Perforated tube silencer and fluid machinery for gaseous media

Abstract

The present disclosure relates to a perforated tube silencer and a fluid machinery for gaseous media. The perforated tube silencer is arranged in an exhaust-end bearing housing and / or an oil cylinder body of the fluid machinery which are located on an exhaust side and connected to each other. The perforated tube silencer comprises a plurality of silencing chambers and a silencing tube having a plurality of silencing hole sections. The silencing tube passes through the plurality of silencing chambers by insertion, such that the plurality of silencing hole sections correspond to the plurality of silencing chambers, and a plurality of silencing holes of each silencing hole section are in communication with the corresponding silencing chamber. By means of multiple combinations of chamber volumes and the silencing hole sections, the perforated tube silencer in the present disclosure provides multiple noise reduction frequency bands, thus better solving the problem of significant noise generated by the fluid machinery due to air flow pulsation at the exhaust side. In addition, a further increase in the size of the fluid machinery is avoided, and the structure can also be simplified.

Description

Multi-hole pipe silencer and fluid machinery equipment for gaseous media

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This disclosure claims the basis of the Chinese application with application number 202311571627.8 and filing date of November 23, 2023, and claims the priority thereof. The entire disclosure of the Chinese application is hereby incorporated by reference into this document. Technical Field

[0003] The present disclosure relates to the field of fluid mechanical equipment, and in particular to a porous tube silencer and a fluid mechanical equipment for gaseous medium. The fluid mechanical equipment for gaseous medium is provided with the porous tube silencer. Background Art

[0004] As the design and manufacturing level of fluid mechanical equipment for gaseous media (hereinafter referred to as fluid mechanical equipment) continues to improve, the market demand for fluid mechanical equipment is also gradually increasing, and the noise level of fluid mechanical equipment has become one of the important factors considered by customers. The noise of fluid mechanical equipment such as compressors mainly includes the noise generated by mechanical operation and the noise generated by the airflow pulsation of the fluid mechanical equipment. With the improvement of machining and assembly levels, mechanical noise has been greatly improved. Airflow noise is generally reduced by adding mufflers, designing exhaust buffer chambers, etc.

[0005] Currently, most fluid machinery equipment on the market uses welded external silencers to reduce airflow noise. External silencers generally consist of a large seamless steel pipe as the shell, with multiple silencer cavities formed internally by welding and expanding hot-rolled steel plates and porous tubes. The external silencer molding process is complex, welding deformation makes it difficult to control the accuracy, and the internal silencer cavity gap cannot be guaranteed. The external silencer has a large volume, and once the silencer is welded, it can only reduce noise at a specific frequency, making it inconvenient to adjust the noise reduction of multi-frequency noise. At the same time, the external silencer itself is large in size, and welding also requires the connection of some pipelines, which takes up a lot of space in the unit. In addition, the porous tube of the external silencer cannot be replaced.

[0006] Summary of the Invention

[0007] The present disclosure aims to solve at least the following technical problems:

[0008] 1. Solved the problem of high noise caused by airflow pulsation on the exhaust side of fluid machinery equipment;

[0009] 2. According to the different operating conditions of fluid machinery equipment, mufflers of different structures can be replaced to adjust the noise reduction; and

[0010] 3. The silencer is installed inside the fluid machinery equipment without increasing the volume of the compressor, which can simplify the volume and structure of the unit.

[0011] In order to solve the above technical problems, the present disclosure provides a porous tube silencer, which provides multiple noise reduction frequency bands through multiple combinations of the chamber volume of the silencer cavity and the silencer hole section of the silencer tube, thereby better solving the problem of high noise generated by the exhaust side airflow pulsation of the fluid mechanical equipment. It will not increase the volume of the fluid mechanical equipment and can also simplify the structure.

[0012] In one aspect, the present disclosure provides a porous tube muffler. The porous tube muffler is built into a connected exhaust end bearing seat and / or cylinder body located on the exhaust side of a fluid mechanical device for a gaseous medium. The porous tube muffler includes a plurality of muffler chambers and a muffler pipe having a plurality of muffler hole sections. The muffler pipe is inserted through the plurality of muffler chambers so that the plurality of muffler hole sections correspond to the plurality of muffler chambers, and the plurality of muffler holes in each muffler hole section communicate with the corresponding muffler chamber.

[0013] Thus, the built-in arrangement of the porous tube silencer does not increase the volume of the fluid machinery equipment and can also simplify the structure. Moreover, the combination of multiple silencer cavities and a silencer tube having multiple silencer hole sections helps to jointly determine the noise reduction frequency provided by the porous tube silencer.

[0014] In one or more embodiments, the plurality of muffler holes of the plurality of muffler hole segments are arranged with different hole spacings and / or different hole numbers and / or different hole diameters along the circumferential direction and the longitudinal direction of the muffler pipe. This facilitates providing muffler hole segments with a wider variety of hole layouts, allowing a wider variety of muffler hole segments to be used in combination with multiple muffler cavities to obtain a porous pipe muffler that can address noise in various frequency bands.

[0015] In one or more embodiments, the multiple muffler cavities have the same volume or different volumes. Thus, the combination of multiple muffler cavities with the same or different volumes and multiple muffler hole sections of the muffler pipe is conducive to providing multiple noise reduction frequencies.

[0016] In one or more embodiments, the different volumes of the muffler cavities are changed by changing the longitudinal dimension and / or radial dimension of each muffler cavity, which provides a possible implementation of muffler cavities with different volumes.

[0017] In one or more embodiments, the multiple muffler chambers of the porous tube muffler include a first group of muffler chambers built into the exhaust end bearing seat and / or a second group of muffler chambers built into the cylinder body. This can achieve the desired noise and vibration reduction effects on at least one of the exhaust end bearing seat and the cylinder body.

[0018] In one or more embodiments, the first group of muffler cavities includes a first sub-muffler cavity arranged parallel to the centerline of the fluid mechanical device, thereby achieving noise and vibration reduction of the fluid mechanical device at the exhaust end bearing seat without excessively increasing the complexity of the exhaust end bearing seat.

[0019] In one or more embodiments, the second group of muffler cavities includes a plurality of second sub-muffler cavities arranged parallel to the center line of the fluid mechanical equipment, thereby achieving better noise reduction and vibration reduction of the fluid mechanical equipment at the cylinder body.

[0020] In one or more embodiments, the plurality of second sub-muffler chambers are separated by blocking steps, and the plurality of second sub-muffler chambers have the same volume or different volumes. Thus, the provision of the blocking steps prevents axial sound propagation of the gas, thereby improving the muffler performance.

[0021] In one or more embodiments, the muffler hole section of the muffler pipe is configured such that no muffler hole exists at the blocking step after the muffler pipe is assembled into the muffler cavity. This prevents completely obstructed muffler holes from becoming ineffective, and prevents partial obstruction of the muffler holes from affecting actual calculations and causing deviations from the actual optimal frequency band.

[0022] In one or more embodiments, a pair of multi-hole pipe mufflers are arranged on either side of the centerline of the fluid machinery, within the exhaust end bearing housing and the cylinder body. This arrangement increases the length of the muffler pipe without increasing the volume of the fluid machinery, meeting the need for a greater number of holes, thereby providing a wider range of noise reduction frequency bands for the fluid machinery.

[0023] In one or more embodiments, the exhaust end bearing seat and the oil cylinder body are detachably connected together to hold the muffler pipe in a clamping manner. Thus, the exhaust end bearing seat and the oil cylinder body hold the porous pipe muffler in a clamping manner without the need for additional upstream and downstream connectors.

[0024] In one or more embodiments, the second connection end of the exhaust end bearing seat has a recessed portion, and the first connection end of the oil cylinder body has a protruding portion that cooperates with the recessed portion. Thus, the cooperation between the recessed portion and the protruding portion facilitates accurate positioning of the connection.

[0025] In one or more embodiments, the porous tube muffler can be selectively replaced with different muffler tubes according to the operating conditions of the fluid machinery equipment, thereby facilitating a simple and convenient provision of a porous tube muffler that is more suitable for specific operating conditions for the fluid machinery equipment.

[0026] In one or more embodiments, the exhaust end bearing seat and the muffler cavity in the oil cylinder body are formed by casting, thereby making the muffler cavity simple and easy to manufacture.

[0027] In one or more embodiments, the porous tube muffler further includes a positioning sleeve, which is arranged at a first end of the muffler tube abutting against the second connection end of the exhaust end bearing seat and / or at a second end of the muffler tube abutting against the second connection end of the cylinder body, thereby providing better sealing and vibration reduction effects.

[0028] In one or more embodiments, the fluid mechanical device further comprises an exhaust pipe, which is detachably connected to the second end of the muffler pipe, thereby facilitating connection of the exhaust pipe with the porous pipe muffler to guide gas out of the fluid mechanical device.

[0029] In one or more embodiments, the fluid mechanical equipment further comprises an oil separation device, and the porous tube muffler is arranged below the oil separation device. Thus, the oil-gas separation device and the porous tube muffler of the fluid mechanical equipment can be integrated.

[0030] In one or more embodiments, the fluid mechanical device is a compressor, thereby better solving the problem of high noise generated by exhaust-side airflow pulsation in the compressor.

[0031] In a second aspect, the present disclosure provides a fluid mechanical device for a gaseous medium, equipped with a porous tube muffler according to the present disclosure. This effectively addresses the issue of high noise levels caused by pulsating airflow on the exhaust side of the fluid mechanical device. Furthermore, this solution does not increase the volume of the fluid mechanical device and simplifies its structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] The present disclosure will be more easily understood by the following detailed description in conjunction with the accompanying drawings, in which like reference numerals represent like elements. The drawings are illustrative and non-limiting. The elements in the drawings are not necessarily drawn to scale. For example, elements may be enlarged for illustrative purposes or may be reduced in scale to keep the drawings clear and easy to understand. In the drawings:

[0033] FIG1 shows an internal structure diagram of a gaseous medium fluid mechanical device in the prior art;

[0034] FIG2A schematically shows a front view of an external muffler of the prior art;

[0035] FIG2B schematically shows a cross-sectional view taken along line AA in FIG2A ;

[0036] FIG3 shows a schematic diagram of a Helmholtz resonator;

[0037] 4A schematically shows a cross-sectional view of a fluid mechanical device for a gaseous medium provided with a porous tube silencer according to the present disclosure, taken along a horizontal plane passing through the center line of the porous tube silencer, to illustrate the layout of the porous tube silencer within the fluid mechanical device;

[0038] 4B schematically shows a cross-sectional view of the gaseous medium fluid mechanical device of FIG. 4A , taken along a vertical plane passing through the center line of the porous tube silencer, to illustrate the layout of the porous tube silencer within the fluid mechanical device;

[0039] FIG4C shows an enlarged view of the circled portion in FIG4B ;

[0040] 5A to 5C respectively show a perspective view, a front view, and a cross-sectional view taken along line AA in FIG. 5B of the cylinder body of the gaseous medium fluid mechanical device of FIG. 4A . DETAILED DESCRIPTION

[0041] The present disclosure will be described below with reference to the accompanying drawings, which illustrate several embodiments of the present disclosure. However, it should be understood that the present disclosure can be presented in many different ways and is not limited to the embodiments described below. The embodiments described below are intended to make the disclosure of the present disclosure more complete and to fully illustrate the scope of protection of the present disclosure to those skilled in the art. It should be understood that the same reference numerals represent the same elements throughout the drawings.

[0042] Unless otherwise defined, all technical and scientific terms used herein have the same meanings as those commonly understood by those skilled in the art. For the sake of brevity and / or clarity, well-known functions or structures may not be described in detail. The terms used herein are for the purpose of describing specific embodiments only and are not intended to limit the present disclosure. The terms "including" and "having" and any derivatives thereof in the specification and claims of the present disclosure and the above-mentioned figure descriptions are intended to cover non-exclusive inclusions.

[0043] In the description of the embodiments of the present disclosure, the terms "first", "second", etc. are only used to distinguish different objects and should not be understood as indicating or implying relative importance or implicitly indicating the number, specific order or primary and secondary relationship of the indicated technical features.

[0044] References herein to "embodiments" mean that a particular feature, structure, or characteristic described in connection with the embodiments may be included in at least one embodiment of the present disclosure. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor does it constitute an independent or alternative embodiment that is mutually exclusive of other embodiments. It is understood, both explicitly and implicitly, by those skilled in the art that the embodiments described herein may be combined with other embodiments.

[0045] In the description of the embodiments of the present disclosure, the term "and / or" is merely a description of the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B can represent three situations: A exists alone, A and B exist at the same time, and B exists alone.

[0046] In the description of the embodiments of the present disclosure, the terms "inside", "outside", "lateral", "horizontal", "vertical", "parallel" and "perpendicular" indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present disclosure and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operate in a specific orientation. Therefore, they cannot be understood as limiting the embodiments of the present disclosure.

[0047] In the description of the embodiments of the present disclosure, unless otherwise expressly specified or limited, the terms "installation," "assembly," and "connection" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integration; they may refer to direct connections or indirect connections through an intermediate medium; they may refer to internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the embodiments of the present disclosure based on specific circumstances.

[0048] In the description of the embodiments of the present disclosure, the fluid mechanical equipment for the gaseous medium may be a compressor, and the following description will be made using the compressor as an example.

[0049] Figure 1 shows the internal structure of a conventional fluid machinery device for gaseous media. The fluid machinery device includes a male rotor 12 and a female rotor 14 housed within a housing 10. The first connection end of an exhaust-end bearing seat 20 is located proximately to the exhaust side of the fluid machinery device, and an exhaust pipe 30 is connected to the second connection end of the exhaust-end bearing seat 20. Gas exhausted from the housing 10 enters the exhaust-end bearing seat 20 through the exhaust port and is then discharged through the exhaust pipe 30. Typically, such fluid machinery devices utilize welded external mufflers to reduce airflow noise.

[0050] Figures 2A and 2B schematically illustrate a front view and a cross-sectional view taken along line AA in Figure 2A, respectively, of a conventional external muffler. The external muffler 50 includes a housing 51, typically formed from a single seamless steel pipe. The interior of the housing is formed by welding and expansion of hot-rolled steel plates and a muffler porous tube 52 to form multiple muffler chambers 53. In other words, a partition 54 formed from hot-rolled steel plates divides the housing 51 into multiple muffler chambers 53. The multiple porous sections of the muffler tube 52 correspond to the multiple muffler chambers 53, thereby reducing noise of different frequencies. This type of external muffler is relatively large and externally mounted, increasing the overall volume of the fluid machinery. Furthermore, once welded, it only reduces noise of a predetermined frequency, making it difficult to adjust noise reduction for multiple frequencies by replacing different muffler tubes 52 as needed. The production and processing of this external muffler is complex, and its precision and efficiency are relatively low. At the same time, the external silencer itself is large in size, and welding also requires connecting some pipes, which takes up a lot of space in the unit.

[0051] In view of the problems existing in the prior art, the present disclosure proposes a built-in porous tube silencer based on the Helmholtz resonator silencer principle, which can reduce noise of various frequencies.

[0052] Figure 3 shows a schematic diagram of a Helmholtz resonator. The Helmholtz resonator may include a cavity 1 and an orifice 2. The orifice 2 may include one or more holes. The air at orifice 2 can be considered an air mass, while the air within cavity 1 acts as a spring. Thus, when driven by an external force, the mass connected to the spring will move up and down according to its natural frequency (ignoring air resistance and friction) due to the spring force and its own weight. This natural frequency can be calculated using the following formula:

[0053] Where f0 is the resonant frequency of the Helmholtz resonator, с is the speed of sound, S is the total cross-sectional area of ​​the orifice, d is the diameter of the orifice, L is the length of the orifice, and V is the volume of the cavity.

[0054] When the sound wave frequency matches the natural frequency of the Helmholtz resonator, a resonance phenomenon occurs, causing the sound wave to be absorbed. Specifically, when a sound wave enters the Helmholtz resonator, it is reflected and refracted multiple times within the cavity, causing interference of the sound waves and dissipation of the sound wave energy. Secondly, the shape of the cavity of the Helmholtz resonator and the cross-sectional area of ​​the orifice affect the propagation path and speed of the sound wave, thereby changing the phase and amplitude of the sound wave. When the sound wave frequency matches the natural frequency of the Helmholtz resonator, a resonance effect is stimulated, and the energy of the sound wave is absorbed and dissipated, thereby achieving a sound elimination effect.

[0055] According to the above formula, the natural frequency of the Helmholtz resonator can be changed by adjusting the cavity volume (V), the length of the orifice (L), and the diameter (d) or cross-sectional area (S) of the orifice.

[0056] Based on the sound-absorbing principle of the Helmholtz resonator, the porous tube silencer proposed in the present disclosure can include multiple silencer cavities and a silencer tube with multiple silencer hole segments that can be removably inserted into the silencer cavities. The chamber defined by the silencer cavity and the outer surface of the silencer tube can be considered the cavity 1 of the Helmholtz resonator, and the combination of the multiple holes in each porous segment of the silencer tube can be considered the orifice 2 of the Helmholtz resonator. Since the wall thickness of the silencer tube is constant, the frequency of the porous tube silencer according to the present disclosure can be changed by changing the volume of the chamber and the total cross-sectional area of ​​the multiple holes in the corresponding porous segment of the silencer tube.

[0057] In other words, based on the muffler principle of a Helmholtz resonator, various combinations of chamber volumes and hole numbers in a porous tube muffler jointly determine the noise reduction and attenuation frequency band of the muffler chamber. Typically, the length of the muffler hole section corresponds to the length of the chamber, and the chamber volume is related to the chamber's longitudinal and / or radial dimensions. The specific values ​​for the chamber volume and the number of holes in the muffler hole section are difficult to quantify, as they are two variables typically determined through simulation or experimental analysis. In practice, varying both variables simultaneously can achieve the same effect. Specifically, the same chamber volume but different hole numbers will result in different noise reduction and attenuation frequency bands; different chamber volumes but the same number of holes will result in different noise reduction and attenuation frequency bands; and different chamber volumes and different hole numbers may result in the same noise reduction and attenuation frequency bands. In practice, various combinations of chamber volume and hole number in porous tube mufflers are designed based on available space and process availability to achieve noise reduction across multiple frequency bands.

[0058] Figures 4A and 4B show cross-sectional views of a fluid machinery device equipped with a porous tube muffler according to the present disclosure, taken along a horizontal plane and a vertical plane respectively passing through the centerline of the porous tube muffler, to illustrate the layout of the porous tube muffler within the fluid machinery device. Figure 4C shows an enlarged view of the circled portion in Figure 4B.

[0059] 4A , the fluid mechanical equipment 100 includes an exhaust end bearing seat 120 and a cylinder body 140 connected to each other on the exhaust side. Specifically, the exhaust end bearing seat 120 and the cylinder body 140 are detachably connected together. The porous tube silencer 200 is built into the fluid mechanical equipment 100. In the examples shown in FIG4A and FIG4B , the porous tube silencer 200 can be built into the exhaust end bearing seat 120 and the cylinder body 140. In an example not shown, according to actual needs, the porous tube silencer 200 can be built into either the exhaust end bearing seat 120 or the cylinder body 140. Since the porous tube silencer 200 is built into the fluid mechanical equipment, the problem of the fluid mechanical equipment generating high noise due to the pulsation of the airflow on the exhaust side is solved without increasing the volume of the fluid mechanical equipment and simplifying the structure.

[0060] In the example shown in Figure 4A , a pair of porous tube silencers 200 are arranged on either side of the centerline C1 of the fluid machinery. This arrangement of the porous tube silencers 200 increases the length of the silencer pipe without increasing the volume of the fluid machinery, thus meeting the space requirements for a greater variety of hole numbers. This makes it possible to provide the fluid machinery with porous tube silencers 200 with a wider range of noise reduction frequency bands.

[0061] In the example shown in FIG4A , each porous tube muffler 200 includes multiple muffler chambers 210 and a muffler pipe 220 having multiple muffler hole sections 222A, 222B, 222C, and 222D. The combination of multiple muffler chambers and a muffler pipe having multiple muffler hole sections helps to jointly determine the noise reduction frequency that the porous tube muffler can provide. Specifically, the multiple muffler chambers 210 may include a first group of muffler chambers built into the exhaust end bearing seat 120 and / or a second group of muffler chambers built into the cylinder body 140. In the example shown in FIG4A , the multiple muffler chambers 210 may be provided in both the exhaust end bearing seat 120 and the cylinder body 140, thereby achieving the desired noise reduction and vibration reduction effects on both.

[0062] In the example shown in FIG4A , the first group of muffler cavities includes a single first sub-muffler cavity 210A to avoid increasing the length and structural complexity of the exhaust-end bearing housing 120. Alternatively, in an example not shown, the first group of muffler cavities may include multiple first sub-muffler cavities to provide a wider range of noise reduction frequency bands and achieve better noise and vibration reduction. The first sub-muffler cavity 210A may be arranged parallel to the centerline C1 of the fluid mechanical device to achieve better noise and vibration reduction for the fluid mechanical device at the exhaust-end bearing housing 120.

[0063] In the example shown in FIG4A , the second group of silencer cavities includes three second sub-silencer cavities 210B, 210C, and 210D. The second group of silencer cavities may also include only one second sub-silencer cavity. Generally, since the structure of the cylinder body 140 is relatively simple, multiple second sub-silencer cavities are provided in the cylinder body 140 to provide a wider range of noise reduction frequency bands without increasing the complexity of the structure too much, thereby better reducing noise and vibration of the fluid mechanical equipment. In other words, the second group of silencer cavities may include at least one second sub-silencer cavity. The second sub-silencer cavity may be arranged parallel to the centerline C1 of the fluid mechanical equipment to achieve better noise reduction and vibration reduction of the fluid mechanical equipment at the cylinder body 140.

[0064] In the example shown in FIG4A , the silencer tube 220 is inserted through the plurality of silencer cavities 210 so that the plurality of silencer hole segments 222A, 222B, 222C, and 222D correspond to the plurality of silencer sub-cavities 210A, 210B, 210C, and 210D, and the plurality of silencer holes of each silencer hole segment are connected to the corresponding silencer cavities, so as to provide a plurality of noise reduction frequency bands accordingly to reduce noise and vibration of the fluid machinery equipment.

[0065] The multiple muffler chambers 210 may have the same volume or different volumes. In the example shown in Figures 4A-4C, the three second sub-muffler chambers 210B, 210C, and 210D have the same volume, but are all different from the volume of the first sub-muffler chamber 210A. In an example not shown, at least two of the multiple second sub-muffler chambers may have different volumes to provide the possibility of forming a wider range of noise reduction frequencies together with the corresponding muffler hole segments. Alternatively, in an example not shown, the four sub-muffler chambers 210A, 210B, 210C, and 210D may all have the same volume, while different noise reduction frequencies are formed by muffler hole segments with different hole layouts. In addition, in an example not shown, the four sub-muffler chambers 210A, 210B, 210C, and 210D may have different volumes, and a variety of different noise reduction frequencies are formed by muffler hole segments with the same hole layout. In an example not shown, the four sub-muffler cavities 210A, 210B, 210C, and 210D can each have different volumes, creating a wider range of possible noise reduction frequencies through muffler hole segments with different hole layouts. In other words, a wider range of combinations of muffler hole segments with various hole layouts and muffler cavities with various volumes in the muffler tube can help provide a wider range of noise reduction frequencies.

[0066] The different volumes of the muffler chamber 210 can be changed by changing the longitudinal dimension and / or radial dimension of the sub-muffler chamber. This provides a possible implementation method for muffler chambers with different volumes. For example, the different volumes of the first sub-muffler chamber 210A and the second sub-muffler chambers 210B, 210C, and 210D can be different by changing the longitudinal dimension of the muffler chamber. Alternatively, in an example not shown, the different volumes of the two muffler chambers can be different by changing the radial dimension of the muffler chamber. In addition, in an example not shown, the different volumes of the two muffler chambers can be different by simultaneously changing the longitudinal dimension and radial dimension of the muffler chamber.

[0067] The exhaust end bearing seat 120 and the silencer chamber in the oil cylinder body 140 are formed by casting. Therefore, the manufacturing is simple and easy to implement. During casting, a blocking step 212 is set between adjacent silencer chambers (see Figure 4B). For example, the multiple second sub-silencer chambers 210B, 210C, and 210D in the oil cylinder body 140 are separated by the blocking step 212. The setting of the blocking step 212 prevents the axial sound propagation of the gas and improves the silencer performance of the silencer. In the example shown in Figures 4A-4C, the silencer chamber of the exhaust end bearing seat 120 includes only one first sub-silencer chamber 210A, so the blocking step is not set. In the case where the silencer chamber of the exhaust end bearing seat 120 includes multiple first sub-silencer chambers, it can be constructed similarly to the multiple silencer chambers in the oil cylinder body 140.

[0068] The silencer holes on the silencer tube 220 are arranged so that after the silencer tube 220 is inserted into the plurality of silencer cavities 210, there are no silencer holes at the blocking step 212. If the silencer holes were located at the blocking step, on the one hand, the completely blocked silencer holes would not function, and on the other hand, the partially blocked silencer holes would affect the actual calculation and cause the actual optimal frequency band to deviate.

[0069] The multiple muffler holes in each muffler hole segment can be arranged in various arrangements, for example, with different hole spacings, different numbers of holes, and / or different hole diameters along the circumferential and longitudinal directions of the muffler pipe 220. In the example shown in Figures 4A-4C, for example, muffler hole segments 222A and 222B have different lengths, but the holes have the same spacing and diameters in the circumferential and longitudinal directions, and the number of holes is different. Muffler hole segments 222A and 222C have different lengths, different spacing and diameters in the circumferential direction, and different numbers of holes. Muffler hole segments 222B and 222D have the same lengths, but different spacing and diameters in the circumferential and longitudinal directions, and different numbers of holes. Muffler hole segments 222B and 222C have different lengths, different spacing and diameters in the circumferential direction, and different numbers of holes. The muffler pipe 220 can have more muffler hole sections, and by analogy, can also have muffler hole sections with more different hole layouts. This facilitates the use of more muffler hole sections in combination with multiple muffler cavities to obtain a porous pipe muffler that can target noise in multiple frequency bands.

[0070] The exhaust end bearing seat 120 and the oil cylinder body 140 can be detachably connected together by a mechanical connection. Specifically, as shown in Figures 4B and 4C, the second connection end of the exhaust end bearing seat 120 is provided with a recessed portion 122, and the first connection end of the oil cylinder body 140 is provided with a protrusion 142 that cooperates with the recessed portion 122 to provide precise positioning of the connection. When assembling the exhaust end bearing seat 120 and the oil cylinder body 140 together, the muffler 220 can be first inserted into one of the exhaust end bearing seat 120 and the oil cylinder body 140, and then aligned with the other to plug in so that the recessed portion 122 and the protrusion 142 are plugged into place. Then, the screws 160 are passed through the mounting holes 141 (see Figure 5A) of the oil cylinder body 140 and the mounting holes of the exhaust end bearing seat 120 to fix them together. Preferably, since the muffler pipe 220 located in the oil cylinder body 140 is relatively long, the muffler pipe 220 can be inserted into the oil cylinder body 140 first, and then aligned with the exhaust end bearing seat 120 for insertion. In this way, the exhaust end bearing seat 120 and the oil cylinder body 140 hold the porous pipe muffler 200 in a clamping manner, without the need for additional upstream and downstream connectors.

[0071] Furthermore, the removable, clip-on assembly of the exhaust-end bearing housing 120 and the cylinder body 140 facilitates easy replacement of different muffler pipes based on the operating conditions of the fluid machinery, thereby conveniently providing a multi-hole pipe muffler more suited to the specific operating conditions of the fluid machinery. Different muffler pipes can have multiple muffler hole sections with different layouts, for example, with different hole spacings, different numbers of holes, and / or different hole diameters.

[0072] In order to provide better sealing and vibration reduction effects, a positioning sleeve 230 may be provided at the first end of the muffler pipe 220 abutting against the second connection end of the exhaust end bearing seat 120 and / or at the second end of the muffler pipe 220 abutting against the second connection end of the cylinder body 140. The positioning sleeve 230 may be made of a flexible material (e.g., rubber).

[0073] Referring to Figure 4B , the fluid machinery 100 further includes an exhaust pipe 130, which is detachably connected to the second end of the muffler 220 and is used to guide gases out of the fluid machinery. To prevent oil from being carried away by the gases during discharge, the exhaust pipe 130 extends through an oil-gas separation device. The oil-gas separation device also includes a main oil-gas separator 150 and a terminal separation filter 170. The exhaust pipe 130 first traverses the main oil-gas separator 150, then makes a 90-degree turn and extends to the vertically arranged cylindrical terminal separation filter 170 at its terminal end.

[0074] Referring to Figure 4B , the porous tube muffler 200 is positioned in the oil tank, below the oil separator. The exterior of the porous tube muffler is immersed in oil, providing excellent noise and vibration isolation. Furthermore, the muffler tube and chamber itself can be considered part of the oil-gas separation device. In other words, the oil-gas separation device and the porous tube muffler of the fluid machinery can be integrated.

[0075] 5A to 5C show a perspective view, a front view, and a cross-sectional view taken along line AA in FIG. 5B of a cylinder block of a fluid machinery device provided with a porous pipe muffler according to the present disclosure.

[0076] As shown in Figures 5A-5C, the cylinder body 140 includes a receiving hole 146 for accommodating components extending from the fluid mechanical equipment. The cylinder body 140 also includes a first receiving hole 142 and a second receiving hole 144 arranged on both sides of the receiving hole 146 for receiving the silencer pipe 220. The first receiving hole 142 and the second receiving hole 144 are also located on both sides relative to the center line C1 of the fluid mechanical equipment. Three second sub-silencer chambers 210B, 210C, and 210D are formed in the first receiving hole 142 and the second receiving hole 144. In an example not shown, the layout of the second sub-silencer chambers in the first receiving hole 142 and the second receiving hole 144 can be the same or different, and the number of second sub-silencer chambers can be at least one, preferably more than one. As a result, multiple silencer chambers of the same or different volumes are arranged in the cylinder body 140 with a relatively simple structure, which facilitates providing a variety of noise reduction frequencies for the fluid mechanical equipment.

[0077] The porous tube muffler disclosed herein can reduce the noise generated by the exhaust airflow during the operation of fluid machinery. Compared to external mufflers, it is easier to manufacture and does not increase the size of the fluid machinery. Furthermore, the muffler tube can be replaced to address different frequency bands, depending on the operating conditions of the fluid machinery. Furthermore, the muffler tube is simple to manufacture and assemble, and does not require welding to other components.

[0078] The gaseous medium fluid machinery equipment disclosed herein, by being equipped with the porous tube silencer disclosed herein, can better solve the problem of high noise generated by exhaust side airflow pulsation in the fluid machinery equipment. In addition, it does not increase the volume of the fluid machinery equipment and can also simplify the structure.

[0079] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the aforementioned embodiments, it should be understood by those skilled in the art that the technical solutions described in the aforementioned embodiments can still be modified, or some or all of the technical features therein can be replaced by equivalents; and these modifications or replacements do not deviate the essence of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present application, and they should all be included in the scope of the claims and description of the present application. In particular, as long as there is no structural conflict, the various technical features mentioned in the various embodiments can be combined in any way. The present application is not limited to the specific embodiments disclosed herein, but includes all technical solutions that fall within the scope of the claims.

Claims

1. A porous tube silencer, wherein the porous tube silencer is built into an exhaust end bearing seat and / or a cylinder body connected to each other on the exhaust side of a fluid mechanical equipment of a gaseous medium, wherein the porous tube silencer comprises a plurality of silencer chambers and a silencer pipe having a plurality of silencer hole sections, wherein the silencer pipe is inserted through the plurality of silencer chambers so that the plurality of silencer hole sections correspond to the plurality of silencer chambers, and the plurality of silencer holes of each of the silencer hole sections are connected to the corresponding silencer chambers.

2. The porous pipe silencer according to claim 1, wherein: The multiple silencer holes of the multiple silencer hole sections are respectively arranged with different hole spacings and / or different hole numbers and / or different hole diameters along the circumferential direction and the longitudinal direction of the silencer pipe.

3. The porous pipe silencer according to claim 1 or 2, wherein: The multiple silencing chambers have the same volume or different volumes.

4. The porous pipe silencer according to claim 3, wherein: The different volumes of the muffler chambers are varied by changing the longitudinal dimension and / or radial dimension of each muffler chamber.

5. The porous tube silencer according to any one of claims 1 to 4, wherein: The multiple silencer chambers of the porous tube silencer include a first group of silencer chambers built into the exhaust end bearing seat and / or a second group of silencer chambers built into the oil cylinder body.

6. The porous pipe silencer according to claim 5, wherein: The first group of muffler chambers includes a first sub-muffler chamber arranged parallel to the center line of the fluid mechanical equipment.

7. The porous pipe silencer according to claim 5, wherein: The second group of muffler chambers includes a plurality of second sub-muffler chambers arranged parallel to a center line of the fluid mechanical equipment.

8. The porous pipe silencer according to claim 7, wherein: The plurality of second sub-muffler chambers are separated by blocking steps, and the plurality of second sub-muffler chambers have the same volume or different volumes.

9. The porous pipe silencer according to claim 8, wherein: The muffler hole section of the muffler pipe is configured such that after the muffler pipe is assembled into the muffler cavity, no muffler hole exists at the blocking step.

10. The porous pipe silencer according to any one of claims 1 to 9, wherein: A pair of porous tube silencers are arranged on both sides of the center line of the fluid mechanical equipment in the exhaust end bearing seat and the cylinder body.

11. The porous pipe silencer according to any one of claims 1 to 10, wherein: The exhaust end bearing seat and the oil cylinder body are detachably connected together to hold the muffler pipe in a clamping manner.

12. The porous pipe silencer according to claim 11, wherein: The second connecting end of the exhaust end bearing seat has a recessed portion, and the first connecting end of the oil cylinder body has a protruding portion matched with the recessed portion.

13. The porous pipe silencer according to claim 11 or 12, wherein: The porous tube silencer can selectively replace different silencer tubes according to the operating conditions of the fluid mechanical equipment.

14. The porous pipe silencer according to any one of claims 1 to 13, wherein: The exhaust end bearing seat and the silencer chamber in the cylinder body are formed by casting.

15. The porous pipe silencer according to any one of claims 1 to 14, wherein: The porous tube silencer also includes a positioning sleeve, which is arranged at the first end of the silencer pipe abutting against the second connecting end of the exhaust end bearing seat and / or the second end of the silencer pipe abutting against the second connecting end of the cylinder body.

16. The perforated pipe silencer according to claim 15, wherein: The fluid mechanical equipment further includes an exhaust pipe detachably connected to the second end of the muffler pipe.

17. The porous pipe silencer according to any one of claims 1 to 16, wherein: The fluid mechanical equipment further comprises an oil separation device, and the porous tube silencer is arranged at a lower position of the oil separation device.

18. The porous pipe silencer according to any one of claims 1 to 17, wherein: The fluid mechanical equipment is a compressor.

19. A fluid mechanical device for a gaseous medium, wherein: The fluid mechanical equipment is provided with a porous tube silencer according to any one of claims 1-18.

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