Air compressor silencing device and air compressor

Abstract

An air compressor silencing and vibration reduction device and an air compressor. An inner sleeve (2) is mounted in an air compressor vent (1), a fixed end (2-1) at one end of the inner sleeve (2) being connected to the inner wall surface of the air compressor vent (1), and a suspension end (2-2) at the other end of the inner sleeve (2) being in a suspended state. A recess is provided in the air compressor vent (1), and the space between the recess and the inner sleeve (2) forms a silencing cavity (6), wherein a plurality of silencing areas distributed at intervals are provided in the silencing cavity (6), and each silencing area is filled with a magnetic fluid (4). The inner sleeve (2) is provided with a first-stage silencing structure (7). Radial oscillation is generated by means of the suspension end (2-2), such that the magnetic fluid (4) in the silencing areas generates tangential oscillation used for attenuating acoustic energy entering the silencing cavity (6). When sound in the air compressor vent enters the tail portion of the silencing cavity, radial oscillation will be generated at the suspension end of the inner sleeve, thereby attenuating acoustic energy.

Description

Air compressor silencer and air compressor Technical Field

[0001] The present invention relates to the field of air compressor noise reduction or air compressor silencing, and in particular to an air compressor silencing device and an air compressor. Background Art

[0002] The advantages of turbocharging include increased power output, lower fuel consumption and reduced pollutant emissions.Turbocharging of engines is no longer primarily considered from the perspective of high power performance, but is seen as a way to reduce fuel consumption and environmental pollution due to lower carbon dioxide (CO2) emissions.

[0003] Currently, the primary reason for turbocharging is to use exhaust gas energy to reduce fuel consumption and emissions. In a turbocharged engine, the combustion air is compressed before being fed into the engine. The engine draws the same volume of air-fuel mixture as a naturally aspirated engine, but due to the higher pressure and, therefore, higher density, a greater mass of air and fuel is delivered to the combustion chamber in a controlled manner. As a result, more fuel is burned, increasing the engine's power output relative to speed and displacement.

[0004] In recent years, superchargers have been used to improve the fuel efficiency of diesel engines and reduce nitrogen oxides (NO x ), requiring a high pressure ratio and high efficiency. This requires the supercharger to be driven at a high speed. However, while driving the supercharger at a high speed can achieve a high pressure ratio and high efficiency, it also leads to the adverse effect of increased noise levels.

[0005] The turbine's inlet and outlet are connected to a pipe that circulates exhaust gas. However, the turbine noise that penetrates through this pipe can be soundproofed by wrapping a soundproofing material around the outer surface of the pipe. This means that conventional soundproofing is not very effective at isolating the compressor outlet.

[0006] Summary of the Invention

[0007] In response to the shortcomings of the prior art, the present invention provides an air compressor silencer and an air compressor, wherein the inner wall surface of the air compressor vent is embedded in one end of an inner sleeve, while the other end of the inner sleeve is in a suspended state. When the sound in the air compressor vent enters the tail of the silencer cavity, radial oscillations will be generated at the suspended end of the inner sleeve, which can attenuate the sound energy.

[0008] The present invention achieves the above technical objectives through the following technical means.

[0009] An air compressor silencer and vibration reduction device comprises an inner sleeve installed in the air compressor vent, a fixed end at one end of the inner sleeve connected to the inner wall surface of the air compressor vent, and a suspended end at the other end of the inner sleeve in a suspended state; a groove is provided on the air compressor vent, and the space between the groove and the inner sleeve constitutes a silencer chamber, wherein the silencer chamber is provided with a plurality of spaced-apart silencer regions, each of which is filled with magnetic fluid, and a first-stage silencer structure is provided on the inner sleeve; radial oscillations are generated by the suspended end, causing the magnetic fluid in the silencer region to generate tangential oscillations, thereby attenuating the sound energy entering the silencer chamber. The radial oscillations generated by the suspended end cause fluctuations in the tail space of the silencer chamber, which causes fluctuations in the thickness of the magnetic fluid in the silencer chamber. Since magnetic fluid is incompressible, the fluctuations in the thickness of the magnetic fluid are converted into tangential oscillations, and the tangential oscillations of adjacent magnetic fluids attenuate the sound energy entering the cavity. That is to say, the sound energy of the sound entering the cavity of the present invention is accelerated to attenuate through tangential oscillation and radial oscillation, and the ability of attenuating sound energy in this way exceeds that of using only tangential oscillation or radial oscillation.

[0010] Furthermore, a magnetic device is provided on the outer wall surface of the air vent of each of the noise reduction areas, which is used to limit the flow of the magnetic fluid by generating a magnetic field.

[0011] Furthermore, each magnetic device is connected to a linear motion mechanism, which enables the magnetic device to move axially along the air compressor outlet through the linear motion mechanism, thereby changing the distance between the magnetic fluid in the silencer area and the suspension end, thereby changing the frequency of radial oscillation generated by the suspension end.

[0012] Furthermore, at least one magnetic device is connected to a rotating mechanism, which causes the magnetic device to periodically swing around the outer wall of the air compressor vent. The circumferential swing of the magnetic fluid is used to alternately compress the cavities on both sides thereof, thereby intensifying the tangential oscillation of the cavity.

[0013] Furthermore, at least two spaced apart magnetic devices are connected to the rotating mechanism.

[0014] Furthermore, a second-stage noise reduction structure is provided in the noise reduction cavity, and the second-stage noise reduction structure is located in the noise reduction cavity between the first-stage noise reduction structure and the noise reduction area.

[0015] Furthermore, the second-stage muffler structure comprises an orifice plate, the upper surface of which is connected to the inner wall of the muffler chamber. A gap X exists between the lower surface of the orifice plate and the outer ring of the inner sleeve. This gap X is greater than the amplitude of the inner sleeve at the point where the orifice plate is mounted. This gap X serves to prevent radial oscillations at the suspended end. The gap X between the lower surface of the orifice plate and the outer ring of the inner sleeve forms an annular gap, which, together with the holes in the orifice plate, achieves muffler effect.

[0016] Furthermore, an installation groove is provided on the inner wall surface of the air vent of the air compressor located at the suspension end, and an elastic hollow tube is installed in the installation groove, and the outer wall surface of the elastic hollow tube is in contact with the suspension end. A through hole is provided on the elastic hollow tube, and the elastic hollow tube is driven by the suspension end to produce resonance. The elastic hollow tube compresses the sound in the hollow tube during the oscillation process, and damping is generated when the sound flows through the through hole of the elastic hollow tube, dissipating the vibration energy, thereby improving the sound absorption performance.

[0017] Furthermore, the outer wall surface of the suspension end is a cone surface, the elastic hollow tube is tangent to the cone surface, and the center line of the through hole is parallel to the tangent line.

[0018] An air compressor, wherein the air compressor silencer and vibration reduction device is installed at the air inlet and / or the air outlet of the air compressor.

[0019] The beneficial effects of the present invention are:

[0020] 1. In the air compressor silencer device described in the present invention, the inner wall surface of the air compressor vent is embedded in one end of the inner sleeve, and the other end of the inner sleeve is in a suspended state. When the sound in the air compressor vent enters the tail end of the silencer cavity, radial oscillations will be generated at the suspended end of the inner sleeve, which can attenuate the sound energy.

[0021] 2. The air compressor silencer device described in the present invention has a plurality of spaced silencer areas in the silencer cavity. Each silencer area is filled with magnetic fluid. The radial oscillation generated by the suspension end is used to cause fluctuations in the tail space of the silencer cavity. Such fluctuations will cause fluctuations in the thickness of the magnetic fluid in the silencer cavity. Since the magnetic fluid is incompressible, the fluctuations in the thickness of the magnetic fluid will be converted into tangential oscillations. The tangential oscillations of the adjacent magnetic fluids will attenuate the sound energy of the sound entering the cavity. In other words, the sound energy of the sound entering the cavity of the present invention is accelerated by tangential and radial oscillations, and the ability to attenuate sound energy exceeds that of using only tangential or radial oscillations.

[0022] 3. The air compressor silencer device described in the present invention is provided with a magnetic device on the outer wall surface of the air compressor vent corresponding to each silencer area, which generates a magnetic field to restrict the flow of magnetic fluid; each magnetic device is connected to a linear motion mechanism, and the linear motion mechanism is used to move the magnetic device along the axial direction of the air compressor vent, so that the magnetic fluid in the corresponding silencer area can be moved axially, so that the distance between the silencer area and the suspension end is changed, and the frequency of radial oscillation generated by the suspension end can be changed.

[0023] 4. In the air compressor silencer device described in the present invention, at least one magnetic device is connected to a rotating mechanism, and the rotating mechanism is used to cause the magnetic device to periodically swing around the outer wall surface of the air compressor vent, so that the magnetic fluid in the corresponding silencer area can swing circumferentially. The circumferential swing of the magnetic fluid can alternately compress the cavities on both sides thereof, thereby intensifying the tangential oscillation of the cavity.

[0024] 5. The air compressor silencer device described in the present invention has a mounting groove provided on the inner wall surface of the air compressor vent located at the suspended end, an elastic hollow tube is installed in the mounting groove, the outer wall surface of the elastic hollow tube is in contact with the suspended end, and a through hole is provided on the elastic hollow tube. When the suspended end generates radial oscillation, the suspended end drives the elastic hollow tube to generate a joint oscillation. The elastic hollow tube compresses the sound inside the hollow tube during the oscillation process. When the sound flows through the through hole of the elastic hollow tube, it generates damping, dissipates vibration energy, and thus improves the sound absorption performance.

[0025] 6. The air compressor silencer device described in the present invention is provided with a first-stage silencer structure on the wall of the inner sleeve for attenuating sound energy; a second-stage silencer structure is provided in the silencer cavity between the first-stage silencer structure and the silencer area, which can further attenuate sound energy. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. The drawings described below are some embodiments of the present invention. For ordinary technicians in this field, it is obvious that other drawings can be obtained based on these drawings without paying any creative work.

[0027] FIG1 is an assembly diagram of the air compressor silencer device according to the present invention.

[0028] FIG2 is a cross-sectional view taken along line AA of FIG1 .

[0029] FIG3 is a sectional view taken along line BB in FIG1 .

[0030] FIG4 is a three-dimensional diagram of the inner sleeve according to the present invention.

[0031] FIG5 is a schematic diagram of a partial installation of the orifice plate according to the present invention.

[0032] FIG6 is a schematic diagram of a partial installation of the elastic hollow tube according to the present invention.

[0033] FIG7 is an assembly diagram of the air compressor silencer of Example 2.

[0034] In the picture:

[0035] 1-air compressor vent; 1-1-protrusion; 2-inner sleeve; 2-1-fixed end; 2-2-suspended end; 2-3-notch; 2-4-conical surface; 3-orifice plate; 4-magnetic fluid; 5-elastic hollow tube; 5-1-through hole; 6-muffler cavity; 7-first-stage muffler structure. DETAILED DESCRIPTION

[0036] The following describes embodiments of the present invention in detail, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and are not to be construed as limiting the present invention.

[0037] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "axial", "radial", "vertical", "horizontal", "inside", "outside" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "multiple" means two or more, unless otherwise clearly and specifically defined.

[0038] In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," "connect," "fixed," etc. should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediary; or internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0039] As shown in Figures 1 and 2, the air compressor silencer device described in the present invention has the inner wall surface of the air compressor vent 1 connected to one end of the inner sleeve 2, that is, one end of the inner sleeve 2 is a fixed end 2-1, and the other end of the inner sleeve 2 is in a suspended state, that is, there is a gap between the other end of the inner sleeve 2 and the inner wall surface of the air compressor vent 1, and the other end of the inner sleeve 2 is a suspended end 2-2. The inner sleeve 2 is a thin-walled tube, and an axial notch 2-3 is provided in the inner sleeve 2. The purpose of the notch 2-3 is to facilitate the installation of the inner sleeve 2 in the air compressor vent 1. In addition, the notch 2-3 can facilitate the deformation of the inner sleeve 2. An annular groove with a notch is provided on the air compressor vent 1. The annular groove and the outer wall surface of the inner sleeve 2 constitute a silencer chamber 6. The axial length of the silencer chamber 6 is less than the axial length of the inner sleeve 2. A notched annular groove forms a protrusion 1-1 within the air compressor vent 1. The notches 2-3 in the inner sleeve 2 are located at the protrusion 1-1. The width of the protrusion 1-1 is greater than the spacing between the notches 2-3, so that the bottom of the inner sleeve 2 can be supported on the protrusion 1-1. The air compressor vent 1 can be an air compressor inlet, an air compressor outlet, or another exhaust bypass of the air compressor.

[0040] The muffler cavity 6 is provided with a plurality of spaced-apart muffler zones, each of which is filled with magnetic fluid 4. A magnetic device is provided on the outer wall of the air compressor vent 1 corresponding to each muffler zone, generating a magnetic field to restrict the flow of the magnetic fluid 4. Furthermore, the position of the magnetic field can be varied, thereby changing the position of the muffler zones. A cavity is formed between adjacent muffler zones. The spaced-apart muffler zones are located near the suspended end 2-2 of the inner sleeve 2, but a certain distance exists between the muffler zones and the suspended end 2-2.

[0041] As shown in Figure 4, the wall surface of the inner sleeve 2 is provided with a first-stage silencer structure 7. The first-stage silencer structure 7 can also be a rectangular groove. At least one rectangular groove is provided on the arc-shaped wall surface of the inner sleeve 2. The rectangular groove connects the air compressor vent 1 with the silencer cavity 6 to attenuate sound energy.

[0042] As shown in FIG7 , the first-stage muffler structure 7 is a plurality of orifice plates. A plurality of through holes are provided on the arc-shaped wall surface of the inner sleeve 2 . The through holes connect the air compressor vent 1 with the muffler cavity 6 to attenuate sound energy.

[0043] Because the other end of the inner sleeve 2 is suspended, when sound from the compressor vent 1 enters the tail of the muffler chamber 6, it generates radial oscillations at the suspended end 2-2 of the inner sleeve 2, further attenuating the sound energy. The frequency of the oscillations is determined by the distance between the muffler region and the suspended end 2-2. Although the bottom of the inner sleeve 2 is supported on the protrusion 1-1, since the protrusion 1-1 is much smaller than the circumference of the inner sleeve 2, its support can be considered as a single point on the circumference. Strictly speaking, while it is possible that there is no possibility of slight suppression of the radial oscillations of the suspended end 2-2, the suppression effect of this point on the circumference is very limited and can be ignored. The magnetic fluid 4 in the muffler chamber 6 can be considered an elastic damping fluid. Although the magnetic field can restrict the flow of the magnetic fluid 4, when sound enters the cavity between adjacent magnetic fluids 4, it can cause the compressed magnetic fluid 4 to oscillate. The radial oscillations of the suspended end 2-2 exacerbate the tangential oscillations of the magnetic fluid 4. Because the radial oscillations of the suspended end 2-2 cause fluctuations in the space at the tail end of the muffler cavity 6, these fluctuations cause fluctuations in the thickness of the magnetic fluid 4 in the muffler cavity 6. Since the magnetic fluid 4 is incompressible, these fluctuations in the thickness of the magnetic fluid 4 are converted into tangential oscillations. The tangential oscillations of the adjacent magnetic fluid 4 attenuate the acoustic energy of the sound entering the cavity. In other words, the acoustic energy of the sound entering the cavity of the present invention is accelerated by tangential and radial oscillations, and the ability to attenuate sound energy exceeds that of using only tangential or radial oscillations.

[0044] In one embodiment, the muffler chamber 6 is provided with 3 to 6 spaced-apart muffler zones, each of which is filled with a magnetic fluid 4. A magnetic device is provided on the outer wall of the air compressor vent 1 corresponding to each muffler zone, wherein each magnetic device is connected to a linear motion mechanism. The linear motion mechanism is used to move the magnetic device axially along the air compressor vent 1, thereby causing the magnetic fluid 4 in the corresponding muffler zone to move axially. This changes the distance between the muffler zone and the suspension end 2-2, thereby changing the frequency of radial oscillations generated by the suspension end 2-2. The linear motion mechanism is generally a pneumatic cylinder, a hydraulic cylinder, or a linear screw.

[0045] In one embodiment, the muffler cavity 6 is provided with 3 to 6 spaced-apart muffler areas, each muffler area is filled with magnetic fluid 4, and a magnetic device is provided on the outer wall of the air compressor vent 1 corresponding to each muffler area, one of the magnetic devices is connected to a rotating mechanism, and the magnetic device is caused to swing periodically around the outer wall of the air compressor vent 1 through the rotating mechanism, so that the magnetic fluid 4 in the corresponding muffler area can swing circumferentially. The circumferential swing of the magnetic fluid 4 can alternately compress the cavities on both sides thereof, thereby intensifying the tangential oscillation of the cavity.

[0046] In one embodiment, multiple magnetic devices may be connected to a rotating mechanism. Here, the multiple magnetic devices may be provided with rotating mechanisms, and each magnetic device may be rotated at different angles. Alternatively, the multiple magnetic devices may be connected to a rotating mechanism to achieve synchronous rotation of the multiple magnetic devices. If multiple magnetic devices are connected to a rotating mechanism, generally multiple spaced magnetic devices are connected to a rotating mechanism. Assume that the muffler chamber 6 is provided with five spaced muffler areas, each muffler area corresponds to a magnetic device, and different magnetic devices are distinguished by serial numbers, i.e., magnetic device No. 1, magnetic device No. 2, magnetic device No. 3, magnetic device No. 4, and magnetic device No. 5; magnetic device No. 1, magnetic device No. 3, and magnetic device No. 5 are connected to a rotating mechanism, or magnetic device No. 2 and magnetic device No. 4 are connected to a rotating mechanism. The rotating mechanism is an existing rotary mechanism and may be composed of a gear train.

[0047] As shown in Figures 1 and 5, in another embodiment, a perforated plate 3 is provided in the muffler chamber 6. The perforated plate 3 is located in the muffler chamber 6 between the first-stage muffler structure and the muffler area. The perforated plate 3 can be considered as a second-stage muffler structure. The upper surface of the perforated plate 3 is connected to the inner wall of the muffler chamber 6, and there is a gap X between the lower surface of the perforated plate 3 and the outer ring of the inner sleeve 2. The gap X is greater than the amplitude of the inner sleeve 2 at the installation point of the perforated plate 3. The role of the gap X is to avoid suppressing the radial oscillation of the suspended end 2-2, and the gap X between the lower surface of the perforated plate 3 and the outer ring of the inner sleeve 2 is a thin annular gap. The thin annular gap and the holes on the perforated plate 3 work together to achieve sound elimination.

[0048] Since there is a gap between the suspended end 2-2 at the other end of the inner sleeve 2 and the inner wall surface of the air compressor vent 1, experiments have shown that when the pressure of the air compressor vent 1 is high, a certain amount of noise will be generated in the gap. Therefore, the present invention provides a mounting groove 1-2 on the inner wall surface of the air compressor vent 1 located at the suspended end 2-2, and an elastic hollow tube 5 is installed in the mounting groove 1-2. The outer wall surface of the elastic hollow tube 5 contacts the suspended end 2-2, and the elastic hollow tube 5 is provided with a through hole 5-1, as shown in Figures 1 and 6. When the suspended end 2-2 produces radial oscillations, the suspended end 2-2 drives the elastic hollow tube 5 to produce a common oscillation. The elastic hollow tube 5 compresses the sound inside the hollow tube during the oscillation process. When the sound flows through the through hole 5-1 of the elastic hollow tube 5, it generates damping, dissipates the vibration energy, and thus improves the sound absorption performance.

[0049] In order to achieve a better muffler effect, the through hole 5 - 1 on the elastic tube 5 only connects the interior of the elastic hollow tube 5 with the muffler chamber 6 ; or the through hole 5 - 1 on the elastic tube 5 only connects the interior of the elastic hollow tube 5 with the air compressor vent 1 .

[0050] As shown in Figure 6, the outer wall surface of the suspension end 2-2 is a tapered conical surface 2-4, the bottom of the elastic hollow tube 5 is tangent to the conical surface 2-4, the elastic hollow tube 5 is in contact with at least one surface of the mounting groove 1-2, and the center line of the through hole 5-1 is parallel to the tangent line. In this way, when the suspension end 2-2 generates radial oscillations, the elastic hollow tube 5 compresses the sound in the hollow tube during the oscillation process, and when the sound flows through the through hole 5-1 of the elastic hollow tube 5, the elastic hollow tube 5 will produce optimal damping.

[0051] The air compressor of the present invention is provided with the air compressor silencer and vibration reduction device installed at the air compressor air inlet and / or the air compressor outlet. Other exhaust bypasses of the air compressor may also be provided with the air compressor silencer and vibration reduction device.

[0052] It should be understood that although this specification is described according to various embodiments, not every embodiment contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

[0053] The series of detailed descriptions listed above are only specific descriptions of feasible embodiments of the present invention. They are not intended to limit the scope of protection of the present invention. Any equivalent embodiments or changes that do not deviate from the technical spirit of the present invention should be included in the scope of protection of the present invention.

Claims

1. A noise reduction and vibration reduction device for an air compressor, characterized in that: An inner sleeve (2) is installed in an air compressor vent (1), a fixed end (2-1) at one end of the inner sleeve (2) is connected to the inner wall surface of the air compressor vent (1), and a suspended end (2-2) at the other end of the inner sleeve (2) is in a suspended state; a groove is provided on the air compressor vent (1), and the space between the groove and the inner sleeve (2) forms a silencer chamber (6), and a plurality of silencer regions are provided in the silencer chamber (6) at intervals, each silencer region is filled with a magnetic fluid (4), and a first-stage silencer structure (7) is provided on the inner sleeve (2); radial oscillations are generated through the suspended end (2-2), so that the magnetic fluid (4) in the silencer region generates tangential oscillations, which are used to attenuate the sound energy entering the silencer chamber (6).

2. The air compressor silencing and vibration reduction device according to claim 1, characterized in that: The outer wall surface of the air compressor vent (1) corresponding to each of the noise reduction areas is provided with a magnetic device for limiting the flow of the magnetic fluid (4) by generating a magnetic field.

3. The air compressor silencing and vibration reduction device according to claim 2, characterized in that: Each magnetic device is connected to a linear motion mechanism, and the linear motion mechanism is used to move the magnetic device along the axial direction of the air compressor outlet, thereby changing the distance between the magnetic fluid (4) in the silencer area and the suspension end (2-2), so as to change the frequency of radial oscillation generated by the suspension end (2-2).

4. The air compressor silencing and vibration reduction device according to claim 2, characterized in that: At least one magnetic device is connected to a rotating mechanism, and the rotating mechanism causes the magnetic device to periodically swing around the outer wall surface of the air compressor vent (1), and the magnetic fluid (4) swings circumferentially to alternately compress the cavities on both sides thereof.

5. The air compressor silencing and vibration reduction device according to claim 4, characterized in that: At least two spaced apart magnetic devices are connected to the rotating mechanism.

6. The air compressor silencing and vibration reduction device according to claim 1, characterized in that: A second-stage sound-absorbing structure is provided in the sound-absorbing cavity (6), and the second-stage sound-absorbing structure is located in the sound-absorbing cavity (6) between the first-stage sound-absorbing structure (7) and the sound-absorbing area.

7. The air compressor silencing and vibration reduction device according to claim 6, characterized in that: The second-stage silencer structure is a perforated plate (3), the upper surface of the perforated plate (3) is connected to the inner wall of the silencer chamber (6), and there is a gap X between the lower surface of the perforated plate (3) and the outer ring of the inner sleeve (2), and the gap X is greater than the amplitude of the inner sleeve (2) at the installation position of the perforated plate (3).

8. The air compressor silencing and vibration reduction device according to claim 1, characterized in that: An installation groove (1-2) is provided on the inner wall surface of the air compressor vent (1) located at the suspension end (2-2), an elastic hollow tube (5) is installed in the installation groove (1-2), and the outer wall surface of the elastic hollow tube (5) is in contact with the suspension end (2-2), and a through hole (5-1) is provided on the elastic hollow tube (5), and the elastic hollow tube (5) is driven by the suspension end (2-2) to produce resonance.

9. The air compressor silencing and vibration reduction device according to claim 8, characterized in that: The outer wall surface of the suspension end (2-2) is a conical surface (2-4), the elastic hollow tube (5) is tangent to the conical surface (2-4), and the center line of the through hole (5-1) is parallel to the tangent line.

10. An air compressor, characterized in that: The air compressor air inlet and / or outlet is installed with the air compressor silencer and vibration reduction device according to any one of claims 1 to 9.

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