Exhaust silencer, method and compressor

Abstract

The application discloses an exhaust silencing device, method and compressor, which is used for exhaust silencing treatment of the compressor. The exhaust silencing device comprises a hollow exhaust silencing shell, the exhaust silencing shell comprises a main cavity and a plurality of auxiliary cavities which are circumferentially arranged outside the main cavity and communicated with the main cavity; at least one auxiliary cavity of the plurality of auxiliary cavities is provided with a first partition plate between the main cavity, so as to form a partitioned cavity; the first partition plate is provided with a through hole, so that the partitioned cavity is communicated with the main cavity and a resonance cavity is formed. The application sets up the partitioned cavity in the silencer by the partition plate, and makes the partitioned cavity communicated with the main cavity, so as to form the resonance cavity, thereby making the pneumatic noise oscillate back and forth in the resonance cavity, so that the exhaust silencing effect of the compressor can be effectively enhanced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to an exhaust silencing device, method, and compressor. Background Technology

[0002] The compressor is the core component of a refrigeration system, and compressor noise is a key indicator for evaluating compressors, with aerodynamic noise being a significant component. For rotary compressors, aerodynamic noise is primarily caused by pressure pulsations, which are resulting from the discontinuous compression process. To reduce aerodynamic noise, existing technologies typically install silencing devices, such as exhaust expansion silencers, at the compressor's exhaust port. However, for exhaust expansion silencers, any alteration to the cavity or exhaust port inevitably creates a trough in the silencer's silencing curve, thus failing to achieve the desired silencing effect. Therefore, how to enhance the silencing effect on compressor noise is a problem that those skilled in the art need to solve. Summary of the Invention

[0003] This invention provides an exhaust silencing device, method, and compressor, aiming to enhance the exhaust silencing effect of the compressor.

[0004] In a first aspect, embodiments of the present invention provide an exhaust silencing device for performing exhaust silencing treatment on a compressor. The exhaust silencing device includes a hollow exhaust silencing shell, and the exhaust silencing shell includes a main cavity and a plurality of secondary cavities circumferentially disposed outside the main cavity and communicating with the main cavity.

[0005] At least one of the multiple sub-cavities is provided with a first partition between itself and the main cavity to form a partition cavity;

[0006] The first partition plate is provided with a through hole so that the partition cavity can communicate with the main cavity and form a resonant cavity.

[0007] Furthermore, the first partition is disposed between the secondary cavity, where the airflow velocity is lower than a preset velocity standard, and the main cavity.

[0008] Furthermore, at least one second partition is provided in the partition cavity, which divides the partition cavity into multiple sub-cavities, and the multiple sub-cavities are respectively connected to the main cavity through the through hole.

[0009] Furthermore, the noise reduction frequencies within the multiple sub-cavities are different.

[0010] Furthermore, the second partition is provided with multiple partitions.

[0011] Furthermore, the number of through holes is equal to the number of sub-cavities, or the number of through holes is greater than the number of sub-cavities.

[0012] Secondly, embodiments of the present invention provide an exhaust silencing method, applied to the exhaust silencing device as described in any of the preceding claims, the exhaust silencing method comprising:

[0013] Fluid domain simulation was performed on the airflow inside the exhaust muffler housing to obtain the corresponding flow field streamlines;

[0014] The airflow velocity within the multiple sub-cavities is obtained based on the flow field streamlines;

[0015] The airflow velocity within each of the sub-cavities is compared with a preset velocity standard to obtain the velocity comparison result;

[0016] The secondary cavity is selected based on the flow rate comparison results;

[0017] The first partition is installed on the selected secondary cavity to obtain the partition cavity.

[0018] Furthermore, the step of selecting the secondary cavity based on the flow rate comparison result includes:

[0019] Select a secondary cavity with an airflow velocity lower than the preset velocity standard.

[0020] Furthermore, it also includes:

[0021] The partition cavity is divided into multiple sub-cavities;

[0022] Obtain the frequency of the airflow noise to be silenced;

[0023] Different noise cancellation frequencies are set for each sub-cavity within the same partition cavity according to the airflow noise frequency, so that the range of noise cancellation frequencies of each sub-cavity covers the airflow noise frequency.

[0024] Thirdly, embodiments of the present invention provide a compressor, including the exhaust silencer as described in any of the preceding claims.

[0025] This invention provides an exhaust silencing device, method, and compressor for silencing the exhaust of a compressor. The exhaust silencing device includes a hollow exhaust silencing shell, which contains a main cavity and multiple secondary cavities circumferentially disposed outside the main cavity and communicating with it. At least one of the secondary cavities is separated from the main cavity by a first partition to form a partition cavity. The first partition has through holes to allow the partition cavity to communicate with the main cavity, forming a resonant cavity. This invention uses a partition to create a partition cavity within the silencer, communicating with the main cavity to form a resonant cavity. This allows aerodynamic noise to oscillate back and forth within the resonant cavity, effectively enhancing the exhaust silencing effect of the compressor. Attached Figure Description

[0026] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of an exhaust muffler provided in an embodiment of the present invention;

[0028] Figure 2 This is a schematic diagram of the structure of an exhaust muffler housing in an exhaust muffler device provided in an embodiment of the present invention;

[0029] Figure 3 This is another structural schematic diagram of an exhaust muffler provided in an embodiment of the present invention;

[0030] Figure 4 for Figure 3 The diagram shows a cross-sectional view of the exhaust muffler.

[0031] Figure 5 This is another structural schematic diagram of an exhaust muffler provided in an embodiment of the present invention;

[0032] Figure 6 An example diagram of an exhaust muffler provided in an embodiment of the present invention;

[0033] Figure 7 for Figure 6 The diagram shows a cross-sectional view of the exhaust muffler.

[0034] Figure 8 A schematic flowchart of an exhaust silencing method provided in an embodiment of the present invention;

[0035] Figure 9This is a schematic diagram of a sub-process of an exhaust silencing method provided in an embodiment of the present invention.

[0036] Markings in the image:

[0037] 1. Exhaust muffler housing; 11. Main cavity; 12. Secondary cavity; 13. Partition cavity; 131. Sub-cavity;

[0038] 2. First partition; 21. Through hole;

[0039] 3. Second partition. Detailed Implementation

[0040] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0041] It should be understood that, when used in this specification and the appended claims, the terms "comprising" and "including" indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.

[0042] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.

[0043] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.

[0044] Please see below. Figure 1 and Figure 2 The present invention provides an exhaust silencing device for performing exhaust silencing treatment on a compressor. The exhaust silencing device includes a hollow exhaust silencing shell 1. The exhaust silencing shell 1 includes a main cavity 11 and a plurality of secondary cavities 12 circumferentially disposed outside the main cavity 11 and communicating with the main cavity 11.

[0045] A first partition 2 is provided between at least one of the plurality of sub-cavities 12 and the main cavity 11 to form a partition cavity 13;

[0046] The first partition 2 is provided with a through hole 21 so that the partition cavity 13 is connected to the main cavity 11 and forms a resonant cavity.

[0047] In this embodiment, the exhaust silencing device includes a main cavity 11 and a plurality of secondary cavities 12 arranged around the main cavity 11. A first partition 2 is provided between a portion of these secondary cavities 12 and the main cavity 11, thereby isolating the corresponding secondary cavity 12 from the main cavity 11 and other secondary cavities 12, forming a partition cavity 13. Simultaneously, the first partition 2 is provided with a through hole 21 for connecting the main cavity 11 and the partition cavity 13. This allows the main cavity 11 and the partition cavity 13 to form a resonant cavity, causing aerodynamic noise to oscillate back and forth within the resonant cavity, thus effectively enhancing the exhaust silencing effect of the compressor. In a specific embodiment, such as... Figure 2 As shown, the sub-cavities 12 are all flap-shaped expansion cavities.

[0048] In one embodiment, the first partition 2 is disposed between the secondary cavity 12, where the airflow velocity is lower than a preset velocity standard, and the main cavity 11.

[0049] This embodiment takes into account that although forming a resonant cavity by setting a partition cavity 13 can enhance the exhaust silencing effect, if the position and setting of the first partition 2 are not appropriate, it may affect the airflow inside the muffler, resulting in a decrease in exhaust performance. Therefore, this embodiment selects a secondary cavity 12 with a slower airflow velocity based on the dynamic characteristics of airflow and sets a first partition 2 on it to form a partition cavity 13. This not only reduces the impact on the gas flow inside the partition cavity 13, but also reduces noise without degrading the exhaust performance of the muffler.

[0050] Specifically, this embodiment first performs fluid domain simulation on the interior of the exhaust muffler to obtain the streamlines of the internal flow field, thereby determining the gas flow rate and flow velocity in different regions during the operation of the exhaust muffler. This allows for the identification of the lobe-shaped cavity where the airflow is relatively slow. The fluid domain simulation process mainly consists of the following steps: muffler fluid domain extraction, mesh generation, solution calculation, and post-processing. These steps can all be implemented using ANSYS simulation software. Specifically, the RNGκ-ε turbulence model can be used for the solution calculation step. This is because the model employs the renormalization group method, corrects the turbulent viscosity, and considers flow rotation and swirl, thus better simulating flows with greater streamline curvature and accurately capturing the anisotropic characteristics of the flow field. After the calculation is completed, the flow field streamlines inside the exhaust silencer can be obtained through post-processing (such as data processing). For example, in different lobed sub-cavities 12, the darker the color, the faster the flow velocity, and the more streamlines, the greater the flow volume. Therefore, a lobed sub-cavity 12 with a slower airflow velocity is selected. In addition, the inlet and outlet pressures and temperatures of the simulation boundary conditions can be obtained through actual measurements in the air conditioning system; the sound velocity and density of the fluid material properties required for the simulation can be determined by consulting the parameters of the corresponding refrigerant.

[0051] Combination Figure 3 and Figure 4 In one embodiment, at least one second partition 3 is provided in the partition cavity 13, the second partition 3 divides the partition cavity 13 into multiple sub-cavities 131, and the multiple sub-cavities 131 are respectively connected to the main cavity 11 through the through hole 21.

[0052] In this embodiment, a second partition 3 is installed within the partition cavity 13, dividing the partition cavity 13 into multiple sub-cavities 131. Each sub-cavity 131 is connected to the main cavity 11, thus creating more resonant cavities and further enhancing the compressor's exhaust noise reduction effect. Furthermore, dividing the partition cavity 13 into multiple sub-cavities 131 allows for easier adjustment of the shape of each sub-cavity 131, maximizing the final noise reduction. It is understood that the number of through holes 21 on the first partition 2 is the same as or greater than the number of sub-cavities 131, ensuring that each sub-cavity 131 can communicate with the main cavity 11 through at least one through hole 21. Figure 3 and Figure 4 (because Figure 3 The second partition 3 is positioned horizontally, which makes the view from this angle unclear. Therefore, Figure 3 and Figure 4As shown in the description, the second partition 3 is arranged horizontally, thereby dividing the partition cavity 13 into two sub-cavities 131, which are connected to the main cavity 11 through through holes 21 arranged vertically. Figure 5 As shown, the second partition 3 is arranged longitudinally, thereby dividing the partition cavity 13 into two sub-cavities 131, which are connected to the main cavity 11 through through holes 21 arranged on the left and right sides. That is to say, the position of the through hole 21 on the first partition 2 can be determined by the position of the sub-cavities 131 in the partition cavity 13. When the sub-cavities 131 are vertically separated, the through hole 21 is also vertically separated; when the sub-cavities 131 are horizontally separated, the through hole 21 is also horizontally separated.

[0053] In one embodiment, the noise reduction frequencies within the plurality of sub-cavities 131 are different.

[0054] This embodiment considers that the noise reduction bandwidth of the resonant cavity mechanism is relatively narrow, while aerodynamic noise is broadband noise. Therefore, the noise reduction bandwidth of the resonant cavity may not meet the noise reduction requirements. Thus, this embodiment comprehensively considers the dynamic characteristics of airflow and the design of the resonant cavity to achieve better noise reduction effect and a wider range of applications. Specifically, this embodiment sets each sub-cavity 131 to have a different noise reduction frequency. When forming a resonant cavity with the main cavity 11, there will be a specific difference between the noise reduction frequencies of each resonant cavity, forming a continuous frequency band. This expands the noise reduction frequency range of the resonance, achieves broadband noise reduction effect, and improves the noise reduction effect near specific frequencies.

[0055] For example, if the broadband noise frequency requiring silencing is 900-1100Hz, and the isolation cavity 13 contains three sub-cavities 131, due to the resonant cavity silencing principle, its silencing bandwidth is relatively narrow. Therefore, the silencing frequencies of these three sub-cavities 131 are designed to be 900Hz, 1000Hz, and 1100Hz, thus ensuring sufficient silencing effect for this broadband noise. In practical applications, the silencing frequency difference can be calculated by using the intersection of the transmission loss curves of adjacent design frequencies as the half-power bandwidth frequency point.

[0056] Combination Figure 6 and Figure 7 In one specific embodiment, the second partition 3 is provided with multiple partitions.

[0057] In this embodiment, the partition cavity 13 is divided into multiple sub-cavities 131 by setting multiple second partitions 3. For example, one second partition 3 can divide the partition cavity 13 into two sub-cavities 131, and the two sub-cavities 131 are connected to the main cavity 11 through through holes 21 to form two resonant cavities; two second partitions 3 can divide the partition cavity 13 into three sub-cavities 131, and the three sub-cavities 131 are connected to the main cavity 11 through through holes 21 to form three resonant cavities. And so on, the more second partitions 3 are set, the more sub-cavities 131 can be obtained, thereby forming more resonant cavities.

[0058] In some optional embodiments, the plurality of second partitions 3 can be arranged laterally or vertically. That is, the plurality of second partitions 3 arranged laterally can divide the partition cavity 13 into a plurality of sub-cavities 131 arranged vertically, and the plurality of second partitions 3 arranged vertically can divide the partition cavity 13 into a plurality of sub-cavities 131 arranged horizontally. Correspondingly, for the plurality of sub-cavities 131 arranged vertically, their corresponding through holes 21 are also arranged vertically, and for the plurality of sub-cavities 131 arranged horizontally, their corresponding through holes 21 are also arranged horizontally. Furthermore, regardless of whether they are arranged laterally or vertically, the plurality of second partitions 3 can be arranged parallel to each other or intersecting each other. In summary, the various resonant cavities in this embodiment can be appropriately partitioned to ensure that the space of each resonant cavity is in the optimal shape, thereby achieving maximum noise reduction.

[0059] For example Figure 6 and Figure 7 As shown, two second partition plates 3 are arranged vertically and horizontally inside the partition cavity 13, thus forming three sub-cavities 131. Correspondingly, three through holes 21 are also opened vertically on the first partition plate 2, so that the three sub-cavities 131 can be connected to the main cavity 11 through their respective through holes 21, thereby forming three resonant cavities.

[0060] In practical applications, the noise reduction frequency f of the corresponding cavity can be calculated based on the thickness of the first partition 2, the diameter of the through hole 21, etc. r The formula is as follows:

[0061]

[0062] Among them, c r The velocity of sound in the gas is represented by S, where S is the diameter of the through-hole 21, and l k V0 is the thickness of the first partition 2 and V0 is the volume of the cavity.

[0063] Furthermore, based on the above-mentioned formula for calculating the noise reduction frequency, after setting the noise reduction frequency, the thickness of the first partition 2 and the diameter of the through hole 21 can be adjusted according to the set noise reduction frequency.

[0064] Furthermore, the shape of both the first partition 2 and the second partition 3 can be selected according to actual needs. For example, it can be a flat plate, an arc-shaped plate, a regular or irregular zigzag plate, or an annular cylindrical plate, etc. The shape of the through hole 21 on the first partition 2 can be rectangular, circular, or any other arbitrary shape. Also, the specific installation method of the first partition 2 and the second partition 3 can be welding, gluing, or other fixing methods; this embodiment is not limited in this regard.

[0065] like Figure 8 As shown, this embodiment of the invention also provides an exhaust silencing method, applied to the exhaust silencing device described above, the method specifically including: steps S101 to S105.

[0066] Step S101: Perform fluid domain simulation on the airflow inside the exhaust muffler housing 1 to obtain the corresponding flow field streamlines;

[0067] Step S102: Obtain the airflow velocity within the multiple sub-cavities 12 based on the flow field streamlines;

[0068] Step S103: Compare the airflow velocity in each of the sub-cavities 12 with a preset velocity standard to obtain the velocity comparison result;

[0069] Step S104: Select the secondary cavity 12 according to the flow rate comparison result; specifically, selecting the secondary cavity according to the flow rate comparison result includes: selecting a secondary cavity with an airflow velocity lower than a preset flow rate standard;

[0070] Step S105: Set the first partition 2 on the selected sub-cavity 12 to obtain the partition cavity 13.

[0071] First, based on the aforementioned exhaust silencing device, this embodiment provides a first partition 2 for a portion of the secondary chamber 12 within the exhaust silencing housing 1, thereby isolating the corresponding secondary chamber 12 from the main chamber 11 and other secondary chambers 12 to form a partition chamber 13. Then, a through hole 21 is formed on the first partition 2 to connect the main chamber 11 and the partition chamber 13. This allows the main chamber 11 and the partition chamber 13 to form a resonant cavity, causing aerodynamic noise to oscillate back and forth within the resonant cavity, thus effectively enhancing the exhaust silencing effect of the compressor. In a specific embodiment, all secondary chambers 12 are petal-shaped expansion chambers.

[0072] Secondly, this embodiment takes into account that although forming a resonant cavity by setting a partition cavity 13 can enhance the exhaust silencing effect, if the position and setting of the first partition 2 are not appropriate, it may affect the airflow inside the muffler, resulting in a decrease in exhaust performance. Therefore, this embodiment selects a secondary cavity 12 with a slower airflow velocity based on the dynamic characteristics of airflow and sets a first partition 2 on it to form a partition cavity 13. This not only reduces the impact on the gas flow inside the partition cavity 13, but also reduces noise without degrading the exhaust performance of the muffler.

[0073] Specifically, this embodiment first performs fluid domain simulation on the interior of the exhaust muffler to obtain the streamlines of the internal flow field, thereby determining the gas flow rate and flow velocity in different regions during the operation of the exhaust muffler. This allows for the identification of the lobed cavities with slower airflow. The fluid domain simulation process mainly involves the following steps: muffler fluid domain extraction, mesh generation, solution calculation, and post-processing. These steps can all be implemented using ANSYS simulation software. Specifically, the RNG turbulence model can be used for the solution calculation step. This model employs the renormalization group method to correct turbulent viscosity and also considers flow rotation and swirl, thus better simulating flows with greater streamline curvature and accurately capturing the anisotropic characteristics of the flow field. After the solution calculation is completed, the streamlines of the internal flow field of the exhaust muffler can be obtained through post-processing (e.g., data processing). For example, in different lobed sub-cavities 12, darker colors indicate faster flow velocities, and more streamlines indicate larger flow rates. Therefore, the lobed sub-cavities 12 with slower airflow velocities are selected. Furthermore, the inlet and outlet pressures and temperatures of the simulation boundary conditions can be obtained through actual measurements in the air conditioning system; the sound velocity and density of the fluid material properties required for the simulation can be determined by querying the parameters of the corresponding refrigerant.

[0074] like Figure 9 As shown, in one embodiment, the exhaust silencing method further includes steps S201 to S203.

[0075] Step S201: The partition cavity 13 is partitioned to obtain multiple sub-cavities 131;

[0076] Step S202: Obtain the frequency of the airflow noise to be silenced;

[0077] Step S203: Set different noise reduction frequencies for each sub-cavity 131 within the same partition cavity 13 according to the airflow noise frequency, so that the range of noise reduction frequencies of each sub-cavity 131 covers the airflow noise frequency.

[0078] In this embodiment, by adding a second partition 3 within the partition cavity 13, the partition cavity 13 is divided into multiple sub-cavities 131, and each sub-cavity 131 is connected to the main cavity 11. This creates more resonant cavities, thereby further enhancing the exhaust noise reduction effect of the compressor. Furthermore, dividing the partition cavity 13 into multiple sub-cavities 131 allows for easier adjustment of the shape of each sub-cavity 131, maximizing the final noise reduction. It is understood that the number of through holes 21 on the first partition 2 is the same as the number of sub-cavities 131, or the number of through holes 21 is greater than the number of sub-cavities 131, ensuring that each sub-cavity 131 can communicate with the main cavity 11 through at least one through hole 21. As shown in the figure, the second partition 3 is arranged horizontally, thereby dividing the partition cavity 13 into two sub-cavities 131, one above the other. The two sub-cavities 131 are connected to the main cavity 11 through through holes 21 arranged vertically. As shown in the figure, the second partition 3 is arranged vertically, thereby dividing the partition cavity 13 into two sub-cavities 131, one on the left and one on the right. The two sub-cavities 131 are connected to the main cavity 11 through through holes 21 arranged horizontally. That is to say, the position of the through hole 21 on the first partition 2 can be determined by the position of the sub-cavities 131 in the partition cavity 13. When the sub-cavities 131 are vertically separated, the through hole 21 is also vertically separated; when the sub-cavities 131 are horizontally separated, the through hole 21 is also horizontally separated.

[0079] Furthermore, this embodiment also considers that the noise reduction bandwidth of the resonant cavity mechanism is relatively narrow, while aerodynamic noise is broadband noise. Therefore, the noise reduction bandwidth of the resonant cavity may not meet the noise reduction requirements. Thus, this embodiment comprehensively considers the dynamic characteristics of airflow and the design of the resonant cavity to achieve better noise reduction effect and a wider range of applications. Specifically, this embodiment sets each sub-cavity 131 to have different noise reduction frequencies. In this way, when forming a resonant cavity with the main cavity 11, there will be a specific difference between the noise reduction frequencies of each resonant cavity, forming a continuous frequency band. This expands the noise reduction frequency range of the resonance, achieves broadband noise reduction effect, and improves the noise reduction effect near specific frequencies. For example, if the broadband noise frequency requiring silencing is 900-1100Hz, and the isolation cavity 13 contains three sub-cavities 131, due to the resonant cavity silencing principle, its silencing bandwidth is relatively narrow. Therefore, the silencing frequencies of these three sub-cavities 131 are designed to be 900Hz, 1000Hz, and 1100Hz, thus ensuring sufficient silencing effect for this broadband noise. In practical applications, the silencing frequency difference can be calculated by using the intersection of the transmission loss curves of adjacent design frequencies as the half-power bandwidth frequency point.

[0080] This invention also provides a compressor, including the exhaust silencer device described above.

[0081] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the systems disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the descriptions are relatively simple; relevant parts can be referred to in the method section. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from the principles of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

[0082] It should also be noted that, in this specification, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

Claims

1. An exhaust sound muffling method applied to an exhaust sound muffling device for performing exhaust sound muffling processing on a compressor, characterized by, The exhaust silencing device comprises a hollow exhaust silencing shell, which comprises a main cavity and a plurality of auxiliary cavities arranged circumferentially outside the main cavity and in communication with the main cavity; At least one of the plurality of auxiliary cavities is provided with a first partition plate between the main cavity to form a partitioned cavity; The first partition plate is provided with a through hole to communicate the partitioned cavity with the main cavity and form a resonance cavity; The first partition plate is arranged between the auxiliary cavity and the main cavity, where the airflow flow rate is lower than the preset flow rate standard; The exhaust silencing method comprises: Fluid domain simulation is performed on the airflow in the exhaust silencing shell to obtain the corresponding flow field streamline; The airflow flow rate in the plurality of auxiliary cavities is obtained according to the flow field streamline; The airflow flow rate in each auxiliary cavity is compared with the preset flow rate standard to obtain a flow rate comparison result; The auxiliary cavity is selected according to the flow rate comparison result; The first partition plate is arranged between the selected auxiliary cavity and the main cavity to obtain the partitioned cavity.

2. The exhaust sound reduction method according to claim 1, characterized by, The partitioned cavity is provided with at least one second partition plate, which divides the partitioned cavity into a plurality of sub-cavities, and each of the plurality of sub-cavities is in communication with the main cavity through the through hole.

3. The exhaust sound reduction method according to claim 2, characterized by, The sound attenuation frequencies of the plurality of sub-cavities are different.

4. The exhaust sound reduction method according to claim 2, characterized by, The second partition plate is provided with a plurality of.

5. The exhaust sound reduction method according to claim 2, characterized by, The number of through holes is equal to the number of sub-cavities, or the number of through holes is more than the number of sub-cavities.

6. The exhaust sound reduction method according to claim 1, characterized by, The auxiliary cavity is selected according to the flow rate comparison result, comprising: Select the auxiliary cavity with airflow flow rate lower than the preset flow rate standard.

7. The exhaust sound reduction method according to claim 1, characterized by, Also includes: Partitioning the partitioned cavity to obtain a plurality of sub-cavities; Obtaining the airflow noise frequency to be attenuated; According to the airflow noise frequency, each sub-cavity in the same partitioned cavity is provided with a different sound attenuation frequency, so that the sound attenuation frequency range of each sub-cavity covers the airflow noise frequency.

8. A compressor characterized by, The exhaust silencing method according to any one of claims 1-7 is adopted.

Images