JP5808970B2 - Open air layer vibration reduction structure - Google Patents

Description

  In the present invention, an air layer is formed between a plate-like member arranged with the front side facing the open space side, and a housing arranged at a distance from the back side of the plate-like member. In terms of structure, the present invention relates to a newly proposed air layer open type vibration reducing structure.

  In order to reduce noise and vibration, a soundproof structure and a vibration proof structure configured to attenuate noise and vibration may be provided in a building indoor space, a car interior space, a road, and the like.

  Regarding the soundproof structure, for example, Non-Patent Document 1 and Non-Patent Document 2 disclose a structure of a double-layer glass used for a window or the like provided in a room of a building. In the structure of Non-Patent Document 1 and Non-Patent Document 2, a fine perforated plate having fine holes formed on one surface of a multilayer glass is arranged, and the sound incident from the fine perforated plate side is sound-insulated It has become. Patent Documents 1 and 2 disclose a structure for absorbing sound incident from an indoor space serving as a sound field. In the structures of Patent Document 1 and Patent Document 2, the fine perforated plate is arranged so that its front side faces the indoor space serving as a sound field and its back side faces the wall or ceiling. An air layer is formed with the ceiling, and a plurality of cylindrical members are arranged on the back side surface of the fine perforated plate corresponding to the plurality of holes of the fine perforated plate.

  In addition, with regard to vibration and noise, which are particularly problematic in building structures, loads such as impacts are applied to the building structure by human actions in the building, and vibrations are generated due to the impacts. Solid propagation sound (so-called floor impact sound) may occur. Patent Document 3 discloses a ceiling and wall structure that insulates floor impact sound applied from the upper floor of a building. In the ceiling and wall structure of Patent Document 3, a perforated plate is disposed on the interior space side of the base casing with a space from the casing, and an air layer is provided between the casing and the perforated plate, which is hard. A support member made of a material is disposed between the perforated plate and the housing, and the perforated plate is supported by the support member.

  Furthermore, in order to reduce the vibration caused by the load applied to the building structure, a double structure may be employed for the floor structure in the building interior. In this double structure, the floor member is arranged so that its front side faces the indoor space side and its back side faces the underlying housing side, and an air layer is formed between the floor member and the housing. The floor member is supported by an anti-vibration rubber disposed between the floor member and the housing. Non-Patent Document 3 discloses that the floor impact sound caused by the load applied to the structure of the building is changed by changing the thickness of the air layer in such a double structure.

JP 2007-11034 A JP 2010-7278 A JP 2003-56092 A

Daigo Takahashi and two others, “Study on improvement of sound insulation performance of double-glazed glass -Proposal of double window structure using micro-perforated plate-", Proc. Of the Acoustical Society of Japan Presentation Meeting (Autumn 2009), Japan Acoustical Society of Japan, September 2009, p1009-p1010 Daigo Takahashi and two others, “Study on double window structure using micro perforated plates”, Acoustical Society of Japan Presentation Meeting (Spring 2010), Acoustical Society of Japan, March 2010, p1159- p1160 Daigo Takahashi and two others, "Study on the effect of air venting on the weight impact sound of double floor structure", Proceedings of the Acoustical Society of Japan Presentation Meeting (Spring 2010), The Acoustical Society of Japan, March 2010, p1181-p1182

  However, in the structure of Patent Document 1, Patent Document 2, Non-Patent Document 1, and Non-Patent Document 2, only the soundproofing against the sound transmitted through the fine perforated plate from the indoor space side is considered. With this structure, it is not possible to obtain a sufficient vibration-proofing effect against a load such as an impact applied to the building structure. Further, in the structure of Patent Document 3, since the perforated plate is supported by the support member made of a hard material, vibration is easily transmitted between the perforated plate and the housing, and an impact applied to the structure of the building, etc. The vibration-proofing effect against the load cannot be obtained sufficiently.

  In order to reduce vibration caused by loads such as impacts applied to the building structure, it is considered effective to use anti-vibration rubber in the double structure of the floor described above. Basically, it is designed in consideration of characteristics such as the spring constant of vibration-proof rubber. However, regarding the double structure of the floor, a structure provided with anti-vibration rubber (hereinafter referred to as “structure with anti-vibration rubber”) and a structure in which the floor member is lifted without being provided with anti-vibration rubber (hereinafter referred to as “non-vibration rubber”). Exciting the housing side with a vibrator and measuring the vibration acceleration at multiple locations on the floor member and the housing, respectively, and the average value of vibration acceleration in the housing The result of calculating the results of the vibration isolation effect amount (= the average value of the vibration acceleration of the casing−the average value of the vibration acceleration of the floor member) for each frequency, which is the difference between the average value of the vibration acceleration in the floor member, As shown in FIG. 14, the result represented by the solid line S1 was obtained for the structure with anti-vibration rubber, and the result represented by the broken line S2 was obtained for the structure without the anti-vibration rubber. In FIG. 14, the vertical axis represents the image stabilization effect amount (dB), and the horizontal axis represented by the logarithmic axis represents the frequency (Hz).

  In FIG. 14, the anti-vibration effect amount of the structure with anti-vibration rubber includes the peak of the resonance frequency f0 (= about 7.4 Hz) indicated by the arrow X and the peak of the resonance frequency f1 (= about 12 Hz) indicated by the arrow Y. These peaks did not appear in the anti-vibration effect amount of the structure without anti-vibration rubber. On the other hand, in FIG. 14, the vibration isolation effect amount of both the structure with anti-vibration rubber and the structure without anti-vibration rubber is in the frequency region after the peak of the resonance frequency f2 (= about 46 Hz) indicated by the arrow Z. There was little change. In the natural vibration mode at the resonance frequency f0, the entire floor member moves in the vertical direction as shown in FIG. 15, and in the natural vibration mode at the resonance frequency f1, each corner of the floor member is a clock as shown in FIG. It moves so as to have the maximum amplitude in the order of the surroundings, and the natural vibration mode of the resonance frequency f0 and the resonance frequency f1 is a natural vibration mode due to the spring property of the vibration-proof rubber. On the other hand, in the natural vibration mode of the resonance frequency f2, as shown in FIG. 17, the floor member moves in a bow shape so that the central portion in the direction of one side has the maximum amplitude, and the natural vibration of the resonance frequency f2 The mode is a natural vibration mode caused by the characteristics of the floor member. Therefore, the effect of the anti-vibration rubber is not very effective against the natural vibration caused by the characteristics of the floor member, and only considering the characteristics such as the spring constant of the anti-vibration rubber, the double structure of the floor A sufficient anti-vibration effect is not obtained.

  About the influence of the air layer in the double structure of a floor mentioned above, it is known that a floor impact sound will change by changing the thickness of the air layer in a double structure like nonpatent literature 3. However, conventionally, no measures have been taken to reduce the vibration caused by the load applied to the building structure in consideration of the effect of the air layer.

  Furthermore, regarding the sound transmission of the sound insulation structure such as the fine perforated plate and the perforated plate in Patent Literature 1 to Patent Literature 3 and Non Patent Literature 1 to Non Patent Literature 3, the sound wave emitted from the sound source is incident on the sound insulation structure. Sound insulation based on the difference between the sound pressure level on the incident side of the sound insulation structure that is the sounding side and the sound pressure level on the transmission side of the sound insulation structure on the side that emits sound waves that have passed through the sound insulation structure after entering from the sound source side When the performance is defined, the same sound insulation performance can be obtained even when the incident side and the reflection side are reversed. That is, the reversible law is established for the sound transmission of the sound insulation structure in the above-mentioned patent document. However, in the above-described double structure of the floor, the vibration characteristics related to the vibration on the casing side when the floor member side is excited and the vibration characteristics related to the vibration on the floor member side when the casing side is excited tend to be different. That is, the reversible law is not established for the vibration characteristics between the floor member and the frame in the double floor structure as described above.

  Therefore, in an anti-vibration structure such as a double floor structure, in order to obtain an effective anti-vibration effect, complicated conditions such as the air layer between the floor member and the frame, the rigidity and weight of the floor member and the frame, and the like. It is important to consider this.

  In addition, in actual use, there is a person in the open space where the front side surface of the floor member or the like faces, and objects are arranged on the front side surface of the floor member or the like. For this reason, it is required to realize a vibration reduction structure having high practicality without affecting the actual use of front surfaces such as open spaces and floor members.

  The present invention has been made in view of such a situation, and the object thereof is to effectively reduce vibration caused by a load such as an impact, and as a new structure having high practicality, an air layer open type vibration is provided. It is to provide a reduction structure.

In order to solve the problem, the air layer open type vibration reducing structure of the present invention may be configured in any one of the following (1) to (3).
(1) The air layer open-type vibration reducing structure of the present invention is spaced apart from a plate-like member disposed with the front side facing the open space and a back side opposite to the front side of the plate-like member. An air layer open type vibration reducing structure in which an air layer is formed between the plate-like member and the housing, and the air layer is disposed between the air layer and the outside of the air layer. The through cylinder is disposed inside the plate-shaped member, and an opening located at an air layer side end of the through-cylinder is disposed on a back side surface of the plate-shaped member, An opening located at the outer side end of the cylinder is disposed on the periphery of the plate-like member.
Therefore, a predetermined ventilation resistance and / or a predetermined sound reduction effect is brought about between the air layer and the outside of the air layer by the through-cylinder, and the through-cylinder in which air provides such an action. By passing through, the spring characteristic or the damping characteristic based on the air layer acts to reduce vibration. Further, such a through cylinder is formed avoiding the front side surface of the plate-shaped member that is often used in an actual use environment. For example, when the front side surface of the plate-like member is configured as a floor surface, the opening at the outer side end of the through-cylinder is arranged avoiding such a floor surface. Therefore, the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced. Further, since the air path between the air layer and the outside of the air layer is simply formed by the through-cylinder that is separate from the plate-like member and the housing, a new structure is provided. The air layer open type vibration reducing structure of the present invention can be adopted not only for objects but also for existing structures. Therefore, the practicality of the air layer open type vibration reducing structure can be enhanced. In particular, since the plate-like member can be fitted into the case after the case has been produced, the through-cylinder is installed inside the plate-like member in the state of the plate-like member alone. Work becomes possible. Therefore, the cylinders can be easily installed, and the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced.

(2) The air layer open-type vibration reducing structure of the present invention is spaced apart from a plate-like member disposed with the front side facing the open space side and a back side opposite to the front side of the plate-like member. An air layer open type vibration reducing structure in which an air layer is formed between the plate-like member and the housing, and the air layer is disposed between the air layer and the outside of the air layer. The through cylinder is disposed inside the housing, and the opening located at the air layer side end of the through cylinder is disposed on the bottom surface of the housing forming the air layer, The opening located at the outer side end of the through-cylinder is disposed on the outer wall side surface of the housing located outside the air layer or the outer bottom surface of the housing located outside the air layer.
Therefore, a predetermined ventilation resistance and / or a predetermined sound reduction effect is brought about between the air layer and the outside of the air layer by the through-cylinder, and the through-cylinder in which air provides such an action. By passing through, the spring characteristic or the damping characteristic based on the air layer acts to reduce vibration. Further, such a through cylinder is formed so as to avoid the front side surface of the plate-like member that is often used in an actual use environment and the surface facing the bottom surface of the housing. For example, when the front side surface of the plate-like member is configured as a floor surface, and the surface facing the bottom surface of the housing is configured as a ceiling surface, avoid such floor surface and ceiling surface, An opening at the outer side end of the cylinder is disposed. Therefore, the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced. Further, since the air path between the air layer and the outside of the air layer is simply formed by the through-cylinder that is separate from the plate-like member and the housing, a new structure is provided. The air layer open type vibration reducing structure of the present invention can be adopted not only for objects but also for existing structures. Therefore, the practicality of the air layer open type vibration reducing structure can be enhanced. In particular, objects are often placed in the open space under an actual use environment, but the area of the housing that contacts the external space of the air layer other than the open space is large. Therefore, the degree of freedom in design for installing the through-cylinder that communicates the air layer with the outside of the air layer is increased, and the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced. .

(3) The air layer open-type vibration reducing structure of the present invention is spaced apart from a plate-like member disposed with the front side facing the open space and a back side opposite to the front side of the plate-like member. An air layer open-type vibration reducing structure in which an air layer is formed between the plate-like member and the housing, and the plate-like member is disposed on the housing with respect to the housing. An anti-vibration rubber is disposed between the plate-like member and the housing so as to support the plate-like member, and is movable between the open space side and the air layer side, and the air layer and the air A through cylinder communicating with the outside of the layer is provided, and the through cylinder is disposed in the air layer.
Therefore, a predetermined ventilation resistance and / or a predetermined sound reduction effect is brought about between the air layer and the outside of the air layer by the through-cylinder, and the through-cylinder in which air provides such an action. By passing through, the spring characteristic or the damping characteristic based on the air layer acts to reduce vibration. Further, such a through cylinder is formed avoiding the front side surface of the plate-shaped member that is often used in an actual use environment. For example, when the front side surface of the plate-like member is configured as a floor surface, the opening at the outer side end of the through-cylinder is arranged avoiding such a floor surface. Therefore, the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced. Further, since the air path between the air layer and the outside of the air layer is simply formed by the through-cylinder that is separate from the plate-like member and the housing, a new structure is provided. The air layer open type vibration reducing structure of the present invention can be adopted not only for objects but also for existing structures. Therefore, the practicality of the air layer open type vibration reducing structure can be enhanced. In particular, since the through-cylinder may be disposed in the air layer that is a cavity, the through-cylinder can be easily installed, and the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced. .

Furthermore, the air layer open type vibration reducing structure of the present invention is preferably configured as follows.
In the air layer open type vibration reduction structure of the present invention, the mean value of the airflow resistance of the surface to form the air layer in the plate-like member or the precursor is greater than 0N · s / m ^3, and 1000N · s / m ³ Since the through-cylinder is configured to be as follows, the air passes through the through-cylinder that communicates between the air layer and the outside of the air layer and has the ventilation resistance. A spring characteristic or a damping characteristic based on the air layer acts to reduce vibration.

  In the air layer open type vibration reducing structure of the present invention, the sound pressure level generated in the air layer due to the addition of an external force is compared with the case where the plate member and the housing have no air permeability, the plate member, Since the through-cylinder is configured to be reduced by 3 dB or more at a dominant frequency based on the characteristics of a series of systems including the casing and the air layer, the air layer having the characteristic of reducing the sound pressure level and the When the air passes through the through-cylinder communicating with the outside of the air layer, the spring characteristic or the damping characteristic based on the air layer acts to reduce vibration.

In the air layer open type vibration reducing structure of the present invention, a sound detector disposed in the air layer or in the through cylinder, a sound detector disposed in the through cylinder, and electrically connected to the sound detector; An output device configured to generate sound or vibration, and to reduce the sound pressure level in the air layer corresponding to the sound pressure level in the air layer detected by the sound detector. In addition, it is preferable that the output device can be controlled.
Alternatively, a vibration detector attached to the plate-like member and / or the housing, a sound detector arranged in the air layer or in the through-cylinder, and arranged in the through-cylinder, the vibration detector And an output device electrically connected to the sound detector and configured to generate sound or vibration, and the vibration of the plate-like member and / or the housing detected by the vibration detector It is preferable that the output device can be controlled so as to reduce the sound pressure level in the air layer detected by the sound detector corresponding to the amplitude.
Alternatively, a vibration detector attached to the plate-like member and / or the housing, a sound detector arranged in the air layer or in the through-cylinder, and arranged in the through-cylinder, the vibration detector And an output device electrically connected to the sound detector and configured to generate sound or vibration, and corresponding to a sound pressure level in the air layer detected by the sound detector. The output device may be controlled so as to reduce the vibration amplitude of the plate-like member and / or the housing detected by the vibration detector.
Alternatively, a vibration detector attached to the plate-like member and / or the housing, and disposed in the through-cylinder, electrically connected to the vibration detector, and configured to generate sound or vibration. And further reducing the vibration amplitude of the plate member and / or the housing corresponding to the vibration amplitude of the plate member and / or the housing detected by the vibration detector, It is preferable that the output device can be controlled.
Therefore, since the sound pressure level in the air layer can be adjusted without being influenced by external factors, the spring characteristic or damping characteristic based on the air layer acts stably to reduce vibrations. Become. Further, in order to provide a predetermined airflow resistance and a predetermined sound reduction effect between the air layer and the outside of the air layer, the sound can be obtained without using a complicated structure such as providing a large number of the cylinders. Using the detector and / or the vibration detector and the output device, the air layer open type vibration reducing structure of the present invention can be simplified. With such a simple structure, the air layer open type vibration reducing structure of the present invention can be easily installed by an existing structure, and the practicality of the air layer open type vibration reducing structure of the present invention can be enhanced. .

  In the air layer open type vibration reducing structure of the present invention, a silencer is attached to the opening located at the outer side end of the cylinder, so that characteristics within the air layer, for example, acoustics inside the air layer, It is possible to prevent the sound pressure outside the air layer from increasing due to resonance or the like. Therefore, the practicality of the air layer open type vibration reducing structure of the present invention can be further enhanced.

  In the open air type vibration reducing structure of the present invention, an acoustically transparent member having a sound insulation performance that reduces the sound pressure level by 0 dB to 2 dB in a frequency range of 30 Hz to 300 Hz is disposed in the through cylinder. Therefore, the cylinder is closed by the acoustically transparent member having only a slight sound insulation performance. Therefore, it is possible to effectively reduce vibration caused by a load such as an impact without impairing a predetermined ventilation resistance and a predetermined acoustic reduction effect between the air layer and the outside of the air layer. In addition, such an acoustically transparent member provides water resistance and dust resistance to the through cylinder, and as a result, prevents foreign matter from entering the air layer through the through cylinder. it can. Therefore, the air layer open type vibration reducing structure of the present invention can be made more practical.

  ADVANTAGE OF THE INVENTION According to this invention, the vibration resulting from loads, such as an impact, can be reduced effectively, and an air layer open | release type vibration reduction structure can be provided as a new structure with high practicality.

(A) It is a top view which shows roughly the basic air layer open | release type vibration reduction structure used as the premise in describing the air layer open type vibration reduction structure which concerns on 1st Embodiment-11th Embodiment. (B) It is AA sectional drawing of Fig.1 (a). In the basic air layer open type vibration reducing structure of FIGS. 1 (a) and 1 (b), an anti-vibration effect amount which is a difference between an average value of vibration acceleration in the housing and an average value of vibration acceleration in the plate member, It is a figure which shows the relationship with a frequency. 1 (a) and 1 (b), the air layer open-type vibration reduction structure includes a wind speed of air passing between the front side surface and the back side surface of the plate-like member, and a ventilation resistance of the plate-like member. It is a figure which shows a relationship. 1 (a) and 1 (b), the sound pressure in the air layer when an external force is applied to the vibration reducing structure using a plate-like member having no air permeability. It is a figure which shows the relationship between the difference of a sound pressure level when an external force is added to the air layer open | release type vibration reduction structure using the plate-shaped member which has a level and a vent hole, and a frequency. (A) It is a top view which shows roughly the air layer open | release type vibration reduction structure which concerns on 1st Embodiment of this invention. (B) It is BB sectional drawing of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 2nd Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 3rd Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 4th Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 5th Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 6th Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 8th Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing which showed the air layer open | release type vibration reduction structure which concerns on 10th Embodiment of this invention similarly to the BB sectional view of Fig.5 (a). It is sectional drawing of the external side periphery periphery of the through-cylinder used for the air layer open | release type reduction structure which concerns on 11th Embodiment of this invention. It is the figure which compared the anti-vibration effect amount at the time of providing anti-vibration rubber, and the anti-vibration effect amount at the time of lifting up a floor member and providing free support without providing anti-vibration rubber. It is a natural vibration mode at the peak indicated by X in FIG. It is a natural vibration mode at the peak indicated by Y in FIG. It is a natural vibration mode at the peak indicated by Z in FIG.

  The air layer open type vibration reducing structure (hereinafter referred to as “vibration reducing structure”) according to the first to eleventh embodiments of the present invention will be described below. In addition, although each embodiment demonstrates the vibration reduction structure provided in the floor in the room of a building, it is not limited to this, The vibration reduction structure which concerns on each embodiment is provided in the wall, ceiling, etc. in the room of a building May be. Moreover, this vibration reduction structure may be provided on the floor, side, ceiling, etc. in the interior of the automobile, or may be provided on the road surface of an outdoor road.

First, characteristics of a basic vibration reduction structure (hereinafter referred to as “basic vibration reduction structure”) that is a premise of the characteristics of the vibration reduction structure according to each embodiment will be described.
As shown in FIGS. 1A and 1B, the basic vibration reducing structure is provided with a plate-like member 1 configured as a floor member. Further, the basic vibration reducing structure is provided with a casing 2 that serves as a foundation for supporting the plate-like member 1. The plate-like member 1 is formed in a quadrangular shape, and its front side surface 1a is arranged facing the indoor open space, and the front side surface 1a of the plate-like member 1 is configured as an indoor floor surface. . The casing 2 is formed in a concave shape, and the concave casing 2 is provided with an opening 2a that opens on the open space side in the room. The plate-like member 1 is configured to be fitted into the opening 2 a of the housing 2. The back side surface 1b of the plate-like member 1 and the bottom surface 2b of the housing 2 are arranged with a space therebetween, and the back-side surface 1b of the plate-like member 1 and the housing 2 are between the plate-like member 1 and the housing 2. An air layer 3 surrounded by the bottom surface 2b and the side wall surface 2c is formed. Antivibration rubber 4 is disposed on the bottom surface 2 b of the housing 2 corresponding to the corners of the plate member 1, and the plate member 1 is supported by the antivibration rubber 4. Note that the peripheral edge 1c of the plate-like member 1 and the side wall surface 2c of the housing 2 are in contact with or close to each other, and the plate-like member 1 has an open space side and an air layer 3 side with respect to the housing 2. It is possible to move to. A plurality of ventilation holes 1 d are formed in the entire plate-like member 1 as ventilation portions that communicate the open space and the air layer 3, and the ventilation holes 1 d penetrate the plate-like member 1.

In this case, as the mean value of the airflow resistance (flow resistance) at the surface to form the air layer 3 of the plate-like member 1 is greater than 0N · s / ^{m 3,} and a 1000 N · s / ^{m 3} or less, through The shape, size, number, etc. of the pores 1d are determined.

Here, the lower limit of the average value of the ventilation resistance is determined as follows.
When the plate-like member 1 is not provided, the average value of the ventilation resistance is 0 N · s / m ³ . However, since it is assumed that the plate-like member 1 is provided in the basic vibration reduction structure, the average value of the ventilation resistance assumed in the basic vibration reduction structure exceeds 0 N · s / m ^{3 due} to such a premise. There is a need. For this reason, the lower limit of the average value of the ventilation resistance described above exceeds 0 N · s / m ³ .

On the other hand, the upper limit of the average value of ventilation resistance is determined as follows.
When the opening ratio, which is the ratio of the area of all the vent holes 1d on the front side surface 1a or the back side surface 1b of the plate-like member 1 to the area of the front side surface 1a or the back side surface 1b of the plate-like member 1, is changed. Anti-vibration effect amount (= average value of vibration acceleration of the casing−average value of vibration acceleration of the floor member), the frequency, and the difference between the average value of vibration acceleration and the average value of vibration acceleration in the plate member 1 The relationship was as shown in FIG. In FIG. 2, the solid line W1 when the aperture ratio is 0.18%, the one-dot chain line W2 when the aperture ratio is 0.36%, the two-dot chain line W3 when the aperture ratio is 0.73%, and the aperture ratio 1.46. % Is a dotted line W4, an aperture ratio is 2.92% is a one-dot chain line W5 (the interval between adjacent one-point portions is wider than W2), and an aperture ratio is 5.83% is a two-dot chain line (adjacent two points A broken line W7 indicates a case where the interval between the portions is wider than W3) W6 and the aperture ratio is 14.58%. In FIG. 2, the natural vibration mode caused by the characteristics of the plate-like member 1, in particular, the primary natural vibration mode of the plate-like member 1 (about 40 Hz in FIG. 2), and the secondary natural vibration mode of the plate-like member 1 (see FIG. 2). 2 is about 80 Hz), it can be confirmed that the vibration reduction effect is obtained when the aperture ratio becomes 0.73% or more.
Therefore, the relationship between the aperture ratio and the ventilation resistance was confirmed.
When the air velocity was changed between the front side surface 1a and the back side surface 1b in the plate-like member 1 having each aperture ratio described above, the wind speed was changed in each plate-like member 1 having each aperture ratio. The relationship with the ventilation resistance was as shown in FIG. In FIG. 3, as in FIG. 2, the solid line W1 when the aperture ratio is 0.18%, the one-dot chain line W2 when the aperture ratio is 0.36%, and the two-dot chain line W3 when the aperture ratio is 0.73%. In the case of an aperture ratio of 1.46%, a dotted line W4, in the case of an aperture ratio of 2.92%, an alternate long and short dash line W5 (the interval between adjacent point portions is wider than W2), and in the case of an aperture ratio of 5.83%, two points A broken line W7 indicates a case of a chain line (interval between adjacent two points wider than W3) W6 and an aperture ratio of 14.58%. Since the wind speed of the air flowing between the front side surface 1a and the back side surface 1b in the plate-like member 1 when vibration is actually generated is 0 m / s to 0.2 m / s, the aperture ratio is within such a range of wind speed. In the case of 0.73% or more, it can be confirmed that the average value of the ventilation resistance is constantly 1000 N · s / m ³ or less.
Therefore, it can be confirmed that the upper limit of the average value of the ventilation resistance described above is preferably 1000 N · s / m ³ or less.

  Alternatively, in the basic vibration reduction structure, the sound pressure level generated in the air layer 3 due to the application of external force is different from that in the case where the plate-like member 1 has no air permeability, from the plate-like member 1, the housing 2 and the air layer 3. The shape, size, number, and the like of the vent hole 1d are determined so as to be reduced by 3 dB or more at the dominant frequency (in FIG. 2, about 40 Hz, about 80 Hz, etc.) based on the characteristics of a series of systems.

This is determined as follows.
As described above, in FIG. 2, the dominant frequency based on the characteristics of a series of systems composed of the plate member 1, the casing 2 and the air layer 3, particularly at about 40 Hz and about 80 Hz, the aperture ratio is 0.73% or more. It can be confirmed that a vibration reduction effect can be obtained in the state.
Therefore, the relationship between the aperture ratio and the sound pressure level was confirmed.
From the sound pressure level in the air layer 3 when an external force is applied to the vibration reduction structure using a plate-like member having no air permeability, the basic vibration reduction structure using the plate-like member 1 having each opening ratio described above is used. When the difference obtained by subtracting each sound pressure level when an external force was applied was measured, the relationship between the sound pressure level difference and the frequency was as shown in FIG. In FIG. 4, as in FIG. 2, the solid line W1 when the aperture ratio is 0.18%, the one-dot chain line W2 when the aperture ratio is 0.36%, and the two-dot chain line W3 when the aperture ratio is 0.73%. In the case of an aperture ratio of 1.46%, a dotted line W4, in the case of an aperture ratio of 2.92%, an alternate long and short dash line W5 (the interval between adjacent point portions is wider than W2), and in the case of an aperture ratio of 5.83%, two points A broken line W7 indicates a case of a chain line (interval between adjacent two points wider than W3) W6 and an aperture ratio of 14.58%. In FIG. 4, when the aperture ratio is 0.73% or more, the above-mentioned sound is obtained at a dominant frequency of about 40 Hz and a dominant frequency of about 80 Hz based on the characteristics of a series of systems including the plate member 1, the casing 2 and the air layer 3. It is confirmed that the pressure level difference is 3 dB or more.
In addition, since the upper limit of the sound pressure level to be reduced is the sound pressure level itself when the plate-like member 1 is not air permeable, it is not particularly specified.

Furthermore, the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 3 of the plate-like member 1 is greater than 0N · s / ^{m 3,} and becomes 1000 N · s / ^{m 3} or less, in addition, The sound pressure level generated in the air layer 3 due to the addition of external force is based on the characteristics of a series of systems composed of the plate-like member 1, the housing 2, and the air layer 3 when the plate-like member 1 has no air permeability. The shape, size, number, etc., of the vent 1d may be determined so that it is reduced by 3 dB or more at the dominant frequency.

[First Embodiment]
The vibration reduction structure according to the first embodiment of the present invention will be described.
As shown in FIGS. 5A and 5B, the vibration reducing structure is provided with a plate-like member 11 configured as a floor member. Further, the vibration reduction structure is provided with a casing 12 that serves as a foundation for supporting the plate-like member 11. The plate-like member 11 is formed in a quadrangular shape, and its front side surface 11a is arranged facing the indoor open space, and the front side surface 11a of the plate-like member 11 is configured as an indoor floor surface. . The casing 12 is formed in a concave shape, and the concave casing 12 is provided with an opening 12a that opens on the open space side in the room. The plate-like member 11 is configured to be fitted into the opening 12a of the housing 12 like this. The back side surface 11 b of the plate-like member 11 and the bottom surface 12 b of the housing 12 are arranged with a space therebetween, and the back side surface 11 b of the plate-like member 11 and the housing 12 are between the plate-like member 11 and the housing 12. An air layer 13 surrounded by the bottom surface 12b and the inner wall side surface 12c is formed. Antivibration rubber 14 is disposed on the bottom surface 12 b of the housing 12 corresponding to the corners of the plate member 11, and the plate member 11 is supported by the antivibration rubber 14. The peripheral edge 11c of the plate-like member 11 and the inner wall side surface 12c of the housing 12 are arranged in contact with or close to each other, and the plate-like member 11 is open to the housing 12 and the air layer 13 side. It is possible to move to.

  At least one through cylinder 15 is arranged inside the plate-like member 11. Further, with respect to the through cylinders 15, a plurality of through cylinders 15 may be arranged inside the plate-like member 11 as long as the operation and effect of the present invention can be obtained. In FIG. 5A and FIG. 5B, as an example, one through cylinder 15 is arranged inside the plate member 11. The communication cylinder 15 communicates between the air layer 13 and the outside of the air layer 13, and extends in a substantially L shape between the back side surface 11 b of the plate-like member 11 and the peripheral edge 11 c of the plate-like member 11. An air layer side opening 15 a is formed at the air layer side end of the through cylinder 15, and the air layer side opening 15 a is disposed on the back side surface 11 b of the plate-like member 11. 5A and 5B, the air layer side opening 15a is arranged at the center of the back surface 11b of the plate-like member 11 as an example. An external opening 15 b is formed at the external end of the through-cylinder 15, and the external opening 15 b is disposed on the peripheral edge 11 c of the plate member 11.

For such a through cylinder 15, the average value of the ventilation resistance (flow resistance) on the surface forming the air layer 13 of the plate-like member 11 exceeds 0 N · s / m ³ , as in the basic vibration reducing structure. The shape, size and number of the through-cylinder 15 and the positions and shapes of the air layer side opening 15a and the external side opening 15b of the through-cylinder 15 are determined so as to be 1000 N · s / m ³ or less.

  Alternatively, in the first embodiment, as in the case of the basic vibration reduction structure, the sound pressure level generated in the air layer 13 due to the application of external force is different from the case where the plate member 11 has no air permeability. The shape, size, and number of the through-cylinder 15, the air-layer side opening 15 a and the external-side opening of the through-cylinder 15 so that the dominant frequency based on the characteristics of a series of systems including the casing 12 and the air layer 13 is reduced by 3 dB or more. The position, shape, etc. of 15b are determined.

Furthermore, in the first embodiment, similarly to the basic vibration reducing structure, the average value of the ventilation resistance on the surface of the plate-like member 11 on which the air layer 13 is formed exceeds 0 N · s / m ³ and 1000 N · s / m ³ or less and becomes, in addition, the sound pressure level generated in the air layer 13 by the addition of external force, for the case there is no ventilation to the plate-like member 11, a plate-like member 11, building frame 12 and the air layer 13 The shape, size and number of the through-cylinder 15 and the positions and shapes of the air layer side opening 15a and the external side opening 15b of the through-cylinder 15 are determined so that the dominant frequency based on the characteristics of the series of systems is reduced by 3 dB or more. May be.

  As described above, according to the first embodiment of the present invention, the through cylinder 15 provides a predetermined ventilation resistance and / or a predetermined sound reduction effect between the air layer 13 and the outside of the air layer 13. When the air passes through the through-cylinder 15 that brings about such an action, the spring characteristic or the damping characteristic based on the air layer 13 acts to reduce vibration. Further, such a through cylinder 15 is formed to avoid the front side surface 11a of the plate-like member 11 that is often used in an actual use environment. In the first embodiment, since the front side surface 11a of the plate-like member 11 is configured as a floor surface, the outer side opening 15a of the through-cylinder 15 is arranged avoiding such a floor surface. Therefore, the practicality of the vibration reducing structure can be enhanced. Furthermore, since the air path between the air layer 13 and the outside of the air layer 13 is simply formed by the through-cylinder 15 that is separate from the plate-like member 11 and the housing 12, a new structure is provided. The vibration reduction structure can be adopted not only for objects but also for existing structures. Therefore, the practicality of the vibration reducing structure can be enhanced. In particular, since the plate-like member 11 can be fitted into the case 12 after producing the base case 12, the through cylinder 15 is installed inside the plate-like member 11 in the state of the plate-like member 11 alone. Work becomes possible. Therefore, the through cylinder 15 can be easily installed, and the practicality of the vibration reduction structure can be enhanced.

  According to the first embodiment of the present invention, the air passes through the through-cylinder 15 that communicates between the air layer 13 and the outside of the air layer 13 and has the above-described ventilation resistance. The spring characteristics or damping characteristics based on it will act to reduce vibrations. Therefore, vibration caused by a load such as an impact can be effectively reduced.

  According to the first embodiment of the present invention, the air passes through the through cylinder 15 communicating between the air layer 13 having the characteristic of reducing the sound pressure level and the outside of the air layer 13 as described above. The spring characteristic or damping characteristic based on the air layer 13 acts to reduce vibration. Therefore, vibration caused by a load such as an impact can be effectively reduced.

[Second Embodiment]
A vibration reducing structure according to the second embodiment of the present invention will be described.
As shown in FIG. 6, the vibration reducing structure is provided with a plate-like member 21 configured as a floor member. In addition, the vibration reduction structure is provided with a casing 22 that serves as a foundation for supporting the plate-like member 21. Similar to the plate-like member 11 of the first embodiment, the plate-like member 21 is formed in a quadrangular shape, and its front side surface 21 a is arranged toward the open space in the room. 21a will be comprised as an indoor floor surface. Similar to the housing 12 of the first embodiment, the housing 22 is formed in a concave shape, and the concave housing 22 is provided with an opening 22a that opens on the open space side in the room. The plate-like member 21 is configured to be fitted into the opening 22 a of the housing 22. The back side surface 21 b of the plate-like member 21 and the bottom surface 22 b of the housing 22 are arranged with a space between each other, and between the plate-like member 21 and the housing 22, the back side surface 21 b and the housing 22 of the plate-like member 21 are arranged. An air layer 23 surrounded by the bottom surface 22b and the inner wall side surface 22c is formed. Similarly to the vibration isolating rubber 14 of the first embodiment, the anti-vibration rubber 24 is disposed on the bottom surface 22 b of the housing 22 corresponding to the corners of the plate-like member 21. It is supported. Note that the peripheral edge 21c of the plate member 21 and the inner wall side surface 22c of the housing 22 are in contact with or close to each other, and the plate member 21 is open to the housing 22 and the air layer 23 side. It is possible to move to.

  At least one through cylinder 25 is arranged inside the housing 22. A plurality of through-cylinders 25 may be arranged inside the housing 22 as long as the operation and effect according to the present invention can be obtained for the through-cylinder 25. In FIG. 6, as an example, one through cylinder 25 is arranged inside the housing 22. The through cylinder 25 communicates the air layer 23 with the outside of the air layer 23, and extends in a substantially L shape between the bottom surface 22 b of the housing 22 and the outer wall side surface 22 d of the housing 22. An air layer side opening 25 a is formed at the air layer side end of the through cylinder 25, and the air layer side opening 25 a is disposed on the bottom surface 22 b of the housing 22. In FIG. 6, as an example, the air layer side opening 25 a is arranged at the center of the bottom surface 22 b of the housing 22. Further, an external opening 25 b is formed at the external end of the through cylinder 25, and the external opening 25 b is disposed on the outer wall side surface 22 d of the housing 22.

Such venting tube 25, similarly to the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 23 of the skeleton 22 is greater than 0N · s / ^{m 3,} and 1000N · s / ^{m 3} The shape, size, and number of the through-cylinder 25 and the positions and shapes of the air layer side opening 25a and the external side opening 25b of the through-cylinder 25 are determined so as to be as follows.

  Similarly to the basic vibration reduction structure, the sound pressure level generated in the air layer 23 due to the application of external force is different from that in the case where the housing 22 is not air permeable, from the plate-like member 21, the housing 22 and the air layer 23. The shape, size and number of the through-cylinder 25 and the position and shape of the air layer side opening 25a and the external side opening 25b of the through-cylinder 25 are determined so that the dominant frequency based on the characteristics of the series of systems is reduced by 3 dB or more. It may be done.

Furthermore, like the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 23 of the skeleton 22 is greater than 0N · s / ^{m 3,} and becomes 1000N · s / ^{m 3} or less, in addition, The sound pressure level generated in the air layer 23 due to the addition of external force is the dominant frequency based on the characteristics of a series of systems composed of the plate-like member 21, the housing 22 and the air layer 23, when the housing 22 is not breathable. In other words, the shape, size, and number of the through-cylinders 25, the positions and shapes of the air layer side opening 25a and the external side opening 25b, and the like may be determined.

  According to the second embodiment of the present invention, the cylinder 25 provides a predetermined ventilation resistance and / or a predetermined sound reduction effect between the air layer 23 and the outside of the air layer 23, and the air is By passing through the through-cylinder 25 that provides such an action, the spring characteristic or the damping characteristic based on the air layer 23 acts to reduce vibration. Further, such a through cylinder 25 is formed avoiding the surface facing the front side surface 21a of the plate-like member 21 and the bottom surface 22b of the housing 22 that are often used in an actual use environment. In the second embodiment, if the front side surface 21a of the plate-like member 21 is configured as a floor surface, and the surface facing the bottom surface 22b of the housing 22 is configured as a ceiling surface, such a floor is used. The outside opening 25b of the through-cylinder 25 is disposed avoiding the surface and the ceiling surface. Therefore, the practicality of the vibration reducing structure can be enhanced. Furthermore, since the air path between the air layer 23 and the outside of the air layer 23 is simply formed by the through-cylinder 25 that is separate from the plate-like member 21 and the housing 22, a new structure is provided. The vibration reduction structure can be adopted not only for objects but also for existing structures. Therefore, the practicality of the vibration reducing structure can be enhanced. In particular, the open space is often used in an actual use environment, but the housing 22 has a large area in contact with the external space of the air layer 23 other than the open space. Therefore, the degree of freedom in design for installing the through cylinder 25 that communicates the air layer 23 with the outside of the air layer 23 is increased, and the practicality of the vibration reduction structure can be enhanced.

  According to the second embodiment of the present invention, the air passes through the through-cylinder 25 that communicates between the air layer 23 and the outside of the air layer 23 and has the above-described ventilation resistance. The spring characteristics or damping characteristics based on it will act to reduce vibrations. Therefore, vibration caused by a load such as an impact can be effectively reduced.

  According to the second embodiment of the present invention, the air passes through the communication cylinder 25 communicating between the air layer 23 having the characteristic of reducing the sound pressure level and the outside of the air layer 23 as described above. The spring characteristic or damping characteristic based on the air layer 23 acts to reduce vibration. Therefore, vibration caused by a load such as an impact can be effectively reduced.

[Third Embodiment]
A vibration reducing structure according to the third embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the third embodiment is the same as that of the vibration reduction structure of the second embodiment. The same elements as those of the second embodiment will be described using the same symbols and names as those of the second embodiment. Here, a configuration different from the first embodiment will be described.

  In the third embodiment, as shown in FIG. 7, an outer bottom surface 22 e extending in the horizontal direction so as to be separated from the housing 22 is formed on the outer wall side surface 22 d of the housing 22. At least one through cylinder 35 is arranged inside the housing 22. The through cylinder 35 communicates the air layer 23 with the outside of the air layer 23, and extends in a substantially U shape between the bottom surface 22 b of the housing 22 and the outer bottom surface 22 e of the housing 22. An air layer side opening 35 a is formed at the air layer side end of the through cylinder 35, and the air layer side opening 35 a is disposed on the bottom surface 22 b of the housing 22. As an example, the air layer side opening 35 a may be disposed at the center of the bottom surface 22 b of the housing 22. An external opening 35 b is formed at the external end of the through-cylinder 35, and the external opening 25 b is disposed on the external bottom surface 22 e of the housing 22 located outside the air layer 23.

Such venting tube 35, similarly to the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 23 of the skeleton 22 is greater than 0N · s / ^{m 3,} and 1000N · s / ^{m 3} The shape, size, and number of the through-cylinder 35 and the positions and shapes of the air layer side opening 35a and the external side opening 35b of the through-cylinder 35 are determined as follows.

  Similarly to the basic vibration reduction structure, the sound pressure level generated in the air layer 23 due to the application of external force is different from that in the case where the housing 22 is not air permeable, from the plate-like member 21, the housing 22 and the air layer 23. The shape, size and number of the through-cylinder 35 and the position and shape of the air layer side opening 35a and the external side opening 35b of the through-cylinder 35 are determined so that the dominant frequency based on the characteristics of the series of systems is reduced by 3 dB or more. It is done.

Furthermore, like the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 23 of the skeleton 22 is greater than 0N · s / ^{m 3,} and becomes 1000N · s / ^{m 3} or less, in addition, The sound pressure level generated in the air layer 23 due to the addition of external force is the dominant frequency based on the characteristics of a series of systems composed of the plate-like member 21, the housing 22 and the air layer 23, when the housing 22 is not breathable. In other words, the shape, size and number of the through-cylinders 35, the positions and shapes of the air layer side openings 35a and the external side openings 35b of the through-cylinders 35, and the like may be determined.

  As described above, according to the third embodiment of the present invention, the same effect as that of the second embodiment can be obtained.

[Fourth Embodiment]
A vibration reducing structure according to the fourth embodiment of the present invention will be described.
As shown in FIG. 8, the vibration reducing structure is provided with a plate-like member 41 configured as a floor member. The vibration reducing structure is provided with a casing 42 that serves as a foundation for supporting the plate-like member 41. Similar to the plate-like member 11 of the first embodiment, the plate-like member 41 is formed in a quadrangular shape, and its front side surface 41 a is arranged toward the open space in the room. 41a will be comprised as an indoor floor surface. Similar to the housing 12 of the first embodiment, the housing 42 is formed in a concave shape, and the concave housing 42 is provided with an opening 42a that opens on the open space side in the room. The plate-like member 41 is configured to be fitted into the opening 42 a of the housing 42. The back side surface 41 b of the plate-like member 41 and the bottom surface 42 b of the housing 42 are arranged at a distance from each other, and the back side surface 41 b of the plate-like member 41 and the housing 42 are between the plate-like member 41 and the housing 42. An air layer 43 surrounded by the bottom surface 42b and the inner wall side surface 42c is formed. Similarly to the anti-vibration rubber 14 of the first embodiment, the anti-vibration rubber 44 is disposed on the bottom surface 42 b of the housing 42 so as to correspond to the corners of the plate-like member 41. It is supported. The peripheral edge 41c of the plate member 41 and the inner wall side surface 42c of the housing 42 are in contact with or close to each other, and the plate member 41 is open to the housing 42 and the air layer 43 side. It is possible to move to.

  At least one cylinder 45 is disposed in the air layer 43. A plurality of through-cylinders 45 may be arranged in the air layer 43 as long as the operation and effect of the present invention can be obtained with respect to the through-cylinder 45. In FIG. 8, as an example, one through cylinder 45 is arranged in the air layer 43. The communication cylinder 45 communicates the air layer 43 with the outside of the air layer 43, extends in the air layer 43 in the horizontal direction, and further extends between the inner wall side surface 42 c and the outer wall side surface 42 d of the housing 42. . An air layer side opening 45 a is formed at the air layer side end of the communication cylinder 45, and the air layer side opening 45 a is disposed in the air layer 43. In FIG. 8, as an example, the air layer side opening 45 a is arranged at the center of the bottom surface 42 b of the housing 42. An external opening 45 b is formed at the external end of the through-cylinder 45, and the external opening 45 b is disposed on the outer wall side surface 42 d of the housing 42.

Such venting tube 45, similarly to the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 43 of the skeleton 42 is greater than 0N · s / ^{m 3,} and 1000N · s / ^{m 3} The shape, dimensions, and number of the through-cylinder 45 and the positions and shapes of the air layer side opening 45a and the external side opening 45b of the through-cylinder 45 are determined so as to be as follows.

  Similarly to the basic vibration reduction structure, the sound pressure level generated in the air layer 43 due to the addition of external force is different from that of the plate-like member 41, the case 42, and the air layer 43 when the case 42 has no air permeability. The shape, size and number of the through-cylinder 45 and the positions and shapes of the air layer side opening 45a and the external side opening 45b of the through-cylinder 45 are determined so that the dominant frequency based on the characteristics of the series of systems is reduced by 3 dB or more. It is done.

Furthermore, like the fundamental vibration reduction structure, the average value of the airflow resistance at the surface to form the air layer 43 of the skeleton 42 is greater than 0N · s / ^{m 3,} and becomes 1000N · s / ^{m 3} or less, in addition, The sound pressure level generated in the air layer 43 due to the addition of external force is the dominant frequency based on the characteristics of a series of systems composed of the plate-like member 41, the housing 42 and the air layer 43 when the housing 42 is not air permeable. In other words, the shape, size, and number of the through-cylinders 45, the positions and shapes of the air layer side openings 45a and the external side openings 45b of the through-cylinders 45, and the like may be determined.

  As described above, according to the fourth embodiment of the present invention, the through-cylinder 45 provides a predetermined ventilation resistance and / or a predetermined sound reduction effect between the air layer 43 and the outside of the air layer 43. When the air passes through the through-cylinder 45 that brings about such an action, the spring characteristic or the damping characteristic based on the air layer 43 acts to reduce vibration. Further, such a through cylinder 45 is formed avoiding the front side surface 41a of the plate-like member 41 that is often used in an actual use environment. For example, when the front side surface 41a of the plate-like member 41 is configured as a floor surface, the outer side opening 45b of the through-cylinder 45 is disposed avoiding such a floor surface. Therefore, the practicality of the vibration reducing structure can be enhanced. Furthermore, since the air path between the air layer 43 and the outside of the air layer 43 is simply formed by the through-cylinder 45 that is separate from the plate-like member 41 and the housing 42, a new structure is provided. The vibration reduction structure can be adopted not only for objects but also for existing structures. Therefore, the practicality of the vibration reducing structure can be enhanced. In particular, since the through-cylinder 45 only needs to be disposed in the air layer 43 that is a cavity, the through-cylinder 45 can be easily installed, and the practicality of the vibration reduction structure can be enhanced.

  According to the fourth embodiment of the present invention, the air passes through the through-cylinder 45 that communicates between the air layer 43 and the outside of the air layer 43 and has the above-described ventilation resistance. The spring characteristics or damping characteristics based on it will act to reduce vibrations. Therefore, vibration caused by a load such as an impact can be effectively reduced.

  According to the fourth embodiment of the present invention, the air passes through the communication cylinder 25 communicating between the air layer 43 having the characteristic of reducing the sound pressure level and the outside of the air layer 43 as described above. The spring characteristic or damping characteristic based on the air layer 43 acts to reduce vibration. Therefore, vibration caused by a load such as an impact can be effectively reduced.

[Fifth Embodiment]
A vibration reducing structure according to the fifth embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the fifth embodiment is the same as that of the vibration reduction structure of the first embodiment. Elements similar to those in the first embodiment will be described using the same symbols and names as those in the first embodiment. Here, a configuration different from the first embodiment will be described.

  As shown in FIG. 9, a microphone 51 is disposed as a sound detector near the air layer side opening 15 a of the cylinder 15 of the air layer 13. The microphone 51 may be disposed in the vicinity of the air layer side opening 15 a in the through cylinder 15 instead of in the vicinity of the air layer side opening 15 a of the through cylinder 15 of the air layer 13. In particular, the microphone 51 is preferably disposed at a position where vibrations of the plate-like member 11 and the housing 12 are not easily transmitted. As the sound detector, other sound pressure sensors or the like may be used instead of the microphone 51.

  Further, a speaker 52 is disposed in the vicinity of the external opening 15b of the through cylinder 15 as an output device for generating sound or vibration. The microphone 51 is electrically connected to the signal processing circuit 53, the signal processing circuit 53 is electrically connected to the amplifier 54, and the amplifier 54 is electrically connected to the speaker 52. Therefore, the microphone 51 is electrically connected to the speaker 52 via the signal processing circuit 53 and the amplifier 54. In addition to the speaker 52, an apparatus that can generate sound or vibration may be used as an output device that generates sound or vibration.

  In such a configuration, as will be described below, the speaker 52 is controlled so as to change the sound pressure level in the air layer 13 corresponding to the sound pressure level in the air layer 13 detected by the microphone 51. The

  A signal of the sound pressure level detected by the microphone 51 (hereinafter referred to as “sound pressure detection signal”) is sent to the signal processing circuit 53. Next, based on the sound pressure detection signal, the dominant frequency based on the characteristics of a series of systems including the plate-like member 11, the casing 12, and the air layer 13 is analyzed. In the fifth embodiment, the dominant frequencies of about 40 Hz and about 80 Hz are obtained by such analysis of the signal processing circuit 53. Further, based on the sound pressure detection signal, the signal processing circuit 53 detects the air detected by the microphone 51 from the sound pressure level of the air layer when the plate-like member has no air permeability at the dominant frequency obtained by the analysis. A signal (hereinafter referred to as “output signal”) is generated so that a difference obtained by subtracting the sound pressure level of the layer 13 (hereinafter referred to as “sound pressure difference”) is 3 dB or more, and a signal is generated based on the generated output signal. The processing circuit 53 applies a voltage to the speaker 52 via the amplifier 54. The sound emitted from the speaker 52 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. As a result, the plate-like member 11 and The vibration of the housing 12 will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 53 operates stably.

  As described above, according to the fifth embodiment of the present invention, in addition to the same effects as those of the first embodiment, the sound pressure level in the air layer 13 can be adjusted without being influenced by external factors. Therefore, the spring characteristic or damping characteristic based on the air layer 13 acts stably so as to reduce vibration. Further, in order to provide the above-described airflow resistance and the above-described sound reduction effect between the air layer 13 and the outside of the air layer 13, the microphone 51 is used without using a complicated structure such as providing a large number of cylinders 15 or the like. And the vibration reduction structure of this invention can be simplified using the speaker 52. FIG. With such a simple structure, the vibration reducing structure of the present invention can be easily installed by an existing structure, and the practicality of the vibration reducing structure of the present invention can be enhanced.

[Sixth Embodiment]
A vibration reducing structure according to the sixth embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the sixth embodiment is the same as that of the vibration reduction structure of the first embodiment. Elements similar to those in the first embodiment will be described using the same symbols and names as those in the first embodiment. Here, a configuration different from the first embodiment will be described.

  As shown in FIG. 10, a first vibration accelerometer 61 as a vibration detector is attached to the back side surface 11 b of the plate-like member 11, and the first vibration accelerometer 61 is an air layer of the cylinder 15. It arrange | positions in the side opening 15a vicinity. A second vibration accelerometer 62 is attached to the bottom surface 12b of the housing 12 as a vibration detector. As a vibration detector, a speedometer, a displacement meter, other vibration sensors, or the like may be used instead of the first vibration accelerometer 61 and the second vibration accelerometer 62.

  A microphone 63 is arranged as a sound detector in the vicinity of the air layer side opening 15a of the cylinder 15 of the air layer 13. Further, the microphone 63 may be disposed in the vicinity of the air layer side opening 15 a in the through cylinder 15 instead of in the vicinity of the air layer side opening 15 a of the through cylinder 15 of the air layer 13. In particular, the microphone 63 is preferably disposed at a position where vibrations of the plate-like member 11 and the housing 12 are not easily transmitted. As the sound detector, other sound pressure sensors or the like may be used instead of the microphone 63.

  A speaker 64 is disposed near the external opening 15b of the through cylinder 15 as an output device that generates sound or vibration. The first vibration accelerometer 61, the second vibration accelerometer 62, and the microphone 63 are electrically connected to a signal processing circuit 65. The signal processing circuit 65 is electrically connected to an amplifier 66. The amplifier 66 is connected to a speaker 64. And are electrically connected. Therefore, the first vibration accelerometer 61, the second vibration accelerometer 62, and the microphone 63 are electrically connected to the speaker 64 via the signal processing circuit 65 and the amplifier 66. In addition to the speaker 64, an apparatus that can generate sound or vibration may be used as an output device that generates sound or vibration.

  In such a configuration, as described below, the microphone 63 corresponds to the vibration amplitude of the plate-like member 11 and the housing 12 detected by the first vibration accelerometer 61 or the second vibration accelerometer 62. The speaker 64 is controlled so as to reduce the detected sound pressure level in the air layer 13.

  When vibration generated by the application of an external force to the plate member 11 is transmitted from the plate member 11 to the housing 12, the first vibration detection signal detected by the first vibration accelerometer 61 on the plate member 11 side is the first vibration detection signal. To the signal processing circuit 65. The sound pressure detection signal detected by the microphone 63 is sent to the signal processing circuit 65. Next, based on the sound pressure detection signal, the dominant frequency based on the characteristics of a series of systems including the plate-like member 11, the casing 12, and the air layer 13 is analyzed. In the sixth embodiment, the dominant frequencies of about 40 Hz and about 80 Hz are obtained by such analysis of the signal processing circuit 65. Furthermore, based on the first vibration detection signal, the signal processing circuit 65 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, The signal processing circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15. At this time, a signal of the sound pressure level detected by the microphone 63 (hereinafter referred to as “sound pressure evaluation signal”) is sent to the signal processing circuit 65. Next, based on the sound pressure evaluation signal, the signal processing circuit 65 determines whether or not the sound pressure difference at the above-described dominant frequency is 3 dB or more. When it is determined that the sound pressure difference is less than 3 dB, the signal processing circuit 65 changes the output signal described above so that the sound pressure difference becomes 3 dB or more based on the first vibration detection signal. Based on the changed output signal, the signal processing circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. As a result, the vibration of the housing 12 is reduced. It will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 65 operates stably.

  On the other hand, when the vibration generated by the external force applied to the housing 12 is transmitted from the housing 12 to the plate-like member 11, a vibration amplitude signal (hereinafter referred to as “below”) detected by the second vibration accelerometer 62 on the housing 12 side. The second vibration detection signal ”is sent to the signal processing circuit 65. The sound pressure detection signal detected by the microphone 63 is sent to the signal processing circuit 65. Next, based on the sound pressure detection signal, the dominant frequency based on the characteristics of a series of systems including the plate-like member 11, the casing 12, and the air layer 13 is analyzed. Furthermore, based on the second vibration detection signal, the signal processing circuit 65 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequencies (about 40 Hz and about 80 Hz) obtained by the analysis, Based on the generated output signal, the signal processing circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15. At this time, the sound pressure evaluation signal detected by the microphone 63 is sent to the signal processing circuit 65. Next, based on the sound pressure evaluation signal, the signal processing circuit 65 determines whether or not the sound pressure difference at the above-described dominant frequency is 3 dB or more. When it is determined that the sound pressure difference is less than 3 dB, the signal processing circuit 65 changes the output signal described above so that the sound pressure difference becomes 3 dB or more based on the second vibration detection signal. Based on the changed output signal, the signal processing circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 65 operates stably.

  Further, when it cannot be assumed whether the external force is applied to the plate-like member 11 or the casing 12, the first vibration detection signal detected by the first vibration accelerometer 61 and the second vibration accelerometer 62 are detected. By monitoring and comparing the second vibration detection signal and the sound pressure detection signal detected by the microphone 63, the direction in which the force is transmitted, the amount of vibration reduction, and the sound pressure level in the air layer 13 are related. Information can be obtained. Based on these pieces of information, the signal processing circuit 65 generates an output signal for reducing the sound pressure level in the air layer 13, and outputs sound from the speaker 64 based on this output signal. The sound pressure level in 13 is effectively reduced, and as a result, vibrations of the plate-like member 11 and the housing 12 are reduced.

  As described above, according to the sixth embodiment of the present invention, in addition to the same effects as those of the first embodiment, the sound pressure level in the air layer 13 can be adjusted without being affected by external factors. Therefore, the spring characteristic or damping characteristic based on the air layer 13 acts stably so as to reduce vibration. Further, in order to provide the above-described ventilation resistance and the above-described sound reduction effect between the air layer 13 and the outside of the air layer 13, the first structure can be used without using a complicated structure such as providing a large number of cylinders 15 or the like. Using the vibration accelerometer 61, the second vibration accelerometer 62, the microphone 63, and the speaker 64, the vibration reduction structure of the present invention can be simplified. With such a simple structure, the vibration reducing structure of the present invention can be easily installed by an existing structure, and the practicality of the vibration reducing structure of the present invention can be enhanced.

[Seventh Embodiment]
A vibration reducing structure according to the seventh embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the seventh embodiment is the same as that of the vibration reduction structure of the sixth embodiment. Elements similar to those in the sixth embodiment will be described using the same reference numerals and names as those in the sixth embodiment. Here, a configuration different from that of the sixth embodiment will be described.

  The vibration reduction structure according to the seventh embodiment is the same as the vibration reduction structure according to the sixth embodiment. In such a configuration, the first vibration accelerometer 61 or the second vibration accelerometer 62 detects the sound pressure level in the air layer 13 detected by the microphone 63 as described below. The speaker 64 is controlled so as to reduce the vibration amplitude of the plate-like member 11 or the casing 12.

  When vibration generated by the application of an external force to the plate member 11 is transmitted from the plate member 11 to the housing 12, the first vibration detection signal detected by the first vibration accelerometer 61 on the plate member 11 side is the first vibration detection signal. To the signal processing circuit 65. The sound pressure detection signal detected by the microphone 63 is sent to the signal processing circuit 65. Next, based on the first vibration detection signal, the dominant frequency based on the characteristics of a series of systems including the plate member 11, the casing 12 and the air layer 13 is analyzed. In the seventh embodiment, the dominant frequencies of about 40 Hz and about 80 Hz are obtained by such analysis of the signal processing circuit 65. Further, based on the sound pressure detection signal, the signal processing circuit 65 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, signal processing is performed. A circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15. At this time, a signal of vibration amplitude detected by the first vibration accelerometer 61 (hereinafter referred to as “first vibration evaluation signal”) is sent to the signal processing circuit 65. Next, based on the first vibration evaluation signal, the signal processing circuit 65 determines whether or not the sound pressure difference at the above-described dominant frequency is 3 dB or more. If it is determined that the sound pressure difference is less than 3 dB, the signal processing circuit 65 changes the output signal described above so that the sound pressure difference becomes 3 dB or more based on the sound pressure detection signal. Based on the output signal, the signal processing circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 65 operates stably.

  On the other hand, when the vibration generated by the addition of the external force to the housing 12 is transmitted from the housing 12 to the housing 11, the second vibration detection signal detected by the second vibration accelerometer 62 on the housing 12 side is subjected to signal processing. It is sent to the circuit 65. The sound pressure detection signal detected by the microphone 63 is sent to the signal processing circuit 65. Next, based on the second vibration detection signal, a dominant frequency (about 40 Hz and about 80 Hz) based on the characteristics of a series of systems including the plate-like member 11, the casing 12, and the air layer 13 is analyzed. Further, based on the sound pressure detection signal, the signal processing circuit 65 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, signal processing is performed. A circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15. At this time, a signal of vibration amplitude detected by the second vibration accelerometer 62 (hereinafter referred to as “second vibration evaluation signal”) is sent to the signal processing circuit 65. Next, based on the second vibration evaluation signal, the signal processing circuit 65 determines whether or not the sound pressure difference at the above-described dominant frequency is 3 dB or more. If it is determined that the sound pressure difference is less than 3 dB, the signal processing circuit 65 changes the output signal described above so that the sound pressure difference becomes 3 dB or more based on the sound pressure detection signal. Based on the output signal, the signal processing circuit 65 applies a voltage to the speaker 64 via the amplifier 66. The sound emitted from the speaker 64 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 65 operates stably.

  As described above, according to the seventh embodiment of the present invention, the same effect as in the sixth embodiment can be obtained.

[Eighth Embodiment]
A vibration reducing structure according to the eighth embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the eighth embodiment is the same as that of the vibration reduction structure of the first embodiment. Elements similar to those in the first embodiment will be described using the same symbols and names as those in the first embodiment. Here, a configuration different from the first embodiment will be described.

  As shown in FIG. 11, a first vibration accelerometer 71 as a vibration detector is attached to the back side surface 11 b of the plate-like member 11, and the first vibration accelerometer 71 is an air layer of the cylinder 15. It arrange | positions in the side opening 15a vicinity. A second vibration accelerometer 72 is attached to the bottom surface 12b of the housing 12 as a vibration detector. As the vibration detector, a speedometer, a displacement meter, other vibration sensors, or the like may be used instead of the first vibration accelerometer 71 and the second vibration accelerometer 72.

  A speaker 73 is disposed in the vicinity of the external opening 15b of the through cylinder 15 as an output device that generates sound or vibration. The first vibration accelerometer 71 and the second vibration accelerometer 72 are electrically connected to the signal processing circuit 74, the signal processing circuit 74 is electrically connected to the amplifier 75, and the amplifier 75 is electrically connected to the speaker 73. It is connected. Therefore, the first vibration accelerometer 71 and the second vibration accelerometer 72 are electrically connected to the speaker 73 via the signal processing circuit 74 and the amplifier 75. In addition to the speaker 73, a device that can generate sound or vibration may be used as an output device that generates sound or vibration.

  In such a configuration, the plate-like member 11 corresponding to the vibration amplitude of the plate-like member 11 and the housing 12 detected by the first vibration accelerometer 71 or the second vibration accelerometer 72, as will be described next. And the speaker 73 is controlled so that the vibration amplitude of the housing 12 is reduced.

  When vibration generated by the application of an external force to the plate member 11 is transmitted from the plate member 11 to the housing 12, the first vibration detection signal detected by the first vibration accelerometer 71 on the plate member 11 side is the first vibration detection signal. To the signal processing circuit 74. Next, based on the first vibration detection signal, the dominant frequency based on the characteristics of a series of systems including the plate member 11, the casing 12 and the air layer 13 is analyzed. In the eighth embodiment, the dominant frequencies of about 40 Hz and about 80 Hz are obtained by the analysis of the signal processing circuit 74 as described above. Further, based on the first vibration detection signal, the signal processing circuit 74 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, The signal processing circuit 74 applies a voltage to the speaker 73 via the amplifier 75. The sound emitted from the speaker 73 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 74 operates stably.

  On the other hand, when the vibration generated by the addition of the external force to the housing 12 is transmitted from the housing 12 to the plate-like member 11, the second vibration detection signal detected by the second vibration accelerometer 72 on the housing 12 side is It is sent to the signal processing circuit 74. Next, based on the second vibration detection signal, a dominant frequency (about 40 Hz and about 80 Hz) based on the characteristics of a series of systems including the plate-like member 11, the casing 12, and the air layer 13 is analyzed. Further, based on the second vibration detection signal, the signal processing circuit 74 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, The signal processing circuit 74 applies a voltage to the speaker 73 via the amplifier 75. The sound emitted from the speaker 73 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 74 operates stably.

  Further, when it cannot be assumed whether the external force is applied to the plate-like member 11 or the casing 12, the first vibration detection signal detected by the first vibration accelerometer 61 and the second vibration accelerometer 62 are detected. By monitoring and comparing the second vibration detection signal, information regarding the direction in which the force is transmitted, the amount of vibration reduction, and the sound pressure level in the air layer 13 can be obtained. Based on these information, the signal processing circuit 74 generates an output signal for reducing the sound pressure level in the air layer 13, and outputs sound from the speaker 73 based on the output signal. The sound pressure level in 13 is effectively reduced, and as a result, vibrations of the plate-like member 11 and the housing 12 are reduced.

  As described above, according to the eighth embodiment of the present invention, in addition to the same effects as those of the first embodiment, the sound pressure level in the air layer 13 can be adjusted without being affected by external factors. Therefore, the spring characteristic or damping characteristic based on the air layer 13 acts stably so as to reduce vibration. Further, in order to provide the above-described ventilation resistance and the above-described sound reduction effect between the air layer 13 and the outside of the air layer 13, the first structure can be used without using a complicated structure such as providing a large number of cylinders 15 or the like. Using the vibration accelerometer 71, the second vibration accelerometer 72, and the speaker 73, the vibration reduction structure of the present invention can be simplified. With such a simple structure, the vibration reducing structure of the present invention can be easily installed by an existing structure, and the practicality of the vibration reducing structure of the present invention can be enhanced.

[Ninth Embodiment]
A vibration reducing structure according to the ninth embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the ninth embodiment is the same as that of the vibration reduction structure of the eighth embodiment. The same elements as those in the eighth embodiment will be described using the same symbols and names as those in the eighth embodiment. Here, a configuration different from that of the eighth embodiment will be described.

  The vibration reduction structure according to the ninth embodiment is the same as the vibration reduction structure according to the eighth embodiment. In such a configuration, the plate-like member 11 corresponding to the vibration amplitude of the plate-like member 11 and the housing 12 detected by the first vibration accelerometer 71 or the second vibration accelerometer 72, as will be described next. And the speaker 73 is controlled so that the vibration amplitude of the housing 12 is reduced.

  When vibration generated by the application of an external force to the plate member 11 is transmitted from the plate member 11 to the housing 12, the first vibration detection signal detected by the first vibration accelerometer 71 on the plate member 11 side is the first vibration detection signal. To the signal processing circuit 74. Further, the second vibration detection signal detected by the second vibration accelerometer 72 on the housing 12 side is sent to the signal processing circuit 74. Next, based on the second vibration detection signal, the dominant frequency based on the characteristics of a series of systems including the plate member 11, the casing 12, and the air layer 13 is analyzed. In the ninth embodiment, the dominant frequencies of about 40 Hz and about 80 Hz are obtained by the analysis of the signal processing circuit 74 as described above. Further, based on the first vibration detection signal, the signal processing circuit 74 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, The signal processing circuit 74 applies a voltage to the speaker 73 via the amplifier 75. The sound emitted from the speaker 73 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 74 operates stably.

  On the other hand, when the vibration generated by the addition of the external force to the housing 12 is transmitted from the housing 12 to the plate-like member 11, the second vibration detection signal detected by the second vibration accelerometer 72 on the housing 12 side is It is sent to the signal processing circuit 74. Further, the first vibration detection signal detected by the first vibration accelerometer 71 on the plate-like member 11 side is sent to the signal processing circuit 74. Next, based on the first vibration detection signal, a dominant frequency (about 40 Hz and about 80 Hz) based on the characteristics of a series of systems including the plate-like member 11, the casing 12, and the air layer 13 is analyzed. Further, based on the second vibration detection signal, the signal processing circuit 74 generates an output signal so that the sound pressure difference is 3 dB or more at the dominant frequency obtained by the analysis, and based on the generated output signal, The signal processing circuit 74 applies a voltage to the speaker 73 via the amplifier 75. The sound emitted from the speaker 73 by the applied voltage is sent into the air layer 13 through the through cylinder 15 and the sound pressure level in the air layer 13 is reduced. Vibration will be reduced. The sound pressure difference is preferably set as large as possible within a range where the signal processing circuit 74 operates stably.

  As described above, according to the ninth embodiment of the present invention, the same effect as in the eighth embodiment can be obtained.

[Tenth embodiment]
A vibration reducing structure according to the tenth embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the tenth embodiment is the same as that of the vibration reduction structure of the first embodiment. Elements similar to those in the first embodiment will be described using the same symbols and names as those in the first embodiment. Here, a configuration different from the first embodiment will be described.

  As shown in FIG. 12, a silencer 81 is disposed in the external opening 15 b of the through cylinder 15. The silencer 81 is attached to the peripheral edge 11 c of the plate-like member 11 corresponding to the outer side opening 15 b of the cylinder 15.

  As described above, according to the tenth embodiment of the present invention, in addition to the same effects as those of the first embodiment, the silencer 81 causes the characteristics in the air layer 13, such as acoustic resonance in the air layer 13. This can prevent the sound pressure outside the air layer 13 from increasing. Therefore, the practicality of the vibration reducing structure of the present invention can be further enhanced.

[Eleventh embodiment]
A vibration reducing structure according to the eleventh embodiment of the present invention will be described below. The basic form of the vibration reduction structure of the eleventh embodiment is the same as that of the vibration reduction structure of the first embodiment. Elements similar to those in the first embodiment will be described using the same symbols and names as those in the first embodiment. Here, a configuration different from the first embodiment will be described.

  As shown in FIG. 13, in the vibration reduction structure in the eleventh embodiment, an acoustically transparent member 91 is disposed on the peripheral edge 11 c of the plate-like member 11. The acoustically transparent member 91 covers the outer opening 15 b of the through cylinder 15 located at the peripheral edge 1 c of the plate-like member 11. The acoustically transparent member 91 has a sound insulation performance for reducing the sound pressure level by 0 dB to 2 dB in the frequency range of 30 Hz to 300 Hz. In the technical field to which the present invention belongs, such a member having only a slight sound insulation performance is called an “acoustic transparent member”. In the eleventh embodiment, as an example, the acoustically transparent member 91 is formed in a sheet shape. The acoustically transparent member 91 may be disposed on the back side surface 11 b of the plate-like member 11 instead of the peripheral edge 11 c of the plate-like member 11. Further, the acoustically transparent member 91 may be disposed inside the through-cylinder 15 instead of the front side surface 11 a of the plate-like member 11.

  As described above, according to the eleventh embodiment of the present invention, the through-cylinder 15 is blocked by the acoustically transparent member 91 having only a slight sound insulation performance. Therefore, vibration due to a load such as an impact can be effectively reduced without impairing the above-described ventilation resistance and the above-described sound reduction effect between the air layer 13 and the outside of the air layer 13. In addition, the acoustically transparent member 91 provides water resistance and dust resistance to the through-cylinder 15, and as a result, foreign matter can enter the air layer through the through-cylinder 15. Can be prevented. Therefore, the air layer open type vibration reducing structure of the present invention can be made more practical.

  Although the embodiments of the present invention have been described so far, the present invention is not limited to the above-described embodiments, and various modifications and changes can be made based on the technical idea of the present invention.

  For example, as a first modification of the present invention, the microphone 51, the speaker 52, the signal processing circuit 53, and the amplifier 54 of the fifth embodiment are the cylinder 25 of the second embodiment, the cylinder 35 of the third embodiment, Alternatively, it may be provided in the cylinder 45 of the fourth embodiment. The same effect as the fifth embodiment can be obtained.

  As a second modification of the present invention, the first vibration accelerometer 61, the second vibration accelerometer 62, the microphone 63, the speaker 64, the signal processing circuit 65, and the amplifier 66 of the sixth embodiment or the seventh embodiment are provided. The cylinder 25 may be provided in the cylinder 25 of the second embodiment, the cylinder 35 of the third embodiment, or the cylinder 45 of the fourth embodiment. In this case, the speaker 64 may be controlled in any manner of the sixth embodiment and the seventh embodiment. The same effects as those in the sixth embodiment or the seventh embodiment are obtained.

  As a third modification of the present invention, the first vibration accelerometer 71, the second vibration accelerometer 72, the speaker 73, the signal processing circuit 74, and the amplifier 75 of the eighth or ninth embodiment are the second modification. It may be provided in the through cylinder 25 of the embodiment, the through cylinder 35 of the third embodiment, or the through cylinder 45 of the fourth embodiment. The same effects as those in the eighth embodiment or the ninth embodiment can be obtained.

  As a fourth modification of the present invention, the silencer 81 of the tenth embodiment includes an external opening 25b of the through cylinder 25 of the second embodiment, an external opening 35b of the through cylinder 35 of the third embodiment, and the fourth embodiment. The outer side opening 45b of the through cylinder 45 of the embodiment and the outer side opening 15b of the through cylinder 15 of the fifth to ninth embodiments may be arranged. The same effect as in the tenth embodiment can be obtained.

  As a fifth modification of the present invention, the acoustically transparent member 91 of the eleventh embodiment includes a cylinder 25 of the second embodiment, a cylinder 35 of the third embodiment, a cylinder 45 of the fourth embodiment, And you may provide in either of the through-cylinder 15 of 5th Embodiment-10th Embodiment. The same effect as in the eleventh embodiment can be obtained.

  As a sixth modified example of the present invention, even if a load from the plate-like members 11, 21, 41 toward the housings 12, 22, 42 is applied to the peripheral portions of the plate-like members 11, 21, 41 of each embodiment. Good. With this load, vibration based on the characteristics of the plate-like members 11, 21, 41 can be further reduced.

  As a seventh modification of the present invention, the plate-like members 11, 21, 41 of each embodiment may be formed in a polygonal shape other than a rectangular shape, a circular shape, an elliptical shape, an arc shape, or the like. The same effect as each embodiment is acquired.

  As an eighth modification of the present invention, the anti-vibration rubbers 14, 24, 44 of each embodiment may be arranged at positions other than the positions corresponding to the corners of the plate-like members 11, 21, 41. , 24, 44 may be appropriately adjusted so that the plate-like members 11, 21, 41 can be supported. The same effect as each embodiment is acquired.

  As a ninth modification of the present invention, in each embodiment, the anti-vibration rubber may not be provided. In this case, as an example, the plate-like members 11, 21, 41 may be suspended in a free support state. The same effect as each embodiment is acquired.

11, 21, 41 Plate-like members 11a, 21a, 41a Front side surfaces 11b, 21b, 41b Back side surfaces 11c, 21c, 41c Peripheries 12, 22, 42 Housings 13, 23, 43 Air layers 15, 25, 35, 45 15a, 25a, 35a, 45a Air layer side opening 15b, 25b, 35b, 45b External side opening 22c Bottom surface 22d Outer wall side surface 22e External bottom surface 51, 63 Microphone 52, 64, 73 Speaker 61, 71 First vibration accelerometer 62, 72 Second vibration accelerometer 81 Silencer 91 Acoustically transparent member X, Y, Z Arrow S1 Solid line S2 Broken line W1 Solid line W2 Dash-dot line W3 Dash-dot line W4 Dotted line W5 Dash-dot line W6 Dash-dot line W7 Dash line

Claims (11)

A plate-like member arranged with the front side facing the open space side,
A housing disposed at a distance from the back side surface facing the front side surface of the plate-like member,
An air layer open type vibration reducing structure in which an air layer is formed between the plate-like member and the housing,
Comprising a cylinder that communicates between the air layer and the outside of the air layer;
The cylinder is disposed inside the plate member;
The opening located at the air layer side end of the cylinder is disposed on the back side surface of the plate-like member,
An air layer opening type vibration reducing structure in which an opening located at an outer side end of the cylinder is disposed at a peripheral edge of the plate member. A plate-like member arranged with the front side facing the open space side,
A housing disposed at a distance from the back side surface facing the front side surface of the plate-like member,
An air layer open type vibration reducing structure in which an air layer is formed between the plate-like member and the housing,
Comprising a cylinder that communicates between the air layer and the outside of the air layer;
The through-cylinder is disposed inside the housing;
The opening located at the air layer side end of the through-cylinder is disposed on the bottom surface of the housing forming the air layer,
The air layer open-type vibration reduction wherein the opening located at the outer side end of the through-cylinder is disposed on the outer wall side surface of the housing located outside the air layer or the outer bottom surface of the housing located outside the air layer Construction. A plate-like member arranged with the front side facing the open space side,
A housing disposed at a distance from the back side surface facing the front side surface of the plate-like member,
An air layer open type vibration reducing structure in which an air layer is formed between the plate-like member and the housing,
The plate-like member is movable to the open space side and the air layer side with respect to the housing,
Anti-vibration rubber is disposed between the plate member and the housing so as to support the plate member,
A through-cylinder communicating between the air layer and the outside of the air layer is provided,
An air layer open type vibration reduction structure in which the cylinder is disposed in the air layer. The average value of the airflow resistance of the surface to form the air layer in the plate-like member or the precursor is greater than 0N · s / m ^3, and so as to 1000N · s / m ³ or less, the through cylinder is formed The air layer open type vibration reducing structure according to any one of claims 1 to 3.   The sound pressure level generated in the air layer by the addition of an external force is a series of systems consisting of the plate member, the housing, and the air layer when the plate member and the housing are not breathable. The air layer open type vibration reduction structure according to any one of claims 1 to 4, wherein the through cylinder is configured to be reduced by 3 dB or more at a dominant frequency based on characteristics. A sound detector disposed in the air layer or in the through cylinder;
An output device disposed in the through-cylinder, electrically connected to the sound detector, and configured to generate sound or vibration;
6. The output device can be controlled so as to reduce the sound pressure level in the air layer corresponding to the sound pressure level in the air layer detected by the sound detector. The air layer open type vibration reducing structure according to any one of the above. A vibration detector attached to the plate-like member and / or the housing;
A sound detector disposed in the air layer or in the through cylinder;
An output device disposed in the through-cylinder, electrically connected to the vibration detector and the sound detector, and configured to generate sound or vibration;
The output device is configured to reduce a sound pressure level in the air layer detected by the sound detector in response to a vibration amplitude of the plate-like member and / or the casing detected by the vibration detector. The air layer open type vibration reducing structure according to any one of claims 1 to 5, wherein the structure is configured to control the vibration. A vibration detector attached to the plate-like member and / or the housing;
A sound detector disposed in the air layer or in the through cylinder;
An output device disposed in the through-cylinder, electrically connected to the vibration detector and the sound detector, and configured to generate sound or vibration;
The output device is adapted to reduce the vibration amplitude of the plate-like member and / or the housing detected by the vibration detector in response to the sound pressure level in the air layer detected by the sound detector. The air layer open type vibration reducing structure according to any one of claims 1 to 5, wherein the structure is configured to control the vibration. A vibration detector attached to the plate-like member and / or the housing;
An output device disposed in the through-cylinder, electrically connected to the vibration detector, and configured to generate sound or vibration;
A configuration capable of controlling the output device so as to reduce the vibration amplitude of the plate member and / or the housing corresponding to the vibration amplitude of the plate member and / or the housing detected by the vibration detector. The air layer open-type vibration reduction structure according to any one of claims 1 to 5.   The air layer open type vibration reducing structure according to any one of claims 1 to 9, wherein a silencer is attached to an opening located at an outer side end of the through-cylinder.   The acoustically transparent member having a sound insulation performance that reduces the sound pressure level by 0 dB to 2 dB in a frequency region of 30 Hz to 300 Hz is disposed in the through-cylinder. The air layer open type vibration reducing structure as described.