JP2009263864A

JP2009263864A - Vibration control device for floor vibration and floor impact sound

Info

Publication number: JP2009263864A
Application number: JP2008110786A
Authority: JP
Inventors: Shuji Ikaga; 修治伊香賀; Yuji Kaida; 優二開田; Takahiro Kachi; 孝啓可知; Yoshihisa Yamamoto; 吉久山本; Ko Uchiyama; 高内山
Original assignee: Sumitomo Riko Co Ltd
Current assignee: Sumitomo Riko Co Ltd
Priority date: 2008-04-21
Filing date: 2008-04-21
Publication date: 2009-11-12

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control device for the floor vibration and floor impact sound of a house which can advantageously reduce weight, and can converge the vibration in an early stage. SOLUTION: This vibration control device includes: a base member 11 which is either a floor 2 or a mounting member mounted on the floor 2; a mass member 20; a plurality of leaf spring members 13 and 14 for supporting the mass member 20 in a plurality of locations on the base member 11 so that the mass member 20 can relatively move in the direction of the vibration of the floor 2 with respect to the base member 11; and an elastic member 30 which is fixed to either of the base member 11 and the mass member 20, and abuts on and is separated from the other one of the base member 11 and the mass member 20 when the floor 2 is vibrated. COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、住宅の床振動および床衝撃音の制振装置に関するものである。 The present invention relates to a vibration control device for house floor vibration and floor impact sound.

住宅の床には、例えば、木材やＦＲＰ、ガラス、鋼板など殆ど減衰性を有しない材料で構成されている。この種の材料で構成された構造物は、一旦振動を開始するとその振動が収まるまでに長時間が掛かることから、その構造物に対して、種々の制振装置を取り付けて振動を抑制するようにしている。 The floor of a house is made of a material that has almost no attenuation, such as wood, FRP, glass, and steel plate. Since a structure composed of this type of material takes a long time for the vibration to settle once it starts vibration, various vibration control devices are attached to the structure to suppress the vibration. I have to.

例えば、特許文献１及び特許文献２には、橋梁や住宅等の構造物の振動を抑制するために用いられる板ばね式ダイナミックダンパが開示されている。この板ばね式ダイナミックダンパは、板ばねの一端部にマス部材（重錘）を設け、制振対象となる構造物に対して、その板ばねの他端部を固定することにより取り付けられて使用される。 For example, Patent Document 1 and Patent Document 2 disclose a leaf spring type dynamic damper used for suppressing vibration of a structure such as a bridge or a house. This leaf spring type dynamic damper is used by attaching a mass member (weight) to one end of the leaf spring and fixing the other end of the leaf spring to the structure to be controlled. Is done.

特許文献１の板ばね式ダイナミックダンパにおいては、互いに間隔をとって平行に配置される２枚以上の板ばねが用いられ、隣り合う２枚の板ばね同士を粘弾性体又は粘性体ダンパを介して固定することにより、板ばねに減衰性を持たせるようにしている。特許文献２、３に開示された板ばね式ダイナミックダンパにおいては、板ばねに対して高減衰ゴム材（ダンピング材）と拘束板（拘束材）を積層状態で固着することにより、板ばねに減衰性を持たせるようにしている。これら特許文献１〜３の板ばね式ダイナミックダンパは、構造がシンプルで、小型軽量化することができ、構造物への取り付けが簡単であるなどの点で有利なものである。
特開昭５９−１１０９３８号公報特開２００５−３５１３６６号公報特開２００４−２８１２４号公報 In the leaf spring type dynamic damper of Patent Document 1, two or more leaf springs arranged in parallel with a space between each other are used, and two adjacent leaf springs are connected to each other via a viscoelastic body or a viscous body damper. By fixing them, the leaf springs are given a damping property. In the leaf spring type dynamic damper disclosed in Patent Documents 2 and 3, a high damping rubber material (damping material) and a restraining plate (restraining material) are fixed to the leaf spring in a laminated state, thereby damping the leaf spring. I try to have sex. These leaf spring type dynamic dampers of Patent Documents 1 to 3 are advantageous in that they have a simple structure, can be reduced in size and weight, and can be easily attached to a structure.
JP 59-110938 A JP-A-2005-351366 JP 2004-28124 A

上記特許文献１の板ばね式ダイナミックダンパにおいては、隣り合う２枚の板ばね同士が粘弾性体又は粘性体ダンパを介して固定されていることから、各板ばねの一端部に設けられたマス部材（重錘）の動きは互いに同位相で振動するが、一方の板ばねに対して他方の板ばねがずれて変位し難くなり、多少のずれによって粘弾性体又は粘性体ダンパ内に剪断変形が生じるとしても、これによる減衰効果は期待できる程ではない。そのため、制振対象となる構造物の振動を早期に収束させることは困難となる。 In the leaf spring type dynamic damper disclosed in Patent Document 1, two adjacent leaf springs are fixed to each other via a viscoelastic body or a viscous body damper, so that a mass provided at one end of each leaf spring is provided. The movements of the members (weights) vibrate in the same phase, but the other leaf spring is displaced with respect to one leaf spring, making it difficult to displace, and shearing deformation into the viscoelastic body or viscous material damper due to some displacement. Even if this occurs, the attenuation effect due to this is not as expected. Therefore, it becomes difficult to quickly converge the vibration of the structure to be controlled.

一方、上記特許文献２及び３の板ばね式ダイナミックダンパのように、板ばねに対して高減衰ゴム材（ダンピング材）と拘束板（拘束材）を積層状態で固着した場合には、板ばねの充分な減衰性を確保するためには、多量の高減衰ゴム材（ダンピング材）や拘束板（拘束材）が必要となる。そのため、重量が著しく増大する傾向にあり、軽量化の点で不利となる。 On the other hand, when the high damping rubber material (damping material) and the restraining plate (restraining material) are fixed to the leaf spring in a laminated state like the leaf spring type dynamic dampers of Patent Documents 2 and 3, the leaf spring In order to ensure sufficient damping performance, a large amount of high damping rubber material (damping material) and restraining plate (restraining material) are required. Therefore, the weight tends to increase remarkably, which is disadvantageous in terms of weight reduction.

本発明は、このような事情に鑑みてなされたものであり、より有利に軽量化が可能であり、振動を早期に収束させ得るようにした、住宅の床振動および床衝撃音の制振装置を提供することを目的とする。 The present invention has been made in view of such circumstances, and is capable of reducing the weight more advantageously, and is capable of converging the vibration at an early stage. The purpose is to provide.

以下、上記課題を解決するのに適した各手段につき、必要に応じて作用効果等を付記しつつ説明する。 Hereinafter, each means suitable for solving the above-described problems will be described with additional effects and the like as necessary.

（手段１）手段１に係る床振動および床衝撃音の制振装置は、
振動体である床、または、前記振動体に取り付けられる取付部材であるベース部材と、
マス部材と、
前記マス部材を前記ベース部材に対して前記振動体の振動方向に相対移動可能となるように、前記ベース部材に対して前記マス部材を複数箇所で支持する複数の板ばね部材と、
前記ベース部材および前記マス部材のうち何れか一方に固定されると共に、前記振動体が振動した場合に前記ベース部材および前記マス部材の他方に対して当接し且つ離間する弾性部材と、
を備えることを特徴とする。 (Means 1) A vibration damping device for floor vibration and floor impact sound according to means 1 comprises:
A floor that is a vibrating body, or a base member that is a mounting member attached to the vibrating body;
A mass member;
A plurality of leaf spring members that support the mass member at a plurality of locations with respect to the base member so that the mass member can be moved relative to the base member in the vibration direction of the vibrating body;
An elastic member fixed to one of the base member and the mass member and abutting against and separating from the other of the base member and the mass member when the vibrating body vibrates;
It is characterized by providing.

手段１によれば、振動体である床が振動した場合（床に衝撃音が発生した場合を含む）に、板ばね部材の弾性力によって、マス部材が、床の振動方向と同じ方向へ振動する。特に、本手段の制振装置は、複数の板ばね部材を備えており、複数の板ばね部材によりベース部材に対してマス部材を複数箇所で支持している。従って、床が振動した場合に、マス部材が、床の振動方向と同じ方向に安定して振動することが可能となる。 According to the means 1, when the floor as a vibrating body vibrates (including the case where an impact sound is generated on the floor), the mass member vibrates in the same direction as the vibration direction of the floor by the elastic force of the leaf spring member. To do. In particular, the vibration damping device of the present means includes a plurality of leaf spring members, and supports the mass member at a plurality of locations with respect to the base member by the plurality of leaf spring members. Therefore, when the floor vibrates, the mass member can stably vibrate in the same direction as the vibration direction of the floor.

この制振装置のうちベース部材に対して振動する部位の振動によって、弾性部材は、ベース部材およびマス部材のうち弾性部材が固定されていない側の部材に対して、当接状態と離間状態とを繰り返す。つまり、弾性部材が、ベース部材およびマス部材のうち弾性部材が固定されていない側の部材に衝突する。この弾性部材の衝突により、ベース部材の振動エネルギーが効果的に吸収される。 Due to the vibration of the part that vibrates with respect to the base member in the vibration damping device, the elastic member is brought into contact with and separated from the member of the base member and mass member to which the elastic member is not fixed. repeat. That is, the elastic member collides with a member on the side of the base member and the mass member where the elastic member is not fixed. The vibration energy of the base member is effectively absorbed by the collision of the elastic member.

特に、上述したように、マス部材が床の振動方向と同じ方向に安定して振動することで、マス部材が、弾性部材との衝突に際して、有効に機能する。換言すると、マス部材の有効質量の割合が高めることができる。ここで、衝突によるベース部材の振動エネルギーの吸収効果は、マス部材の有効質量に依存する。従って、本手段によれば、マス部材の質量を低減しつつ、ベース部材の振動エネルギーを効果的に吸収することができる。 In particular, as described above, the mass member stably vibrates in the same direction as the vibration direction of the floor, so that the mass member functions effectively when it collides with the elastic member. In other words, the proportion of the effective mass of the mass member can be increased. Here, the absorption effect of the vibration energy of the base member due to the collision depends on the effective mass of the mass member. Therefore, according to this means, the vibration energy of the base member can be effectively absorbed while the mass of the mass member is reduced.

弾性部材による衝突の他にも、本手段における制振装置は、ダイナミックダンパとしても機能し得る。従って、本手段の制振装置は、衝突による制振効果に加えて、ダイナミックダンパとしての制振効果を発揮する。従って、これらの制振効果により、ベース部材の振動が早期に収束すると共に、振動ピーク値が低減する。その結果、床振動および床衝撃音を早期に収束すると共に、振動ピーク値を低減できる。このように、より有利に軽量化することが可能となり、振動体である床の振動および衝撃音を早期に収束させることが可能となる。そうすることで、上階の床の振動および音が下階へ伝達することを抑制できる。 In addition to the collision caused by the elastic member, the vibration damping device in this means can function as a dynamic damper. Therefore, the vibration damping device of this means exhibits the vibration damping effect as a dynamic damper in addition to the vibration damping effect due to the collision. Therefore, due to these damping effects, the vibration of the base member converges early and the vibration peak value is reduced. As a result, floor vibration and floor impact sound can be converged early, and the vibration peak value can be reduced. In this way, it is possible to reduce the weight more advantageously, and it is possible to quickly converge the vibration and impact sound of the floor as a vibrating body. By doing so, it is possible to suppress the vibration and sound of the upper floor from being transmitted to the lower floor.

ここで、本手段の制振装置のうちベース部材に対して振動する部位は、衝突による振動体である床の振動または衝撃音が問題となる振動数領域において、床振動と位相差を生じる固有振動数、好ましくは床の固有振動数より小さい固有振動数を有するようにチューニングされているとよい。本手段の制振装置のうちベース部材に対して振動する部位（以下、「制振装置の振動部位」という）における周波数特性は、この制振装置の振動部位の固有振動数付近における位相差が９０°となり、当該固有振動数より大きな周波数における位相差は１８０°に近づくように変化し、逆に当該固有振動数より小さな周波数における位相差は０°に近づくように変化する。従って、上記のように固有振動数をチューニングすることで、制振装置の振動部位と振動体である床との位相差が９０°付近から１８０°までの位相差となる。このようにすれば、振動体である床が振動した際に、制振装置の振動部位と振動体である床とが逆位相に近い位相で振動することにより相対変位する。従って、弾性部材による衝突を確実に繰り返すように動作する。 Here, in the vibration damping device of the present means, the portion that vibrates with respect to the base member has a characteristic that causes a phase difference with floor vibration in a frequency region where vibration of the floor, which is a vibrating body due to collision, or impact noise is a problem. It may be tuned to have a natural frequency that is less than the natural frequency, preferably the floor natural frequency. The frequency characteristics of a part that vibrates with respect to the base member (hereinafter referred to as “vibration part of the vibration damping device”) of the vibration damping device of the present means has a phase difference near the natural frequency of the vibration part of the vibration damping device. The phase difference at a frequency larger than the natural frequency changes so as to approach 180 °, and conversely, the phase difference at a frequency smaller than the natural frequency changes so as to approach 0 °. Therefore, by tuning the natural frequency as described above, the phase difference between the vibration part of the vibration damping device and the floor as the vibrating body becomes a phase difference from around 90 ° to 180 °. In this way, when the floor that is the vibrating body vibrates, the vibration part of the vibration damping device and the floor that is the vibrating body vibrate at a phase close to the opposite phase, thereby causing relative displacement. Therefore, it operates to reliably repeat the collision by the elastic member.

（手段２）手段１の床振動および床衝撃音の制振装置において、前記板ばね部材は、前記マス部材の支持位置と前記ベース部材の支持位置との間に１以上の屈曲箇所を有するように形成されているとよい。 (Means 2) In the floor vibration and floor impact sound damping device of means 1, the leaf spring member has one or more bent portions between the support position of the mass member and the support position of the base member. It is good to be formed.

ここで、耐久性を維持するために、板ばね部材の板厚は大きい方が好ましい。しかし、板ばね部材の板厚が大きいと、板ばね部材の剛性が高くなってしまう。板ばね部材の剛性が高いと、本手段の制振装置の振動部位の固有振動数が大きくなる。本手段の制振対象である床の振動は、例えば１００Ｈｚ以下の低い周波数帯である。耐久性を確保するために、板ばね部材の板厚を大きくするのみでは、本手段の制振装置の振動部位の固有振動数を目的の範囲にチューニングすることが容易ではない。制振装置の振動部位の固有振動数を小さくするためには、板ばね部材のばね定数を小さくすることと、マス部材の質量を大きくすることにより達成できる。ただし、マス部材の質量を大きくすることは、軽量化に反するため、適切ではない。そこで、本手段のように、板ばね部材に屈曲箇所を設けることで、当該屈曲箇所が変形しやすい箇所となる。つまり、本手段によれば、板ばね部材のばね定数を小さくすることが容易となる。 Here, in order to maintain durability, it is preferable that the plate spring member has a large plate thickness. However, if the plate thickness of the leaf spring member is large, the rigidity of the leaf spring member is increased. If the rigidity of the leaf spring member is high, the natural frequency of the vibration part of the vibration damping device of this means increases. The vibration of the floor which is the vibration suppression target of this means is a low frequency band of, for example, 100 Hz or less. In order to ensure durability, it is not easy to tune the natural frequency of the vibration part of the vibration damping device of this means to the target range only by increasing the plate thickness of the leaf spring member. In order to reduce the natural frequency of the vibration part of the vibration damping device, it can be achieved by reducing the spring constant of the leaf spring member and increasing the mass of the mass member. However, it is not appropriate to increase the mass of the mass member because it is contrary to weight reduction. Then, like this means, by providing a bent part in the leaf spring member, the bent part becomes a part that is easily deformed. That is, according to this means, it is easy to reduce the spring constant of the leaf spring member.

（手段３）手段２の床振動および床衝撃音の制振装置において、前記板ばね部材は、階段状を含むように形成してもよい。 (Means 3) In the vibration damping device for floor vibration and floor impact sound of means 2, the leaf spring member may be formed to include a stepped shape.

板ばね部材は、階段状であるため、少なくとも２以上の屈曲箇所を有することになる。そして、板ばね部材を階段状に形成することは、曲げプレス加工により比較的容易にできる。従って、本手段によれば、容易に形成でき、且つ、板ばね部材のばね定数を確実に小さくできる。なお、板ばね部材のばね定数の微調整は、板ばね部材の板幅により行うことができる。従って、板ばね部材の基本形状（屈曲箇所など）を変更することなく、ばね定数の微調整を非常に容易に行うことができる。 Since the leaf spring member has a step shape, it has at least two or more bent portions. And it is comparatively easy to form a leaf | plate spring member in step shape by bending press work. Therefore, according to this means, it can form easily and the spring constant of a leaf | plate spring member can be made small reliably. The fine adjustment of the spring constant of the leaf spring member can be performed by the leaf width of the leaf spring member. Therefore, fine adjustment of the spring constant can be performed very easily without changing the basic shape (such as a bent portion) of the leaf spring member.

（手段４）手段１〜３の何れかの床振動および床衝撃音の制振装置において、前記板ばね部材は、前記マス部材の支持位置と前記ベース部材の支持位置との間に、湾曲部を有するように形成してもよい。 (Means 4) In the floor vibration and floor impact sound damping device according to any one of the means 1 to 3, the leaf spring member has a bending portion between a support position of the mass member and a support position of the base member. You may form so that it may have.

階段状でなく、湾曲部を有する場合であっても、板ばね部材のばね定数を小さくすることができる。そして、板ばね部材に湾曲部を形成することは、プレス加工により比較的容易にできる。従って、本手段によれば、容易に形成でき、且つ、板ばね部材のばね定数を確実に小さくできる。なお、板ばね部材のばね定数の微調整は、板ばね部材の板幅により行うことができる。従って、板ばね部材の基本形状（湾曲部の曲率など）を変更することなく、ばね定数の微調整を非常に容易に行うことができる。 The spring constant of the leaf spring member can be reduced even when it has a curved portion instead of a stepped shape. And it is comparatively easy to form a curved part in a leaf | plate spring member by press work. Therefore, according to this means, it can form easily and the spring constant of a leaf | plate spring member can be made small reliably. The fine adjustment of the spring constant of the leaf spring member can be performed by the leaf width of the leaf spring member. Therefore, fine adjustment of the spring constant can be performed very easily without changing the basic shape of the leaf spring member (such as the curvature of the curved portion).

（手段５）手段４の床振動および床衝撃音の制振装置において、前記板ばね部材は、Ｓ字状を含むように形成するとよい。 (Means 5) In the floor vibration and floor impact sound damping device of means 4, the leaf spring member may be formed to include an S-shape.

湾曲部が１か所では、板ばね部材のばね定数を小さくするには限界がある。そこで、Ｓ字状、すなわち、湾曲部が少なくとも２か所有する形状とすることで、確実に、板ばね部材のばね定数を小さくできる。 There is a limit to reducing the spring constant of the leaf spring member at one bending portion. Therefore, the spring constant of the leaf spring member can be reliably reduced by forming an S shape, that is, a shape having at least two curved portions.

（手段６）手段１〜５の何れかの床振動および床衝撃音の制振装置において、それぞれの前記板ばね部材は、同一形状に形成されているとよい。 (Means 6) In the floor vibration and floor impact sound damping device according to any one of the means 1 to 5, the leaf spring members may be formed in the same shape.

手段６によれば、複数の板ばね部材を同一形状に形成することで、マス部材を床の振動方向と同じ方向に安定して振動させることができる。その結果、マス部材の有効質量の割合が高めることができる。 According to the means 6, by forming the plurality of leaf spring members in the same shape, the mass member can be stably vibrated in the same direction as the vibration direction of the floor. As a result, the ratio of the effective mass of the mass member can be increased.

（手段７）手段１〜６の何れかの床振動および床衝撃音の制振装置において、それぞれの前記板ばね部材は、同一のばね定数に設定されているとよい。 (Means 7) In the floor vibration and floor impact sound damping device according to any one of the means 1 to 6, the leaf spring members may be set to the same spring constant.

手段７によれば、マス部材を床の振動方向と同じ方向に安定して振動させることができる。その結果、マス部材の有効質量の割合が高めることができる。 According to the means 7, the mass member can be stably vibrated in the same direction as the vibration direction of the floor. As a result, the ratio of the effective mass of the mass member can be increased.

（手段８）手段１〜７の何れかの床振動および床衝撃音の制振装置において、前記マス部材の重心と全ての前記板ばね部材の弾性中心とを結ぶ直線が、前記振動体の主振動方向に一致するように設定されているとよい。 (Means 8) In the floor vibration and floor impact sound damping device according to any one of the means 1 to 7, a straight line connecting the center of gravity of the mass member and the elastic center of all the leaf spring members is the main body of the vibrator. It is good to set so that it may correspond to a vibration direction.

手段８によれば、確実に、マス部材を床の振動方向と同じ方向に安定して振動させることができる。その結果、マス部材の有効質量の割合が高めることができる。 According to the means 8, the mass member can be reliably vibrated in the same direction as the vibration direction of the floor. As a result, the ratio of the effective mass of the mass member can be increased.

（手段９）手段８の床振動および床衝撃音の制振装置において、前記弾性部材のうち前記ベース部材および前記マス部材の他方との当接平面の図心が、前記マス部材の重心と前記弾性中心とを結ぶ直線上に位置するように設定されているとよい。 (Means 9) In the vibration damping device for floor vibration and floor impact sound of means 8, the centroid of the contact plane of the elastic member with the other of the base member and the mass member is the center of gravity of the mass member and the mass member. It is good to set so that it may be located on the straight line which connects an elastic center.

手段９によれば、より確実に、マス部材を床の振動方向と同じ方向に安定して振動させることができる。その結果、マス部材の有効質量の割合が高めることができる。なお、図心とは、平面における重心に相当する点である。 According to the means 9, the mass member can be more reliably vibrated stably in the same direction as the vibration direction of the floor. As a result, the ratio of the effective mass of the mass member can be increased. The centroid is a point corresponding to the center of gravity in the plane.

（手段１０）手段１〜９の何れかの床振動および床衝撃音の制振装置において、
それぞれの前記板ばね部材は、前記取付部材と一体的に形成されており、
前記弾性部材は、前記取付部材および前記マス部材のうち何れか一方に固定されると共に、前記振動体が振動した場合に前記取付部材および前記マス部材の他方に対して当接し且つ離間するようにするとよい。 (Means 10) In the floor vibration and floor impact sound damping device according to any one of the means 1 to 9,
Each of the leaf spring members is formed integrally with the mounting member,
The elastic member is fixed to one of the attachment member and the mass member, and contacts and separates from the other of the attachment member and the mass member when the vibrating body vibrates. Good.

仮に、板ばね部材がベース部材と別体に取り付けられており、弾性部材がマス部材に固定されている場合には、マス部材のうち弾性部材が固定される位置とベース部材との離間距離を、高精度にすることが容易ではない。例えば、ベース部材のうち弾性部材が当接する位置の形状や表面粗さなどが異なると、当該離間距離が変化するおそれがある。これに対して、本手段のように、それぞれの板ばね部材と取付部材とが一体的に形成されている場合には、取付部材とマス部材との離間距離は、この一体形成品の精度に依存する。つまり、この一体形成品がどこに固定される場合であっても、常に、当該離間距離の精度は、一体形成品の精度に依存する。従って、取付部材とマス部材との離間距離を高精度にすることができる。 If the leaf spring member is attached separately from the base member and the elastic member is fixed to the mass member, the separation distance between the position of the mass member where the elastic member is fixed and the base member is set. It is not easy to make high precision. For example, if the shape of the position where the elastic member abuts on the base member or the surface roughness is different, the separation distance may change. On the other hand, when each leaf spring member and the mounting member are integrally formed as in this means, the separation distance between the mounting member and the mass member depends on the accuracy of the integrally formed product. Dependent. That is, no matter where the integrally formed product is fixed, the accuracy of the separation distance always depends on the accuracy of the integrally formed product. Therefore, the separation distance between the mounting member and the mass member can be made highly accurate.

（手段１１）手段１〜１０の何れかの床振動および床衝撃音の制振装置において、
前記板ばね部材は、前記弾性部材を間に挟むように配置された一対からなり、
それぞれの前記板ばね部材により前記マス部材が支持される複数の支持位置と、それぞれの前記板ばね部材により前記ベース部材が支持される複数の支持位置とが直線状に位置するように設定されているとよい。 (Means 11) In the floor vibration and floor impact sound damping device of any one of means 1 to 10,
The leaf spring member consists of a pair arranged so as to sandwich the elastic member therebetween,
A plurality of support positions where the mass members are supported by the plate spring members and a plurality of support positions where the base member is supported by the plate spring members are set linearly. It is good to be.

手段１１によれば、制振装置における、マス部材側の複数の支持位置とベース部材側の複数の支持位置とを結ぶ直線に直交する方向の幅が、小さくできる。従って、床下などの狭いスペースに、本手段の制振装置を設置することが可能となる。 According to the means 11, the width in the direction orthogonal to the straight line connecting the plurality of support positions on the mass member side and the plurality of support positions on the base member side in the vibration damping device can be reduced. Therefore, it is possible to install the vibration damping device of this means in a narrow space such as under the floor.

（手段１２）手段１〜１１の何れかの床振動および床衝撃音の制振装置において、前記弾性部材は、粘弾性体または液体封入ダンパとしてもよい。 (Means 12) In the floor vibration and floor impact sound damping device according to any one of the means 1 to 11, the elastic member may be a viscoelastic body or a liquid-filled damper.

手段１２によれば、弾性部材がベース部材およびマス部材のうち固定されていない部材に衝突した時に、良好な減衰機能を発揮することができる。粘弾性体としては、例えば、熱可塑性エラストマ-やブチルゴムなどの合成ゴムの加硫状態または未加硫状態、あるいは、天然ゴムの加硫状態または未加硫状態などの材料を用いることができる。また、液体封入ダンパとしては、例えば、少なくとも一部に弾性変形可能な可撓部を有する容器部材と、該容器部材の内部に封入された液体とを備えたものなど、従来から公知のものを採用することができる。 According to the means 12, when the elastic member collides with an unfixed member among the base member and the mass member, a good damping function can be exhibited. As the viscoelastic body, for example, a material such as a vulcanized state or an unvulcanized state of a synthetic rubber such as thermoplastic elastomer or butyl rubber, or a vulcanized state or an unvulcanized state of natural rubber can be used. In addition, as the liquid-filled damper, for example, a conventionally known one including a container member having a flexible part that can be elastically deformed at least in part and a liquid sealed inside the container member is used. Can be adopted.

以下、本発明の床振動および床衝撃音の制振装置を具体化した実施形態について図面を参照しつつ説明する。 DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of a floor vibration and floor impact sound damping device according to the invention will be described with reference to the drawings.

＜第一実施形態＞
第一実施形態の床振動および床衝撃音の制振装置（以下、単に「制振装置」と称する）１について、図１〜図６を参照して説明する。図１は、制振装置１を振動体である床２に取り付けた状態の正面図である。図２は、図１の右側面である。図３は、制振装置１の平面図である。図４は、制振装置１の底面図である。図５は、制振装置１の右側面図である。図６は、図５のＡ−Ａ断面図である。 <First embodiment>
A floor vibration and floor impact sound damping device (hereinafter simply referred to as a “damping device”) 1 according to the first embodiment will be described with reference to FIGS. FIG. 1 is a front view of a state in which the vibration damping device 1 is attached to a floor 2 that is a vibrating body. FIG. 2 is a right side view of FIG. FIG. 3 is a plan view of the vibration damping device 1. FIG. 4 is a bottom view of the vibration damping device 1. FIG. 5 is a right side view of the vibration damping device 1. 6 is a cross-sectional view taken along the line AA in FIG.

図１および図２に示すように、制振装置１は、住宅の床２と天井３との間であって、床根太４およびＬ字型ブラケット５を介して住宅の床２に固定されている。床根太４は、住宅の床２の下面に固定されている。Ｌ字型ブラケット５は、Ｌ字型形状をなしており、床根太４の側面に固定される鉛直方向に平行な鉛直平板部５１と、鉛直平板部５１の上端から水平方向に延びる水平平板部５２とから構成されている。水平平板部５２には、４か所の貫通ねじが形成されている。そして、制振装置１は、水平平板部５２の上面に固定されている。 As shown in FIG. 1 and FIG. 2, the vibration damping device 1 is fixed between the floor 2 and the ceiling 3 of the house and the floor 2 of the house via the floor joists 4 and the L-shaped brackets 5. Yes. The floor joists 4 are fixed to the lower surface of the floor 2 of the house. The L-shaped bracket 5 has an L-shape, and is a vertical flat plate portion 51 that is fixed to the side surface of the floor joist 4 and is parallel to the vertical direction, and a horizontal flat plate portion that extends in the horizontal direction from the upper end of the vertical flat plate portion 51. 52. The horizontal flat plate portion 52 has four through screws. The vibration damping device 1 is fixed to the upper surface of the horizontal flat plate portion 52.

図３〜図６に示すように、制振装置１は、支持部材１０と、マス部材２０と、弾性部材３０とから構成されている。支持部材１０は、鋼板により形成されており、ベース部１１（本発明の「ベース部材」および「取付部材」に相当する）と、保持部１２（本発明の「ベース部材」および「取付部材」に相当する）と、板ばね部１３、１４（本発明の「板ばね部材」に相当する」と、マス側取付座部１５、１６とから構成される。支持部材１０を構成する各部は、平板をプレス加工することにより、一体的に形成されている。 As shown in FIGS. 3 to 6, the vibration damping device 1 includes a support member 10, a mass member 20, and an elastic member 30. The support member 10 is formed of a steel plate, and includes a base portion 11 (corresponding to “base member” and “mounting member” of the present invention) and a holding portion 12 (“base member” and “mounting member” of the present invention). ), Leaf spring portions 13 and 14 (corresponding to the “plate spring member” of the present invention ”), and mass side mounting seat portions 15 and 16. Each portion constituting the support member 10 includes: The flat plate is integrally formed by pressing.

ベース部１１は、外形が矩形の平板状をなしている。このベース部１１には、四隅にボルト挿通孔１１ａが形成されている。このボルト挿通孔１１ａに挿通されたボルトは、Ｌ字型ブラケット５の水平平板部５２の貫通ねじに螺合される。つまり、ベース部１１は、Ｌ字型ブラケット５に固定される。 The base portion 11 has a flat plate shape with a rectangular outer shape. The base portion 11 has bolt insertion holes 11a formed at four corners. The bolt inserted into the bolt insertion hole 11 a is screwed into the through screw of the horizontal flat plate portion 52 of the L-shaped bracket 5. That is, the base portion 11 is fixed to the L-shaped bracket 5.

保持部１２は、ベース部１１の中央に形成されており、ベース部１１に対して鉛直上方に突出するように形成されている。この保持部１２の外形は、長円形をなしている。保持部１２には、中央に、図４に示すような瓢箪型の貫通孔１２ａが形成されている。この瓢箪型の貫通孔１２ａの一端側（図４の右側）は、大径の円形をなしている。この保持部１２には、弾性部材３０が固定される。 The holding part 12 is formed at the center of the base part 11 and is formed so as to protrude vertically upward with respect to the base part 11. The outer shape of the holding portion 12 is oval. The holding portion 12 is formed with a bowl-shaped through hole 12a as shown in FIG. One end side (the right side in FIG. 4) of the bowl-shaped through hole 12a has a large-diameter circle. An elastic member 30 is fixed to the holding portion 12.

板ばね部１３、１４は、弾性部材３０を挟むように一対設けられている。板ばね部１３、１４は、ベース部１１の対向する一対の外縁から、それぞれ外側で且つ直線状の反対方向に延びるように設けられている。 A pair of leaf springs 13 and 14 are provided so as to sandwich the elastic member 30. The leaf spring parts 13 and 14 are provided so as to extend from the pair of opposing outer edges of the base part 11 to the outside and in the linear opposite directions, respectively.

板ばね部１３は、細長板状の長手方向に２つの屈曲箇所を有する形状に形成されている。板ばね部１３の２つの屈曲箇所は、９０°で、相互に反対側に屈曲されている。すなわち、板ばね部１３は、何れも、階段状またはクランク状に形成されている。そして、板ばね部１３の一端の平板部分が、ベース部１１の端辺から鉛直上方に延びるように屈曲形成されている。つまり、板ばね部１３の長手方向一端は、ベース部１１の支持位置となる。一方、板ばね部１３の他端は、マス部材２０の下面に当接する位置となる。つまり、板ばね部１３の長手方向他端は、マス部材２０の支持位置となる。従って、板ばね部１３は、ベース部１１とマス部材２０との間に２つの屈曲箇所を有しており、板ばね部１３の中間平板部分が、ベース部１１の鉛直上方空間の外側であって、ベース部１１に平行に設けられている。 The leaf spring portion 13 is formed in a shape having two bent portions in the longitudinal direction of the elongated plate shape. The two bent portions of the leaf spring portion 13 are bent at 90 ° and opposite to each other. That is, each of the leaf spring portions 13 is formed in a stepped shape or a crank shape. The flat plate portion at one end of the leaf spring portion 13 is bent so as to extend vertically upward from the end side of the base portion 11. That is, one end in the longitudinal direction of the leaf spring portion 13 is a support position for the base portion 11. On the other hand, the other end of the leaf spring portion 13 is a position that abuts against the lower surface of the mass member 20. That is, the other end in the longitudinal direction of the leaf spring portion 13 is a support position for the mass member 20. Accordingly, the leaf spring portion 13 has two bent portions between the base portion 11 and the mass member 20, and the intermediate flat plate portion of the leaf spring portion 13 is outside the vertical upper space of the base portion 11. The base portion 11 is provided in parallel.

板ばね部１４は、板ばね部１３と、同一形状であって、同一材料により形成されている。つまり、板ばね部１４のばね定数は、板ばね部１３のばね定数と同一となるように設定されている。この板ばね部１４は、板ばね部１３に対して、弾性部材３０が配置される位置を中心とする対称形状に形成されている。つまり、板ばね部１４の長手方向一端は、ベース部１１のうち板ばね部１３が設けられている外縁に平行な外縁に設けられている。そして、板ばね部１４の長手方向他端は、板ばね部１３の長手方向他端の高さと同一高さに設けられている。 The leaf spring portion 14 has the same shape as the leaf spring portion 13 and is formed of the same material. That is, the spring constant of the leaf spring portion 14 is set to be the same as the spring constant of the leaf spring portion 13. The leaf spring portion 14 is formed in a symmetrical shape with respect to the leaf spring portion 13 with the position where the elastic member 30 is disposed as the center. That is, one end in the longitudinal direction of the leaf spring portion 14 is provided on the outer edge parallel to the outer edge of the base portion 11 where the leaf spring portion 13 is provided. The other end in the longitudinal direction of the leaf spring portion 14 is provided at the same height as the other end in the longitudinal direction of the leaf spring portion 13.

一方のマス側取付座部１５は、ほぼ正方形の板状に形成されており、一方の板ばね部１３の長手方向他端から、ベース部１１から離れる側に且つベース部１１に平行となるように設けられている。このマス側取付座部１５には、ボルト挿通孔が設けられている。また、他方のマス側取付座部１６は、一方のマス側取付座部１５と同一形状に形成されており、他方の板ばね部１４の長手方向他端から、ベース部１１から離れる側に且つベース部１１に平行となるように設けられている。つまり、一対のマス側取付座部１５、１６は、同一平面上に位置している。 One mass-side mounting seat portion 15 is formed in a substantially square plate shape, and is parallel to the base portion 11 on the side away from the base portion 11 from the other longitudinal end of the one leaf spring portion 13. Is provided. The mass side mounting seat portion 15 is provided with a bolt insertion hole. Further, the other mass side mounting seat portion 16 is formed in the same shape as the one mass side mounting seat portion 15, on the side away from the base portion 11 from the other longitudinal end of the other leaf spring portion 14 and It is provided so as to be parallel to the base portion 11. That is, the pair of mass side mounting seat portions 15 and 16 are located on the same plane.

マス部材２０は、鉄系金属により所定の質量を有するようにして直方体状に形成されている。このマス部材２０の下面には、両端側に雌ねじが形成されている。そして、マス部材２０は、一対のマス側取付座部１５、１６の上面に配置され、ボルトによりマス側取付座部１５、１６に固定されている。つまり、マス部材２０は、ベース部１１に対して、床２の振動方向（鉛直方向）に相対移動可能となるように、ベース部１１に対して一対の板ばね部材１３、１４により複数箇所で支持されている。マス部材２０がベース部１１に対して、床２の振動方向に相対移動可能となるようにするために、マス部材２０の重心Ｇ１と一対の板ばね部１３、１４の弾性中心Ｇ２とを結ぶ直線が、床２の振動方向に一致するように設定されている。さらに、このマス部材２０と板ばね部１３、１４のばね定数とによって得られる固有振動数は、床２の固有振動数よりも小さくなるようにチューニングされている。 The mass member 20 is formed in a rectangular parallelepiped shape so as to have a predetermined mass by an iron-based metal. On the lower surface of the mass member 20, internal threads are formed on both end sides. The mass member 20 is disposed on the upper surfaces of the pair of mass side mounting seat portions 15 and 16 and is fixed to the mass side mounting seat portions 15 and 16 with bolts. That is, the mass member 20 can be moved relative to the base portion 11 in the vibration direction (vertical direction) of the floor 2 at a plurality of locations by the pair of leaf spring members 13 and 14 with respect to the base portion 11. It is supported. In order to allow the mass member 20 to move relative to the base portion 11 in the vibration direction of the floor 2, the center of gravity G 1 of the mass member 20 and the elastic center G 2 of the pair of leaf spring portions 13 and 14 are connected. The straight line is set to coincide with the vibration direction of the floor 2. Further, the natural frequency obtained by the mass member 20 and the spring constants of the leaf spring portions 13 and 14 is tuned to be smaller than the natural frequency of the floor 2.

弾性部材３０は、ゴム（粘弾性体）からなり、保持部１２に固定されると共に、床２が振動した場合にマス部材２０の下面に対して当接し且つ離間する。具体的には、弾性部材３０は、衝突本体部３１と、係合ストッパ部３２とから構成される。衝突本体部３１は、円錐台形状に形成されている。この端面間距離は、保持部１２の上面と、床２が振動していない状態におけるマス部材２０の下面との離間距離にほぼ等しくされている。係合ストッパ部３２は、衝突本体部３１の大径側端面に設けられ、茸状に形成されている。この係合ストッパ部３２の首部３２ａの直径は、保持部１２の瓢箪型の貫通孔１２ａの幅細側の幅より僅かに小さくされている。また、係合ストッパ部３２の先端大径突起部３２ｂの高さは、保持部１２の下面とベース部１１の下面との離間距離とほぼ等しく形成されている。この係合ストッパ部３２の先端大径突起部３２ｂの直径は、瓢箪型の貫通孔１２ａの大径円形の直径より小さく、かつ、貫通孔１２ａの幅細側の幅より大きくされている。 The elastic member 30 is made of rubber (viscoelastic body), is fixed to the holding portion 12, and abuts against and separates from the lower surface of the mass member 20 when the floor 2 vibrates. Specifically, the elastic member 30 includes a collision main body portion 31 and an engagement stopper portion 32. The collision main body 31 is formed in a truncated cone shape. The distance between the end faces is substantially equal to the separation distance between the upper surface of the holding portion 12 and the lower surface of the mass member 20 when the floor 2 is not vibrating. The engagement stopper portion 32 is provided on the large-diameter side end surface of the collision main body portion 31 and is formed in a bowl shape. The diameter of the neck portion 32 a of the engagement stopper portion 32 is slightly smaller than the width of the narrow side of the saddle-shaped through hole 12 a of the holding portion 12. Further, the height of the tip large-diameter protrusion 32 b of the engagement stopper portion 32 is formed to be approximately equal to the separation distance between the lower surface of the holding portion 12 and the lower surface of the base portion 11. The diameter of the tip large-diameter protrusion 32b of the engagement stopper 32 is smaller than the diameter of the large-diameter circle of the bowl-shaped through hole 12a and larger than the width of the narrow side of the through-hole 12a.

このように形成される弾性部材３０は、以下のようにして、保持部１２に固定される。まず、衝突本体部３１が、マス部材２０側に位置するようにして、係合ストッパ部３２の先端大径突起部３２ｂを保持部１２の瓢箪型の貫通孔１２ａの大径円形に挿通する。続いて、係合ストッパ部３２の首部３２ａが、瓢箪型の貫通孔１２ａの幅細側にスライドさせる。このとき、弾性部材３０の衝突本体部３１と、係合ストッパ部３２の先端大径突起部３２ｂとにより、保持部１２が挟まれる。さらに、衝突本体部３１の先端は、初期状態（床２が振動していない状態）において、マス部材２０の下面に当接している状態としても、マス部材２０の下面から僅かに離間している状態としてもよい。また、係合ストッパ部３２の先端大径突起部３２ｂは、保持部１２とＬ字型フランジ部５の水平平板部５２の上面とにより僅かに押圧された状態で挟まれている。このようにして、弾性部材３０が保持部１２に固定される。 The elastic member 30 formed in this way is fixed to the holding part 12 as follows. First, the distal end large-diameter protrusion 32b of the engagement stopper portion 32 is inserted into the large-diameter circle of the saddle-shaped through hole 12a of the holding portion 12 so that the collision main body portion 31 is positioned on the mass member 20 side. Subsequently, the neck portion 32a of the engagement stopper portion 32 is slid to the narrow side of the bowl-shaped through hole 12a. At this time, the holding portion 12 is sandwiched between the collision main body portion 31 of the elastic member 30 and the distal end large-diameter projection portion 32 b of the engagement stopper portion 32. Further, the tip of the collision main body 31 is slightly separated from the lower surface of the mass member 20 even in a state where it is in contact with the lower surface of the mass member 20 in the initial state (the state where the floor 2 is not vibrating). It is good also as a state. Further, the distal end large-diameter protruding portion 32 b of the engagement stopper portion 32 is sandwiched between the holding portion 12 and the upper surface of the horizontal flat plate portion 52 of the L-shaped flange portion 5 in a slightly pressed state. In this way, the elastic member 30 is fixed to the holding portion 12.

このとき、弾性部材３０の衝突本体部３１とマス部材２０の下面との当接し得る平面（本実施形態では円形）の図心は、マス部材２０の重心Ｇ１と一対の板ばね部１３、１４の弾性中心Ｇ２とを結ぶ直線上に位置するように設定されている。 At this time, the centroid of the flat surface (circular in this embodiment) where the collision main body portion 31 of the elastic member 30 and the lower surface of the mass member 20 can contact each other is the center of gravity G1 of the mass member 20 and the pair of leaf spring portions 13 and 14. It is set so as to be positioned on a straight line connecting the elastic center G2.

制振装置１を以上のように構成することにより、以下のように動作する。床２が振動した場合（床２に衝撃音が発生した場合を含む）に、板ばね部１３、１４の弾性力によって、マス部材２０が、床２の振動方向と同じ方向へ振動する。 By configuring the vibration damping device 1 as described above, it operates as follows. When the floor 2 vibrates (including a case where an impact sound is generated on the floor 2), the mass member 20 vibrates in the same direction as the vibration direction of the floor 2 by the elastic force of the leaf spring portions 13 and 14.

特に、制振装置１は、２つの板ばね部１３、１４を備えており、２つの板ばね部１３、１４によりベース部１１に対してマス部材２０を複数箇所で支持している。２つの板ばね部１３、１４は、同一形状に形成され、且つ、同一のばね定数に設定されている。さらに、マス部材２０の重心Ｇ１と２つの板ばね部１３、１４の弾性中心Ｇ２とを結ぶ直線が、床２の振動方向に一致するように設定されている。従って、床２が振動した場合に、マス部材２０が、床２の振動方向と同じ方向に安定して振動することが可能となる。さらに加えて、弾性部材３０の衝突本体部３１とマス部材２０の下面との当接し得る平面の図心が、マス部材２０の重心Ｇ１と一対の板ばね部１３、１４の弾性中心Ｇ２とを結ぶ直線上に位置するように設定されていることにより、より確実に、マス部材２０を床２の振動方向と同じ方向に安定して振動させることができる。 In particular, the vibration damping device 1 includes two leaf spring portions 13 and 14, and the mass member 20 is supported at a plurality of locations with respect to the base portion 11 by the two leaf spring portions 13 and 14. The two leaf springs 13 and 14 are formed in the same shape and set to the same spring constant. Further, a straight line connecting the center of gravity G1 of the mass member 20 and the elastic center G2 of the two leaf spring portions 13 and 14 is set to coincide with the vibration direction of the floor 2. Therefore, when the floor 2 vibrates, the mass member 20 can stably vibrate in the same direction as the vibration direction of the floor 2. In addition, the plane centroid at which the collision main body portion 31 of the elastic member 30 and the lower surface of the mass member 20 can contact each other includes the center of gravity G1 of the mass member 20 and the elastic center G2 of the pair of leaf spring portions 13 and 14. The mass member 20 can be stably vibrated in the same direction as the vibration direction of the floor 2 by being set so as to be positioned on the connecting straight line.

そして、ベース部１１に対するマス部材２０の振動によって、弾性部材３０は、マス部材２０に対して当接状態と離間状態とを繰り返す。つまり、弾性部材３０が、マス部材２０に衝突する。この弾性部材３０がマス部材２０に衝突することにより、ベース部１１、ひいては、ベース部１１が固定されている床２の振動エネルギーが効果的に吸収される。 Then, due to the vibration of the mass member 20 with respect to the base portion 11, the elastic member 30 repeats the contact state and the separation state with respect to the mass member 20. That is, the elastic member 30 collides with the mass member 20. When the elastic member 30 collides with the mass member 20, the vibration energy of the base portion 11, and thus the floor 2 to which the base portion 11 is fixed is effectively absorbed.

特に、上述したように、マス部材２０が床２の振動方向と同じ方向に安定して振動することで、マス部材２０が、弾性部材３０との衝突に際して、有効に機能する。つまり、マス部材２０の有効質量（振動エネルギー吸収に寄与する質量）の割合が高めることができる。特に、上述したように設定することで、マス部材２０の振動方向が、床２の振動方向にほぼ完全に一致させることができるため、マス部材２０の有効質量が１００％に近くなる。 In particular, as described above, the mass member 20 stably vibrates in the same direction as the vibration direction of the floor 2, so that the mass member 20 functions effectively when it collides with the elastic member 30. That is, the ratio of the effective mass (mass that contributes to vibration energy absorption) of the mass member 20 can be increased. In particular, by setting as described above, the vibration direction of the mass member 20 can be almost completely matched with the vibration direction of the floor 2, so that the effective mass of the mass member 20 is close to 100%.

ここで、衝突によるベース部材の振動エネルギーの吸収効果は、マス部材２０の有効質量に依存する。つまり、マス部材２０全体の質量に対するマス部材２０の有効質量の割合が大きいほど、マス部材２０の質量を小さくしたとしても、振動エネルギーの吸収効果が高くなる。従って、本実施形態の制振装置１によれば、マス部材２０の質量を低減しつつ、床２の振動エネルギーを効果的に吸収することができる。
弾性部材３０による衝突の他にも、本実施形態における制振装置１は、ダイナミックダンパとしても機能し得る。従って、制振装置１は、衝突による制振効果に加えて、ダイナミックダンパとしての制振効果を発揮する。従って、これらの制振効果により、床の振動が早期に収束すると共に、振動ピーク値が低減する。その結果、床振動および床衝撃音を早期に収束すると共に、振動ピーク値を低減できる。このように、より有利に軽量化することが可能となり、振動体である床の振動および衝撃音を早期に収束させることが可能となる。そうすることで、上階の床の振動および音が下階へ伝達することを抑制できる。 Here, the absorption effect of the vibration energy of the base member due to the collision depends on the effective mass of the mass member 20. That is, as the ratio of the effective mass of the mass member 20 to the mass of the entire mass member 20 increases, the vibration energy absorption effect increases even if the mass of the mass member 20 is reduced. Therefore, according to the vibration damping device 1 of the present embodiment, the vibration energy of the floor 2 can be effectively absorbed while the mass of the mass member 20 is reduced.
In addition to the collision caused by the elastic member 30, the vibration damping device 1 in the present embodiment can also function as a dynamic damper. Accordingly, the vibration damping device 1 exhibits a vibration damping effect as a dynamic damper in addition to a vibration damping effect due to a collision. Therefore, due to these damping effects, floor vibrations converge early and vibration peak values are reduced. As a result, floor vibration and floor impact sound can be converged early, and the vibration peak value can be reduced. In this way, it is possible to reduce the weight more advantageously, and it is possible to quickly converge the vibration and impact sound of the floor as a vibrating body. By doing so, it is possible to suppress the vibration and sound of the upper floor from being transmitted to the lower floor.

ここで、マス部材２０と板ばね部１３、１４のばね定数とによって得られる固有振動数Ｆ１は、床２の問題となる振動数Ｆ２との位相差を生じるようにチューニングされている。制振装置１の振動部位における周波数特性は、この制振装置１の振動部位の固有振動数Ｆ１付近における位相差が９０°となり、当該固有振動数Ｆ１より大きな周波数における位相差は１８０°に近づくように変化し、逆に当該固有振動数Ｆ１より小さな周波数における位相差は０°に近づくように変化する。従って、上記のように固有振動数Ｆ１をチューニングすることで、制振装置１の振動部位と床２との位相差が生じ、好ましくは９０°付近から１８０°までの位相差となる。このようにすれば、床２が振動した際に、制振装置１の振動部位と床２とが逆位相に近い位相で振動することにより相対変位する。従って、弾性部材３０とマス部材２０との衝突を確実に繰り返すように動作する。 Here, the natural frequency F1 obtained by the mass member 20 and the spring constants of the leaf spring portions 13 and 14 is tuned so as to produce a phase difference from the frequency F2 which is a problem of the floor 2. Regarding the frequency characteristics of the vibration part of the vibration damping device 1, the phase difference near the natural frequency F1 of the vibration part of the vibration damping device 1 is 90 °, and the phase difference at a frequency larger than the natural frequency F1 approaches 180 °. Conversely, the phase difference at a frequency smaller than the natural frequency F1 changes so as to approach 0 °. Therefore, by tuning the natural frequency F1 as described above, a phase difference between the vibration part of the vibration damping device 1 and the floor 2 is generated, and preferably a phase difference from around 90 ° to 180 °. In this way, when the floor 2 vibrates, the vibration part of the vibration damping device 1 and the floor 2 vibrate at a phase close to the opposite phase, thereby causing relative displacement. Therefore, it operates so that the collision between the elastic member 30 and the mass member 20 is reliably repeated.

また、板ばね部１３、１４は、マス部材２０の支持位置とベース部１１の支持位置との間に２つの屈曲箇所を有するように形成している。つまり、板ばね部１３、１４は、階段状を含むように形成している。 Further, the leaf spring portions 13 and 14 are formed to have two bent portions between the support position of the mass member 20 and the support position of the base portion 11. That is, the leaf | plate spring parts 13 and 14 are formed so that step shape may be included.

ここで、耐久性を維持するために、板ばね部１３、１４の板厚は大きい方が好ましい。しかし、板ばね部１３、１４の板厚が大きいと、板ばね部１３、１４の剛性が高くなってしまう。板ばね部１３、１４の剛性が高いと、制振装置１の振動部位の固有振動数Ｆ１が大きくなる。上述したように、マス部材２０と板ばね部１３、１４のばね定数とによって得られる床の振動または衝撃音が問題となる振動数領域において、床振動と位相差を生じる固有振動数、好ましくは床の固有振動数より小さい固有振動数を有するようにチューニングされる必要がある。しかし、耐久性を確保するために、板ばね部１３、１４の板厚を大きくするのみでは、制振装置１の振動部位の固有振動数Ｆ１を床２の問題となる振動数Ｆ２付近にチューニングすることが容易ではない。 Here, in order to maintain durability, it is preferable that the plate spring portions 13 and 14 have a large plate thickness. However, if the plate spring portions 13 and 14 have a large plate thickness, the rigidity of the plate spring portions 13 and 14 is increased. When the rigidity of the leaf spring portions 13 and 14 is high, the natural frequency F1 of the vibration part of the vibration damping device 1 increases. As described above, in the frequency region where floor vibration or impact sound obtained by the mass member 20 and the spring constants of the leaf spring portions 13 and 14 becomes a problem, the natural frequency that causes a phase difference from the floor vibration, preferably It needs to be tuned to have a natural frequency that is smaller than the natural frequency of the floor. However, in order to ensure durability, the natural frequency F1 of the vibration part of the vibration damping device 1 is tuned to the frequency F2 in the vicinity of the floor 2 only by increasing the plate thickness of the leaf spring portions 13 and 14. Not easy to do.

制振装置１の振動部位の固有振動数Ｆ１を小さくするためには、板ばね部１３、１４のばね定数を小さくすることと、マス部材２０の質量を大きくすることにより達成できる。ただし、マス部材２０の質量を大きくすることは、軽量化に反するため、適切ではない。そこで、上記のように、板ばね部１３、１４に屈曲箇所を設けて階段状とすることで、屈曲箇所が変形しやすい箇所となる。つまり、板ばね部１３、１４のばね定数を小さくすることが容易となる。 In order to reduce the natural frequency F1 of the vibration part of the vibration damping device 1, it can be achieved by reducing the spring constants of the leaf spring portions 13 and 14 and increasing the mass of the mass member 20. However, it is not appropriate to increase the mass of the mass member 20 because it is contrary to weight reduction. Therefore, as described above, the bent portions are easily deformed by providing bent portions in the leaf spring portions 13 and 14 to form steps. That is, it becomes easy to make the spring constant of the leaf | plate spring parts 13 and 14 small.

さらに、板ばね部１３、１４を階段状に形成することは、曲げプレス加工により比較的容易にできる。なお、板ばね部１３、１４のばね定数の微調整は、板ばね部１３、１４の板幅（図４の上下方向幅）を調整することにより行うことができる。従って、板ばね部１３、１４の基本形状（屈曲箇所など）を変更することなく、板ばね部１３、１４のばね定数の微調整を非常に容易に行うことができる。 Further, the leaf spring portions 13 and 14 can be formed in a step shape relatively easily by bending press working. The fine adjustment of the spring constants of the leaf spring portions 13 and 14 can be performed by adjusting the leaf width (vertical width in FIG. 4) of the leaf spring portions 13 and 14. Therefore, fine adjustment of the spring constants of the leaf spring portions 13 and 14 can be performed very easily without changing the basic shape (such as a bent portion) of the leaf spring portions 13 and 14.

また、２つの板ばね部１３、１４は、ベース部１１と一体的に形成されており、弾性部材３０は、ベース部１１に一体的な保持部１２に固定されると共に、床２が振動した場合に弾性部材３０はマス部材２０に対して当接し且つ離間するように動作する。 The two leaf spring portions 13 and 14 are formed integrally with the base portion 11, and the elastic member 30 is fixed to the holding portion 12 integral with the base portion 11 and the floor 2 vibrates. In some cases, the elastic member 30 operates to abut against and separate from the mass member 20.

仮に、板ばね部１３、１４がベース部１１と別体に取り付けられており、弾性部材３０がマス部材２０に固定されている場合には、マス部材２０のうち弾性部材３０が固定される位置とベース部１１またはＬ字型フランジ部５の水平平板部５２との離間距離を、高精度にすることが容易ではない。しかし、本実施形態のようにすることで、ベース部１１とマス部材２０との離間距離は、ベース部１１と板ばね部１３、１４を備える一体形成品（支持部材１０）の成形精度に依存する。つまり、この一体形成品である支持部材１０がどこに固定される場合であっても、常に、当該離間距離の精度は、一体形成品である支持部材１０の成形精度に依存する。従って、ベース部１１とマス部材２０との離間距離を高精度にすることができる。 Temporarily, the leaf | plate spring parts 13 and 14 are attached separately from the base part 11, and when the elastic member 30 is being fixed to the mass member 20, the position where the elastic member 30 is fixed among the mass members 20. It is not easy to make the separation distance between the base 11 and the horizontal flat plate 52 of the L-shaped flange 5 highly accurate. However, with the present embodiment, the distance between the base portion 11 and the mass member 20 depends on the molding accuracy of the integrally formed product (support member 10) including the base portion 11 and the leaf spring portions 13 and 14. To do. That is, regardless of where the support member 10 that is an integrally formed product is fixed, the accuracy of the separation distance always depends on the molding accuracy of the support member 10 that is an integrally formed product. Therefore, the separation distance between the base portion 11 and the mass member 20 can be made highly accurate.

また、板ばね部１３、１４は、弾性部材３０を間に挟むように配置された一対からなり、２つの板ばね部材１３、１４によりマス部材２０が支持される複数の支持位置と、２つの板ばね部１３、１４によりベース部１１が支持される複数の支持位置とが直線状に位置するように設定されている。これにより、制振装置１における、マス部材２０側の複数の支持位置とベース部１１側の複数の支持位置とを結ぶ直線に直交する方向の幅が、小さくできる。従って、床下などの狭いスペースに、本実施形態の制振装置１を設置することが可能となる。 Further, the leaf spring portions 13 and 14 are a pair arranged so as to sandwich the elastic member 30 therebetween, and a plurality of support positions where the mass member 20 is supported by the two leaf spring members 13 and 14, and two The plurality of support positions where the base portion 11 is supported by the leaf spring portions 13 and 14 are set so as to be positioned linearly. Thereby, the width | variety of the direction orthogonal to the straight line which connects the some support position by the side of the mass member 20 and the some support position by the side of the base part 11 in the damping device 1 can be made small. Accordingly, the vibration damping device 1 of the present embodiment can be installed in a narrow space such as under the floor.

＜第一実施形態の変形態様＞
上記実施形態において、弾性部材３０は、ゴム（粘弾性体）を用いた。この他に、弾性部材３０は、液体封入ダンパを用いることもできる。液体封入ダンパとしては、例えば、少なくとも一部に弾性変形可能な可撓部を有する容器部材と、該容器部材の内部に封入された液体とを備えたものなど、従来から公知のものを採用することができる。 <Modification of First Embodiment>
In the above embodiment, the elastic member 30 is rubber (viscoelastic body). In addition, the elastic member 30 can use a liquid-filled damper. As the liquid-filled damper, for example, a conventionally known one such as a container member having a flexible part that can be elastically deformed at least in part and a liquid sealed inside the container member is employed. be able to.

＜第二実施形態＞
第二実施形態の床振動および床衝撃音の制振装置１００について、図７を参照して説明する。図７は、制振装置１００をＬ字型フランジ部５に固定した状態における、断面図である。なお、図７は、第一実施形態における制振装置１を示す図５のＡ−Ａ断面図に対応する。第二実施形態の制振装置１００は、第一実施形態の制振装置１に対して、支持部材１０を上下反対に取り付けたものである。 <Second embodiment>
The floor vibration and floor impact sound damping device 100 of the second embodiment will be described with reference to FIG. FIG. 7 is a cross-sectional view of the vibration damping device 100 fixed to the L-shaped flange portion 5. 7 corresponds to a cross-sectional view taken along line AA of FIG. 5 showing the vibration damping device 1 according to the first embodiment. The vibration damping device 100 of the second embodiment has a support member 10 attached upside down with respect to the vibration damping device 1 of the first embodiment.

つまり、第一実施形態におけるベース部１１の部分が、マス部材２０の下面に固定される。一方、第一実施形態におけるマス側座部１５、１６が、Ｌ字型フランジ部５の水平平板部５２に固定される。そして、弾性部材３０は、保持部１２に固定される。従って、床２が振動した場合には、弾性部材３０の先端が、Ｌ字型フランジ部５の水平平板部５２の上面に衝突する。 That is, the portion of the base portion 11 in the first embodiment is fixed to the lower surface of the mass member 20. On the other hand, the mass side seat portions 15 and 16 in the first embodiment are fixed to the horizontal flat plate portion 52 of the L-shaped flange portion 5. The elastic member 30 is fixed to the holding unit 12. Therefore, when the floor 2 vibrates, the tip of the elastic member 30 collides with the upper surface of the horizontal flat plate portion 52 of the L-shaped flange portion 5.

この場合も、第一実施形態と同様に、マス部材２０の有効質量を高めることができる。従って、高い制振効果を発揮する。ただし、第二実施形態の制振装置１００は、弾性部材３０がＬ字型フランジ部５に衝突する。そのため、第一実施形態の制振装置１に比べて、第二実施形態の制振装置１００は、弾性部材３０が固定される位置と弾性部材３０が衝突する対象物との離間距離を、高精度にすることについては劣る。その他は、第一実施形態の制振装置１と実質的に同様の効果を発揮する。 Also in this case, the effective mass of the mass member 20 can be increased as in the first embodiment. Therefore, a high vibration damping effect is exhibited. However, in the vibration damping device 100 of the second embodiment, the elastic member 30 collides with the L-shaped flange portion 5. Therefore, compared with the vibration damping device 1 of the first embodiment, the vibration damping device 100 of the second embodiment increases the separation distance between the position at which the elastic member 30 is fixed and the object on which the elastic member 30 collides. It is inferior in terms of accuracy. The other effects are substantially the same as those of the vibration damping device 1 of the first embodiment.

＜第三実施形態＞
第三実施形態の床振動および床衝撃音の制振装置２００について、図８を参照して説明する。図８は、制振装置２００の断面図である。なお、図８は、第一実施形態における制振装置１を示す図５のＡ−Ａ断面図に対応する。第三実施形態の制振装置２００は、第一実施形態の制振装置１に対して、支持部材２１０の形状が異なる。 <Third embodiment>
A floor vibration and floor impact sound damping device 200 according to a third embodiment will be described with reference to FIG. FIG. 8 is a cross-sectional view of the vibration damping device 200. FIG. 8 corresponds to the AA sectional view of FIG. 5 showing the vibration damping device 1 in the first embodiment. The vibration damping device 200 of the third embodiment is different in the shape of the support member 210 from the vibration damping device 1 of the first embodiment.

支持部材２１０は、ベース部１１と、保持部１２と、板ばね部２１３、２１４と、マス側座部１５、１６とから構成される。つまり、第三実施形態の支持部材２１０は、第一実施形態の支持部材１０に対して、板ばね部２１３、２１４のみ相違する。板ばね部２１３、２１４は、細長板状の長手方向に２つの屈曲箇所を有する。板ばね部２１３、２１４の２つの屈曲箇所は、約６０°で、相互に反対側に屈曲されている。そして、板ばね部２１３、２１４の一端の平板部分が、ベース部１１の端辺から僅かに屈曲する状態となるように設けられている。一方、板ばね部２１３、２１４の他端は、マス側座部１５、１６から僅かに屈曲する状態となるように設定されている。そして、板ばね部２１３、２１４の中間平板部分が、ベース部１１に対して直交するように設けられている。第三実施形態の制振装置２００は、第一実施形態１と同様の効果を奏する。なお、第二実施形態の制振装置１００のように、第三実施形態の制振装置２００における支持部材２１０を上下反対に取り付けることもできる。 The support member 210 includes a base portion 11, a holding portion 12, leaf spring portions 213 and 214, and mass side seat portions 15 and 16. That is, the support member 210 of the third embodiment is different from the support member 10 of the first embodiment only in the leaf spring portions 213 and 214. The leaf spring portions 213 and 214 have two bent portions in the longitudinal direction of the elongated plate shape. The two bent portions of the leaf spring portions 213 and 214 are bent at about 60 ° and opposite to each other. And the flat plate part of the end of the leaf | plate spring parts 213 and 214 is provided so that it may be in the state slightly bent from the edge of the base part 11. FIG. On the other hand, the other ends of the leaf spring portions 213 and 214 are set to be bent slightly from the mass side seat portions 15 and 16. The intermediate flat plate portions of the leaf spring portions 213 and 214 are provided so as to be orthogonal to the base portion 11. The vibration damping device 200 of the third embodiment has the same effects as those of the first embodiment 1. In addition, like the vibration damping device 100 of the second embodiment, the support member 210 in the vibration damping device 200 of the third embodiment can be attached upside down.

＜第四実施形態＞
第四実施形態の床振動および床衝撃音の制振装置３００について、図９を参照して説明する。図９は、制振装置３００の断面図である。なお、図９は、第一実施形態における制振装置１を示す図５のＡ−Ａ断面図に対応する。第四実施形態の制振装置３００は、第一実施形態の制振装置１に対して、支持部材３１０の形状が異なる。 <Fourth embodiment>
A vibration damping device 300 for floor vibration and floor impact sound according to the fourth embodiment will be described with reference to FIG. FIG. 9 is a cross-sectional view of the vibration damping device 300. 9 corresponds to a cross-sectional view taken along line AA of FIG. 5 showing the vibration damping device 1 according to the first embodiment. The vibration damping device 300 of the fourth embodiment differs from the vibration damping device 1 of the first embodiment in the shape of the support member 310.

支持部材３１０は、ベース部１１と、保持部１２と、板ばね部３１３、３１４と、マス側座部１５、１６とから構成される。つまり、第四実施形態の支持部材３１０は、第一実施形態の支持部材１０に対して、板ばね部３１３、３１４のみ相違する。板ばね部３１３、３１４は、Ｓ字状からなる湾曲部を有する。第四実施形態の制振装置３００は、第一実施形態１と同様の効果を奏する。なお、第二実施形態の制振装置１００のように、第四実施形態の制振装置３００における支持部材３１０を上下反対に取り付けることもできる。 The support member 310 includes a base portion 11, a holding portion 12, leaf spring portions 313 and 314, and mass side seat portions 15 and 16. That is, the support member 310 of the fourth embodiment differs from the support member 10 of the first embodiment only in the leaf spring portions 313 and 314. The leaf spring portions 313 and 314 have a curved portion having an S shape. The vibration damping device 300 according to the fourth embodiment has the same effects as those of the first embodiment 1. In addition, like the vibration damping device 100 of the second embodiment, the support member 310 in the vibration damping device 300 of the fourth embodiment can be attached upside down.

＜その他＞
上記実施形態においては、制振装置１をＬ字型フランジ部５に固定した。この他に、制振装置１を、床根太４または床２に直接固定してもよい。また、床２にフランジを固定して、当該フランジに制振装置を固定してもよい。 <Others>
In the above embodiment, the vibration damping device 1 is fixed to the L-shaped flange portion 5. In addition, the vibration damping device 1 may be directly fixed to the floor joists 4 or the floor 2. Further, a flange may be fixed to the floor 2 and the vibration damping device may be fixed to the flange.

制振装置１を振動体である床２に取り付けた状態の正面図である。It is a front view of the state which attached the damping device 1 to the floor 2 which is a vibrating body. 図１の右側面である。It is a right side surface of FIG. 制振装置１の平面図である。1 is a plan view of a vibration damping device 1. FIG. 制振装置１の底面図である。2 is a bottom view of the vibration damping device 1. FIG. 制振装置１の右側面図である。2 is a right side view of the vibration damping device 1. FIG. 図５のＡ−Ａ断面図である。It is AA sectional drawing of FIG. 制振装置１００をＬ字型フランジ部５に固定した状態における、断面図である。FIG. 4 is a cross-sectional view of the vibration damping device 100 fixed to the L-shaped flange portion 5. 制振装置２００の断面図である。2 is a cross-sectional view of a vibration damping device 200. FIG. 制振装置３００の断面図である。3 is a cross-sectional view of a vibration damping device 300. FIG.

Explanation of symbols

１、１００、２００、３００：制振装置
２：床、３：天井、４：床根太、５：Ｌ字型フランジ部
１０、２１０、３１０：支持部材、１１：ベース部、１１ａ：ボルト挿通孔
１２：保持部、１２ａ：瓢箪型の貫通孔
１３、１４、２１３、２１４、３１３、３１４：板ばね部
１５、１６：マス側取付座部
２０：マス部材、３０：弾性部材
３１：衝突本体部、３２：係合ストッパ部
３２ａ：首部、３２ｂ：先端大径突起部
Ｇ１：マス部材２０の重心、Ｇ２：一対の板ばね部１３、１４の弾性中心 1, 100, 200, 300: Damping device 2: Floor, 3: Ceiling, 4: Floor joist, 5: L-shaped flange portion 10, 210, 310: Support member, 11: Base portion, 11a: Bolt insertion hole 12: holding part, 12a: bowl-shaped through-holes 13, 14, 213, 214, 313, 314: leaf spring part 15, 16: mass side mounting seat part 20: mass member, 30: elastic member 31: collision body part 32: engagement stopper portion 32a: neck portion, 32b: tip large-diameter projection portion G1: center of gravity of mass member 20, G2: elastic center of a pair of leaf spring portions 13, 14

Claims

A vibration damping device for floor vibration and floor impact sound,
A floor that is a vibrating body, or a base member that is a mounting member attached to the vibrating body;
A mass member;
A plurality of leaf spring members that support the mass member at a plurality of locations with respect to the base member so that the mass member can be moved relative to the base member in the vibration direction of the vibrating body;
An elastic member fixed to one of the base member and the mass member and abutting against and separating from the other of the base member and the mass member when the vibrating body vibrates;
A floor vibration and floor impact sound damping device comprising:

2. The floor vibration and floor impact noise suppression according to claim 1, wherein the leaf spring member is formed to have one or more bent portions between a support position of the mass member and a support position of the base member. Shaker.

The floor vibration member and the floor impact sound damping device according to claim 2, wherein the leaf spring member is formed to include a stepped shape.

The floor vibration according to any one of claims 1 to 3, wherein the leaf spring member is formed to have a curved portion between a support position of the mass member and a support position of the base member. Vibration control device for floor impact sound.

The floor vibration member and the floor impact sound damping device according to claim 4, wherein the leaf spring member is formed to include an S-shape.

Each said leaf | plate spring member is a vibration suppression apparatus of the floor vibration and floor impact sound as described in any one of Claims 1-5 currently formed in the same shape.

Each said leaf | plate spring member is a damping device of the floor vibration and floor impact sound as described in any one of Claims 1-6 set to the same spring constant.

The straight line which connects the gravity center of the said mass member and the elastic center of all the said leaf | plate spring members is set so that it may correspond with the main vibration direction of the said vibrating body. Damping device for floor vibration and floor impact sound.

The centroid of a contact plane with the other of the base member and the mass member among the elastic members is set so as to be positioned on a straight line connecting the center of gravity of the mass member and the elastic center. A vibration control device for floor vibration and floor impact sound described in 1.

Each of the leaf spring members is formed integrally with the mounting member,
The elastic member is fixed to one of the attachment member and the mass member, and contacts and separates from the other of the attachment member and the mass member when the vibrating body vibrates. The floor vibration and floor impact sound damping device according to any one of 1 to 9.

The leaf spring member consists of a pair arranged so as to sandwich the elastic member therebetween,
A plurality of support positions where the mass members are supported by the plate spring members and a plurality of support positions where the base member is supported by the plate spring members are set linearly. The floor vibration and floor impact sound damping device according to any one of claims 1 to 10.

The floor vibration and floor impact sound damping device according to any one of claims 1 to 11, wherein the elastic member is a viscoelastic body or a liquid-filled damper.