JPH10266388A - Damping sound insulating panel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To form a damping sound insulating panel having high damping sound insulating property with lightweight by fluidally sealing inorganic powder in a hollow panel inside space, and converting vibration energy of powder particles into thermal energy. SOLUTION: A partition plate 11 composed of aluminum honeycomb material exists between aluminum surface materials 10, 10 to form a hollow panel, and powder 2 is fluidally sealed in the hollow part to form a damping sound insulating panel. The powder 2 preferably has an inside space or minute holes, made an inorganic system such as glass beads, a silica balloon, vermiculite and perlite, an acrylic sphere can be also used, a particle diameter is made 30-1000 μm, exciting acceleration is in the neighborhood of 1G, and a fluidal phenomenon produced in the powder 2 is effectively utilized to convert vibration energy of the particles of the powder 2 into thermal energy. Thus, when the damping sound insulating panel is used for floor material, wall material and ceiling material of a shinkansen vehicle, a noise level can be reduced in a wide frequency band.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration-damping and sound-insulating panel used for vibration suppression and sound-insulating, and more particularly to a vibration-damping and sound-insulating panel for use where vibration acceleration is large.

[0002]

2. Description of the Related Art For a vehicle running at high speed, there is a conflict between high speed and provision of a comfortable space. In order to enable high-speed driving, it is effective to reduce the weight of the vehicle, whereas lightening generally causes a decrease in rigidity, which tends to increase vibration noise. Combined with the increase, it becomes extremely difficult to provide a comfortable space. Such problems are most noticed in Shinkansen vehicles, which are scheduled to be operated at higher running speeds in the future. 300km
In order to be able to perform business operation at a speed exceeding / h, it is necessary to have extremely good vibration damping and sound insulating performance in order to provide a comfortable space in the vehicle compartment, as well as to reduce the weight.

[0003] By the way, in-vehicle noise of a Shinkansen vehicle is generated from various factors, and the rolling noise and electric equipment sound transmitted from under the floor to the room through the floor structure are greatly affected. 16 and 17 show a conventional example of this floor structure. FIG. 16 shows a structure in which a sound absorbing material 32 such as glass wool or rock wool is filled between a keystone plate 30 and a floor plate 31, and FIG. 17 shows an aluminum honeycomb formed between two surface materials 34, 34 made of an aluminum plate. The panel on which the material 35 is arranged is shown installed on the underframe 33. In addition, a resin or rubber damping sheet is attached to the panel surface, or a damping steel plate is used.

[0004]

However, those using the above sound absorbing material have an effect on sound absorption in a high frequency region.
No effect can be expected with respect to vibration or noise in a low frequency region, which is likely to be a problem in high-speed running vehicles. Further, although the panel provided with the honeycomb material can achieve both reduction in weight and maintenance of strength, there is a problem in terms of vibration suppression and sound insulation. Further, in the case of using a vibration damping sheet or the like, it is difficult to reduce the weight because the sound insulation effect cannot be increased unless the weight is extremely large.

The present invention has been made in view of the above points, and an object of the present invention is to provide a vibration-damping and sound-insulating panel which is lightweight and has high vibration-damping and sound-insulating performance.

[0006]

SUMMARY OF THE INVENTION A vibration-damping and sound-insulating panel according to the present invention is a hollow panel having two opposing surface members, and has an average particle size of 30 to 1000 .mu.m in an internal space.
Is stored. FIG.
Shows an example of this, in which the powder 2 having the above-mentioned particle size is stored in the internal space of the hollow panel 1 in which the surface materials 10 face each other at an interval.

When the hollow panel 1 is vibrated by sound or vibration, the powder 2 stored in the internal space moves due to the vibrating force. In this invention, vibration energy is converted into heat energy by a particle deformation at the time of collision or a friction or collision between two particles of the powder and the inner surface of the hollow panel 1 to exert a vibration damping and sound insulating effect. Vibration acceleration g is almost 1 G (9.8 m /
s ² ) The flow phenomenon that occurs in powder 2 when it is around (see Yoshihiro Taguchi: Journal of the Society of Powder Engineering, Vol. 30, 173 (1993).
Arakawa Masafumi, Nishino Misao: Materials, Volume 20, 776 (197
1)), it indicates that the movement of the pattern as shown by the arrow in FIG. 1 occurs in the powder 2 and the momentum of the powder 2 increases sharply. In order to effectively use this flow phenomenon, The powder 2 has a particle size of 30 to 1000 μm. In the case of the powder 2 having a particle diameter smaller than 30 μm, the adhesive force acting between the particles of the powder 2 becomes large and the powder 2 is agglomerated, so that the fluidity is impaired.
This is because if the powder 2 has a particle size larger than 0 μm, the mass of each particle is too large and the fluidity is significantly reduced.

The hollow panel 1 is provided with a partition plate 11 for dividing the internal space into a plurality of sections, and it is preferable that the powder 2 is stored in at least one section. This is because the fluidity of the powder when subjected to vibration is increased by the presence of the partition plate, and it is expected that the vibration suppression and sound insulation effect of the powder 2 can be expected regardless of the use posture of the hollow panel 1. it can. Note that the powder 2 need not be stored in all sections.

The powder 2 may be a hollow powder 2 having an internal space 20 as shown in FIG. 2A or a powder 2 having fine holes 21 as shown in FIG. 2B. preferable. Since the bulk density is generally smaller than that of the solid powder 2, it is advantageous in terms of weight reduction, and at the same time, since the powder 2 is light, the movement of the powder 2 due to the vibrating force increases. It is. As such powder 2, inorganic powders such as glass beads, silica balloons, shirasu balloons, vermiculite, and pearlite can be suitably used. This is because the surface of the powder 2 is hard, the surface is less likely to be worn due to collision or friction caused by the flow, and the durability is increased. An acrylic sphere or the like may be used.

Further, it is preferable that the amount of the powder 2 not to fill the internal space of the hollow panel 1 without a gap but to store an amount to leave a gap 16 as shown in FIG. This is because when the powder 2 is filled so that the gap 16 is not generated, the movement of the powder 2 is suppressed and the fluidity is reduced. Also, if the amount of the powder 2 is too small, the vibration-damping and sound-insulating effect is reduced. However, if the thickness of the layer of the powder 2 is approximately 2 to 3 mm or more, the sound insulating effect due to the flow phenomenon can be obtained. Has been confirmed.

The flow phenomenon of the powder 2 will be described in more detail. As shown in FIG. 3, a container 40 containing the powder 2 is vibrated in a vertical direction by a vibrator 41, The viscous resistance was measured by the rotational viscometer 42, and the viscous resistance ratio λ obtained by dividing the viscous resistance at the time of vibration by the viscous resistance at rest was calculated as an index indicating fluidity. FIG. 4 shows a powder 2 composed of glass beads having an average particle diameter of 45,15.
Excitation frequency of 125H for 0,300 μm
The correlation between the viscous resistance ratio λ at the time of z and the vibration acceleration level La is shown. The vibration acceleration level La of the vibration applied to the container 40 is expressed as follows: La = 20 log (a / a0) a: vibration acceleration applied to the container (m / s ² ) a0: reference vibration acceleration 10 ⁻⁵ (m / s ² ) La = 120 dB corresponds to an acceleration of about 1 G.

As is apparent from FIG. 4, although depending on the average particle size, the vibration acceleration level La is 100 dB to 110 dB.
Beyond B, the viscous resistance ratio λ rapidly decreases. This is because the powder 2 has flowed. Average particle size 150μ
FIG. 5 shows the results of measuring the viscous resistance ratio λ of the powder 2 composed of m glass beads while changing the excitation frequency to 125 Hz, 250 Hz, and 500 Hz. When the vibration acceleration level La exceeds 110 dB, the viscous resistance ratio λ rapidly decreases.
It can be seen that the fluidity has increased.

The relationship between the flow of the powder 2 and the sound radiated from the hollow panel 1 was determined for the hollow panel 1 containing the powder 2 using an experimental apparatus shown in FIG. That is, the center of the lower surface of the hollow panel 1 is vibrated by the vibrator 41 via the force transducer 43, and the sound radiated from the central panel 1 is picked up by the microphone 44 installed at a position 300 mm away from the center of the upper surface of the central panel 1. Input to the FFT analyzer 45. In the figure, 46 is a personal computer, 47 is a noise generator, and 48 is an amplifier. The hollow panel 1 has an upper surface side material 10 having a thickness of 1.2 mm, a lower surface side material 10 having a thickness of 0.6 mm, and a partition plate 11 having a height of 20.2 mm.
An aluminum panel of 30 mm × 22 mm was used.
The powder 2 has an average particle diameter of 300 μm and a bulk density of 14 μm.
It was housed in the hollow panel 2 so as to have a layer thickness of 15.7 mm using a 0 kg / m ³ shirasu balloon.

FIG. 7 shows the experimental results obtained when the excitation acceleration level La is 110 dB and 120 dB by the above-mentioned experimental apparatus, and the radiated sound is based on the radiated sound from the hollow panel 1 not containing the powder 2. It is shown in the amount of reduction (dB). It can be seen that there is a radiation sound reduction effect in almost the entire range of 100 Hz to 500 Hz, and that the amount of radiation sound reduction in the low frequency range of 250 Hz or less is large.

A hollow panel 1 filled with rock wool having a density of 130 kg / m ³ instead of the powder 2;
A density of 1 is formed on the lower surface side of the hollow panel 1 in which the powder 2 is not put.
Using a vibration damping sheet made of a soft vinyl chloride resin sheet having a weight of 47 kg / m ³ , the amount of radiation noise reduction when a vibration having an excitation acceleration level La of 120 dB was applied was measured. In order to make the areal density of the hollow panel 1 all 2.2 kg / m ² , the layer thickness of the powder 2 (Shirasu balloon) is 15.7 mm, the thickness of rock wool is 17 mm, and the thickness of the vibration damping sheet is 1 0.5 mm.
FIG. 8 shows the results. In the figure, a shows a case where powder 2 made of the above-mentioned shirasu balloon is stored, B shows a case where rock wool is stored, and C shows a case where a vibration damping sheet is attached.
It can be seen that the use of the powder 2 significantly reduces the amount of radiated sound particularly in the low frequency range than the rock wool or vibration damping sheet of the same weight.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described. FIG. 9 shows a pair of aluminum surface materials 1.
A hollow panel 1 having a partition plate 11 made of an aluminum honeycomb material of the form shown in FIG. 10 interposed between 0 and 10 is formed, and a hollow powder 2 is stored in the hollow panel 1. 2 is housed in each space partitioned by the partition plate 11, and the layer thickness D of the powder 2 is smaller than the height h (height of the internal space) of the partition plate 11. I have. As described above, the powder 2 having an average particle size of 30 to 1000 μm is used.

The material of the surface material 10 is not limited to aluminum, and does not prevent the use of a damping steel plate. Further, the partition plate 11 may not be a honeycomb material. However, in order to achieve both weight reduction and strength, it is preferable to provide the partition plate 11 made of a honeycomb material as shown in the illustrated example. FIG. 11 shows a configuration in which a hollow panel 1 containing powder 2 shown in FIG. 9 is arranged in place of the floor plate 31 in the conventional example shown in FIG. 16, and FIG. Is a surface material 10 in which a partition plate 11 is arranged in the concave groove portion, and the powder 2 is stored between the other surface material 10 laid on the keystone plate 30 and the bottom of the concave groove portion. I have.

The vibration damping and sound insulating panel P thus formed
Can be suitably used as a floor material, a wall material, or a ceiling material of a vehicle T, particularly a Shinkansen vehicle T, as shown in FIGS. That is, when the degree of vibration acceleration applied to a running Shinkansen vehicle was examined, the relationship between the traveling speed and the floor vibration acceleration level La was as shown in the table below.

[0019]

[Table 1]

As is clear from the above table, 270 km / h
It can be seen that the vibration acceleration of about 1 G or more is applied to the floor surface during the high-speed running described above. The running speed is 240 km / h.
And the acceleration level at 270 km / h are actually measured values.
It is an estimated value based on the 6th power law of aerodynamic noise from actual measured values at 40 km / h and 270 km / h. For this reason, the panel of the present invention, which obtains high vibration damping and sound insulating performance based on the flow generated when a vibration acceleration of about 1 G is applied, can be suitably used for a Shinkansen vehicle.

When the main transformer, the underfloor air conditioner, the bogie, and the like are subject to large vibration and noise,
Vibration acceleration of about 1 G or more may be applied even at a running speed of km / h or less, and vibration acceleration of 1 G or more may be applied to other vehicles having a running speed lower than that of Shinkansen vehicles, depending on the vehicle configuration and road surface conditions. It may be added to the vehicle.
A vibration acceleration of G or more may be applied. For this,
Of course, it is also effective for vehicles other than Shinkansen vehicles.

Now, a hollow panel 1 shown in FIG.
0.6m thick between the aluminum surface material 10m
m, a length L of one side is 6 mm, and a height h is 20.2 mm. The partition plate 11 is made of an aluminum honeycomb material, and has an average particle size of 300 μm and a bulk density of 140 k.
Using a shirasu balloon of g / m ³ as the powder 2, the powder was put into the hollow panel 1 so as to have a layer thickness of 15.7 mm and an areal density of 2.2 kg / m ² . As shown in FIG. 13, a microphone installed at the center of the Shinkansen vehicle T when traveling in a tunnel section at 300 km / h in a central section of the Shinkansen vehicle T using the hollow panel 1 containing the powder 2 as a floor panel. When measured at 44, as shown by E in FIG. 14, the sound pressure level was 63H as compared with the case where the hollow panel 1 containing no powder 2 was used (f in the figure).
2-5d over a wide frequency band of z-4kHz
B was reduced, and the reduction in noise level was 3.0 dB. In addition to the panel radiation noise reduction effect based on the flow of the powder 2, the panel radiation noise reduction effect due to the vibration of the powder 2 that counteracts the excitation force acts in a combined manner, so that the reduction effect can be achieved in a wide frequency range. It is thought that it appeared.

[0023]

As described above, in the present invention, since a powder having an average particle size of 30 to 1000 μm is stored in the internal space of a hollow panel having two facing surface materials, sound and noise are reduced. When the hollow panel is vibrated by vibration, the powder stored in the internal space moves under the vibrating force and converts the vibration energy into heat energy to exhibit vibration damping and sound insulation. When the vibration acceleration is about 1 G, the movement of the powder caused by the flow phenomenon can be used effectively, so that extremely high vibration damping and sound insulating performance can be obtained. Since the increase in weight due to the body is small, it is possible to achieve compatibility with weight reduction.

By providing the hollow panel with a partition plate for partitioning the internal space into a plurality of sections, it is possible to achieve both a reduction in weight and strength, and also to obtain a powder when subjected to vibration. Can be increased by the presence of the partition plate. In addition, it is possible to expect a vibration-damping and sound-insulating effect due to the powder without depending on the use posture of the hollow panel.

Furthermore, if the powder is a hollow powder or a powder having fine pores, the increase in weight due to the powder can be further reduced, which is advantageous in terms of weight reduction. By storing the powder in the internal space of the hollow panel with a gap left therebetween, the vibration damping and sound insulating properties can be further enhanced.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view illustrating an example of a vibration damping sound insulation panel according to the present invention.

FIGS. 2A and 2B show examples of the powder used in the above example, wherein FIG. 2A is a cross-sectional view of one example, and FIG.

FIG. 3 is an explanatory view of a device for measuring fluidity of powder.

FIG. 4 is an explanatory diagram of a correlation between a vibration acceleration level of a powder and a viscous resistance ratio.

FIG. 5 is an explanatory diagram of a correlation between a vibration acceleration level and a viscous resistance ratio due to a difference in a vibration frequency of powder.

FIG. 6 is an explanatory diagram of a device for measuring a radiation sound level.

FIG. 7 is an explanatory diagram of a correlation between a frequency and a radiation sound reduction amount.

FIG. 8 is an explanatory diagram of a correlation between a frequency and a radiation sound reduction amount.

FIG. 9 is a perspective view of an example of the embodiment.

FIG. 10 is a perspective view of a partition plate used in the above.

FIG. 11 is a cutaway perspective view of another example.

FIG. 12 is a cutaway perspective view of still another example.

FIG. 13 is a schematic sectional view showing a state of use for a Shinkansen vehicle.

FIG. 14 is an explanatory diagram of the effect of reducing the vehicle interior noise level of the above.

FIG. 15 is a schematic sectional view showing another example of a use state for a Shinkansen vehicle.

FIG. 16 is a cutaway perspective view of a conventional example of a vehicle floor structure.

FIG. 17 is a cutaway perspective view of another conventional example of a vehicle floor structure.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hollow panel 2 Powder 10 Surface material 11 Partition plate

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[Procedure amendment]

[Submission date] June 23, 1997

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0007

[Correction method] Change

[Correction contents]

When the hollow panel 1 is vibrated by sound or vibration, the powder 2 stored in the internal space moves due to the vibrating force. In this invention, vibration energy is converted into heat energy by a particle deformation at the time of collision or a friction or collision between two particles of the powder and the inner surface of the hollow panel 1 to exert a vibration damping and sound insulating effect. Vibration acceleration g is almost 1 G (9.8 m /
s ² ) The flow phenomenon that occurs in powder 2 when it is around (see Yoshihiro Taguchi: Journal of the Society of Powder Engineering, Vol. 30, 173 (1993).
Arakawa Masafumi, Nishino Misao: Materials, Volume 20, 776 (197
In order to effectively use 1)), the powder 2 having a particle size of 30 to 1000 μm is used. This flow phenomenon is
Points to the motion of the pattern as shown by the arrows in FIG. 1 momentum of the powder 2 rapidly increases occurred in the powder 2
You. In the case of the powder 2 having a particle size smaller than 30 μm, the adhesive force acting between the particles of the powder 2 is increased, and the powder 2 is aggregated, so that the fluidity is impaired.
This is because if the powder 2 has a larger particle size, the mass of each particle is too large and the fluidity is significantly reduced.

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0013

[Correction method] Change

[Correction contents]

The relationship between the flow of the powder 2 and the sound radiated from the hollow panel 1 was determined for the hollow panel 1 containing the powder 2 using an experimental apparatus shown in FIG. That is, to vibrate via the force transducer 43 by the vibrator 41 to the center of the lower surface of the hollow panel 1, by the microphone 44 installed sound radiation from the hollow panel 1 in a position away 300mm from the center of the upper surface of the hollow panel 1 Input to the FFT analyzer 45. In the figure, 46 is a personal computer, 47 is a noise generator, and 48 is an amplifier. The hollow panel 1 has an upper surface side material 10 having a thickness of 1.2 mm, a lower surface side material 10 having a thickness of 0.6 mm, and a partition plate 11 having a height of 20.2 mm.
An aluminum panel of 30 mm × 22 mm was used.
The powder 2 has an average particle diameter of 300 μm and a bulk density of 14 μm.
Using a 0 kg / m ³ shirasu balloon, it was housed in the hollow panel 1 so as to have a layer thickness of 15.7 mm.

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Kenji Onishi 1048 Ojimon Kadoma, Kadoma-shi, Osaka Matsushita Electric Works, Ltd. Inventor Fujio Horie 3-9-60 Inadashinmachi, Higashiosaka-shi, Osaka Kinki Vehicle Co., Ltd.

Claims (4)

[Claims] 1. A vibration-damping and sound-insulating panel, comprising: a hollow panel having two opposing surface materials, wherein powder having an average particle size of 30 to 1000 μm is stored in an internal space. 2. The hollow panel includes a partition plate for dividing an internal space into a plurality of sections, and the powder is stored in at least one section.
The described vibration damping sound insulation panel. 3. The vibration damping and sound insulating panel according to claim 1, wherein the powder is a hollow powder or a powder having fine holes. 4. The vibration damping and sound insulating panel according to claim 1, wherein the powder is stored in the internal space with a gap left.