JP7721063B2 - Vibration damping structure and automobile equipped with said vibration damping structure - Google Patents
Vibration damping structure and automobile equipped with said vibration damping structureInfo
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- JP7721063B2 JP7721063B2 JP2022008858A JP2022008858A JP7721063B2 JP 7721063 B2 JP7721063 B2 JP 7721063B2 JP 2022008858 A JP2022008858 A JP 2022008858A JP 2022008858 A JP2022008858 A JP 2022008858A JP 7721063 B2 JP7721063 B2 JP 7721063B2
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Description
本発明は、制振構造体及び該制振構造体を備える自動車に係り、更に詳細には、音響ブラックホール効果を利用した制振構造体及び該制振構造体を備える自動車に関する。 The present invention relates to a vibration-damping structure and a vehicle equipped with the vibration-damping structure, and more specifically to a vibration-damping structure that utilizes the acoustic black hole effect and a vehicle equipped with the vibration-damping structure.
振動や騒音の対策として、音響ブラックホール効果を利用した制振構造体を用いることが知られている。 As a countermeasure against vibration and noise, it is known to use vibration-damping structures that utilize the acoustic black hole effect.
この制振構造体は、板厚が先端に向けて減少する楔形の構造を有し、この制振構造体を伝搬する振動（波）は、先端に向かうにつれて振幅が大きくなって伝搬速度が遅くなるので、板厚が０（零）になる楔形の先端では、伝搬速度が０になり、振動が反射されないことを利用している。 This vibration-damping structure has a wedge-shaped structure in which the plate thickness decreases towards the tip. The vibrations (waves) propagating through this vibration-damping structure increase in amplitude and their propagation speed slows as they approach the tip. At the tip of the wedge, where the plate thickness becomes 0 (zero), the propagation speed becomes 0 and vibrations are not reflected.
しかしながら、先端の厚さが０になる楔形の制振構造体を実際に製造することはできず、振動の反射を完全になくすことはできないので、その反射を低減するために楔形の先端に減衰材が設けられる。 However, since it is not possible to actually manufacture a wedge-shaped vibration-damping structure with a tip that is zero thickness, and vibration reflection cannot be completely eliminated, damping material is provided at the tip of the wedge to reduce the reflection.
特許文献１には、振動エネルギーが集中する楔形の先端にポリマー膜から成る減衰材を貼り付け、振動エネルギーを減衰する弾性くさびダンパが開示されている。 Patent Document 1 discloses an elastic wedge damper that attenuates vibration energy by attaching a damping material made of a polymer film to the tip of a wedge where vibration energy is concentrated.
しかしながら、特許文献１に記載の制振構造体は、減衰材や該減衰材を貼り付ける接着剤などに樹脂が使用されており、経時劣化し易く長期に亘る耐久性が低いので、外部環境に曝され、環境変化が大きい自動車などに適用することはできない。 However, the vibration-damping structure described in Patent Document 1 uses resin for the damping material and the adhesive used to attach the damping material, which is prone to deterioration over time and has low long-term durability, making it unsuitable for use in automobiles and other vehicles that are exposed to the external environment and are subject to large environmental changes.
本発明は、このような従来技術の有する課題に鑑みてなされたものであり、その目的とするところは、経時劣化し難く長期に亘る耐久性が高い制振構造体を提供することにある。 The present invention was made in consideration of these problems with the prior art, and its purpose is to provide a vibration-damping structure that is resistant to deterioration over time and has high long-term durability.
本発明者は、上記目的を達成すべく鋭意検討を重ねた結果、制振構造体を金属製の部材のみで作製することにより、上記目的が達成できることを見出し、本発明を完成するに至った。 After extensive research to achieve the above objective, the inventor discovered that this could be achieved by constructing a vibration control structure using only metal components, leading to the completion of the present invention.
即ち、本発明の制振構造体は、少なくとも楔形部を有する金属制振板と、上記金属制振板の先端部に当接した金属板と、を備える。
そして、上記楔形部の板厚が下記式（１）を満たして変化し、上記金属板が、上記金属制振板と摩擦可能に設けられたことを特徴とする；
ｈ（ｘ） ＝ ε・ｘｎ ＋ ｈ０ ・・・式（１）
但し、式（１）中、
ｘ ： 楔形部の薄肉端からの距離（ｍｍ）
ｈ（ｘ）： 楔形部の薄肉端からの距離ｘにおける板厚（ｍｍ）
ｈ０ ： 楔形部の薄肉端の板厚（ｍｍ）
ε ： 正の定数
ｎ ： １以上の実数
That is, the vibration damping structure of the present invention comprises at least a metal vibration damping plate having a wedge-shaped portion, and a metal plate abutting against the tip end of the metal vibration damping plate.
The thickness of the wedge-shaped portion varies to satisfy the following formula (1), and the metal plate is provided so as to be able to frictionally contact the metal vibration damping plate:
h(x) = ε・x n + h 0 ...Formula (1)
However, in formula (1),
x: Distance from the thin end of the wedge (mm)
h(x): Plate thickness at distance x from the thin end of the wedge (mm)
h0 : Plate thickness of the thin end of the wedge-shaped part (mm)
ε: positive constant n: real number greater than or equal to 1
また、本発明の自動車は、上記制振構造体を備えることを特徴とする。 The automobile of the present invention is characterized by being equipped with the above-mentioned vibration damping structure.
本発明によれば、樹脂材料を用いずに、金属製の部材のみで制振構造体を作製することしたため、経時劣化し難く長期に亘り耐久性が高い制振構造体を提供することができる。 According to the present invention, the vibration-damping structure is made using only metal components, without using resin materials, making it possible to provide a vibration-damping structure that is resistant to deterioration over time and has high durability over the long term.
本発明の制振構造体について詳細に説明する。
本発明の制振構造体は、金属制振板と金属板とを備える。
上記金属制振板は、板厚が自由端方向に漸減する楔形部を有し、上記金属板は、上記金属制振板の自由端先端部に金属制振板と摩擦可能に当接して設けられる。
The vibration damping structure of the present invention will now be described in detail.
The vibration damping structure of the present invention includes a metal vibration damping plate and a metal plate.
The metal damping plate has a wedge-shaped portion whose thickness gradually decreases toward the free end, and the metal plate is provided at the tip of the free end of the metal damping plate so as to be in frictional contact with the metal damping plate.
上記金属制振板は、楔形部が下記式（１）を満たして板厚が変化することで、音響ブラックホール効果が得られる。
ｈ（ｘ） ＝ ε・ｘｎ ＋ ｈ０ ・・・式（１）
但し、式（１）中、
ｘ ： 楔形部の薄肉端からの距離（ｍｍ）
ｈ（ｘ）： 楔形部の薄肉端からの距離ｘにおける板厚（ｍｍ）
ｈ０ ： 楔形部の薄肉端の板厚（ｍｍ）
ε ： 正の定数
ｎ ： １以上の実数
The metal vibration damping plate has an acoustic black hole effect when the wedge-shaped portion satisfies the following formula (1) and the plate thickness changes.
h(x) = ε・x n + h 0 ...Formula (1)
However, in formula (1),
x: Distance from the thin end of the wedge (mm)
h(x): Plate thickness at distance x from the thin end of the wedge (mm)
h0 : Plate thickness of the thin end of the wedge-shaped part (mm)
ε: positive constant n: real number greater than or equal to 1
式（１）を満たす楔形部を有する金属制振板は、図１に示すように、入射した振動（波）が、金属制振板の厚さが減少する方向の自由端に向かって伝搬し、先端に向かうにつれて振幅が大きくなって伝搬速度が遅くなる。 As shown in Figure 1, in a metal vibration damping plate with a wedge-shaped portion that satisfies equation (1), incident vibrations (waves) propagate toward the free end of the metal vibration damping plate, in the direction in which the thickness of the plate decreases, and the amplitude increases and the propagation speed slows as it approaches the tip.
本発明の金属制振板は、振幅が大きく伝搬速度が遅い自由端先端部に、金属板が摩擦可能に当接して設けられているので、上記自由端先端部に伝搬した振動エネルギーが摩擦熱に変換されて減衰する。 The metal vibration damping plate of the present invention has a metal plate that is in frictional contact with the free end tip, which has a large amplitude and a slow propagation speed, so the vibration energy propagated to the free end tip is converted into frictional heat and attenuated.
したがって、制振構造体は、金属制振板の自由端の板厚（ｈ０）が０でなくても、自由端の振動を抑えることができる。 Therefore, the vibration damping structure can suppress vibration at the free end even if the plate thickness (h 0 ) of the free end of the metal vibration damping plate is not zero.
また、本発明においては、上記減衰材として金属板を用いているので、樹脂製の減衰材に比して耐候性に優れ、経時劣化し難く耐久性が高いので、長期に亘る制振が可能である。 In addition, in this invention, metal plates are used as the damping material, which has superior weather resistance and is less susceptible to deterioration over time than resin damping materials, making it highly durable and enabling vibration damping over a long period of time.
本発明において「自由端先端部」とは、金属制振板の主面の自由端と該自由端から金属制振板の厚さが増加する方向に連続する先端部分をいい、金属制振板の自由端の端面や側面部分を言わない。
また、「摩擦可能」とは、振動の入力によって金属制振板が波打って生じる微視的な金属制振板の伸縮により、金属制振板と金属板とが部分的に摩擦すれば足り、金属制振板と金属板とが相対的に移動し、金属制振板と金属板との全体的な位置関係が変わることまでを意味するものではない。
In the present invention, the "free end tip" refers to the free end of the main surface of the metal vibration damper and the tip portion that continues from the free end in the direction in which the thickness of the metal vibration damper increases, and does not refer to the end face or side portion of the free end of the metal vibration damper.
Furthermore, "frictionable" means that it is sufficient for the metal damping plate and the metal plate to partially rub against each other due to microscopic expansion and contraction of the metal damping plate caused by the metal damping plate rippling due to input of vibration, and does not mean that the metal damping plate and the metal plate move relative to each other and the overall positional relationship between the metal damping plate and the metal plate changes.
上記制振構造体は、金属板の縁と金属制振板の自由端とがぴったりと重なっていることで、自由端での振動を効率よく抑えることができる。また、金属板の主面の全面が金属制振板の主面に当接していることで、金属板と金属制振板との接触面積が大きくなって、金属制振板の振動エネルギーを摩擦熱に効率よく変換することができる。 The above-mentioned vibration-damping structure efficiently suppresses vibrations at the free end because the edge of the metal plate and the free end of the metal vibration-damping plate tightly overlap. Furthermore, the entire main surface of the metal plate abuts against the main surface of the metal vibration-damping plate, increasing the contact area between the metal plate and the metal vibration-damping plate, allowing the vibration energy of the metal vibration-damping plate to be efficiently converted into frictional heat.
上記金属板の大きさとしては、自由端の振動を摩擦により減衰できればよく、入力される振動のエネルギーや振動数にもよるが、自由端の板厚（ｈ０）に応じてその大きさを調整する。 The size of the metal plate may be adjusted according to the plate thickness (h 0 ) of the free end, as long as it can damp the vibration of the free end by friction, and depends on the energy and frequency of the input vibration.
具体的には、金属板の種類にもよるが、金属板の厚さは、自由端の厚さと同程度であることが好ましく０．１～０．３ｍｍであることが好ましい。また、自由端からの長さは５～３０ｍｍであることが好ましい。 Specifically, although this depends on the type of metal plate, the thickness of the metal plate is preferably about the same as the thickness of the free end, preferably 0.1 to 0.3 mm. Furthermore, the length from the free end is preferably 5 to 30 mm.
上記自由端の板厚（ｈ０）は、金属制振板自体の重さや金属板の重さによって金属制振板が変形せず、その形状を維持できればできるだけ薄いことが好ましく、０．１～０．３ｍｍであることが好ましい。 The thickness (h 0 ) of the free end is preferably as thin as possible so long as the metal damping plate is not deformed by the weight of the metal damping plate itself or the weight of the metal plate and can maintain its shape, and is preferably 0.1 to 0.3 mm.
また、金属制振板の楔形部の長さ、すなわち、金属制振板の板厚が減少し始める箇所から自由端までの長さは、入力された振動を先端部に集中させることができればよく、金属制振板の厚肉部の厚さにもよるが、２０～２０００ｍｍであることが好ましい。 Furthermore, the length of the wedge-shaped portion of the metal damping plate, i.e., the length from the point where the thickness of the metal damping plate begins to decrease to the free end, should be sufficient to concentrate the input vibrations at the tip, and although this depends on the thickness of the thick portion of the metal damping plate, it is preferably between 20 and 2000 mm.
また、上記金属制振板の厚肉部の厚さは、０．５～５０ｍｍであることが好ましい。 Furthermore, it is preferable that the thickness of the thick portion of the metal vibration damping plate be 0.5 to 50 mm.
上記金属制振板の楔形部は、自由端側に向けて板厚が徐々に減少していればよく、一方の主面と他方の主面の両方が、平面で形成されていても曲面で形成されていてもよく、また、一方の主面が平面で形成され、他方の主面が曲面で形成されていてもよい。 The wedge-shaped portion of the metal vibration damping plate may have a thickness that gradually decreases toward the free end, and both of the main surfaces may be flat or curved, or one main surface may be flat and the other main surface may be curved.
上記金属制振板の全体形状としては、楔形部を有していれば特に制限はなく、正方形や長方形などの多角形状の他、円形や楕円形などを挙げることができ、楔形部の自由端が金属制振板の外側に向いていても、金属制振板の内側（中心側や中央部側）に向いてすり鉢形をしていてもよい。 The overall shape of the metal damping plate is not particularly limited as long as it has a wedge-shaped portion, and examples include polygonal shapes such as squares and rectangles, as well as circles and ellipses. The free end of the wedge-shaped portion may face the outside of the metal damping plate, or may face the inside of the metal damping plate (towards the centre or central part) to form a mortar shape.
また、上記金属制振板は、必要に応じて、楔形部の薄肉側（自由端側）に、楔形部の薄肉端の板厚と同じで板厚が一定の薄肉部を有することができる。
金属制振板が、薄肉部を有する場合は、薄肉部の自由端先端部に上記金属板が設けられる。
Furthermore, the metal damping plate may have a thin portion with a constant thickness on the thin side (free end side) of the wedge portion, as required, the thickness of which is the same as that of the thin end of the wedge portion.
When the metal damping plate has a thin portion, the metal plate is provided at the tip of the free end of the thin portion.
上記金属制振板は、さらに、楔形部の厚肉側に板厚が、楔形部の厚肉端の板厚と同じで板厚が一定の厚肉部を有していてもよい。 The above-mentioned metal vibration damping plate may further have a thick portion on the thick side of the wedge-shaped portion, the thickness of which is constant and the same as the thickness of the thick end of the wedge-shaped portion.
上記金属板を、上記金属制振板と摩擦可能に当接させる方法としては、重ね合わせた金属板と金属制振板を金属製弾性部材で挟持する方法や、金属製締結部材で締結する方法を挙げることができる。 Methods for frictionally abutting the metal plate against the metal vibration damping plate include sandwiching the overlapping metal plate and metal vibration damping plate with a metal elastic member, or fastening them together with a metal fastening member.
上記金属製弾性部材としては、クリップや板バネなどを挙げることができ、金属製締結部材としてはボルトとナットなどを挙げることができる。 Examples of the above-mentioned metallic elastic members include clips and leaf springs, and examples of metallic fastening members include bolts and nuts.
上記金属制振板や金属板としては、従来から制振板として使用されている金属材を使用することができ、例えば、鉄、アルミニウム、亜鉛、ニッケル、錫 鉛、銅、及びこれらを含む合金などを挙げることができる。 The above-mentioned metal vibration damping plate or metal plate can be made from metal materials that have traditionally been used as vibration damping plates, such as iron, aluminum, zinc, nickel, tin-lead, copper, and alloys containing these.
金属制振板と金属板とは、同種の金属材であることが好ましいが、異種の金属材を用いる場合は、金属板の自然電位が、上記金属制振板の自然電位よりも低いことが好ましい。 It is preferable that the metal damping plate and the metal plate are made of the same metal material, but if different metal materials are used, it is preferable that the natural potential of the metal plate be lower than the natural potential of the metal damping plate.
金属板が金属制振板よりも卑な金属材であることで、金属制振板の腐食を防止することができ、振動減衰効果の変化を抑制でき耐久性が向上する。 By using a metal plate made of a less noble metal than the metal damping plate, corrosion of the metal damping plate can be prevented, changes in vibration damping effect can be suppressed, and durability can be improved.
上記制振構造体は、自動車のサスペンションとボディとの間に設けてタイヤからの振動の減衰や、自動車のパネルなどの振動防止に好適に使用できる。 The above-mentioned vibration-damping structure can be installed between the suspension and body of an automobile to dampen vibrations from tires and prevent vibrations from automobile panels, etc.
以下、本発明を実施例により詳細に説明するが、本発明は下記実施例に限定されるものではない。 The present invention will be described in detail below using examples, but the present invention is not limited to the following examples.
［比較例１］
熱間圧延鋼板（ＳＳ４００）を用いて、図２に示す形状をした、長さ（Ｌ）３００ｍｍ、幅（Ｗ）５０ｍｍで、楔形部の厚肉端から自由端までの長さ（Ｌ’）が２００ｍｍ、板厚が一定の薄肉部の長さ（Ｌ”）が１０ｍｍ、自由端（薄肉部）の板厚（Ｔ）が０．２ｍｍ、厚肉部の板厚（Ｔ’）が５ｍｍであり、楔形部（厚肉端から薄肉端（Ｌ’－Ｌ”））の板厚の変化ｈ（ｘ）が、（４．８／１９０２）ｘ２＋０．２であるくさび形金属制振板を作製し、制振構造体とした。
[Comparative Example 1]
A wedge-shaped metal vibration-damping plate having the shape shown in FIG. 2 was fabricated using hot-rolled steel plate (SS400), with a length (L) of 300 mm and a width (W) of 50 mm, a length (L') from the thick end to the free end of the wedge-shaped portion of 200 mm, a length (L") of a thin portion with constant thickness of 10 mm, a thickness (T) of the free end (thin portion) of 0.2 mm, a thickness (T') of the thick portion of 5 mm, and a change in thickness h(x) of the wedge-shaped portion (from the thick end to the thin end (L'-L")) of (4.8/190 2 )x 2 + 0.2, to form a vibration-damping structure.
＜評価＞
上記比較例及び実施例の制振構造体を楔形部の先端を下方に向け、ゴム紐で支柱に吊り下げて自由支持とし、制振構造体の上端から３０ｍｍ、側端から１０ｍｍの位置に加速度センサ（ＰＣＢ社製 ３５６Ａ０１）を取り付けた。
<Evaluation>
The vibration damping structures of the above comparative example and example were freely supported by being hung from a support column with a rubber string, with the tip of the wedge-shaped portion facing downward, and an acceleration sensor (356A01 manufactured by PCB Co.) was attached 30 mm from the top end of the vibration damping structure and 10 mm from the side end.
加速度センサ付近を、インパルスハンマ（ＰＣＢ社製 ０８６Ｃ０３（ハードチップ））で打撃し、インパルスハンマ（入力）の力と加速度センサ（応答）の加速度をＦＦＴアナライザ（シーメンス株式会社製 ＳＣＡＤＡＳ ＩＩＩ）に取り込んでフーリエ変換を行い、加速度／力の伝達関数（イナータンス）を取得した。打撃を５回繰り返し平均してイナータンスを測定した。評価結果を図３に示す。 An impulse hammer (PCB Corporation 086C03 (hard tip)) was used to strike the area near the acceleration sensor, and the force of the impulse hammer (input) and the acceleration of the acceleration sensor (response) were input into an FFT analyzer (Siemens AG SCADAS III) for a Fourier transform to obtain the acceleration/force transfer function (inertance). The strike was repeated five times and the average inertance was measured. The evaluation results are shown in Figure 3.
［比較例２］
比較例１のくさび形金属制振板の楔形部の先端部に、長さ（Ｌ’’’）１０ｍｍ、幅（Ｗ）５０ｍｍ、厚さ０．８ｍｍ、質量３．１ｇのマグネットシート（酸化鉄、塩素化ポリエチレンの減衰板）を、その縁が自由端と重なるようにぴったりと重ね、全面を両面テープで貼り付けて制振構造体を作製した。比較例１と同様に評価した結果を図４に示す。
[Comparative Example 2]
A magnetic sheet (damping plate made of iron oxide and chlorinated polyethylene) with a length (L''') of 10 mm, width (W) of 50 mm, thickness of 0.8 mm, and mass of 3.1 g was tightly placed on the tip of the wedge-shaped part of the wedge-shaped metal vibration damping plate of Comparative Example 1 so that its edge overlapped the free end, and the entire surface was attached with double-sided tape to create a vibration damping structure. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 4.
［比較例３］
長さ（Ｌ’’’）１０ｍｍ、幅（Ｗ）５０ｍｍ、厚さ０．２ｍｍ、質量１．６ｇの冷間圧延鋼板（ＳＰＣＣ）板の全面をハンダで接合する他は、比較例２と同様にして制振構造体を作製した。比較例１と同様に評価した結果を図５に示す。
[Comparative Example 3]
A vibration damping structure was fabricated in the same manner as in Comparative Example 2, except that the entire surface of a cold-rolled steel plate (SPCC) having a length (L''') of 10 mm, a width (W) of 50 mm, a thickness of 0.2 mm, and a mass of 1.6 g was soldered. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 5.
［実施例１］
比較例３の冷間圧延鋼板（ＳＰＣＣ）板をターンクリップで２箇所挟持し留める他は比較例３と同様にして制振構造体を作製した。比較例１と同様に評価した結果を図６に示す。
[Example 1]
A vibration damping structure was fabricated in the same manner as in Comparative Example 3, except that the cold-rolled steel plate (SPCC) of Comparative Example 3 was clamped and fastened at two points with turn clips. The results of evaluation in the same manner as in Comparative Example 1 are shown in FIG. 6.
［実施例２］
比較例３の冷間圧延鋼板（ＳＰＣＣ）板をゼムクリップ（登録商標）で２箇所挟持し留める他は比較例３と同様にして制振構造体を作製した。比較例１と同様に評価した結果を図７に示す。
[Example 2]
A vibration damping structure was fabricated in the same manner as in Comparative Example 3, except that the cold-rolled steel plate (SPCC) of Comparative Example 3 was clamped and fastened at two points with Gem Clips (registered trademark). The results of evaluation in the same manner as in Comparative Example 1 are shown in FIG. 7.
［比較例４］
比較例１のくさび形金属制振板の楔形部の先端部に金属板を設けずに、合計質量が５．０ｇのボルトとナットを締結して制振構造体を作製した。比較例１と同様に評価した結果を図８に示す。
[Comparative Example 4]
A damping structure was fabricated by fastening bolts and nuts with a total mass of 5.0 g without providing a metal plate at the tip of the wedge-shaped portion of the wedge-shaped metal damping plate of Comparative Example 1. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 8.
［実施例３］
比較例３の冷間圧延鋼板（ＳＰＣＣ）板と金属制振板との自由端を、比較例４と同じボルトとナットで締結する他は実施例１と同様にして制振構造体を作製した。比較例１と同様に評価した結果を図９に示す。
[Example 3]
A vibration damping structure was fabricated in the same manner as in Example 1, except that the free ends of the cold-rolled steel plate (SPCC) plate of Comparative Example 3 and the metal vibration damping plate were fastened with the same bolts and nuts as in Comparative Example 4. The results of evaluation in the same manner as in Comparative Example 1 are shown in FIG.
［実施例４］
冷間圧延鋼板（ＳＰＣＣ）板を、長さ（Ｌ’’’）１０ｍｍ、幅（Ｗ）５０ｍｍ、厚さ０．１２ｍｍ、質量３．４ｇのアルミニウム板に変える他は実施例２と同様にして制振構造体を作製した。比較例１と同様に評価した結果を図１０に示す。
[Example 4]
A vibration damping structure was fabricated in the same manner as in Example 2, except that the cold-rolled steel plate (SPCC) was replaced with an aluminum plate having a length (L''') of 10 mm, a width (W) of 50 mm, a thickness of 0.12 mm, and a mass of 3.4 g. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 10.
［比較例５］
ステンレスを用いて、直径（Ｌ）が６４ｍｍの円盤の中心に、直径が１７ｍｍの円形の貫通孔を有し、この円盤の外縁を自由端とする楔形部の長さ（Ｌ’）が３２ｍｍ、自由端の板厚（Ｔ）が０．２ｍｍ、厚肉部の板厚（Ｔ’）が２ｍｍであり、楔形部の板厚の変化ｈ（ｘ）が、（１．８／３２２）ｘ２＋０．２である円盤型金属制振板を作製し、制振構造体とした。比較例１と同様に評価した結果を図１２に示す。
[Comparative Example 5]
A disk-shaped metal vibration-damping plate was fabricated using stainless steel, and used as a vibration-damping structure. The plate had a diameter (L) of 64 mm, a circular through-hole of 17 mm in the center, a wedge-shaped portion whose free end was the outer edge of the disk, a length (L') of 32 mm, a thickness (T) of 0.2 mm at the free end, a thickness (T') of 2 mm at the thick portion, and a change in thickness h(x) of (1.8/32 2 )x 2 + 0.2. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 12.
［比較例６］
比較例５の円盤型金属制振板の楔形部の外周先端部に、天然ゴム製の内径４４ｍｍ、外径６４ｍｍ、厚さ０．８ｍｍ、質量４．０ｇの減衰板を、その外縁が円盤型金属制振板の自由端と重なるようにぴったりと重ね、ゼムクリップ（登録商標）で２箇所挟持し制振構造体を作製した。比較例１と同様に評価した結果を図１３に示す。
[Comparative Example 6]
A damping plate made of natural rubber with an inner diameter of 44 mm, an outer diameter of 64 mm, a thickness of 0.8 mm, and a mass of 4.0 g was placed snugly on the outer periphery of the wedge-shaped portion of the disk-shaped metal damping plate of Comparative Example 5 so that its outer edge overlapped the free end of the disk-shaped metal damping plate, and the plate was clamped in two places with Gem Clips (registered trademark) to produce a damping structure. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 13.
［実施例５］
比較例５の円盤型金属制振板の楔形部の外周先端部に、冷間圧延鋼板（ＳＰＣＣ）製の内径４４ｍｍ、外径６４ｍｍ、厚さ０．２ｍｍ、質量２．６ｇの減衰板を、その外縁が円盤型金属制振板の自由端と重なるようにぴったりと重ね、ゼムクリップ（登録商標）で２箇所挟持し制振構造体を作製した。比較例１と同様に評価した結果を図１４に示す。
[Example 5]
A damping plate made of cold-rolled steel (SPCC) with an inner diameter of 44 mm, an outer diameter of 64 mm, a thickness of 0.2 mm, and a mass of 2.6 g was placed snugly on the outer periphery of the wedge-shaped portion of the disk-shaped metal damping plate of Comparative Example 5 so that its outer edge overlapped the free end of the disk-shaped metal damping plate, and the plate was clamped in two places with Gem Clips (registered trademark) to produce a damping structure. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 14.
［比較例７］
熱間圧延鋼板（ＳＳ４００）を用いて、一辺が１３０ｍｍの正方形の中心に直径が１４ｍｍの円形の貫通孔を有し、この貫通孔を自由端とする外径が９７ｍｍである楔形部を有し、上記自由端の板厚が０．２３ｍｍ、厚肉部の板厚が４．５ｍｍであり、楔形部の板厚の変化ｈ（ｘ）が、（４．２７／４１．５２）ｘ２＋０．１４であるすり鉢状金属制振板を作製し、制振構造体とした。比較例１と同様に評価した結果を図１７に示す。
[Comparative Example 7]
A cone-shaped metal damping plate was fabricated using hot-rolled steel plate (SS400) to serve as a damping structure. The plate had a circular through-hole with a diameter of 14 mm at the center of a square with sides of 130 mm, a wedge-shaped portion with an outer diameter of 97 mm and the through-hole as its free end, the thickness of the free end was 0.23 mm, the thickness of the thick portion was 4.5 mm, and the change in thickness of the wedge-shaped portion h(x) was (4.27/41.5 2 )x 2 + 0.14. The results of evaluation in the same manner as in Comparative Example 1 are shown in Figure 17.
［比較例８］
比較例７のすり鉢状金属制振板の楔形部の先端部に、天然ゴム製の内径１４ｍｍ、外径３４ｍｍ、厚さ０．８ｍｍ、質量１．３ｇの減衰板を、その内縁がすり鉢状金属制振板の自由端と重なるようにぴったりと重ね、ゼムクリップ（登録商標）で２箇所挟持し制振構造体を作製した。比較例１と同様に評価した結果を図１７に示す。
[Comparative Example 8]
A damping plate made of natural rubber with an inner diameter of 14 mm, an outer diameter of 34 mm, a thickness of 0.8 mm, and a mass of 1.3 g was placed snugly on the tip of the wedge-shaped part of the cone-shaped metal damping plate of Comparative Example 7 so that its inner edge overlapped the free end of the cone-shaped metal damping plate, and the plate was clamped in two places with Gem Clips (registered trademark) to produce a damping structure. The results of evaluation in the same way as in Comparative Example 1 are shown in Figure 17.
［実施例６］
比較例７のすり鉢状金属制振板の楔形部の先端部に、冷間圧延鋼板（ＳＰＣＣ）製の内径１４ｍｍ、外径３４ｍｍ、厚さ０．２ｍｍ、質量１．１６ｇの減衰板を、その内縁がすり鉢状金属制振板の自由端と重なるようにぴったりと重ね、ゼムクリップ（登録商標）で２箇所挟持し制振構造体を作製した。比較例１と同様に評価した結果を図１８に示す。
[Example 6]
A damping plate made of cold-rolled steel (SPCC) with an inner diameter of 14 mm, an outer diameter of 34 mm, a thickness of 0.2 mm, and a mass of 1.16 g was placed snugly on the tip of the wedge-shaped part of the cone-shaped metal damping plate of Comparative Example 7 so that its inner edge overlapped the free end of the cone-shaped metal damping plate, and the plate was clamped in two places with Gem Clips (registered trademark) to produce a damping structure. The results of evaluation in the same way as in Comparative Example 1 are shown in Figure 18.
比較例１と比較例２との結果から、マグネットシートを貼付することで振動を減衰できることが分かる。 The results of Comparative Examples 1 and 2 show that vibrations can be damped by attaching a magnetic sheet.
実施例１，２と比較例３との結果から、金属板が金属制振板と摩擦することで振動を減衰できることが分かり、比較例２との差から、金属板を摩擦可能に設けることで弾性材であるマグネットシートよりも軽量であるにも拘らず、同等かそれ以上の制振効果を奏することが分かる。 The results of Examples 1 and 2 and Comparative Example 3 show that vibrations can be damped by friction between the metal plate and the metal vibration damping plate, and the difference with Comparative Example 2 shows that by providing a metal plate that can be subjected to friction, it can achieve the same or greater vibration damping effect, despite being lighter than a magnetic sheet, which is an elastic material.
実施例３は、実施例１，２よりも制振効果が低下したが、ボルト締結によって実施例１，２よりも金属板の摩擦が制限されたためであると考えられる。
また、実施例４は、実施例１よりも制振効果が低下したが、アルミニウム板の質量が冷間圧延鋼板よりも軽量であることによると考えられる。
The vibration damping effect of Example 3 was lower than that of Examples 1 and 2, but this is thought to be because the friction of the metal plates was more limited than in Examples 1 and 2 due to bolt fastening.
Furthermore, the vibration damping effect of Example 4 was lower than that of Example 1, but this is thought to be because the mass of the aluminum plate was lighter than that of the cold-rolled steel plate.
実施例５と比較例５，６の結果から、円盤状の金属制振板も金属板を摩擦可能に設けることで制振効果を奏することが分かる。 The results of Example 5 and Comparative Examples 5 and 6 show that a disk-shaped metal vibration damping plate can also provide vibration damping effects by providing a metal plate that can be frictionally attached.
実施例６と比較例７、８の結果から、すり鉢状の金属制振板も金属板を摩擦可能に設けることで制振効果を奏することが分かる。 The results of Example 6 and Comparative Examples 7 and 8 show that a mortar-shaped metal vibration damping plate also provides vibration damping effects by providing a metal plate that can be rubbed.
１ 金属制振板
１１ 楔形部
１２ 自由端
１３ 厚肉部
２ 金属板
REFERENCE SIGNS LIST 1 metal damping plate 11 wedge-shaped portion 12 free end 13 thick portion 2 metal plate
Claims (6)
上記楔形部の板厚が下記式（１）を満たして変化し、
上記金属板が、上記金属制振板と摩擦可能に設けられたことを特徴とする制振構造体。
ｈ（ｘ） ＝ ε・ｘｎ ＋ ｈ０ ・・・式（１）
但し、式（１）中、
ｘ ： 楔形部の薄肉端からの距離（ｍｍ）
ｈ（ｘ）： 楔形部の薄肉端からの距離ｘにおける板厚（ｍｍ）
ｈ０ ： 楔形部の薄肉端の板厚（ｍｍ）
ε ： 正の定数
ｎ ： １以上の実数 A vibration-damping structure comprising a metal vibration-damping plate having at least a wedge-shaped portion and a metal plate abutting against a free end tip of the metal vibration-damping plate,
The thickness of the wedge-shaped portion changes to satisfy the following formula (1),
A vibration-damping structure characterized in that the metal plate is provided so as to be able to frictionally contact the metal vibration-damping plate.
h(x) = ε・x n + h 0 ...Formula (1)
However, in formula (1),
x: Distance from the thin end of the wedge (mm)
h(x): Plate thickness at distance x from the thin end of the wedge (mm)
h0 : Plate thickness of the thin end of the wedge-shaped part (mm)
ε: positive constant n: real number greater than or equal to 1
上記薄肉部の板厚が、楔形部の薄肉端の板厚と同じであり、
上記金属板が、上記薄肉部に設けられたことを特徴とする請求項１～３のいずれか１つの項に記載の制振構造体。 the metal vibration damping plate further includes a thin-walled portion having a constant plate thickness at a thin-walled end of the wedge-shaped portion,
The thickness of the thin-walled portion is the same as the thickness of the thin-walled end of the wedge-shaped portion,
4. The vibration damping structure according to claim 1, wherein the metal plate is provided on the thin portion.
上記制振構造体が請求項１～５のいずれか１つの項に記載の制振構造体であることを特徴とする自動車。 A vehicle equipped with a vibration damping structure,
An automobile, wherein the vibration damping structure is the vibration damping structure according to any one of claims 1 to 5.
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| JP2002115418A (en) | 2000-10-06 | 2002-04-19 | Penta Ocean Constr Co Ltd | Friction dampers for seismic devices |
| JP2010144868A (en) | 2008-12-19 | 2010-07-01 | Ihi Corp | Elastic wedge damper |
| US20160348752A1 (en) | 2014-12-09 | 2016-12-01 | Hrl Laboratories, Llc | Hingeless, large-throw negative stiffness structure |
| JP2018511757A (en) | 2015-04-02 | 2018-04-26 | リゼガ エスエーＬｉｓｅｇａ Ｓｅ | Shaft damper |
| US20210054898A1 (en) | 2018-01-30 | 2021-02-25 | The Hong Kong Polytechnic University | Wideband vibration suppression device utilizing properties of sonic black hole |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002115418A (en) | 2000-10-06 | 2002-04-19 | Penta Ocean Constr Co Ltd | Friction dampers for seismic devices |
| JP2010144868A (en) | 2008-12-19 | 2010-07-01 | Ihi Corp | Elastic wedge damper |
| US20160348752A1 (en) | 2014-12-09 | 2016-12-01 | Hrl Laboratories, Llc | Hingeless, large-throw negative stiffness structure |
| JP2018511757A (en) | 2015-04-02 | 2018-04-26 | リゼガ エスエーＬｉｓｅｇａ Ｓｅ | Shaft damper |
| US20210054898A1 (en) | 2018-01-30 | 2021-02-25 | The Hong Kong Polytechnic University | Wideband vibration suppression device utilizing properties of sonic black hole |
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