JP4562959B2

JP4562959B2 - Floating body mooring device with non-linear reaction force characteristics

Info

Publication number: JP4562959B2
Application number: JP2001199212A
Authority: JP
Inventors: 寛大久保; 勝彦井口
Original assignee: Nippon Steel Engineering Co Ltd
Current assignee: Nippon Steel Engineering Co Ltd
Priority date: 2001-06-29
Filing date: 2001-06-29
Publication date: 2010-10-13
Anticipated expiration: 2021-06-29
Also published as: JP2003011883A

Description

【０００１】
【発明の属する技術分野】
本発明は海上に浮遊する大規模浮体構造物等の浮体を係留する装置であって、暴風時の係留外力を軽減可能な係留装置に関する。
【０００２】
【従来の技術】
浮体人工島等に利用される大規模浮体の係留装置は平常時の波浪、潮流、風荷重などの外力に対してはできるだけ動揺が小さく、暴風時の波浪・風荷重に対してはある程度の動揺を許容することによって係留力を小さくして安全に係留することが求められる。また、浮体とのアクセス等のため船舶接舷に障害とならないような係留方式が望ましい。なお、超大型の大規模浮体では外気温の変化による浮体の膨張収縮が数ｍにもなるため係留装置はこれを吸収する必要がある。
【０００３】
従来から浮体の係留方式には、海底に設置したアンカーやシンカーと浮体をチェーンやワイヤロープ等の係留索で連結する係留索方式と、係留用のドルフィンや岸壁と浮体間にゴムフェンダーを介在させて係留するゴムフェンダー方式が知られている。
【０００４】
前者の係留索方式は平常時の波浪、潮流及び風荷重等の定常外力等の比較的小さい外力に対してはカテナリー係留のため水平移動量が大きく、係留設備の占有範囲が大きくなる欠点がある。また、暴風時の外力に対抗するため浮体の周りに大型の係留索を多数設置する必要があり付近の船舶航行に支障がある。
【０００５】
一方、後者のゴムフェンダー方式の場合は、ばね係数が大きいため平常時の変位量を小さくでき付近の船舶航行に支障を及ぼすような問題はないが、変形能力（ストローク）が小さいため暴風時に過大な作用外力が生じる。また、外気温の変化による浮体の膨張収縮による浮体の面内変形を吸収可能とする場合は変形能力の増大対策が必要となる。
現在、国内で市販されている最大級のゴムフェンダーはセル型のフェンダー（外径約３ｍ、長さ３ｍ、設計限界歪み（５０％）時の変形能力１．５ｍ、最大反力約４００ｔ〜６００ｔ）である。
【０００６】
このゴムフェンダーの変形能力を増大するには複数個直列に接続して使用する手段があり、特開平６−１４４３５６等で開示されているものがある。なお、特別に変形能力の大きな長尺フェンダーを製作することが考えられるが、ねじれ座屈の問題があり難しい。
【０００７】
【発明が解決しようとする課題】
通常、係留装置の設計係留力は暴風時に生じる最大作用外力に対して安全なように決定される。この暴風時に生じる作用外力は反力体（係留装置）の変位量と相関関係があり、係留装置の変形が制限される場合は作用外力が大きく、大きな変位を許容すればエネルギーを吸収して作用外力を減じることができる。従って、暴風時において作用外力を小さくするには係留装置に大きな変位を生じさせて係留した方が有利となる。
【０００８】
前述のゴムフェンダー方式の場合、単独使用では変形能力が小さいため暴風時に過大な外力が生じるため反力容量の大きな多数の大型フェンダーを並列に使用して対抗する必要がある。なお、複数個を直列に接続して変形能力を増大した場合はいくらか外力を低減できるが、大型フェンダーの使用個数が多くなることに変わりはなく、係留設備に高額投資が必要となる課題があった。
【０００９】
また、大型ゴムフェンダーを複数個直列接続しても変形能力の増大に制約があり、且つねじれ座屈の対策が必要になるためさらに設備費が増大する。
【００１０】
本発明は、平常時の外力に対しては浮体変位量を抑え、且つ暴風時の浮体変位を許容して作用外力を減じることにより経済的な係留装置を提供することを目的としたものである。
【００１１】
【課題を解決する手段】
本発明の要旨は以下のとおりである。
【００１２】
第１の発明は、海底に設置された基体に浮体を係留する係留装置であって、ストッパーにより変位した状態を維持することで初期反力を導入したばね係数の小さい弾性体Ａと、該弾性体Ａより大きいばね係数の弾性体Ｂを用い、浮体の係留力を前記弾性体Ｂから弾性体Ａに伝達させ、係留力が前記弾性体Ａの初期反力を超えた際に前記弾性体Ａが変位するようにしたことを特徴とする非線形反力特性を備えた浮体係留装置である。
【００１３】
第２の発明は、第１の発明において、海底に設置された基体から水平突設された支持体に弾性体Ａの一端を固定し、前記支持体にピン結合した弾性体Ｂを垂下し、前記弾性体Ａを伸長または圧縮状態でストッパーにより一方の水平変位を規制して弾性体Ｂの上端部に連結して弾性体Ａに初期反力を導入しておき、前記弾性体Ｂの下部に浮体から突設した係留材を上下移動可能に当接させ、潮位変化に応じて浮体の一方向の水平変位をばね係数の異なる弾性体Ａと弾性体Ｂによって支持したことを特徴とする。
【００１４】
第３の発明は、第２の発明の係留装置を、浮体の片側に設置した基体上に互いに相反する方向の水平変位を支持するように並列して設け、浮体の左右方向の水平変位を支持するようにしたことを特徴とする非線形反力特性を備えた浮体係留装置である。
【００１５】
第４の発明は、第１の発明において、海底に設置された基体から水平突設された支持体の両端に弾性体Ａ１と弾性体Ａ２を対向させてそれぞれの一端を固定し、前記支持体にピン結合した弾性体Ｂ1と弾性体Ｂ２を垂下し、前記弾性体Ａ１、弾性体Ａ２を伸長または圧縮状態でそれぞれのストッパーに相反する各一方向の水平変位を規制して弾性体Ｂ１、弾性体Ｂ２の上端部に連結して弾性体Ａ１、弾性体Ａ２に相反する方向の初期反力を導入しておき、それぞれの弾性体Ｂ1、弾性体Ｂ２の下部に浮体から突設した係留材を上下移動可能に当接させ、潮位変化に応じて浮体の左右両方向の水平変位をばね係数の異なる弾性体Ａ１，Ａ２と弾性体Ｂ１，Ｂ２によって支持したことを特徴とする。
【００１６】
第５の発明は、第１の発明において、一端に反力板Ａを設け他端に孔明きストッパーを設けた小径円筒の孔明きストッパー側に、一端を開口し他端に反力板を設けた大径円筒をスライド自在に被せ、前記小径円筒内には前記ストッパーで変位を規制して初期圧縮力を導入した弾性体Ａを収納し、大径円筒内には反力板に圧縮力のみ伝達するようにした弾性体Ｂを収納し、小径円筒と大径円筒の両方に渡って前記孔明きストッパーの孔を通して弾性体Ａと弾性体Ｂを連結するロッドが配置しており、浮体の係留力をばね係数の大きい弾性体Ｂをロッドを介して初期圧縮力を導入したばね係数の小さい弾性体Ａに圧縮力として伝達し、この圧縮力がストッパーで規制された初期圧縮力を超えた際に弾性体Ａを変位させるようにしたことを特徴とする。
【００１７】
第６の発明は、第１の発明において、一端に反力板を設け他端に孔明きストッパーを設けた小径円筒のストッパー側に、一端を開口し他端に反力板を設けた大径円筒をスライド自在に被せ、小径円筒内には反力板に一端を固定した弾性体Ａを収納し、大径円筒内には、反力板に一端を固定した弾性体Ｂと弾性体Ａと弾性体Ｂを連結するロッド付連結具を収納し、
前記弾性体Ａと前記ロッド付連結具とが、前記孔明きストッパーの孔を挿通したロッドによって、弾性体Ａに初期張力を導入した状態で連結され、弾性体Ａと弾性体Ｂには引張力のみが伝達されるようになっており、浮体の係留力をばね係数の大きい弾性体Ｂを介して初期引張力を導入したばね係数の小さい弾性体Ａに引張力として伝達し、この引張力がストッパーで規制された初期引張力を超えた際に弾性体Ａを変位させるようにしたことを特徴とする。
【００１８】
第７の発明は、第５の発明および第６の発明の係留装置を、浮体の片側に設置した基体上に並列して設け、浮体の左右方向の水平変位を支持するようにしたことを特徴とする非線形反力特性を備えた浮体係留装置である。
【００１９】
第８の発明は、第５から第７の発明のいずれか１つの発明において、小径円筒の反力板および大径円筒の反力板に自在継手を設け、該自在継手を介して海底に設置された基体と、浮体を連結するようにしたことを特徴とする。
【００２０】
＜作用＞
本発明のポイントは、平常時の波浪、潮流、風荷重等の比較的小さな外力に対しては弾性体Ａの初期反力内でばね係数の大きな弾性体Ｂで係留して浮体の動揺を抑え、弾性体の初期反力を超えるような暴風時の大きな外力に対してはばね係数の小さい弾性体Ａを可動させ浮体の変位を許容してエネルギーを吸収させるようにした非線形反力特性を備えた係留装置として、暴風時の作用外力を軽減させることにより設計を有利にしたものである。
【００２１】
図１３は、ばね係数の異なる係留装置の変形と係留装置反力の関係を本発明と比較例を合わせて示したものである。図１３において、（ａ）は、ばね係数の大きな線形もしくは反力漸増形の反力特性の係留装置における変形と反力の関係を示す。（ｂ）は、ばね係数の小さな線形もしくは反力漸増形の反力特性の係留装置における変形と反力の関係を示す。（ｃ）は、本発明の非線形反力特性を備えた係留装置における変形と反力の関係を示す。
【００２２】
比較例（ａ）は係留装置の変形が小さく平常時は小さな変位量(a1）のため問題ないが、暴風時に大きな反力(a2)が生じるため設計外力が過大になる。
比較例（ｂ）は係留装置の変形が大きいため暴風時においてエネルギーを吸収して小さな反力（b2）となり、暴風時の設計外力を小さくできるが、平常時の変位量(b1)が大きくなる。
【００２３】
一方、（ｃ）は本発明の係留装置であって、ストッパーで初期反力を導入した小さなばね係数を有する弾性体Ａと、係留材からの係留力を伝達する大きなばね係数の弾性体Ｂを組合わせた非線型反力特性を有するもので、平常時の小外力に対しては弾性体Ａに導入した初期反力内で弾性体Ｂのみが作用して比較的小さな変位量(c1)で係留し、弾性体Ａに導入した初期反力を超えるような暴風時の外力に対しては弾性体Ａが作動して大きな変位を許容してエネルギーを吸収することにより発生反力(c2)が小さくなるため設計外力を低減できる。なお、図１３の反力Riはストッパーで弾性体Ａに導入した初期反力値である。
【００２４】
【発明の実施形態と実施例】
図１〜図９は本発明に係るレバー方式の係留装置１に関する実施形態を示したものである。
図１は、第１実施形態の例であって、１方向の水平変位を規制する係留装置１を浮体２の左右側に設置した基体３上に設けて浮体２を挟み込むようにして左右方向の水平変位を支持するようにしたものである。
【００２５】
係留装置１は海底４に設置されたドルフィン等の基体３から水平突設された支持体５に所定のばね係数kaで伸縮するコイルばね、空圧シリンダー等からなる弾性体Ａの一端を固定し、弾性体Ａの他端を支持体５にピン結合した垂下弾性体Ｂの支持部材６上端部に間隔L1をおいて連結している。
前記支持体５には、弾性体Ａと反対側の支持部材取付ピン９下側にストッパー７が間隔L2をおいて設けられており、このストッパー７により垂下弾性体Ｂの支持部材６の一方（右方向）の変位が規制され、前記弾性体Ａに導入した初期引張力Riを保持している。
【００２６】
浮体２の係留は弾性体Ｂの下方において、浮体２から突設した係留材２ａを当接して行う。ここで、浮体２は潮位差で係留装置１と相対的に上下に動くため、弾性体Ｂと係留材２ａを自由に当接させて潮位変動に追随して上下移動可能としている。
【００２７】
前記支持部材６の下方に延在する弾性体Ｂは、例えば普通鋼を弾性領域で使用する板ばねを用いることができる。なお、この板ばねは上部の支持部材６と一体的にしてもよい。
この弾性体Ｂは前記弾性体Ａより大きいばね係数kbを有し（ka＜kb）、暴風時の作用外力に対抗できる耐力を備えたものとする必要がある。また、係留材２ａと接触して上下に移動を繰返すため耐摩耗性のよいものを使用する必要がある。
【００２８】
図２は、係留装置１が静止時（浮体の係留力が作用しない状態）、平常時の外力を受けた際および暴風時の外力を受けた際の弾性体Ａ、弾性体Ｂの動きを表したものである。
（ａ）弾性体Ｂに浮体２の係留力が作用しない状態（図２ａ）では、弾性体Ａの初期張力Riは全てストッパー７の反力Rsで受け持ち、RiとRsの関係は、Ri×L1＝Rs×L2である。
（ｂ）平常時の外力P1に対しては弾性体Ｂはストッパー７から離脱することなく、kbのばね係数によって生じる小さな変形で応答し、弾性体Ａの張力は初期張力Ri、ストッパー７の反力はRs−ΔRs(＞0)となる（図２ｂ参照）。
（ｃ）暴風時の外力P2では、弾性体Ｂに作用した大きな外力P2が初期張力Riを超えると、P2×L3＞Ri×L1となり、弾性体Ｂを支える支持部材６がストッパー７から離脱し、弾性体Ａがばね係数kaで伸張して浮体２に大きな変位を生じさせる（図２ｃ参照）。この結果、弾性体Ａの弾性変形により浮体２の外力エネルギーが吸収される。
なお、（ｃ）の状態では外力P2と弾性体Ａの荷重バランスは、
P2×L3＝（Ri＋ΔRi2）×L1となる。
【００２９】
図３は、第２実施形態を示すもので、係留装置１側から離れる方向の浮体２の移動を規制する係留装置１である。第２実施形態では、弾性体Ａ、ストッパーは第１実施形態とは反対側に設け、浮体２から突設した係留材２ａには弾性体Ｂを引寄せるローラー支承８を用いる。
第２実施形態と第１実施形態の係留装置を交互に配置すれば、浮体の一方の側のみに設置した基体で係留することができる。
【００３０】
図４は第３実施形態を示すもので、初期反力導入手段を圧縮力としたものである。圧縮力を初期反力とした場合は、第１実施形態、第２実施形態とストッパー７の位置が異なる。すなわち、第３実施形態では、支持体５上方で、圧縮力を導入した弾性体Ａが支持体５と垂下弾性体Ｂの支持部材６とに連結され、支持体５下方では弾性体Ａ側にストッパー７が設けられており、このストッパー７により垂下弾性体Ｂの支持部材６の一方（左方向）への変位が規制され、前記弾性体Ａに導入した初期圧縮力が保持される。
【００３１】
図５は第４実施形態を示すもので、引張力を導入した弾性体Ａの配置を基体３の支持体５下方にしたものである。この場合、ストッパー７は、支持体５に設けた支持部材取付けピン９と弾性体Ａとの間に配置する。
【００３２】
図６は、第５実施形態の係留装置の側面図であり、図７は、図６の平面図である。第５実施形態は、第１実施形態と第２実施形態とを組合わせた実施形態である。
第５実施形態の係留装置１では、海底４に設置された基体３から水平突設された支持体５の両端に弾性体Ａ１と弾性体Ａ２を対向させて配置し、支持体５にそれぞれの一端を固定している。前記支持体５には垂下した弾性体Ｂ１と弾性体Ｂ２がそれぞれピン結合されている。また、弾性体Ｂ1、Ｂ２の支持部材６上端部には、それぞれ前記弾性体Ａ１、Ａ２の他端が初期張力を導入した伸長状態で連結されている。
【００３３】
前記弾性体Ａ１、Ａ２に導入した初期張力はそれぞれ対応するストッパー７によって保持されている。このような構成によって弾性体Ｂ1と弾性体Ｂ２は相反する各一方向の水平変位を規制し、各反対方向の変位に対しては弾性体Ａ１、弾性体Ａ２に導入した初期張力（反力）で規制している。
【００３４】
弾性体Ｂ１、弾性体Ｂ２の下部には浮体２から突設した係留材２ａがローラー支承８を介して当接され、引寄せ・押当てるようにされており、左右方向の係留力が伝達される。また、この係留材２ａのローラー支承８は上下移動可能にされており、潮位変化があってもこれに追随できるようにしている。
このようにして、ストッパー７によって導入した初期反力を保持した小さいばね係数kaの弾性体Ａ１、弾性体Ａ２と大きなばね係数kbの弾性体Ｂ１、弾性体Ｂ２の異なったばね係数の非線形反力特性を備えた係留装置１によって浮体２の左右両方向の水平変位を支持している。
図８、図９は第５実施形態の係留装置１を用いて浮体２を一方の側に設置した基体３によって係留した場合の側面図と平面図である。
【００３５】
図１０〜図１２は本発明に係る円筒方式の係留装置１０の実施形態を示したものである。
【００３６】
図１０は、第６実施形態であって、浮体２が基体３に対して圧縮力として作用する際の円筒方式の係留装置１０ａである。
第６実施形態の係留装置１０ａは、小径円筒１１と、内径が小径円筒１１よりも大きい大径円筒１２とを組合せてなる。
小径円筒１１の一端には、基体３または浮体２に固定する反力板１１ａを設け、他端には孔明きストッパー１１ｂが設けられている。そして、小径円筒の孔明きストッパー１１ｂ側に、一端を開口し他端に反力板１２ａを設けた大径円筒１２を被せて、両円筒をスライド自在としている。
【００３７】
小径円筒１１内には、一端が反力板１１ａと連結されている弾性体Ａが収納され、大径円筒１２内には、反力板１２ａとは連結されないフリーの状態で、弾性体Ｂが収納される。そして、前記小径円筒１１と前記大径円筒１２との両方に渡って、弾性体Ａと弾性体Ｂとを連結するロッド１３が、前記孔明きストッパー１１ｂの孔を通るように配置されている。
【００３８】
前記弾性体Ａは所定のばね係数kaを有し、弾性体Ａには変位可能なコイルばねや空圧シリンダー等を用いることができる。また、弾性体Ｂは前記弾性体Ａのばね係数kaより大きいばね係数kbを有し（ka＜kb）、且つ弾性体Ｂは、暴風時の外力に耐える強度を備えた大容量のゴムフェンダーやコイルばね、鋼製ベローズなどから選択できる。
【００３９】
小径円筒１１内に収納されている弾性体Ａは、端部の孔明きストッパー１１ｂとロッド１３端部のアンカー部材１３ａで変位が規制されて平常時の係留力P1が範囲内に収まる所定の初期圧縮力Piが導入されている（P1＜Pi）。なお、初期圧縮力の導入手段は例えば反力板１１ａと小径円筒１１の端部をねじ接合とし、弾性体Ａを小径円筒１１に所定圧縮力で押込んだ状態でねじ接合すればよい。
【００４０】
前記孔明きストッパー１１ｂを通して配置されているロッド１３は浮体２の圧縮係留力を弾性体Ｂから弾性体Ａに伝達するもので、前記弾性体Ａの変位可能長さ以上移動でき、且つ暴風時の外力に耐える強度を備える必要がある。
【００４１】
前記ロッド１３に連結固定している弾性体Ｂは反力板１２ａに固定せず離間可能に当接させて圧縮力のみ伝達するようにしている。この理由は係留装置１０ａに引張力が作用した際にアンカー部材１３ａと孔明きストッパー１１ｂに過大な反力が生じるのを回避するためである。
【００４２】
図１０（ａ）は係留装置１０ａがフリー状態において引張力が作用した場合、すなわち基体３に対して浮体２が離れる方向に外力が働いた場合の状態を示すものである。この状態では弾性体Ｂは反力板１２ａに固定せず離間可能に当接させて圧縮力のみ伝達するようにしているため、係留装置１０ａはフリーに挙動する。
【００４３】
図１０（ｂ）は平常時の係留状態を示すもので、浮体２と基体３間に作用する係留時の圧縮力P1は弾性体Ａに導入した初期圧縮力Pi内であるため（P1＜Pi）、弾性体Ａには変位が生じないで弾性体Ｂのみにより大きなばね係数kbによって小さな変位で係留される。
【００４４】
図１０(ｃ)は暴風時の係留状態を示すもので、係留時の圧縮外力P2が弾性体Ａに導入した初期圧縮力Piを超えるため（Pi＜P2）、ロッド１３を介して伝達された係留力により弾性体Ａはストッパーから離れて変位する。この際、暴風時の外力は弾性体Ｂのばね係数kbによる変位と弾性体Ａのばね係数kaの変位によってエネルギーが吸収されて係留装置の反力を低減することができる。
【００４５】
以上の如く構成した係留装置１０ａによって、浮体２の係留力をばね係数の大きい弾性体Ｂをロッド１３を介して初期圧縮力を導入したばね係数の小さい弾性体Ａに圧縮力として伝達し、平常時の係留は弾性体Ｂによって小さな変位で係留し、弾性体Ａの初期圧縮力を超えた際（暴風時のような大きな圧縮外力が作用した場合）にばね係数の小さな弾性体Ａを変位させるようにして異なったばね係数の弾性体で係留力に対抗するようにした非線形反力特性を備えた浮体係留装置が実現する。
【００４６】
図１１は第７実施形態であって、浮体２が基体３に対して引張力として作用する際の円筒方式の係留装置１０ｂである。
【００４７】
第７実施形態の円筒方式の係留装置１０ｂが、第６実施形態の円筒方式の係留装置（圧縮力が作用する場合）と異なる点は、弾性体Ａに初期張力を導入した状態でロッド付連結具１４と連結し、弾性体Ｂと引張力のみ伝達するように連結している点である。
以下、第７実施形態が第６実施形態と異なる点のみ説明し、第６実施形態と重複する箇所の説明は省略する。
【００４８】
第７実施形態の大径円筒１２には、大径円筒軸方向に離間可能なロッド付連結具１４と、反力板１２ａに一端を固定され他端が前記ロッド付連結具１４と連結した弾性体Ｂとが収納されている。
【００４９】
ここで、ロッド付連結具１４は、一端に弾性体Ａと連結される第１ロッド１５ａが設けられ、かつ他端に孔明きストッパー１５ｂを有するシリンダー部材１５と、弾性体Ｂと連結される第２ロッド１６とからなる。そして、シリンダー部材１５の孔明きストッパー１５ｂに第２ロッド１６を挿通配置している。尚、第２ロッド１６のシリンダー部材側端部には、引き抜け防止のためにアンカー部材１６ａが設けられている。
【００５０】
また、シリンダー部材の第１ロッド１５ａは、小径円筒１１の孔明きストッパー１１ｂの孔を通って、初期張力を導入された弾性体Ａと連結される。
【００５１】
すなわち、弾性体Ａに初期引張力を導入するため、弾性体Ａと弾性体Ｂを連結するロッド付連結具１４を大径円筒１２に収納し、小径円筒１１の孔明きストッパー１１ｂの孔に第１ロッド１５ａを通して、ロッド付連結具１４と弾性体Ａとを連結している。
【００５２】
また、係留外力（引張力）のみを伝達する手段として弾性体Ｂと反力板１２ａと連結し、シリンダー部材側の第１ロッド１５ａとは別に、連結具（シリンダー部材１５）から引張力のみ伝達する第２ロッド１６を設け、弾性体Ｂと第２ロッド１６とを連結している。
これにより、大径円筒軸方向に離間可能にロッド付連結具１４が構成され、ロッド付連結具１４が浮体２からの圧縮力を負担する一方で、弾性体Ａ、弾性体Ｂは引張力のみ負担するようになっている。
【００５３】
図１１（ａ）は係留装置１０ｂがフリー状態において圧縮力が作用した場合、すなわち基体３に対して浮体２が接近する方向に外力が働いた場合の状態を示すものである。この状態では反力板１２ａに固定された弾性体Ｂを、引張力のみ伝達する第２ロッド１６で離間可能に連結具と取付けて引張力のみ伝達するようにしているため、係留装置１０ｂはフリーに挙動する。
【００５４】
図１１（ｂ）は、この実施形態における平常時の係留状態を示すもので、浮体２と基体３間に作用する係留時の引張力P3は弾性体Ａに導入した初期引張力Pi内であるため（P3＜Pi）、弾性体Ａには変位が生じないで弾性体Ｂのみにより大きなばね係数kbによって小さな変位で係留される。
【００５５】
図１１（ｃ）は暴風時の係留状態を示すもので、係留時の引張外力P4が弾性体Ａに導入した初期引張力Piを超えるため（Pi＜P4）、ロッドを介して伝達された係留力により弾性体Ａは孔明きストッパー１１ｂ側に伸長変位する。この際、暴風時の外力は弾性体Ｂのばね係数kbによる変位と弾性体Ａのばね係数kaの変位によってエネルギーが吸収されて係留装置１０ｂの反力を低減することができる。
【００５６】
図１２は本発明に係る係留装置１０を海底４に設置された基体３と浮体２間を連結する係留装置１０両端の反力板１１ａ，１２ａに、ヒンジ結合部材１７を設けピン結合によって連結した側面図である。ピン結合することにより潮位差によって浮体２が上下移動しても係留装置１０を自由に追随させることができる。
【００５７】
なお、第６、第７実施形態のように、係留装置両端の大径円筒の反力板と小径円筒の反力板に自在継手を設けると、潮位差によって浮体が上下移動する際、係留装置を上下自由に追随させるとともに浮体が係留装置と直交方向にずれる際にも無理な反力が生じることなく自由に追随させることが可能となる。
【００５８】
上記第６、第７実施形態の圧縮力係留と引張力係留として作用する円筒方式の係留装置を並べて配置すれば、浮体の片側に設置した基体で係留することができる。
【００５９】
【発明の効果】
本発明は、海底に設置された基体に固定した支持体に、ストッパーにより変位した状態を維持することで初期反力を導入したばね係数の小さい弾性体Ａの一端を固定し、他端に前記弾性体Ａの初期反力を超えた外力で可動するようにしたばね係数の大きい弾性体Ｂを連結し、該弾性体Ｂに浮体から突設した係留材を上下移動可能に当接させた非線形反力特性を備えた浮体係留装置としているため、平常時の小さな外力に対してはばね係数の大きな弾性体Ｂによって浮体変位量を抑えて係留し、ストッパーの反力を超える大きな暴風時外力に対してはばね係数の小さな弾性体Ａを作動させて浮体変位を許容してエネルギーを吸収して大きな作用外力を減じることにより設計外力を低減できるため経済的な係留装置を提供する効果を奏する。
また、浮体の係留材は上下移動可能に係留装置に当接させているため浮体の潮位変動に追随して係留できる。
【００６０】
さらに、係留装置を円筒方式としたものは係留装置をコンパクトにでき、基体および浮体との取付け部に自在継手を用いれば潮位変動に追随することができるとともに係留直交方向のずれにも対応できる。
【図面の簡単な説明】
【図１】本発明の第１実施形態であって、１方向の水平変位を規制する係留装置を浮体の左右側に設置した基体上に設けた側面図である。
【図２】第１実施形態で係留装置が（ａ）静止時、（ｂ）平常時の外力を受けた際、（ｃ）暴風時の外力を受けた際、における弾性体Ａ、弾性体Ｂの動きを表した図である。
【図３】本発明の第２実施形態を示す図である。
【図４】本発明の第３実施形態を示す図である。
【図５】本発明の第４実施形態を示す図である。
【図６】本発明の第５実施形態を示す側面図である。
【図７】図６の平面図である。
【図８】第５実施形態の係留装置を用いて浮体を一方の側に設置した基体によって係留した場合の側面図である。
【図９】図８の平面図である。
【図１０】本発明の第６実施形態を示す図であり、円筒方式の圧縮係留装置が、（ａ）フリー時、（ｂ）平常時の外力を受けた際、（ｃ）暴風時の外力を受けた際、における弾性体Ａ，弾性体Ｂの動きを表した図である。
【図１１】本発明の第７実施形態を示す図であり、円筒方式の引張係留装置が、（ａ）フリー時、（ｂ）平常時の外力を受けた際、（ｃ）暴風時の外力を受けた際、における弾性体Ａ，弾性体Ｂの動きを表した図である。
【図１２】上記円筒方式の係留装置を基体と浮体間にピン結合により設置した側面図である。
【図１３】ばね係数の異なる係留装置の変形と反力の関係を本発明と比較例を合わせて示した図である。
【符号の説明】
１係留装置
２浮体
２ａ係留材
３基体
４海底
４ａ海水面
５支持体
６支持部材
７ストッパー
８ローラー支承
９支持部材取付ピン
１０，１０ａ，１０ｂ係留装置
１１小径円筒
１１ａ反力板
１１ｂ孔明きストッパー
１２大径円筒
１２ａ反力板
１３ロッド
１３ａアンカー部材
１４ロッド付連結具
１５シリンダー部材
１５ａ第１ロッド
１５ｂ孔明きストッパー
１６第２ロッド
１６ａアンカー部材
１７ヒンジ結合部材
Ａ，Ａ１，Ａ２弾性体
Ｂ，Ｂ１，Ｂ２弾性体[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a mooring device for mooring a floating body such as a large-scale floating structure floating on the sea, which can reduce mooring external force during a storm.
[0002]
[Prior art]
Mooring devices for large-scale floating bodies used for floating islands are as small as possible for external forces such as normal waves, tidal currents, and wind loads, and to some extent for waves and wind loads during storms. Therefore, it is required to moor safely by reducing the mooring force. Also, a mooring system is desirable so that it does not interfere with the ship's connection due to access to the floating body. In addition, in a very large large-scale floating body, the expansion and contraction of the floating body due to a change in outside air temperature is several meters, so the mooring device needs to absorb this.
[0003]
Conventionally, mooring methods for floating bodies include anchors and sinkers installed on the seabed and mooring lines that connect floating bodies with mooring lines such as chains and wire ropes, and rubber fenders interposed between mooring dolphins and quay walls and floating bodies. A rubber fender method is known.
[0004]
The former mooring line method has the disadvantage that the horizontal movement amount is large due to catenary mooring for relatively small external force such as normal wave, tidal current and wind load, etc. . In addition, it is necessary to install a large number of large mooring lines around the floating body in order to counter external forces during windstorms, which hinders the navigation of nearby ships.
[0005]
On the other hand, the latter rubber fender method has a large spring coefficient, so the amount of displacement in normal times can be reduced, and there is no problem that hinders the navigation of nearby vessels. However, the deformation capacity (stroke) is small, so it is excessive during storms. An external force is generated. Further, when it is possible to absorb the in-plane deformation of the floating body due to the expansion and contraction of the floating body due to a change in the outside air temperature, it is necessary to take measures to increase the deformation capacity.
The largest rubber fender currently on the market in Japan is a cell-type fender (outer diameter 3m, length 3m, deformation capacity 1.5m at design limit strain (50%), maximum reaction force 400t-600t) ).
[0006]
In order to increase the deformability of the rubber fender, there are means for connecting a plurality of them in series, such as those disclosed in JP-A-6-144356. Although it is conceivable to produce a long fender with a particularly large deformation capability, there is a problem of torsional buckling, which is difficult.
[0007]
[Problems to be solved by the invention]
Usually, the mooring force of the mooring device is determined so as to be safe against the maximum external force generated during a storm. The acting external force generated during this storm correlates with the amount of displacement of the reaction body (the mooring device). When the deformation of the mooring device is restricted, the acting external force is large, and if large displacement is allowed, it absorbs energy and acts. External force can be reduced. Therefore, in order to reduce the external force during a storm, it is advantageous to moor the mooring device with a large displacement.
[0008]
In the case of the above-described rubber fender method, since the deformability is small when used alone, an excessive external force is generated during a storm, so it is necessary to counteract by using a large number of large fenders having a large reaction force capacity in parallel. If the deformation capacity is increased by connecting multiple units in series, the external force can be reduced somewhat, but the number of large fenders used remains the same, and there is an issue that requires a large investment in mooring equipment. It was.
[0009]
Further, even if a plurality of large rubber fenders are connected in series, the increase in deformation capacity is limited, and a countermeasure against torsional buckling is required, which further increases the equipment cost.
[0010]
An object of the present invention is to provide an economical mooring device by suppressing the amount of displacement of a floating body with respect to a normal external force and allowing the floating body to be displaced during a storm and reducing the acting external force. .
[0011]
[Means for solving the problems]
The gist of the present invention is as follows.
[0012]
A first invention is a mooring device for mooring a floating body to a base body installed on the seabed, and includes a stopper. By maintaining the displaced state Using the elastic body A having a small spring coefficient introduced with the initial reaction force and the elastic body B having a spring coefficient larger than the elastic body A, the mooring force of the floating body is transmitted from the elastic body B to the elastic body A, and the mooring force is The floating body mooring device having a nonlinear reaction force characteristic, wherein the elastic body A is displaced when the initial reaction force of the elastic body A is exceeded.
[0013]
According to a second invention, in the first invention, one end of the elastic body A is fixed to a support body protruding horizontally from a base installed on the seabed, and the elastic body B pin-coupled to the support body is suspended, In the stretched or compressed state of the elastic body A, one horizontal displacement is regulated by a stopper and connected to the upper end of the elastic body B to introduce an initial reaction force to the elastic body A. The mooring material protruding from the floating body is brought into contact with the movable body so as to be movable up and down, and the horizontal displacement in one direction of the floating body is supported by the elastic body A and the elastic body B having different spring coefficients according to the change in the tide level.
[0014]
According to a third aspect of the present invention, the mooring device according to the second aspect of the present invention is provided in parallel so as to support horizontal displacements in directions opposite to each other on a base installed on one side of the floating body, and supports the horizontal displacement of the floating body in the left-right direction. This is a floating body mooring device having a nonlinear reaction force characteristic.
[0015]
According to a fourth aspect of the present invention, in the first aspect, the elastic body A1 and the elastic body A2 are opposed to both ends of a support body that is horizontally provided from a base body installed on the seabed, and one end thereof is fixed. The elastic body B1 and the elastic body B2 that are pin-coupled to each other are suspended, and the elastic body B1 and the elastic body B1 are elastically controlled by restricting horizontal displacement in one direction opposite to the respective stoppers when the elastic body A1 and the elastic body A2 are extended or compressed. The mooring material connected to the upper end of the body B2 is introduced with an initial reaction force in a direction opposite to the elastic body A1 and the elastic body A2, and the anchoring material projecting from the floating body below each elastic body B1 and elastic body B2. It is abutted so that it can move up and down, and the horizontal displacement of the left and right sides of the floating body is supported by elastic bodies A1 and A2 and elastic bodies B1 and B2 having different spring coefficients according to changes in the tide level.
[0016]
In a fifth aspect of the present invention, in the first aspect, a reaction force plate A is provided at one end and a hole stopper is provided at the other end. A large-diameter cylinder is slidably covered, and the elastic body A into which the initial compression force is introduced by restricting the displacement by the stopper is accommodated in the small-diameter cylinder, and only the compression force is applied to the reaction force plate in the large-diameter cylinder. An elastic body B adapted to transmit is housed, and a rod for connecting the elastic body A and the elastic body B through the hole of the perforated stopper is arranged over both the small diameter cylinder and the large diameter cylinder, and the floating body is moored. When the elastic body B having a large spring coefficient is transmitted as a compressive force to the elastic body A having a small spring coefficient introduced through the rod, and the compressive force exceeds the initial compressive force regulated by the stopper. It is characterized in that the elastic body A is displaced to .
[0017]
A sixth aspect of the invention is the first aspect according to the first aspect, wherein a large-diameter having a reaction force plate provided at one end and a reaction force plate provided at the other end on the stopper side of a small diameter cylinder provided with a reaction force plate at one end and a perforated stopper provided at the other end. A cylinder is slidably covered, and an elastic body A having one end fixed to a reaction force plate is accommodated in the small diameter cylinder, and an elastic body B and an elastic body A each having one end fixed to the reaction force plate are accommodated in the large diameter cylinder. A connecting tool with a rod for connecting the elastic body B is stored,
The elastic body A and the connecting tool with the rod are connected in a state where initial tension is introduced into the elastic body A by a rod inserted through the hole of the perforated stopper, and a tensile force is applied to the elastic body A and the elastic body B. Only the mooring force of the floating body is transmitted as a tensile force to the elastic body A having a small spring coefficient introduced through the elastic body B having a large spring coefficient. The elastic body A is displaced when it exceeds the initial tensile force regulated by the stopper.
[0018]
The seventh invention is characterized in that the mooring device according to the fifth and sixth inventions is provided in parallel on a base body installed on one side of the floating body to support horizontal displacement of the floating body in the left-right direction. It is the floating body mooring device provided with the nonlinear reaction force characteristic.
[0019]
According to an eighth invention, in any one of the fifth to seventh inventions, a universal joint is provided on the reaction plate of the small diameter cylinder and the reaction force plate of the large diameter cylinder, and the universal joint is installed on the seabed via the universal joint. It is characterized in that the substrate and the floating body are connected.
[0020]
<Action>
The point of the present invention is that, for relatively small external forces such as waves, tidal currents, and wind loads during normal times, the elastic body B is moored by the elastic body B having a large spring coefficient within the initial reaction force of the elastic body A to suppress the swinging of the floating body. It has a nonlinear reaction force characteristic that allows the elastic body A with a small spring coefficient to move and allow the displacement of the floating body to absorb the energy against a large external force during a storm that exceeds the initial reaction force of the elastic body. As a mooring device, the design is advantageous by reducing the external action force during a storm.
[0021]
FIG. 13 shows the relationship between the deformation of the mooring device having a different spring coefficient and the mooring device reaction force together with the present invention and a comparative example. In FIG. 13, (a) shows the relationship between deformation and reaction force in a mooring device with a reaction force characteristic of linear or reaction force gradually increasing type with a large spring coefficient. (B) shows the relationship between deformation and reaction force in a mooring device with a linear or small reaction force incremental reaction force characteristic with a small spring coefficient. (C) shows the relationship between deformation and reaction force in the mooring device having the nonlinear reaction force characteristic of the present invention.
[0022]
In Comparative Example (a), there is no problem because the deformation of the mooring device is small and the displacement (a1) is small in normal times, but a large reaction force (a2) is generated during a storm, and the design external force becomes excessive.
In comparative example (b), since the mooring device is largely deformed, it absorbs energy during a storm and produces a small reaction force (b2), which can reduce the design external force during a storm but increases the displacement (b1) during normal times. .
[0023]
On the other hand, (c) is a mooring device of the present invention, comprising an elastic body A having a small spring coefficient with an initial reaction force introduced by a stopper, and an elastic body B having a large spring coefficient for transmitting the mooring force from the mooring material. It has a combined non-linear reaction force characteristic. For a small external force in normal times, only the elastic body B acts within the initial reaction force introduced into the elastic body A, and the displacement (c1) is relatively small. For external forces that are moored and exceed the initial reaction force introduced into the elastic body A, the elastic body A operates to allow a large displacement and absorb the energy to generate a reaction force (c2). The design external force can be reduced because it becomes smaller. The reaction force Ri in FIG. 13 is an initial reaction force value introduced into the elastic body A by the stopper.
[0024]
Embodiments and Examples of the Invention
1 to 9 show an embodiment relating to a lever-type mooring apparatus 1 according to the present invention.
FIG. 1 is an example of the first embodiment, and a mooring device 1 that restricts horizontal displacement in one direction is provided on a base body 3 installed on the left and right sides of a floating body 2 so that the floating body 2 is sandwiched between them. The horizontal displacement is supported.
[0025]
The mooring device 1 fixes one end of an elastic body A composed of a coil spring, a pneumatic cylinder, and the like that expands and contracts with a predetermined spring coefficient ka to a support body 5 that is horizontally projected from a base 3 such as a dolphin installed on the seabed 4. The other end of the elastic body A is connected to the upper end portion of the support member 6 of the drooping elastic body B in which the other end of the elastic body A is connected to the support body 5 with a gap L1.
A stopper 7 is provided on the support 5 below the support member mounting pin 9 on the opposite side of the elastic body A with a gap L2, and one of the support members 6 of the drooping elastic body B (by this stopper 7) Displacement in the right direction) is restricted, and the initial tensile force Ri introduced into the elastic body A is held.
[0026]
The mooring of the floating body 2 is performed by contacting the mooring material 2a protruding from the floating body 2 below the elastic body B. Here, since the floating body 2 moves up and down relatively with the mooring device 1 due to the tide level difference, the elastic body B and the mooring material 2a are freely brought into contact with each other so as to be able to move up and down following the tide level fluctuation.
[0027]
As the elastic body B extending below the support member 6, for example, a leaf spring using ordinary steel in an elastic region can be used. The leaf spring may be integrated with the upper support member 6.
This elastic body B needs to have a spring coefficient kb larger than that of the elastic body A (ka <kb) and to have a proof strength capable of resisting an external force during a storm. Moreover, it is necessary to use a thing with good abrasion resistance in order to contact the mooring material 2a and to repeat a movement up and down.
[0028]
FIG. 2 shows the movements of the elastic bodies A and B when the mooring device 1 is stationary (in the state where the mooring force of the floating body does not act), when receiving external force during normal times, and when receiving external force during storms. It is a thing.
(A) In the state where the mooring force of the floating body 2 does not act on the elastic body B (FIG. 2a), the initial tension Ri of the elastic body A is all handled by the reaction force Rs of the stopper 7, and the relationship between Ri and Rs is Ri × L1 = Rs × L2.
(B) The elastic body B responds to the external force P1 in the normal state with a small deformation caused by the spring coefficient of kb without detaching from the stopper 7, and the tension of the elastic body A is the initial tension Ri and the reaction of the stopper 7 The force is Rs−ΔRs (> 0) (see FIG. 2b).
(C) With the external force P2 during a storm, when the large external force P2 acting on the elastic body B exceeds the initial tension Ri, P2 × L3> Ri × L1, and the support member 6 supporting the elastic body B is released from the stopper 7. The elastic body A expands with a spring coefficient ka to cause a large displacement in the floating body 2 (see FIG. 2c). As a result, the external force energy of the floating body 2 is absorbed by the elastic deformation of the elastic body A.
In the state of (c), the load balance between the external force P2 and the elastic body A is
P2 × L3 = (Ri + ΔRi2) × L1.
[0029]
FIG. 3 shows a second embodiment, which is a mooring device 1 that regulates the movement of the floating body 2 in a direction away from the mooring device 1 side. In the second embodiment, the elastic body A and the stopper are provided on the opposite side of the first embodiment, and the roller support 8 that draws the elastic body B is used for the anchoring material 2a protruding from the floating body 2.
If the mooring devices of the second embodiment and the first embodiment are alternately arranged, the mooring device can be moored by a base installed only on one side of the floating body.
[0030]
FIG. 4 shows a third embodiment in which the initial reaction force introducing means is a compressive force. When the compression force is the initial reaction force, the positions of the stoppers 7 are different from those in the first and second embodiments. That is, in the third embodiment, the elastic body A into which the compressive force is introduced is connected to the support body 5 and the support member 6 of the hanging elastic body B above the support body 5, and on the elastic body A side below the support body 5. A stopper 7 is provided, and this stopper 7 restricts the displacement of the supporting member 6 of the hanging elastic body B in the left direction (the left direction), and the initial compressive force introduced into the elastic body A is held.
[0031]
FIG. 5 shows a fourth embodiment in which the elastic body A into which the tensile force is introduced is arranged below the support body 5 of the base 3. In this case, the stopper 7 is disposed between the support member mounting pin 9 provided on the support 5 and the elastic body A.
[0032]
FIG. 6 is a side view of the mooring device of the fifth embodiment, and FIG. 7 is a plan view of FIG. The fifth embodiment is an embodiment in which the first embodiment and the second embodiment are combined.
In the mooring device 1 according to the fifth embodiment, the elastic bodies A1 and A2 are arranged opposite to each other at both ends of the support body 5 that is horizontally projected from the base body 3 installed on the seabed 4, and each of the support bodies 5 is provided with each of them. One end is fixed. A suspended elastic body B1 and elastic body B2 are pin-coupled to the support body 5, respectively. Further, the other ends of the elastic bodies A1 and A2 are connected to the upper ends of the support members 6 of the elastic bodies B1 and B2 in an extended state where initial tension is introduced.
[0033]
The initial tension introduced into the elastic bodies A1 and A2 is held by the corresponding stopper 7, respectively. With this configuration, the elastic body B1 and the elastic body B2 restrict horizontal displacements in opposite directions, and initial tension (reaction force) introduced into the elastic bodies A1 and A2 with respect to displacements in opposite directions. It is regulated by.
[0034]
The anchoring material 2a protruding from the floating body 2 is brought into contact with the lower part of the elastic body B1 and elastic body B2 via the roller support 8 so as to be drawn and pressed, and the mooring force in the left-right direction is transmitted. The Further, the roller support 8 of the mooring material 2a is movable up and down so that it can follow even if the tide level changes.
In this way, the non-linear reaction force characteristics of the elastic body A1, the elastic body A2 having the small spring coefficient ka, the elastic body B1 having the large spring coefficient kb, and the elastic body B2 having the initial reaction force introduced by the stopper 7 are different. The horizontal displacement of the floating body 2 in both the left and right directions is supported by the mooring device 1 having the above.
8 and 9 are a side view and a plan view when the floating body 2 is moored by the base 3 installed on one side using the mooring device 1 of the fifth embodiment.
[0035]
10 to 12 show an embodiment of a cylindrical mooring device 10 according to the present invention.
[0036]
FIG. 10 shows a sixth embodiment, which is a cylindrical mooring device 10 a when the floating body 2 acts as a compressive force on the base 3.
The mooring device 10 a according to the sixth embodiment is formed by combining a small diameter cylinder 11 and a large diameter cylinder 12 having an inner diameter larger than that of the small diameter cylinder 11.
One end of the small-diameter cylinder 11 is provided with a reaction force plate 11 a that is fixed to the base 3 or the floating body 2, and a perforated stopper 11 b is provided at the other end. The small-diameter cylinder is covered with a large-diameter cylinder 12 having one end opened and a reaction force plate 12a at the other end on the perforated stopper 11b side so that both cylinders can slide.
[0037]
The small-diameter cylinder 11 stores an elastic body A, one end of which is connected to the reaction force plate 11a, and the large-diameter cylinder 12 has an elastic body B in a free state that is not connected to the reaction force plate 12a. Stored. And the rod 13 which connects the elastic body A and the elastic body B over both the small diameter cylinder 11 and the large diameter cylinder 12 is disposed so as to pass through the hole of the perforated stopper 11b.
[0038]
The elastic body A has a predetermined spring coefficient ka, and the elastic body A can be a displaceable coil spring, a pneumatic cylinder, or the like. The elastic body B has a spring coefficient kb larger than the spring coefficient ka of the elastic body A (ka <kb). Can be selected from coil springs, steel bellows, etc.
[0039]
The elastic body A housed in the small-diameter cylinder 11 has a predetermined initial state in which the displacement is regulated by the perforated stopper 11b at the end and the anchor member 13a at the end of the rod 13 so that the normal mooring force P1 is within the range. A compression force Pi is introduced (P1 <Pi). The initial compressive force can be introduced by, for example, connecting the reaction force plate 11a and the end portion of the small diameter cylinder 11 with screws and screwing the elastic body A into the small diameter cylinder 11 with a predetermined compressive force.
[0040]
The rod 13 disposed through the perforated stopper 11b transmits the compressive mooring force of the floating body 2 from the elastic body B to the elastic body A, and can move more than the displaceable length of the elastic body A, and can be used during a storm. It must be strong enough to withstand external forces.
[0041]
The elastic body B connected and fixed to the rod 13 is not fixed to the reaction force plate 12a but abuts so as to be separable so as to transmit only the compression force. The reason for this is to avoid the occurrence of an excessive reaction force on the anchor member 13a and the perforated stopper 11b when a tensile force acts on the anchoring device 10a.
[0042]
FIG. 10A shows a state where a tensile force is applied when the mooring device 10a is in a free state, that is, a case where an external force is applied in a direction in which the floating body 2 is separated from the base 3. In this state, since the elastic body B is not fixed to the reaction force plate 12a but is detachably contacted to transmit only the compression force, the mooring device 10a behaves freely.
[0043]
FIG. 10 (b) shows a normal mooring state, since the compressive force P1 during mooring acting between the floating body 2 and the base 3 is within the initial compressive force Pi introduced into the elastic body A (P1 <Pi). ), The elastic body A is not displaced, and only the elastic body B is moored with a small spring by a large spring coefficient kb.
[0044]
FIG. 10 (c) shows the mooring state during a storm. Since the compressive external force P2 at the time of mooring exceeds the initial compressive force Pi introduced into the elastic body A (Pi <P2), it is transmitted through the rod 13. The elastic body A is displaced away from the stopper by the mooring force. At this time, the external force during the storm is absorbed by the displacement of the elastic body B due to the spring coefficient kb and the displacement of the spring coefficient ka of the elastic body A, so that the reaction force of the mooring device can be reduced.
[0045]
By the mooring device 10a configured as described above, the mooring force of the floating body 2 is transmitted as a compressive force to the elastic body B having a small spring coefficient introduced into the elastic body B having a large spring coefficient through the rod 13, and is normal. The mooring at the time is moored by the elastic body B with a small displacement, and when the initial compressive force of the elastic body A is exceeded (when a large external compression force is applied as in a storm), the elastic body A having a small spring coefficient is displaced. Thus, a floating body mooring device having a nonlinear reaction force characteristic that counteracts the mooring force with elastic bodies having different spring coefficients is realized.
[0046]
FIG. 11 shows a seventh embodiment, which is a cylindrical mooring device 10b when the floating body 2 acts on the base 3 as a tensile force.
[0047]
The cylindrical mooring device 10b of the seventh embodiment is different from the cylindrical mooring device of the sixth embodiment (when compressive force is applied) in that the initial tension is introduced into the elastic body A and connected with a rod. It is connected to the tool 14 and connected to the elastic body B so as to transmit only a tensile force.
Hereinafter, only a point in which the seventh embodiment is different from the sixth embodiment will be described, and description of portions overlapping with the sixth embodiment will be omitted.
[0048]
The large-diameter cylinder 12 of the seventh embodiment includes a connecting tool 14 with a rod that can be separated in the axial direction of the large-diameter cylinder, and an elastic structure in which one end is fixed to the reaction force plate 12a and the other end is connected to the connecting tool 14 with a rod. The body B is stored.
[0049]
Here, the connecting tool 14 with the rod is provided with a first rod 15a connected to the elastic body A at one end, and a cylinder member 15 having a perforated stopper 15b at the other end and a first connecting member connected to the elastic body B. 2 rods 16. The second rod 16 is inserted into the perforated stopper 15 b of the cylinder member 15. An anchor member 16a is provided at the cylinder member side end of the second rod 16 to prevent pull-out.
[0050]
The first rod 15a of the cylinder member is connected to the elastic body A into which the initial tension is introduced through the hole of the perforated stopper 11b of the small diameter cylinder 11.
[0051]
That is, in order to introduce an initial tensile force to the elastic body A, the connecting tool 14 with the rod for connecting the elastic body A and the elastic body B is accommodated in the large diameter cylinder 12 and is inserted into the hole of the perforated stopper 11b of the small diameter cylinder 11. The connecting tool 14 with a rod and the elastic body A are connected through one rod 15a.
[0052]
Further, as a means for transmitting only the mooring external force (tensile force), the elastic body B is connected to the reaction force plate 12a, and only the tensile force is transmitted from the coupling tool (cylinder member 15) separately from the first rod 15a on the cylinder member side. The second rod 16 is provided to connect the elastic body B and the second rod 16.
Thereby, the connecting tool 14 with the rod is configured to be separable in the large-diameter cylindrical axis direction, and the connecting tool 14 with the rod bears the compressive force from the floating body 2, while the elastic body A and the elastic body B are only tensile force. It comes to bear.
[0053]
FIG. 11A shows a state where a compressive force is applied while the mooring device 10b is in a free state, that is, a case where an external force is applied in a direction in which the floating body 2 approaches the base 3. In this state, the elastic body B fixed to the reaction force plate 12a is attached to the connector so as to be separated by the second rod 16 that transmits only the tensile force so as to transmit only the tensile force, so that the mooring device 10b is free. Behaves.
[0054]
FIG. 11 (b) shows a normal mooring state in this embodiment, and the tensile force P 3 during mooring acting between the floating body 2 and the base body 3 is within the initial tensile force Pi introduced into the elastic body A. Therefore (P3 <Pi), the elastic body A is not displaced and is anchored by the elastic body B only with a small spring with a large spring coefficient kb.
[0055]
FIG. 11 (c) shows a mooring state during a storm. Since the tensile external force P4 during mooring exceeds the initial tensile force Pi introduced into the elastic body A (Pi <P4), the mooring transmitted through the rod The elastic body A is extended and displaced toward the perforated stopper 11b by the force. At this time, the external force during the storm is absorbed by the displacement of the elastic body B due to the spring coefficient kb and the displacement of the spring coefficient ka of the elastic body A, and the reaction force of the mooring device 10b can be reduced.
[0056]
FIG. 12 shows a mooring device 10 according to the present invention, in which a hinge coupling member 17 is provided on reaction force plates 11a and 12a at both ends of the mooring device 10 for connecting the base 3 installed on the seabed 4 and the floating body 2 and coupled by pin coupling. It is a side view. The pin connection allows the mooring device 10 to follow freely even if the floating body 2 moves up and down due to the difference in tide level.
[0057]
As in the sixth and seventh embodiments, when a universal joint is provided on the reaction plate of the large-diameter cylinder and the reaction plate of the small-diameter cylinder at both ends of the mooring device, when the floating body moves up and down due to the tide level difference, Can be allowed to follow freely without any excessive reaction force even when the floating body is displaced in a direction orthogonal to the mooring device.
[0058]
If the cylindrical mooring devices acting as the compressive force mooring and the tensile force mooring of the sixth and seventh embodiments are arranged side by side, they can be moored by the base installed on one side of the floating body.
[0059]
【The invention's effect】
The present invention uses a stopper on a support fixed to a base installed on the seabed. By maintaining the displaced state One end of an elastic body A having a small spring coefficient introduced with an initial reaction force is fixed, and an elastic body B having a large spring coefficient is connected to the other end so as to be movable by an external force exceeding the initial reaction force of the elastic body A. Since the floating body anchoring device has a nonlinear reaction force characteristic in which the anchoring material protruding from the floating body is brought into contact with the elastic body B so as to be movable up and down, the elastic body has a large spring coefficient for a small external force in normal times. The body B is moored while suppressing the displacement of the floating body, and for large stormy external forces exceeding the reaction force of the stopper, the elastic body A with a small spring coefficient is operated to allow the floating body displacement and absorb the energy and have a large effect Since the design external force can be reduced by reducing the external force, an economical mooring device is provided.
Further, since the mooring material of the floating body is brought into contact with the mooring device so as to be movable up and down, it can be moored following the tide level fluctuation of the floating body.
[0060]
Further, when the mooring device is of a cylindrical type, the mooring device can be made compact, and if a universal joint is used for the attachment portion between the base body and the floating body, it is possible to follow fluctuations in the tide level and to cope with a deviation in the mooring orthogonal direction.
[Brief description of the drawings]
FIG. 1 is a side view of a first embodiment of the present invention, in which a mooring device for restricting horizontal displacement in one direction is provided on a base body installed on the left and right sides of a floating body.
FIGS. 2A and 2B are elastic bodies A and B when the mooring device according to the first embodiment is (a) when stationary, (b) when receiving an external force during normal times, and (c) when receiving an external force during a storm. FIG.
FIG. 3 is a diagram showing a second embodiment of the present invention.
FIG. 4 is a diagram showing a third embodiment of the present invention.
FIG. 5 is a diagram showing a fourth embodiment of the present invention.
FIG. 6 is a side view showing a fifth embodiment of the present invention.
7 is a plan view of FIG. 6. FIG.
FIG. 8 is a side view when a floating body is moored by a base body installed on one side using the mooring device of the fifth embodiment.
9 is a plan view of FIG. 8. FIG.
FIGS. 10A and 10B are diagrams showing a sixth embodiment of the present invention, in which a cylindrical compression mooring device receives (a) free, (b) normal external force, and (c) storm external force. It is the figure showing the motion of the elastic body A and the elastic body B in receiving.
FIGS. 11A and 11B are diagrams showing a seventh embodiment of the present invention, in which a cylindrical tension mooring device is subjected to (a) free, (b) normal external force, and (c) storm external force. It is the figure showing the motion of the elastic body A and the elastic body B in receiving.
FIG. 12 is a side view in which the cylindrical mooring device is installed by pin coupling between a base and a floating body.
FIG. 13 is a diagram showing the relationship between deformation and reaction force of a mooring device having different spring coefficients, together with the present invention and a comparative example.
[Explanation of symbols]
1 Mooring device
2 Floating body
2a Mooring material
3 Base
4 Seabed
4a Sea level
5 Support
6 Support members
7 Stopper
8 Roller support
9 Supporting member mounting pin
10, 10a, 10b Mooring device
11 Small diameter cylinder
11a Reaction plate
11b Perforated stopper
12 Large diameter cylinder
12a reaction force plate
13 Rod
13a Anchor member
14 Connecting tool with rod
15 Cylinder member
15a First rod
15b Perforated stopper
16 Second rod
16a Anchor member
17 Hinge coupling member
A, A1, A2 elastic body
B, B1, B2 elastic body

Claims

A mooring device for mooring a floating body to a base body installed on the seabed, wherein an elastic body A having an initial reaction force introduced by maintaining a displaced state by a stopper and a spring coefficient larger than the elastic body A The elastic body B is used to transmit the mooring force of the floating body from the elastic body B to the elastic body A, and the elastic body A is displaced when the mooring force exceeds the initial reaction force of the elastic body A. A floating body mooring device having a non-linear reaction force characteristic.

One end of the elastic body A is fixed to a support body protruding horizontally from a base body installed on the seabed, an elastic body B pin-coupled to the support body is suspended, and the elastic body A is stretched or compressed by a stopper. One horizontal displacement is restricted and connected to the upper end of the elastic body B so that an initial reaction force is introduced into the elastic body A, and the anchoring material protruding from the floating body below the elastic body B can be moved up and down. The floating body mooring with nonlinear reaction force characteristics according to claim 1, wherein the horizontal displacement in one direction of the floating body is supported by elastic bodies A and B having different spring coefficients according to a change in tide level. apparatus.

The mooring device according to claim 2 is provided in parallel so as to support horizontal displacements in directions opposite to each other on a base body installed on one side of the floating body so as to support horizontal displacement in the left-right direction of the floating body. Floating body mooring device with characteristic non-linear reaction force characteristics.

The elastic body A1 and the elastic body A2 are opposed to both ends of a support body that is horizontally projected from a base body installed on the seabed, and one end thereof is fixed. The elastic body A1 is coupled to the upper ends of the elastic bodies B1 and B2 by restricting horizontal displacement in one direction opposite to the respective stoppers when the elastic bodies A1 and A2 are stretched or compressed in the stretched or compressed state. The initial reaction force in the opposite direction is introduced into the elastic body A2, and the anchoring material protruding from the floating body is brought into contact with the elastic body B1 and the lower part of the elastic body B2 so as to be movable up and down. 2. The floating body anchoring device with nonlinear reaction force characteristics according to claim 1, wherein the horizontal displacement of the floating body is supported by elastic bodies A1 and A2 and elastic bodies B1 and B2 having different spring coefficients.

A small diameter cylinder having a reaction force plate A at one end and a hole stopper at the other end is slidably covered with a large diameter cylinder having one end opened and a reaction plate at the other end. In the cylinder, the elastic body A in which the displacement is regulated by the stopper and the initial compressive force is introduced is stored, and in the large diameter cylinder, the elastic body B that transmits only the compressive force to the reaction force plate is stored. A rod that connects the elastic body A and the elastic body B through the hole of the perforated stopper is arranged over both the small-diameter cylinder and the large-diameter cylinder, and the anchoring force of the floating body is fixed to the elastic body B having a large spring coefficient. The initial compression force is transmitted to the elastic body A having a small spring coefficient as a compression force, and the elastic body A is displaced when the compression force exceeds the initial compression force regulated by the stopper. The non-linear reaction force characteristic according to claim 1 is provided. It was floating mooring equipment.

A small-diameter cylinder with a reaction plate at one end and a perforated stopper at the other end is slidably covered with a large-diameter cylinder with one end open and a reaction plate at the other end. The elastic body A having one end fixed to the reaction force plate is accommodated, and the elastic body B having one end fixed to the reaction force plate and the connector with a rod for connecting the elastic body A and the elastic body B are accommodated in the large-diameter cylinder. And
The elastic body A and the connecting tool with the rod are connected in a state where initial tension is introduced into the elastic body A by a rod inserted through the hole of the perforated stopper, and a tensile force is applied to the elastic body A and the elastic body B. Only the mooring force of the floating body is transmitted as a tensile force to the elastic body A having a small spring coefficient introduced through the elastic body B having a large spring coefficient. 2. The floating body mooring device with a nonlinear reaction force characteristic according to claim 1, wherein the elastic body A is displaced when the initial tensile force regulated by the stopper is exceeded.

A non-linearity characterized in that the mooring device according to claim 5 and the mooring device according to claim 6 are provided in parallel on a base body installed on one side of the floating body to support horizontal displacement of the floating body in the left-right direction. Floating body mooring device with reaction force characteristics.

6. A universal joint is provided on the reaction force plate of the small diameter cylinder and the reaction force plate of the large diameter cylinder B, and the base body installed on the seabed is connected to the floating body via the universal joint. A floating body mooring device having the nonlinear reaction force characteristic according to claim 7.