JPH11270656A - Gear noise preventing device - Google Patents

Gear noise preventing device

Info

Publication number
JPH11270656A
JPH11270656A JP10071007A JP7100798A JPH11270656A JP H11270656 A JPH11270656 A JP H11270656A JP 10071007 A JP10071007 A JP 10071007A JP 7100798 A JP7100798 A JP 7100798A JP H11270656 A JPH11270656 A JP H11270656A
Authority
JP
Japan
Prior art keywords
gear
coil spring
torsion coil
retainer
auxiliary gear
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
JP10071007A
Other languages
Japanese (ja)
Other versions
JP3319718B2 (en
Inventor
Yoshitaka Nukada
芳隆 額田
Yoji Shimizu
要司 清水
Takashi Ishizaka
孝史 石坂
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.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
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 Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to JP07100798A priority Critical patent/JP3319718B2/en
Priority to TW087121550A priority patent/TW417012B/en
Priority to CN99101346A priority patent/CN1107179C/en
Priority to BR9902213-3A priority patent/BR9902213A/en
Priority to KR1019990009405A priority patent/KR100324251B1/en
Priority to IDP990242A priority patent/ID22258A/en
Publication of JPH11270656A publication Critical patent/JPH11270656A/en
Application granted granted Critical
Publication of JP3319718B2 publication Critical patent/JP3319718B2/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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)

Abstract

PROBLEM TO BE SOLVED: To keep spring load of a torsion coil spring constant to smooth the operation of an auxiliary gear in a gear-engagement noise reducing device. SOLUTION: An auxiliary gear 6 is rotatably provided adjacent to a primary driving gear 5, and a retainer 7 pressed onto the shaft-end of a rotary shaft 4 and the auxiliary gear 6 are connected by a torsion coil spring 30. A part of an outside peripheral flange 21 in the retainer 7 is formed into a notch-like shape, and a guide part 25 which is projected parallel to the axial direction of the rotary shaft 4 on the inside peripheral side relative to the outside peripheral flange. Then, the torsion coil spring 30 is provided to pass through between the outside peripheral flange 21 and the guide par 25. When the diameter of the torsion coil spring 30 is reduced in order to given a pre-load, a part of the inside peripheral surface of the coil spring is brought into contact with the guide part 25, whereas other part cannot contact the rotary shaft 4 or the like.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】この発明は、同軸上に設けら
れた主歯車と副歯車に位相差を与えて相手歯車と噛み合
わせることにより、噛み合い騒音を低減するようにした
歯車騒音防止装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear noise prevention device which reduces a mesh noise by providing a phase difference between a main gear and a sub gear provided on the same axis and meshing with a mating gear.

【０００２】[0002]

【従来の技術】実開昭６３−５９２６０号には、エンジ
ンのクランク軸上に設けられた歯車騒音防止装置が示さ
れている。この歯車騒音防止装置は、クランク軸上へ隣
り合わせに配設された主歯車であるプライマリドライブ
歯車と、副歯車とを備え、副歯車とプライマリドライブ
歯車の間には位相差が与えられ、かつクランク軸へ一体
回転するように設けられたリテーナと副歯車の間にねじ
りコイルスプリングが介装され、このねじりコイルスプ
リングにより副歯車を位相差解消方向へ回動付勢するよ
うプリロードが与えられ、プライマリドライブ歯車と副
歯車を相手歯車である変速クラッチのプライマリドリブ
ン歯車と噛み合わせることにより噛み合い騒音を低減す
るようになっている。2. Description of the Related Art Japanese Unexamined Utility Model Publication No. 63-59260 discloses a gear noise reduction device provided on an engine crankshaft. This gear noise prevention device includes a primary drive gear, which is a main gear disposed adjacent to the crankshaft, and a sub gear, wherein a phase difference is given between the sub gear and the primary drive gear, and A torsion coil spring is interposed between the retainer provided to rotate integrally with the shaft and the auxiliary gear, and a preload is applied by the torsion coil spring so as to urge the auxiliary gear to rotate in the phase difference elimination direction, thereby providing a primary load. The drive gear and the auxiliary gear mesh with the primary driven gear of the transmission clutch, which is the mating gear, to reduce mesh noise.

【０００３】[0003]

【発明が解決しようとする課題】図７はこの装置におい
て、副歯車ａを作動回転方向（Ａ矢示方向）へ回転させ
てねじりコイルスプリングｂにプリロードを発生させる
状態を示す模式図であり、ねじりコイルスプリングｂ
は、副歯車ａとの係合端ｃが自由時の位置（破線指示）
からＡ矢示方向へ移動することにより縮径して実線指示
位置に来ると、ねじりコイルスプリングｂの中心が自由
時のＯ１からＯ２へとリテーナｄ及び回転軸ｅの各中心
に対して偏心し、その結果ねじりコイルスプリングｂの
一部がリテーナｄの内周面へ接触したり（Ｂ点）、回転
軸ｅの外周面へ接触する（Ｃ点）。FIG. 7 is a schematic diagram showing a state in which the auxiliary gear a is rotated in the operating rotation direction (the direction indicated by the arrow A) to generate a preload in the torsion coil spring b in this device. Torsion coil spring b
Is the position when the engagement end c with the auxiliary gear a is free (indicated by a broken line)
When the diameter of the torsion coil spring b reaches the position indicated by the solid line by moving in the direction of arrow A from FIG. As a result, a part of the torsion coil spring b contacts the inner peripheral surface of the retainer d (point B) or contacts the outer peripheral surface of the rotating shaft e (point C).

【０００４】しかしながら、このような接触が不規則な
場所や長さで発生すると、副歯車ａに対してプリロード
を与えるために必要なねじりコイルスプリングｂのばね
荷重が一定しなくなり、その結果、副歯車ａの作動が不
安定になることがある。また、図８に示すように、ねじ
りコイルスプリングｂが複数巻きになっていると、縮径
時に部分的に巻き線が重なり合うことがあり、このよう
な場合によっても前記ねじりコイルスプリングｂのばね
荷重が不安定になることによる副歯車ａの作動不安定を
生じるおそれがある。[0004] However, if such contact occurs at irregular places or lengths, the spring load of the torsion coil spring b required to apply a preload to the auxiliary gear a becomes inconsistent. The operation of the gear a may become unstable. Further, as shown in FIG. 8, if the torsion coil spring b has a plurality of turns, the windings may partially overlap when the diameter is reduced. Even in such a case, the spring load of the torsion coil spring b may be increased. Of the auxiliary gear a due to the instability of the gear.

【０００５】[0005]

【課題を解決するための手段】上記課題を解決するため
本願の歯車騒音防止装置に係る第１の発明は、同一回転
軸上へ隣り合わせに配設された主歯車と副歯車の間に位
相差を設け、かつ前記回転軸と一体回転するように設け
られたリテーナと副歯車との間へねじりコイルスプリン
グを介装し、このねじりコイルスプリングにより前記位
相差が解消される方向へ副歯車を回動付勢することによ
りプリロードを与え、相手歯車との噛み合い騒音を低減
するようにした歯車騒音防止装置において、前記ねじり
コイルスプリングの内周側を支持するためのガイド部を
前記リテーナに設けたことを特徴とする。According to a first aspect of the present invention, there is provided a gear noise reduction device comprising: a main gear and a sub gear arranged adjacently on the same rotating shaft; And a torsion coil spring is interposed between the retainer and the auxiliary gear provided so as to rotate integrally with the rotary shaft, and the auxiliary gear is rotated in a direction in which the phase difference is eliminated by the torsion coil spring. In the gear noise prevention device, in which a preload is given by dynamic biasing to reduce meshing noise with a mating gear, a guide portion for supporting the inner peripheral side of the torsion coil spring is provided in the retainer. It is characterized by.

【０００６】第２の発明は前記第１の発明において、前
記ガイド部とリテーナの間隔をＤ、ねじりコイルスプリ
ングの線径をｄとしたとき、Ｄ＜２ｄであることを特徴
とする。A second invention is characterized in that, in the first invention, when the distance between the guide portion and the retainer is D and the wire diameter of the torsion coil spring is d, D <2d.

【０００７】[0007]

【発明の効果】リテーナにねじりコイルスプリングの内
周を支持するためのガイド部を設けたので、プリロード
を与えるためにねじりコイルスプリングを縮径させる
と、その内周がガイド部へ接触して支持される。このた
め、ねじりコイルスプリングの内周はガイド部とのみ接
触し、かつ接触点が一定し、そのうえ接触長さも比較的
短くできるので、ねじりコイルスプリングのばね荷重が
安定し、その結果、副歯車の作動が安定する。Since the retainer is provided with a guide portion for supporting the inner circumference of the torsion coil spring, if the diameter of the torsion coil spring is reduced to provide a preload, the inner circumference contacts the guide portion and is supported. Is done. For this reason, the inner periphery of the torsion coil spring contacts only the guide portion, and the contact point is constant, and the contact length can be relatively short, so that the spring load of the torsion coil spring is stabilized, and as a result, the auxiliary gear Operation stabilizes.

【０００８】また、ガイド部とリテーナの間隔をＤ、ね
じりコイルスプリングの線径をｄとしたとき、Ｄ＜２ｄ
とすれば、縮径時にねじりコイルスプリングの巻き線が
部分的に重なり合う事態が発生することを防止できる。
従って、これによっても副歯車の作動を安定化できる。When the distance between the guide portion and the retainer is D and the wire diameter of the torsion coil spring is d, D <2d
Then, it is possible to prevent a situation in which the windings of the torsion coil spring partially overlap with each other when the diameter is reduced.
Therefore, the operation of the auxiliary gear can be stabilized also by this.

【０００９】[0009]

【発明の実施の形態】図１乃至図６にエンジンのクラン
ク軸上に設けられるプライマリドライブ歯車に適用され
た本願発明の一実施例を示す。図１はプライマリドライ
ブ歯車部分近傍の拡大断面図、図２は本実施例に係るエ
ンジンの断面図、図３はガイド部を示す部分拡大断面
図、図４は図１のＥ矢示方向図、図５は作動回転前（プ
リロード前）の状態を示す図１の５−５線断面図、図６
はプリロード時における図５の同様図である。1 to 6 show an embodiment of the present invention applied to a primary drive gear provided on a crankshaft of an engine. 1 is an enlarged sectional view of the vicinity of a primary drive gear portion, FIG. 2 is a sectional view of an engine according to the present embodiment, FIG. 3 is a partially enlarged sectional view showing a guide portion, FIG. FIG. 5 is a sectional view taken along the line 5-5 in FIG. 1 showing a state before operation rotation (before preloading);
FIG. 6 is a view similar to FIG. 5 at the time of preloading.

【００１０】まず図２において、このエンジンは、ピス
トンロッド１の連結されたクランク軸２と、その一端が
接続する発進クラッチ３と、この発進クラッチ３を介し
てクランク軸２と接続しかつその外周へ遊転自在に設け
られた回転軸４とを備える。Referring first to FIG. 2, the engine includes a crankshaft 2 to which a piston rod 1 is connected, a starting clutch 3 connected to one end of the engine, and a crankshaft 2 connected to the crankshaft 2 via the starting clutch 3 and its outer periphery. And a rotating shaft 4 provided so as to be freely rotatable.

【００１１】この回転軸４上には主歯車であるプライマ
リドライブ歯車５と副歯車６が隣り合わせに配設され、
さらに副歯車６を挟んでプライマリドライブ歯車５の反
対側となる回転軸４の軸端部にリテーナ７が配設されて
いる。A primary drive gear 5 as a main gear and a sub gear 6 are disposed adjacent to each other on the rotating shaft 4.
Further, a retainer 7 is disposed at the shaft end of the rotary shaft 4 opposite to the primary drive gear 5 with the auxiliary gear 6 interposed therebetween.

【００１２】副歯車６はプライマリドライブ歯車５と同
径、同歯数もしくはこれらが若干異なる歯車であり、こ
れらプライマリドライブ歯車５と副歯車６はそれぞれク
ラッチ８のプライマリドリブン歯車９に噛み合ってい
る。The auxiliary gear 6 has the same diameter and the same number of teeth as or slightly different from the primary drive gear 5. The primary drive gear 5 and the auxiliary gear 6 are meshed with the primary driven gear 9 of the clutch 8.

【００１３】プライマリドリブン歯車９はクラッチ８の
クラッチアウタと一体であり、その回転はクラッチイン
ナを経てメイン軸１０へ伝達され、さらにメイン軸歯車
１１からカウンタ軸１２のカウンタ軸歯車１３へ伝達さ
れる。The primary driven gear 9 is integral with the clutch outer of the clutch 8, and its rotation is transmitted to the main shaft 10 via the clutch inner, and further transmitted from the main shaft gear 11 to the counter shaft gear 13 of the counter shaft 12. .

【００１４】次に、騒音防止機構について説明する。図
１及び図３乃至図６に示すように、副歯車６は回転軸４
上の主歯車５近傍部１４上へ転動自在に支持され、回転
軸４に対してサークリップ１５により抜け止めされてい
る。Next, the noise prevention mechanism will be described. As shown in FIGS. 1 and 3 to 6, the auxiliary gear 6 has a rotating shaft 4.
It is rotatably supported on the upper portion 14 near the main gear 5 and is prevented from falling off by the circlip 15 with respect to the rotating shaft 4.

【００１５】副歯車６と主歯車５の各歯のうち、一対の
位置合わせ用歯には、それぞれ面取り部１６、１７が形
成され、各面取り部１６、１７を一致させることによ
り、プリロード時における副歯車６と主歯車５の位置決
めが容易になっている。副歯車６の面取り部１７近傍に
は係止穴１８が側面に貫通形成されている。Among the teeth of the auxiliary gear 6 and the main gear 5, a pair of positioning teeth are formed with chamfered portions 16 and 17, respectively. Positioning of the auxiliary gear 6 and the main gear 5 is facilitated. In the vicinity of the chamfered portion 17 of the auxiliary gear 6, a locking hole 18 is formed to penetrate the side surface.

【００１６】回転軸４における主歯車５の位置合わせ用
歯と同一位相となる位置に、軸端部から軸方向内方へ切
り込まれた位置決め溝１９が形成され、この位置決め溝
１９は軸端部で開放されている。A positioning groove 19 is formed at the position on the rotary shaft 4 at the same phase as the positioning teeth of the main gear 5, and the positioning groove 19 is cut inward from the shaft end in the axial direction. It is open in the department.

【００１７】リテーナ７は略カップ状をなして、鉄板も
しくはその他の適宜金属をプレス成形により形成され、
回転軸４の回転面と平行な側壁２０と、その外周部から
副歯車６側へ突出するよう一体に形成された外周フラン
ジ２１と、内周部に反対方向へ突出するように一体に形
成された内周フランジ２２とが設けられている。The retainer 7 has a substantially cup shape, and is formed by press-forming an iron plate or other appropriate metal.
A side wall 20 parallel to the rotation surface of the rotating shaft 4, an outer peripheral flange 21 integrally formed so as to protrude from the outer peripheral portion toward the auxiliary gear 6, and an integrally formed so as to protrude in the opposite direction to the inner peripheral portion. The inner peripheral flange 22 is provided.

【００１８】内周フランジ２２の一部には、中心側へ突
出する位置決め凹部２３が設けられ、位置決め溝１９へ
嵌合可能になっている。内周フランジ２２の周方向にお
ける位置決め凹部２３の中央部近傍と同一位相の側壁２
０には係止穴２４が貫通形成されている。さらに、この
係止穴２４から作動回転方向へ略６０゜位相差がある位
置にガイド部２５が形成されている。A part of the inner peripheral flange 22 is provided with a positioning recess 23 protruding toward the center, and can be fitted into the positioning groove 19. Side wall 2 having the same phase as the vicinity of the center of positioning recess 23 in the circumferential direction of inner circumferential flange 22
0 has a locking hole 24 formed therethrough. Further, a guide portion 25 is formed at a position having a phase difference of about 60 ° in the operation rotation direction from the locking hole 24.

【００１９】ガイド部２５は外周フランジ２１の一部を
切り欠いて、側壁２０と平行するよ中心方向へ折り返し
たものであり、その外周側表面と外周フランジ２１の内
周面との間隔Ｄは後述する所定のものになっている。The guide portion 25 is formed by cutting out a part of the outer peripheral flange 21 and folding it back toward the center so as to be parallel to the side wall 20. The distance D between the outer peripheral surface and the inner peripheral surface of the outer peripheral flange 21 is This is a predetermined one described later.

【００２０】また、ガイド部２５の内周側表面と内周フ
ランジ２２の内周面との間隔Ｆも、縮径時に他の部分を
外周フランジ２１や回転軸４と非接触になるようガイド
するに十分な大きさが確保されている。The distance F between the inner peripheral surface of the guide portion 25 and the inner peripheral surface of the inner peripheral flange 22 also guides other portions so as not to be in contact with the outer peripheral flange 21 and the rotary shaft 4 when the diameter is reduced. Enough size is secured.

【００２１】なお、ガイド部２５の位置は、係止穴２４
の位置からからプリロードを与えるために副歯車を回転
する作動回転方向（Ａ矢示方向）へ所定角度開いてお
り、本実施例では略６０゜程度になっている。この角度
は後述するねじりコイルスプリング３０の最も効率的な
ガイドが可能である。但し、この角度の好ましい範囲は
略１８０゜以内、より好ましくは略９０゜以内で任意範
囲に設定すればよい。The position of the guide part 25 is
From the position, a predetermined angle is opened in the operating rotation direction (the direction indicated by the arrow A) for rotating the auxiliary gear in order to apply a preload, and in this embodiment, it is approximately 60 °. This angle enables the most efficient guide of the torsion coil spring 30 described later. However, a preferable range of this angle may be set to an arbitrary range within about 180 °, more preferably, within about 90 °.

【００２２】リテーナ７と副歯車６とはねじりコイルス
プリング３０で連結されている。ねじりコイルスプリン
グ３０は複数巻きのものであり、巻き方向の両端部はそ
れぞれ逆向きに略９０゜折れ曲り、副歯車６の係止穴１
８へ係止される係合端３１及びリテーナ７の係止穴２４
へ係止される係合端３２をなしている。係合端３１、３
２の位置は作動回転時に一致するよう、自由時では位相
差が与えられている。The retainer 7 and the auxiliary gear 6 are connected by a torsion coil spring 30. The torsion coil spring 30 has a plurality of turns, and both ends in the winding direction are bent approximately 90 ° in opposite directions, respectively, so that the locking hole 1 of the auxiliary gear 6 is formed.
8 and the engaging hole 24 of the retainer 7
The engaging end 32 is locked by the engaging end 32. Engagement ends 31, 3
In the free state, a phase difference is given so that the position 2 coincides with the operation rotation.

【００２３】ねじりコイルスプリング３０はガイド部２
５と外周フランジ２１の間を通るようにリテーナ７へ取
付けられ、ガイド部２５と外周フランジ２１間の前記間
隔Ｄは、ねじりコイルスプリング３０の線径をｄとした
とき、Ｄ＜２ｄなる関係を満たすように設定されてい
る。The torsion coil spring 30 is connected to the guide 2
5 is attached to the retainer 7 so as to pass between the outer flange 5 and the outer peripheral flange 21, and the distance D between the guide portion 25 and the outer peripheral flange 21 has a relation of D <2d when the wire diameter of the torsion coil spring 30 is d. It is set to meet.

【００２４】次に、本実施例の作用を説明する。まず、
回転軸４の主歯車近傍部１４上を自由に回転可能でかつ
サークリップ１４により抜け止めされている副歯車６の
係止穴１８へ、ねじりコイルスプリング３０の係合端３
１を係合し、かつ係合端３２をリテーナ７の係止穴２４
へ係合し、位置決め凹部２３を位置決め溝１９へ嵌合す
るようにして内周フランジ２２を回転軸４の外周へ圧入
により固定する。Next, the operation of this embodiment will be described. First,
The engagement end 3 of the torsion coil spring 30 is inserted into the engagement hole 18 of the auxiliary gear 6 which is freely rotatable on the vicinity of the main gear 14 of the rotary shaft 4 and is prevented from falling off by the circlip 14.
1 and the engaging end 32 is engaged with the locking hole 24 of the retainer 7.
Then, the inner peripheral flange 22 is fixed to the outer periphery of the rotary shaft 4 by press-fitting so that the positioning recess 23 is fitted into the positioning groove 19.

【００２５】これによりねじりコイルスプリング３０は
リテーナ７と副歯車６を連結し、かつ外周フランジ２１
とガイド部２５の間を通るように回転軸４の周囲へ配設
される自由状態となる。この状態が図５に示す状態であ
り、ねじりコイルスプリング３０はリテーナ７の内周及
び回転軸４の外周のいずれとも非接触で間隔を保ってい
る。As a result, the torsion coil spring 30 connects the retainer 7 and the auxiliary gear 6 and the outer peripheral flange 21
And a free state in which it is disposed around the rotary shaft 4 so as to pass between the guide shaft 25 and the guide portion 25. This state is the state shown in FIG. 5, in which the torsion coil spring 30 is kept in contact with both the inner periphery of the retainer 7 and the outer periphery of the rotating shaft 4 without contact.

【００２６】そこで、副歯車６をＡ矢示方向の作動回転
方向へ回動し、その面取り部１７を主歯車５の面取り部
１６へ合わせると、係合端３１がガイド部２５側へ移動
し、これに伴ってねじりコイルスプリング３０が縮径
し、その中心が自由状態のＯ１からＯ２へ偏心する。Then, when the auxiliary gear 6 is turned in the direction of operation rotation in the direction of arrow A and its chamfered portion 17 is aligned with the chamfered portion 16 of the main gear 5, the engaging end 31 moves to the guide portion 25 side. Accordingly, the diameter of the torsion coil spring 30 is reduced, and the center thereof is eccentric from O1 in a free state to O2.

【００２７】その結果、ねじりコイルスプリング３０
は、固定端である係合端３２より回転方向へ向って前半
側が回転軸４側へ移動し、後半側が外周フランジ２１側
へ移動しようとするが、その内周部がガイド部２５へ当
接して支持されるため、ガイド部２５を支点として位置
決めされる。As a result, the torsion coil spring 30
The first half moves toward the rotation shaft 4 from the engagement end 32, which is a fixed end, toward the rotation shaft 4 and the second half tries to move toward the outer peripheral flange 21. Therefore, the guide portion 25 is positioned with the guide portion 25 as a fulcrum.

【００２８】その結果、ねじりコイルスプリング３０は
リテーナ７における外周フランジ２１の内周面及び回転
軸４の外周面と所定の間隔を持ってガイド部２５以外で
は非接触になり、ねじりコイルスプリング３０のリテー
ナ７側に対する接触位置が一定し、かつ接触長もガイド
部２５の外周面側における周方向長さだけの最小限程度
になる。As a result, the torsion coil spring 30 is not in contact with the inner peripheral surface of the outer peripheral flange 21 of the retainer 7 and the outer peripheral surface of the rotating shaft 4 except for the guide portion 25 at a predetermined interval. The contact position with respect to the retainer 7 side is constant, and the contact length is also a minimum of the circumferential length on the outer peripheral surface side of the guide portion 25.

【００２９】このため、ねじりねじりコイルスプリング
３０はばね荷重が一定となり、副歯車６をスムーズに作
動させ、副歯車６を作動回転方向と反対方向へ回動付勢
してプリロードを与えるとともに、プライマリドリブン
歯車１１との噛み合い騒音を低減させることができる。For this reason, the spring load of the torsion torsion coil spring 30 is constant, the sub gear 6 is smoothly operated, the sub gear 6 is rotationally urged in a direction opposite to the operation rotation direction to give a preload, and a primary load is applied. The meshing noise with the driven gear 11 can be reduced.

【００３０】しかも、図５の自由状態から図６の作動状
態に変化するとき、ガイド部２５と係止穴２４との間隔
Ｄは、Ｄ＜２ｄなる関係にあるので、この間隔Ｄにより
巻き線の一部が重なり合うことがなくなり、その結果、
図８に示す従来例の現象は阻止される。ゆえに、これに
よってもねじりねじりコイルスプリング３０のばね荷重
を一定とし、副歯車６の作動をスムーズにできる。Further, when the state changes from the free state in FIG. 5 to the operating state in FIG. 6, the distance D between the guide portion 25 and the locking hole 24 is in a relationship of D <2d. No longer overlap, so that
The phenomenon of the conventional example shown in FIG. 8 is prevented. Therefore, the spring load of the torsion torsion coil spring 30 can be kept constant, and the operation of the auxiliary gear 6 can be smoothly performed.

【００３１】また、副歯車６を作動回転方向へ回動させ
た状態において、係合端３１と３２の位置が略一致する
ようにしたので、ねじりコイルスプリング３０にプリロ
ードを加えたときも、ねじりコイルスプリング３０のよ
じれが防止され、これによってもプリロードを安定させ
副歯車６の作動をスムーズにできる。When the auxiliary gear 6 is rotated in the operating rotation direction, the positions of the engagement ends 31 and 32 are made to substantially coincide with each other. Twisting of the coil spring 30 is prevented, whereby the preload is stabilized and the operation of the auxiliary gear 6 can be smoothly performed.

【００３２】さらに、ガイド部２５の位置を作動回転方
向で係合端３１へ比較的近い位置である開き角略６０゜
の位置に設けたので、最も大きく移動し易い位置を支持
することにより作動回転時にあまりねじりコイルスプリ
ング３０を大きく移動させず、効率的にガイドできる。
そのうえ外周フランジ２１を切り欠いてガイド部２５を
形成したので、ガイド部２５を容易に形成できる。Further, since the guide portion 25 is provided at an opening angle of approximately 60 °, which is a position relatively close to the engagement end 31 in the operating rotation direction, the guide portion 25 is operated by supporting the most easily movable position. The torsion coil spring 30 does not move much during rotation, and can be efficiently guided.
In addition, since the guide portion 25 is formed by cutting the outer peripheral flange 21, the guide portion 25 can be easily formed.

【００３３】さらにまた、内周フランジ部２２の周方向
における位置決め凹部２３の中央部と同一位相となる側
壁２０上に係止穴２４を設けたので、係止穴２４の位置
を側壁２０内においてより内周側へ設けることができ、
それだけ装置全体の小型化に役立つ。Furthermore, since the locking hole 24 is provided on the side wall 20 which is in the same phase as the center of the positioning recess 23 in the circumferential direction of the inner peripheral flange portion 22, the position of the locking hole 24 is adjusted within the side wall 20. It can be provided on the more inner side,
That helps to reduce the size of the entire device.

【００３４】そのうえまた、副歯車６と回転軸４を従来
のようにピンで位置決めせず、サークリップ１５で抜け
止めするだけであるため、製造並びに組立が容易にな
り、高価なピンを省略できるためコストもダウンでき
る。In addition, since the auxiliary gear 6 and the rotary shaft 4 are not positioned by pins as in the prior art, but are merely prevented from falling off by the circlip 15, manufacture and assembly are easy, and expensive pins can be omitted. Therefore, costs can be reduced.

【００３５】しかもまた、リテーナ７を鉄板等を用いた
プレス成形により製造するので軽量にできるとともに、
従来のアルミ鍛造品等と比べると遥かに容易に成形で
き、その結果コストダウンできる。そのうえさらに、内
周フランジ２２を回転軸４の端部へ圧入することにより
回転軸４とリテーナ７とを予め小組化しておくことが可
能になるため取扱性も向上する。Further, since the retainer 7 is manufactured by press molding using an iron plate or the like, the weight can be reduced.
It can be formed much more easily than conventional aluminum forgings and the like, resulting in cost reduction. Furthermore, by press-fitting the inner peripheral flange 22 into the end of the rotating shaft 4, the rotating shaft 4 and the retainer 7 can be previously assembled in a small assembly, so that the handleability is improved.

【００３６】なお、本願発明は上記実施例に限定され
ず、種々に変形可能である。例えば、ガイド部２５の一
部を切り欠くばかりでなく、側壁２０から切り起こし状
に形成したり、内周フランジ２２側から同様にして形成
することもできる。It should be noted that the present invention is not limited to the above embodiment, but can be variously modified. For example, not only a part of the guide portion 25 may be cut out, but also a cut-and-raised shape may be formed from the side wall 20, or a similar shape may be formed from the inner peripheral flange 22 side.

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

【図１】実施例に係るプライマリドライブ歯車部分近傍
の拡大断面図FIG. 1 is an enlarged sectional view of the vicinity of a primary drive gear portion according to an embodiment.

【図２】本実施例に係るエンジンの断面図FIG. 2 is a cross-sectional view of the engine according to the embodiment.

【図３】ガイド部を示す部分拡大断面図FIG. 3 is a partially enlarged sectional view showing a guide portion.

【図４】図１のＥ矢示方向図FIG. 4 is a view in a direction indicated by an arrow E in FIG. 1;

【図５】作動回転前（プリロード前）の状態を示す図１
の５−５線断面図FIG. 5 shows a state before an operation rotation (before preloading).
5-5 section view

【図６】プリロード時における図５の同様図FIG. 6 is a view similar to FIG. 5 at the time of preloading;

【図７】従来例のプリロードを発生させる状態を示す模
式図FIG. 7 is a schematic diagram showing a state in which a preload is generated in a conventional example.

【図８】従来例のねじりコイルスプリングが巻線部で重
なる状態を示す断面図FIG. 8 is a cross-sectional view showing a state in which a conventional torsion coil spring overlaps a winding portion.

【符号の説明】[Explanation of symbols]

２：クランク軸、４：回転軸、５：プライマリドライブ
歯車、６：副歯車、７：リテーナ、２５：ガイド部、３
０：ねじりコイルスプリング2: crankshaft, 4: rotary shaft, 5: primary drive gear, 6: auxiliary gear, 7: retainer, 25: guide section, 3
0: Torsion coil spring

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】同一回転軸上へ隣り合わせに配設された主
歯車と副歯車の間に位相差を設け、かつ前記回転軸と一
体回転するように設けられたリテーナと副歯車との間へ
ねじりコイルスプリングを介装し、このねじりコイルス
プリングにより前記位相差が解消される方向へ副歯車を
回動付勢することによりプリロードを与え、相手歯車と
の噛み合い騒音を低減するようにした歯車騒音防止装置
において、前記ねじりコイルスプリングの内周側を支持
するためのガイド部を前記リテーナに設けたことを特徴
とする歯車騒音防止装置。1. A phase difference is provided between a main gear and a sub-gear arranged adjacently on the same rotary shaft, and between a retainer and a sub-gear provided to rotate integrally with the rotary shaft. Gear noise in which a torsion coil spring is interposed, and a preload is given by rotating and biasing the sub gear in a direction in which the phase difference is eliminated by the torsion coil spring, thereby reducing mesh noise with a mating gear. A gear noise prevention device, wherein a guide portion for supporting an inner peripheral side of the torsion coil spring is provided on the retainer. 【請求項２】前記ガイド部とリテーナの間隔をＤ、ねじ
りコイルスプリングの線径をｄとしたとき、Ｄ＜２ｄで
あることを特徴とする請求項１に記載した歯車騒音防止
装置。2. The gear noise prevention device according to claim 1, wherein D <2d, where D is the distance between the guide portion and the retainer, and d is the wire diameter of the torsion coil spring.
JP07100798A 1998-03-19 1998-03-19 Gear noise prevention device Expired - Fee Related JP3319718B2 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP07100798A JP3319718B2 (en) 1998-03-19 1998-03-19 Gear noise prevention device
TW087121550A TW417012B (en) 1998-03-19 1998-12-23 Device for preventing gear noise
CN99101346A CN1107179C (en) 1998-03-19 1999-01-22 Device for preventing gear noise
BR9902213-3A BR9902213A (en) 1998-03-19 1999-03-18 Gear noise prevention system
KR1019990009405A KR100324251B1 (en) 1998-03-19 1999-03-19 Apparatus for preventing a noise of a toothed wheel
IDP990242A ID22258A (en) 1998-03-19 1999-03-19 DENTAL WHEEL PREVENTION SYSTEM

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP07100798A JP3319718B2 (en) 1998-03-19 1998-03-19 Gear noise prevention device

Publications (2)

Publication Number Publication Date
JPH11270656A true JPH11270656A (en) 1999-10-05
JP3319718B2 JP3319718B2 (en) 2002-09-03

Family

ID=13448027

Family Applications (1)

Application Number Title Priority Date Filing Date
JP07100798A Expired - Fee Related JP3319718B2 (en) 1998-03-19 1998-03-19 Gear noise prevention device

Country Status (6)

Country Link
JP (1) JP3319718B2 (en)
KR (1) KR100324251B1 (en)
CN (1) CN1107179C (en)
BR (1) BR9902213A (en)
ID (1) ID22258A (en)
TW (1) TW417012B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100481291B1 (en) * 2001-12-26 2005-04-07 대림자동차공업주식회사 Apparatus for preventing a gear noise of motorcycle

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100368705C (en) * 2004-01-28 2008-02-13 重庆力帆实业（集团）有限公司 Noise reduction apparatus for engine clutches and gears
JP4053528B2 (en) * 2004-09-07 2008-02-27 本田技研工業株式会社 Scissor gear
CN102192303B (en) * 2011-06-22 2013-11-06 株洲齿轮有限责任公司 Method for calculating engagement noises of spiral bevel gear pair
CN102359572B (en) * 2011-09-28 2015-08-26 四川省眉山市东升齿轮有限公司 A kind of Double-row gap gear
US9010209B2 (en) * 2012-03-05 2015-04-21 Caterpillar Inc. Scissors gear assembly

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100481291B1 (en) * 2001-12-26 2005-04-07 대림자동차공업주식회사 Apparatus for preventing a gear noise of motorcycle

Also Published As

Publication number Publication date
KR100324251B1 (en) 2002-02-21
TW417012B (en) 2001-01-01
JP3319718B2 (en) 2002-09-03
CN1107179C (en) 2003-04-30
BR9902213A (en) 1999-12-28
ID22258A (en) 1999-09-23
KR19990078079A (en) 1999-10-25
CN1229889A (en) 1999-09-29

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