JPH08254244A - Composite damping metal plate - Google Patents
Composite damping metal plateInfo
- Publication number
- JPH08254244A JPH08254244A JP5885395A JP5885395A JPH08254244A JP H08254244 A JPH08254244 A JP H08254244A JP 5885395 A JP5885395 A JP 5885395A JP 5885395 A JP5885395 A JP 5885395A JP H08254244 A JPH08254244 A JP H08254244A
- Authority
- JP
- Japan
- Prior art keywords
- plate
- damping
- ratio
- metal
- metal plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
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- Vibration Prevention Devices (AREA)
- Laminated Bodies (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、有機物を使用すること
なく、複数枚の金属板を積重結合した軽量な複合型の制
振金属板に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lightweight composite vibration-damping metal plate in which a plurality of metal plates are stacked and joined without using an organic substance.
【０００２】[0002]
【従来の技術】制振材料として一般に使用されている制
振合金や、高分子樹脂を２枚の金属板で挟んだ樹脂サン
ドイッチ型の複合制振金属板は、いずれも溶接による接
続が困難であったり、例え溶接が可能であっても溶接後
の制振性能が著しく低下するといった欠点を有する。こ
の欠点を解消したのが金属板を直接積重して部分的に接
合した複合制振金属板である（例えば特開昭６１−３７
３１６号公報、特開昭６１−３７３１７号公報、特開昭
６１−１１９３９０号公報、特開昭６１−１８２８２０
号公報、特開平１−１１４４３２号公報、特開平５−１
９６０９１号公報、特開平５−２０８２１２号公報、特
願平５−８９４１３号公報）。2. Description of the Related Art Damping alloys commonly used as damping materials and resin sandwich type composite damping metal plates in which a polymer resin is sandwiched between two metal plates are difficult to connect by welding. However, even if welding is possible, there is a drawback that the vibration damping performance after welding is significantly reduced. This drawback is solved by a composite vibration-damping metal plate in which metal plates are directly stacked and partially joined (for example, JP-A-61-37).
316, JP-A 61-37317, JP-A 61-119390, and JP-A 61-182820.
Japanese Patent Application Laid-Open No. 1-114432, Japanese Patent Application Laid-Open No. 5-1
96091, Japanese Patent Application Laid-Open No. 5-208212, Japanese Patent Application No. 5-89413).
【０００３】この種の複合制振金属板は、図１６に示す
ように、強度部材としての主板１の両面を、制振性を発
現するための補助板２で挟み、主板１と補助板２からな
る３枚以上の金属板を一定以上の間隔をあけてできるだ
け均等に分散配置した複数箇所で点溶接したものであ
り、複合型であるにもかかわらず有機物を必要としない
ので、溶接性や耐久性，耐火性にも優れており、例えば
船舶の床材や壁材等の構造材料として近年大きな注目を
集めている。なお、図１６中の３は点溶接した溶接部を
示す。As shown in FIG. 16, this type of composite vibration-damping metal plate sandwiches both sides of a main plate 1 as a strength member with auxiliary plates 2 for exerting vibration-damping properties, and the main plate 1 and the auxiliary plate 2 are sandwiched. It is made by spot welding 3 or more metal plates consisting of 3 or more metal plates at even intervals apart from each other at a certain distance, and even if it is a composite type, it does not require organic matter. It is also excellent in durability and fire resistance, and has recently attracted a great deal of attention as a structural material such as floor materials and wall materials for ships. In addition, 3 in FIG. 16 indicates a spot welded portion.
【０００４】このような複合制振金属板では、振動が生
じたときに各金属板の振動モードが相違することによ
り、相互干渉作用が生じ、その結果、金属板同士が直接
擦れ合うことによって発生する摩擦による減衰作用によ
り、優れた制振性が得られることになる。しかも、有機
物を必要としないので、端面を突き合わせ溶接すること
も可能である。さらには、金属板の成分組成に対する制
限がないので、強度，靱性等の確保も容易である。In such a composite vibration-damping metal plate, when the vibrations occur, the vibration modes of the metal plates are different from each other, so that mutual interference occurs, and as a result, the metal plates directly rub against each other. Due to the damping action due to friction, excellent vibration damping property can be obtained. Moreover, since no organic matter is required, the end faces can be butt-welded together. Further, since there is no limitation on the component composition of the metal plate, it is easy to secure strength, toughness and the like.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、前記し
た複合制振金属板は、主板，補助板とも金属板であるの
で、複合制振金属板全体の重量が重たくなるという問題
を内在している。従って、従来は補助板の板厚を主板の
板厚に対してできるだけ薄くするという方法で重量増を
抑えていたが、この方法でも主板の板厚に対して１：１
６程度が十分な制振性を発現させる限界であり、これ以
上は補助板を薄くできないので、主板の板厚が厚くなっ
てくると重量増が無視できなくなってくる。However, since the composite vibration-damping metal plate described above is a metal plate for both the main plate and the auxiliary plate, there is an inherent problem that the weight of the composite vibration-damping metal plate becomes heavy. Therefore, conventionally, the weight increase is suppressed by reducing the thickness of the auxiliary plate to the thickness of the main plate as much as possible, but even with this method, the weight of the main plate is 1: 1.
Around 6 is the limit for exhibiting sufficient vibration damping properties, and since the auxiliary plate cannot be made thinner than this, an increase in the weight of the main plate cannot be ignored.
【０００６】また、複合制振金属板は構造材料として用
いられるので曲げ剛性が求められる。従って、この曲げ
剛性によって主板の厚みが決定される。必要な曲げ剛性
を得るためには、主板の厚みは通常１０ｍｍ以上必要と
なり、このことが重量を増加させるもう一つの要因とな
っている。Further, since the composite vibration-damping metal plate is used as a structural material, bending rigidity is required. Therefore, the bending rigidity determines the thickness of the main plate. In order to obtain the required bending rigidity, the thickness of the main plate is usually 10 mm or more, which is another factor that increases the weight.
【０００７】本発明は、上記した従来の問題点に鑑みて
なされたものであり、必要な主板の強度及び曲げ剛性を
得るとともに、制振性を損なうことなく軽量な複合制振
金属板を提供することを目的としている。The present invention has been made in view of the above-mentioned conventional problems, and provides a lightweight composite vibration-damping metal plate that obtains necessary strength and bending rigidity of the main plate and does not impair the vibration-damping property. The purpose is to do.
【０００８】[0008]
【課題を解決するための手段】上記した目的を達成する
ために、本発明の複合制振金属板は、主板の両面を補助
板で挟み、これら主板と補助板とを部分的に結合した複
合制振金属板であって、主板の形状を、長さ方向又は幅
方向に波形又はハット状の凹凸形、若しくは長さ方向及
び幅方向にハット状の凹凸形となしているのであり、ま
た、必要に応じて波形又はハット状の凹凸形部分の適所
に金属棒又は金属管を挿入するのである。In order to achieve the above object, the composite vibration-damping metal plate of the present invention is a composite plate in which both sides of a main plate are sandwiched by auxiliary plates and the main plate and the auxiliary plate are partially connected. The vibration-damping metal plate, the shape of the main plate is a wavy or hat-shaped uneven shape in the length direction or the width direction, or a hat-shaped uneven shape in the length direction and the width direction, If necessary, a metal rod or metal tube is inserted into the corrugated or hat-shaped concavo-convex portion at an appropriate position.
【０００９】本発明において、主板の両面を挟む補助板
は、それぞれの面に一枚づつ配置するのが軽量化をはか
るためには最も好ましいが、軽量の補助板を使用した場
合は若干重量増にはなるものの、曲げ剛性や制振性が向
上するので、それぞれの面に二枚以上配置してもよい。In the present invention, it is most preferable to arrange one auxiliary plate sandwiching both sides of the main plate for each surface in order to reduce the weight, but when the lightweight auxiliary plate is used, the weight is slightly increased. However, since the bending rigidity and the vibration damping property are improved, two or more sheets may be arranged on each surface.
【００１０】また、本発明においては、主板と補助板の
材料は金属系のものであれば殆ど適用可能である。具体
的には、鋼材，ステンレス，アルミニウム，銅等であ
る。また、本発明においては、主板と補助板の材料の組
み合わせについても特に限定されず、どのような組み合
わせであってもよい。Further, in the present invention, most of the materials for the main plate and the auxiliary plate can be applied as long as they are made of metal. Specifically, it is steel, stainless steel, aluminum, copper or the like. Further, in the present invention, the combination of materials for the main plate and the auxiliary plate is not particularly limited, and may be any combination.
【００１１】なお、長さ方向と幅方向の曲げ剛性を良く
するためには、本発明の複合制振金属板のなかでは、主
板の形状を長さ方向及び幅方向にハット状の凹凸形とな
したものが最も良いが、これは長さ方向又は幅方向にハ
ット状の凹凸形となしたものよりも主板と補助板の接触
面積が小さくなるので、制振性の点では長さ方向又は幅
方向にハット状の凹凸形となしたものよりも劣る。In order to improve the bending rigidity in the length direction and the width direction, in the composite vibration-damping metal plate of the present invention, the shape of the main plate is made into a hat-shaped uneven shape in the length direction and the width direction. It is best done, but this is because the contact area of the main plate and the auxiliary plate is smaller than that of the hat-shaped concavo-convex shape in the length direction or the width direction, so in terms of vibration damping property It is inferior to the one with a hat-shaped concavo-convex shape in the width direction.
【００１２】[0012]
【作用】本発明の複合制振金属板は、主板の両面を補助
板で挟み、これら主板と補助板とを部分的に結合した複
合制振金属板であって、主板の形状を、長さ方向又は幅
方向に波形又はハット状の凹凸形、若しくは長さ方向及
び幅方向にハット状の凹凸形となしているので、必要な
主板の強度や曲げ剛性が得られるとともに、制振性を損
なうことなく複合制振金属板の軽量化が図れる。この
時、波形又はハット状の凹凸形部分の適所に金属棒又は
金属管を挿入すれば、複合制振金属板全体の強度が更に
向上する。The composite vibration-damping metal plate of the present invention is a composite vibration-damping metal plate in which both sides of the main plate are sandwiched by the auxiliary plates, and the main plate and the auxiliary plate are partially connected to each other. The wavy or hat-shaped uneven shape in the width direction or the width direction, or the hat-shaped uneven shape in the length direction and the width direction, provides the necessary strength and bending rigidity of the main plate and impairs the vibration damping property. The weight of the composite vibration-damping metal plate can be reduced without any effort. At this time, if a metal rod or a metal tube is inserted into the corrugated or hat-shaped concavo-convex portion at appropriate positions, the strength of the entire composite vibration-damping metal plate is further improved.
【００１３】すなわち、図９に示すような矩形状の平板
４の曲げ剛性Ｄは、平板４の縦弾性係数をＥ、ポアソン
比をν、板厚をｈとすると、下記１式で表される。That is, the flexural rigidity D of the rectangular flat plate 4 as shown in FIG. 9 is expressed by the following formula 1 where E is the longitudinal elastic coefficient of the flat plate 4, ν is the Poisson's ratio, and h is the plate thickness. .
【００１４】[0014]
【数１】Ｄ＝（Ｅ×ｈ3 ）／１２（１−ν2 ）## EQU1 ## D = (E × h 3 ) / 12 (1-ν 2 ).
【００１５】これに対して図１０に示すような形状をし
た波板５の曲げ剛性Ｄ1 は、波板の断面係数をＩ1 、波
のピッチ長さをｂ、波板の一波長分の板に沿った長さを
ｂWとすると、波に対して直角方向では下記２式で表さ
れる。On the other hand, the bending rigidity D 1 of the corrugated plate 5 having the shape shown in FIG. 10 is I 1 as the section modulus of the corrugated plate, b as the pitch length of the wave, and one wavelength of the corrugated plate. When the length along the plate is b W , it is expressed by the following two equations in the direction perpendicular to the wave.
【００１６】[0016]
【数２】 [Equation 2]
【００１７】この数式１及び数式２において、〔Ｅ／１
２（１−ν2 ）〕×（Ｉ1 ／ｂ）＞（Ｅ×ｈ3 ）／１２
（１−ν2 ）となるので、波板の曲げ剛性Ｄ1 ＞平板の
曲げ剛性Ｄとなる。また、図１１は板厚ｈ及び波のピッ
チ長さｂが等しいが波の高さｂh が異なる波板５におい
て、波の高さｂh の変化に対する曲げ剛性の比Ｄ1 ／Ｄ
の変化を表した図である。この図１１から、板厚ｈ及び
波のピッチ長さｂが等しい場合には、波の高さｂh が高
くなればなるほど曲げ剛性の比Ｄ1 ／Ｄが大きくなるの
が判る。In the equations 1 and 2, [E / 1
2 (1-ν 2 )] × (I 1 / b)> (E × h 3 ) / 12
Since it is (1-ν 2 ), the bending rigidity D 1 of the corrugated plate> the bending rigidity D of the flat plate. Further, FIG. 11 is the plate thickness h and the corrugated plate 5 the pitch length b equal to the height b h waves different waves, the bending rigidity with respect to the change of the wave height b h ratio D 1 / D
It is a figure showing the change of. It can be seen from FIG. 11 that when the plate thickness h and the wave pitch length b are equal, the bending rigidity ratio D 1 / D increases as the wave height b h increases.
【００１８】波板５の場合、波の高さｂh によって波板
５の一波長分の板に沿った長さｂWが決まり、このｂW
が決まれば数式２によって波板５の曲げ剛性Ｄ1 を求め
ることができる。従って、この波板５の曲げ剛性Ｄ1 を
数式１における平板の曲げ剛性Ｄとして代入すれば、そ
の時の波板と等しい曲げ剛性を有する平板４の板厚ｈα
（以下、「相当板厚」という）を求めることができる。
図１２は板厚ｈ及び波のピッチ長さｂが等しい場合にお
ける、波の高さｂh の変化に対する相当板厚と実際の板
厚との比（以下、「相当板厚比」という）を表した図で
ある。この図１２から、板厚ｈ及び波のピッチ長さｂが
等しい場合には、波の高さｂh を大きくすると相当板厚
比、つまり相当板厚ｈαが大きくなるのが判る。[0018] When the wave plate 5, determines the length b W along the plates of one wavelength of the wave plate 5 by the waves of height b h, the b W
Then, the bending rigidity D 1 of the corrugated plate 5 can be obtained by the mathematical formula 2. Therefore, by substituting the bending rigidity D 1 of the corrugated plate 5 as the bending rigidity D of the flat plate in Formula 1, the plate thickness hα of the flat plate 4 having the same bending rigidity as the corrugated plate at that time is obtained.
(Hereinafter, referred to as “equivalent plate thickness”) can be obtained.
FIG. 12 shows the ratio of the equivalent plate thickness to the actual plate thickness (hereinafter, referred to as “equivalent plate thickness ratio”) with respect to the change in the wave height b h when the plate thickness h and the wave pitch length b are equal. FIG. From FIG. 12, when the pitch length b of the plate thickness h and wave are equal, it corresponds the thickness ratio A larger height b h of the wave, is that is the equivalent thickness hα increases seen.
【００１９】また、図１３に示すように、波板５に金属
棒１７を挿入した場合の曲げ剛性も上記した数式２と同
様に表すことができる。しかし、この場合の曲げ剛性を
Ｄ2とすると波の形状ｚが異なるので、Ｄ2 ＞Ｄ1 とな
る。この値は挿入する金属棒１７の断面直径ｃによって
決まり、断面直径ｃが大きくなればその比Ｄ2 ／Ｄ1も
大きくなる。Further, as shown in FIG. 13, the bending rigidity when the metal rod 17 is inserted into the corrugated plate 5 can also be expressed in the same manner as in the above-mentioned mathematical formula 2. However, assuming that the bending rigidity in this case is D 2 , the wave shape z is different, and thus D 2 > D 1 . This value is determined by the sectional diameter c of the metal rod 17 to be inserted, and the ratio D 2 / D 1 increases as the sectional diameter c increases.
【００２０】図１４は金属棒１７の断面直径ｃの波のピ
ッチ長さｂに対する比ｃ／ｂと剛性比Ｄ2 ／Ｄ1 の関係
を表した図であり、この図１４から、挿入する金属棒１
７の断面直径ｃを大きくすれば剛性比Ｄ2 ／Ｄ1 が大き
くなることが判る。FIG. 14 is a diagram showing the relationship between the ratio c / b of the sectional diameter c of the metal rod 17 to the pitch length b of the wave and the rigidity ratio D 2 / D 1. From FIG. Stick 1
It can be seen that the rigidity ratio D 2 / D 1 increases as the cross-sectional diameter c of 7 increases.
【００２１】また、図１５は板厚ｈ及び波のピッチ長さ
ｂ、波の高さｂh が等しい時、金属棒１７の断面直径ｃ
と等しい曲げ剛性になる平板４の板厚ｈａ（以下、「相
当板厚」という）と実際の板厚との比（以下、「相当板
厚比」という）を表した図である。この図１５から、金
属棒１７の断面直径ｃを大きくすると相当板厚ｈａが大
きくなることが判る。しかし、金属棒１７を挿入するこ
とによって鋼板の総重量も増加するので、挿入する金属
棒１７の断面直径ｃと波のピッチ長さｂに対する比ｃ／
ｂを１／１０以下に抑え、挿入間隔も数波毎にする必要
がある。Further, FIG. 15 shows that when the plate thickness h, the wave pitch length b, and the wave height bh are equal, the cross-sectional diameter c of the metal rod 17 is shown.
It is a figure showing the ratio (henceforth "equivalent plate thickness ratio") of the plate thickness ha (henceforth "equivalent plate thickness") and the actual plate thickness of the flat plate 4 which becomes bending rigidity equal to. It can be seen from FIG. 15 that the equivalent plate thickness ha increases as the sectional diameter c of the metal rod 17 increases. However, since the total weight of the steel plate is also increased by inserting the metal rod 17, the ratio of the cross-sectional diameter c of the metal rod 17 to be inserted and the pitch length b of the wave c /
It is necessary to suppress b to 1/10 or less and also to insert at intervals of several waves.
【００２２】さらに、金属棒１７を挿入する代わりに、
金属管を挿入すればより軽量な制振性に優れた超軽量複
合金属板を得ることができる。Further, instead of inserting the metal rod 17,
By inserting a metal tube, it is possible to obtain a lighter weight, super lightweight composite metal plate having excellent vibration damping properties.
【００２３】[0023]
【実施例】以下、本発明の複合制振金属板を図１〜図８
に示す１実施例に基づいて説明する。図１は請求項１に
対応する本発明の複合制振金属板の実施例を示す斜視図
で、（ａ）はその第１実施例、（ｂ）は第２実施例，
（ｃ）は第３実施例、図２は請求項２に対応する本発明
の複合制振金属板の実施例を示す斜視図で、（ａ）はそ
の第１実施例、（ｂ）は第２実施例，（ｃ）は第３実施
例、図３は本発明の効果を示す実験に用いた請求項１に
対応する本発明の複合制振金属板の実施例を示す斜視図
で、（ａ）はその第１実施例、（ｂ）は第２実施例，
（ｃ）は第３実施例、図４は本発明の効果を示す実験に
用いた治具の斜視図、図５は請求項１に対応する本発明
の効果を示す実験の結果を示す図で、実施例及び従来例
における減衰比と相当板厚比との関係図、図６は請求項
１に対応する本発明の効果を示す実験の結果を示す図
で、実施例及び従来例における剛性値と平板での剛性値
との比と、相当板厚比との関係図、図７は請求項２に対
応する本発明の効果を示す実験の結果を示す図で、実施
例及び従来例における減衰比と相当板厚比との関係図、
図８は請求項２に対応する本発明の効果を示す実験の結
果を示す図で、実施例及び従来例における剛性値と平板
での剛性値との比と、相当板厚比との関係図である。EXAMPLE A composite vibration-damping metal plate of the present invention will be described below with reference to FIGS.
A description will be given based on an example shown in FIG. 1 is a perspective view showing an embodiment of a composite vibration-damping metal plate of the present invention corresponding to claim 1, (a) is the first embodiment, (b) is the second embodiment,
(C) is a third embodiment, FIG. 2 is a perspective view showing an embodiment of the composite vibration-damping metal plate of the present invention corresponding to claim 2, (a) is the first embodiment, (b) is the first embodiment. 2 embodiment, (c) is a third embodiment, FIG. 3 is a perspective view showing an embodiment of the composite vibration-damping metal plate of the present invention corresponding to claim 1 used in an experiment showing the effect of the present invention. a) is the first embodiment, (b) is the second embodiment,
(C) is a third embodiment, FIG. 4 is a perspective view of a jig used in the experiment showing the effect of the present invention, and FIG. 5 is a diagram showing the result of the experiment showing the effect of the present invention corresponding to claim 1. FIG. 6 is a diagram showing the relationship between the damping ratio and the equivalent plate thickness ratio in the example and the conventional example, and FIG. 6 is a diagram showing the results of an experiment showing the effect of the present invention corresponding to claim 1, and the rigidity values in the example and the conventional example. Fig. 7 is a diagram showing the relationship between the ratio of the rigidity value of the flat plate and the equivalent plate thickness, and the equivalent plate thickness ratio. Fig. 7 is a diagram showing the results of an experiment showing the effect of the present invention corresponding to claim 2. Diagram of the ratio and equivalent plate thickness ratio,
FIG. 8 is a diagram showing a result of an experiment showing an effect of the present invention corresponding to claim 2, and is a relational diagram of a ratio between a rigidity value in a working example and a conventional example and a rigidity value in a flat plate, and an equivalent plate thickness ratio. Is.
【００２４】図１において、１１は主板１２の両面を補
助板１３で挟みんだ請求項１に対応する本発明の複合制
振金属板であり、主板１２の形状を、（ａ）に示すよう
に例えば長さ方向に波形となしたり、また、（ｂ）に示
すように例えば長さ方向にハット状の凹凸形となした
り、また、（ｃ）に示すように長さ方向及び幅方向にハ
ット状の凹凸形となしたりしているのである。In FIG. 1, 11 is a composite vibration-damping metal plate of the present invention corresponding to claim 1 in which both sides of the main plate 12 are sandwiched by auxiliary plates 13. The shape of the main plate 12 is as shown in FIG. For example, as shown in (b), for example, a wavy corrugated shape is formed in the length direction, or as shown in (c), in the length direction and the width direction. It has a hat-shaped concavo-convex shape.
【００２５】上記した請求項１に対応する本発明の複合
制振金属板１１の効果を確認するために、長さ２０００
ｍｍ、幅１０００ｍｍ、厚さ４ｍｍの鋼板を、幅方向
にピッチが１００ｍｍで、高さが１０，２０，３０，４
０ｍｍの波形に形成したもの〔図３（ａ）〕、幅方向
にピッチが１００ｍｍで、高さが１０，２０，３０，４
０ｍｍのハット状の凹凸形に形成したもの〔図３
（ｂ）〕、幅及び長さ方向にピッチが１００ｍｍで、
高さが１０，２０，３０，４０ｍｍのハット状の凹凸形
に形成したもの〔図３（ｃ）〕、を主板１２とし、これ
らの主板１２の両面をそれぞれ厚さ０．３ｍｍの１枚の
補助板１３で挟み、その周囲４点を点溶接して複合制振
金属板１１を作成した。比較として、長さ２０００ｍ
ｍ、幅１０００ｍｍ、厚さ４ｍｍの鋼板を平板のまま主
板とし、これの両面をそれぞれ厚さ０．３ｍｍの１枚の
補助板で挟み、その周囲４点を点溶接して従来の複合制
振金属板を作成した。In order to confirm the effect of the composite vibration damping metal plate 11 of the present invention corresponding to the above-mentioned claim 1, the length 2000
mm, width 1000 mm, thickness 4 mm, steel plate with a pitch of 100 mm and a height of 10, 20, 30, 4 in the width direction.
Formed in a waveform of 0 mm [Fig. 3 (a)], with a pitch of 100 mm in the width direction and heights of 10, 20, 30, 4
Formed in 0 mm hat-shaped concavo-convex shape [Fig. 3
(B)], with a pitch of 100 mm in the width and length directions,
What is formed in a hat-shaped concavo-convex shape having a height of 10, 20, 30, 40 mm [Fig. 3 (c)] is used as a main plate 12, and both sides of each of the main plates 12 have a thickness of 0.3 mm. The composite vibration-damping metal plate 11 was created by sandwiching the auxiliary plate 13 and spot welding four points around the auxiliary plate 13. For comparison, length 2000m
A steel plate of m, width of 1000 mm, and thickness of 4 mm is used as a main plate as a flat plate, both sides of which are sandwiched by one auxiliary plate of thickness 0.3 mm, and four points around the same are spot-welded to form a conventional composite vibration control. I made a metal plate.
【００２６】上記したそれぞれの複合制振金属板を、図
４に示すように、長さ方向の両端を治具１４で固定した
後に裏面側中央部を加振機１５で定常状態になるまで加
振した後加振を止め、その後、非接触変位計１６を用い
て表面側中央部の減衰波形を測定した。そして、得られ
た減衰波形から対数減衰比を求め、さらに減衰比を計算
した。また、同時に各複合制振金属板の曲げ剛性も測定
した。得られた減衰比と相当板厚比との関係を図５に、
また、得られた剛性値と平板での剛性値との比と相当板
厚比との関係を図６に示す。なお、図５、図６における
測定点に記載した括弧内の数字は波形，ハット状の凹凸
形の高さである。As shown in FIG. 4, each of the above-described composite vibration-damping metal plates is fixed at both ends in the lengthwise direction by jigs 14, and then the center portion on the back surface side is shaken by a vibrator 15 until a steady state is reached. After shaking, the vibration was stopped, and thereafter, the damping waveform of the central portion on the front surface side was measured using the non-contact displacement meter 16. Then, the logarithmic damping ratio was obtained from the obtained damping waveform, and the damping ratio was calculated. At the same time, the flexural rigidity of each composite damping metal plate was also measured. The relationship between the obtained damping ratio and the equivalent plate thickness ratio is shown in FIG.
Further, FIG. 6 shows the relationship between the ratio of the obtained rigidity value and the rigidity value of the flat plate and the equivalent plate thickness ratio. The numbers in parentheses described at the measurement points in FIGS. 5 and 6 are the heights of corrugated and hat-shaped concavo-convex shapes.
【００２７】図５より明らかなように、減衰比は従来例
と比較してやや減少するが、単板（図５中の一点鎖線）
よりは十分高く、十分な制振性能を有していることが判
る。また、図６より明らかなように、曲げ剛性は従来例
より大幅に高くなることが判る。これより、等しい強度
を持たせるためにはより薄い金属板を主板として使用す
ることが可能であることが明らかである。また、主板を
薄くできることから補助板の板厚も薄くできるので、軽
量化を図りつつ高い制振性能を持つ複合制振金属板を得
ることが可能となる。なお、図６に示すように、曲げ剛
性は図３（ｂ）（ｃ）に示す実施例ともに同じ値である
が、これは本実験では一方向（幅方向）からの曲げ剛性
のみ測定した結果だからである。As is apparent from FIG. 5, the damping ratio is slightly reduced as compared with the conventional example, but a single plate (dashed line in FIG. 5)
It can be seen that it has a sufficiently high vibration damping performance. Further, as is clear from FIG. 6, it is found that the bending rigidity is significantly higher than that of the conventional example. From this, it is clear that a thinner metal plate can be used as the main plate in order to have equal strength. Further, since the main plate can be made thin, the plate thickness of the auxiliary plate can also be made thin, so that it is possible to obtain a composite vibration-damping metal plate having high vibration-damping performance while achieving weight reduction. As shown in FIG. 6, the flexural rigidity has the same value in the examples shown in FIGS. 3B and 3C, but this is the result of measuring only the flexural rigidity from one direction (width direction) in this experiment. That's why.
【００２８】図２において、１１’は請求項２に対応す
る本発明の複合制振金属板であり、図２（ａ）〜（ｃ）
はそれぞれ図１（ａ）〜（ｃ）に示す請求項１に対応す
る本発明の複合制振金属板１１における、結合部に金属
棒１７を挿入したものである。In FIG. 2, 11 'is the composite vibration-damping metal plate of the present invention corresponding to claim 2, and is shown in FIGS.
Is a composite vibration-damping metal plate 11 of the present invention corresponding to claim 1 shown in FIGS.
【００２９】上記した請求項２に対応する本発明の複合
制振金属板１１’の効果を確認するために、長さ２００
０ｍｍ、幅１０００ｍｍ、厚さ４ｍｍの鋼板を使用して
幅方向にピッチが１００ｍｍで、高さが１０ｍｍの波形
に形成し、断面半径が５，１０，２０，４０，６０ｍｍ
の金属棒１７を長さ方向に２５０ｍｍピッチで幅方向に
２波毎に挿入し、溶接したものを主板１２とし、これら
の主板１２の両面をそれぞれ厚さ０．３ｍｍの１枚の補
助板１３で挟み、その周囲４点を点溶接して複合制振金
属板１１’を作成した。比較として、金属棒を挿入しな
い上記した波板を主板１２とし、その両面をそれぞれ厚
さ０．３ｍｍの１枚の補助板１３で挟み、その周囲４点
を点溶接した請求項１に対応する複合制振金属板や、長
さ２０００ｍｍ、幅１０００ｍｍ、厚さ４ｍｍの鋼板を
平板のまま主板とし、これの両面をそれぞれ厚さ０．３
ｍｍの１枚の補助板で挟み、その周囲４点を点溶接して
従来の複合制振金属板を作成した。In order to confirm the effect of the composite damping metal plate 11 'of the present invention corresponding to the above-mentioned claim 2, the length 200
A steel plate having a width of 0 mm, a width of 1000 mm, and a thickness of 4 mm is used to form a corrugation having a pitch of 100 mm in the width direction and a height of 10 mm, and a cross-sectional radius of 5, 10, 20, 40, 60 mm.
The metal rods 17 are inserted into the lengthwise direction at a pitch of 250 mm every two waves in the widthwise direction and welded to form the main plate 12, and both sides of these main plates 12 are one auxiliary plate 13 each having a thickness of 0.3 mm. The composite vibration damping metal plate 11 ′ was prepared by sandwiching and sandwiching four points around it. For comparison, it corresponds to claim 1 in which the above-mentioned corrugated plate into which a metal rod is not inserted is used as a main plate 12, both surfaces thereof are sandwiched by one auxiliary plate 13 having a thickness of 0.3 mm, and four points around the auxiliary plate 13 are spot-welded. A composite vibration-damping metal plate or a steel plate having a length of 2000 mm, a width of 1000 mm, and a thickness of 4 mm is used as a flat plate as a main plate, and both surfaces thereof have a thickness of 0.3.
It was sandwiched by one mm auxiliary plate, and four points around the auxiliary plate were spot-welded to produce a conventional composite vibration-damping metal plate.
【００３０】上記したそれぞれの複合制振金属板を、図
４に示すように、長さ方向の両端を治具１４で固定した
後に裏面側中央部を加振機１５で定常状態になるまで加
振した後加振を止め、その後、非接触変位計１６を用い
て表面側中央部の減衰波形を測定した。そして、得られ
た減衰波形から対数減衰比を求め、さらに減衰比を計算
した。また、同時に各複合制振金属板の曲げ剛性も測定
した。得られた減衰比と相当板厚比との関係を図７に、
また、得られた剛性値と平板での剛性値との比と相当板
厚比との関係を図８に示す。As shown in FIG. 4, each of the above-described composite vibration-damping metal plates is fixed at both ends in the lengthwise direction by jigs 14, and then the center portion on the back surface side is shaken by a vibrator 15 until a steady state is reached. After shaking, the vibration was stopped, and thereafter, the damping waveform of the central portion on the front surface side was measured using the non-contact displacement meter 16. Then, the logarithmic damping ratio was obtained from the obtained damping waveform, and the damping ratio was calculated. At the same time, the flexural rigidity of each composite damping metal plate was also measured. The relationship between the obtained damping ratio and the equivalent plate thickness ratio is shown in FIG.
FIG. 8 shows the relationship between the ratio of the obtained rigidity value and the rigidity value of a flat plate and the equivalent plate thickness ratio.
【００３１】図７より明らかなように、減衰比は従来例
と比較してやや減少するが、単板（図７中の一点鎖線）
よりは十分高く、さらに金属棒を挿入することによって
減衰比は請求項１に対応する複合制振金属板よりも従来
例に近くなっていることが判る。また、図８より明らか
なように、曲げ剛性は従来例より大幅に高くなり、また
請求項１に対応する複合制振金属板よりもさらに高くな
ることが判る。これより、等しい強度を持たせるために
はより薄い金属板を主板として使用することが可能であ
ることが明らかである。また、主板を薄くできることか
ら補助板の板厚も薄くできるので、軽量化を図りつつ高
い制振性能を持つ複合制振金属板を得ることが可能とな
る。さらに、金属棒を予め挿入しておくことにより、３
枚の鋼板を点接合することが容易になるという利点も確
認できた。As is clear from FIG. 7, the damping ratio is slightly reduced as compared with the conventional example, but a single plate (dashed line in FIG. 7)
It is found that the damping ratio is much higher than that of the conventional example and the damping ratio is closer to that of the conventional vibration damping metal plate by inserting the metal rod. Further, as is clear from FIG. 8, it is understood that the bending rigidity is significantly higher than that of the conventional example, and is even higher than that of the composite damping metal plate corresponding to claim 1. From this, it is clear that a thinner metal plate can be used as the main plate in order to have equal strength. Further, since the main plate can be made thin, the plate thickness of the auxiliary plate can also be made thin, so that it is possible to obtain a composite vibration-damping metal plate having high vibration-damping performance while achieving weight reduction. Furthermore, by inserting a metal rod in advance,
It was also confirmed that the advantage of facilitating spot welding of one steel plate was obtained.
【００３２】なお、金属棒１７に代えて金属管を挿入し
た場合にはより軽量化をはかることができることはいう
までもない。この場合、金属管を金属棒と同様に溶接し
てもよいが、ボルト等を用いて取り付けてもよい。Needless to say, when a metal tube is inserted instead of the metal rod 17, the weight can be further reduced. In this case, the metal tube may be welded in the same manner as the metal rod, but may be attached using bolts or the like.
【００３３】[0033]
【発明の効果】以上説明したように、本発明の複合制振
金属板は、その両面を補助板で挟んだ主板の形状を、長
さ方向又は幅方向に波形又はハット状の凹凸形、若しく
は長さ方向及び幅方向にハット状の凹凸形となしている
ので、同一厚さの主板を用いた場合、複合制振金属板の
曲げ剛性を大きくすることが可能となる。この効果よ
り、等しい曲げ剛性を有する複合制振金属板を作成する
場合には、主板や補助板の板厚を薄くでき、軽量化が図
れる。As described above, in the composite vibration-damping metal plate of the present invention, the shape of the main plate whose both sides are sandwiched by the auxiliary plates has a corrugated or hat-shaped concavo-convex shape in the length direction or the width direction, or Since the hat-shaped concavo-convex shape is formed in the length direction and the width direction, when the main plate having the same thickness is used, the bending rigidity of the composite vibration-damping metal plate can be increased. Due to this effect, in the case of producing a composite vibration-damping metal plate having the same bending rigidity, the plate thickness of the main plate and the auxiliary plate can be reduced, and the weight can be reduced.
【００３４】また、結合部に金属棒を挿入したり、ま
た、結合部に金属管を挿入し、ボルトを用いて結合した
りすれば、複合制振金属板の作成が容易になるとともに
複合制振金属板全体の強度が更に向上する。If a metal rod is inserted into the joint portion or a metal tube is inserted into the joint portion and they are joined with bolts, the composite vibration-damping metal plate can be easily manufactured and the composite damping metal plate can be manufactured. The strength of the entire vibration metal plate is further improved.
【図１】図１は請求項１に対応する本発明の複合制振金
属板の実施例を示す斜視図で、（ａ）はその第１実施
例、（ｂ）は第２実施例，（ｃ）は第３実施例である。FIG. 1 is a perspective view showing an embodiment of a composite vibration damping metal plate of the present invention corresponding to claim 1, (a) is the first embodiment, (b) is the second embodiment, c) is the third embodiment.
【図２】請求項２に対応する本発明の複合制振金属板の
実施例を示す斜視図で、（ａ）はその第１実施例、
（ｂ）は第２実施例，（ｃ）は第３実施例である。2 is a perspective view showing an embodiment of a composite vibration-damping metal plate of the present invention corresponding to claim 2, (a) is the first embodiment thereof, FIG.
(B) is the second embodiment, and (c) is the third embodiment.
【図３】本発明の効果を示す実験に用いた請求項１に対
応する本発明の複合制振金属板の実施例を示す斜視図
で、（ａ）はその第１実施例、（ｂ）は第２実施例，
（ｃ）は第３実施例である。FIG. 3 is a perspective view showing an embodiment of the composite vibration-damping metal plate of the present invention corresponding to claim 1, which is used in an experiment showing the effect of the present invention, wherein (a) is the first embodiment and (b) thereof. Is the second embodiment,
(C) is a third embodiment.
【図４】本発明の効果を示す実験に用いた治具の斜視図
である。FIG. 4 is a perspective view of a jig used in an experiment showing the effect of the present invention.
【図５】請求項１に対応する本発明の効果を示す実験の
結果を示す図で、実施例及び従来例における減衰比と相
当板厚比との関係図である。FIG. 5 is a diagram showing a result of an experiment showing an effect of the present invention corresponding to claim 1, and is a relationship diagram between the damping ratio and the equivalent plate thickness ratio in the example and the conventional example.
【図６】請求項１に対応する本発明の効果を示す実験の
結果を示す図で、実施例及び従来例における剛性値と平
板での剛性値との比と、相当板厚比との関係図である。FIG. 6 is a diagram showing a result of an experiment showing an effect of the present invention corresponding to claim 1, showing a relationship between a ratio of a rigidity value in a working example and a conventional example and a rigidity value of a flat plate, and an equivalent plate thickness ratio. It is a figure.
【図７】請求項２に対応する本発明の効果を示す実験の
結果を示す図で、実施例及び従来例における減衰比と相
当板厚比との関係図である。FIG. 7 is a diagram showing a result of an experiment showing an effect of the present invention corresponding to claim 2, and is a relationship diagram between the damping ratio and the equivalent plate thickness ratio in the example and the conventional example.
【図８】請求項２に対応する本発明の効果を示す実験の
結果を示す図で、実施例及び従来例における剛性値と平
板での剛性値との比と、相当板厚比との関係図である。FIG. 8 is a diagram showing the results of an experiment showing the effect of the present invention corresponding to claim 2, and showing the relationship between the ratio of the rigidity value of the example and the conventional example and the rigidity value of the flat plate, and the equivalent plate thickness ratio. It is a figure.
【図９】矩形状の平板の斜視図である。FIG. 9 is a perspective view of a rectangular flat plate.
【図１０】（ａ）は波板の斜視図、（ｂ）は波板端面の
拡大図である。10A is a perspective view of a corrugated plate, and FIG. 10B is an enlarged view of an end face of the corrugated plate.
【図１１】板厚ｈ及び波のピッチ長さｂが等しいが波の
高さｂh が異なる波板において、波の高さｂh の変化に
対する曲げ剛性の比Ｄ1 ／Ｄの変化を表した図である。[11] In although plate thickness h and wave pitch length b equal corrugated plate height b h of the wave are different, the table changes the ratio D 1 / D of the bending stiffness with respect to a change in the height b h of the wave FIG.
【図１２】板厚ｈ及び波のピッチ長さｂが等しい場合に
おける、波の高さｂh の変化に対する相当板厚と実際の
板厚との比（相当板厚比）を表した図である。[Figure 12] when the plate thickness h and wave pitch length b are equal, a diagram showing the ratio (equivalent plate thickness ratio) between the actual plate thickness and the corresponding thickness to changes in wave height b h is there.
【図１３】（ａ）は金属棒を挿入した波板の斜視図、
（ｂ）は金属棒を挿入した波板端面の拡大図である。FIG. 13A is a perspective view of a corrugated plate into which a metal rod is inserted,
(B) is an enlarged view of an end face of a corrugated plate into which a metal rod is inserted.
【図１４】板厚ｈ、波のピッチ長さｂ及び波の高さｂh
が等しい波板において、金属棒の断面直径ｃの波のピッ
チ長さｂに対する比ｃ／ｂの変化に対する曲げ剛性の比
Ｄ 2 ／Ｄ1 の変化を表した図である。FIG. 14 is a plate thickness h, a wave pitch length b, and a wave height b.h
In a corrugated plate with equal
B Ratio of bending rigidity to change in ratio c / b to length b
D 2/ D1It is a figure showing the change of.
【図１５】板厚ｈ、波のピッチ長さｂ及び波の高さｂh
が等しい波板において、金属棒の断面直径ｃの波のピッ
チ長さｂに対する比ｃ／ｂの変化に対する相当板厚と実
際の板厚との比（相当板厚比）を表した図である。FIG. 15: Plate thickness h, wave pitch length b, and wave height b h
FIG. 6 is a diagram showing a ratio (corresponding plate thickness ratio) between an equivalent plate thickness and an actual plate thickness with respect to a change in a ratio c / b of a cross-sectional diameter c of a metal rod to a pitch length b of a wave in a corrugated plate having the same value. .
【図１６】従来の複合制振金属板の斜視図である。FIG. 16 is a perspective view of a conventional composite vibration damping metal plate.
１１ 複合制振金属板 １２ 主板 １３ 補助板 １７ 金属棒 11 Composite Vibration Control Metal Plate 12 Main Plate 13 Auxiliary Plate 17 Metal Rod
Claims (2)
と補助板とを部分的に結合した複合制振金属板であっ
て、主板の形状を、長さ方向又は幅方向に波形又はハッ
ト状の凹凸形、若しくは長さ方向及び幅方向にハット状
の凹凸形となしたことを特徴とする複合制振金属板。1. A composite vibration-damping metal plate in which both sides of a main plate are sandwiched by auxiliary plates, and the main plate and the auxiliary plate are partially connected to each other, and the shape of the main plate is corrugated or hated in a length direction or a width direction. A composite vibration-damping metal plate characterized by having a concave-convex shape or a hat-shaped uneven shape in the length direction and the width direction.
金属棒又は金属管を挿入することを特徴とする請求項１
記載の複合制振金属板。2. A metal rod or a metal tube is inserted into an appropriate place of the corrugated or hat-shaped concavo-convex portion.
The composite vibration damping metal plate described.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5885395A JPH08254244A (en) | 1995-03-17 | 1995-03-17 | Composite damping metal plate |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5885395A JPH08254244A (en) | 1995-03-17 | 1995-03-17 | Composite damping metal plate |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08254244A true JPH08254244A (en) | 1996-10-01 |
Family
ID=13096253
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5885395A Pending JPH08254244A (en) | 1995-03-17 | 1995-03-17 | Composite damping metal plate |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08254244A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1861616A1 (en) * | 2005-03-14 | 2007-12-05 | Robert Bosch Gmbh | Intermediate element for a fuel injection valve |
| US20140367999A1 (en) * | 2011-12-20 | 2014-12-18 | Nippon Steel & Sumitomo Metal Corporation | Front floor panel |
-
1995
- 1995-03-17 JP JP5885395A patent/JPH08254244A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1861616A1 (en) * | 2005-03-14 | 2007-12-05 | Robert Bosch Gmbh | Intermediate element for a fuel injection valve |
| JP2008533374A (en) * | 2005-03-14 | 2008-08-21 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Intermediate element for fuel injection valve |
| US20140367999A1 (en) * | 2011-12-20 | 2014-12-18 | Nippon Steel & Sumitomo Metal Corporation | Front floor panel |
| US9296430B2 (en) * | 2011-12-20 | 2016-03-29 | Nippon Steel & Sumitomo Metal Corporation | Front floor panel |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A02 | Decision of refusal |
Effective date: 20040427 Free format text: JAPANESE INTERMEDIATE CODE: A02 |