JPS5833313Y2 - Uzumakibanenokadotanmatsushijisouchi - Google Patents

Description

【考案の詳細な説明】 本考案は、捩り蓄力を以て負荷を駆動するようにした動
力用渦巻ばねの可動端末支持装置に関するものである。[Detailed Description of the Invention] The present invention relates to a movable terminal support device for a power spiral spring that drives a load using torsionally accumulated force.

か＼る渦巻ばねは外端末を固定機枠に、自端末を負荷に
連なる巻込み軸にそれぞれ係止されるが、従来のもので
は渦巻ばねの捩り蓄力の放出時、その強大な捩り蓄力が
該ばね可動端末即ち自端末の巻込み軸係止部に集中的に
作用しっぺ巻込み軸を回転１駆動するので、該ばね自端
末に内部応力が集中しそれを疲労、損傷させる惧れがあ
り、さらに前記捩り蓄力の放出終了時において、巻込み
軸の慣性回転力により、渦巻ばね自端末が反転して折損
したり巻込み軸から離脱したりする惧れがあった。Such a spiral spring has its outer terminal fixed to the fixed machine frame and its own terminal fixed to the winding shaft connected to the load, but in the conventional type, when the torsional accumulated force of the spiral spring is released, the strong torsional accumulated force is released. Since the force acts intensively on the movable end of the spring, that is, the winding shaft locking portion of the own end, and drives the winding shaft one rotation, there is a risk that internal stress will concentrate on the spring's own end, causing fatigue and damage to it. Furthermore, when the torsional accumulated force is released, there is a risk that the end of the spiral spring may reverse and break or separate from the winding shaft due to the inertial rotational force of the winding shaft.

本考案は、上記のような惧４゛、を解消した構造簡単な
前記装置を得ることを目１闇とするものである。The object of the present invention is to provide a device with a simple structure that eliminates the above-mentioned concerns.

以下、図面により本考案の一実施例について説明すると
、１は自動二輪車の、・ンジン始動用渦巻ばねで、エン
ジン２に連なるｆｉ動ケーヌ４Ｑ・内壁にクランク軸３
の端部に対向して形成した／・、ウジング５に収容され
る。Hereinafter, one embodiment of the present invention will be described with reference to the drawings. 1 is a spiral spring for starting an engine of a motorcycle, and a crankshaft 3 is attached to the inner wall of a fi dynamic canine 4Q connected to an engine 2.
is housed in the housing 5 formed opposite to the end of the housing.

ハウジング５には、１１周壁に突起６が、また内側壁に
り′）ンク軸３とシ・；軸線上に並ぶ支軸７が一体に形
成されており、突起６には渦巻ばね１のフック状の外端
末１ａを係止し、支軸７に巻込み軸たる始動軸８を回転
自在に支承し、その始動軸８の一側の凹溝９に、渦巻（
７：ね１の自端末を内側に折曲して形成した鉤部１ｂを
係合する。The housing 5 is integrally formed with a protrusion 6 on the circumferential wall and a support shaft 7 on the inner wall that is aligned with the link shaft 3. The protrusion 6 has a hook for the spiral spring 1. A starting shaft 8, which is a winding shaft, is rotatably supported on a support shaft 7, and a concave groove 9 on one side of the starting shaft 8 has a spiral (
7: Engage the hook portion 1b formed by bending the end of the screw 1 inward.

渦巻ばね１は、その内周部の−巻き以上図示例では二巻
きを、それ自身の収縮力にまり前Ｓ口鈎部１ｂをその外
側より始動軸８に緊縛する弾性収縮部１Ｂに形成し、そ
の他の部分には従来同様に拡張方向の張りを付与する。The spiral spring 1 has one or more turns (in the illustrated example, two turns) of its inner peripheral portion formed into an elastic contracting portion 1B that is held by its own contractile force and tightens the front S mouth hook portion 1b to the starting shaft 8 from the outside. , and other parts are given tension in the direction of expansion as in the conventional case.

始動軸８はスプロケット１０、チェイン１１等を用いた
始動伝動機構１２を介して伝動ケース４に軸支した始動
ペダル１３に連結される。The starting shaft 8 is connected to a starting pedal 13 pivotally supported on the transmission case 4 via a starting transmission mechanism 12 using a sprocket 10, a chain 11, etc.

而して始動伝動機構１２は、始動ペダル１３に与える数
回の踏込力を以て渦巻ばね１を充分巻込むように始動軸
８を一方向に回転でき、かつ適時始動軸８を釈放できる
ようになっている。Thus, the starting transmission mechanism 12 can rotate the starting shaft 8 in one direction so as to sufficiently wind up the spiral spring 1 with the force applied to the starting pedal 13 several times, and can also release the starting shaft 8 at the appropriate time. ing.

また始動軸８はクランク軸３にオーバーランニングクラ
ッチ１４を介して連結され、そのオ バーランニングク
ラッチ１４は従来普通のように、クラッチ軸３が始動軸
８より速く回転したとき、その間の伝動を遮断するよう
になっている。Further, the starting shaft 8 is connected to the crankshaft 3 via an overrunning clutch 14, and when the clutch shaft 3 rotates faster than the starting shaft 8, the overrunning clutch 14 interrupts the transmission between them as usual. It is supposed to be done.

上記のような横取であるから、渦巻ばね１を充分巻込ん
だ始動軸８を釈放すると、渦巻ばね１の捩り蓄力が一挙
に放出され、始動軸８がその強力な捩りトルクを受けて
オーバーランニングクラッチ１４を介してクランク軸３
を回転、駆動し、エンジン２を始動することができる。Because of the above-mentioned usurpation, when the starting shaft 8 that has fully wound the spiral spring 1 is released, the torsional force of the spiral spring 1 is released all at once, and the starting shaft 8 receives the strong torsional torque. Crankshaft 3 via overrunning clutch 14
can be rotated and driven, and the engine 2 can be started.

その際渦巻ばね１の強大な捩り蓄力は、該ばね鉤部１ｂ
を外側より緊縛する弾性収縮部１Ｂを介して始動軸８に
伝達されるので、該ばね１の内部応力を、その弾性収縮
部１Ｂに沿って広く分散させることができ、鉤部１ｂへ
の応力集中はない。At this time, the strong torsional force of the spiral spring 1 is applied to the spring hook portion 1b.
The internal stress of the spring 1 can be widely dispersed along the elastic contraction part 1B, reducing the stress on the hook part 1b. There is no concentration.

また渦巻ばね１の蓄力放出完了時においては、始動軸８
の慣性回転力が渦巻ばね１に反転力として作用するが、
前記弾性収縮部１Ｂの収縮応力が上記反転力を効果的に
吸収するため、始動軸８の慣性回転は緩衝的かつ静粛に
減速停止し、しかも該ばね鉤部１ｂには上記反転力が伺
等加わらずその折損、および始動軸８の凹溝９からの離
脱が防止される。Furthermore, when the discharge of the stored force of the spiral spring 1 is completed, the starting shaft 8
The inertial rotational force of acts on the spiral spring 1 as a reversing force,
Since the contraction stress of the elastic contracting portion 1B effectively absorbs the reversing force, the inertial rotation of the starting shaft 8 decelerates and stops quietly and bufferingly, and the reversing force is not applied to the spring hook portion 1b. This prevents the starting shaft 8 from being damaged and breaking, and from coming off the starting shaft 8 from the groove 9.

以上のように本考案によれば、渦巻ばね１の内端末を内
側に折曲して鉤部１ｂに形成し、それを巻込み軸の一側
面に設けた凹溝９に係合し、さらに該ばねの内周部に、
前記鉤部１ｂをその外側より巻込み軸に緊縛する弾性収
縮部１Ｂを形成したので、渦巻ばね１の捩り蓄力放出時
において、その強大な捩り蓄力は上記弾性収縮部１Ｂを
介して巻込み軸に伝達され、該弾性収縮部１Ｂに内部応
力を広く分散させて、該ばね１内端末の鉤部１ｂへの集
中応力の発生を回避することができ、その耐久性を著し
く高めることができる。As described above, according to the present invention, the inner end of the spiral spring 1 is bent inward to form the hook portion 1b, which is engaged with the groove 9 provided on one side of the winding shaft. On the inner circumference of the spring,
Since the elastic contraction part 1B is formed to tighten the hook part 1b to the winding shaft from the outside, when the torsional accumulated force of the spiral spring 1 is released, the strong torsional accumulated force is unwound through the elastic contraction part 1B. It is possible to widely disperse the internal stress in the elastic contracting portion 1B, thereby avoiding the occurrence of concentrated stress on the hook portion 1b at the end of the spring 1, and significantly increasing its durability. can.

また渦巻ばね１の捩り蓄力放出完了時においては、該ば
ね１に反転力として強力に作用する巻込み軸の慣性回転
力を、上記弾性収縮部１Ｂにより効果的に吸収すること
ができ、従って巻込み軸の慣性回転を緩衝的かつ静粛に
減速停止させることができると共に、該ばね鉤部１ｂへ
の上記反転力の伝達を抑止してその折損、および巻込み
細凹溝９からの離脱を防止することができる。Furthermore, when the torsional force accumulation of the spiral spring 1 is completed, the inertial rotational force of the winding shaft that strongly acts on the spring 1 as a reversing force can be effectively absorbed by the elastic contracting portion 1B. The inertial rotation of the winding shaft can be decelerated and stopped in a buffering manner and quietly, and the transmission of the reversing force to the spring hook portion 1b can be suppressed to prevent breakage and separation from the winding groove 9. It can be prevented.

さらに前記渦巻ばね１内端末の鉤部１ｂは、巻込み軸に
常時強固に緊縛固定され、線巻込み軸との間に遊びやガ
タがないので、渦巻ばね１の巻込みに際して巻込み軸の
回転をはね巻込みに無駄なく利用してその巻込み操作を
能率よく行なうことができると共に、振動等に起因した
、鉤部１ｂの巻込み細凹溝９からの離脱故障を皆無とす
ることができ、しかもまた巻込み軸には、鉤部１ｂに対
して単に凹溝９を形成すれば足り、特別な固定部材を設
ける必要がないので、その構造を簡単化して生産コスト
を低減することができ、また巻込み軸自体の強度を弱め
ることもない。Furthermore, the hook portion 1b at the end of the spiral spring 1 is always firmly tied and fixed to the winding shaft, and there is no play or backlash between the wire winding shaft and the winding shaft when winding the spiral spring 1. To efficiently perform the winding operation by utilizing rotation without waste in winding, and to eliminate failures in detachment of the hook part 1b from the narrow winding groove 9 due to vibrations, etc. In addition, it is sufficient to simply form a concave groove 9 in the hook portion 1b on the winding shaft, and there is no need to provide a special fixing member, which simplifies the structure and reduces production costs. It also does not weaken the strength of the winding shaft itself.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本考案をエンジン始動用渦巻ばねに実施した自
動二輪車のパワーユニットの要部縦断平面図、第２図は
そのＡ−Ａ線拡大断面図である。 １・・・・・・渦巻ばね、１ａ・・・・・・外端末、１
ｂ・・・・・・鉤部、１Ｂ・・・・・・弾性収縮部、４
・・・・・・固定機枠としての伝動ケース、８・・・・
・・巻込み軸としての始動軸、９・・・・・・凹溝。FIG. 1 is a longitudinal sectional plan view of a main part of a power unit for a motorcycle in which the present invention is applied to an engine starting spiral spring, and FIG. 2 is an enlarged sectional view taken along the line A--A. 1...Spiral spring, 1a...Outer terminal, 1
b...Hook part, 1B...Elastic contraction part, 4
...Transmission case as fixed machine frame, 8...
...Starting shaft as a winding shaft, 9...concave groove.

Claims (1)

【実用新案登録請求の範囲】[Scope of utility model registration request] 外端末１ａを固定機枠に、自端末を巻込み軸にそれぞれ
係止し、捩り蓄力の放出により前記巻込み軸を回転１駆
動するようにした渦巻ばね１において、該ばねの自端末
を内側に折曲し７て鉤部１ｂに形成し、この鉤部１ｂを
前記巻込み軸の一側面に設けた凹溝９に係合し、さらに
該ばねの内周部に、前記鉤部１ｂをその外側より前記巻
込み軸に緊縛する弾性収縮部１Ｂを形成してなる、渦巻
ばねの可動端末支持装置。In a spiral spring 1, the outer terminal 1a is fixed to a fixed frame and the own terminal is fixed to a winding shaft, and the winding shaft is driven one rotation by releasing the torsional accumulated force. The hook portion 1b is bent inward 7 to form a hook portion 1b, and the hook portion 1b is engaged with a groove 9 provided on one side of the winding shaft. A movable terminal support device for a spiral spring, which is formed with an elastic contracting portion 1B that is tightly bound to the winding shaft from the outside.