JPS6256348B2 - - Google Patents
Info
- Publication number
- JPS6256348B2 JPS6256348B2 JP13269280A JP13269280A JPS6256348B2 JP S6256348 B2 JPS6256348 B2 JP S6256348B2 JP 13269280 A JP13269280 A JP 13269280A JP 13269280 A JP13269280 A JP 13269280A JP S6256348 B2 JPS6256348 B2 JP S6256348B2
- Authority
- JP
- Japan
- Prior art keywords
- pinion gear
- pinion
- shaft
- movable cylinder
- combustion engine
- 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.)
- Expired
Links
- 238000002485 combustion reaction Methods 0.000 claims description 33
- 230000005540 biological transmission Effects 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 description 5
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000010273 cold forging Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 239000007858 starting material Substances 0.000 description 1
Landscapes
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Description
【発明の詳細な説明】
本発明は内燃機関のリングギヤからピニオンギ
ヤが早期に離脱するのを防止する機構を備えた慣
性摺動式の内燃機関の始動装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an inertial sliding type internal combustion engine starting device that is equipped with a mechanism that prevents a pinion gear from prematurely disengaging from a ring gear of an internal combustion engine.
ベンデイツクス式と称される慣性摺動式の内燃
機関の始動装置は一般的に、電動機部の出力軸で
回転せしめられるピニオン軸に移動筒部材を慣性
摺動自在にヘリカルスプライン嵌合し、この移動
筒部材に一方向クラツチを介してピニオンギヤを
連結して構成され、出力軸によるピニオン軸の急
速回転で移動筒部材が慣性摺動するとピニオンギ
ヤが内燃機関のリングギヤに飛び込んでこれと噛
合し、ピニオン軸と一体に移動筒部材、一方向ク
ラツチを介して回転し始めるピニオンギヤにより
リングギヤが回転せしめられ、内燃機関が始動す
る。内燃機関始動後は高速回転し始めたリングギ
ヤから逆にピニオンギヤが動力を伝達されるよう
になり、高速回転するこのピニオンギヤとピニオ
ン軸との回転数差及びリターンスプリングの作用
によりピニオンギヤはリングギヤから離脱し、ピ
ニオン軸上を戻る。 The inertial sliding type internal combustion engine starting device, called the Bendix type, generally has a movable cylinder member fitted with a helical spline to allow inertial sliding on a pinion shaft rotated by the output shaft of the electric motor. A pinion gear is connected to a cylindrical member via a one-way clutch, and when the movable cylindrical member slides inertia due to the rapid rotation of the pinion shaft by the output shaft, the pinion gear jumps into the ring gear of the internal combustion engine and meshes with it, and the pinion shaft The ring gear is rotated by the pinion gear, which starts rotating integrally with the movable cylinder member and the one-way clutch, and the internal combustion engine is started. After the internal combustion engine is started, power is transmitted from the ring gear, which begins to rotate at high speed, to the pinion gear, and due to the difference in rotational speed between the high-speed rotation of the pinion gear and the pinion shaft, and the action of the return spring, the pinion gear separates from the ring gear. , return on the pinion axis.
ところで内燃機関、特に単気筒内燃機関や２サ
イクル内燃機関は始動後直ちに回転するものでは
なく、回転数、トルクが波状に変動する。このよ
うに回転数、トルクが変動する一瞬に内燃機関回
転数がリングギヤからピニオンギヤが離脱する高
回転数に達すると、内燃機関が所望の回転状態と
なつていないのにもかかわらず、ピニオンギヤは
リングギヤから早期に離脱してしまう。 Incidentally, an internal combustion engine, particularly a single-cylinder internal combustion engine or a two-stroke internal combustion engine, does not rotate immediately after starting, but its rotational speed and torque fluctuate in a wave-like manner. If the internal combustion engine speed reaches a high speed at which the pinion gear separates from the ring gear in an instant when the rotation speed and torque fluctuate in this way, the pinion gear will shift from the ring gear even though the internal combustion engine is not in the desired rotational state. will leave early.
本発明は以上の如き従来の問題点に鑑み、これ
を有効に解決するために成されたものである。 The present invention has been made in view of the above-mentioned conventional problems and to effectively solve them.
本発明の目的は、内燃機関が所望回転に達する
までピニオンギヤ及び移動筒部材をピニオン軸に
係止状態とし、以つてリングギヤからのピニオン
ギヤの早期離脱を防止できるようにした始動装置
を提供する処にあり、特に本発明の目的は、ピニ
オン軸に対してピニオンギヤ、移動筒部材を係止
状態とする係止部材を前記一方向クラツチを境に
してリングギヤ側のピニオンギヤと一体化された
部材に設けるようにし、該部材に係止部材を軸径
方向に揺動自在に枢着し、ピニオンギヤの高速回
転により係止部材を遠心力で軸外径方向へ揺動さ
せることによりピニオン軸に対するピニオンギ
ヤ、移動筒部材の係止状態を解除し、このように
内燃機関のリングギヤと接続されるピニオンギヤ
と一体の部材に係止部材を設けることにより、内
燃機関の回転数が増す程係止部材の上記遠心力が
大きくなつて係止解除作動の確実化を期待できる
ようにした内燃機関の始動装置を提供する処にあ
る。 SUMMARY OF THE INVENTION An object of the present invention is to provide a starter device that locks a pinion gear and a movable cylinder member to a pinion shaft until an internal combustion engine reaches a desired rotation, thereby preventing the pinion gear from prematurely disengaging from the ring gear. In particular, it is an object of the present invention to provide a locking member that locks the pinion gear and the movable cylinder member to the pinion shaft on a member integrated with the pinion gear on the ring gear side with the one-way clutch as the boundary. The locking member is pivotally attached to the member so as to be able to swing freely in the shaft radial direction, and the locking member is rocked in the shaft outer diameter direction by centrifugal force due to high-speed rotation of the pinion gear. By releasing the locked state of the member and providing the locking member in a member integrated with the pinion gear connected to the ring gear of the internal combustion engine, the centrifugal force of the locking member increases as the rotational speed of the internal combustion engine increases. An object of the present invention is to provide a starting device for an internal combustion engine that is enlarged and can be expected to perform a lock release operation reliably.
以下に本発明の好適一実施例を添付図面に基づ
いて詳述する。 A preferred embodiment of the present invention will be described in detail below with reference to the accompanying drawings.
第１図は本発明に係る始動装置の概略基本構成
を示した側断面図で、第２図は第１図の２矢視方
向図、第３図、第４図は同始動装置の作動状態を
示す図である。 FIG. 1 is a side cross-sectional view showing the general basic configuration of the starting device according to the present invention, FIG. 2 is a view in the direction of arrow 2 in FIG. 1, and FIGS. 3 and 4 are the operating states of the starting device. FIG.
始動スイツチの閉成で駆動される電動機部のア
マーチユアの出力軸１０はピニオン軸１１の減速
用従動ギヤ１１ａと噛合し、出力軸１０の回転で
ピニオン軸１１が回転せしめられる。ピニオン軸
１１の小径軸部１１ｂの外周面にはヘリカルスプ
ライン１１ｃが形成され、これに移動筒部材１２
の後部１２ａが嵌合し、ピニオン軸１１の段部１
１ｄと移動筒部材１２の後部１２ａとの間にはリ
ターンスプリング１３が縮装介入され、リターン
スプリング１３の弾発力で移動筒部材１２は常時
後方へ弾発付勢されているとともに、後退限はピ
ニオン軸１１の後部に固設されたストツパー１４
で規制されている。移動筒部材１２にはスプリン
グ、ローラからなる一方向クラツチ１５を介して
ピニオン軸１１の大径軸部１１ｃ上に摺動可能に
嵌合されたピニオンギヤ１６が連結され、本実施
例ではピニオンギヤ１６の後部大径筒部１６ａが
移動筒部材２の外周を囲み、従つて移動筒部材１
２がクラツチインナーとなり、後部大径筒部１６
ａがクラツチアウター１７となつている。 The armature output shaft 10 of the electric motor section, which is driven when the start switch is closed, meshes with the speed reduction driven gear 11a of the pinion shaft 11, and the rotation of the output shaft 10 causes the pinion shaft 11 to rotate. A helical spline 11c is formed on the outer peripheral surface of the small diameter shaft portion 11b of the pinion shaft 11, and the movable cylinder member 12
The rear part 12a of the pinion shaft 11 is fitted into the stepped part 1 of the pinion shaft 11.
A return spring 13 is compressed and intervened between 1d and the rear part 12a of the movable cylinder member 12, and the elastic force of the return spring 13 constantly urges the movable cylinder member 12 backward, and is a stopper 14 fixed to the rear of the pinion shaft 11.
regulated by. A pinion gear 16 slidably fitted onto the large diameter shaft portion 11c of the pinion shaft 11 is connected to the movable cylinder member 12 via a one-way clutch 15 consisting of a spring and a roller. The rear large-diameter cylindrical portion 16a surrounds the outer periphery of the movable cylindrical member 2, so that the movable cylindrical member 1
2 is the clutch inner, and the rear large diameter cylinder part 16
A is the clutch outer 17.
このクラツチアウター１７の後端面にはピン１
８で係止部材であるガバナーウエイト１９が軸径
方向に揺動自在に枢着され、ガバナーウエイト１
９は内端部に軸方向へ折曲された突片１９ａを一
体に備えた断面Ｌ字状となつており、又第２図に
示す通りバネ２０の引張力でピン１８廻りに常時
内径方向に引張付勢されている。前記ストツパ−
１４に前方へ延びる筒部１４ａを一体に備え、こ
の筒部１４ａ内に後退限における移動筒部材１２
の後部１２ａが挿入されているとともに、筒部１
４ａの外周面にガバナーウエイト１９の折曲突片
１９ａが接触している。 A pin 1 is provided on the rear end surface of this clutch outer 17.
At 8, a governor weight 19, which is a locking member, is pivotally attached to the governor weight 19 so as to be swingable in the radial direction of the shaft.
9 has an L-shaped cross section with an integral protrusion 19a bent in the axial direction at the inner end, and as shown in FIG. is tensilely biased. The stopper
14 is integrally provided with a cylindrical portion 14a extending forward, and the movable cylindrical member 12 at the backward limit is disposed within this cylindrical portion 14a.
The rear part 12a of the cylinder part 1 is inserted, and the cylindrical part 1
A bent protrusion 19a of the governor weight 19 is in contact with the outer peripheral surface of the governor weight 4a.
電動機部の出力軸１０によつてピニオン軸１１
が急速回転すると、ピニオン軸１１とヘリカルス
プライン嵌合している移動筒部材１２は重量慣性
によつてピニオン軸１１上をリターンスプリング
１３を圧縮しつつ前方へ摺動し、ピニオンギヤ１
６も第３図の通り移動筒部材１２と一体に前方へ
摺動し、内燃機関のリングギヤ２１にピニオンギ
ヤ１６が飛び込み、これと噛合する。前進限に達
したピニオンギヤ１６はヘリカルスプライン１１
ｃ、移動筒部材１２、接続状態の一方向クラツチ
１５を介してピニオン軸１１と一体に回転し始
め、リングギヤ２１が回転せしめられて内燃機関
は始動する。 The pinion shaft 11 is driven by the output shaft 10 of the electric motor section.
When the pinion shaft 11 rotates rapidly, the movable cylinder member 12 that is helically spline-fitted with the pinion shaft 11 slides forward on the pinion shaft 11 due to weight inertia while compressing the return spring 13, and the pinion gear 1
As shown in FIG. 3, the pinion gear 6 also slides forward together with the movable cylinder member 12, and the pinion gear 16 jumps into the ring gear 21 of the internal combustion engine and meshes with it. The pinion gear 16 that has reached its forward limit is the helical spline 11
c, the movable cylinder member 12 begins to rotate together with the pinion shaft 11 via the one-way clutch 15 in the connected state, the ring gear 21 is rotated, and the internal combustion engine is started.
移動筒部材１２が上述の通り慣性摺動し、ピニ
オンギヤ１６が前方へ移動したさい第３図の通
り、移動筒部材１２の後部１２ａはストツパー１
４の筒部１４ａから抜け出し、筒部１４ａの前方
にガバナーウエイト１９が達し、常時内径方向へ
引張されているガバナーウエイト１９はピン１８
廻りに軸内径方向に揺動することとなり、第４図
の通り内端の折曲突片１９ａが移動筒部材１２の
外周面に当接し、ストツパー１４の筒部１４ａ前
方を塞ぐ。 When the movable cylinder member 12 slides inertia as described above and the pinion gear 16 moves forward, the rear part 12a of the movable cylinder member 12 is moved to the stopper 1 as shown in FIG.
The governor weight 19 comes out of the cylindrical part 14a of No. 4 and reaches the front of the cylindrical part 14a, and the governor weight 19, which is constantly pulled in the inner radial direction,
As a result, as shown in FIG. 4, the bent protrusion 19a at the inner end comes into contact with the outer peripheral surface of the movable cylindrical member 12, and closes the front of the cylindrical portion 14a of the stopper 14.
従つて内燃機関の始動初期における内燃機関の
瞬間的な高回転によつてリングギヤ２１からピニ
オンギヤ１６が逆に動力を伝達され、リターンス
プリング１３の弾発作用と相俟つてピニオンギヤ
１６とピニオン軸１１との回転数差、具体的には
ピニオンギヤ１６からの移動筒部材１２に伝達さ
れる一方向クラツチ１５の引きずりトルクにより
ピニオンギヤ１６がリンクギヤ２１から離脱し、
移動筒部材１２が後退動しようとしても、ガバナ
ーウエイト１９の背面にストツパー１４が衝合す
るためガバナーウエイト１９の係止作用によつて
ピニオンギヤ１６、移動筒部材１２はピニオン軸
１１に係止状態となり、このため内燃機関が安定
駆動する以前のピニオンギヤの早期離脱は防止さ
れ、ピニオン軸１１の駆動力はピニオンギヤ１６
によりリングギヤ２１に伝達されて内燃機関は初
期の回転から所定の回転に移行する。 Therefore, power is transmitted from the ring gear 21 to the pinion gear 16 in the opposite direction due to the instantaneous high rotation of the internal combustion engine at the initial stage of starting the internal combustion engine, and together with the spring action of the return spring 13, the pinion gear 16 and the pinion shaft 11 are The pinion gear 16 separates from the link gear 21 due to the difference in rotational speed, specifically, the drag torque of the one-way clutch 15 transmitted from the pinion gear 16 to the movable cylinder member 12.
Even if the movable cylinder member 12 attempts to move backward, the stopper 14 abuts against the back surface of the governor weight 19, so the pinion gear 16 and the movable cylinder member 12 are locked to the pinion shaft 11 due to the locking action of the governor weight 19. Therefore, early disengagement of the pinion gear before the internal combustion engine is stably driven is prevented, and the driving force of the pinion shaft 11 is transferred to the pinion gear 16.
The rotation is transmitted to the ring gear 21, and the internal combustion engine shifts from an initial rotation to a predetermined rotation.
内燃機関がアイドリング回転の所定の回転に達
すると、一方向クラツチ１５の断絶作動によりピ
ニオンギヤ１６はリングギヤ２１から動力が伝達
されて高速の自由回転し、ガバナーウエイト１９
にはバネ２０に打ち勝つ遠心力が発生し、ピン１
８廻りにガバナーウエイト１９が第３図の如く軸
外径方向に揺動し、即ちガバナーウエイト１９に
よるピニオンギヤ１６、移動筒部材１２のピニオ
ン軸１１に対する係止状態は解除され、リターン
スプリング１３の作用と上記引きずりトルクとに
よりピニオンギヤ１６と移動筒部材１２はピニオ
ン軸１１上の旧位の後退位置に戻る。 When the internal combustion engine reaches a predetermined idling speed, the one-way clutch 15 is disconnected and the pinion gear 16 receives power from the ring gear 21 and rotates freely at high speed.
A centrifugal force is generated that overcomes the spring 20, and the pin 1
8, the governor weight 19 swings in the direction of the outer diameter of the shaft as shown in FIG. The above dragging torque causes the pinion gear 16 and the movable cylinder member 12 to return to the previous retracted position on the pinion shaft 11.
以上の作動において、ピニオンギヤ１６、移動
筒部材１２をピニオン軸１１に係止状態とすべく
ガバナーウエイト１９の背面にストツパー１４が
当接したさいガバナーウエイト１９には軸方向荷
重が作用するが、本実施例のガバナーウエイト１
９は既述の通り内端に折曲突片１９ａを備えた断
面Ｌ字状として形成され、軸方向への長さをもつ
たこの突片１９ａが上記荷重を受けることとなる
ため、ガバナーウエイト１９を平板状とした場合
の如くピン１８による枢着部に無理な応力が作用
することを防止できる。 In the above operation, when the stopper 14 comes into contact with the back surface of the governor weight 19 in order to lock the pinion gear 16 and the movable cylinder member 12 to the pinion shaft 11, an axial load acts on the governor weight 19. Governor weight 1 of the example
9 is formed to have an L-shaped cross section with a bent protrusion 19a at the inner end as described above, and since this protrusion 19a having a length in the axial direction receives the above load, the governor weight It is possible to prevent excessive stress from being applied to the pivot joint by the pin 18, as would be the case if the pin 19 were made into a flat plate.
又、ガバナーウエイト１９は一方向クラツチ１
５を境としてリングギヤ側のピニオンギヤ１６と
一体化されたクラツチアウター１７に設けられ、
このピニオンギヤ１６及びクラツチアウター１７
は内燃機関と同数回転するものであるため内燃機
関の回転数が増す程ガバナーウエイト１９に発生
する遠心力は大きくなり、例えばピニオン軸１１
の回転によつて遠心力が発生するようにウエイト
部材を移動筒部材１２に軸径方向移動自在に設
け、このウエイト部材によつてピニオンギヤ１
６、移動筒部材１２をピニオン軸１１に係止する
ようにするよりも内燃機関の回転状態に応じてガ
バナーウエイト１９に遠心力が発生するため、ガ
バナーウエイト１９の係止解除作動を内燃機関の
回転状態と適合した確実なものとして行わせるこ
とができる。 In addition, the governor weight 19 is connected to the one-way clutch 1.
5 is provided on the clutch outer 17 integrated with the pinion gear 16 on the ring gear side,
This pinion gear 16 and clutch outer 17
Since the rotation speed of the internal combustion engine is the same as that of the internal combustion engine, the centrifugal force generated in the governor weight 19 increases as the rotation speed of the internal combustion engine increases.
A weight member is provided on the movable cylinder member 12 so as to be movable in the axial and radial direction so that centrifugal force is generated by the rotation of the pinion gear 1.
6. Rather than locking the movable cylinder member 12 to the pinion shaft 11, centrifugal force is generated in the governor weight 19 depending on the rotational state of the internal combustion engine. This can be done reliably and in accordance with the rotational conditions.
ガバナーウエイト１９が軸外径方向に揺動する
回転数はガバナーウエイト１９の重量とバネ２０
の張力によつて決定され、これらを調整すること
により係止解除回転数を設定することができる
が、内燃機関始動時（クランキング時）の略２〜
３倍であつて内燃機関のアイドリング時の略0.5
〜0.9倍の回転数領域においてガバナーウエイト
１９が係止解除作動するように設定することが望
ましい。 The number of rotations at which the governor weight 19 swings in the direction of the outer diameter of the shaft is determined by the weight of the governor weight 19 and the spring 20.
The unlocking rotation speed can be set by adjusting these tensions, but it is approximately 2 to
3 times, approximately 0.5 when the internal combustion engine is idling
It is desirable to set the governor weight 19 to release the lock in the rotation speed range of ~0.9 times.
次に本発明に係る具体的な実施例を説明する。
以下の説明において理解を容易化するため前記と
同じ部材には同じ符号を用いる。 Next, specific examples according to the present invention will be described.
In the following description, the same reference numerals are used for the same members as above to facilitate understanding.
第５図乃至第７図は具体的な第１実施例を示
し、第５図はピニオン軸及びストツパーを除いて
示したアツセンブリの断面図で、第６図は第５図
６−６線断面図、第７図はピニオン軸、ストツパ
ーを含めた分解斜視図である。この実施例ではピ
ニオンギヤ１６とクラツチアウター１７は別体に
成形され、クラツチアウター１７に被冠したキヤ
ツプ部材３０の端部周縁３０ａを加締めることに
よりピニオンギヤ１６とクラツチアウター１７に
軸方向に結合して一体化し、且つピン３１によつ
てピニオンギヤ１６とクラツチアウター１７とを
回転方向にも一体化した。このようにクラツチア
ウター１７をピニオンギヤ１６とは別体品とする
ことにより、第６図で示した一方向クラツチ１５
を構成するローラ１５ａを収容するテーパ状凹部
１７ａの加工性が良好となるため、凹部１７ａを
ブローチ加工で高精度に仕上げることができ、且
つ少量生産の場合にはこの加工コストを冷鍛加工
よりも安価とすることができる。更にピニオンギ
ヤ１６、クラツチアウター１７、キヤツプ部材３
０の材料をその部分が必要とする硬度、ねばり性
等を有する最適のものに個別に選択できる。 5 to 7 show a concrete first embodiment, FIG. 5 is a sectional view of the assembly with the pinion shaft and stopper removed, and FIG. 6 is a sectional view taken along the line 6-6 in FIG. , FIG. 7 is an exploded perspective view including the pinion shaft and stopper. In this embodiment, the pinion gear 16 and the clutch outer 17 are formed separately, and are coupled to the pinion gear 16 and the clutch outer 17 in the axial direction by tightening the peripheral edge 30a of the cap member 30 that covers the clutch outer 17. In addition, the pinion gear 16 and clutch outer 17 are integrated in the rotational direction by the pin 31. By making the clutch outer 17 a separate item from the pinion gear 16 in this way, the one-way clutch 15 shown in FIG.
Since the workability of the tapered recess 17a that accommodates the roller 15a constituting the roller 15a is good, the recess 17a can be finished with high precision by broaching, and in the case of small-scale production, this processing cost can be reduced compared to cold forging. It can also be made cheaper. Furthermore, a pinion gear 16, a clutch outer 17, and a cap member 3
0 material can be individually selected to have the optimum hardness, tenacity, etc. required for that part.
断面Ｌ字状ガバナーウエイト１９はピン１８で
キヤツプ部材３０の後端面に枢着され、このガバ
ナーウエイト１９は第７図で示す通り２個あり、
夫々の間に架設したバネ２０，２０の引張力で軸
内径方向に引張付勢されている。このガバナーウ
エイト１９の揺動限は第５図に示したピン３２に
よつて規制される。キヤツプ部材３０の内周面に
はサークリツプ３３が止着され、この着脱自在な
サークリツプ３３によつてピニオンギヤ１６、ク
ラツチアウター１７と移動筒部材１２とが軸方向
に連結され、サークリツプ３３の取り外しにより
クラツチローラ１５ａ、凹部１７ａ部分の清掃が
行える。サークリツプ３３と移動筒部材１２の環
状提部１２ｂとの間にはスラストワツシヤー３４
が介在され、相対回転運転するピニオンギヤ１６
側のサークリツプ３３と移動筒部材１２との回転
摩擦力をこのワツシヤー３４が軽減する。 A governor weight 19 having an L-shaped cross section is pivotally attached to the rear end surface of the cap member 30 by a pin 18, and there are two governor weights 19 as shown in FIG.
They are tensilely biased in the radially inner direction of the shaft by the tensile force of springs 20, 20 installed between them. The limit of the swing of the governor weight 19 is regulated by a pin 32 shown in FIG. A circlip 33 is fixed to the inner peripheral surface of the cap member 30, and this removable circlip 33 connects the pinion gear 16, the clutch outer 17, and the movable cylinder member 12 in the axial direction. The roller 15a and recessed portion 17a can be cleaned. A thrust washer 34 is provided between the circlip 33 and the annular support portion 12b of the movable cylinder member 12.
A pinion gear 16 that operates in relative rotation with
This washer 34 reduces the rotational friction force between the side circlip 33 and the movable cylinder member 12.
更に第６図の通りクラツチアウター１７に被冠
されるキヤツプ部材３０はクラツチバネ１５ｂの
押え部材を兼ねる。 Furthermore, as shown in FIG. 6, a cap member 30 that is covered with the clutch outer 17 also serves as a holding member for the clutch spring 15b.
第８図、第９図は具体的な第２実施例を示し、
第９図の分解斜視図は第７図と共通する部材を省
略し、変更部材を主として示した。 FIG. 8 and FIG. 9 show a concrete second embodiment,
The exploded perspective view of FIG. 9 omits the same members as those of FIG. 7 and mainly shows changed members.
ピニオンギヤ１６とクラツチアウター１７とは
前記実施例と同様にキヤツプ部材３０、ピン３１
によつて一体化されているが、ガバナーウエイト
１９は平板状に形成され、サークリツプ３３とガ
バナーウエイト１９との間にプレート４０を介入
した。ピニオンギヤ１６、移動筒部材１２をピニ
オン軸１１に係止状態とすべくガバナーウエイト
１９の背面がピニオン軸１１に固設されたストツ
パー１４に当接した場合、ガバナーウエイト１９
に作用する軸方向荷重はこのプレート４０で受け
られ、これにより平板状にガバナーウエイト１９
が形成されていても曲がり変形することなく、且
つピン１８によるガバナーウエイト枢着部に無理
な応力が加わることはない。 The pinion gear 16 and clutch outer 17 are connected to a cap member 30 and a pin 31 as in the previous embodiment.
However, the governor weight 19 is formed into a flat plate shape, and a plate 40 is interposed between the circlip 33 and the governor weight 19. When the back of the governor weight 19 comes into contact with the stopper 14 fixed to the pinion shaft 11 in order to lock the pinion gear 16 and the movable cylinder member 12 to the pinion shaft 11, the governor weight 19
The axial load acting on the plate 40 is received by the plate 40, and the governor weight 19 is thereby
Even if it is formed, it will not bend or deform, and no unreasonable stress will be applied to the pivot point of the governor weight by the pin 18.
以上の説明で明らかな如く本発明によれば、ガ
バナーウエイトの如き係止部材の係止作用によつ
て内燃機関の始動初期にピニオンギヤ及び移動筒
部材をピニオン軸に係止し、リングギヤからのピ
ニオンギヤの早期離脱を防止できるとともに、こ
の係止部材はピニオンギヤと一体化された部材に
枢着されているため、内燃機関の回転状態に応じ
て係止部材に遠心力が発生するようになり、上記
の係止状態を解除する遠心力は内燃機関の回転数
向上に伴つて大きくなり、内燃機関が高速の所定
回転状態に移行するとともに係止解除作動を行わ
せることができ、作動の確実化を実現できる。 As is clear from the above description, according to the present invention, the pinion gear and the movable cylinder member are locked to the pinion shaft at the initial stage of starting the internal combustion engine by the locking action of the locking member such as the governor weight, and the pinion gear from the ring gear is locked. In addition to preventing premature disengagement, this locking member is pivotally connected to a member integrated with the pinion gear, so centrifugal force is generated in the locking member depending on the rotational state of the internal combustion engine. The centrifugal force that releases the locked condition increases as the rotational speed of the internal combustion engine increases, and the unlocking operation can be performed as the internal combustion engine shifts to a high speed predetermined rotational state, ensuring reliable operation. realizable.
第１図は始動装置の概略基本構成を示した断面
図、第２図は第１図の２矢視方向図、第３図、第
４図は同装置の作動状態を示す第１図と同様の
図、第５図乃至第７図は具体的な実施例を示し、
第５図はピニオン軸、ストツパーを除いたアツセ
ンブリの断面図、第６図は第５図６−６線断面
図、第７図はピニオン軸、ストツパーを含めた分
解斜視図、第８図及び第９図は具体的な別実施例
を示し、第８図は第５図と同様の図、第９図は変
更部材を主として示した第７図と同様の図であ
る。
尚図面中、１０は出力軸、１１はピニオン軸、
１２は移動筒部材、１５は一方向クラツチ、１６
はピニオンギヤ、１９は係止部材であるガバナー
ウエイト、２１はリングギヤである。
Fig. 1 is a cross-sectional view showing the general basic configuration of the starting device, Fig. 2 is a view taken in the direction of arrow 2 in Fig. 1, and Figs. 3 and 4 are the same as Fig. 1, showing the operating state of the device. , and FIGS. 5 to 7 show specific examples,
Fig. 5 is a sectional view of the assembly excluding the pinion shaft and stopper, Fig. 6 is a sectional view taken along the line 6-6 in Fig. 5, Fig. 7 is an exploded perspective view including the pinion shaft and stopper, and Figs. FIG. 9 shows another specific embodiment, FIG. 8 is a view similar to FIG. 5, and FIG. 9 is a view similar to FIG. 7 mainly showing changed members. In the drawing, 10 is the output shaft, 11 is the pinion shaft,
12 is a movable cylinder member, 15 is a one-way clutch, 16
1 is a pinion gear, 19 is a governor weight that is a locking member, and 21 is a ring gear.
Claims (1)
ニオン軸に移動筒部材を慣性摺動自在にヘリカル
スプライン嵌合し、該移動筒部材に一方向クラツ
チを介して内燃機関のリングギヤに飛び込み噛合
するピニオンギヤを連結するとともに、該ピニオ
ンギヤと一体化された部材にピニオンギヤのリン
グギヤからの早期離脱を防止すべくピニオンギヤ
及び上記移動筒部材をピニオン軸に係止状態とす
る係止部材を軸径方向に揺動自在に枢着し、リン
グギヤからの動力伝達によるピニオンギヤの高速
回転で該係止部材を遠心力で軸外径方向へ揺動さ
せてピニオン軸に対するピニオンギヤ及び移動筒
部材の係止状態を解除するように構成したことを
特徴とする内燃機関の始動装置。1. A movable cylinder member is fitted with a helical spline so as to be inertially slidable on a pinion shaft rotated by an output shaft of an electric motor section, and a pinion gear that jumps into engagement with a ring gear of an internal combustion engine is connected to the movable cylinder member via a one-way clutch. At the same time, a locking member that locks the pinion gear and the movable cylinder member to the pinion shaft is provided in a member integrated with the pinion gear so as to be able to swing freely in the radial direction of the shaft in order to prevent the pinion gear from prematurely separating from the ring gear. The pinion gear is pivotally mounted, and the locking member is pivoted in the direction of the outer diameter of the shaft by centrifugal force when the pinion gear rotates at high speed due to power transmission from the ring gear, thereby releasing the locking state of the pinion gear and the movable cylinder member with respect to the pinion shaft. An internal combustion engine starting device characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13269280A JPS5759055A (en) | 1980-09-24 | 1980-09-24 | Starting device of internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13269280A JPS5759055A (en) | 1980-09-24 | 1980-09-24 | Starting device of internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5759055A JPS5759055A (en) | 1982-04-09 |
| JPS6256348B2 true JPS6256348B2 (en) | 1987-11-25 |
Family
ID=15087299
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13269280A Granted JPS5759055A (en) | 1980-09-24 | 1980-09-24 | Starting device of internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5759055A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0167155U (en) * | 1987-10-27 | 1989-04-28 | ||
| JPH0167154U (en) * | 1987-10-27 | 1989-04-28 | ||
| JPH0167153U (en) * | 1987-10-27 | 1989-04-28 | ||
| JPH038037U (en) * | 1989-06-12 | 1991-01-25 |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5913670U (en) * | 1982-07-15 | 1984-01-27 | 澤藤電機株式会社 | Inertia sliding starting device |
-
1980
- 1980-09-24 JP JP13269280A patent/JPS5759055A/en active Granted
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0167155U (en) * | 1987-10-27 | 1989-04-28 | ||
| JPH0167154U (en) * | 1987-10-27 | 1989-04-28 | ||
| JPH0167153U (en) * | 1987-10-27 | 1989-04-28 | ||
| JPH038037U (en) * | 1989-06-12 | 1991-01-25 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5759055A (en) | 1982-04-09 |
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