Axial flow fan silencer with vibration reduction function and ship

Abstract

The invention discloses an axial flow fan silencer with a vibration reduction function and a ship. The axial flow fan silencer with the vibration reduction function comprises a silencing module and a vibration reduction module. The first end of the silencing module is coaxially connected with the axial flow fan; the first end of the vibration reduction module is coaxially connected with the second end of the noise elimination module, and the second end of the vibration reduction module is coaxially connected with a fan seat frame; the vibration damping module comprises a flexible flow guide cover and a vibration damper array. The first end of the flexible flow guide cover is connected with the second end of the silencing module through a first connecting flange, and the second end of the flexible flow guide cover is connected with the fan seat frame through a second connecting flange; the flexible flow guide cover is communicated with the inner cavity of the silencing module and the inner cavity of the fan seat frame to form an airflow channel; the shock absorber array is installed between the first connecting flange and the second connecting flange and located outside the flexible flow guide cover.

Description

Technical Field

[0001] The present application relates to the field of ship technology, and in particular to an axial flow fan silencer with a vibration reduction function and a ship. Background Art

[0002] In the development and design of shipbuilding technology, axial fans, as ventilation equipment customized specifically for ships, are an indispensable component of shipbuilding. Currently, marine axial fan mufflers primarily utilize two basic technologies: resistive and reactive. Resistive mufflers absorb sound energy through porous sound-absorbing materials, achieving some effectiveness in reducing mid- and high-frequency noise but exhibiting limited suppression of low-frequency noise. Resistive mufflers utilize acoustic cavity resonance and sudden changes in duct cross-section to attenuate noise at specific frequencies. However, due to their high frequency selectivity, their application is relatively limited.

[0003] With the continuous advancement of shipbuilding technology, the performance requirements for silencers are becoming increasingly stringent, and the current silencers for axial fans have significant limitations that are gradually becoming apparent. On the one hand, their functions are relatively simple and cannot meet the diverse needs of ships under complex operating conditions. On the other hand, their vibration reduction effect is poor, making it difficult to effectively suppress the vibrations generated by the fan operation. During the ship's voyage, this lack of vibration reduction not only weakens the stability of the silencer's own operation, but also greatly reduces the noise reduction effect. Ships are compact and contain a large number of equipment. Fan vibrations can easily cause resonance in other structures, interfering with the normal operation of surrounding equipment. For example, vibrations transmitted to the hull structure may cause the bulkhead to shake and generate additional noise. For precision instruments and equipment, it can also affect their measurement accuracy and service life. Therefore, existing silencers cannot meet the stringent requirements of ships for low vibration and low noise equipment. Summary of the Invention

[0004] The purpose of the embodiments of the present invention is to provide an axial flow fan silencer with a vibration reduction function and a ship, which can solve the above-mentioned problems existing in the prior art.

[0005] To achieve the above objectives, this application adopts the following technical solutions: On the one hand, as an embodiment of the present application, an axial flow fan muffler with a vibration reduction function is provided, comprising: A silencer module, wherein a first end of the silencer module is coaxially connected to the axial flow fan; A vibration reduction module, wherein the first end of the vibration reduction module is coaxially connected to the second end of the muffler module, and the second end of the vibration reduction module is coaxially connected to the fan base; the vibration reduction module comprises: A flexible air guide cover, wherein a first end of the flexible air guide cover is connected to a second end of the muffler module via a first connecting flange, and a second end of the flexible air guide cover is connected to the fan mount via a second connecting flange; the flexible air guide cover is connected to the inner cavity of the muffler module and the inner cavity of the fan mount to form an air flow channel; A vibration damper array is installed between the first connecting flange and the second connecting flange.

[0006] Preferably, the vibration absorber array includes at least four nonlinear damping vibration absorbers, and the four nonlinear damping vibration absorbers are evenly distributed around the circumference of the flexible fairing; the axial stiffness of each nonlinear damping vibration absorber is and the radial stiffness of each of the nonlinear damping shock absorbers The stiffness matching relationship satisfies .

[0007] Preferably, the distance L between the first connecting flange and the second connecting flange is 1.2H-1.5H, wherein H is the free height of the nonlinear damping vibration absorber.

[0008] Preferably, the vibration reduction module further includes: an annular bellows connected between the first connecting flange and the second connecting flange; the annular bellows has a preset axial compression amount δ=0.3Δ-0.5Δ, where Δ is the compression amount of the nonlinear damping shock absorber; a limiting ring, the limiting ring being supported and mounted on the first connecting flange or the second connecting flange by a mounting bracket; When the actual axial compression amount of the annular bellows exceeds the preset axial compression amount of the annular bellows, the annular bellows abuts against the limiting ring.

[0009] Preferably, the vibration reduction module further includes: A non-combustible rubber gasket is abutted between the first connecting flange and the second end of the muffler module; and / or the non-combustible rubber gasket is abutted between the second connecting flange and the fan mount.

[0010] Preferably, the flexible air guide cover includes a high-temperature resistant canvas layer, a sound-absorbing cotton layer and a metal wire mesh reinforcement layer in sequence from the inside of the air flow channel to the outside of the air flow channel.

[0011] Preferably, the muffler module comprises, from the inside of the air flow channel to the outside of the air flow channel, an expansion chamber muffler section, a resonance sound absorption section and a micro-perforated plate muffler section; The resonant sound absorption section is provided with a tunable Helmholtz resonance cavity, and the resonant frequency of the tunable Helmholtz resonance cavity is: ; Where c is the speed of sound, S is the equivalent area of ​​the radial annular opening of the tunable Helmholtz resonator, V is the volume of the annular cavity of the tunable Helmholtz resonator, L is the radial length of the neck of the tunable Helmholtz resonator, is the neck correction length of the tunable Helmholtz resonator, generally =0.8r-0.85r, r is the average radius of the tunable Helmholtz resonant cavity.

[0012] Preferably, it also includes: An acoustic decoupling ring is coaxially mounted between the first end of the vibration reduction module and the second end of the silencer module; the acoustic decoupling ring includes hard spacer rings and elastic gasket rings alternately arranged along the circumferential direction; wherein the thickness t of the hard spacer ring and the thickness T of the elastic gasket satisfy t / T=1 / 3-1 / 2.

[0013] Preferably, it also includes: A mass tuning block is mounted on the fan mount; the mass m of the mass tuning block and the mass M of the impeller in the axial flow fan satisfy m=0.1M-0.2M, and the eccentricity e between the center of mass of the mass tuning block and the axis of the axial flow fan is ≤0.05D, where D is the cylinder diameter of the axial flow fan.

[0014] On the other hand, as an embodiment of the present application, a ship is provided, comprising the axial flow fan silencer with vibration reduction function as described above.

[0015] The beneficial effects of this application are: The setting of the vibration reduction module in this application can reduce the vibration transmission rate of the fan by more than 60%, effectively avoiding structural resonance caused by vibration, reducing bulkhead shaking and additional noise generation. At the same time, the vibration reduction unit can improve the operating stability of the axial flow fan silencer itself and avoid loosening of the internal structure caused by vibration. Furthermore, the silencer module and the vibration reduction module in this application work together to reduce the operating noise of the fan and suppress vibration transmission, meeting the diverse needs under complex working conditions of ships. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The present application is further described in detail below with reference to the accompanying drawings and examples.

[0017] Figure 1 Schematic diagram of the structure of an axial flow fan muffler with vibration reduction function provided in an embodiment of the present application.

[0018] Figure 2 for Figure 1 Schematic diagram of the axial structure.

[0019] In the picture: 100, muffler module; 110, expansion chamber muffler section; 120, resonance sound absorption section; 130, micro-perforated plate muffler section; 200, vibration reduction module; 210, flexible fairing; 220, first connecting flange; 230, second connecting flange; 240, nonlinear damping vibration absorber; 250, non-combustible rubber gasket; 300, axial flow fan; 310, impeller; 400. Fan mount; 410. Mass tuning block. DETAILED DESCRIPTION

[0020] To make the technical problems solved by this application, the technical solutions adopted, and the technical effects achieved more clearly, the technical solutions of the embodiments of this application are further described in detail below. Obviously, the embodiments described are only part of the embodiments of this application, not all of them. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without making any creative efforts shall fall within the scope of protection of this application.

[0021] In the description of this application, unless otherwise expressly specified or limited, the terms "connected," "connected," and "fixed" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integration; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and can 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 present invention based on the specific circumstances.

[0022] In this application, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Moreover, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0023] Figure 1 Schematic diagram of the structure of an axial flow fan muffler with vibration reduction function provided in an embodiment of the present application. Figure 2 for Figure 1 Schematic diagram of the axial structure. Figure 1 and Figure 2As shown, this embodiment provides an axial fan silencer with a vibration reduction function, comprising: a silencer module 100 and a vibration reduction module 200; the first end of the silencer module 100 is coaxially connected to the axial fan 300; the first end of the vibration reduction module 200 is coaxially connected to the second end of the silencer module 100, and the second end of the vibration reduction module 200 is coaxially connected to the fan mount 400. The vibration reduction module 200 comprises: a flexible air guide 210 and a vibration damper array; the first end of the flexible air guide 210 is connected to the second end of the silencer module 100 via a first connecting flange 220, and the second end of the flexible air guide 210 is connected to the fan mount 400 via a second connecting flange 230; the flexible air guide 210 communicates with the inner cavity of the silencer module 100 and the inner cavity of the fan mount 400 to form an air flow channel; the vibration damper array is installed between the first connecting flange 220 and the second connecting flange 230.

[0024] The vibration absorber array is described in detail as follows: the vibration absorber array includes at least four nonlinear damping vibration absorbers 240, and the four nonlinear damping vibration absorbers 240 are evenly distributed around the circumference of the flexible deflector 210; the axial stiffness of each nonlinear damping vibration absorber 240 is and the radial stiffness of each of the nonlinear damping shock absorbers 240 The stiffness matching relationship satisfies .

[0025] Here, the nonlinear damping shock absorber 240 can be made of high-damping synthetic rubber specially used for ships, which can not only have both elasticity and damping performance but also be resistant to seawater corrosion and have a flame retardant grade that can meet the requirements.

[0026] In this embodiment, the nonlinear damping vibration isolator 240 creates a synergistic vibration reduction effect in both the axial direction (the thrust direction of the axial fan) and the radial direction (the direction of the eccentric vibration of the axial fan). By balancing the stiffness, the resonant frequency of the axial fan muffler is shifted to the non-operating frequency band, reducing coupling with the fan's operating frequency and avoiding vibration amplification caused by insufficient stiffness in a single direction.

[0027] In an optional embodiment, the distance L between the first connecting flange 220 and the second connecting flange 230 is 1.2H-1.5H, where H is the free height of the nonlinear damping vibration absorber 240 .

[0028] Regarding the free height of the nonlinear damping vibration absorber 240, it should be noted that the free height of the nonlinear damping vibration absorber 240 is its height in the unloaded state. The reserved vibration absorber array installation spacing between the first connecting flange 220 and the second connecting flange 230 in this embodiment ensures that the nonlinear damping vibration absorber 240 is in the optimal elastic deformation range, providing sufficient rigidity to support the weight of the wind turbine while maintaining good dynamic response. The nonlinear damping vibration absorber 240 can fully utilize its multi-directional rigidity matching and broadband damping characteristics, significantly improving overall stability and noise reduction.

[0029] In one embodiment, the vibration damping module 200 further includes an annular bellows and a retaining ring. The annular bellows is connected between the first connecting flange 220 and the second connecting flange 230. The annular bellows has a preset axial compression of δ = 0.3Δ - 0.5Δ, where Δ is the compression of the nonlinear damping vibration absorber 240. The retaining ring is mounted on the first connecting flange 220 or the second connecting flange 230 via a mounting bracket.

[0030] When the actual axial compression amount of the annular bellows exceeds the preset axial compression amount of the annular bellows, the annular bellows abuts against the limiting ring.

[0031] In this embodiment, the annular bellows and the limiting ring serve as dynamic compensation structures between the first connecting flange 220 and the second connecting flange 230. The annular bellows achieves an auxiliary vibration reduction effect, and cooperates with the setting of the limiting ring to constrain the actual axial compression of the annular bellows within the preset axial compression amount, thereby preventing the bellows from fatigue failure due to excessive deformation.

[0032] In one embodiment, the vibration reduction module 200 further includes a non-combustible rubber gasket 250 .

[0033] Optionally, the non-combustible rubber gasket 250 abuts between the first connecting flange 220 and the second end of the muffler module 100 .

[0034] Optionally, the non-combustible rubber gasket 250 abuts between the second connecting flange 230 and the fan mount 400 .

[0035] Optionally, the non-combustible rubber gasket 250 is respectively abutted between the first connecting flange 220 and the second end of the muffler module 100 , and between the second connecting flange 230 and the fan mount 400 .

[0036] In this embodiment, the non-combustible rubber gasket 250 can reduce the vibration transmissibility in the frequency range of 100 Hz to 500 Hz by 20% to 30%, and reduce the aerodynamic noise in the frequency range above 1 kHz by 2 dB to 4 dB.

[0037] In this embodiment, the non-combustible rubber gasket 250 is provided to effectively improve the sealing reliability and vibration reduction performance of the ventilation system while ensuring fire safety.

[0038] The flexible air guide cover 210 is introduced in detail as follows. The flexible air guide cover 210 includes a high-temperature resistant canvas layer, a sound-absorbing cotton layer and a metal wire mesh reinforcement layer from the inside of the air flow channel to the outside of the air flow channel.

[0039] The thickness of the high temperature resistant canvas layer involved here can generally be 2mm to 3mm, and the surface of the high temperature resistant canvas layer is provided with a fine perforated structure.

[0040] In this embodiment, the three-layer composite design of the high-temperature resistant canvas layer, the sound-absorbing cotton layer and the metal mesh reinforcement layer enables the flexible air guide cover 210 to achieve multiple functions of high-temperature resistance, noise reduction and structural strengthening, and is particularly suitable for use in environments with limited space and sensitive to vibration and noise.

[0041] In an optional embodiment, the silencer module 100 includes, from the inside of the air flow channel to the outside of the air flow channel, an expansion chamber silencer section 110 , a resonance sound absorption section 120 , and a micro-perforated plate silencer section 130 .

[0042] The resonant sound absorbing section 120 is provided with a tunable Helmholtz resonant cavity, and the resonant frequency of the tunable Helmholtz resonant cavity is: ; Where c is the speed of sound, S is the equivalent area of ​​the radial annular opening of the tunable Helmholtz resonator, V is the volume of the annular cavity of the tunable Helmholtz resonator, L is the radial length of the neck of the tunable Helmholtz resonator, is the neck correction length of the tunable Helmholtz resonator, generally =0.8r-0.85r, where r is the average radius of the tunable Helmholtz resonant cavity. The tunable Helmholtz resonant cavity neck mentioned here generally refers to a relatively narrow channel structure connecting the tunable Helmholtz resonant cavity and the air flow channel.

[0043] The resonant frequency of the tunable Helmholtz resonant cavity is adjusted to cover a range from 1 / 3 octave to 3 octave of the fundamental frequency of the fan by adjusting the annular cavity volume V of the tunable Helmholtz resonant cavity, the radial length L of the neck of the tunable Helmholtz resonant cavity, and the average radius r of the tunable Helmholtz resonant cavity.

[0044] In this embodiment, the expansion chamber muffler section 110, the resonant sound absorption section 120, and the micro-perforated plate muffler section 130 are radially arranged, surrounding the airflow channel in an annular configuration. This arrangement eliminates axial space and improves space utilization. Furthermore, this segment arrangement reduces the impact of airflow scour on the performance of the tunable Helmholtz resonator, enhancing its resistance to airflow interference.

[0045] In an optional embodiment, the muffler module 100 can be arranged along the airflow direction (eg Figure 1 (As indicated by the arrow in the middle) an expansion chamber muffler section, a resonant sound absorption section, and a micro-perforated plate muffler section are sequentially arranged. The axial length ratio of the expansion chamber muffler section, the resonant sound absorption section, and the micro-perforated plate muffler section can be 4:2:1. This ratio should not be used as a limitation and can be adjusted adaptively according to design requirements.

[0046] Furthermore, the resonant sound absorbing section is provided with a tunable Helmholtz resonance cavity, and the resonant frequency of the tunable Helmholtz resonance cavity is: ; Wherein, c is the speed of sound, S is the opening area of ​​the neck of the tunable Helmholtz resonator, V is the volume of the tunable Helmholtz resonator, L is the axial length of the neck of the tunable Helmholtz resonator, is the neck correction length of the tunable Helmholtz resonator, generally =0.8r-0.85r, where r is the average radius of the tunable Helmholtz resonant cavity. The tunable Helmholtz resonant cavity neck mentioned here generally refers to a relatively narrow channel structure connecting the tunable Helmholtz resonant cavity and the air flow channel.

[0047] The resonant frequency of the tunable Helmholtz resonant cavity is adjusted to cover a range from 1 / 3 octave to 3 octave of the fundamental frequency of the fan by adjusting the annular cavity volume V of the tunable Helmholtz resonant cavity, the radial length L of the neck of the tunable Helmholtz resonant cavity, and the average radius r of the tunable Helmholtz resonant cavity.

[0048] In one embodiment, it also includes: an acoustic decoupling ring, which is coaxially installed between the first end of the vibration reduction module 200 and the second end of the silencer module 100; the acoustic decoupling ring includes hard spacer rings and elastic gaskets alternately arranged along the circumferential direction; wherein the thickness t of the hard spacer ring and the thickness T of the elastic gasket satisfy t / T=1 / 3-1 / 2.

[0049] The acoustic-vibration decoupling ring provided in this embodiment adopts a hard-soft alternating structure, utilizes a hard spacer ring to transmit part of the force, and an elastic gasket ring to buffer vibration, and is adapted according to the t / T ratio. It can effectively cut off the coupled transmission of sound and vibration, improve the decoupling effect of the axial fan silencer, and optimize the overall noise reduction performance.

[0050] In one embodiment, it further includes: a mass tuning block 410, which is installed on the fan mount 400; the mass m of the mass tuning block 410 and the mass M of the impeller 310 in the axial flow fan 300 satisfy m=0.1M-0.2M, and the eccentricity e between the center of mass of the mass tuning block 410 and the axis of the axial flow fan 300 is ≤0.05D, where D is the cylinder diameter of the axial flow fan 300.

[0051] The mass tuning block provided in this embodiment matches the mass M of the impeller 310 with the eccentricity e between the center of mass of the mass tuning block 410 and the axis of the axial flow fan 300, and utilizes the principle of dynamic vibration absorption to offset the vibration energy of the impeller during operation of the axial flow fan, suppress resonance, reduce fan vibration transmission, and improve system stability and noise reduction effects.

[0052] As an embodiment of the present application, a ship is also provided, comprising the axial flow fan silencer with vibration reduction function as described above, wherein the cabin noise is reduced from 95dB to 88dB, and the vibration amplitude of the hull structure is reduced by 55%.

[0053] In the description herein, it should be understood that the terms "upper," "lower," "left," "right," and other positions or relationships are used solely for ease of description and simplified operation, and are not intended to indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on this application. Furthermore, the terms "first" and "second" are used solely for descriptive purposes and have no special meaning.

[0054] In this specification, reference to terms such as "one embodiment" or "example" means that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment or example.

[0055] In addition, it should be understood that although this specification is described in terms of implementation methods, not every implementation method 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.

[0056] The technical principles of the present application have been described above in conjunction with specific embodiments. These descriptions are intended solely to explain the principles of the present application and are not to be construed in any way as limiting the scope of protection of the present application. Based on the explanations herein, those skilled in the art will be able to devise other specific implementations of the present application without inventive effort, and such implementations will fall within the scope of protection of the present application.

Claims

1. An axial flow fan muffler with a vibration reduction function, characterized in that: include: A silencer module (100), wherein a first end of the silencer module (100) is coaxially connected to the axial flow fan (300); A vibration reduction module (200), wherein a first end of the vibration reduction module (200) is coaxially connected to a second end of the muffler module (100), and a second end of the vibration reduction module (200) is coaxially connected to a fan mount (400); the vibration reduction module (200) comprises: A flexible air guide cover (210), wherein a first end of the flexible air guide cover (210) is connected to a second end of the muffler module (100) via a first connecting flange (220), and a second end of the flexible air guide cover (210) is connected to the fan mount (400) via a second connecting flange (230); the flexible air guide cover (210) is connected to the inner cavity of the muffler module (100) and the inner cavity of the fan mount (400) to form an air flow channel; A vibration damper array is installed between the first connecting flange (220) and the second connecting flange (230).

2. The axial flow fan muffler with vibration reduction function according to claim 1, characterized in that: The vibration absorber array comprises at least four nonlinear damping vibration absorbers (240), and the four nonlinear damping vibration absorbers (240) are evenly distributed around the circumference of the flexible fairing (210); the axial stiffness of each nonlinear damping vibration absorber (240) is and the radial stiffness of each of the nonlinear damping shock absorbers (240) The stiffness matching relationship satisfies .

3. The axial flow fan silencer with vibration reduction function according to claim 2, characterized in that: The distance L between the first connecting flange (220) and the second connecting flange (230) is 1.2H-1.5H, wherein H is the free height of the nonlinear damping vibration isolator (240).

4. The axial flow fan silencer with vibration reduction function according to claim 2, characterized in that: The vibration reduction module (200) further includes: an annular bellows, the annular bellows being connected between the first connecting flange (220) and the second connecting flange (230); a preset axial compression amount of the annular bellows δ=0.3Δ-0.5Δ, wherein Δ is the compression amount of the nonlinear damping shock absorber (240); a limiting ring, the limiting ring being supported and mounted on the first connecting flange (220) or the second connecting flange (230) via a mounting bracket; When the actual axial compression amount of the annular bellows exceeds the preset axial compression amount of the annular bellows, the annular bellows abuts against the limiting ring.

5. The axial flow fan silencer with vibration reduction function according to claim 1, characterized in that: The vibration reduction module (200) further includes: A non-combustible rubber gasket (250), the non-combustible rubber gasket (250) abutting between the first connecting flange (220) and the second end of the muffler module (100); and / or the non-combustible rubber gasket (250) abutting between the second connecting flange (230) and the fan mount (400).

6. The axial flow fan silencer with vibration reduction function according to claim 1, characterized in that: The flexible air guide cover (210) comprises, from the inside of the air flow channel to the outside of the air flow channel, a high-temperature resistant canvas layer, a sound-absorbing cotton layer, and a metal wire mesh reinforcement layer.

7. The axial flow fan silencer with vibration reduction function according to claim 1, characterized in that: The muffler module (100) comprises, from the inside of the airflow channel to the outside of the airflow channel, an expansion chamber muffler section (110), a resonance sound absorption section (120), and a micro-perforated plate muffler section (130); The resonant sound absorbing section (120) is provided with a tunable Helmholtz resonance cavity, and the resonant frequency of the tunable Helmholtz resonance cavity is: ； Where c is the speed of sound, S is the equivalent area of ​​the radial annular opening of the tunable Helmholtz resonator, V is the volume of the annular cavity of the tunable Helmholtz resonator, L is the radial length of the neck of the tunable Helmholtz resonator, is the neck correction length of the tunable Helmholtz resonator, generally =0.8r-0.85r, r is the average radius of the tunable Helmholtz resonant cavity.

8. The axial flow fan silencer with vibration reduction function according to claim 1, characterized in that: Also includes: An acoustic vibration decoupling ring is coaxially mounted between the first end of the vibration reduction module (200) and the second end of the muffler module (100); the acoustic vibration decoupling ring comprises a hard spacer ring and an elastic gasket ring alternately arranged along the circumference; wherein the thickness t of the hard spacer ring and the thickness T of the elastic gasket satisfy t / T=1 / 3-1 / 2.

9. The axial flow fan silencer with vibration reduction function according to claim 1, characterized in that: Also includes: A mass tuning block (410) is mounted on the fan mount (400); the mass m of the mass tuning block (410) and the mass M of the impeller (310) in the axial flow fan (300) satisfy m=0.1M-0.2M, and the eccentricity e between the center of mass of the mass tuning block (410) and the axis of the axial flow fan (300) is ≤0.05D, where D is the cylinder diameter of the axial flow fan (300).

10. A ship, characterized in that: The utility model comprises an axial flow fan silencer with a vibration reduction function as claimed in any one of claims 1 to 9.

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