Perforated plate type air flow pulsation attenuation device and compressor

Abstract

The present disclosure proposes a perforated plate type airflow pulsation attenuation device, which is arranged in the exhaust passage of the compressor. The perforated plate type airflow pulsation attenuation device includes a tube body. A first perforated plate, a partition plate, and a second perforated plate are arranged in axial order and at intervals in the tube cavity of the tube body to divide the tube cavity into a first cavity, two resonance cavities, and a second cavity arranged in order, the first perforated plate is provided with a first guide hole, the second perforated plate is provided with a second guide hole, the tube body is provided with a first through hole connected to the first cavity and a second through hole connected to the second cavity, and the outer diameter of the tube body is smaller than the inner diameter of the exhaust passage. Among them, the perforated plate type airflow pulsation attenuation device is configured to generate Helmholtz resonance respectively by utilizing the gas in the exhaust passage to enter the two resonance cavities when the compressor is running, thereby generating an airflow pulsation, and the airflow pulsation is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself.

Description

Technical Field

[0001] The present disclosure relates to the technical field of compressors, and in particular to a perforated plate type airflow pulsation attenuation device and a compressor. Background Art

[0002] Compressors, as equipment that can increase gas pressure and transport gas, are widely used in the fields of petroleum, natural gas, chemical industry, metallurgy, etc. Screw compressors are an important type of compressors. The periodic suction and exhaust of existing screw compressors will cause periodic fluctuations in gas pressure and flow in the exhaust chamber, namely, air flow pulsation. Air flow pulsation will not only reduce the volumetric efficiency of the screw compressor and increase the power consumption of the screw compressor, but also stimulate the vibration of the exhaust chamber to induce aerodynamic noise.

[0003] In addition, the periodic suction and exhaust of the existing screw compressor will cause periodic fluctuations in the gas pressure and flow rate in the exhaust chamber, namely, air flow pulsation. Air flow pulsation will not only reduce the volumetric efficiency of the screw compressor and increase the power consumption of the screw compressor, but also stimulate the vibration of the exhaust chamber and induce aerodynamic noise.

[0004] In order to solve the above technical problems, an existing screw compressor is provided with an air flow pulsation attenuation flange between its exhaust port and the bearing seat flange. Figure 1 and Figure 2 As shown, a side channel 120 is provided inside the air flow pulsation attenuation flange 100, an air flow inlet 121 of the side channel 120 is located on one side of the exhaust port 110 of the air flow pulsation attenuation flange 110, and an air flow outlet 122 of the side channel 120 is located on the other side of the exhaust port 110. Thus, the screw compressor can generate air flow pulsation opposite to the original air flow pulsation by using the above design, thereby canceling out the air flow noise.

[0005] However, for the design of attenuating air flow pulsation of the above-mentioned existing screw compressor, since the newly added air flow pulsation attenuation flange 100 is arranged between the exhaust port and the bearing seat flange, rather than being arranged at the rotor end of the compressor (i.e., the part of the rotor located at the bearing seat flange), the attenuation effect on the air flow pulsation is poor. In addition, it is necessary to increase the structure of the air flow pulsation attenuation flange 100, and the exhaust port and the bearing seat flange need to be structurally modified accordingly. In addition, the structure of the air flow pulsation attenuation flange 100 and the side branch flow channel 120 are complex in shape, requiring a large number of complicated calculations during the design process, and requiring high processing accuracy. Summary of the invention

[0006] A main purpose of the present disclosure is to overcome at least one of the defects of the above-mentioned prior art and provide a perforated plate type airflow pulsation attenuation device capable of attenuating compressor airflow pulsation.

[0007] Another main purpose of the present disclosure is to overcome at least one of the defects of the above-mentioned prior art and provide a compressor with the perforated plate type airflow pulsation attenuation device.

[0008] To achieve the above objectives, the present disclosure adopts the following technical solutions:

[0009] According to one aspect of the present disclosure, a perforated plate type airflow pulsation attenuation device is provided, which is arranged in the exhaust passage of the compressor. Wherein, the perforated plate type airflow pulsation attenuation device includes a tube body. A first perforated plate, a partition plate, and a second perforated plate are arranged in axial order and at intervals in the tube cavity of the tube body to divide the tube cavity into a first cavity, two resonance cavities, and a second cavity arranged in order, the first perforated plate is provided with a first guide hole, the second perforated plate is provided with a second guide hole, the tube body is provided with a first through hole connected to the first cavity and a second through hole connected to the second cavity, and the outer diameter of the tube body is smaller than the inner diameter of the exhaust passage. Wherein, the perforated plate type airflow pulsation attenuation device is configured to generate Helmholtz resonances respectively by utilizing the gas in the exhaust passage to enter the two resonance cavities when the compressor is running, so as to generate airflow pulsation opposite to the airflow pulsation generated by the compressor itself and cancel each other out.

[0010] According to one embodiment of the present disclosure, the radial cross-section of the tube is circular.

[0011] According to one embodiment of the present disclosure, the radial cross section of the exhaust passage is circular, wherein the center of the circle corresponding to the radial cross section of the tube body coincides with the center of the circle corresponding to the radial cross section of the exhaust passage, and an annular gap is formed between the tube body and the exhaust passage.

[0012] According to one embodiment of the present disclosure, the width of the gap is 0.5 mm to 1.5 mm.

[0013] According to one embodiment of the present disclosure, the plane where the first perforated plate is located is perpendicular to the axial direction of the tube body; and / or, the plane where the second perforated plate is located is perpendicular to the axial direction of the tube body; and / or, the plane where the partition is located is perpendicular to the axial direction of the tube body.

[0014] According to one embodiment of the present disclosure, the first cavity is closer to the exhaust port of the exhaust channel than the second cavity, and the distance between the first perforated plate and the corresponding tube port of the tube body is greater than the distance between the second perforated plate and the corresponding tube port of the tube body, so that the volume of the first cavity is greater than the volume of the second cavity.

[0015] According to one embodiment of the present disclosure, the number of the first through holes is greater than the number of the second through holes.

[0016] According to one embodiment of the present disclosure, the first through holes include multiple groups distributed at intervals along the axial direction of the tube body, each group of the first through holes includes multiple first through holes, and the multiple first through holes in the same group are distributed around the outer circumference of the tube body. The second through holes include multiple groups distributed at intervals along the axial direction of the tube body, each group of the second through holes includes multiple second through holes, and the multiple second through holes in the same group are distributed around the outer circumference of the tube body.

[0017] According to one embodiment of the present disclosure, the number of openings in each group of the first through holes and the number of openings in each group of the second through holes are equal, and the number of groups of the first through holes is greater than the number of groups of the second through holes.

[0018] According to one embodiment of the present disclosure, multiple groups of the first through holes are evenly spaced along the axial direction of the tube body, and multiple groups of the second through holes are evenly spaced along the axial direction of the tube body. The spacing between two adjacent groups of the first through holes in the axial direction of the tube body is equal to the spacing between two adjacent groups of the second through holes in the axial direction of the tube body.

[0019] According to one embodiment of the present disclosure, the distance between the first perforated plate and the partition is equal to the distance between the second perforated plate and the partition, so that the volumes of the two resonance cavities are equal.

[0020] According to one embodiment of the present disclosure, the first perforated plate is provided with a plurality of the first flow guide holes, the second perforated plate is provided with a plurality of the second flow guide holes, and the number of the first flow guide holes is equal to the number of the second flow guide holes.

[0021] According to one embodiment of the present disclosure, the plurality of first flow guide holes are evenly distributed, and the plurality of second flow guide holes are evenly distributed.

[0022] According to one embodiment of the present disclosure, the perforated plate type airflow pulsation attenuation device further includes a connecting plate. The connecting plate is provided at an end of the pipe body, the end of the pipe body opens to the connecting plate, and the connecting plate is configured to detachably fix the pipe body at the exhaust port of the exhaust channel.

[0023] According to one embodiment of the present disclosure, an exhaust flange is provided at the exhaust port of the exhaust passage, wherein the connecting plate is a flange structure, and the connecting plate is detachably connected to the exhaust flange.

[0024] According to another aspect of the present disclosure, a compressor is provided, the compressor comprising an exhaust passage. The compressor further comprises a perforated plate type airflow pulsation attenuation device proposed in the present disclosure and described in the above-mentioned embodiment. The perforated plate type airflow pulsation attenuation device is arranged in the exhaust passage. The perforated plate type airflow pulsation attenuation device is configured to generate Helmholtz resonance respectively by utilizing the gas in the exhaust passage to enter the two resonance cavities when the compressor is running, thereby generating an airflow pulsation opposite to the airflow pulsation generated by the compressor itself and making the two cancel each other out.

[0025] According to one of the embodiments of the present disclosure, the compressor is a twin-screw compressor, and the compressor further includes an exhaust bearing seat. The exhaust bearing seat is connected to the exhaust port of the compressor body, and the exhaust bearing seat is provided with two rotor positioning holes; two independent resonance cavities are provided in the exhaust bearing seat, and the two resonance cavities are respectively located on the relatively outer sides of the two rotor positioning holes; the docking surface of the exhaust bearing seat facing the exhaust port is provided with two guide holes, and the two guide holes respectively connect the two resonance cavities with the inner cavity of the compressor. Wherein, the exhaust bearing seat is configured to generate Helmholtz resonances respectively by utilizing the gas in the inner cavity to enter the two resonance cavities when the compressor is running, so as to respectively attenuate the airflow pulsation of the two rotors of the compressor.

[0026] It can be seen from the above technical solutions that the advantages and positive effects of the perforated plate type airflow pulsation attenuation device and compressor proposed in the present disclosure are:

[0027] The perforated plate type airflow pulsation attenuation device proposed in the present disclosure is arranged in the exhaust passage of the compressor and includes a tube body. A first perforated plate, a partition plate, and a second perforated plate are arranged in axial order and at intervals in the tube cavity of the tube body to divide the tube cavity into a first cavity, two resonance cavities, and a second cavity arranged in order. The first perforated plate is provided with a first guide hole, the second perforated plate is provided with a second guide hole, and the tube body is provided with a first through hole connected to the first cavity and a second through hole connected to the second cavity. Through the above design, when the compressor is running, the perforated plate type airflow pulsation attenuation device can utilize the gas in the exhaust passage to enter the two resonance cavities to generate Helmholtz resonance respectively, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Various objects, features and advantages of the present disclosure will become more apparent by considering the following detailed description of preferred embodiments of the present disclosure in conjunction with the accompanying drawings. The accompanying drawings are merely exemplary illustrations of the present disclosure and are not necessarily drawn to scale. In the accompanying drawings, the same reference numerals always refer to the same or similar parts. Among them:

[0029] Figure 1 The invention relates to an air flow pulsation attenuation flange of an existing screw compressor;

[0030] Figure 2 yes Figure 1 A cross-sectional view of an air flow pulsation attenuation flange is shown;

[0031] Figure 3 is a schematic structural diagram of an exhaust bearing seat according to an exemplary embodiment;

[0032] Figure 4 yes Figure 1 A perspective view of the exhaust bearing housing is shown;

[0033] Figure 5 is a schematic structural diagram of an exhaust bearing seat according to another exemplary embodiment;

[0034] Figure 6 is a perspective view of a perforated plate type airflow pulsation attenuation device according to an exemplary embodiment;

[0035] Figure 7 yes Figure 6 Another perspective view of the perforated plate type air flow pulsation attenuation device is shown;

[0036] Figure 8 yes Figure 6 A three-dimensional cross-sectional view of a perforated plate type air flow pulsation attenuation device is shown;

[0037] Fig. 9 yes Figure 6 The structural schematic diagram of the perforated plate type air flow pulsation attenuation device is shown;

[0038] Fig.10 yes Figure 6 A partial plan cross-sectional view of a perforated plate type airflow pulsation attenuation device is shown.

[0039] The following are the descriptions of the reference numerals:

[0040] 100. Air flow pulsation attenuation flange; 222. Second cover plate;

[0041] 110. Exhaust hole; 2221. Second guide hole.

[0042] 120.Bypass channel; 300.Perforated plate type air flow pulsation attenuation device;

[0043] 121. air flow inlet; 310. tube body;

[0044] 122. air flow outlet; 3101. first pipe opening;

[0045] 200. Exhaust bearing seat; 3102. Second pipe opening;

[0046] 201. first positioning hole; 3103. first through hole;

[0047] 202. Second positioning hole; 3104. Second through hole;

[0048] 203. Exhaust port; 311. Partition plate;

[0049] 204. docking surface; 312. first perforated plate;

[0050] 211. first slot; 3121. first flow guide hole;

[0051] 2111. First sub-slot; 313. Second perforated plate;

[0052] 2112. The second sub-slot; 3131. The second diversion hole;

[0053] 212. First cover plate; 314. First cavity;

[0054] 212'. First sub-cover plate 315. Second cavity;

[0055] 2121. first guide hole; 316. first resonance cavity;

[0056] 2122. Connector; 317. Second resonance cavity;

[0057] 221. Second slot; 320. Connecting plate. DETAILED DESCRIPTION

[0058] Typical embodiments that embody the features and advantages of the present disclosure will be described in detail in the following description. It should be understood that the present disclosure can have various changes in different embodiments without departing from the scope of the present disclosure, and the descriptions and drawings therein are essentially for illustrative purposes rather than for limiting the present disclosure.

[0059] In the following description of different exemplary embodiments of the present disclosure, reference is made to the accompanying drawings, which form a part of the present disclosure and in which different exemplary structures, systems and steps that can implement multiple aspects of the present disclosure are shown by way of example. It should be understood that other specific schemes of components, structures, exemplary devices, systems and steps can be used, and structural and functional modifications can be made without departing from the scope of the present disclosure. Moreover, although the terms "above", "between", "within", etc. may be used in this specification to describe different exemplary features and elements of the present disclosure, these terms are used herein only for convenience, such as according to the direction of the examples described in the accompanying drawings. Nothing in this specification should be construed as requiring a specific three-dimensional orientation of the structure to fall within the scope of the present disclosure.

[0060] See also Figure 6 , which representatively shows a stereoscopic view of the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure. In this exemplary embodiment, the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure is described by taking the application to a compressor as an example. It is easy for those skilled in the art to understand that in order to apply the relevant design of the present disclosure to other similar devices, various modifications, additions, substitutions, deletions or other changes are made to the specific embodiments described below, and these changes are still within the scope of the principle of the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure.

[0061] like Figure 6 As shown, in this embodiment, the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure is applied to a compressor as an example. The compressor includes an exhaust passage, and the perforated plate type airflow pulsation attenuation device 300 is arranged in the airflow passage, and the perforated plate type airflow pulsation attenuation device 300 at least includes a tube body 310. Specifically, the tube body 310 has a tube cavity and two tube openings. For ease of understanding and description, the two are named as the first tube opening 3101 and the second tube opening 3102 in the following content. Figures 7 to 10 , Figure 7 , another perspective view of the perforated plate type airflow pulsation attenuation device 300 is representatively shown; Figure 8 A three-dimensional cross-sectional view of the perforated plate type airflow pulsation attenuation device 300 is representatively shown in FIG. Fig. 9 The structural schematic diagram of the perforated plate type airflow pulsation attenuation device 300 is representatively shown in FIG. Fig.10 A partial planar cross-sectional view of the perforated plate type airflow pulsation damping device 300 is representatively shown in FIG. 2 and FIG. 3 are combined with the above drawings to describe in detail the structure, arrangement and functional relationship of each main component of the perforated plate type airflow pulsation damping device 300 proposed in the present disclosure.

[0062] like Figures 6 to 9As shown, in this embodiment, the first perforated plate 312, the partition plate 311 and the second perforated plate 313 are arranged in sequence and at intervals along the axial direction of the tube body 310 in the tube cavity of the tube body 310, so that the tube cavity of the tube body 310 is divided into a first cavity 314, two resonance cavities and a second cavity 315 arranged in sequence along the axial direction by the first perforated plate 312, the partition plate 311 and the second perforated plate 313. For the convenience of understanding and explanation, the two resonance cavities are named as the first resonance cavity 316 and the second resonance cavity 317 in the following content. That is, the first cavity 314, the first resonance cavity 316, the second resonance cavity 317 and the second cavity 315 are arranged in sequence in the axial direction from the first pipe opening 3101 to the second pipe opening 3102. Among them, the first perforated plate 312 is provided with a first guide hole 3121, and the second perforated plate 313 is provided with a second guide hole 3131. In addition, the tube body 310 is provided with a first through hole 3103 and a second through hole 3104. The first through hole 3103 is provided at a position of the tube body 310 corresponding to the first cavity 314, that is, the first through hole 3103 is connected to the first cavity 314. The second through hole 3104 is provided at a position of the tube body 310 corresponding to the second cavity 315, that is, the second through hole 3104 is connected to the second cavity 315. In addition, the outer diameter of the tube body 310 is smaller than the inner diameter of the exhaust passage. That is, when the perforated plate type airflow pulsation attenuation device 300 is arranged in the airflow passage, a gap is formed between the tube body 310 and the airflow passage in the radial cross-sectional direction. Through the above and design, when the compressor is running, the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure can utilize the gas in the exhaust passage to enter the two resonance cavities to generate Helmholtz resonance respectively, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself.

[0063] like Figure 6 and Figure 7 As shown, in this embodiment, the radial cross section of the tube body 310 can preferably be circular, that is, the radial cross section of each section of the lumen (the first cavity 314, the second cavity 315, the first resonance cavity 316, and the second resonance cavity 317) is circular. Through the above design, the airflow state in each cavity of the lumen can be optimized, thereby optimizing the resonance effect of the two resonance cavities. In other embodiments, the radial cross section of the tube body 310 can also be selected from other shapes, such as elliptical, polygonal, etc., and is not limited to this embodiment.

[0064] Preferably, in this embodiment, the radial cross section of the exhaust passage of the compressor is circular as an example for explanation. On this basis, when the radial cross section of the tube body 310 is circular, it is preferable to adopt a design in which the center of the corresponding circle of the radial cross section of the tube body 310 coincides with the center of the corresponding circle of the radial cross section of the exhaust passage. Through the above design, an annular gap can be formed between the tube body 310 and the exhaust passage, and the width of the gap at each position in the radial direction is substantially the same.

[0065] Furthermore, based on the design that the center of the corresponding circle of the radial cross section of the tube body 310 coincides with the center of the corresponding circle of the radial cross section of the exhaust passage, in this embodiment, the width of the gap in the radial direction may preferably be 0.5 mm to 1.5 mm. The above-mentioned design disclosed in the present invention is intended to make the outer diameter of the tube body 310 as close as possible to the inner diameter of the exhaust passage, further optimize the resonance effect of the two resonance cavities, and thus optimize the airflow pulsation attenuation effect of the perforated plate type airflow pulsation attenuation device 300. Therefore, under the premise of ensuring that the processing and manufacturing can be realized, in other embodiments, the width of the gap may also be less than 0.5 mm or greater than 1.5 mm, and is not limited to this embodiment.

[0066] It should be noted that, in this embodiment, when the tube body 310 is arranged in the exhaust passage in such a manner that the center of the corresponding circle of its radial cross section coincides with the center of the corresponding circle of the radial cross section of the exhaust passage, the first pipe opening 3101 of the tube body 310 is farther away from the exhaust port of the exhaust passage than the second pipe opening 3102 of the tube body 310. In the operation of the compressor, the path of the airflow discharged from the exhaust passage by the compressor is roughly as follows: the airflow starts from the upstream of the exhaust passage, enters the first cavity 314 through the first pipe opening 3101, enters the exhaust passage from the first cavity 314 through the first through hole 3103, enters the second cavity 315 through the exhaust passage via the second through hole 3104, and is discharged from the exhaust passage through the second pipe opening 3102. Among them, the airflow can flow between the first cavity 314 and the first resonance cavity 316 through the first guide hole 3121, and the airflow can flow between the second cavity 315 and the second resonance cavity 317 through the second guide hole 3131, so that the first resonance cavity 316 and the second resonance cavity 317 respectively generate Helmholtz resonance, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself. In addition, the exhaust port of the exhaust channel and the outer wall of the second pipe port 3102 of the tube body 310 are relatively closed, that is, when the airflow is discharged through the above path, it can only be discharged through the second pipe port 3102 of the tube body 310, and cannot be discharged from the gap between the exhaust port and the tube body 310.

[0067] like Figure 8 and Fig. 9As shown, in this embodiment, the plane where the first perforated plate 312 is located can be preferably perpendicular to the axial direction of the tube body 310. The plane where the second perforated plate 313 is located can be preferably perpendicular to the axial direction of the tube body 310. And the plane where the partition 311 is located can be preferably perpendicular to the axial direction of the tube body 310. That is, the first perforated plate 312, the second perforated plate 313 and the partition 311 are parallel to each other, and the first cavity 314, the second cavity 315, the first resonance cavity 316 and the second resonance cavity 317 are all cylindrical cavity structures. In other embodiments, the relationship between the plane where at least one of the first perforated plate 312, the second perforated plate 313 and the partition 311 is located and the axial direction of the tube body 310 can also be inclined, and the first perforated plate 312, the second perforated plate 313 or the partition 311 are not limited to being parallel to each other, and are not limited to this embodiment.

[0068] like Figure 8 and Fig. 9 As shown, in this embodiment, since the first cavity 314, the first resonance cavity 316, the second resonance cavity 317 and the second cavity 315 are sequentially arranged in the axial direction from the first pipe opening 3101 to the second pipe opening 3102, the first cavity 314 is closer to the exhaust port of the exhaust channel than the second cavity 315. As mentioned above, the distance between the first perforated plate 312 and the first pipe opening 3101 can be preferably greater than the distance between the second perforated plate 313 and the second pipe opening 3102, that is, the volume of the first cavity 314 can be preferably greater than the volume of the second cavity 315.

[0069] It should be noted that Figure 8 and Fig. 9 The volume difference between the first cavity 314 and the second cavity 315 shown in the figure is only an exaggerated exemplary display. When the design in this embodiment is adopted that the volume of the first cavity 314 is larger than the volume of the second cavity 315, the volume of the first cavity 314 is actually preferably slightly larger than the volume of the second cavity 315. For example, the difference between the distance between the first perforated plate 312 and the first nozzle 3101 and the distance between the second perforated plate 313 and the second nozzle 3102 can be approximately 1 mm to 3 mm. In other embodiments, the volume of the first cavity 314 can also be less than or equal to the volume of the second cavity 315, and is not limited to this embodiment.

[0070] like Figures 6 to 9 As shown, based on the design that the distance between the first perforated plate 312 and the first pipe opening 3101 is greater than the distance between the second perforated plate 313 and the second pipe opening 3102 , in this embodiment, the number of the first through holes 3103 may preferably be greater than the number of the second through holes 3104 .

[0071] like Figures 6 to 9As shown, in this embodiment, there are multiple first through holes 3103, and the multiple first through holes 3103 can preferably be arranged around the outer periphery of the tube body 310, and the multiple first through holes 3103 can preferably include multiple groups distributed axially at intervals, each group of first through holes 3103 is multiple, and the multiple first through holes 3103 in the same group are distributed around the outer periphery of the tube body 310. Through the above design, the airflow in the first cavity 314 can be made more uniform and stable when entering the exhaust channel through the first through holes 3103. In other embodiments, when there are multiple first through holes 3103, other arrangements can also be adopted. Of course, the number of the first through holes 3103 is not limited to multiple, and can also be one, which is not limited to this embodiment.

[0072] like Figures 6 to 9 As shown, in this embodiment, there are multiple second through holes 3104, and the multiple second through holes 3104 can preferably be arranged around the outer periphery of the tube body 310, and the multiple second through holes 3104 can preferably include multiple groups distributed axially at intervals, each group of second through holes 3104 is multiple, and the multiple second through holes 3104 in the same group are distributed around the outer periphery of the tube body 310. Through the above design, the airflow in the exhaust channel can be made more uniform and stable when entering the second cavity 315 through the second through holes 3104. In other embodiments, when there are multiple second through holes 3104, other arrangements can also be adopted. Of course, the number of second through holes 3104 is not limited to multiple, and can also be one, which is not limited to this embodiment.

[0073] Preferably, if Figure 6 , Figure 8 and Fig. 9 As shown, based on the design that the number of first through holes 3103 is greater than the number of second through holes 3104, and based on the design that the above-mentioned multiple groups of first through holes 3103 and second through holes 3104 are distributed around the periphery of the tube body 310, in this embodiment, the number of openings of each group of first through holes 3103 and the number of openings of each group of second through holes 3104 can preferably be equal, and the number of groups of first through holes 3103 can preferably be greater than the number of groups of second through holes 3104. In other embodiments, if the number of first through holes 3103 is desired to be greater than the number of second through holes 3104, and based on the design that the above-mentioned multiple groups of first through holes 3103 and second through holes 3104 are distributed around the circumference of the tube body 310, the number of openings in each group of first through holes 3103 can be different from the number of openings in each group of second through holes 3104. In this case, the number of groups of first through holes 3103 can be equal to or even less than the number of groups of second through holes 3104, which is not limited to the present embodiment.

[0074] Preferably, based on the design that the above-mentioned multiple groups of first through holes 3103 are distributed around the outer circumference of the tube body 310 , in this embodiment, the multiple groups of first through holes 3103 may preferably be evenly spaced along the axial direction of the tube body 310 .

[0075] Preferably, based on the design that the above-mentioned multiple groups of second through holes 3104 are distributed around the outer circumference of the tube body 310 , in this embodiment, the multiple groups of second through holes 3104 may preferably be evenly spaced along the axial direction of the tube body 310 .

[0076] Further, when multiple groups of first through holes 3103 and multiple groups of second through holes 3104 are designed to be evenly spaced along the axis of the tube body 310, the axial spacing between two adjacent groups of first through holes 3103 in the tube body 310 can be further preferably equal to the axial spacing between two adjacent groups of second through holes 3104 in the tube body 310.

[0077] In this embodiment, in the axial direction of the tube body 310, the distance between the first perforated plate 312 and the partition 311 may preferably be equal to the distance between the second perforated plate 313 and the partition 311, that is, the volume of the first resonance cavity 316 may preferably be equal to the volume of the second resonance cavity 317. It should be noted that the above preferred design is based on the tube body 310 being a uniform tubular structure with the same outer diameter at each position in the axial direction. In other embodiments, when the tube body 310 is a tubular structure with other non-uniform outer diameters, if the volume of the first resonance cavity 316 is to be equal to the volume of the second resonance cavity 317, the distance between the first perforated plate 312 and the partition 311 may also be greater than or less than the distance between the second perforated plate 313 and the partition 311, and is not limited to this embodiment.

[0078] like Figures 6 to 8 As shown, in this embodiment, the first perforated plate 312 may preferably be provided with a plurality of first guide holes 3121. Through the above design, the airflow between the first cavity 314 and the first resonance cavity 316 can be made more uniform and stable. At the same time, each first guide hole 3121 and the first resonance cavity 316 form a resonance cavity (Helmholtz resonance cavity), and the design of the plurality of first guide holes 3121 can be regarded as forming a plurality of resonance cavities connected in parallel with each other. In other embodiments, the number of the first guide holes 3121 is not limited to a plurality, and may be one, and is not limited to this embodiment.

[0079] Preferably, based on the design that the first perforated plate 312 is provided with a plurality of first guide holes 3121 , in the present embodiment, the plurality of first guide holes 3121 may preferably be provided on the first perforated plate 312 in a uniform arrangement.

[0080] like Figures 6 to 8As shown, in this embodiment, the second perforated plate 313 may preferably be provided with a plurality of second guide holes 3131. Through the above design, the airflow between the second cavity 315 and the second resonance cavity 317 can be made more uniform and stable. At the same time, each second guide hole 3131 and the second resonance cavity 317 form a resonance cavity (Helmholtz resonance cavity), and the design of the plurality of second guide holes 3131 can be regarded as forming a plurality of resonance cavities connected in parallel. In other embodiments, the number of the second guide holes 3131 is not limited to a plurality, and may be one, and is not limited to this embodiment.

[0081] Preferably, based on the design that the second perforated plate 313 is provided with a plurality of second guide holes 3131 , in this embodiment, the plurality of second guide holes 3131 may preferably be provided on the second perforated plate 313 in a uniform arrangement.

[0082] Further, based on the design that both the first perforated plates 312 and the second perforated plates 313 are multiple, in this embodiment, the number of the first perforated plates 312 may preferably be equal to the number of the second perforated plates 313 .

[0083] Furthermore, based on the design of uniform arrangement of the first perforated plates 312 and the second perforated plates 313, and based on the design that the number of the first perforated plates 312 is equal to the number of the second perforated plates 313, in the present embodiment, the plurality of first perforated plates 312 and the plurality of second perforated plates 313 may preferably be arranged one-to-one in the axial direction of the tube body 310.

[0084] like Fig.10 As shown, it specifically shows a partial cross-sectional view of one of the resonance cavities of the tube body of the perforated plate type airflow pulsation attenuation device proposed in the present disclosure. Taking the first resonance cavity 316 as an example, the distance between the first perforated plate 312 and the partition plate 311 in the axial direction of the tube body (i.e., the depth of the first resonance cavity 316) is D, the thickness of the first perforated plate 312 is t, the aperture of the first guide hole 3121 is d, and the perforation rate of the first perforated plate 312 (i.e., the sum of the areas of all the first guide holes 3121 / the area of ​​the first perforated plate 312×100%) is P. As mentioned above, the attenuation frequency f of the perforated plate pulsation attenuation structure formed by the above-mentioned resonance cavity of the present application is MPA It can be expressed as:

[0085]

[0086] like Figures 6 to 9As shown, in this embodiment, the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure may also preferably include a connecting plate 320. Specifically, the connecting plate 320 is arranged at one end of the pipe body 310, and the end of the pipe body 310 opens to the connecting plate 320. The connecting plate 320 can detachably fix the pipe body 310 at the exhaust port of the exhaust channel. Among them, based on the design that the first pipe port 3101 is farther away from the exhaust port than the second pipe port 3102 in this embodiment, the above-mentioned end pipe port is the second pipe port 3102.

[0087] Preferably, if Figures 6 to 9 As shown, in this embodiment, an example is given in which an exhaust flange is provided at the exhaust port of the exhaust passage of the compressor. On this basis, the connecting plate 320 can preferably adopt a flange structure, and the connecting plate 320 can be detachably connected to the exhaust flange of the compressor, and at the same time, the gap between the pipe body 310 and the exhaust passage can be closed at the exhaust port by using the connecting plate 320 with a flange structure.

[0088] It should be noted that the perforated plate type airflow pulsation damping devices shown in the drawings and described in this specification are only a few examples of the many types of perforated plate type airflow pulsation damping devices that can employ the principles of the present disclosure. It should be clearly understood that the principles of the present disclosure are by no means limited to any details of the perforated plate type airflow pulsation damping devices shown in the drawings or described in this specification or any components of the perforated plate type airflow pulsation damping devices.

[0089] Based on the above detailed exemplary description of the perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure, the compressor proposed in the present disclosure will be exemplified below. It is easy for those skilled in the art to understand that in order to apply the relevant design of the compressor to other equipment, various modifications, additions, substitutions, deletions or other changes are made to the specific embodiments described below, and these changes are still within the scope of the principle of the compressor proposed in the present disclosure.

[0090] In the present embodiment, the compressor proposed in the present disclosure mainly includes an exhaust channel and a perforated plate type airflow pulsation attenuation device 300 proposed in the present disclosure and in the above-mentioned embodiment. Specifically, the perforated plate type airflow pulsation attenuation device 300 is arranged in the exhaust channel. Through the above-mentioned design, when the compressor proposed in the present disclosure is running, the perforated plate type airflow pulsation attenuation device 300 can utilize the gas in the exhaust channel to enter the two resonance cavities to respectively generate Helmholtz resonance, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself. In addition, the exhaust port of the exhaust channel can be connected to the exhaust duct, so that after the airflow after attenuation through the airflow pulsation attenuation is discharged from the second pipe port 3102 (exhaust port), it can be discharged to a downstream position through the exhaust duct.

[0091] It should be noted here that the compressors shown in the drawings and described in this specification are only a few examples of the many types of compressors that can employ the principles of the present disclosure. It should be clearly understood that the principles of the present disclosure are by no means limited to any details of the compressors shown in the drawings or described in this specification or any components of the compressors.

[0092] Based on the above-mentioned design of the compressor proposed in the present disclosure, the present disclosure also proposes an exhaust bearing seat for installation on the compressor proposed in the present disclosure, wherein the compressor proposed in the present disclosure is a twin-screw compressor. Figure 3 As shown, it representatively shows a schematic diagram of the structure of the exhaust bearing seat 200 proposed in the present disclosure. In this exemplary embodiment, the exhaust bearing seat 200 proposed in the present disclosure is explained by taking the application to a twin-screw compressor as an example, that is, when the compressor proposed in the present disclosure includes the exhaust bearing seat 200 proposed in the present disclosure, the compressor is a twin-screw compressor, and the twin-screw compressor also follows the inventive concept of the present disclosure, that is, it is equipped with the perforated plate type airflow pulsation attenuation device proposed in the present disclosure. It is easy for those skilled in the art to understand that in order to apply the relevant designs of the present disclosure to other similar equipment, various modifications, additions, substitutions, deletions or other changes are made to the specific embodiments described below, and these changes are still within the scope of the principle of the exhaust bearing seat proposed in the present disclosure.

[0093] like Figure 3 As shown, in this embodiment, the exhaust bearing seat 200 proposed in the present disclosure is taken as an example of the compressor (twin-screw compressor) proposed in the present disclosure. Specifically, the exhaust bearing seat 200 is installed on the end of the rotor of the twin-screw compressor by using a connection structure such as a flange structure. The twin-screw compressor includes two rotors, namely a first rotor and a second rotor (such as a male rotor and a female rotor). The exhaust bearing seat 200 is provided with two rotor positioning holes, namely a first positioning hole 201 and a second positioning hole 202, and the first positioning hole 201 can be used for the end of the first rotor to be penetrated and positioned, and the second positioning hole 202 can be used for the end of the second rotor to be penetrated and positioned. In addition, the exhaust bearing seat 200 is also provided with an exhaust port 203, and the exhaust port 203 is roughly located between the two rotor positioning holes and is connected to the inner cavity of the twin-screw compressor. For reference, Figure 4 , Figure 4 The figure shows a stereoscopic view of an exhaust bearing seat 200 that can embody the principles of the present disclosure, wherein the structure of two cover plates (which will be described in detail below) is specifically omitted. The structure, arrangement and functional relationship of the main components of the exhaust bearing seat 200 proposed in the present disclosure are described in detail below in conjunction with the above-mentioned figures.

[0094] like Figure 3 and Figure 4As shown, in this embodiment, the exhaust bearing seat 200 proposed in the present disclosure has a docking surface 204 that is connected to the compressor body. Two independent resonance cavities are provided in the exhaust bearing seat 200, and the two resonance cavities are respectively located on the relatively outer sides of the two rotor positioning holes. The docking surface 204 of the exhaust bearing seat 200 is provided with two guide holes, and the two guide holes respectively connect the two resonance cavities with the inner cavity of the compressor. Through the above design, when the twin-screw compressor is running, the exhaust bearing seat 200 proposed in the present disclosure can use the gas in the inner cavity of the twin-screw compressor to enter the two resonance cavities, thereby generating Helmholtz resonances respectively, so as to respectively attenuate the airflow pulsation of the two rotors of the compressor. Compared with the existing scheme, since the exhaust bearing seat 200 proposed in the present disclosure is arranged at the rotor end of the compressor, it has a better attenuation effect on the airflow pulsation.

[0095] It should be noted that when the exhaust bearing seat 200 of the present disclosure is installed at the end of the rotor of the compressor, the exhaust bearing seat 200 is connected and positioned with the end of the rotor through the rotor positioning hole on the one hand, and is installed on the compressor body through the exhaust bearing seat 200 itself with the docking surface 204 on the other hand. The compressor body has an opening connected to its inner cavity, and the exhaust bearing seat 200 is installed and closed in the opening (the exhaust port 203 on the exhaust bearing seat 200 is connected to the inner cavity of the compressor via the opening). Accordingly, the exhaust bearing seat 200 is installed in the compressor body, and together with the opening, forms the exhaust port of the compressor.

[0096] like Figure 3 and Figure 4 As shown, in this embodiment, the docking surface 204 of the exhaust bearing seat 200 is provided with two slots, and the slots of the two slots are respectively provided with a cover plate detachably mounted thereon, and the two cover plates respectively close the two slots to form the above-mentioned two resonance cavities. In other embodiments, the resonance cavity can also be formed in the exhaust bearing seat 200 by other methods or processes, such as integral casting, etc., and is not limited to this embodiment.

[0097] To facilitate understanding, based on the design concept of the present disclosure and the structural characteristics of the twin-screw compressor, in the following content, the slot corresponding to the slot outside the first positioning hole 201 is defined as the first slot 211, the cover plate buckled on the first slot 211 is the first cover plate 212, and the guide hole connected to the first slot 211 is the first guide hole 2121. Correspondingly, the slot corresponding to the slot outside the second positioning hole 202 is defined as the second slot 221, the cover plate buckled on the second slot 221 is the second cover plate 222, and the guide hole connected to the second slot 221 is the second guide hole 2221.

[0098] Preferably, if Figure 3As shown, in this embodiment, for at least one of the two resonance cavities, when the cover plate is buckled on the slot, the surface of the cover plate facing away from the slot can preferably be flush with the docking surface 204 of the exhaust bearing seat 200.

[0099] Furthermore, if Figure 4 As shown, based on the design that the surface of the cover plate is flush with the docking surface 204, in this embodiment, for at least one of the two resonance cavities, the slot may preferably include a first sub-slot 2111 and a second sub-slot 2112. Specifically, the first sub-slot 2111 is opened on the docking surface 204 of the exhaust bearing seat 200. The second sub-slot 2112 is opened on part of the bottom of the first sub-slot 2111, that is, the slot of the second sub-slot 2112 completely falls within the bottom range of the first sub-slot 2111. On this basis, the thickness of the cover plate may preferably be equal to the slot depth of the first sub-slot 2111, and the shape of the orthographic projection of the cover plate on the docking surface 204 is the same as the shape of the orthographic projection of the first sub-slot 2111 on the docking surface 204. Accordingly, when the cover plate is buckled on the slot, the cover plate is embedded in the first sub-slot 2111. That is, the resonance cavity formed by the set of cover plates and the slot is formed by the second sub-slot 2112 and the cover plate. That is, based on the design that the slot includes the first sub-slot 2111 and the second sub-slot 2112 , the volume of the resonance cavity formed by the slot is substantially equal to the volume of the second sub-slot 2112 .

[0100] Furthermore, if Figure 3 As shown, based on the design that the slot includes a first sub-slot 2111 and a second sub-slot 2112, in this embodiment, for at least one of the two resonance cavities, the cover plate can preferably be detachably connected to the slot through a plurality of connectors 2122. On this basis, the position where the connector 2122 is connected to the slot can preferably be located at the portion of the bottom of the first sub-slot 2111 where the second sub-slot 2112 is not provided. That is, by utilizing the structural form of the first sub-slot 2111 and the second sub-slot 2112, the bottom of the first sub-slot 2111 where the second sub-slot 2112 is not provided forms a step structure for the connector 2122 to connect. In other embodiments, no matter what structure the slot adopts, the cover plate can be detachably connected to the slot through the connector 2122, and the connection position of the connector 2122 and the slot can be flexibly adjusted according to the specific structure of the slot, and is not limited to this embodiment.

[0101] As mentioned above, in this embodiment, the connecting member 2122 may preferably be a screw. In other embodiments, the connecting member 2122 may also be a rivet, etc., and is not limited to this embodiment. Figure 3As shown, based on the design of the cover plate, in this embodiment, the two guide holes can be preferably opened on the two cover plates respectively. In other embodiments, the guide holes can also be opened at other positions, which is not limited to this embodiment.

[0102] Preferably, if Figure 3 As shown, based on the design of the guide hole being opened on the cover plate, in this embodiment, the guide hole can be preferably opened at the lower end of the cover plate. Accordingly, the attenuation effect of the exhaust bearing seat 200 proposed in the present disclosure on the rotor airflow pulsation can be further improved. In other embodiments, the guide hole can also be opened at other positions of the cover plate, and the positions of the first guide hole 2121 and the second guide hole 2221 relative to the respective cover plates can be similar or the same, or different, all of which are not limited to this embodiment.

[0103] Preferably, if Figure 3 As shown, since the present embodiment is based on the twin-screw compressor as an example, with reference to the structural characteristics of the twin-screw compressor, the outer diameter of the male rotor and the female rotor is usually larger than the outer diameter of the female rotor due to the different rotor tooth structures. Correspondingly, the aperture of the first positioning hole 201 (used to penetrate and position the male rotor) on the exhaust bearing seat 200 is larger than the aperture of the second positioning hole 202 (used to penetrate and position the female rotor). At the same time, based on the design that the guide hole is opened on the cover plate, in the present embodiment, the first guide hole 2121 can be preferably an oblong hole, that is, the hole shape is roughly rectangular and the two ends are in the shape of circular arcs. And, the second guide hole 2221 can be preferably a circular hole. In other embodiments, whether the guide hole is opened on the cover plate or other arrangements are adopted, the guide hole can also be flexibly selected as a circular hole, an ellipse, an oblong hole, a rectangular hole, a regular polygonal hole, etc., and the hole shapes of the first guide hole 2121 and the second guide hole 2221 can be the same or different, which are not limited to the present embodiment.

[0104] It should be noted that, in the present embodiment, a slot is provided on the docking surface 204 of the exhaust bearing seat 200, and a cover plate matching the slot is buckled at the notch of the slot, that is, the resonance cavity is formed by the slot and the cover plate as an example for explanation. On this basis, regardless of whether the outer surface of the cover plate (the surface of the cover plate facing away from the slot) is flush with the docking surface 204, that is, it can include the situation that the outer surface of the cover plate is flush with, recessed in, or protruding from the docking surface 204, when the cover plate is covered in the notch of the slot, it can be regarded as a part of the docking surface 204. On this basis, in the present embodiment, the design of the guide hole being provided on the cover plate can actually be understood as an extension or deformation of the basic concept that the guide hole is provided on the docking surface 204 of the exhaust bearing seat 200, and does not contradict the relevant description that the guide hole is provided on the docking surface 204.

[0105] In other embodiments, the two resonance cavities may also be formed in different ways. For example, one resonance cavity may be formed by a groove on the docking surface 204 and the cover body, and the other resonance cavity may be directly formed in the exhaust bearing seat 200 by other methods such as integral molding (casting), which are not limited to the present embodiment.

[0106] In other embodiments, even if the cover plate and the slot are used to form a resonance cavity, the guide hole may not be provided on the cover body, but may be provided at other positions of the docking surface 204. Moreover, the extension path of the guide hole in the exhaust bearing seat 200 or the cover body is not limited to a straight line, but may also be a curve or a broken line. In addition, for two resonance cavities, the opening positions or extension forms of the two guide holes connected to each other may not be completely the same. For example, one guide hole is provided on the cover body, and the other guide hole is not provided on the other cover body but is provided at other positions of the docking surface 204, which is not limited to the present embodiment.

[0107] like Figure 3 and Figure 4 As shown, in this embodiment, for at least one of the two resonant cavities, the shape of the orthographic projection of the resonant cavity on the docking surface 204 can preferably be a curved band, and the orthographic projection of the resonant cavity in the shape of a curved band can preferably bend along an arc path.

[0108] Preferably, if Figure 4 As shown, based on the design that the shape of the orthographic projection of the resonance cavity on the docking surface 204 is a strip-shaped design curved along an arc path, in this embodiment, for at least one of the two resonance cavities, the center point of the corresponding circle of the arc path where the orthographic projection of the resonance cavity is located coincides with the axial center of the rotor positioning hole corresponding to the resonance cavity.

[0109] Preferably, if Figure 4 As shown, based on the design that the shape of the orthographic projection of the resonance cavity on the docking surface 204 is a band-shaped design curved along a circular path, in this embodiment, for at least one of the two resonance cavities, the radian of the circular path where the orthographic projection of the resonance cavity on the docking surface 204 is located can preferably be less than or equal to π.

[0110] Preferably, if Figure 4 As shown, based on the design that the shape of the orthographic projection of the resonant cavity on the butt joint surface 204 is a strip-shaped design that is bent along an arc path, in this embodiment, the two resonant cavities can preferably both adopt the above-mentioned strip-shaped design that is bent along an arc path. On this basis, the orthographic projections of the two resonant cavities are arranged relative to each other with the arc openings of their respective arc paths.

[0111] like Figure 3 and Figure 4As shown, since the present embodiment is based on the twin-screw compressor as an example, with reference to the structural characteristics of the twin-screw compressor, the outer diameter of the male rotor and the female rotor is usually larger than the outer diameter of the female rotor due to the different rotor tooth structures. Accordingly, the aperture of the first positioning hole 201 (used to penetrate and position the male rotor) on the exhaust bearing seat 200 is larger than the aperture of the second positioning hole 202 (used to penetrate and position the female rotor). In other embodiments, when the exhaust bearing seat 200 proposed in the present disclosure is applicable to twin-screw compressors with other rotor structures, the aperture relationship between the two rotor positioning holes can also be flexibly adjusted according to the specific structure of the two rotors, and is not limited to the present embodiment.

[0112] Preferably, if Figure 4 As shown, based on the design that the aperture of the first positioning hole 201 is larger than the aperture of the second positioning hole 202, in this embodiment, the volume of the first cavity corresponding to the first positioning hole 201 can be preferably larger than the volume of the second cavity corresponding to the second positioning hole 202. Specifically, in this embodiment, the area of ​​the first cavity (which can also be understood as the size of the orthographic projection of the first cavity on the docking surface 204) can be preferably larger than the area of ​​the second cavity (which can also be understood as the size of the orthographic projection of the second cavity on the docking surface 204). Accordingly, when the depths of the first cavity and the second cavity are approximately the same, the volume of the first cavity is larger than the volume of the second cavity. In other embodiments, when the shapes of the first cavity and the second cavity are similar, and the area of ​​the first cavity is larger than the area of ​​the second cavity, the depth of the first cavity can also be less than or equal to the depth of the second cavity. Alternatively, the area of ​​the first cavity can be less than or equal to the area of ​​the second cavity, but by designing the depth of the first cavity to be greater than the depth of the second cavity, the design that the volume of the first cavity is greater than the volume of the second cavity can also be achieved. Alternatively, the shape of the first cavity is not limited to being the same as or similar to the shape of the second cavity. In this case, the area or depth of the first cavity and the area or depth of the second cavity can be designed with other relationships, thereby achieving the design purpose of making the volume of the first cavity larger than the volume of the second cavity, which is not limited to this embodiment.

[0113] Furthermore, if Figure 4 As shown, based on the fact that the shapes of the orthographic projections of the two resonant cavities on the docking surface 204 are both in the form of a band that curves along a circular path, in this embodiment, the corresponding circular radius of the circular path where the orthographic projection of the first cavity is located can preferably be greater than the corresponding circular radius of the circular path where the orthographic projection of the second cavity is located.

[0114] Furthermore, if Figure 4As shown, based on the fact that the shapes of the orthographic projections of the two resonant cavities on the docking surface 204 are both in the form of a strip curved along a circular arc path, in this embodiment, the strip width of the orthographic projection of the first cavity can preferably be greater than the strip width of the orthographic projection of the second cavity.

[0115] Furthermore, if Figure 4 As shown, based on the fact that the shapes of the orthographic projections of the two resonant cavities on the butt joint surface 204 are both in the form of a band curved along an arc path, in this embodiment, the radian of the arc path where the orthographic projection of the first cavity is located can be preferably greater than or equal to the radian of the arc path where the orthographic projection of the second cavity is located. For example, the radians of the arc paths where the orthographic projections of the first cavity and the second cavity are located can both be approximately π.

[0116] Preferably, in this embodiment, a sealing structure may be preferably provided between the cover plate and the slot of the slot. The sealing structure may be a sealing gasket, a sealing ring, etc. The material of the sealing structure may be a material with waterproof, moisture-proof, corrosion-resistant and other properties. Through the above design, the sealing structure can optimize the sealing effect between the slot and the cover plate, and further enhance the resonance effect of the resonance cavity. In other embodiments, when the processing precision of the cover plate and the slot is high, the sealing structure may not be provided, and is not limited to this embodiment.

[0117] In other embodiments, Figure 5 As shown, at least one of the two resonant cavities may also adopt a design of multiple sub-resonant cavities. Specifically, for a resonant cavity that adopts a design of multiple sub-resonant cavities, the multiple sub-resonant cavities it contains are arranged at intervals and located on the same side of the rotor positioning hole corresponding to the resonant cavity, and the docking surface 204 is respectively provided with multiple sub-flow guide holes corresponding to the multiple sub-resonant cavities of the resonant cavity, and the multiple sub-flow guide holes respectively connect the multiple sub-resonant cavities with the inner cavity of the compressor. Among them, Figure 5 The structure shown shows a design in which one resonant cavity includes two sub-resonant cavities and the other resonant cavity is a single structure, and Figure 5 Specifically shown are the second cover plate 222 and two first sub-cover plates 212' on the second resonant cavity or the first sub-resonant cavity. In other embodiments, the first resonant cavity and the second resonant cavity corresponding to the first positioning hole 201 and the second positioning hole 202, respectively, may both adopt a design of multiple sub-resonant cavities, or either of them may adopt a design of multiple sub-resonant cavities, and when both resonant cavities adopt a design of multiple sub-resonant cavities, the number of sub-resonant cavities included in the two may be the same or different.

[0118] It should be noted that the exhaust bearing seats shown in the drawings and described in this specification are only a few examples of the many types of exhaust bearing seats that can employ the principles of the present disclosure. It should be clearly understood that the principles of the present disclosure are in no way limited to any details of the exhaust bearing seats shown in the drawings or described in this specification or any components of the exhaust bearing seats.

[0119] In summary, the perforated plate type airflow pulsation attenuation device proposed in the present disclosure is arranged in the exhaust passage of the compressor and includes a tube body. A first perforated plate, a partition plate, and a second perforated plate are arranged in axial order and at intervals in the tube cavity of the tube body to divide the tube cavity into a first cavity, two resonance cavities, and a second cavity arranged in order, the first perforated plate is provided with a first guide hole, the second perforated plate is provided with a second guide hole, and the tube body is provided with a first through hole connected to the first cavity and a second through hole connected to the second cavity. Through the above design, when the compressor is running, the perforated plate type airflow pulsation attenuation device can utilize the gas in the exhaust passage to enter the two resonance cavities to generate Helmholtz resonance respectively, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself.

[0120] Furthermore, the exhaust bearing seat proposed in the present invention has two independent resonance cavities formed inside, and the two resonance cavities are respectively located on the relatively outer sides of the two rotor positioning holes. Two guide holes are formed on the docking surface of the exhaust bearing seat facing the compressor body, and the two guide holes respectively connect the two resonance cavities with the inner cavity of the compressor. Through the above design, when the compressor is running, the exhaust bearing seat can utilize the gas in the inner cavity to enter the two resonance cavities to generate Helmholtz resonance respectively, so as to respectively attenuate the airflow pulsation of the two rotors of the compressor. Compared with the existing scheme, since the exhaust bearing seat proposed in the present invention is arranged at the rotor end of the compressor, it has a better attenuation effect on the airflow pulsation. In addition, the exhaust bearing seat does not require additional structures.

[0121] Based on the above description, when the compressor proposed in the present invention includes the perforated plate type airflow pulsation attenuation device proposed in the present invention, when the compressor is running, the perforated plate type airflow pulsation attenuation device can utilize the gas in the exhaust channel to enter the two resonance cavities to generate Helmholtz resonance respectively, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be utilized to offset the airflow pulsation generated by the compressor itself.

[0122] Furthermore, when the compressor proposed in the present disclosure includes both the exhaust bearing seat and the perforated plate type airflow pulsation attenuation device proposed in the present disclosure, in addition to the above-mentioned effects provided by the perforated plate type airflow pulsation attenuation device, when the compressor is running, the exhaust bearing seat can utilize the gas in the inner cavity to enter the two resonance cavities to generate Helmholtz resonance respectively, so as to respectively attenuate the airflow pulsation of the two rotors of the compressor. Compared with the existing solutions, since the exhaust bearing seat proposed in the present disclosure is arranged at the rotor end of the compressor, it has a better attenuation effect on the airflow pulsation. Moreover, the exhaust bearing seat does not need to add other additional structures.

[0123] The above describes and / or illustrates in detail the exemplary embodiments of the perforated plate type airflow pulsation attenuation device and the compressor proposed by the present disclosure. However, the embodiments of the present disclosure are not limited to the specific embodiments described herein. On the contrary, the components and / or steps of each embodiment can be used independently and separately from other components and / or steps described herein. Each component and / or each step of an embodiment can also be used in combination with other components and / or steps of other embodiments. When introducing the elements / components / etc. described and / or illustrated herein, the terms "one", "one" and "above" are used to indicate the presence of one or more elements / components / etc. The terms "comprising", "including" and "having" are used to indicate the meaning of open inclusion and mean that in addition to the listed elements / components / etc., there may be other elements / components / etc. In addition, the terms "first" and "second" in the claims and the specification are used only as marks and are not numerical restrictions on their objects.

[0124] Although the perforated plate type air flow pulsation attenuation device and compressor proposed in the present disclosure have been described according to different specific embodiments, those skilled in the art will recognize that the implementation of the present disclosure can be modified within the spirit and scope of the claims.

Claims

1. A perforated plate type air flow pulsation attenuation device, arranged in the exhaust passage of a compressor; characterized in that: The perforated plate type air flow pulsation attenuation device comprises: A tube body, wherein a first perforated plate, a partition plate, and a second perforated plate are arranged in sequence and at intervals along the axial direction in the tube cavity, so as to divide the tube cavity into a first cavity, two resonance cavities, and a second cavity arranged in sequence, the first perforated plate is provided with a first guide hole, the second perforated plate is provided with a second guide hole, the tube body is provided with a first through hole connected to the first cavity and a second through hole connected to the second cavity, and the outer diameter of the tube body is smaller than the inner diameter of the exhaust passage; Among them, the perforated plate type airflow pulsation attenuation device is configured to utilize the gas in the exhaust channel to enter the two resonance cavities to generate Helmholtz resonance respectively when the compressor is running, thereby generating an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation can be used to offset the airflow pulsation generated by the compressor itself.

2. The perforated plate type air flow pulsation attenuation device according to claim 1, characterized in that: The radial cross section of the tube body is circular.

3. The perforated plate type air flow pulsation attenuation device according to claim 2, characterized in that: The radial cross section of the exhaust passage is circular; wherein the center of a circle corresponding to the radial cross section of the tube body coincides with the center of a circle corresponding to the radial cross section of the exhaust passage, and an annular gap is formed between the tube body and the exhaust passage.

4. The perforated plate type air flow pulsation attenuation device according to claim 3, characterized in that: The width of the gap is 0.5 mm to 1.5 mm.

5. The perforated plate type air flow pulsation attenuation device according to claim 1, characterized in that: The plane where the first perforated plate is located is perpendicular to the axial direction of the tube body; and / or, the plane where the second perforated plate is located is perpendicular to the axial direction of the tube body; and / or, the plane where the partition is located is perpendicular to the axial direction of the tube body.

6. The perforated plate type air flow pulsation attenuation device according to claim 1, characterized in that: The first cavity is closer to the exhaust port of the exhaust channel than the second cavity, and the distance between the first perforated plate and the corresponding tube port of the tube body is greater than the distance between the second perforated plate and the corresponding tube port of the tube body, so that the volume of the first cavity is greater than the volume of the second cavity.

7. The perforated plate type air flow pulsation attenuation device according to claim 6, characterized in that: The number of the first through holes is greater than the number of the second through holes.

8. The perforated plate type air flow pulsation attenuation device according to claim 7, characterized in that: The first through holes include a plurality of groups distributed along the axial direction of the tube body, each group includes a plurality of first through holes, and the plurality of first through holes in the same group are distributed around the circumference of the tube body; the second through holes include a plurality of groups distributed along the axial direction of the tube body, each group includes a plurality of second through holes, and the plurality of second through holes in the same group are distributed around the circumference of the tube body.

9. The perforated plate type air flow pulsation attenuation device according to claim 8, characterized in that: The number of openings in each group of the first through holes and the number of openings in each group of the second through holes are equal, and the number of groups of the first through holes is greater than the number of groups of the second through holes.

10. The perforated plate type air flow pulsation attenuation device according to claim 8, characterized in that: Multiple groups of the first through holes are evenly spaced along the axial direction of the tube body, and multiple groups of the second through holes are evenly spaced along the axial direction of the tube body; wherein the spacing between two adjacent groups of the first through holes in the axial direction of the tube body is equal to the spacing between two adjacent groups of the second through holes in the axial direction of the tube body.

11. The perforated plate type air flow pulsation attenuation device according to claim 1, characterized in that: The distance between the first perforated plate and the partition is equal to the distance between the second perforated plate and the partition, so that the volumes of the two resonance cavities are equal.

12. The perforated plate type air flow pulsation attenuation device according to claim 11, characterized in that: The first perforated plate is provided with a plurality of the first flow guide holes, and the second perforated plate is provided with a plurality of the second flow guide holes, and the number of the first flow guide holes is equal to the number of the second flow guide holes.

13. The perforated plate type air flow pulsation attenuation device according to claim 12, characterized in that: The plurality of first flow guide holes are evenly distributed, and the plurality of second flow guide holes are evenly distributed.

14. The perforated plate type air flow pulsation attenuation device according to claim 1, characterized in that: The perforated plate type air flow pulsation attenuation device also includes: A connecting plate is arranged at one end of the tube body, the end of the tube body opens to the connecting plate, and the connecting plate is configured to detachably fix the tube body at the exhaust port of the exhaust passage.

15. The perforated plate type air flow pulsation attenuation device according to claim 14, characterized in that: An exhaust flange is provided at the exhaust port of the exhaust channel; wherein the connecting plate is a flange structure, and the connecting plate is detachably connected to the exhaust flange.

16. A compressor comprising an exhaust passage; characterized in that: The compressor also includes: The perforated plate type airflow pulsation attenuation device according to any one of claims 1 to 15, arranged in the exhaust passage; Among them, the perforated plate type airflow pulsation attenuation device is configured to utilize the gas in the exhaust channel to enter the two resonance cavities to generate Helmholtz resonance respectively when the compressor is running, thereby generating airflow pulsation opposite to the airflow pulsation generated by the compressor itself so that the two cancel each other out.

17. The compressor according to claim 16, characterized in that The compressor is a twin-screw compressor, and the compressor further comprises: An exhaust bearing seat is connected to the exhaust port of the compressor body, and the exhaust bearing seat is provided with two rotor positioning holes; two independent resonance cavities are provided in the exhaust bearing seat, and the two resonance cavities are respectively located on the opposite outer sides of the two rotor positioning holes; two guide holes are provided on the docking surface of the exhaust bearing seat facing the exhaust port, and the two guide holes respectively connect the two resonance cavities with the inner cavity of the compressor; Wherein, the exhaust bearing seat is configured to utilize the gas in the inner cavity to enter the two resonance cavities to generate Helmholtz resonance respectively when the compressor is running, so as to respectively attenuate the air flow pulsation of the two rotors of the compressor.

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