JPH0861383A - Housing vibration control structure of frictional engagement device - Google Patents

Housing vibration control structure of frictional engagement device

Info

Publication number
JPH0861383A
JPH0861383A JP6201701A JP20170194A JPH0861383A JP H0861383 A JPH0861383 A JP H0861383A JP 6201701 A JP6201701 A JP 6201701A JP 20170194 A JP20170194 A JP 20170194A JP H0861383 A JPH0861383 A JP H0861383A
Authority
JP
Japan
Prior art keywords
housing
clutch
flat surface
shoe
vibration control
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
Application number
JP6201701A
Other languages
Japanese (ja)
Other versions
JP3322014B2 (en
Inventor
Yukinobu Sato
之信 佐藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Suzuki Motor Corp
Original Assignee
Suzuki Motor Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Suzuki Motor Corp filed Critical Suzuki Motor Corp
Priority to JP20170194A priority Critical patent/JP3322014B2/en
Publication of JPH0861383A publication Critical patent/JPH0861383A/en
Application granted granted Critical
Publication of JP3322014B2 publication Critical patent/JP3322014B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D2043/145—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members the centrifugal masses being pivoting

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Braking Arrangements (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

PURPOSE: To suppress the abnormal noise generated between a shoe member and a housing member by forming a flat surface and a recessed part on the outer peripheral surface of a housing member and setting a vibration control member in contact with the flat surface including the boundary between the flat surface and the recessed part. CONSTITUTION: The housing vibration control structure installed on a clutch device mounted on a power unit for a motorcycle is formed to a frictional engagement device consisting of a housing 48, clutch shoe, and a vibration control plate 50. The housing 48 has a nearly bowl shape as a whole, and has a bottom part 48a extended outwardly from the center axis and a side edge part 48b which is formed to a cylindrical shape along the center axis continuously to the outer peripheral part of the bottom part 48a, The clutch shoe is engaged and separated from the housing 48 through the contact and separation with the inner peripheral surface of the outer edge part 48b of the housing 48. The vibration control plate 50 having the nearly bowl shape is externally fitted with the housing 48. Accordingly, the vibration control effect of the vibration control member can be surely developed, and the abnormal noise generated between the shoe member and the inner peripheral surface of the housing member can be surely suppressed.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、例えば二輪車における
クラッチ装置の多板式と遠心シュー式とのうちの遠心シ
ュー式クラッチ装置、あるいは、摩擦クラッチ装置、ド
ラム式ブレーキ装置等の摩擦係合装置のハウジング制振
構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal shoe clutch device of a multi-disc type and a centrifugal shoe type of a clutch device for a two-wheeled vehicle, or a friction engagement device such as a friction clutch device and a drum brake device. Housing damping structure.

【０００２】[0002]

【従来の技術】スクータ等の自動二輪車には、煩雑なク
ラッチ入り・切りの操作をエンジン回転数にしたがって
自動的に行う遠心シュー式クラッチ装置と変速操作を自
動的に行う自動変速装置とを搭載して、運転者の運転操
作負担を極力減らすようにした種類のものがある。2. Description of the Related Art A motorcycle such as a scooter is equipped with a centrifugal shoe clutch device for automatically performing complicated clutch on / off operations according to the engine speed and an automatic transmission device for automatically performing gear shifting operations. Then, there is a type in which the driver's operation load is reduced as much as possible.

【０００３】図５にこのような種類の自動二輪車におけ
るパワーユニットの動力伝達経路の概要を示す。図のパ
ワーユニットにおいては、まず、エンジン１０のピスト
ン１２の往復運動はクランクシャフト１４の回転運動に
変換される。このクランクシャフト１４の回転運動は、
Ｖベルト式自動変速装置により後輪側に伝達される。つ
まり、このＶベルト式自動変速装置においては、前記回
転運動を、駆動側プーリ１６のドライブフェースからＶ
ベルト１８を介して、被動側プーリ２０のドリブンフェ
ースに伝達され、さらに遠心クラッチ装置を介して後輪
側に伝達する。図６に遠心クラッチ装置のクラッチ・ア
ッシ・シュー２２とクラッチハウジング２６との詳細な
軸長手方向視図を示す。FIG. 5 shows an outline of a power transmission path of a power unit in a motorcycle of this kind. In the illustrated power unit, first, the reciprocating motion of the piston 12 of the engine 10 is converted into the rotary motion of the crankshaft 14. The rotational movement of the crankshaft 14 is
It is transmitted to the rear wheel side by the V-belt type automatic transmission. That is, in this V-belt type automatic transmission, the rotational movement is transmitted from the drive face of the drive side pulley 16 to the V side.
It is transmitted to the driven face of the driven pulley 20 via the belt 18, and further transmitted to the rear wheel side via the centrifugal clutch device. FIG. 6 shows a detailed axial longitudinal view of the clutch assembly shoe 22 and the clutch housing 26 of the centrifugal clutch device.

【０００４】この遠心クラッチ装置では、被動側プーリ
２０に軸回転方向に固定されたクラッチ・アッシ・シュ
ー（クラッチ・アッシ２３とクラッチ・シュー２４の結
合したもの）２２が回転することとなり、このクラッチ
・アッシ・シュー２２の回転運動が高まると、遠心力に
よってクラッチ・シュー２４自身がウェイトとなって拡
張し、クラッチ・シュー２４外周面のライニング２４ａ
が、クラッチハウジング２６の内周面２６ａに接触し、
その直後に接続されることとなる。In this centrifugal clutch device, a clutch assembly shoe (a combination of a clutch assembly 23 and a clutch shoe 24) 22 fixed to the driven pulley 20 in the axial rotation direction rotates, and this clutch When the rotational movement of the assy shoe 22 is increased, the clutch shoe 24 itself expands as a weight due to centrifugal force, and the lining 24a of the outer peripheral surface of the clutch shoe 24 is expanded.
Contact the inner peripheral surface 26a of the clutch housing 26,
It will be connected immediately after that.

【０００５】これにより、クラッチ・アッシュ・シュー
２２の回転力は、クラッチハウジング２６に伝達され、
さらに、このクラッチハウジング２６の回転運動は、ド
ライブ・シャフト２８へと伝達され、減速ギアー機構３
０を介して最終的にリア・アクスルシャフト３２に伝達
され、後輪（図示省略）が回転することとなる。As a result, the rotational force of the clutch ash shoe 22 is transmitted to the clutch housing 26,
Further, the rotational movement of the clutch housing 26 is transmitted to the drive shaft 28, and the reduction gear mechanism 3
Finally, it is transmitted to the rear axle shaft 32 via 0, and the rear wheel (not shown) rotates.

【０００６】前記クラッチハウジング２６は、詳細には
図７に示すように、全体が軸対称の概略椀形状であって
軸から外方向に向けてほぼ円板形状に延設される底部２
６ａおよび該底部２６ａの外周部に連続して軸に沿う円
筒形形状に形成された側縁部２６ｂを有する。また、ク
ラッチ・シュー２４は、前記クラッチハウジング２６の
側縁部２６ｂ内周面に接触・離間して前記クラッチハウ
ジング２６に係合・離脱するものである。このクラッチ
シュー２４のクラッチハウジング２６への係合・離脱に
よりクラッチシュー２４側に入力されたエンジン回転出
力をクラッチハウジング２６側へ伝達・遮断する。な
お、図７において、符号３３は前記ドライブ・シャフト
２８をハウジングに回転方向に固定する嵌合筒である。As shown in detail in FIG. 7, the clutch housing 26 has a substantially bowl-shaped structure which is entirely axisymmetric, and the bottom portion 2 which extends from the shaft outward in a substantially disc shape.
6a and an outer peripheral portion of the bottom portion 26a, and a side edge portion 26b which is formed in a cylindrical shape along the axis and is continuous. Further, the clutch shoe 24 contacts and separates from the inner peripheral surface of the side edge portion 26b of the clutch housing 26 and engages and disengages from the clutch housing 26. By engaging and disengaging the clutch shoe 24 with the clutch housing 26, the engine rotation output input to the clutch shoe 24 side is transmitted to and cut off from the clutch housing 26 side. In FIG. 7, reference numeral 33 is a fitting cylinder for fixing the drive shaft 28 to the housing in the rotational direction.

【０００７】前記図６において、クラッチ・シュー２４
は停止状態として示されているが、クラッチ・アッシ２
３が回転すると、遠心力によってクラッチ・シュー２４
自身がウェイトとなり拡張とすることとなる。クラッチ
・アッシ・シュー２２が回転し、クラッチ・シュー２４
が拡張し、クラッチハウジング２６の内周面に接触する
際に、時として、クラッチ・シュー２４がクラッチハウ
ジング２６内周面に断続的に接触することが起きること
がある。すなわち、伝達トルクの振動が、“クラッチハ
ウジングの鳴き”という異音を発生させ、二輪車に乗る
ドライバーに対して、不快音を感ぜしめることとなる。In FIG. 6, the clutch shoe 24 is shown.
Is shown in a stopped condition, but clutch assembly 2
When the 3 rotates, the clutch shoe 24 is centrifugally driven.
It becomes a weight and becomes an extension. Clutch assembly shoe 22 rotates and clutch shoe 24
When the clutch expands and contacts the inner peripheral surface of the clutch housing 26, the clutch shoe 24 sometimes comes into intermittent contact with the inner peripheral surface of the clutch housing 26. That is, the vibration of the transmission torque causes an abnormal noise of “squeaking of the clutch housing”, which causes the driver of the two-wheeled vehicle to feel uncomfortable.

【０００８】通常、クラッチ・ハウジング２６は前記図
７の如く、単体では、概略椀形形状の構造を有してい
る。クラッチ・ハウジング２６から異音が発生すること
は、クラッチ・ハウジング２６の内周面の形状・面粗度
あるいはクラッチ・シュー２４の外面に固定されたライ
ニング２４ａの形状・面粗度、もしくは材質等が大きな
要因となっている。Normally, the clutch housing 26, as shown in FIG. 7, has a substantially bowl-shaped structure as a single unit. The abnormal noise is generated from the clutch housing 26 because the shape and surface roughness of the inner peripheral surface of the clutch housing 26, the shape and surface roughness of the lining 24a fixed to the outer surface of the clutch shoe 24, the material, etc. Is a major factor.

【０００９】ここで、図８に示すような、音楽にて使用
されるトライアングル３４を例として考えてみる。トラ
イアングル３４を打棒３６により打つと、トライアング
ル３４は振動し、“チィーン”と振動音が発せられて周
囲に響きわたることとなる。そして、この振動している
トライアングル３４に打棒３６を触れると、トライアン
グル３４の振動音は消失し、音は発せられなくなる。Now, let us consider an example of a triangle 34 used in music as shown in FIG. When the triangle 34 is hit with the striking rod 36, the triangle 34 vibrates, and a vibration sound such as "chain" is emitted and resonates around. When the striking rod 36 touches the vibrating triangle 34, the vibration sound of the triangle 34 disappears and no sound is emitted.

【００１０】図９と図１０とは、クラッチシュー２４と
クラッチハウジング２６内周面との間で、種々の要因に
より発生する“クラッチハウジングの鳴き”を抑制する
各構造例である（例えば実開昭６３−１９３１３１号参
照）。その原理は、図８に示した原理を採用して制振し
ようとするものである。図９の構造（第１の従来構造と
いう）では、制振板３８は、クラッチハウジング２６よ
り薄い板材で形成されたほぼ椀形形状であって、当該椀
形形状の底部の中央が削除された構造部の板材（ここで
は、この板材を制振板と称することとする）３８を作製
し、この制振板３８をクラッチハウジング２６の外周側
に軽い圧力で圧入し、かつ、クラッチハウジング２６の
底部２６ａにおいて、この制振板３８の底部３８ａを例
えばスポット溶接により固着する。この制振構造は全体
的には、図１１に示されるようになる。また、図１０の
構造（第２の従来構造という）では、クラッチハウジン
グ２６の開放端（縁部２６ａ）の近くに、帯板材をリン
グ状に形成した制振板４０を圧入するものである。FIGS. 9 and 10 show structural examples of suppressing "squeaking of the clutch housing" caused by various factors between the clutch shoe 24 and the inner peripheral surface of the clutch housing 26 (for example, actual opening). (See Sho 63-193131). The principle is to adopt the principle shown in FIG. 8 to suppress vibration. In the structure shown in FIG. 9 (referred to as the first conventional structure), the damping plate 38 has a substantially bowl shape formed of a plate material thinner than the clutch housing 26, and the center of the bottom of the bowl shape is deleted. A plate member (herein, referred to as a damping plate) 38 of the structural portion is produced, and this damping plate 38 is press-fitted into the outer peripheral side of the clutch housing 26 with a light pressure, and the clutch housing 26 At the bottom portion 26a, the bottom portion 38a of the vibration damping plate 38 is fixed by spot welding, for example. This damping structure is as shown in FIG. 11 as a whole. Further, in the structure of FIG. 10 (referred to as a second conventional structure), a damping plate 40, which is a ring-shaped band plate material, is press-fitted near the open end (edge portion 26a) of the clutch housing 26.

【００１１】ここで、前記制振板３８、４０のクラッチ
ハウジング２６への取付方法を考えてみる。前記第１の
構造では、クラッチハウジング２６の底部２６ａと制振
板３８の底部３８ａとのみが固定されるときにおいて、
制振板３８の縁部３８ｂは、前記打棒３６の如き機能を
示すことができる。また、第２の構造では、クラッチハ
ウジング２６の側縁部２６ｂの後方（底部２６ａ側）の
部分と制振板４０の後方部４０ａとのみが固定されると
きにおいて、制振板４０の縁部４０ｂが前記打棒３６の
ような機能を示すことになる。Now, let us consider a method of mounting the damping plates 38, 40 on the clutch housing 26. In the first structure, when only the bottom portion 26a of the clutch housing 26 and the bottom portion 38a of the vibration damping plate 38 are fixed,
The edge portion 38b of the vibration damping plate 38 can exhibit the same function as the striking rod 36. In the second structure, when only the rear (bottom 26a side) portion of the side edge portion 26b of the clutch housing 26 and the rear portion 40a of the vibration damping plate 40 are fixed, the edge portion of the vibration damping plate 40 is fixed. 40b will have the same function as the striking rod 36.

【００１２】つまり、クラッチシュー２４とクラッチハ
ウジング２６内周面との間で発生した異音を消失させる
ためには、クラッチハウジング２６と制振板３８、４０
とがあたかも別体として機能し、かつ、圧入代を、ゼロ
に近似する値にする必要がある。ゼロに近似する圧入代
とは、クラッチハウジング２６と制振板３８、４０とが
接触するかしないかの状態、言い換えれば、時には接触
し、時には互いに離れ合うという状態であり、圧入代が
ゼロに近似されるときは、前記トライアングル３４の如
き振動するクラッチハウジング２６の椀形形状外周面に
対して、振動音を停止させる打棒３６の如く、制振板３
８、４０の縁部３８ｂ、４０ｂは、クラッチハウジング
２６の縁部２６ｂに触れることとなる。That is, in order to eliminate the abnormal noise generated between the clutch shoe 24 and the inner peripheral surface of the clutch housing 26, the clutch housing 26 and the damping plates 38, 40 are removed.
It is necessary that and function as separate bodies, and the press-fitting margin is set to a value close to zero. The press-fitting margin that approximates to zero is a state in which the clutch housing 26 and the damping plates 38 and 40 are in contact with each other, in other words, they are in contact with each other and sometimes separated from each other, and the press-fitting margin is zero. When approximated, the damping plate 3 such as the striking rod 36 for stopping the vibration sound is applied to the bowl-shaped outer peripheral surface of the vibrating clutch housing 26 such as the triangle 34.
The edges 38b and 40b of the wheels 8 and 40 come into contact with the edge 26b of the clutch housing 26.

【００１３】[0013]

【発明が解決しようとする課題】しかしながら、前記従
来の制振構造では、次のような問題点がある。すなわ
ち、前記図９の制振構造においては、一般に制振板３８
とクラッチハウジング２６とは、共にプレス絞り加工に
より加工製造されるが、同様の形状のため、同じ方向に
抜き勾配が付く。したがって、クラッチハウジング２６
側縁部２６ｂにおいての軸方向の幅全体に亙って、圧入
力が軽くなり、振動振幅の大きい側縁部２６ｂの開放端
近くの圧入状態をコントロールすることができない。こ
の場合に、クラッチハウジング２６への圧入代が大きす
ぎると図１２の（ａ）に示すように、制振板３８の底部
３８ａ付近は密着するが側縁部３８ｂの先端部が開いて
しまい、また、圧入代がルーズであると図１２の（ｂ）
に示すように、前記側縁部３８ｂが全体的に開いてしま
い、いずれのときも制振効果がなくなる。したがって、
圧入状態のコントロールができないという制振効果にば
らつきが生じるという問題点がある。However, the conventional vibration damping structure has the following problems. That is, in the damping structure of FIG. 9, the damping plate 38 is generally used.
The clutch housing 26 and the clutch housing 26 are both manufactured by press drawing, but since they have the same shape, they have a draft in the same direction. Therefore, the clutch housing 26
The pressure input is reduced over the entire axial width of the side edge portion 26b, and it is not possible to control the press-fitting state near the open end of the side edge portion 26b having a large vibration amplitude. In this case, if the press-fitting margin into the clutch housing 26 is too large, as shown in FIG. 12 (a), the vicinity of the bottom portion 38a of the vibration damping plate 38 adheres, but the tip of the side edge portion 38b opens. Also, if the press-fitting margin is loose, (b) of FIG.
As shown in FIG. 5, the side edge portion 38b is opened as a whole, and the damping effect is lost in any case. Therefore,
There is a problem in that the damping effect varies because the press-fitted state cannot be controlled.

【００１４】また、図１０の制振構造においては、制振
板４０を固定するためには強く圧入するすなわち圧入代
を大きく取る必要があるが、そのように固定すると制振
板４０はクラッチハウジング２６と一体化してしまい制
振効果がなくなる。Further, in the damping structure of FIG. 10, in order to fix the damping plate 40, it is necessary to press it firmly, that is, to take a large press-fitting margin. Since it is integrated with 26, the damping effect is lost.

【００１５】なお、ハウジング部材およびシュー部材の
接触・離脱で異音が生じる恐れがあるのは、前記の遠心
クラッチ装置の他にブレーキ装置や他の種のクラッチ装
置などの摩擦係合装置で起きることである。It is to be noted that there is a possibility that abnormal noise may occur due to contact / disengagement of the housing member and the shoe member with a friction engagement device such as a brake device or another type of clutch device other than the centrifugal clutch device. That is.

【００１６】本発明は、前記従来の問題点を解消するべ
くなされたものであって、制振部材の制振効果が確実に
発揮できるようにして、シュー部材とハウジング部材内
周面との間で発生した異音を確実に消失させることがで
きる摩擦係合装置のハウジング制振構造を提供すること
を課題とする。The present invention has been made to solve the above-mentioned conventional problems, and ensures that the vibration damping effect of the vibration damping member can be exerted so that the space between the shoe member and the inner peripheral surface of the housing member is increased. An object of the present invention is to provide a housing damping structure for a friction engagement device that can surely eliminate the abnormal noise generated in 1.

【００１７】[0017]

【課題を解決するための手段】請求項１の発明では、前
記課題を解決するべく、全体が概略椀形形状であって中
心軸から外方向に向けて延設される底部および該底部の
外周部に連続して中心軸に沿う円筒形形状に形成された
側縁部を有するハウジング部材と、このハウジング部材
の側縁部内周面に接触・離間して前記ハウジング部材に
係合・離脱するシュー部材と、前記ハウジング部材に外
嵌された環状の制振部材からなる摩擦係合装置のハウジ
ング制振構造において、前記ハウジング部材の側縁部外
周面には平坦な面と当該平坦面に続く凹部が形成されて
おり、前記制振部材は前記平坦面と凹部との境界を含ん
で前記平坦面に接していることを特徴とする摩擦係合装
置のハウジング制振構造の構成を有する。請求項１の発
明において、側縁部外周面の平坦面を、ハウジング部材
開放端部に設けると共に、前記外周面の凹部を、ハウジ
ング部材底部から開放端部近傍に亙る部分を前記開放端
部の外周面よりも小径に形成したものとし得る。According to a first aspect of the invention, in order to solve the above-mentioned problems, a bottom part having a substantially bowl shape as a whole and extending outward from a central axis and an outer periphery of the bottom part are provided. Housing member having a side edge portion formed in a cylindrical shape continuous with the central axis along the central axis, and a shoe that engages / disengages with the housing member by contacting / separating from the inner peripheral surface of the side edge portion of the housing member. In a housing damping structure of a friction engagement device comprising a member and an annular damping member externally fitted to the housing member, a flat surface is provided on an outer peripheral surface of a side edge portion of the housing member, and a concave portion continuing to the flat surface. Is formed, and the damping member is in contact with the flat surface including the boundary between the flat surface and the concave portion, and has a structure of the housing damping structure of the friction engagement device. In the invention of claim 1, the flat surface of the outer peripheral surface of the side edge portion is provided at the open end of the housing member, and the concave portion of the outer peripheral surface is a portion extending from the bottom of the housing member to the vicinity of the open end of the open end. The diameter may be smaller than that of the outer peripheral surface.

【００１８】[0018]

【作用】本発明によれば、ハウジング部材の外周面には
平坦面と凹部とを形成し、制振部材を平坦面と凹部との
境界を含んで前記平坦面に接しさせるので、たとえ、制
振部材の圧入代が大きいものとしても、前記制振部材
は、前記境界で確実にハウジング部材の外周面に緩やか
に接して、圧入代がゼロに近似されるため、当該緩やか
に接する部分でハウジング部材を制振する。According to the present invention, a flat surface and a recess are formed on the outer peripheral surface of the housing member, and the damping member is brought into contact with the flat surface including the boundary between the flat surface and the recess. Even if the press-fitting margin of the vibration member is large, the vibration-damping member surely makes a gentle contact with the outer peripheral surface of the housing member at the boundary, and the press-fitting margin is approximate to zero. Damping parts.

【００１９】[0019]

【実施例】以下、図面を参照して本発明の実施例を詳細
に説明する。なお、前記図５〜図１２と同様に部分に
は、同一の番号を付してその説明を略する。図１は本発
明の実施例に係る自動二輪車のクラッチ装置の制振構造
の全体断面説明図、図２〜図４は図１の部分詳細図であ
る。Embodiments of the present invention will be described below in detail with reference to the drawings. The same parts as those in FIGS. 5 to 12 are designated by the same reference numerals and the description thereof is omitted. 1 is an overall cross-sectional explanatory view of a vibration damping structure of a clutch device for a motorcycle according to an embodiment of the present invention, and FIGS. 2 to 4 are partial detailed views of FIG.

【００２０】この実施例は、前記図５に示したものと同
様の自動二輪車用のパワーユニットに搭載されるクラッ
チ装置に設けられたハウジング制振構造である。前記制
振構造は、全体が概略椀形状であって中心軸から外方向
に向けて延設される底部４８ａおよび該底部４８ａの外
周部に連続して中心軸Ｃに沿う円筒形形状に形成された
側縁部４８ｂを有するハウジング（ハウジング部材に相
当）４８と、このハウジング４８の側縁部４８ｂ内周面
に接触・離間して前記ハウジング４８に係合・離脱する
クラッチシュー２４と、前記ハウジング４８に外嵌され
た概略椀形形状の制振板５０からなる摩擦係合装置に形
成されたものである。This embodiment has a housing damping structure provided in a clutch device mounted on a power unit for a motorcycle similar to that shown in FIG. The vibration damping structure is generally in the shape of a bowl and is formed in a cylindrical shape along the central axis C, which is continuous with the bottom portion 48a extending outward from the central axis and the outer peripheral portion of the bottom portion 48a. A housing (corresponding to a housing member) 48 having a side edge portion 48b, a clutch shoe 24 that comes into contact with and separates from an inner peripheral surface of the side edge portion 48b of the housing 48 and engages with and disengages from the housing 48; It is formed in a friction engagement device composed of a vibration damping plate 50 having a substantially bowl shape externally fitted to 48.

【００２１】さらに、前記ハウジング４８の側縁部４８
ｂ外周面には、該ハウジング開放端部４８ｃの外周面に
幅Ｌ0の平坦面４８ｄが形成され、かつ当該平坦面４８
ｄにテーパー部４９ａを介して続く凹部４９が形成され
ている。前記テーパー部４９ａは、平坦面４８ｄから前
記底部４８ａ側に向かう方向に沿って徐々に絞り込むよ
うに小径になっていくものである。ハウジング４８の側
縁部の外周面形状は、絞りプレス加工の際に同時にある
いは後に旋盤加工を行う等いずれのときにも形成するこ
とができる。また、仕上げ荒さは適宜に選定できる。Further, a side edge portion 48 of the housing 48 is provided.
On the outer peripheral surface of b, a flat surface 48d having a width L 0 is formed on the outer peripheral surface of the housing open end portion 48c, and the flat surface 48d is formed.
A concave portion 49 is formed so as to continue to d via the tapered portion 49a. The taper portion 49a has a small diameter so that the taper portion 49a is gradually narrowed along the direction from the flat surface 48d toward the bottom portion 48a. The outer peripheral surface shape of the side edge portion of the housing 48 can be formed at the same time as the drawing press working or at the time of lathe working later. Further, the finish roughness can be appropriately selected.

【００２２】前記凹部４９は、前記ハウジング底部４８
ａから開放端部４８ｃ近傍に亙る部分を前記開放端部４
８ｃの外周面平坦面４８ｄ（図３では、平坦面４８ｄの
径と同様の位置を一点鎖線で示す）の外径よりも小径の
外径に形成して凹ませたものであって、前記テーパー部
４９ａの底部４８ａ側端縁に角度を持って繋がり、ほぼ
全体的にほぼ同一の外径に形成されている。The recess 49 is the bottom 48 of the housing.
The portion extending from a to the vicinity of the open end 48c is the open end 4
The outer diameter of the flat surface 48c of 8c (in FIG. 3, the same position as the diameter of the flat surface 48d is indicated by a dashed line) is smaller than the outer diameter of the outer surface and is recessed. The portion 49a is connected to the edge of the bottom portion 48a on the side of the bottom portion 48a at an angle, and is formed to have substantially the same outer diameter as a whole.

【００２３】前記制振板５０は、前記図９、図１１に示
した制振板３８と同様の構成を有するものであって、椀
形形状のハウジング４８の外周面にそれを覆うように底
部５０ａと側縁部５０ｂとからなる概略椀形形状の制振
板５０が圧入代を持って外嵌される。前記外嵌において
は、前記平坦面４８ｄと凹部４９との境界であるテーパ
ー部４９ａを含んで前記凹部４９を覆いかつ前記平坦面
４８ｄに接している。The damping plate 50 has the same construction as the damping plate 38 shown in FIGS. 9 and 11, and has a bottom portion so as to cover the outer peripheral surface of the bowl-shaped housing 48. A generally bowl-shaped damping plate 50, which is composed of 50a and a side edge portion 50b, is externally fitted with a press-fitting margin. In the external fitting, the concave portion 49 is included in contact with the flat surface 48d including the tapered portion 49a which is a boundary between the flat surface 48d and the concave portion 49.

【００２４】前記制振板５０は、その底部５０ａ中央部
に円形の貫通孔５０ａ１が形成されている。また、前記
外嵌においては制振板５０は前記側縁部４８ｂの開放端
部４８ｃの形成された幅Ｌ0の平坦面４８ｄの部分に接
しており、それ以外の部分には接しない。The damping plate 50 has a circular through hole 50a1 formed at the center of the bottom portion 50a. Further, in the external fitting, the damping plate 50 is in contact with a portion of the flat surface 48d of the width L 0 where the open end portion 48c of the side edge portion 48b is formed, and does not contact with other portions.

【００２５】また、前記平坦面のハウジング４８の軸方
向の幅Ｌ0は、適宜に長さに設定することができる。例
えば、図４に示すように、前記側縁部４８ｂの長さをＬ
1とすれば、 Ｌ0≦Ｌ1／２ であることが好ましい。このようにすれば、最も制振効
果の大きな開放側端部４８ｃのみに確実に制振板５０を
接しさせることができる。なお、前記制振板５０は、ハ
ウジング４８に底部５０ａ（先端縁部以外の部分に相
当）が溶接により固定されたものである。The axial width L 0 of the flat surface of the housing 48 can be set to a suitable length. For example, as shown in FIG. 4, the length of the side edge portion 48b is L
If 1 and is preferably L 0 ≦ L 1/2. With this configuration, the damping plate 50 can be reliably brought into contact with only the open side end portion 48c having the largest damping effect. The damping plate 50 has a bottom portion 50a (corresponding to a portion other than the leading edge portion) fixed to the housing 48 by welding.

【００２６】実施例の作用を説明する。実施例によれ
ば、ハウジング４８の側縁部４８ｂ外周面には平坦面４
８ｄと凹部４９とを形成し、制振板５０を平坦面４８ｄ
と凹部４９との境界であるテーパー部４９ａを含んで前
記平坦面４８ｄに接しさせるので、たとえ、制振部材５
０の圧入代が大きいものとしても、前記制振部材５０
は、前記テーパー部４９ａで確実にハウジング４８の外
周面に緩やかに接し、圧入代はゼロに近似されるため、
当該緩やかに接する部分でハウジング４８を確実に制振
する。The operation of the embodiment will be described. According to the embodiment, the flat surface 4 is formed on the outer peripheral surface of the side edge portion 48b of the housing 48.
8d and the concave portion 49 are formed, and the damping plate 50 is attached to the flat surface 48d.
Since the flat surface 48d is brought into contact with the taper portion 49a, which is the boundary between the concave portion 49 and the concave portion 49,
Even if the press-fitting margin of 0 is large, the damping member 50
Is surely gently contacted with the outer peripheral surface of the housing 48 at the tapered portion 49a, and the press-fitting margin is approximated to zero.
The housing 48 is reliably damped by the gently contacting portion.

【００２７】また、最も制振効果の大きいのはハウジン
グ４８の開放端部４８ｃ付近を制振板５０で緩やかに接
することである。実施例では、前記開放端部４８ｃ付近
に平坦面４８ｄを形成し、かつこの平坦面４８ｄに続く
テーパー部４９ａに制振板５０で接するため、制振効果
が大きい。The most effective damping effect is that the damping plate 50 gently contacts the vicinity of the open end 48c of the housing 48. In the embodiment, since the flat surface 48d is formed near the open end 48c and the tapered portion 49a following the flat surface 48d is in contact with the damping plate 50, the damping effect is large.

【００２８】なお、本発明は、クラッチ装置のハウジン
グに適用されるものに限定されず、その他のブレーキ装
置やその他のクラッチ装置等の、ハウジング部材の内周
面にシュー部材が接触してそれら同士が係合する種々の
摩擦係合装置に制振構造として適用できる。また、本発
明のハウジングや制振部材に構成は前記実施例により限
定されないことは明らかである。すなわち、ハウジング
に形成する凹部および平坦面の位置および形状は前記実
施例ものに限定されず、例えば、凹部をハウジング側縁
部のほぼ中央部あるいは開放端部近傍に形成することが
できる。また、制振部材は、前記椀形状のものではな
く、前記図１０に示したような、帯板形状とするように
してもよい。The present invention is not limited to the application to the housing of the clutch device, and the shoe member comes into contact with the inner peripheral surface of the housing member, such as other brake devices and other clutch devices, so that the shoe members contact each other. It can be applied as a vibration damping structure to various friction engagement devices that engage with each other. Further, it is obvious that the structure of the housing and the damping member of the present invention is not limited to the above-mentioned embodiment. That is, the positions and shapes of the recess and the flat surface formed in the housing are not limited to those in the above-described embodiment, and the recess can be formed, for example, in the substantially central portion of the side edge of the housing or in the vicinity of the open end. Further, the vibration damping member may have a strip plate shape as shown in FIG. 10 instead of the bowl shape.

【００２９】[0029]

【発明の効果】以上説明した通り、本発明によれば、制
振部材の制振効果が確実に発揮できるようにして、シュ
ー部材とハウジング部材内周面との間で発生した異音を
確実に消失させることができる。As described above, according to the present invention, the vibration damping effect of the vibration damping member can be surely exerted so that the abnormal noise generated between the shoe member and the inner peripheral surface of the housing member can be reliably generated. Can be made to disappear.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の実施例に係るクラッチ装置のクラッチ
ハウジングの断面の構成図である。FIG. 1 is a cross-sectional configuration diagram of a clutch housing of a clutch device according to an embodiment of the present invention.

【図２】図１の部分詳細図である。FIG. 2 is a partial detailed view of FIG.

【図３】図１のハウジングの部分詳細図である。FIG. 3 is a partial detailed view of the housing of FIG.

【図４】図１のハウジングおよび制振板の詳細図であ
る。FIG. 4 is a detailed view of the housing and the vibration damping plate of FIG.

【図５】一般の遠心シュー式のクラッチ装置の搭載され
たエンジンの説明図である。FIG. 5 is an explanatory diagram of an engine equipped with a general centrifugal shoe clutch device.

【図６】一般的な遠心シュー式のクラッチ装置の説明図
である。FIG. 6 is an explanatory diagram of a general centrifugal shoe clutch device.

【図７】図６のクラッチ・ハウジングの断面説明図であ
る。7 is a cross-sectional explanatory view of the clutch housing of FIG.

【図８】クラッチハウジングの振動を説明するためのト
ライアングルの振動音の説明図である。FIG. 8 is an explanatory diagram of a vibration noise of a triangle for explaining the vibration of the clutch housing.

【図９】従来の制振板が外嵌されたクラッチハウジング
一例の断面構成図である。FIG. 9 is a cross-sectional configuration diagram of an example of a clutch housing to which a conventional damping plate is fitted.

【図１０】従来の制振板が外嵌されたクラッチハウジン
グ他の例の断面構成図である。FIG. 10 is a cross-sectional configuration diagram of another example of a clutch housing to which a conventional damping plate is fitted.

【図１１】従来の制振板が外嵌されたクラッチハウジン
グ一例の断面構成図である。FIG. 11 is a cross-sectional configuration diagram of an example of a clutch housing to which a conventional damping plate is fitted.

【図１２】（ａ），（ｂ）はＡ従来の制振板が外嵌され
たクラッチハウジングの問題点の各説明図である。12A and 12B are explanatory views of problems of the clutch housing in which the conventional damping plate A is fitted.

【符号の説明】 ４８ クラッチハウジング ４８ａ クラッチハウジング底部 ４８ｂ クラッチハウジング側縁部 ４８ｃ 平面部 ４９ 凹部 ４９ａ テーパー部 ５０ 制振板 ５０ａ 制振板底部 ５０ｂ 制振板先端縁部[Description of Reference Signs] 48 clutch housing 48a clutch housing bottom portion 48b clutch housing side edge portion 48c flat surface portion 49 concave portion 49a taper portion 50 damping plate 50a damping plate bottom portion 50b damping plate tip edge portion

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】 全体が概略椀形形状であって中心軸から
外方向に向けて延設される底部および該底部の外周部に
連続して中心軸に沿う円筒形形状に形成された側縁部を
有するハウジング部材と、このハウジング部材の側縁部
内周面に接触・離間して前記ハウジング部材に係合・離
脱するシュー部材と、前記ハウジング部材に外嵌された
環状の制振部材からなる摩擦係合装置のハウジング制振
構造において、前記ハウジング部材の側縁部外周面には
平坦な面と当該平坦面に続く凹部が形成されており、前
記制振部材は前記平坦面と凹部との境界を含んで前記平
坦面に接していることを特徴とする摩擦係合装置のハウ
ジング制振構造。1. A bottom part having a substantially bowl shape as a whole and extending outward from a central axis, and a side edge formed in a cylindrical shape continuous with the central axis and continuous with an outer peripheral part of the bottom part. A housing member having a portion, a shoe member that comes into contact with and separates from an inner peripheral surface of a side edge of the housing member to engage and disengage from the housing member, and an annular damping member externally fitted to the housing member. In the housing damping structure of the friction engagement device, a flat surface and a concave portion continuing to the flat surface are formed on the outer peripheral surface of the side edge portion of the housing member, and the damping member has the flat surface and the concave portion. A housing damping structure for a friction engagement device, wherein the housing damping structure is in contact with the flat surface including a boundary.
JP20170194A 1994-08-26 1994-08-26 Housing vibration control structure of friction engagement device Expired - Fee Related JP3322014B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP20170194A JP3322014B2 (en) 1994-08-26 1994-08-26 Housing vibration control structure of friction engagement device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP20170194A JP3322014B2 (en) 1994-08-26 1994-08-26 Housing vibration control structure of friction engagement device

Publications (2)

Publication Number Publication Date
JPH0861383A true JPH0861383A (en) 1996-03-08
JP3322014B2 JP3322014B2 (en) 2002-09-09

Family

ID=16445492

Family Applications (1)

Application Number Title Priority Date Filing Date
JP20170194A Expired - Fee Related JP3322014B2 (en) 1994-08-26 1994-08-26 Housing vibration control structure of friction engagement device

Country Status (1)

Country Link
JP (1) JP3322014B2 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1564428A1 (en) * 2004-02-17 2005-08-17 HONDA MOTOR CO., Ltd. Centrifugal clutch
JP2011509377A (en) * 2007-12-21 2011-03-24 フスクバルナ アクティエボラーグ Centrifugal clutch compact and lightweight clutch drum
JP2016151279A (en) * 2015-02-16 2016-08-22 株式会社エクセディ Centrifugal clutch, and housing cover
EP3916260A1 (en) * 2020-05-29 2021-12-01 Yamaha Hatsudoki Kabushiki Kaisha Centrifugal clutch, and a straddled vehicle having the centrifugal clutch

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1564428A1 (en) * 2004-02-17 2005-08-17 HONDA MOTOR CO., Ltd. Centrifugal clutch
US7234581B2 (en) 2004-02-17 2007-06-26 Honda Motor Co., Ltd. Centrifugal clutch, and method of making same
CN1325816C (en) * 2004-02-17 2007-07-11 本田技研工业株式会社 Centrifugal clutch
JP2011509377A (en) * 2007-12-21 2011-03-24 フスクバルナ アクティエボラーグ Centrifugal clutch compact and lightweight clutch drum
JP2016151279A (en) * 2015-02-16 2016-08-22 株式会社エクセディ Centrifugal clutch, and housing cover
WO2016132636A1 (en) * 2015-02-16 2016-08-25 株式会社エクセディ Centrifugal clutch and housing cover
EP3916260A1 (en) * 2020-05-29 2021-12-01 Yamaha Hatsudoki Kabushiki Kaisha Centrifugal clutch, and a straddled vehicle having the centrifugal clutch
TWI783470B (en) * 2020-05-29 2022-11-11 日商山葉發動機股份有限公司 Centrifugal clutch, its manufacturing method, and a straddled vehicle having the centrifugal clutch

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Publication number Publication date
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