JPH0649826A - Fender - Google Patents
FenderInfo
- Publication number
- JPH0649826A JPH0649826A JP4201077A JP20107792A JPH0649826A JP H0649826 A JPH0649826 A JP H0649826A JP 4201077 A JP4201077 A JP 4201077A JP 20107792 A JP20107792 A JP 20107792A JP H0649826 A JPH0649826 A JP H0649826A
- Authority
- JP
- Japan
- Prior art keywords
- elastic body
- fender
- height
- rubber
- rigid spacer
- 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.)
- Granted
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/30—Adapting or protecting infrastructure or their operation in transportation, e.g. on roads, waterways or railways
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、ほぼ円筒状をなすゴ
ムもしくはゴム状弾性体を具える防舷材、とくには、弾
性体軸線と交差する方向の外力に対して十分な強度をも
たらすとともに、吸収エネルギー量を有効に高めること
ができる防舷材に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention provides a fender having a substantially cylindrical rubber or rubber-like elastic body, and in particular, provides sufficient strength against an external force in a direction intersecting the axis of the elastic body. The present invention relates to a fender that can effectively increase the amount of absorbed energy.
【０００２】[0002]
【従来の技術】従来既知の防舷材としては、たとえば実
公平２−30505 号公報に開示されたものがある。これ
は、図４に軸線方向断面図で示すように、弾性ゴムから
一体的に作られた肉厚の中空体であって、該中空体は、
直円錐台状の支承部ａと、該支承部の底面に沿って半径
方向に延びる環状の取付部ｂと、該支承部ａの台面の周
縁部から底面と反対側に延びる筒状の受衝部ｃとから成
り、該受衝部ｃの高さｈ及び最小外径ｒ2 が中空体全体
の高さＨおよびその支承部の最大内径ｒ1 に対し、 ｒ1 ≧ｒ2 及び0.15Ｈ≦ｈ≦0.35Ｈ の関係を有すると共に、前記受衝部ｃの周面の母線が、
上記支承部ａの仮想台面に対し直交するか又は母線の延
長線と該仮想台面とが作る仮想直円錐の底面が、80°以
上90°未満であることを特徴とするものであり、これに
よれば、接舷初期における反力が小さく、しかも大きな
エネルギー吸収量を有する改良された防舷材がもたらさ
れるとしている。2. Description of the Related Art A conventionally known fender is disclosed in, for example, Japanese Utility Model Publication No. 2-30505. This is a thick hollow body integrally made of elastic rubber, as shown in the axial sectional view of FIG.
A right circular truncated cone-shaped bearing portion a, an annular mounting portion b extending in the radial direction along the bottom surface of the bearing portion, and a tubular impact receiving portion extending from the peripheral edge of the base surface of the bearing portion a to the side opposite to the bottom surface. consists of a part c, to the maximum inner diameter r 1 of the receiving衝部height height h and the minimum outer diameter r 2 of the entire hollow body of c H and its bearing, r 1 ≧ r 2 and 0.15 h ≦ While having a relationship of h ≦ 0.35H, the generatrix of the peripheral surface of the impact receiving portion c is
It is characterized in that the bottom surface of a virtual right circular cone that is orthogonal to the virtual base surface of the support portion a or is formed by the extension line of the generatrix and the virtual base surface is 80 ° or more and less than 90 °. According to this, an improved fender having a small reaction force in the initial stage of the porting and having a large amount of energy absorption is provided.
【０００３】[0003]
【発明が解決しようとする課題】ところが、かかる従来
技術にあっては、円筒状をなす受衝部の高さｈが、中空
全体の高さＨに対して 0.15Ｈ≦ｈ≦0.35Ｈ の範囲にあって、その受衝部高さｈの、中空体全体の高
さＨに占める割合が比較的大きいことから、中空体軸線
と交差する方向の接舷荷重の作用に対する強度が、支衝
部に比してはるかに小さくなり、それ故に、たとえば、
船舶が傾斜してその受衝部に衝接した場合には、その受
衝部が、緩衝機能を有効に発揮することなく折曲変形す
るおそれが高かった。However, in such a prior art, the height h of the cylindrical impact receiving portion is within the range of 0.15H≤h≤0.35H with respect to the height H of the entire hollow. Since the height h of the impact receiving portion occupies a relatively large proportion to the height H of the entire hollow body, the strength against the action of the port side load in the direction intersecting the axis of the hollow body is increased. Much smaller than, and therefore, for example,
When the ship leans and collides with the impact receiving portion, the impact receiving portion is likely to be bent and deformed without effectively exerting the cushioning function.
【０００４】しかも、この防舷材では、接舷荷重の作用
によって、それが軸線方向断面内で、壁部から全体的に
Ｓ字状をなす形状に変形するに当り、その変形が、支衝
部内面同志および、支衝部外面と受衝部外面とのそれぞ
れが相互に接触することによって制限されることになる
ため、吸収エネルギー量をそれほど大ならしめることが
できないという問題があった。In addition, in this fender, when it is deformed from the wall portion into the overall S-shape in the axial cross section by the action of the fender load, the deformation is a collision. There is a problem that the amount of absorbed energy cannot be increased so much because the inner surface of the inner part and the outer surface of the impact part and the outer surface of the impact part are limited by contact with each other.
【０００５】そしてさらに、この従来技術では、支承部
の最大内径を、受衝部の最小外径以上の寸法としている
ことから、防舷材の、岸壁その他への取付面積が大きく
なるという不都合があった。Furthermore, in this prior art, since the maximum inner diameter of the support portion is set to be equal to or larger than the minimum outer diameter of the impact receiving portion, there is a disadvantage that the mounting area of the fender on the quay or the like becomes large. there were.
【０００６】この発明は、従来技術の有するかかる問題
をことごとく解決するものであり、接舷荷重の作用方向
のいかんにかかわらず、緩衝機能の、常に十分なる発揮
を担保し、また、吸収エネルギー量を一層増加させ、さ
らに、据付面積を十分小ならしめることができる防舷材
を提供するものである。The present invention solves all of the problems of the prior art, irrespective of the direction of action of the port load, guarantees the cushioning function to be fully exerted at all times, and the absorbed energy amount. Further, the present invention provides a fender capable of further increasing the installation area and sufficiently reducing the installation area.
【０００７】[0007]
【課題を解決するための手段】この発明の防舷材は、全
体としてほぼ円筒状をなすゴムもしくはゴム状弾性体の
基端部に、岸壁その他への取付けフランジを設けるとと
もに、その弾性体の先端に剛性スペーサを取付けたとこ
ろにおいて、前記弾性体の基端部側の約半部を直円筒状
とするとともに、その直円筒状部分より先端側の外輪郭
形状をぼぼ截頭円錐状とし、前記剛性スペーサの高さ
を、弾性体の高さの0.05〜0.3 倍の範囲としたものであ
る。According to the fender of the present invention, a rubber or rubber-like elastic body having a substantially cylindrical shape as a whole is provided with a mounting flange for a quay or the like, and the elastic body Where a rigid spacer is attached to the tip, approximately half of the base end side of the elastic body is made into a right cylinder shape, and the outer contour shape of the tip side from the right cylinder part is a truncated cone shape, The height of the rigid spacer is in the range of 0.05 to 0.3 times the height of the elastic body.
【０００８】[0008]
【作用】この防舷材では、ゴムもしくはゴム状弾性体の
先端側部分の外輪郭形状を、ほぼ截頭円錐状とすること
によって、軸線と交差する方向の接舷荷重の作用に対し
て、その截頭円錐状部分の強度を十分に高めることがで
きるので、截頭円錐状部分は、接触荷重の作用方向のい
かんにかわらず、常にすぐれた緩衝機能を発揮すること
ができ、併せて、エネルギー吸収機能を発揮することが
できる。In this fender, by making the outer contour shape of the tip side portion of the rubber or rubber-like elastic body substantially frustoconical, against the action of the port load in the direction intersecting the axis, Since the strength of the frusto-conical portion can be sufficiently increased, the frusto-conical portion can always exhibit an excellent cushioning function regardless of the acting direction of the contact load. It can exert an energy absorbing function.
【０００９】なおこの弾性体では、その基端部側の約半
部を直円筒状としているも、この直円筒状部分は、岸壁
その他への取付部に近接して位置することから、その直
円筒状部分に、それの軸線と交差する方向の接舷荷重が
作用しても、その部分のモーメントアームが短かく、そ
れ故に、直円筒状部分の折曲変形を有効に防止すること
ができる。In this elastic body, approximately half of the base end side thereof has a straight cylindrical shape. However, since this straight cylindrical portion is located close to the mounting portion to the quay or the like, the straight cylindrical portion Even when a port load acting in a direction intersecting with the axis of the cylindrical portion is applied, the moment arm of the portion is short, and therefore bending deformation of the right cylindrical portion can be effectively prevented. .
【００１０】またここでは、防舷材が接触荷重によっ
て、その極限まで圧縮変形されるに当り、剛性スペーサ
の作用下で、舷側の、防舷材への衝接を十分に防止でき
ることはもちろん、その剛性スペーサの、円筒状弾性体
内への潜り込みおよび、直円筒状部分の拡径及び先端の
載頭円錐状部分のＳ字状変形による円筒状弾性体内への
潜り込みにより、吸収するエネルギー量を、従来技術の
それより一層大ならしめることができる。Further, here, when the fender is compressed and deformed to its limit by the contact load, the contact of the fender with the fender on the fender side can be sufficiently prevented under the action of the rigid spacer. The amount of energy absorbed by the submerged rigid spacer into the cylindrical elastic body and the submerged cylindrical elastic body due to the diameter expansion of the right cylindrical portion and the S-shaped deformation of the truncated cone at the tip, It can be made even larger than that of the prior art.
【００１１】しかもこの防舷材は、弾性体の基端部側を
直円筒状とし、防舷材の取付けを、基端部に設けた取付
けフランジによって行うことから、基端部部分を截頭円
錐形状とした従来技術に比して、取付面積を有効に低減
させることができる。Moreover, in this fender, the base end side of the elastic body is formed into a straight cylindrical shape, and the fender is attached by a mounting flange provided at the base end, so that the base end is truncated. The mounting area can be effectively reduced as compared with the conventional technique having a conical shape.
【００１２】[0012]
【実施例】以下にこの発明の実施例を図面に基づいて説
明する。図１は、この発明の実施例を示す部分断面図で
あり、図中１は、全体としてほぼ円筒状をなすゴムもし
くはゴム状の弾性体を示し、２は、その弾性体１の、基
端部に設けた取付けフランジを、また３は、弾性体１の
先端に取付けられて、その先端径と同等もしくは、それ
以下の輪郭寸法を有する剛性スペーサをそれぞれ示す。
なお、取付けフランジ２および弾性体先端部のそれぞれ
は、剛性材料からなるそれぞれの埋設リング４，５を有
する。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a partial cross-sectional view showing an embodiment of the present invention. In FIG. 1, reference numeral 1 denotes a rubber or rubber-like elastic body having a substantially cylindrical shape as a whole, and 2 denotes a base end of the elastic body 1. 3 is a rigid spacer attached to the tip of the elastic body 1 and having a contour dimension equal to or smaller than the tip diameter.
It should be noted that each of the mounting flange 2 and the elastic body tip portion has respective embedded rings 4 and 5 made of a rigid material.
【００１３】そしてここでは、弾性体１の基端部側の約
半部を直円筒状部分６とするとともに、その直円筒状部
分６より先端側の部分を外輪郭形状がほぼ截頭円錐状を
なす部分７とする。ここで好ましくは、弾性体１の基端
部分の外周面で、取付けフランジ２の突出基端に、断面
形状がたとえば弧状をなす環状溝８を設けるとともに、
その弾性体１の先端部分の外周面に、埋設リング５より
わずかに基端部側に位置して、断面形状が、これもたと
えば弧状をなす環状溝９を設け、これらのそれぞれの環
状溝８，９によって、弾性体１の、圧縮変形時の変形挙
動を常に一定ならしめる。Here, about half of the elastic body 1 on the base end side is a straight cylindrical portion 6, and the portion on the tip side of the straight cylindrical portion 6 has a substantially frustoconical outer contour. And the part 7 forming. Here, preferably, an annular groove 8 having a cross-sectional shape of, for example, an arc is provided on the outer peripheral surface of the base end portion of the elastic body 1 at the protruding base end of the mounting flange 2.
On the outer peripheral surface of the distal end portion of the elastic body 1, there is provided an annular groove 9 which is located slightly closer to the base end side than the embedded ring 5 and has a sectional shape, for example, an arc shape. , 9 make the deformation behavior of the elastic body 1 during compression deformation always constant.
【００１４】さらにここでは、剛性スペーサ３の高さｈ
0 を、弾性体全体の高さＨ0 の0.05〜0.3 倍とすること
によって、剛性スペーサの前面に設置する受衝フレーム
及び受衝パッド又は船体と弾性体との当接による破損を
防止することが出来る。すなわち、それが0.05倍未満で
は、弾性体外壁が前面フレーム又は船体と早期に接触
し、弾性体の破損並びに圧縮変形量を低下する要因とな
る。一方、それが0.3 倍を越えると、全体の高さが高く
なり過ぎ横剛性が低下し、チェーン又は、杭等による支
持が必要となり大幅なコストアップの要因となる。Further, here, the height h of the rigid spacer 3 is
By setting 0 to 0.05 to 0.3 times the height H 0 of the entire elastic body, it is possible to prevent damage due to the contact between the impact frame and the impact pad installed on the front surface of the rigid spacer or the hull and the elastic body. Can be done. That is, if it is less than 0.05 times, the outer wall of the elastic body comes into early contact with the front frame or the hull, which causes damage to the elastic body and decreases the amount of compressive deformation. On the other hand, if it exceeds 0.3 times, the overall height will be too high and the lateral rigidity will be reduced, and it will be necessary to support it with chains or piles, which will be a significant cost factor.
【００１５】ところで、ここおいてより好ましくは、直
円筒状部分６の高さｈ1 を、弾性体全体の高さＨ0 の0.
4 〜0.6 倍、また、その直円筒状部分６の弾性体肉厚ｔ
を、弾性体全体の高さＨ0 の0.1 〜0.25倍、さらに、直
円筒状部分６と、截頭円錐状部分７とのそれぞれの内表
面の交角αを160 °〜175 °の範囲とすることによっ
て、剛性スペーサを直円筒状内部に導く拡径量を確保で
き、圧縮変形量の増大あ確保できる。By the way, more preferably here, the height h 1 of the right cylindrical portion 6 is equal to the height H 0 of the entire elastic body.
4 to 0.6 times, and the elastic wall thickness t of the right cylindrical portion 6
Is 0.1 to 0.25 times the total height H 0 of the elastic body, and the crossing angle α between the inner surfaces of the right cylindrical portion 6 and the frustoconical portion 7 is in the range of 160 ° to 175 °. As a result, it is possible to secure the amount of diameter expansion that guides the rigid spacer into the right cylindrical shape, and it is possible to secure an increase in the amount of compression deformation.
【００１６】なおここで、直円筒状部６の外径Ｄを、弾
性体先端の外径ｄ以下の寸法とした場合には、先端の載
頭円錐状弾性体が直円筒状弾性体内部への潜り込みが生
じなくなり、圧縮変形量を増加させることができない。Here, when the outer diameter D of the right cylindrical portion 6 is set to be equal to or smaller than the outer diameter d of the tip of the elastic body, the frustoconical elastic body at the tip moves to the inside of the right cylindrical elastic body. No more slipping in and the amount of compressive deformation cannot be increased.
【００１７】以上のように構成してなる防舷材は、図２
(a) に示すように、その取付けフランジ２をアンカーボ
ルトその他によって、たとえば岸壁11に固定し、そして
剛性スペーサ３の前面に受衝板12を固定することにより
使用に供される。The fender having the above structure is shown in FIG.
As shown in (a), the mounting flange 2 is fixed to the quay wall 11 by anchor bolts or the like, and the impact plate 12 is fixed to the front surface of the rigid spacer 3 for use.
【００１８】ここで、受衝板12に接舷荷重が作用した場
合には、弾性体１は、図２(b) に示すように、直円筒状
部分６と截頭円錐状部分７との境界部分の拡径変形挙動
の下で、その軸線方向に弾性的に圧縮変形され、これに
よって、緩衝機能およびエネルギー吸収機能のそれぞれ
が有効に発揮される。Here, when a port load is applied to the impact receiving plate 12, the elastic body 1 is composed of a right cylindrical portion 6 and a truncated conical portion 7 as shown in FIG. 2 (b). Under the radial expansion behavior of the boundary portion, the boundary portion is elastically compressed and deformed in the axial direction, whereby the cushioning function and the energy absorbing function are effectively exhibited.
【００１９】弾性体１のこの圧縮変形は、接舷荷重の大
きさに応じて図２(c) および(d) に示すように進行し、
直円筒状部分６の内表面と、截頭円錐状部分７の内表面
とが、図２(d) に示すように相互接触した状態でその圧
縮変形の進行が停止される。This compressive deformation of the elastic body 1 progresses as shown in FIGS. 2 (c) and 2 (d) according to the magnitude of the port load,
The progress of the compressive deformation is stopped in a state where the inner surface of the right cylindrical portion 6 and the inner surface of the truncated cone portion 7 are in mutual contact as shown in FIG. 2 (d).
【００２０】このように、ここでの弾性体１の圧縮変形
は、直円筒状弾性部の拡径、次いで、載頭円錐状弾性部
の潜り込み及び剛性スペーサの潜り込みの順で行われる
ので、従来技術に比して圧縮変形量を大ならしめて、エ
ネギー吸収量を有効に増加させることができる。As described above, the compressive deformation of the elastic body 1 is performed in the order of expanding the diameter of the right cylindrical elastic portion, then submerging the frusto-conical elastic portion and submerging the rigid spacer. The amount of compressive deformation can be increased as compared with the technology, and the amount of energy absorption can be effectively increased.
【００２１】また、弾性体１の上述したような圧縮変形
に際しては、剛性スペーサ３がその弾性体内に潜り込む
ことから、受衝板12および／または舷側が、圧縮変形さ
れた截頭円錐状部分７の外表面に当接するのを十分に防
止することができ、これによってもまたエネルギー吸収
量を増加させることができる。Further, when the elastic body 1 is compressed and deformed as described above, the rigid spacer 3 sunk into the elastic body, so that the impact plate 12 and / or the port side is compressed and deformed into the truncated conical portion 7. It is possible to sufficiently prevent the contact with the outer surface of the sheet, which also increases the energy absorption amount.
【００２２】しかも、この防舷材によれば、弾性体１の
先端側部分を截頭円錐状部分７として、軸線と交差する
方向の外力に対する剛性を高めることにより、たとえ
ば、斜め方向および横方向からの接触荷重に対しても、
その截頭円錐状部分７の折れ曲がり変形を有効に防止し
て、防舷材それ自体の、十分適正な圧縮変形をもたらす
ことができ、この結果として、所要に応じた緩衝機能お
よびエネルギー吸収機能のそれぞれを有効に発揮させる
ことができる。なおこの場合、直円筒状部分６に折れ曲
がり変形が生じるおそれのないことは前述した通りであ
る。Further, according to this fender, the tip end side portion of the elastic body 1 is made into the frustoconical portion 7 so as to enhance the rigidity against the external force in the direction intersecting the axis line, for example, in the oblique direction and the lateral direction. Against the contact load from
The bending deformation of the frusto-conical portion 7 can be effectively prevented, and the fender itself can be sufficiently appropriately compressed and deformed. As a result, the cushioning function and the energy absorbing function as required can be obtained. Each can be effectively demonstrated. In this case, as described above, there is no possibility that the right cylindrical portion 6 is bent and deformed.
【００２３】加えてここでは、直円筒状部分６の基端部
に設けた取付フランジ２によって防舷材の取付けを行う
ことから、その防舷材の、取付けのための占有面積を効
果的に低減させることができる。In addition, here, since the fender is mounted by the mounting flange 2 provided at the base end of the straight cylindrical portion 6, the fender is effectively occupied by the fender. Can be reduced.
【００２４】図３に、以上のように構成してなる発明防
舷材と、前述した従来の防舷材との、歪量に対する反力
および吸収エネルギーの関係を示す。これよれば、従来
防舷材では許容圧縮歪量57.5％、反力1.5tf で、吸収エ
ネルギーが0.122tf ・m であるに対し、発明防舷材で
は、許容圧縮歪量が62.5％、反力が1.5tf で、吸収エネ
ルギーが0.152tf ・m であって、発明品では、変形量お
よび吸収エネルギー量をともに有効に増加させ得ること
が明らかである。FIG. 3 shows the relationship between the reaction force and the absorbed energy with respect to the amount of strain between the invention fender having the above-mentioned structure and the above-mentioned conventional fender. According to this, the conventional fender has an allowable compression strain amount of 57.5% and a reaction force of 1.5 tf, and the absorbed energy is 0.122 tf.m, whereas the invention fender has an allowable compression strain amount of 62.5% and a reaction force. Is 1.5tf and the absorbed energy is 0.152tf · m, it is clear that the invention product can effectively increase both the deformation amount and the absorbed energy amount.
【００２５】なおここで用いた発明防舷材の寸法諸元
は、 Ｈ0 ：200 mm ｈ0 ： 16 mm φｄ：166 mm φＤ：188 mm であり、従来防舷材の寸法諸元は、図４に絶対値で示す
通りである。The dimensional specifications of the invention fender used here are H 0 : 200 mm h 0 : 16 mm φd: 166 mm φD: 188 mm. It is as shown by the absolute value in 4.
【００２６】[0026]
【発明の効果】以上に述べたところから明らかなよう
に、この発明によれば、弾性体の軸線と交差する方向の
外力の作用に対して、とくには截頭円錐状部分の折曲変
形を十分に防止することができ、また、吸収エネルギー
量を一層増加させることができ、さらには、防舷材の据
付面積を有効に低減させることができる。As is clear from the above description, according to the present invention, the bending deformation of the truncated cone portion is particularly caused by the action of the external force in the direction intersecting the axis of the elastic body. It can be sufficiently prevented, the amount of absorbed energy can be further increased, and the installation area of the fender can be effectively reduced.
【図１】この発明の一実施例を示す部分断面図である。FIG. 1 is a partial sectional view showing an embodiment of the present invention.
【図２】防舷材の据付け状態およびそれの変形状態を示
す略線図である。FIG. 2 is a schematic diagram showing an installed state of a fender and a deformed state thereof.
【図３】歪量に対する反力および吸収エネルギーを示す
グラフである。FIG. 3 is a graph showing reaction force and absorbed energy with respect to strain amount.
【図４】従来例を示す軸線方向断面図である。FIG. 4 is an axial sectional view showing a conventional example.
１ 弾性体 ２ 取付けフランジ ３ 剛性スペーサ ４，５ 埋設リング ６ 直円筒状部分 ７ 截頭円錐状部分 ８，９ 環状溝 Ｈ0 弾性体高さ ｈ0 スペーサ高さ ｈ1 直円筒状部分高さ ｔ 弾性体肉厚 α 交角1 elastic body 2 mounting flange 3 rigid spacer 4,5 buried ring 6 right cylindrical portion 7 frustoconical portion 8 and 9 annular groove H 0 elastic body height h 0 spacer height h 1 right cylindrical portion height t elasticity Body thickness α Intersection angle
Claims (1)
はゴム状弾性体の基端部に、岸壁その他への取付けフラ
ンジを設けるとともに、その弾性体の先端に剛性スペー
サを取付けてなる防舷材であって、 前記弾性体の基端部側の約半部を直円筒状とするととも
に、その直円筒状部分より先端側の外輪郭形状をほぼ截
頭円錐状とし、前記剛性スペーサの高さを、弾性体の高
さの0.05〜0.3 倍の範囲としてなる防舷材。1. A fender material comprising a rubber or rubber-like elastic body having a substantially cylindrical shape as a whole, provided with a mounting flange for a quay or the like at a base end portion thereof, and a rigid spacer attached to a tip end of the elastic body. There, approximately half of the base end side of the elastic body is a right cylindrical shape, and the outer contour shape of the tip side from the right cylindrical portion is a truncated cone shape, and the height of the rigid spacer is Fenders that are in the range of 0.05 to 0.3 times the height of the elastic body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20107792A JP3234637B2 (en) | 1992-07-28 | 1992-07-28 | Fender |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20107792A JP3234637B2 (en) | 1992-07-28 | 1992-07-28 | Fender |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0649826A true JPH0649826A (en) | 1994-02-22 |
| JP3234637B2 JP3234637B2 (en) | 2001-12-04 |
Family
ID=16435014
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20107792A Expired - Lifetime JP3234637B2 (en) | 1992-07-28 | 1992-07-28 | Fender |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3234637B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7034521B2 (en) | 1999-06-02 | 2006-04-25 | Koyo Seiko Co., Ltd. | Wheel speed detector having stationary seal member for mounting magnetic sensor |
| US7336067B2 (en) | 2003-02-03 | 2008-02-26 | Jtekt Corporation | Sensor assembly, sealing device, and roller bearing apparatus for vehicles having integrated connector and ring |
| JP2008051135A (en) * | 2006-08-22 | 2008-03-06 | Kurashiki Kako Co Ltd | Damper |
-
1992
- 1992-07-28 JP JP20107792A patent/JP3234637B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7034521B2 (en) | 1999-06-02 | 2006-04-25 | Koyo Seiko Co., Ltd. | Wheel speed detector having stationary seal member for mounting magnetic sensor |
| US7336067B2 (en) | 2003-02-03 | 2008-02-26 | Jtekt Corporation | Sensor assembly, sealing device, and roller bearing apparatus for vehicles having integrated connector and ring |
| JP2008051135A (en) * | 2006-08-22 | 2008-03-06 | Kurashiki Kako Co Ltd | Damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3234637B2 (en) | 2001-12-04 |
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