JP2002082012A - Silencing facility - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a silencing facility having an improved sound reduction effect as a whole, by preventing airflow from degrading the sound reduction effect in a resonant chamber. SOLUTION: This silencing facility comprises a passage 4 for jet airflow partitioned with a partition 3 from the outside, the resonant chamber 6 having an opening 7 disposed outside the partition 3 for communicating with the passage 4, and a windbreak 8 that is spaced from the partition 3 by a clearance with the same dimension as at least a substantial radius of the opening 7 and formed of a porous plate with 20% or more of porosity disposed along the partition. The windbreak 8 allows transmission of sound wave and suppresses pass of the airflow.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to a silencer.
More specifically, the present invention relates to a silencer for reducing noise caused by gas ejection by sound absorption and resonance.

[0002]

2. Description of the Related Art Conventionally, there are facilities for generating noise in a wide frequency band in various fields. For example, a wind tunnel experiment facility for performing a wind tunnel experiment using a model subject.

FIG. 9 shows an example of a wind tunnel experimental facility. The wind tunnel experimental equipment 51 is provided with a spherical pressure storage tank 52 for storing compressed air. High-pressure air from the accumulator tank 52 is guided to the variable nozzle 54 as a high-speed airflow from the collecting cylinder 53 through the pressure regulating valve 53a. Variable nozzle 5
A measuring unit 55 on which a subject is set is disposed at the discharge port 4. Then, the high-speed airflow is guided from the measuring section 55 through the diffuser 56, which is an enlarged diameter passage, into the silencer 57, and is discharged.

In research and development that requires wind tunnel experiments for aircraft and the like, a high Reynolds number test that can simulate a phenomenon closer to that of an actual machine is required. Then, it is necessary to increase the pressure of the test airflow and increase the size of the equipment. Also, it is known that noise generated in a blow-out type wind tunnel generally has a substantially flat sound output characteristic from an extremely low frequency range of about several hertz to an entire audible range. Therefore, in a wind tunnel that achieves a high Reynolds number test under conditions close to actual equipment, large flow rate, large pressure ratio, and large diameter are required, so that noise cannot avoid the increase in sound output in all frequency bands and lower frequency. .

[0005] Therefore, the noise reduction equipment provided in the wind tunnel experimental equipment is also increased in size, the resonance type noise reduction for eliminating low frequency noise, and the sound absorption for eliminating higher frequency noise, that is, noise in the audible range. It is used in combination with silence.

FIG. 10 shows TECHNIC issued in 1955 by the National Aviation Advisory Committee (NACA) at the time of the United States.
This is a noise reduction facility disclosed in AL NOTE 3378. A plurality of resonance chambers 63a are provided around the diffuser 62 along the diffuser 62, and a plurality of resonance chambers 63b are provided downstream of the diffuser 62 along the flow path 64. A splitter 65 serving as a sound absorbing means is provided further downstream of the flow path 64. Note that the reference numeral 66 in the figure indicates the flow path 6
4 is an opening communicating with the resonance chambers 63a and 63b.

The resonance chambers 63a and 63b are for reducing sound by resonance. Specifically, the general idea is that sound waves whose phases are shifted by resonance in the resonance chamber interfere with each other to reduce sound.

[0008]

In the above silencer, the resonance chambers 63a and 63b exhibit a certain amount of sound reduction effect. However, it is generally said that the degree of sound reduction is degraded by the airflow flowing through the passage.

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above-mentioned problem, and it is an object of the present invention to provide a noise reduction system which effectively prevents deterioration of sound reduction of a resonance chamber due to an air flow, and has an improved sound reduction effect as a whole. It is an object.

[0010]

According to the present invention, there is provided a muffler comprising a passage for ejecting airflow defined by a partition wall from the outside, and an opening provided outside the partition wall for communicating with the passage. And a windshield provided at a distance from the partition wall and arranged along the partition wall, and the windshield plate allows transmission of sound waves and suppresses passage of airflow. Is configured.

The resonance chamber is an image chamber having a volume, and the resonance chamber is provided with the opening to form a resonance type silencer. Then, the noise in the passage is reduced by the resonance phenomenon of the resonance type silencer.

Further, since the windbreak plate is provided, there is almost no influence of the airflow between the windbreak plate and the partition plate. Therefore, the kinetic energy (so-called acoustic energy) accompanying the vibration due to the resonance of the resonance chamber is not lost by the airflow. As a result, deterioration of the sound reduction effect of the resonance chamber due to the air flow is prevented.

The distance between the partition wall and the windbreak plate is
By setting the diameter to be equal to or greater than the substantial radius of the opening, it is possible to prevent the sound reduction effect from being deteriorated and to minimize the reduction in the substantial cross-sectional area of the airflow passage.

Further, the windbreak plate is constituted by a perforated plate having a large number of holes, and the aperture ratio of the windbreak plate by the holes is 2%.
By configuring so as to be 0% or more, it is possible to effectively introduce low-frequency sound waves to be reduced by the resonance chamber into the resonance chamber.

Further, by disposing a silencer in the opening, it is possible to effectively suppress the audible sound wave from entering the resonance chamber.

[0016]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a muffler according to an embodiment of the present invention.

FIG. 1 is a side sectional view showing an embodiment of the sound deadening equipment of the present invention. FIG. 2 is a plan sectional view of a first-floor portion, which is a sectional view taken along line II-II of FIG.

1 and 2 is a diffuser 2 that blows out a high-speed airflow from a wind tunnel experimental facility (not shown).
It is located downstream of. The outlet end of the diffuser 2 is inserted into the silencer. The flow path for the air flow ejected from the diffuser 2 is constituted by a passage 4 defined from the outside by a partition wall 3. A splitter 5 for absorbing noise is provided in the passage 4 along the flow direction of the air flow.

As shown in FIGS. 1 and 2, a plurality of resonance chambers 6 are arranged on both sides (see FIG. 2) and above (see FIG. 1) of the passage 4. Each resonance chamber 6 is separated from the passage 4 by a partition wall 3, and the partition wall 3 is provided with a plurality of openings 7 that communicate the resonance chamber 6 and the passage 4.
The resonance chamber 6 and the opening 7 constitute a resonance type silencer. The wind tunnel noise emitted from the diffuser 2 is attenuated by each resonance type silencer as it travels in the passage.

Of course, a resonance type silencer may be provided below the passage 4, that is, below the floor.

Each of the plurality of resonance chambers 6 has a different volume. This is because the resonance frequency is changed to cope with low-frequency noise in a wide frequency band.

As is clear from FIG. 3 as well,
A windbreak plate 8 is provided along the entire surface of the partition wall 3 forming the passage 4 on the passage side. As shown in FIG. 3, the windbreak plate 8 is disposed at a position slightly apart from the surface of the partition wall 3 and substantially parallel to the wall surface. The opening 7 of the partition 3
Is also separated from the passage 4 by a windbreak plate 8.

However, since the windshield 8 has a sound wave transmitting property, low frequency noise passes through the windshield 8 and passes through the opening 7 through the resonance chamber 6.
To enter. This is because the windbreak plate 8 is formed of a perforated plate such as a punching metal or a grating metal. Therefore, no special sound absorbing function is given to the windproof plate 8. However, the airflow flowing through the passage 4 does not affect the partition wall side by the windbreak plate 8. That is, almost no airflow enters the space between the windbreak plate 8 and the partition wall 3. Of course, it does not matter whether or not the windproof plate has a sound absorbing function, as long as it has a function of preventing airflow from flowing to the partition wall side.

With this configuration, the loss of the air vibration energy in the resonance chamber 6 is prevented, and as a result, the sound reduction effect of the resonance chamber is prevented from deteriorating. The reason is as follows.

FIG. 4 shows a model of the resonance chamber. Resonance caused by sound waves propagating on the passage side in the resonance chamber 6 is caused by vibration of air in the opening 7. It is as if the air in the resonance chamber 6 is a spring that compresses and expands, and the air in the opening 7 is the mass point. The mass m of the air in the portion of the opening 7 that vibrates at the time of resonance is represented by the following equation, where ρ is the density of the air, A is the area of the opening 7, and L is the length of the opening 7 (thickness of the partition wall). Is obtained.

M = ρ × A × L + dm.

Here, dm is an additional mass due to the piston movement of the air in the opening 7 due to the vibration. This portion is generally considered to be a hemispherical portion having a radius equal to the equivalent radius R of the cross section of the opening 7.

Assuming that the airflow flows on the passage side of the partition wall 3 without installing the windbreak plate 8, the portion indicated by hatching in FIG. 4A is caused to flow by the airflow, and the vibration energy is lost. Will suffer. As a result, the energy for sound reduction due to the phase shift with the sound wave propagating on the passage side is reduced, and the sound reduction effect is also reduced. This is the deterioration of the sound reduction effect due to the airflow described above.

However, as described above, the airflow flowing along the partition plate 3 hardly enters the space between the partition wall 3 and the partition wall 3 due to the installation of the windbreak plate 8. Therefore, there is no movement of the additional mass (see FIG. 4B), and the vibration energy does not suffer any loss. That is, deterioration of the sound reduction effect is prevented.

The distance D between the partition wall 3 and the windbreak plate 8 (see FIG. 4B) must be at least equal to the radius R of the opening 7 or more. This is to prevent the influence of the air flow on the additional mass dm. However, if the distance is too large, the cross-sectional area of the airflow passage 4 is reduced.

FIGS. 5 to 7 show the results of experiments on the silencer with the wind shield 8 installed and without the silencer.
In this experiment, the conditions were similarly reduced using a 1/30 reduced model of the actual product. Therefore, FIG.
The peak of the sound reduction in FIG. 7 is at a frequency of about 100 Hz, which corresponds to about 3.3 Hz in actual equipment.

FIG. 5 shows the case where the airflow speed (wind speed) is 10 m / s, FIG. 6 shows the case where the wind speed is 20 m / s, and FIG.
In each of the figures, the case where the windbreak plate 8 is installed is indicated by a circle, and the case where the windbreak plate 8 is not installed is indicated by the cross.

As described above, when the windbreak plate is not installed, an air current is generated as compared with the case where the windbreak plate is installed, and a decrease in sound volume reduction is conspicuous as the speed of the airflow increases.

In order to exert the above-mentioned effects, the windbreak plate 8
Any structure may be used as long as it prevents generation of an airflow flowing along the partition wall 3 in the space between the partition wall 3 and allows low-frequency transmission from the airflow toward the opening 7 of the partition wall 3. For this purpose, a large number of holes are formed in the windshield 8, and the aperture ratio of the windshield 8 due to the large number of holes may be 20% or more. An example is a perforated plate such as a punching metal or a grating metal. Of course, other known devices may be used.

As shown in FIG. 8, another silencer 9 is provided on the side of the resonance chamber 6 of each opening 7. This silencer 9 has a flow path cross section substantially matching the shape of the opening 7. By disposing the silencer 9, in addition to the function of the windproof plate 8 on the wall surface, sound waves in the audible range that enter the resonance chamber 6 are further reduced. As a result, the noise level in the audible range in the resonance chamber is reduced, the transmission loss of the partition wall to the outside of the resonance chamber can be reduced, and the partition wall to the outside can be made thin.

It has been proved by a model experiment that the arrangement of the windbreak plate 8 does not affect the function of the resonance type silencer.

As shown in FIG. 8, the silencer 9 at the opening 7 is provided.
Is attached to the surface of the partition wall 3 on the resonance chamber 6 side in the opening 7. By doing so, the function of the resonance type silencer is not affected as compared with the case where the silencer 9 is attached in a form inserted into the opening.

[0038]

According to the present invention, a simple configuration prevents deterioration of the noise reduction effect of the resonance chamber due to airflow, and improves the noise reduction effect of the entire noise reduction system.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing an embodiment of a sound deadening device of the present invention.

FIG. 2 is a plan sectional view showing a section taken along line II-II of FIG. 1;

FIG. 3A is an enlarged view of a main part of FIG. 2;

4A and 4B are cross-sectional views of a main part of a resonance chamber for explaining deterioration of a sound reduction effect. FIG. 4A shows a comparative example in which no windshield is installed, and FIG. An example is shown.

FIG. 5 is a graph showing experimental results of the example of FIG. 4 and a comparative example.

FIG. 6 is a graph showing experimental results of the example of FIG. 4 and a comparative example.

FIG. 7 is a graph showing experimental results of the example of FIG. 4 and a comparative example.

FIG. 8 is a cross-sectional view of a main part showing an opening of a partition wall in another embodiment of the sound deadening equipment of the present invention.

FIG. 9 is a schematic diagram illustrating an example of a wind tunnel experimental facility in which a noise reduction facility is provided.

FIG. 10 is a cross-sectional plan view showing an example of a conventional silencer.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Silencer 2 ... Diffuser 3 ... Partition wall 4 ... Passage 5 ... Splitter 6 ... Resonance chamber 7 ... Opening 8 ... Windbreak board 9: silencer

Claims (4)

[Claims] An airflow passage defined by a partition wall from the outside, a resonance chamber disposed outside the partition wall and having an opening for communicating with the passage, and a space spaced from the partition wall. And a windbreak plate disposed along the partition wall, wherein the windbreak plate is configured to allow transmission of sound waves and suppress passage of an air flow. 2. The silencer according to claim 1, wherein a distance between the partition wall and the windbreak plate is set to be equal to or larger than a substantial radius of the opening. 3. The sound deadening equipment according to claim 1, wherein the windproof plate is constituted by a perforated plate having a large number of holes formed therein, and the aperture ratio of the windproof plate by the holes is set to 20% or more. 4. The muffler according to claim 1, wherein a muffler is provided in the opening.