CN111503410A - Helmholtz type silencer - Google Patents
Helmholtz type silencer Download PDFInfo
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- CN111503410A CN111503410A CN202010248113.9A CN202010248113A CN111503410A CN 111503410 A CN111503410 A CN 111503410A CN 202010248113 A CN202010248113 A CN 202010248113A CN 111503410 A CN111503410 A CN 111503410A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/02—Energy absorbers; Noise absorbers
- F16L55/033—Noise absorbers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00507—Details, e.g. mounting arrangements, desaeration devices
- B60H1/00557—Details of ducts or cables
- B60H1/00564—Details of ducts or cables of air ducts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
- B61D27/00—Heating, cooling, ventilating, or air-conditioning
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/02—Energy absorbers; Noise absorbers
- F16L55/033—Noise absorbers
- F16L55/0333—Noise absorbers by means of an active system
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00507—Details, e.g. mounting arrangements, desaeration devices
- B60H2001/006—Noise reduction
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Exhaust Silencers (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
Abstract
The present disclosure discloses a helmholtz type muffler, including: the device comprises a plurality of resonant chambers arranged in an array mode and an interpolation neck arranged in each resonant chamber, wherein each resonant chamber is in the same horizontal position, and a partition is arranged between each resonant chamber; the height of each resonant cavity is arranged in an increasing or decreasing manner; the length of each interpolation neck is arranged along the height of the resonance chamber in an increasing or decreasing way; each inserted neck is provided with an air inlet and an air outlet, the air inlet and the bottom end of the resonance cavity are horizontally arranged, and the air outlet and the top end of the resonance cavity keep a proper distance. According to the acoustic attenuation device, the resonant cavities with different heights and the interpolation necks with different lengths are arranged, and the acoustic attenuation target with a certain width frequency band in a medium-low frequency range can be realized by utilizing the resonance sound absorption effect of the resonant cavities.
Description
Technical Field
The disclosure belongs to the field of mechanical noise and environmental noise control, and particularly relates to a Helmholtz type silencer.
Background
In daily production and life, various mechanical equipment noises, traffic noises and the like are enriched, the noises seriously affect the activities of people, and the noises not only can damage the hearing, but also can cause diseases of various systems of the human body; therefore, noise is also known as "a chronic poison causing death. Especially, due to the characteristics of low frequency and long wavelength, the medium and low frequency noise is slowly attenuated in the air and has strong penetration capability, and the control of the medium and low frequency noise is a difficult challenge. However, the above-mentioned method cannot be applied to a pipe having a gas or liquid flowing therein, and a number of obstacles are formed around the pipe, which limits the size of the muffler. For the train air supply pipeline, because the train air supply pipeline is positioned at the top of a train, the space is very narrow, the noise has larger energy in a wider frequency band, and the existing silencers are limited by the volume of the pipeline and have the defects of larger volume, single sound insulation peak, narrower frequency band and the like.
Considering the specific engineering application background, such as the air-conditioning ventilation duct of a train or a heavy truck, the wheel track noise and the structural noise generated by an air-conditioning compressor are transmitted into a cabin through an air supply duct, and the riding comfort of passengers is influenced, due to the practical situation of the ventilation duct, the silencer suitable for the ventilation duct needs to meet three requirements that ① attenuates the noise in a wide frequency band with medium and low frequency (600 + 900Hz) and meets T L ≥ 5-6dB, ② cannot obstruct the flow of air flow, and avoids causing large pressure loss, ③ avoids occupying large space and changing the original pipeline structure as far as possible, therefore, the application research of the design of the silencer is guided by the method, and the following problems exist in the research of the existing pipeline silencer:
1) most pipeline silencers belong to external inserted neck structure, and the resonant frequency is related to neck length, neck area and cavity volume, and in order to satisfy the requirement of low frequency resonance, the cavity volume of helmholtz resonant cavity is designed to be bigger, the neck is longer, which causes the cavity to be unusable in some narrow places, and has bigger limitation in practical engineering application. In addition, it can have strong sound attenuation capability only at the resonance frequency point, but its sound attenuation band is relatively narrow;
2) some mufflers have too complex structures and need to be precisely processed to ensure the accuracy of the resonant frequency, so that the manufacturing process of sample pieces is complex and time-consuming, and is not beneficial to practical engineering application;
3) many mufflers are designed with a structure inside the pipe to block the flow of air, resulting in a certain pressure loss.
Disclosure of Invention
To the deficiencies in the prior art, it is an object of the present disclosure to provide a helmholtz-type muffler that can eliminate noise in different frequency bands by moving the acoustic attenuation region at different frequencies and adjusting the size and material parameters.
In order to achieve the above purpose, the present disclosure provides the following technical solutions:
a helmholtz-type muffler comprising: a plurality of resonant chambers arranged in an array and an interposer neck disposed within each resonant chamber, wherein,
each resonant cavity is in the same horizontal position, and a partition is arranged between each resonant cavity;
the height of each resonant cavity is arranged in an increasing or decreasing manner;
the length of each interpolation neck is arranged along the height of the resonance chamber in an increasing or decreasing way;
each inserted neck is provided with an air inlet and an air outlet, the air inlet and the bottom end of the resonance cavity are horizontally arranged, and the air outlet and the top end of the resonance cavity keep a proper distance.
Preferably, the resonance chamber is bonded to or integrally formed with the inner hosel.
Preferably, the height of the resonance chamber is 15mm-20 mm.
Preferably, the length of the interpolation neck part is 3mm-9.5 mm.
Preferably, the end surface of the inner insertion neck portion has a rectangular or diverging tubular shape.
Preferably, the insert neck is located in the middle or on both sides of the resonance chamber.
Preferably, a porous medium is arranged at the upper part of the resonance chamber.
Preferably, the sound attenuation performance of the muffler is evaluated by the transmission loss ST L, specifically by the following formula:
wherein the content of the first and second substances,
in order for the acoustic energy to be incident,
for transmission of acoustic energy, PiIs incident sound pressure, PtFor transmission of sound pressure, p0Is the density of the gas in the pipeline, c0Is the velocity of sound of the gas in the pipe.
Preferably, the resonant frequency of the resonant chamber is:
wherein M isbFor acoustic mass in tubes, CbIs the volume of the cavity, and l is the length of the neck0+1.2a)，SbIs the cross-sectional area of the neck, VbIs the volume of the acoustic cavity and pi is the circumferential ratio.
Compared with the prior art, the beneficial effect that this disclosure brought does:
1. a wider sound attenuation area can appear in the middle frequency range of 550-1000Hz, and the frequency bandwidth of T L which is more than or equal to 10dB reaches 430Hz, so that the effect of broadband high sound attenuation is realized;
2. the structure is improved by changing the shape of the end face of the interpolation neck, changing the position of the interpolation neck, adding a porous medium and the like, so that a plurality of wider attenuation frequency bands can appear in a frequency range lower than 1000Hz, and the adjustability of the sound absorption characteristic of the structure and the sound attenuation target of the wider frequency bands are realized;
3. the sound absorption characteristics of the unit structure and the improved unit structure designed by the disclosure and the length and height of the structure cavity, the width and length of the inserted neck part, the number and size of the mass blocks all have certain change rules, so that the structural dimension can be determined and the structure can be improved according to the sound insulation target purposefully and instructively.
Drawings
FIG. 1 is a schematic view of a Helmholtz type muffler according to one embodiment of the present disclosure;
FIG. 2 is another Helmholtz type muffler provided in accordance with an embodiment of the present disclosure;
FIG. 3 is another Helmholtz type muffler provided in accordance with an embodiment of the present disclosure;
FIG. 4 is a helmholtz type muffler provided in accordance with another embodiment of the present disclosure;
FIG. 5 is a schematic view of a simulation model of a finite element analysis of the composite panel of FIG. 1;
FIG. 6 is a schematic structural dimension view of the basic unit of the interpolation neck array silencer in FIG. 1;
FIG. 7 is a graph of finite element simulated transmission loss for the muffler of FIG. 1;
FIG. 8 is a finite element simulated transmission coefficient, sound absorption coefficient and reflection coefficient plot for the muffler of FIG. 1;
FIG. 9 is a sound intensity flow diagram of the muffler of FIG. 1 at 600Hz, 780Hz, and 950Hz, respectively;
fig. 10 is a graph of finite element simulated transmission loss for the muffler shown in fig. 1-4.
Detailed Description
Specific embodiments of the present disclosure will be described in detail below with reference to fig. 1 to 10. While specific embodiments of the disclosure are shown in the drawings, it should be understood that the disclosure may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.
It should be noted that certain terms are used throughout the description and claims to refer to particular components. As one skilled in the art will appreciate, various names may be used to refer to a component. This specification and claims do not intend to distinguish between components that differ in name but not function. In the following description and in the claims, the terms "include" and "comprise" are used in an open-ended fashion, and thus should be interpreted to mean "include, but not limited to. The description which follows is a preferred embodiment of the invention, but is made for the purpose of illustrating the general principles of the invention and not for the purpose of limiting the scope of the invention. The scope of the present disclosure is to be determined by the terms of the appended claims.
To facilitate an understanding of the embodiments of the present disclosure, the following detailed description is to be considered in conjunction with the accompanying drawings, and the drawings are not to be construed as limiting the embodiments of the present disclosure.
In one embodiment, as shown in fig. 1, the present disclosure provides a helmholtz-type muffler comprising: each resonant cavity is in the same horizontal position, and a partition is arranged between each resonant cavity;
the height of each resonant cavity is arranged in an increasing or decreasing manner;
the length of each interpolation neck is arranged along the height of the resonance chamber in an increasing or decreasing way;
each inserted neck is provided with an air inlet and an air outlet, the air inlet and the bottom end of the resonance cavity are horizontally arranged, and the air outlet and the top end of the resonance cavity keep a proper distance.
The embodiment provides a novel silencer structure, which is different from the existing common pipeline silencer in that the silencer provided by the embodiment can utilize the resonance sound absorption function of a resonance cavity under the excitation of sound waves, so that a wider action frequency band (the frequency band of T L is more than or equal to 10dB and more than 400Hz) is formed in the 568 and 992Hz frequency band, and the sound attenuation target of a certain width frequency band in a medium-low frequency range can be easily realized.
In another embodiment, the resonance chamber is bonded to or integrally formed with the inner hosel.
In this embodiment, the resonant cavity and the inner insertion neck portion may be adhered by glue, or may be processed by a numerically controlled milling machine or integrally printed, and since the height of the resonant cavity, the length of the inner insertion neck portion, the cross-sectional dimension of the inner insertion neck portion, and the position of the inner insertion neck portion have a certain influence on the acoustic attenuation and the frequency of action thereof, in order to ensure the manufacturing accuracy, the entire structure is preferably integrally printed and processed by using a mature 3D printing technology (with an error of plus or minus 0.1 mm).
In another embodiment, the height of the resonance chamber is 15mm-20 mm.
Since the resonant frequency of the silencer is different between different cavity heights and the length of the inserted neck, the value of T L is the largest at the resonant frequency, and in order to realize a larger value of T L in a wider frequency band, the resonant frequency of the silencer must be slightly changed by means of a certain number of structures in the pipe wall array so as to couple the peaks, in a specific embodiment of the present embodiment, 10 resonant cavities are arranged from left to right in the height order of 15mm, 16mm, 17mm, 18mm, 19mm, and 20mm, wherein the resonant cavity with the height of 20mm corresponds to the resonant frequency of 552HZ, and the resonant cavity with the height of 15mm corresponds to the resonant frequency of 942 HZ.
It should be noted that the number of the resonant chambers may be set to be greater than 10, and the operating frequency band can be made wider and the amount of noise elimination can be made larger to some extent, but the increased number may result in occupying a larger space, which is contrary to the scenario (i.e. narrow space) to which the present disclosure is applicable, and in addition, the number of the resonant chambers is set to be 10, which may actually meet the engineering requirement, and therefore, in view of the practical use effect, the number of the resonant chambers in this embodiment is preferably 10.
It should be noted that the resonant frequency of the muffler is determined by the volume of the resonant cavity and the length and cross-sectional area of the interpolation neck, and in order to ensure wide-frequency sound absorption in the range of 550-.
In addition, it should be noted that the shape of the resonant cavity may be square, rectangular, or cut into a geometric regular shape such as a circle, a regular hexagon, etc. according to the actual application.
In another embodiment, the length of the interpolation neck is 3mm-9.5 mm.
In this embodiment, the length of the insertion neck corresponds to the height of the resonance chamber one by one, and is set to be 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, and 9.5mm, respectively, that is, the length of the insertion neck in the resonance chamber with the height of 15mm is 3mm, and the length of the insertion neck in the resonance chamber with the height of 20mm is 9.5 mm.
It will be appreciated that the resonant frequency of each cell is determined by the volume of the resonant chamber and the length and cross-sectional area of the interpolation neck, and in order to ensure broad frequency sound absorption in the range of 500-1000Hz, the resonant frequency of each cell is dispersed within this range, and therefore the length of the interpolation neck is set to be in the range of 3mm-9.5mm, and if this is exceeded, it cannot be ensured that the resonant frequency falls within the range of 500-1000 Hz.
In combination with the former embodiment, the present disclosure needs to determine the target frequency, then determine the working principle of the muffler, then determine the size of the resonant cavity and the size of the inserted neck, and if the target frequency changes, the size range will also change under the premise that the action principle is not changed.
The present disclosure provides an improvement over the above-described embodiment, as shown in fig. 2, in one embodiment, the end surface shape of the interpolation neck is changed from the existing rectangular shape to a diverging tubular shape.
In this embodiment, when the end surface shape of the interpolation neck portion is changed from the conventional rectangular shape to the diverging tube shape, the frequency band having the T L curve of more than 10dB is widened by approximately 30Hz at high frequencies (see the curve shown by the chain line in fig. 10) as compared with the case where the end surface shape of the interpolation neck portion is rectangular (the solid line in fig. 10 indicates the T L curve without any modification).
It should be noted that the lower the frequency of the sound, the longer the wavelength thereof, and the more difficult it is to control, and this embodiment is more advantageous for the effect of sound attenuation by changing the end surface shape of the interpolation neck portion so that the T L curve moves to a certain extent at a low frequency.
The present disclosure provides yet another improvement, as shown in fig. 3, in one embodiment, the position of the interpolation neck is changed from the middle of the resonance chamber to be arranged near the side end of the resonance chamber.
In this embodiment, after the position of the interpolation neck is changed from the middle of the resonance chamber to be disposed near the left or right side of the resonance chamber, the frequency band having the T L curve greater than 10dB is shifted to a lower frequency direction (see the curve indicated by the dashed line in fig. 10) compared with the case where the interpolation neck is disposed at the middle of the resonance chamber (the solid line in fig. 10 indicates the T L curve without any modification).
By adjusting the position of the interpolation neck in the resonance chamber, the technical effects consistent with the above embodiments can be achieved, and are not described herein.
The present disclosure provides yet another improvement, as shown in fig. 4, in one embodiment, a porous medium is disposed at an upper portion of the resonance chamber.
In this embodiment, after disposing the porous medium in the upper portion of the resonant cavity, the initial frequency of the T L curve greater than 10dB is shifted to a lower frequency direction (see the curve shown by the long dashed line in fig. 10) compared to the case where the porous medium is not disposed (the solid line in fig. 10 indicates the T L curve without any modification).
Next, a finite element simulation model of the muffler is established by using an acoustic-solid coupling frequency domain analysis module of large commercial finite element software COMSO L Multiphysics 5.4, and the sound absorption characteristics of the pipe muffler of the present disclosure are analyzed.
As shown in fig. 5, the finite element simulation model is composed of two parts, namely an incident sound cavity 11 and a pipeline silencer unit structure 13. When plane sound wave is incident from plane wave radiation surface 10, passes through pipe internal air 11 and pipe silencer, and exits from plane wave radiation surface 12, the internal air region contains incident sound pressure PiReflected sound pressure PrAnd transmission sound pressure PtAccordingly, the transmission loss ST L of the muffler can be calculated from this, as shown in the following equation.
Wherein the content of the first and second substances,
in order for the acoustic energy to be incident,
for transmission of acoustic energy, p0Is the density of the gas in the pipeline, c0Is the velocity of sound of the gas in the pipe.
The incident sound pressure is defined to be 1Pa, the frequency scanning frequency band is 100Hz-1200Hz, and the step length is 10 Hz. The finite element simulation results in a transmission loss curve for the muffler as shown in fig. 7. With 10dB as a standard, it can be found from fig. 7 that an acoustic absorption band with 568 and 992Hz and a bandwidth of 430Hz, wherein at 735 and 850Hz, there is also a peak band of acoustic attenuation, and the transmission loss reaches more than 20 dB. As can be seen from fig. 8, the sound absorption coefficient of the muffler is high (close to 0.9) in the active band, and in order to further reveal the sound absorption mechanism behind the muffler, the sound energy flow graphs of the muffler at the start frequency of the transmission loss curve of 600Hz, the end frequency of 920Hz and the peak point of 780Hz are calculated respectively, as shown in fig. 9. As is apparent from fig. 9, at 600Hz, the acoustic flow flows to the right chamber of the structure, and the right unit structure with the largest volume is in resonance, and the acoustic energy is converted into heat energy and consumed; at 780Hz, sound waves enter a cavity in the middle of the silencer array unit, and at the moment, the sound waves resonate with the middle cavity, so that the consumption capacity of sound wave energy reaches the maximum; at 950Hz, the sound wave enters the left chamber with smaller volume, the left unit structure is in resonance state, the sound energy is converted into heat energy in the chamber and consumed, and the unit structure is in resonance state. As can be seen from fig. 9, in the higher transmission loss frequency band (568Hz-992Hz), the reason for the acoustic attenuation is that the different sizes of chambers are at the resonance frequency, and the acoustic wave enters the chamber in the frequency band, so that the acoustic energy is converted into viscous heat energy in the chamber and is further consumed, and the higher transmission loss occurs.
It should be understood that, by theoretical calculation, the resonant frequencies of resonant chambers of different sizes can be obtained as shown in the following formula:
wherein M isbFor acoustic mass in tubes, CbIs the volume of the cavity, and l is the length of the neck0+1.2a)，SbIs the cross-sectional area of the neck, VbIs the volume of the acoustic cavity, pi is the circumferential ratio, p0Is the density of the gas in the pipeline, c0Is the velocity of sound of the gas in the pipe.
For a certain cavity in the middle of the structure, the relevant dimension is substituted, and the length l of the interpolation neck is 6mm, which can be calculated by the following formula:
the resonant frequency is 759Hz, and the resonant cavity at the center is in the resonant state, the transmission loss is maximum, and is in the frequency range of 850Hz and 735 < the peak frequency of the transmission loss curve in FIG. 7.
While the embodiments of the disclosure have been described above in connection with the drawings, the disclosure is not limited to the specific embodiments and applications described above, which are intended to be illustrative, instructive, and not restrictive. Those skilled in the art, having the benefit of this disclosure, may effect numerous modifications thereto and changes may be made without departing from the scope of the disclosure as set forth in the claims that follow.
Claims (9)
1. A helmholtz-type muffler comprising: a plurality of resonant chambers arranged in an array and an interposer neck disposed within each resonant chamber, wherein,
each resonant cavity is in the same horizontal position, and a partition is arranged between each resonant cavity;
the height of each resonant cavity is arranged in an increasing or decreasing manner;
the length of each interpolation neck is arranged along the height of the resonance chamber in an increasing or decreasing way;
each inserted neck is provided with an air inlet and an air outlet, the air inlet and the bottom end of the resonance cavity are horizontally arranged, and the air outlet and the top end of the resonance cavity keep a proper distance.
2. The muffler of claim 1 wherein said resonant cavity is preferably bonded or integrally formed with said inner hosel.
3. The muffler of claim 1 wherein the height of said resonant chamber is 15mm-20 mm.
4. The muffler of claim 1 wherein said inner plug neck portion has a length of 3mm-9.5 mm.
5. The muffler of claim 4 wherein the end surface of the inner plug neck is rectangular or diverging tubular in shape.
6. The muffler of any one of claims 1 to 5 wherein the insert neck is located in the middle or on both sides of the resonant chamber.
7. The muffler according to claim 1, wherein a porous medium is provided on an upper portion of the resonance chamber.
8. The muffler of claim 1, wherein the sound attenuation performance of the muffler is evaluated by transmission loss ST L, specifically by the following equation:
wherein the content of the first and second substances,
in order for the acoustic energy to be incident,
for transmission of acoustic energy, PiIs incident sound pressure, PtFor transmission of sound pressure, p0Is the density of the gas in the pipeline, c0Is the velocity of sound of the gas in the pipe.
9. The muffler of claim 1 wherein the resonant cavity has a resonant frequency of:
wherein M isbFor acoustic mass in tubes, CbIs the volume of the cavity, and l is the length of the neck0+1.2a)，SbIs the cross-sectional area of the neck, VbIs the volume of the acoustic cavity and pi is the circumferential ratio.
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| CN202010248113.9A CN111503410A (en) | 2020-04-01 | 2020-04-01 | Helmholtz type silencer |
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| CN202010248113.9A CN111503410A (en) | 2020-04-01 | 2020-04-01 | Helmholtz type silencer |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112648724A (en) * | 2020-12-28 | 2021-04-13 | 江苏科技大学 | Condensate water recovery device of wall-mounted air conditioner indoor unit |
| CN115076129A (en) * | 2022-06-23 | 2022-09-20 | 西安交通大学 | Centrifuge diffuser with self-adaptive noise reduction function |
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