JPH051532A - Flexible pipe device for exhaust pipe - Google Patents
Flexible pipe device for exhaust pipeInfo
- Publication number
- JPH051532A JPH051532A JP3178912A JP17891291A JPH051532A JP H051532 A JPH051532 A JP H051532A JP 3178912 A JP3178912 A JP 3178912A JP 17891291 A JP17891291 A JP 17891291A JP H051532 A JPH051532 A JP H051532A
- Authority
- JP
- Japan
- Prior art keywords
- support cover
- bellows
- cushioning material
- pin
- cap member
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/18—Construction facilitating manufacture, assembly, or disassembly
- F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
- F01N13/1811—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
- Joints Allowing Movement (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両排気管に用いられ
るフレキシブルパイプ装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flexible pipe device used for a vehicle exhaust pipe.
【０００２】[0002]
【従来の技術】本出願人により、先に、実願平２−２１
８４１号として、排気管用フレキシブルパイプ装置が提
案された。その排気管用フレキシブルパイプ装置は、図
１０に示すように、ベローズ１の一端に第１のサポート
カバー２を、ベローズの他端に第２のサポートカバー３
を、それぞれ固定し、第１のサポートカバー２にピン部
材４を取付け、第２のサポートカバー３にキャップ部材
５を取付け、ピン部材を取付けた第１のサポートカバー
とキャップ部材を取付けた第２のサポートカバーとの間
に形成される空間に、ワイヤメッシュから一体に形成さ
れたハット状（鍔付き帽子状）の緩衝材６を設けたもの
から構成されていた。2. Description of the Related Art The applicant of the present invention previously filed Japanese Patent Application No. 2-21.
As No. 841, a flexible pipe device for an exhaust pipe was proposed. As shown in FIG. 10, the flexible pipe device for an exhaust pipe has a first support cover 2 at one end of a bellows 1 and a second support cover 3 at the other end of the bellows.
Are fixed, the pin member 4 is attached to the first support cover 2, the cap member 5 is attached to the second support cover 3, and the first support cover having the pin member attached and the second member having the cap member attached In the space formed between the support cover and the support cover, a hat-like (cap-like cap-like) cushioning material 6 integrally formed from a wire mesh is provided.
【０００３】[0003]
【発明が解決しようとする課題】しかし、上述のハット
状緩衝材６の構造では、プレス成形時にハット状の筒状
部のワイヤメッシュ密度を十分に確保することが困難で
あった。しかも、このハット状の筒状部は軸受として最
も厳しい条件で使用されるので、密度不足によって、筒
状部つぶれ、へたりによるピン連結部のガタが発生し、
エンジンのローリング振動やエンジン爆発振動が排気管
を介してかかったときに、ピン連結部に打音が発生する
という問題があった。However, with the structure of the above-mentioned hat-shaped cushioning material 6, it was difficult to secure a sufficient wire mesh density in the hat-shaped tubular portion during press molding. Moreover, since this hat-shaped tubular portion is used under the most severe conditions as a bearing, the tubular portion is crushed due to insufficient density, and rattling of the pin connecting portion due to fatigue occurs,
There was a problem that when the rolling vibration of the engine or the engine explosion vibration was applied through the exhaust pipe, a hammering sound was generated at the pin connecting portion.
【０００４】本発明は、フレキシブル装置のピン部材と
キャップ部材間に介装したワイヤメッシュ緩衝材がつぶ
れやへたりあるいは摩耗することにより、前記ピン部材
とキャップ部材間にガタが生じたとしても、このガタの
範囲内で生じる排気管共振に起因する振動を減衰させ、
打音の発生を抑制できる排気管用フレキシブルパイプ装
置を提供することを目的とする。According to the present invention, even if the wire mesh cushioning material interposed between the pin member and the cap member of the flexible device is crushed, worn or worn, a play is generated between the pin member and the cap member. Attenuates the vibration caused by the exhaust pipe resonance that occurs within the range of this play,
An object of the present invention is to provide a flexible pipe device for an exhaust pipe that can suppress the generation of tapping sound.
【０００５】[0005]
【課題を解決するための手段】上記目的は、本発明によ
れば、排気管用フレキシブルパイプ装置が、次の手段を
備えることによって達成される。すなわち、第１の端部
および第２の端部を有するベローズと、一端が前記ベロ
ーズの第１の端部に固定され他端が前記ベローズの外側
で前記ベローズの第２の端部に向かって延びる第１のサ
ポートカバーと、一端が前記ベローズの第２の端部に固
定され他端が前記第１のサポートカバーの外側で前記ベ
ローズの第１の端部に向かって延びる第２のサポートカ
バーと、前記第１のサポートカバーに取付けられ前記第
１のサポートカバーからベローズ軸芯と直角方向にベロ
ーズ半径方向外方に延び前記第２のサポートカバーに形
成した切欠を挿通して前記第２のサポートカバーより外
側に延びるピン部材、前記ピン部材を該ピン部材の外側
から覆うようにして前記第２のサポートカバーに取付け
られたキャップ部材、及び前記ピン部材と前記キャップ
部材との間の空間に設けられたワイヤメッシュからなる
緩衝材、で構成されるピンジョイント部と、からなる排
気管用フレキシブルパイプ装置において、前記ピンジョ
イント部の、前記ピン部材とキャップ部材間の空間に設
けられる緩衝材は、該空間のピン部材径方向距離の変位
量が略同等である部位に、並列に配設された、荷重受用
緩衝材及び該荷重受用緩衝材より小さい弾性係数を有す
る減衰用緩衝材から構成されることを特徴とする排気管
用フレキシブルパイプ装置。According to the present invention, the above object is achieved by a flexible pipe device for an exhaust pipe comprising the following means. That is, a bellows having a first end and a second end, and one end fixed to the first end of the bellows and the other end outside the bellows toward the second end of the bellows. A first support cover extending and a second support cover having one end fixed to a second end of the bellows and the other end extending outside the first support cover toward the first end of the bellows. And a second notch formed in the second support cover, which is attached to the first support cover and extends outward from the first support cover in the radial direction of the bellows in a direction perpendicular to the bellows axis. A pin member extending to the outside of the support cover, a cap member attached to the second support cover so as to cover the pin member from the outside of the pin member, the pin member and the cap member. In a flexible pipe device for an exhaust pipe, which comprises a pin joint portion formed of a wire mesh cushioning material provided in a space between the pin member and the cap member, The cushioning material provided in the space has a load receiving cushioning material and a modulus of elasticity smaller than that of the load receiving cushioning material, which are arranged in parallel at the portions having substantially the same displacement amount in the radial direction of the pin member in the space. A flexible pipe device for an exhaust pipe, which is composed of a damping cushioning material.
【０００６】[0006]
【作用】上記本発明の排気管用フレキシブルパイプ装置
では、ピン部材とキャップ部材との間に、弾性係数が大
きい荷重受用緩衝材と弾性係数が小さい減衰用緩衝材と
が、互いに並列に配設されたシステムとなっている。使
用初期はガタがないから、打音は発生せず、荷重は主に
荷重受用緩衝材で受けられる。長期使用しているうち
に、荷重受用緩衝材には高荷重を受けて高面圧となるた
めにつぶれやへたりや摩耗が生じて、軽微ではあるがピ
ン部材とキャップ部材及び荷重受用緩衝材との間にガタ
が生じるかもしれない。この時にも、弾性係数の小さい
減衰用緩衝材は受ける面圧も低く、つぶれ、へたり、摩
耗は更に軽微であるため、ピン部材とキャップ部材及び
減衰用緩衝材との間にはほとんどガタは生じない。した
がって、大きな荷重がかかると、減衰用緩衝材が荷重受
用緩衝材側のガタ分だけ弾性変形する迄は減衰用緩衝材
で荷重が受けられ、それ以上の荷重に対しては荷重受用
緩衝材と減衰用緩衝材の両方が効くので、主に荷重受用
緩衝材で受けられる。そのため、荷重受用緩衝材につぶ
れやへたりが生じても、それによるガタ域において、減
衰用緩衝材のばね力と減衰力が働くので、打音の発生が
防止される。In the above-described flexible pipe apparatus for an exhaust pipe of the present invention, the load receiving cushioning material having a large elastic coefficient and the damping cushioning material having a small elastic coefficient are arranged in parallel between the pin member and the cap member. It has become a system. Since there is no rattling at the beginning of use, no hammering sound is produced and the load is mainly received by the load receiving cushioning material. During long-term use, the load-bearing cushioning material receives a high load and has a high surface pressure, which causes crushing, squatting, and wear, and although it is slight, the pin member, cap member, and load-bearing cushioning material There may be some play between and. Even at this time, since the damping cushioning material having a small elastic coefficient also receives a low surface pressure, and the crushing, the settling, and the wear are further slight, there is almost no play between the pin member, the cap member and the damping cushioning material. Does not happen. Therefore, when a large load is applied, the damping cushioning material receives the load until the damping cushioning material is elastically deformed by the amount of the play on the side of the load receiving cushioning material, and for a larger load, the damping cushioning material acts as the load absorbing cushioning material. Since both of the damping cushioning materials are effective, they are mainly received by the load receiving cushioning material. Therefore, even if the load receiving cushioning material is crushed or squeezed, the spring force and the damping force of the damping cushioning material act in the backlash region, so that the tapping noise is prevented.
【０００７】[0007]
【実施例】図１−図３は本発明の第１実施例（シングル
タイプ）を示し、図４−図６は本発明の第２実施例（デ
ュアルタイプ）を示し、図７および図８は両実施例に共
通に適用し得るピンジョイント部の構成を、２例、拡大
して示し、図９は両実施例に共通に適用し得る荷重対た
わみ量特性を示す。図中、両実施例について共通する部
材には同一の符号を付してある。1 to 3 show a first embodiment (single type) of the present invention, FIGS. 4 to 6 show a second embodiment (dual type) of the present invention, and FIGS. Two examples of the structure of the pin joint portion which can be commonly applied to both embodiments are shown in an enlarged manner, and FIG. 9 shows a load-deflection amount characteristic which can be commonly applied to both embodiments. In the figure, members common to both embodiments are designated by the same reference numerals.
【０００８】まず、両実施例についての共通構成を説明
する。排気管用フレキシブルパイプ装置は、総じて、ベ
ローズ１０、第１のサポートカバー２０、第２のサポー
トカバー３０、およびピンジョイント部８０から構成さ
れる。そして、ピンジョイント部８０は、ピン部材４
０、キャップ部材５０、荷重受用緩衝材６０、および減
衰用緩衝材９０、９０´から成る。ベローズ１０は、第
１の端部１１と、それと反対側の第２の端部１２と、第
１、第２の端部１１、１２を連結する蛇腹部１３とを有
する。第１、第２の端部１１、１２には、それぞれ排気
管（図示せず）が挿入され、ベローズと溶接により固定
される。First, a common configuration for both embodiments will be described. The exhaust pipe flexible pipe device generally includes a bellows 10, a first support cover 20, a second support cover 30, and a pin joint portion 80. Then, the pin joint portion 80 is connected to the pin member 4
0, the cap member 50, the load receiving cushioning material 60, and the damping cushioning materials 90 and 90 '. The bellows 10 has a first end portion 11, a second end portion 12 opposite to the first end portion 11, and a bellows portion 13 connecting the first and second end portions 11 and 12. An exhaust pipe (not shown) is inserted into each of the first and second ends 11 and 12, and is fixed to the bellows by welding.
【０００９】第１のサポートカバー２０は、第１の端部
２１と、該第１の端部２１より大径の第２の端部２２
と、第１の端部２１と第２の端部２２を連結する拡径部
２３とを有する。第１のサポートカバー２０の第１の端
部２１は、ベローズ１０の第１の端部１１および排気管
（図示せず）に、全周溶接により固定される。第１のサ
ポートカバー２０の第２の端部２２は、ベローズ１０の
外側でベローズの第２の端部１２に向かって延び、ベロ
ーズ蛇腹部１３を外周側から覆う。第１のサポートカバ
ー２０の、ベローズ蛇腹部１３の外側に対応する位置に
は、ベローズの直径の延長線上に、一対の穴が形成さ
れ、ここにピン部材４０、４０が挿入、固定される。The first support cover 20 has a first end portion 21 and a second end portion 22 having a diameter larger than that of the first end portion 21.
And an enlarged diameter portion 23 connecting the first end portion 21 and the second end portion 22. The first end portion 21 of the first support cover 20 is fixed to the first end portion 11 of the bellows 10 and the exhaust pipe (not shown) by welding all around. The second end 22 of the first support cover 20 extends toward the second end 12 of the bellows outside the bellows 10 and covers the bellows bellows 13 from the outer peripheral side. A pair of holes is formed on the first support cover 20 at a position corresponding to the outside of the bellows bellows portion 13 on an extension line of the diameter of the bellows, and the pin members 40, 40 are inserted and fixed therein.
【００１０】第２のサポートカバー３０は、第１の端部
３１と、該第１の端部３１より大径の第２の端部３２
と、第１の端部３１と第２の端部３２を連結する拡径部
３３とを有する。第２のサポートカバー３０の第１の端
部３１はベローズ１０の第２の端部１２および排気管
（図示せず）に、全周溶接により固定される。第２のサ
ポートカバー３０の第２の端部３２は、ベローズ１０の
外側でかつ第１のサポートカバー２０の外側でベローズ
の第１の端部１１に向かって延びる。第２のサポートカ
バー３０の第２の端部３２は、第１のサポートカバー２
０の第２の端部２２よりも大径であり、内周側に第１の
サポートカバー２０の第２の端部２２を受入れる。The second support cover 30 has a first end 31 and a second end 32 having a diameter larger than that of the first end 31.
And an enlarged diameter portion 33 connecting the first end portion 31 and the second end portion 32. The first end 31 of the second support cover 30 is fixed to the second end 12 of the bellows 10 and the exhaust pipe (not shown) by welding all around. The second end 32 of the second support cover 30 extends toward the first end 11 of the bellows outside the bellows 10 and outside the first support cover 20. The second end 32 of the second support cover 30 is formed by the first support cover 2
It has a larger diameter than the second end 22 of 0 and receives the second end 22 of the first support cover 20 on the inner peripheral side.
【００１１】第２のサポートカバー３０の、第１のサポ
ートカバー２０に形成したピン穴の外側に対応する部位
には、一対の切欠３４、３４が形成されている。この切
欠３４は、たとえば図２に示すように、第２のサポート
カバー３０の第２の端部３２側の端から第１の端部３１
側に向かって延びる平行切欠部３４ａと、平行切欠部３
４ａの巾より大径の部分円形部３４ｂとを組合せた形状
を有する。この切欠３４の部分円形部３４ｂにピン部材
４０が挿通される。平行切欠部３４ａより大径の部分円
形部３４ｂを設けたことによって、部分円形部３４ｂと
同径の外形を有するキャップ部材５０を部分円形部３４
ｂに嵌入したときにキャップ部材５０が平行切欠部３４
ａの方向にずれるのを防止でき、キャップ部材５０の位
置決めが容易になる。A pair of notches 34, 34 are formed in a portion of the second support cover 30 corresponding to the outside of the pin hole formed in the first support cover 20. For example, as shown in FIG. 2, the notch 34 extends from the end on the second end 32 side of the second support cover 30 to the first end 31.
Parallel notch 34a extending toward the side and parallel notch 3
It has a shape in combination with a partial circular portion 34b having a diameter larger than the width of 4a. The pin member 40 is inserted into the partial circular portion 34b of the notch 34. By providing the partial circular portion 34b having a diameter larger than that of the parallel cutout portion 34a, the cap member 50 having the same outer diameter as the partial circular portion 34b is provided.
When the cap member 50 is inserted into the
It is possible to prevent the displacement in the direction of “a” and facilitate the positioning of the cap member 50.
【００１２】ピン部材４０は、図７に拡大して示すよう
に、鍔部４１と円筒状部４２とから成る。円筒状部４２
の鍔部４１と反対側は開放しており、底をもたない。こ
の底無し構造により、ピン部材成形時において円筒状部
４２の長さを長くでき、軸受面積を大にして荷重受用緩
衝材６０および減衰用緩衝材９０にかかる単位面積当り
荷重を減少させる。ピン部材４０は第１のサポートカバ
ー２０のピン穴に内周側からさし込まれ、鍔部４１を第
１のサポートカバー２０の内周面に当接した状態で、第
１のサポートカバー２０に溶接により固定される。ピン
部材４０の円筒状部４２は第１のサポートカバー２０の
ピン穴を挿通して外側に延び、第２のサポートカバー３
０の切欠３４の部分円形部３４ｂを遊隙をもって挿通し
てさらに外側に延びる。ピン部材４０の外径は切欠３４
の平行部３４ａの巾より小であり、第２のサポートカバ
ー３０と第１のサポートカバー２０を組付けるときに、
ピン部材４０を平行部３４ａを通して部分円形部３４ｂ
に軸方向に入れる。The pin member 40 comprises a collar portion 41 and a cylindrical portion 42, as shown in an enlarged view in FIG. Cylindrical part 42
The side opposite to the collar portion 41 is open and has no bottom. With this bottomless structure, the length of the cylindrical portion 42 can be increased when the pin member is molded, and the bearing area is increased to reduce the load per unit area applied to the load receiving cushioning material 60 and the damping cushioning material 90. The pin member 40 is inserted into the pin hole of the first support cover 20 from the inner peripheral side, and in the state where the flange portion 41 is in contact with the inner peripheral surface of the first support cover 20, the first support cover 20. It is fixed by welding. The cylindrical portion 42 of the pin member 40 is inserted through the pin hole of the first support cover 20 and extends outward, and the second support cover 3
The partial circular portion 34b of the notch 34 of 0 is inserted with a clearance and extends further outward. The outer diameter of the pin member 40 is notched 34
The width is smaller than the width of the parallel portion 34a, and when the second support cover 30 and the first support cover 20 are assembled,
The pin member 40 is passed through the parallel portion 34a to form the partial circular portion 34b.
To the axial direction.
【００１３】キャップ部材５０は、図７に拡大して示す
ように、円筒状部５１と底部５２とを有し、円筒状部５
１の底部５２と反対側端にフランジを有さない。キャッ
プ部材５０は、ピン部材４０を間隔をもって外側から覆
う。キャップ部材の開放側端部の外周面を第２のサポー
トカバー３０の切欠３４の部分円筒部３４ｂに嵌入さ
せ、円筒状部５１の軸方向端面を荷重受用緩衝材６０の
鍔部に当接させた状態で、キャップ部材５０を第２のサ
ポートカバー３０に溶接により固定する。キャップ部材
５０はフランジをもたない構造としたために切欠３４へ
の嵌入が可能になり、かつキャップ部材５０成形時に円
筒状部５１の長さを長くすることができ、荷重受用緩衝
材６０にかかる面圧を減少させることができる。As shown in the enlarged view of FIG. 7, the cap member 50 has a cylindrical portion 51 and a bottom portion 52.
1 does not have a flange at the end opposite to the bottom 52. The cap member 50 covers the pin member 40 from the outside with a gap. The outer peripheral surface of the open end of the cap member is fitted into the partial cylindrical portion 34b of the cutout 34 of the second support cover 30, and the axial end surface of the cylindrical portion 51 is brought into contact with the flange portion of the load receiving cushioning material 60. In this state, the cap member 50 is fixed to the second support cover 30 by welding. Since the cap member 50 has a structure without a flange, the cap member 50 can be fitted into the notch 34, and the length of the cylindrical portion 51 can be lengthened when the cap member 50 is molded, so that the load receiving cushioning material 60 is applied. The surface pressure can be reduced.
【００１４】図７に示す構造においては、シャフト５３
が、キャップ部材５０に固定されており、キャップ部材
５０の一部を構成している。シャフト５３は、ピン部材
４０の円筒状部４２内に延びている。シャフト５３は、
ストレート部５４とその先端に設けた傘状部５５とを有
する。キャップ部材５０は底部５２の中央に穴を有して
おり、そこにシャフト５３のストレート部５４の、傘状
部５５と反対側の端部が挿入され、溶接により固定され
る。ストレート部５４の外径はピン部材４０の円筒状部
４２の内径より小であり、ストレート部５４の外周とピ
ン部材４０の円筒状部４２の内周との間には環状空間が
形成される。In the structure shown in FIG. 7, the shaft 53
Is fixed to the cap member 50 and constitutes a part of the cap member 50. The shaft 53 extends into the cylindrical portion 42 of the pin member 40. The shaft 53 is
It has a straight portion 54 and an umbrella-shaped portion 55 provided at the tip thereof. The cap member 50 has a hole at the center of the bottom portion 52, and the end portion of the straight portion 54 of the shaft 53 on the side opposite to the umbrella-shaped portion 55 is inserted therein and fixed by welding. The outer diameter of the straight portion 54 is smaller than the inner diameter of the cylindrical portion 42 of the pin member 40, and an annular space is formed between the outer periphery of the straight portion 54 and the inner periphery of the cylindrical portion 42 of the pin member 40. ..
【００１５】荷重受用緩衝材６０は、図７に拡大して示
すように、ピン部材４０を取付けた第１のサポートカバ
ー２０と、キャップ部材５０を取付けた第２のサポート
カバー３０との間に形成される空間に設けられる。荷重
受用緩衝材６０は、ワイヤメッシュの成形材から成り、
高い弾性係数をもつように高密度に成形される。また、
荷重受用緩衝材６０は、互いに別体に形成された鍔部６
１と筒部６２とから成る。筒部６２は底をもたず、両端
が開放されている。鍔部６１と筒部６２とを別体に成形
したので、従来のような板状メッシュ２から筒部をプレ
ス成形するときに生じるような引張りによる筒部ワイヤ
メッシュの密度不足、密度不均一は生じず、十分な密度
をもちかつ密度の均一なワイヤメッシュ筒部６２を作製
できる。また筒部６２を鍔部６１と別体に形成するの
で、筒部６２の長さを長くでき、荷重受面積を大にで
き、筒部ワイヤメッシュにかかる面圧を減少できる。As shown in the enlarged view of FIG. 7, the load receiving cushioning member 60 is provided between the first support cover 20 having the pin member 40 attached thereto and the second support cover 30 having the cap member 50 attached thereto. It is provided in the space formed. The load receiving cushioning material 60 is made of a wire mesh molding material,
It is densely molded to have a high elastic modulus. Also,
The load receiving cushioning material 60 is a collar portion 6 formed separately from each other.
1 and a tubular portion 62. The tubular portion 62 has no bottom and both ends are open. Since the collar portion 61 and the tubular portion 62 are molded separately, the tubular wire mesh lacks in density and uneven density due to the pulling that occurs when the tubular portion is press-molded from the plate mesh 2 as in the conventional case. It is possible to produce the wire mesh tube portion 62 that does not occur and has a sufficient density and a uniform density. Further, since the tubular portion 62 is formed separately from the collar portion 61, the length of the tubular portion 62 can be increased, the load receiving area can be increased, and the surface pressure applied to the tubular wire mesh can be reduced.
【００１６】鍔部６１は、第１のサポートカバー２０の
外面と第２のサポートカバー３０の内面の間の環状空間
に配され、筒部６２はピン部材４０の外周面とキャップ
部材５０の内周面との間に形成される円筒状空間に配さ
れる。この円筒状空間は、ピン部材４０および緩衝材６
０が底無しで形成されることにより、十分な長さに形成
され、軸受として最も厳しい条件となる筒部６２の面圧
を十分にさげることができる。The collar portion 61 is arranged in an annular space between the outer surface of the first support cover 20 and the inner surface of the second support cover 30, and the tubular portion 62 is provided in the outer peripheral surface of the pin member 40 and the cap member 50. It is arranged in a cylindrical space formed between itself and the peripheral surface. This cylindrical space has a pin member 40 and a cushioning member 6.
Since 0 is formed without a bottom, it is formed to have a sufficient length, and the surface pressure of the cylindrical portion 62, which is the most severe condition for the bearing, can be sufficiently reduced.
【００１７】減衰用緩衝材９０は、図７に示す構造にお
いては、ピン部材４０の円筒状部４２の内周面とシャフ
ト５３のストレート部５４の外周面との間で、かつ、キ
ャップ部材５０の底部５２とシャフト５３の傘状部５５
との間に形成される環状空間に、半径方向軸方向ともに
圧入によりある程度の予荷重を与えて配設される。減衰
用緩衝材９０は、ワイヤメッシュの円筒状成形材から成
り、荷重受用緩衝材６０の弾性係数より小さい弾性係数
を有するように、比較的低密度に成形される。たとえ
ば、荷重受用緩衝材６０のばね定数を５０００Ｋｇ／ｍ
ｍ、減衰用緩衝材９０のばね定数を１００Ｋｇ／ｍｍと
いうように設定する。したがって、ピン部材４０と、シ
ャフト５３付きキャップ部材５０との間には、荷重受用
緩衝材６０と減衰用緩衝材９０とが、力の伝達経路とし
てみた場合、互いに並列となるように、配設されてい
る。In the structure shown in FIG. 7, the damping cushioning material 90 is between the inner peripheral surface of the cylindrical portion 42 of the pin member 40 and the outer peripheral surface of the straight portion 54 of the shaft 53, and the cap member 50. Bottom 52 of the shaft and the umbrella-shaped portion 55 of the shaft 53
A certain amount of preload is applied to the annular space formed between and by a press fit in both the radial and axial directions. The damping cushioning material 90 is made of a wire mesh cylindrical molding material, and is molded to have a relatively low density so as to have an elastic coefficient smaller than that of the load receiving cushioning material 60. For example, if the spring constant of the load receiving cushioning material 60 is 5000 Kg / m
m, and the spring constant of the damping cushioning material 90 is set to 100 Kg / mm. Therefore, the load receiving cushioning material 60 and the damping cushioning material 90 are arranged between the pin member 40 and the cap member 50 with the shaft 53 so as to be in parallel with each other when viewed as a force transmission path. Has been done.
【００１８】図８は、図７とは別の、本発明に係るもう
一つのピンジョイント部８０の構造を示している。図８
の構造で図７の構造と同一の部分は、図７と同一の符号
を付すことにより説明を省略し、以下、異なる部分のみ
を説明する。図８において、キャップ部材５０はシャフ
トを有していない。減衰用緩衝材９０´はキャップ部材
５０の内周面とピン部材４０の外周面との間の環状空間
内に配される。さらに詳しく説明すると、荷重受用緩衝
材６０の筒部６２の長さはキャップ部材５０の円筒状部
５１の長さより小としてあり、このため荷重受用緩衝材
６０の筒部６２に軸方向に隣接して空間が形成され、こ
の空間を埋めるようにして円筒状の減衰用緩衝材９０´
が予圧縮した状態で配設される。したがって、ピン部材
４０とキャップ部材５０との間には、荷重受用緩衝材６
０と減衰用軸受材９０´とが、力の伝達経路としてみた
場合、互いに並列となるように、配設されている。FIG. 8 shows a structure of another pin joint portion 80 according to the present invention, which is different from that shown in FIG. Figure 8
7, the description of the same parts as those of FIG. 7 will be omitted by giving the same reference numerals to those of FIG. 7, and only the different parts will be described below. In FIG. 8, the cap member 50 does not have a shaft. The damping cushioning material 90 ′ is arranged in the annular space between the inner peripheral surface of the cap member 50 and the outer peripheral surface of the pin member 40. More specifically, the length of the tubular portion 62 of the load receiving cushioning material 60 is smaller than the length of the cylindrical portion 51 of the cap member 50. Therefore, it is adjacent to the tubular portion 62 of the load receiving cushioning material 60 in the axial direction. To form a space, and the cylindrical damping cushioning material 90 'is formed so as to fill the space.
Are arranged in a pre-compressed state. Therefore, the load receiving cushioning material 6 is provided between the pin member 40 and the cap member 50.
0 and the damping bearing material 90 ′ are arranged so as to be in parallel with each other when viewed as a force transmission path.
【００１９】なお、ベローズ１０の内周面には、排気ガ
ス流が凹凸するベローズ蛇腹部１３から流れ抵抗を受け
ないように、また、排気脈動がベローズ凹凸部に直接当
たることによる異音の発生を防止するために、ベローズ
１０の上流側の端部、図示例では第２の端部１２から、
下流側の端部、図示例では第１の端部１１に向けて延び
るなめらかな整流管７０が、設けられている。整流管７
０は、その一端をベローズ１０の上流側端部内周に固定
されている。On the inner peripheral surface of the bellows 10, the exhaust gas flow does not receive flow resistance from the bellows bellows portion 13 having irregularities, and the exhaust pulsation directly causes the irregularities of the bellows to generate abnormal noise. In order to prevent the above, from the upstream end of the bellows 10, that is, the second end 12 in the illustrated example,
A smooth rectifying tube 70 extending toward the downstream end, that is, the first end 11 in the illustrated example, is provided. Rectifier tube 7
0 has one end fixed to the inner circumference of the upstream end of the bellows 10.
【００２０】次に各実施例について異なる構造について
説明する。ただし、図において第１実施例に特有な構造
については符号にサフィックスＡを付してあり、第２実
施例に特有な構造については符号にサフィックスＢを付
してある。第１実施例においては、図１−図３に示すよ
うに、ベローズ１０の個数は１個であり、第１、第２の
サポートカバー２０Ａ、３０Ａは、断面が円形である。
これに対し、第２実施例においては、図４−図６に示す
ように、ベローズ１０の個数は２個であり、第１、第２
のサポートカバー２０Ｂ、３０Ｂは、断面がほぼひょう
たん形をしている。Next, a different structure of each embodiment will be described. However, in the drawing, suffixes A are added to the reference numerals for the structures unique to the first embodiment, and suffixes B are added to the reference numerals for the structures unique to the second embodiment. In the first embodiment, as shown in FIGS. 1 to 3, the number of bellows 10 is one, and the first and second support covers 20A and 30A have a circular cross section.
On the other hand, in the second embodiment, the number of bellows 10 is two, as shown in FIGS.
Each of the support covers 20B and 30B has a gourd-shaped cross section.
【００２１】次に、作用を説明する。フレキシブルパイ
プ装置にかかる荷重は、第１、第２のサポートカバー２
０、３０のピン部材４０による連結構造によって受け持
たれ、ベローズ１０に過大な荷重はかからない。ピン連
結構造はフレキシブルパイプ装置に屈曲を許しつつ２つ
の排気管を連結する。また、第１、第２のサポートカバ
ー２０、３０は、ベローズ１０を飛石、路面干渉、融雪
塩による塩害腐食等から保護する。Next, the operation will be described. The load applied to the flexible pipe device depends on the first and second support covers 2
It is carried by the connecting structure of the pin members 40 of 0 and 30, and the bellows 10 is not overloaded. The pin connection structure connects the two exhaust pipes while allowing the flexible pipe device to bend. Further, the first and second support covers 20 and 30 protect the bellows 10 from flying stones, road surface interference, salt damage corrosion due to snow melting salt, and the like.
【００２２】２つの排気管間にかかる荷重は、ピン部材
４０、キャップ部材５０、ワイヤメッシュの荷重受用緩
衝材６０、およびワイヤメッシュの減衰用緩衝材９０ま
たは９０´から成るピンジョイント部８０にかかる。荷
重受用緩衝材６０および減衰用緩衝材９０、９０´は弾
性を有しクッションとして作用する他、振動に対して減
衰材としても機能する。荷重受用緩衝材６０および減衰
用緩衝材９０、９０´を介装することにより、ピン部材
４０とキャップ部材５０、第１のサポートカバー２０と
第２のサポートカバー３０の直接の当りがなくなり、メ
タル衝突音の発生はない。また、緩衝材６０、９０、９
０´がワイヤメッシュから成るので、比較的高温がかか
る排気管の連結構造に用いても熱的問題は生じない。The load applied between the two exhaust pipes is applied to the pin member 40, the cap member 50, the wire mesh load receiving cushioning material 60, and the wire mesh damping cushioning material 90 or 90 '. .. The load receiving cushioning material 60 and the damping cushioning materials 90 and 90 'have elasticity and act as cushions, and also function as damping materials against vibration. By interposing the load receiving cushioning material 60 and the damping cushioning materials 90 and 90 ′, the pin member 40 and the cap member 50, the first support cover 20 and the second support cover 30 are not directly contacted, and the metal No collision sound is generated. Also, the cushioning material 60, 90, 9
Since 0'is composed of a wire mesh, there is no thermal problem even if it is used in a structure for connecting exhaust pipes to which relatively high temperature is applied.
【００２３】使用初期においては、荷重受用緩衝材６０
につぶれやへたりが発生していないので、ピン部材４０
の外周、荷重受用緩衝材６０、およびキャップ部材５０
間にガタはなく、ガタの存在下で部材同志が衝突するこ
とによる異音の発生はない。この場合、ピン部材４０と
キャップ部材５０間には、図９に示すように、主に荷重
受用緩衝材６０によって力が伝達される。In the initial stage of use, the load receiving cushioning material 60
Since there is no crushing or sagging on the pin member 40
Outer periphery, load receiving cushioning material 60, and cap member 50
There is no play between them, and no abnormal noise is generated due to collision between members in the presence of play. In this case, as shown in FIG. 9, the force is mainly transmitted between the pin member 40 and the cap member 50 by the load receiving cushioning material 60.
【００２４】しかし、排気管用フレキシブルパイプ装置
には、エンジンのローリングや爆発行程による振動がか
かり、これらは莫大な回数繰返されて軸受部に繰返し荷
重をかけるので、ついには弾性係数の大きい荷重受用緩
衝材６０につぶれやへたりや摩耗等の永久変形が生じ、
ピン部材４０、キャップ部材５０、荷重受用緩衝材６０
間に、軽微ではあるが、ガタが生じる。However, the flexible pipe device for the exhaust pipe is vibrated due to the rolling of the engine and the explosive stroke, and these are repeated a huge number of times to repeatedly apply a load to the bearing portion, so that finally the load receiving buffer having a large elastic coefficient is received. Permanent deformation such as crushing, fatigue and wear occurs on the material 60,
Pin member 40, cap member 50, load receiving cushioning material 60
In the meantime, a slight amount of backlash occurs.
【００２５】このようなガタが生じた後では、ピン部材
４０とキャップ部材５０間の力の伝達は使用初期と異な
ってくる。すなわち、図９に示すように、ガタの範囲に
おいては、荷重は減衰用緩衝材９０、９０´のみによっ
てピン４０部材とキャップ部材５０との間に伝達され、
ガタ以上の変位になったときに荷重受用緩衝材６０も働
いて、荷重受用緩衝材６０と減衰用緩衝材９０、９０´
の両方によって荷重を伝達する。両方の緩衝材６０、９
０、９０´が効くときは、主に荷重受用緩衝材６０が荷
重を伝達するので、減衰用緩衝材９０、９０´には大き
な荷重は作用せず、つぶれやへたりや摩耗は生じにく
い。更に、万一軽微なつぶれ、へたり、摩耗が生じたと
しても、組付け時に与えられた予荷重により、これを吸
収し、ピン部材４０とキャップ部材５０及び減衰用緩衝
材９０、９０´との間にガタが発生することはない。After such backlash occurs, the force transmission between the pin member 40 and the cap member 50 is different from the initial stage of use. That is, as shown in FIG. 9, in the range of play, the load is transmitted between the pin 40 member and the cap member 50 only by the damping cushioning members 90, 90 '.
When the displacement exceeds the play, the load receiving cushioning material 60 also works, and the load receiving cushioning material 60 and the damping cushioning materials 90, 90 '.
The load is transmitted by both. Both cushioning materials 60, 9
When 0 and 90 ′ are effective, the load receiving cushioning material 60 mainly transmits the load, so that a large load does not act on the damping cushioning material 90 and 90 ′, and crushing, squatting, and abrasion are less likely to occur. Further, even if slight crushing, fatigue, or wear occurs, it is absorbed by the preload given at the time of assembly, and the pin member 40, the cap member 50, and the damping cushioning members 90, 90 'are absorbed. There is no play during the period.
【００２６】荷重受用緩衝材６０側のガタの範囲におい
て、減衰用緩衝材９０、９０´が働くときには、減衰用
緩衝材９０、９０´のばね力と変位の積であるエネルギ
（図９のハッチ部分）は、ワイヤメッシュの減衰用緩衝
材９０、９０´に吸収されるとともに、ワイヤメッシュ
のもつヒステリシスが減衰力となって振動を抑える。ま
た、減衰用緩衝材９０、９０´のばね力によって、ピン
部材４０とキャップ部材５０の相対変位時の速度も抑え
られ、ピン部材４０、キャップ部材５０、荷重受用緩衝
材６０の衝突力も大巾に弱められ衝突音が抑えられる。
このようにして、荷重受用緩衝材６０のつぶれ、へたり
等によって荷重受用緩衝材６０側に軽微なガタが生じて
も、減衰用緩衝材９０、９０´のばね力と減衰力とによ
って、打音は抑えられる。When the damping cushioning materials 90, 90 'act in the play range on the side of the load receiving cushioning material 60, the energy (the hatch in FIG. 9) which is the product of the spring force and the displacement of the damping cushioning material 90, 90'. (Part) is absorbed by the damping material 90, 90 'for damping the wire mesh, and the hysteresis of the wire mesh serves as a damping force to suppress vibration. In addition, the spring force of the damping cushioning materials 90 and 90 ′ also suppresses the speed at the time of relative displacement of the pin member 40 and the cap member 50, and the collision force of the pin member 40, the cap member 50, and the load receiving cushioning material 60 is also large. It is weakened by and the collision noise is suppressed.
In this way, even if slight backlash occurs on the load-receiving cushioning material 60 side due to crushing, sagging, etc. of the load-receiving cushioning material 60, the damping force of the damping cushioning materials 90 and 90 ′ is reduced by the spring force and the damping force. The sound is suppressed.
【００２７】軸受部の打音を抑制するとともに軸受部の
信頼性、耐久性を向上させるには、荷重受用緩衝材６０
自体の密度、信頼性、耐久性を上げること、および軸受
面積を大にして軸受の単位面積当り荷重を減少させるこ
とが有効である。In order to suppress the impact sound of the bearing portion and improve the reliability and durability of the bearing portion, the load receiving cushioning material 60 is used.
It is effective to increase the density, reliability and durability of the bearing itself and to increase the bearing area to reduce the load per unit area of the bearing.
【００２８】従来はハット状ワイヤメッシュを作製する
のにワイヤメッシュを板状にしたものをプレス成形して
図１０のようなハット状にしていたが、製作時に筒状部
のワイヤメッシュ密度が疎となり、軸受として最も厳し
い条件で使用される筒状部の密度を十分に確保すること
ができなかった。しかし、本発明実施例では、荷重受用
緩衝材６０の鍔部６０ａと筒部６０ｂとを別体としたの
で、筒部６０ｂを板状ワイヤメッシュを丸めて作製で
き、あるいはパイプ状ワイヤメッシュの切断により作製
でき、十分な密度で、しかも均一な密度に製作できる。
また、プレスによるハット状成形におけるような無理な
成形がないため、ワイヤメッシュのほつれ等もない。こ
れらによって、荷重受用緩衝材６０自体の信頼性、耐久
性が高められる。Conventionally, in order to manufacture a hat-shaped wire mesh, a plate-shaped wire mesh was press-molded into a hat shape as shown in FIG. 10. However, during manufacturing, the wire mesh density of the tubular portion is sparse. Therefore, it was not possible to sufficiently secure the density of the cylindrical portion used under the most severe conditions as a bearing. However, in the embodiment of the present invention, since the collar portion 60a and the tubular portion 60b of the load receiving cushioning material 60 are separate bodies, the tubular portion 60b can be manufactured by rolling the plate-shaped wire mesh or cutting the pipe-shaped wire mesh. It is possible to manufacture with a sufficient density and a uniform density.
Further, since there is no unreasonable forming as in the hat-shaped forming by pressing, there is no fraying of the wire mesh. These enhance the reliability and durability of the load receiving cushioning material 60 itself.
【００２９】軸受の単位面積あたりの荷重の軽減には種
々の構成が寄与する。荷重受用緩衝材６０を筒部６２と
鍔部６１とに分割形成するので、筒部６２は鍔部６１か
ら拘束されることなく自由に長く作製でき、軸受面積を
増加できる。たとえば、従来のようにプレスによるハッ
ト状成形の場合は、円筒状部自体の長さも制約を受ける
し、かつハット状の先端の底板への移り変わり部にＲが
かかるので円筒状部はその分短くなっていたが、本発明
実施例の場合はそのような制約を受けない。Various configurations contribute to reducing the load per unit area of the bearing. Since the load receiving cushioning material 60 is divided into the tubular portion 62 and the flange portion 61, the tubular portion 62 can be freely made long without being restricted by the flange portion 61, and the bearing area can be increased. For example, in the case of hat-shaped molding by pressing as in the past, the length of the cylindrical portion itself is also restricted, and since the transition of the hat-shaped tip to the bottom plate is R, the cylindrical portion is shortened accordingly. However, the embodiment of the present invention is not subject to such a restriction.
【００３０】また、ピン部材４０も、従来の深絞り加工
による有底ハット状からパイプ材の鍔出し加工による底
無しの円筒状部４２としたので、円筒状部４２の長さを
長くでき、軸受面積を増加できる。また、キャップ部材
５０も従来のように鍔部をもたなくてよいので、円筒状
部５１の長さを従来に比べて長くでき、軸受面積を増加
できる。さらに、従来のように鍔部をもつキャップ部材
の場合は、鍔の内周にＲがかかり、ワイヤメッシュ保持
面が一部全周にわたって欠落し、かつサポートカバーの
切欠部も部分的にワイヤメッシュ保持面が欠落していた
が、本発明ではキャップ部材５０は鍔をもたず端部を荷
重受用緩衝材６０の鍔部６１に当接させる構造としたの
で、ワイヤメッシュ保持面に欠落は生じず、軸受面が増
加する。これらの総合作用により、軸受の単位面積あた
りの荷重が軽減し、軸受の信頼性、耐久性が向上する。Further, the pin member 40 is also changed from the conventional bottomed hat shape formed by deep drawing to the bottomless cylindrical portion 42 formed by the pipe material projecting, so that the length of the cylindrical portion 42 can be increased and the bearing The area can be increased. Further, since the cap member 50 does not have to have the flange portion as in the conventional case, the length of the cylindrical portion 51 can be made longer than in the conventional case, and the bearing area can be increased. Further, in the case of a cap member having a collar portion as in the conventional case, R is applied to the inner circumference of the collar, the wire mesh holding surface is partially cut off all around, and the notch portion of the support cover is partially wire mesh. Although the holding surface is missing, in the present invention, since the cap member 50 has a structure in which the end portion is brought into contact with the brim portion 61 of the load receiving cushioning material 60 without a flange, the wire mesh holding surface is not missing. However, the bearing surface increases. The combined action reduces the load per unit area of the bearing and improves the reliability and durability of the bearing.
【００３１】[0031]
【発明の効果】本発明によれば、ピンジョイント部の、
ピン部材とキャップ部材間の空間において、それら空間
のピン径方向への変位量が略同等である部位に、荷重受
用緩衝材と該荷重受用緩衝材より小さい弾性系数を有す
る減衰用緩衝材を並列に介装したので、荷重受用緩衝材
につぶれやへたりが生じても、減衰用緩衝材がばね力と
減衰力でガタの影響を吸収し、打音の発生を抑制でき
る。According to the present invention, the pin joint portion,
In the space between the pin member and the cap member, a load receiving cushioning material and a damping cushioning material having an elastic modulus smaller than that of the load receiving cushioning material are arranged in parallel at the portions where the displacements in the space in the pin radial direction are substantially equal. Even if the load receiving cushioning material is crushed or squeezed, the damping cushioning material absorbs the influence of backlash by the spring force and the damping force, and the generation of hammering noise can be suppressed.
【図１】本発明の第１実施例に係る排気管用フレキシブ
ルパイプ装置の断面図である。FIG. 1 is a cross-sectional view of a flexible pipe device for an exhaust pipe according to a first embodiment of the present invention.
【図２】図１の装置の平面図である。2 is a plan view of the device of FIG. 1. FIG.
【図３】図１の装置の正面図である。FIG. 3 is a front view of the device of FIG.
【図４】本発明の第２実施例に係る排気管用フレキシブ
ル装置の一部を断面にして示した側面図である。FIG. 4 is a side view showing a partial cross section of a flexible device for an exhaust pipe according to a second embodiment of the present invention.
【図５】図４の装置の一部断面平面図である。5 is a partial cross-sectional plan view of the device of FIG.
【図６】図４の装置の正面図である。FIG. 6 is a front view of the device of FIG.
【図７】第１実施例、第２実施例に共通なピンジョイン
ト部の拡大断面図である。FIG. 7 is an enlarged sectional view of a pin joint portion common to the first and second embodiments.
【図８】第１実施例、第２実施例に共通な、ピンジョイ
ント部のもう一つの例の拡大断面図である。FIG. 8 is an enlarged cross-sectional view of another example of the pin joint portion, which is common to the first and second embodiments.
【図９】本発明の排気管用フレキシブルパイプ装置の荷
重対たわみ特性図である。FIG. 9 is a load vs. deflection characteristic diagram of the exhaust pipe flexible pipe device of the present invention.
【図１０】実願平２−２１８４１号で提案された排気管
用フレキシブルパイプ装置に準じた装置の断面図であ
る。FIG. 10 is a cross-sectional view of an apparatus conforming to the exhaust pipe flexible pipe apparatus proposed in Japanese Patent Application No. 2-21841.
１０ ベローズ １１ ベローズの第１の端部 １２ ベローズの第２の端部 ２０ 第１のサポートカバー ３０ 第２のサポートカバー ３４ 切欠 ３４ａ 切欠の平行部 ３４ｂ 切欠の部分円形部 ４０ ピン部材 ４１ ピン部材の鍔部 ４２ ピン部材の円筒状部 ５０ キャップ部材 ５１ キャップ部材の円筒状部 ５２ キャップ部材の底部 ５３ シャフト ５４ ストレート部 ５５ 傘状部 ６０ 荷重受用緩衝材 ６１ 荷重受用緩衝材の鍔部 ６２ 荷重受用緩衝材の筒部 ９０ 減衰用緩衝材 ９０´ 減衰用緩衝材 10 Bellows 11 First End of Bellows 12 Second End of Bellows 20 First Support Cover 30 Second Support Cover 34 Notch 34a Notch Parallel Part 34b Notch Circular Part 40 Pin Member 41 Pin Member Collar part 42 Cylindrical part of pin member 50 Cap member 51 Cylindrical part of cap member 52 Bottom part of cap member 53 Shaft 54 Straight part 55 Umbrella part 60 Load receiving buffer material 61 Load receiving buffer material flange part 62 Load receiving buffer material Cylinder of material 90 Damping material for damping 90 'Damping material for damping
Claims (1)
ローズと、一端が前記ベローズの第１の端部に固定され
他端が前記ベローズの外側で前記ベローズの第２の端部
に向かって延びる第１のサポートカバーと、一端が前記
ベローズの第２の端部に固定され他端が前記第１のサポ
ートカバーの外側で前記ベローズの第１の端部に向かっ
て延びる第２のサポートカバーと、前記第１のサポート
カバーに取付けられ前記第１のサポートカバーからベロ
ーズ軸芯と直角方向にベローズ半径方向外方に延び前記
第２のサポートカバーに形成した切欠を挿通して前記第
２のサポートカバーより外側に延びるピン部材、前記ピ
ン部材を該ピン部材の外側から覆うようにして前記第２
のサポートカバーに取付けられたキャップ部材、及び前
記ピン部材と前記キャップ部材との間の空間に設けられ
たワイヤメッシュからなる緩衝材、で構成されるピンジ
ョイント部と、からなる排気管用フレキシブルパイプ装
置において、前記ピンジョイント部の、前記ピン部材と
キャップ部材間の空間に設けられる緩衝材は、該空間の
ピン部材径方向距離の変位量が略同等である部位に、並
列に配設された、荷重受用緩衝材及び該荷重受用緩衝材
より小さい弾性係数を有する減衰用緩衝材から構成され
ることを特徴とする排気管用フレキシブルパイプ装置。Claim: What is claimed is: 1. A bellows having a first end and a second end, and one end fixed to the first end of the bellows and the other end outside the bellows. A first support cover extending toward a second end of the bellows, and a first end of the bellows having one end fixed to the second end of the bellows and the other end outside the first support cover. A second support cover extending toward the first support cover, and a second support cover attached to the first support cover and extending outward from the first support cover in a radial direction of the bellows in a direction perpendicular to a bellows axis. The pin member that extends through the notch through the second support cover and the pin member that covers the pin member from the outside of the second member.
Flexible pipe device for an exhaust pipe, comprising: a cap member attached to a support cover of the above; and a pin joint portion composed of a buffer member made of a wire mesh provided in a space between the pin member and the cap member. In the above, the cushioning material provided in the space between the pin member and the cap member of the pin joint portion is arranged in parallel at a portion where the displacement amount of the space in the pin member radial direction is substantially equal. A flexible pipe device for an exhaust pipe, comprising a load-absorbing cushioning material and a damping cushioning material having an elastic coefficient smaller than that of the load-receiving cushioning material.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3178912A JP2819868B2 (en) | 1991-06-25 | 1991-06-25 | Flexible pipe device for exhaust pipe |
| EP92305288A EP0519636B1 (en) | 1991-06-14 | 1992-06-09 | Flexible joint for an exhaust pipe |
| DE69205499T DE69205499T2 (en) | 1991-06-14 | 1992-06-09 | Flexible connection for an exhaust pipe. |
| US07/896,179 US5318329A (en) | 1991-06-14 | 1992-06-10 | Flexible joint for an exhaust pipe |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3178912A JP2819868B2 (en) | 1991-06-25 | 1991-06-25 | Flexible pipe device for exhaust pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH051532A true JPH051532A (en) | 1993-01-08 |
| JP2819868B2 JP2819868B2 (en) | 1998-11-05 |
Family
ID=16056843
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3178912A Expired - Fee Related JP2819868B2 (en) | 1991-06-14 | 1991-06-25 | Flexible pipe device for exhaust pipe |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2819868B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100353122B1 (en) * | 2000-08-25 | 2002-09-16 | 주식회사 에스제이엠 | Exhaust decoupler system |
| DE112008002406T5 (en) | 2007-09-06 | 2010-07-15 | Toyota Jidosha Kabushiki Kaisha, Toyota-shi | Exhaust device for an internal combustion engine of a vehicle |
| KR101379273B1 (en) * | 2012-07-24 | 2014-03-27 | 타타대우상용차 주식회사 | Multi-axis automobile exhaust pipe joint connection |
| US9051476B2 (en) | 2010-12-30 | 2015-06-09 | Ticona Llc | Powder containing a polyoxymethylene polymer for coating metallic substrates |
| US20170145882A1 (en) * | 2015-04-09 | 2017-05-25 | K&N Engineering, Inc. | Drone elimination muffler |
| CN109339929A (en) * | 2018-11-05 | 2019-02-15 | 徐州瑞田工程机械有限公司 | A kind of car exhaust pipe fixed equipment |
-
1991
- 1991-06-25 JP JP3178912A patent/JP2819868B2/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100353122B1 (en) * | 2000-08-25 | 2002-09-16 | 주식회사 에스제이엠 | Exhaust decoupler system |
| DE112008002406T5 (en) | 2007-09-06 | 2010-07-15 | Toyota Jidosha Kabushiki Kaisha, Toyota-shi | Exhaust device for an internal combustion engine of a vehicle |
| US9051476B2 (en) | 2010-12-30 | 2015-06-09 | Ticona Llc | Powder containing a polyoxymethylene polymer for coating metallic substrates |
| KR101379273B1 (en) * | 2012-07-24 | 2014-03-27 | 타타대우상용차 주식회사 | Multi-axis automobile exhaust pipe joint connection |
| US20170145882A1 (en) * | 2015-04-09 | 2017-05-25 | K&N Engineering, Inc. | Drone elimination muffler |
| US10519828B2 (en) * | 2015-04-09 | 2019-12-31 | K&N Engineering, Inc. | Drone elimination muffler |
| US11655740B2 (en) | 2015-04-09 | 2023-05-23 | K&N Engineering, Inc. | Drone elimination muffler |
| CN109339929A (en) * | 2018-11-05 | 2019-02-15 | 徐州瑞田工程机械有限公司 | A kind of car exhaust pipe fixed equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2819868B2 (en) | 1998-11-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |