. The corrugated structure is arranged on four inner walls of the first through pipe.

[0013] Optionally, it further includes a partition plate arranged in the cavity. The through pipe passes through the partition plate and is supported on the partition plate. The partition plate divides the cavity into a first cavity and a second cavity.

[0014] Optionally, the air inlet is close to the first cavity, the air outlet is close to the second cavity. The second through pipe is arranged in the second cavity. One end of the first through pipe passes through the partition plate and extends into the first cavity. The other end of the first through pipe is connected to the second through pipe, and there is a gap between one end of the first through pipe and the air inlet. The first cavity is communicated with the air inlet through the gap.

[0015] Optionally, the air inlet and the air outlet are respectively arranged on adjacent side walls of the housing assembly, and the through pipe is an L-shaped through pipe.

[0016] The present utility model also provides a compressor, including the above-mentioned intake silencer.

[0017] The present utility model discloses an intake silencer and a compressor. In the embodiment of the present utility model, by arranging through pipes respectively communicated with the air inlet and the air outlet in the intake silencer, and arranging a corrugated structure fluctuating along the intake direction on the inner wall of at least a part of the through pipes, this design of the corrugated structure can make the refrigerant gas separate from the wall surface when flowing towards the peak and valley regions, and then recombine with the wall surface in the valley and peak regions to form a recirculation zone. The existence of the recirculation zone destroys the boundary layer, enhances the ability of the refrigerant to be disturbed, enhances the heat exchange performance, effectively reduces the intake superheat of the intake silencer, and further improves the intake efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions of the embodiments of the present utility model, the drawings required for the description of the embodiments will be briefly introduced below. Obviously, the drawings in the following description are some embodiments of the present utility model. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0019] Figure 1 It is a schematic structural diagram of the intake silencer provided by the present utility model;

[0020] Figure 2 Schematic cross-sectional structure diagram of the intake silencer provided by the present utility model;

[0021] Figure 3 is Figure 2 Partial enlarged structure diagram of A in

[0022] Figure 4 is Figure 2 Partial enlarged structure diagram of B in

[0023] Figure 5 Schematic diagram of the principle of gas flowing on the inner wall of the first through pipe provided by the present utility model;

[0024] Figure 6 Schematic structure diagram of the through pipe and the partition provided by the present utility model.

[0025] Explanation of the markings in the figure:

[0026] 1. Housing assembly; 11. Cavity; 111. First cavity; 112. Second cavity; 12. Intake port; 13. Exhaust port; 14. Oil leakage hole;

[0027] 2. Through pipe; 21. Wavy structure; 211. Upper end face; 212. Lower end face; 213. First stage; 214. Second stage; 22. First through pipe; 23. Second through pipe; 231. Sound absorption hole;

[0028] 3. Partition;

[0029] 4. Gap. Detailed implementation manners

[0030] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are part of the embodiments of the present utility model, rather than all of the embodiments. Based on the embodiments in the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present utility model.

[0031] It should be understood that when used in this specification and the appended claims, the terms "include" and "comprise" indicate the presence of the described features, wholes, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, wholes, steps, operations, elements, components, and / or their combinations.

[0032] It should also be understood that the terms used in the description of the present utility model herein are merely for the purpose of describing specific embodiments and are not intended to limit the present utility model. As used in the description of the present utility model and the appended claims, unless the context clearly indicates otherwise, the singular forms "a", "an" and "the" are intended to include the plural forms.

[0033] It should be further understood that the term "and / or" used in the description of the present utility model and the appended claims refers to any combination and all possible combinations of one or more of the associated listed items, and includes these combinations.

[0034] Please refer to Figure 1 and Figure 2 , an embodiment of the present utility model provides an intake silencer, which includes: a housing assembly 1, a cavity 11 is provided inside the housing assembly 1, and an intake port 12 and an exhaust port 13 are provided on the housing assembly 1; a through pipe 2, which is arranged in the cavity 11, and both ends of the through pipe 2 are respectively communicated with the intake port 12 and the exhaust port 13; wherein, at least a part of the inner wall of the through pipe 2 is provided with a wavy structure 21 that fluctuates along the intake direction.

[0035] In this embodiment, in order to solve the problem of overheating of the intake of the intake silencer during the operation of the compressor in the prior art, a wavy structure 21 that fluctuates along the intake direction is provided on at least a part of the inner wall of the through pipe 2.

[0036] Specifically, as Figure 4 and Figure 5 shown, the inner wall surface of the through pipe 2 is a wavy structure 21, which is characterized by the existence of continuously alternating peak and valley regions. When the refrigerant gas flows through these regions, its flow path is no longer a simple straight line or a smooth curve, but a complex and variable wavy line. Specifically, when the refrigerant gas flows from left to right, for the fluid, when passing through the first stage 213, at this time the lower end surface 212 is convex and the upper end surface 211 is concave. That is to say, when the refrigerant gas flows to the first stage 213, due to the change of flow rate and direction, the fluid is separated from the wall surface to a certain extent, forming vortex or turbulent flow phenomena, and a so-called "recirculation zone" is formed on the upper end surface 211. Subsequently, during the process of the refrigerant gas flowing to the second stage 214, these vortex or turbulent flows will recombine with the wall surface again, and a so-called "recirculation zone" is formed on the lower end surface 212.

[0037] The existence of the recirculation zone is crucial for enhancing the heat exchange efficiency. In the traditional smooth wall design, the refrigerant gas easily forms a stable boundary layer along the wall. The refrigerant gas within this boundary layer flows slowly, and the heat exchange efficiency is relatively low. However, the design of the wavy structure 21 continuously disrupts and reconstructs the boundary layer, causing the refrigerant gas to be continuously disturbed during the flow process. This enhances the heat exchange between the refrigerant gas and the wall. This enhanced disturbance not only improves the heat exchange efficiency but also helps to reduce the suction superheat phenomenon within the suction muffler, that is, it reduces the additional heat generated by factors such as friction when the refrigerant gas enters the compressor.

[0038] Finally, after continuous and complex flow and heat exchange processes, the refrigerant gas, carrying the heat absorbed from the suction port 12, is transported through the through pipe 2 to the exhaust port 13 of the suction muffler, and finally further compressed by the compressor and transported to the condenser to release heat.

[0039] It should be noted that the through pipe 2 provided in the cavity 11 has good disassembly and maintainability. The suction port 12 and the exhaust port 13 on the housing assembly 1 are usually designed as standardized interfaces for easy connection with the through pipe 2. At the same time, the design of the wavy structure 21 on the inner wall of the through pipe 2 can be a modular design, enabling separate replacement or repair when necessary, reducing the maintenance cost and downtime.

[0040] Furthermore, as Figure 6 shown, the through pipe 2 includes a first through pipe 22 and a second through pipe 23 connected to the first through pipe 22. The first through pipe 22 is close to the suction port 12, and the second through pipe 23 is close to the exhaust port 13. The wavy structure 21 is provided on the inner wall of the first through pipe 22.

[0041] In this embodiment, in the refrigeration system, the through pipe 2 often bears the flow of the refrigerant gas. By arranging the first through pipe 22 close to the suction port 12, it can ensure that the refrigerant gas has a relatively high temperature and pressure before entering the heat exchanger, thereby improving the heat exchange efficiency. At the same time, the design of the second through pipe 23 close to the exhaust port 13 helps to timely discharge the heat-exchanged refrigerant gas, avoiding retention, accumulation, or backflow phenomena within the second through pipe 23, which may affect the heat exchange effect.

[0042] It should be noted that during the actual operation, the operating conditions of the refrigeration system may change due to load changes, ambient temperature changes, etc. The segmented design of the first through pipe 22 and the second through pipe 23 enables the suction muffler to respond more flexibly to these changes. For example, when the load increases, the fluid volume in the first through pipe 22 can be adjusted to ensure that the refrigeration system has sufficient refrigeration capacity; while when the load decreases, the fluid volume in the first through pipe 22 can be reduced to lower energy consumption and noise.

[0043] In this embodiment, a plurality of sound-absorbing holes 231 are provided on the pipe wall of the second through pipe 23. During the operation of the compressor, it is necessary not only to solve the problem of overheating of the suction muffler during suction, but also to ensure that the suction muffler has a better sound-absorbing effect. Therefore, a plurality of sound-absorbing holes 231 are provided on the pipe wall of the second through pipe 23. After the sound waves are diffused through the pores, the pressure decreases, the flow velocity of the refrigerant gas is diffused and reduced, and then the noise will also decrease.

[0044] Specifically, the through pipe 2 is divided into two sections of pipes. The surface of the inner wall of the first through pipe 22 close to the suction port 12 is a wavy structure 21 that fluctuates left and right. This design can cause the refrigerant gas to separate from the wall surface when flowing towards the peak and trough regions, and then re-combine with the wall surface in the trough and peak regions to form a recirculation zone. The existence of the recirculation zone destroys the boundary layer, enhances the disturbance of the refrigerant gas, improves the heat transfer performance, and effectively reduces the overheating of the suction muffler during suction; after the refrigerant gas enters the second through pipe 23 through the first through pipe 22, it will be transmitted to the exhaust port 13 of the suction muffler. After the sound waves are diffused through the pores, the pressure decreases, the flow velocity is diffused and reduced, and the noise will also decrease. The designs of the first through pipe 22 and the second through pipe 23 can ensure that the suction muffler has a better sound-absorbing effect while solving the problem of overheating of the suction muffler during suction.

[0045] In this embodiment, as Figure 2 and Figure 3 shown, the sound-absorbing holes 231 are arranged in multiple rows and columns. The distance (longitudinal spacing D1) between two adjacent sound-absorbing holes 231 in the longitudinal direction ranges from 1 to 3 mm, and the distance (transverse spacing D2) between two adjacent sound-absorbing holes 231 in the transverse direction ranges from 0.5 to 1.0 mm. The layout and spacing of the sound-absorbing holes 231 affect their attenuation ability for sound waves of different frequencies. A smaller transverse spacing D2 helps to more effectively attenuate high-frequency sound waves because these sound waves have shorter wavelengths and are more sensitive to changes in hole spacing, while the longitudinal spacing D1 is manifested in the attenuation of medium- and low-frequency sound waves, enabling the entire suction muffler to function within a wider frequency range.

[0046] An appropriate hole spacing can also reduce the risk of blockage between two sound-absorbing holes 231. However, an overly small spacing may make it easier for impurities such as dust and particulate matter to accumulate between the holes, affecting the sound-absorbing effect and even causing blockage of the second through pipe 23.

[0047] Furthermore, the aperture R1 of the sound-absorbing hole 231 (i.e., the diameter of the sound-absorbing hole 231) ranges from 0.4 to 1.0 mm. A smaller aperture R1 of the sound-absorbing hole 231 (such as 0.4 to 0.6 mm) usually has a better attenuation effect on high-frequency sound waves because the wavelength of high-frequency sound waves is relatively short, similar to the size of the aperture R1, and is prone to diffraction and scattering, thus being effectively absorbed or reflected. The smaller the aperture R1, the more sound-absorbing holes 231 are distributed on the wall of the second through pipe 23, and the better the noise reduction effect.

[0048] In one embodiment, the cross-sections of the first through pipe 22 and the second through pipe 23 are both rectangular. The sound-absorbing holes 231 are provided on the four side walls of the second through pipe 23. There are multiple rows and multiple columns of sound-absorbing holes 231 on each side wall, and the sound-absorbing holes 231 on the two opposite side walls are symmetrically arranged; the wavy structure 21 is provided on the four inner walls of the first through pipe 22. Compared with the first through pipe 22 and the second through pipe 23 with circular or other complex shapes, a rectangle provides more stable support in a specific direction, which is beneficial to improving the stability of the overall structure of the air intake silencer. Moreover, the long side direction of the rectangle can guide the fluid to flow in the direction from the first through pipe 22 to the second through pipe 23, helping to reduce vortex and turbulence phenomena, thereby improving the fluid transmission efficiency and stability.

[0049] By providing multiple rows and multiple columns of sound-absorbing holes 231 on the four side walls of the second through pipe 23, the noise generated when the fluid passes through can be effectively dispersed and attenuated. These sound-absorbing holes 231 can absorb and dissipate the sound wave energy, reduce the outward propagation of noise, and improve the sound-absorbing effect of the air intake silencer. At the same time, the sound-absorbing holes 231 on the two opposite side walls are symmetrically arranged, which can further optimize the sound-absorbing effect. This symmetrical layout helps to form a more uniform sound field distribution, making the attenuation of noise in all directions more balanced, thereby further improving the overall sound-absorbing efficiency of the air intake silencer.

[0050] Since the wavy structure 21 can change the flow path of the fluid, causing minute disturbances and vortices during the fluid flow, these disturbances help reduce the direct contact area between the fluid and the inner wall of the pipe, thereby reducing the frictional resistance and the intensity of turbulence. Therefore, wavy structures 21 are provided on the four inner walls of the first through-pipe 22, bringing multiple effects, namely, significantly improving the heat exchange efficiency and significantly reducing the suction overheating phenomenon in the suction muffler. At the same time, by providing wavy structures 21 on the four inner walls of the first through-pipe 22, the surface area of the inner wall of the first through-pipe 22 is increased. When the refrigerant gas enters the first through-pipe 22, it can guide the fluid to form a more uniform distribution within the first through-pipe 22, reducing the impact and wear of the fluid on the inner wall of the first through-pipe 22.

[0051] In addition, the wavy structure 21 can also promote the mixing and energy exchange within the fluid, enhancing the transmission uniformity and efficiency of the fluid. At the same time, providing wavy structures 21 on the four inner walls of the first through-pipe 22 will also have a certain scattering and absorption effect on sound waves, bringing a noise reduction effect.

[0052] Furthermore, the suction muffler further includes a partition 3 disposed in the cavity 11. The through-pipe 2 passes through the partition 3 and is supported on the partition 3. The partition 3 divides the cavity 11 into a first cavity 111 and a second cavity 112. In this embodiment, the partition 3 not only serves to divide the cavity 11 but also optimizes the flow path of the fluid within the suction muffler by supporting the through-pipe 2.

[0053] Specifically, when the fluid (refrigerant gas) enters the first cavity 111 through the suction port 12, it will be forced to change its flow direction due to the obstruction of the partition 3, enabling the fluid to flow along the first through-pipe 22 towards the second through-pipe 23, reducing the occurrence of vortex phenomena, thereby improving the stability and efficiency of fluid transmission. At the same time, during this process, part of the noise energy will be absorbed by the partition 3, reducing the propagation of noise; subsequently, when the fluid enters the second through-pipe 23, it will undergo a noise reduction process again, further reducing the noise output. As a support structure for the through-pipe 2, the partition 3 can effectively disperse and bear the pressure and vibration generated during the flow of the through-pipe 2 and the fluid inside it.

[0054] In this embodiment, as Figure 2 shown, the suction port 12 is close to the first cavity 111, the exhaust port 13 is close to the second cavity 112, the second through-pipe 23 is disposed in the second cavity 112, one end of the first through-pipe 22 passes through the partition 3 and extends into the first cavity 111, the other end of the first through-pipe 22 is connected to the second through-pipe 23, and there is a gap 4 between one end of the first through-pipe 22 and the suction port 12. The first cavity 111 is in communication with the suction port 12 through the gap 4.

[0055] The arrangement of the first through pipe 22 and the second through pipe 23 ensures the smooth transmission of fluid within the intake silencer. The gap 4 between one end of the first through pipe 22 and the intake port 12 allows fluid to enter the first cavity 111 with relatively small resistance, and enter the second cavity 112 through the first through pipe 22, reducing the energy loss during fluid transmission and improving the transmission efficiency.

[0056] The relative positional relationships of components such as the intake port 12, the exhaust port 13, the first through pipe 22, the second through pipe 23, and the partition 3 are clear, making the maintenance and debugging of the intake silencer easier. When it is necessary to clean or replace components, each component can be conveniently disassembled and installed without disassembling the entire intake silencer. In addition, the silencing effect can be optimized by adjusting the size of the gap 4 or changing the length of the through pipe 2, etc.

[0057] It should be noted that the debugging process of the intake silencer plays a crucial role in the maintenance and optimization of the intake silencer. It mainly involves evaluating and adjusting the performance of each component of the intake silencer (such as the intake port 12, the exhaust port 13, the first through pipe 22, the second through pipe 23, and the partition 3, etc.) to ensure that the intake silencer can achieve a better silencing effect. Specifically, the debugging process is used to evaluate the performance of the intake silencer under the current working conditions, including the silencing effect, the resistance of fluid flow, the vibration situation, etc. Through debugging, problems existing in the intake silencer, such as excessive noise, poor flow, loose components, etc., can be discovered in a timely manner. For the problems found, the components of the intake silencer are adjusted and optimized to improve its performance.

[0058] Specifically, if it is necessary to adjust the size of the gap 4, first, it is necessary to clarify the problems existing in the current silencing effect, such as excessive noise or difficulty in eliminating noise at specific frequencies. A noise measuring instrument can be used to measure the noise levels at the intake port 12 and the exhaust port 13, and record the data. Analyze the spectral characteristics of the noise to determine the main frequency range that needs to be optimized. According to the analysis results, gradually adjust the size of the gap 4 between one end of the first through pipe 22 and the intake port 12. After each adjustment, re-measure the noise level and compare it with the previous data. Finally, evaluate the adjusted silencing effect to see if it meets the expected goal. If the silencing effect is not ideal, continue to adjust the size of the gap 4 and repeat the steps of measurement and evaluation. It should be noted that when adjusting the size of the gap 4, pay attention not to make it too large or too small, so as not to affect the smoothness of fluid flow in the through pipe 2 and the silencing performance of the intake silencer, and ensure that the adjusted gap 4 has good sealing performance to prevent noise leakage.

[0059] If it is necessary to change the length of the through pipe 2, first determine whether it is necessary to increase or decrease the length of the through pipe 2 according to the noise characteristics and the requirements of fluid transmission. Gradually increase or decrease the length of the through pipe 2 in a predetermined direction (the direction from the first through pipe 22 to the second through pipe 23), pay attention to keeping the joints of the pipes well sealed to prevent air leakage. After adjustment, re-measure the noise level and compare it with the previous data to evaluate whether the sound absorption effect after adjustment has been improved. If the effect after the initial adjustment is not ideal, further change the length of the through pipe 2 or consider optimizing it by combining other sound absorption measures (such as increasing the number of sound absorption holes 231, changing the shape of the through pipe 2, etc.). It should be noted that when changing the length of the through pipe 2, ensure the overall structural stability of the through pipe 2 to avoid the increase of vibration and noise caused by the length change, and ensure that the length of the adjusted through pipe 2 can not only meet the sound absorption requirements but also ensure the smooth transmission of the fluid.

[0060] Furthermore, the air inlet 12 and the air outlet 13 are respectively arranged on the adjacent side walls of the housing assembly 1, and the through pipe 2 is an L-shaped through pipe 2. Preferably, the air inlet 12 is located on the front side wall of the housing assembly 1 and penetrates through the front side wall of the housing assembly 1, and the air outlet 13 is located at the top of the housing assembly 1 and penetrates through the top. Arranging the air inlet 12 on the front side wall and the air outlet 13 at the top helps to improve the heat exchange efficiency.

[0061] The L-shaped through pipe 2 not only changes the flow direction of the fluid but also increases the travel length of the fluid inside the intake silencer, enabling the fluid to have more opportunities to interact with components such as the partition plate 3, the first through pipe 22, and the second through pipe 23 when passing through the intake silencer, thereby further improving the sound absorption effect.

[0062] Furthermore, an oil leakage hole 14 is also arranged on the housing assembly 1. The oil leakage hole 14 is arranged at the bottom of the housing assembly 1 and penetrates through the bottom of the housing assembly 1. During the operation of the compressor, part of the oil will be discharged along the oil leakage hole 14.

[0063] In this embodiment, the main purpose of setting the oil leakage hole 14 is to prevent the oil generated during the operation of the compressor from accumulating inside the housing assembly 1. The oil leakage hole 14 is arranged at the bottom of the second cavity 112. Specifically, during the operation of the compressor, friction between mechanical components will generate a certain amount of oil. If this oil accumulates inside the second cavity 112 for a long time, it will not only increase the operating resistance of the intake silencer but also may cause corrosion to the internal components or affect the overall performance of the compressor. However, the oil leakage hole 14 enables these excess oils to be discharged in time, keeping the inside of the housing assembly 1 clean and dry.

[0064] The present utility model further provides a compressor, which includes the suction muffler described in any one of the above. The suction muffler can be installed on the suction port 12 of the compressor, or can also be installed at the position connecting the suction port 12 of the compressor and the external suction pipeline, and can effectively capture and attenuate the noise carried in the fluid entering the compressor from the outside, thereby reducing the overall noise level of the compressor.

[0065] The various embodiments in the specification are described in a progressive manner. Each embodiment focuses on the differences from other embodiments. The same or similar parts among the various embodiments can be referred to each other. For the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant parts can be referred to the description of the method part. It should be noted that for those of ordinary skill in the art in this technical field, without departing from the principle of the present utility model, several improvements and modifications can be made to the present utility model, and these improvements and modifications also fall within the protection scope of the claims of the present utility model.

[0066] It should also be noted that in this specification, relational terms such as first and second are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the term "comprises", "comprising" or any other variation thereof is intended to cover a non-exclusive inclusion.

[0067] Comprising, so that a process, method, article or device including a series of elements not only includes those elements, but also includes other elements not explicitly listed, or further includes elements inherent to such process, method, article or device. Without more limitations, the element defined by the statement "including one..." does not exclude the existence of another identical element in the process, method, article or device including the said element.

Claims

1. A suction muffler, characterized in that: include: A shell assembly, wherein a cavity is provided inside the shell assembly, and an air intake port and an air exhaust port are provided on the shell assembly; A through pipe is arranged in the cavity, and two ends of the through pipe are respectively connected with the air intake port and the air exhaust port; Wherein, the inner wall of at least a portion of the through-pipe is configured as a wavy structure that fluctuates along the air intake direction.

2. The suction muffler according to claim 1, characterized in that: The through-pipe includes a first through-pipe and a second through-pipe connected to the first through-pipe, the first through-pipe is close to the air intake port, the second through-pipe is close to the air exhaust port, and the wavy structure is arranged on the inner wall of the first through-pipe.

3. The suction muffler according to claim 2, characterized in that: The pipe wall of the second through pipe is provided with a plurality of muffler holes.

4. The suction muffler according to claim 3, characterized in that: The distance between two adjacent muffler holes in the longitudinal direction ranges from 1 to 3 mm, and the distance between two adjacent muffler holes in the transverse direction ranges from 0.5 to 1.0 mm.

5. The suction muffler according to claim 3, characterized in that: The diameter of the muffler hole ranges from 0.4 to 1.0 mm.

6. The suction muffler according to claim 3, characterized in that: The cross-sections of the first through pipe and the second through pipe are both rectangular, the silencer holes are arranged on the four side walls of the second through pipe, the silencer holes on each side wall are arranged in multiple rows and columns, and the silencer holes on two opposite side walls are symmetrically arranged; the wavy structure is arranged on the four inner walls of the first through pipe.

7. The suction muffler according to claim 2, characterized in that: It also includes a partition plate arranged in the cavity, the through-pipe passes through the partition plate and is supported on the partition plate, and the partition plate divides the cavity into a first cavity and a second cavity.

8. The suction muffler according to claim 7, characterized in that: The air intake port is close to the first cavity, and the air exhaust port is close to the second cavity. The second through-pipe is arranged in the second cavity. One end of the first through-pipe passes through the partition and extends into the first cavity. The other end of the first through-pipe is connected to the second through-pipe. There is a gap between one end of the first through-pipe and the air intake port, and the first cavity is connected to the air intake port through the gap.

9. The suction muffler according to claim 1, characterized in that: The air intake port and the air exhaust port are respectively arranged on adjacent side walls of the shell component, and the through-pipe is an L-shaped through-pipe.

10. A compressor, characterized in that: It comprises the suction silencer as described in any one of claims 1 to 9.

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