JPS61223368A - Vibration damping gear - Google Patents
Vibration damping gearInfo
- Publication number
- JPS61223368A JPS61223368A JP6373085A JP6373085A JPS61223368A JP S61223368 A JPS61223368 A JP S61223368A JP 6373085 A JP6373085 A JP 6373085A JP 6373085 A JP6373085 A JP 6373085A JP S61223368 A JPS61223368 A JP S61223368A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- synthetic resin
- metal
- tooth
- disposed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明は、衝撃緩衝機能や振動減衰機能を有する割振歯
車に関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to an allocation gear having a shock absorbing function and a vibration damping function.
〈゛従来の技術〉
回転動力伝達系において、増減速等を行う場合に使用さ
れる歯車は、一般に材料強度的及び歯車寿命等の観点か
ら鋼等の金属製、のものが使われることが多い。特に、
・伝達ト〃りの大きな歯車では歯面の強度増加のために
浸炭や窒化等の表面処理が施され、歯面を非常に硬くし
ている。゛
一方、歯車を含む動力伝達系においては歯車の噛み合い
率が整数ではなく、製作や組立誤差等に′よる歯車の噛
み合い状態の変動かある上、エンジン中モータ等の駆動
機械或いは圧縮機や剪断機等の被部5動機械やカップリ
ング部等の各部でトルク脈動を生じ、これが伝達すべき
設定トルクに重畳された形で系内を伝わってゆく6
′
〈発明が解決しようとする問題点〉
通常、動力伝達系内ではねじシ振動が発生し1.特に共
振時や軽負荷時には相互に噛み合う歯車間で肯、面分離
を伴う振動が起こp、歯面への衝撃荷重の増大と同時に
衝撃音の増大を来たす・。これ等の問題は衝撃緩衝機能
や振 □動減衰機能の小さい金属製の歯車で顕著
であ ゛る。<Conventional technology> In a rotary power transmission system, gears used for speeding up and slowing down are generally made of metal such as steel from the viewpoint of material strength and gear life. . especially,
・For gears with large transmission torque, surface treatments such as carburizing and nitriding are applied to increase the strength of the tooth surfaces, making them extremely hard.゛On the other hand, in a power transmission system that includes gears, the meshing ratio of the gears is not an integer, and the meshing state of the gears may fluctuate due to manufacturing or assembly errors. Torque pulsations occur in various parts such as moving machines and coupling parts, and this is transmitted through the system in a form superimposed on the set torque to be transmitted6.
<Problems to be solved by the invention> Normally, screw vibration occurs within the power transmission system. Particularly during resonance or light loads, vibrations occur between gears that mesh with each other, accompanied by surface separation, which increases the impact load on the tooth surfaces and simultaneously increases the impact noise. These problems are most noticeable with metal gears that have low impact buffering and vibration damping functions.
本発明はかか、る知見に基づき、衝撃緩衝機能及び振動
減衰機能に優れた高トルク伝達用の制振歯車を提供する
ことを目的とする。Based on this knowledge, the present invention aims to provide a vibration damping gear for high torque transmission that has excellent shock buffering and vibration damping functions.
〈問題点を解決するための手段〉
本発明の割振歯車は、金属製歯車の側方にとの金属製歯
車の回転方向に有効に作用するばね要素を介して環状の
合成樹脂製歯車を配設し、前記金属製歯車と一体の回転
軸に対して相対回転自在に嵌合されたこの合成樹脂製歯
車を前記金属製歯車に対して任意の位相に固定し得る手
段が設けられたことを特徴とするものである。<Means for Solving the Problems> The allocation gear of the present invention has an annular synthetic resin gear disposed on the side of the metal gear via a spring element that effectively acts in the rotational direction of the metal gear. and a means for fixing the synthetic resin gear, which is fitted to the metal gear so as to be rotatable relative to the rotating shaft integral with the metal gear, at an arbitrary phase with respect to the metal gear. This is a characteristic feature.
〈作用〉
―
金属製歯車に対して合成樹脂製歯車を相対回転させ、金
属製歯車の歯面に対して合成樹脂製歯車の歯面をばね要
素によりその回転方向に突出させるが、この突出量は位
相調整手段によシ行われる。従って、この歯車はまず合
成樹脂製歯車の部分がこれと噛み合う他の歯車に当接し
て弾性変形し、次いで金属製歯車の部分が他の歯車に当
接する。この弾性変形により、衝撃緩衝機能や振動減衰
機能が発生する。<Operation> - The synthetic resin gear is rotated relative to the metal gear, and the tooth surface of the synthetic resin gear is caused to protrude in the direction of rotation by a spring element relative to the tooth surface of the metal gear, but the amount of this protrusion is is performed by the phase adjustment means. Therefore, in this gear, the synthetic resin gear portion first comes into contact with another gear that meshes with it and is elastically deformed, and then the metal gear portion comes into contact with the other gear. This elastic deformation generates a shock buffering function and a vibration damping function.
〈実施□例〉
本発明による制振歯車の一実施例の断面構造を表す第1
図及びその右側面形状を表す第2図及びその■矢視形状
を拡大した第3図に示すように、歯車軸1とこの歯車軸
1と一体に形成された金属製歯車2とは、本実施例では
一体成形したものであるが、これらを別々に作っておき
、キーやスプライン或いは焼ばめ等の他の結合法によっ
て一体化するようにしても良い。金属製歯車2の歯3は
本実施例のような平歯車の他に、傘歯車やねじれ歯車等
の他の形式の歯車についても同様に適用できる。金属製
歯車20回転方向に作用するねじ夛ばね等のばね要素4
は、その一端が金属製歯車2或いは歯車軸1に結合され
、他端はナイロンやポリプロピレン等の弾性を有する合
成樹脂製歯車5に結合されており、合成ゴム等の他につ
るまきばねや板ばね或いはコイルばね及びこれ等の組合
せで構成しても良い。〈Example〉 First example showing the cross-sectional structure of an example of the damping gear according to the present invention
As shown in FIG. 2, which shows the right side shape of the figure, and FIG. 3, which is an enlarged view of the shape viewed from the In the embodiment, they are integrally molded, but they may be made separately and integrated using other joining methods such as keys, splines, or shrink fitting. The teeth 3 of the metal gear 2 can be applied to other types of gears, such as bevel gears and helical gears, in addition to spur gears as in this embodiment. Metal gear 20 Spring element 4 such as a screw spring that acts in the rotational direction
is connected at one end to a metal gear 2 or gear shaft 1, and at the other end to a gear 5 made of elastic synthetic resin such as nylon or polypropylene. It may be constructed of a spring, a coil spring, or a combination thereof.
従って、はね要素7の軸方向の厚みは特に問題ではない
。歯車軸1に回転自在に嵌合された環状の合成樹脂製歯
車5は金属製歯車2と同一条件の歯6を有しているが、
その歯幅は金属製歯車2の1/3〜1/2程度にするこ
とが多い。しかし、特にこの値に限定するものではなく
、その軸方向の摺動を阻止す゛るストッパを付加するこ
とも可能であ゛る。合成樹脂製歯車5の歯6は図示しな
い一方の歯車に対する作用力の方向に金属製歯車2の歯
3よりも突出するようにはね要素4によシ金属製歯車2
の円周方向に少しずらして配設しである。Therefore, the axial thickness of the spring element 7 is not a particular problem. The annular synthetic resin gear 5 rotatably fitted to the gear shaft 1 has teeth 6 having the same conditions as the metal gear 2.
The tooth width is often about 1/3 to 1/2 that of the metal gear 2. However, the value is not particularly limited to this value, and it is also possible to add a stopper to prevent sliding in the axial direction. The teeth 6 of the synthetic resin gear 5 are attached to the metal gear 2 by the spring element 4 so that they protrude beyond the teeth 3 of the metal gear 2 in the direction of the force acting on one gear (not shown).
They are arranged slightly offset in the circumferential direction.
金属製歯車2の歯3の歯面に対する合成樹脂製歯車5の
歯6の歯面の′突出量δは数マイクロメートルから数百
マイクロメニトルに設定することが多いが、通常、合成
樹脂製歯車5の歯6は少し太き目の歯先修正がなされる
。The amount of protrusion δ of the tooth surface of the tooth 6 of the synthetic resin gear 5 with respect to the tooth surface of the tooth 3 of the metal gear 2 is often set to several micrometers to several hundred micrometers. The tips of the teeth 6 of the gear 5 are modified to make them slightly thicker.
なお、ばね要素4を介してこの突出量δを良・ 好に設
定できない場合には、金属製歯車2の歯3に対して合成
樹脂製歯車5の歯6の歯厚を数マイクロメートルから数
十マイクロメートル太き目に加工することも可能である
。要するに、金属製歯車2と合成樹脂製歯車8と □は
同一歯形条件゛である必要はなく、突出量δの調節や長
時間使用後のこの突出量δの調整 □等が実際
の使用に当って重要であp、このための調節機構の一例
を表す第4図に示すように、抑圧ブロック10は合成□
樹脂製歯車5の側端面属一体的に結合されて円周方向の
一面□に斜面11を有しておシ、この斜面11とスライ
ドブロック12に形成された斜面13とが摺動可能に接
触している。スライドブロック12は歯車軸1に一端を
支持された伸縮アーム14により軸方向に移動可能であ
シ、従ってスライドブロック12を第4図中、左方向に
所望量動゛かせば、合成樹脂製歯車5が金属・製・歯車
2に対して相手歯車対する作用力の方向と反対の方向に
所望角度相対回転し1、金属製歯車2の歯□面に対する
高分子製歯車5の歯面の突出量δを適正な値に設定する
ことができる。なお、ばね要素4の効果を減殺してしま
わないように合成樹脂製歯車5と抑圧ブロック10との
結合部に回転方向に弾性変形するばね要素を介在させる
ことも可能である。In addition, if this protrusion amount δ cannot be properly set via the spring element 4, the tooth thickness of the teeth 6 of the synthetic resin gear 5 should be adjusted from several micrometers to several micrometers relative to the teeth 3 of the metal gear 2. It is also possible to process it to a thickness of 10 micrometers. In short, it is not necessary that the metal gear 2 and the synthetic resin gear 8 and □ have the same tooth profile conditions, and it is necessary to adjust the protrusion amount δ and adjust the protrusion amount δ after long-term use, etc. in actual use. As shown in FIG. 4, which shows an example of an adjustment mechanism for this purpose, the suppression block 10
The side end surfaces of the resin gear 5 are integrally connected and have a slope 11 on one surface □ in the circumferential direction, and this slope 11 and a slope 13 formed on the slide block 12 are slidably in contact with each other. are doing. The slide block 12 is movable in the axial direction by a telescoping arm 14 whose one end is supported by the gear shaft 1. Therefore, by moving the slide block 12 a desired amount to the left in FIG. 4, the synthetic resin gear can be moved. 5 is made of metal and rotates relative to the gear 2 at a desired angle in the direction opposite to the direction of the force acting on the mating gear 1, and the amount of protrusion of the tooth surface of the polymer gear 5 relative to the tooth surface of the metal gear 2 δ can be set to an appropriate value. In addition, in order not to reduce the effect of the spring element 4, it is also possible to interpose a spring element that is elastically deformed in the rotational direction at the joint between the synthetic resin gear 5 and the suppression block 10.
本実施例の制振歯車は相互に噛み合う歯車のうちの少な
くとも一方に適用する。例えば、駆動系内で発生する各
種トルク脈動によシ歯車系はねじシ振動又はねじ9曲げ
振動を起こすが、定常噛み合い時に必ず合成樹脂製歯車
5が先に当たるため、噛み合い衝撃が緩和されてトルク
脈動そのものが小さくなる。又、・
合成樹脂製歯車5の材料減衰中ばね要素4自体の材料及
び構造減衰効果により振動エネルギが吸収され、振動レ
ベルを低減させることができるが、これは特に共振時に
有効である。The vibration damping gear of this embodiment is applied to at least one of the gears that mesh with each other. For example, various torque pulsations that occur in the drive system cause screw vibration or screw bending vibration in the gear system, but since the synthetic resin gear 5 always hits first during steady meshing, the meshing impact is alleviated and the torque is increased. The pulsation itself becomes smaller. Also, during the material damping of the synthetic resin gear 5, vibration energy is absorbed by the material and structural damping effect of the spring element 4 itself, making it possible to reduce the vibration level, which is particularly effective during resonance.
更に、歯面分離振動時にはまず合成樹脂製歯車5が先に
衝突するため、緩衝効果を生じて金属製歯車2への衝撃
が弱まシ、応力的にも有利となって叩き音も緩和される
。なお、軽負荷時には合成樹脂製歯車5部分のみの駆動
も可能であり、割振及び低騒音化できる。Furthermore, during tooth surface separation vibration, the synthetic resin gear 5 collides first, which creates a buffering effect and weakens the impact on the metal gear 2, which is advantageous in terms of stress and reduces knocking noise. Ru. In addition, when the load is light, it is also possible to drive only the 5 parts of the synthetic resin gear, which can reduce vibration and reduce noise.
〈発明の効果〉
本発明によれば、金属製歯車に対して合成樹脂製歯車を
相対回転させて所望位置に固定できるので、金属製歯車
の歯面からの合成樹脂製歯車の歯面の突出量を適正な値
に調節できる。そして、定常噛み合い時には合成樹脂製
歯車の弾性変形によシ噛み合い衝撃が緩和されてトルク
脈動そのものを小さくできる。<Effects of the Invention> According to the present invention, since the synthetic resin gear can be rotated relative to the metal gear and fixed at a desired position, the protrusion of the tooth surface of the synthetic resin gear from the tooth surface of the metal gear can be avoided. The amount can be adjusted to an appropriate value. During steady meshing, the meshing impact is alleviated by the elastic deformation of the synthetic resin gears, and the torque pulsation itself can be reduced.
又、合成樹脂製歯車及びばね要素によシ振動エネルギが
吸収されて振動レベルが低減する。Also, vibration energy is absorbed by the synthetic resin gears and spring elements, reducing the vibration level.
この現象は特に共振時に有効である。又、歯面分離振動
時には合成樹脂製歯車によシ緩衝効果を生じて金属製歯
車への衝撃が弱まシ、応力的にも有利となって叩き音も
緩和される。This phenomenon is particularly effective during resonance. In addition, during tooth surface separation vibration, the synthetic resin gear produces a buffering effect, weakening the impact on the metal gear, which is advantageous in terms of stress, and the knocking noise is also alleviated.
又、軽負荷時には合成樹脂製歯車部分のみの駆動も可能
で、割振及び低騒音化に有効である。Also, when the load is light, it is possible to drive only the synthetic resin gear part, which is effective in allocating vibration and reducing noise.
第1図は本発明の一実施例の断面図、第2図はその右側
面図、第3図はその■矢視拡大図、第4図は突出量δの
調節機構の一例を表す概念図である。
又、図中の符号で1は歯車軸、2は金属製歯車、3,6
は歯、4はばね要素、5は合成樹脂製歯車、10は抑圧
ブロック、12はスライドブロック、11.13は斜面
、14は伸縮アーム、δは金属製歯車の歯面に対する合
成樹脂製歯車の歯面の突出量である。
特許出願人 三菱重工業株式会社
復代理人弁理士 元方 士 部(他1名)第1図
第2図
2 、m
(○。
第3図Fig. 1 is a cross-sectional view of one embodiment of the present invention, Fig. 2 is a right side view thereof, Fig. 3 is an enlarged view of the same in the direction of the ■ arrow, and Fig. 4 is a conceptual diagram showing an example of a mechanism for adjusting the protrusion amount δ. It is. Also, in the figures, 1 is a gear shaft, 2 is a metal gear, 3, 6
is a tooth, 4 is a spring element, 5 is a synthetic resin gear, 10 is a suppression block, 12 is a slide block, 11.13 is a slope, 14 is a telescopic arm, δ is the synthetic resin gear relative to the tooth surface of the metal gear This is the amount of tooth surface protrusion. Patent Applicant: Mitsubishi Heavy Industries, Ltd. Patent Attorney, Patent Attorney, Motogata (and 1 other person) Figure 1 Figure 2 Figure 2, m (○. Figure 3
Claims (1)
に作用するばね要素を介して環状の合成樹脂製歯車を配
設し、前記金属製歯車と一体の回転軸に対して相対回転
自在に嵌合されたこの合成樹脂製歯車を前記金属製歯車
に対して任意の位相に固定し得る手段が設けられたこと
を特徴とする制振歯車。An annular synthetic resin gear is disposed on the side of the metal gear via a spring element that effectively acts in the direction of rotation of the metal gear, and is rotatable relative to the rotating shaft integrated with the metal gear. A vibration damping gear, characterized in that means is provided for fixing the synthetic resin gear fitted to the metal gear in an arbitrary phase with respect to the metal gear.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP60063730A JP2575615B2 (en) | 1985-03-29 | 1985-03-29 | Damping gear |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP60063730A JP2575615B2 (en) | 1985-03-29 | 1985-03-29 | Damping gear |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS61223368A true JPS61223368A (en) | 1986-10-03 |
JP2575615B2 JP2575615B2 (en) | 1997-01-29 |
Family
ID=13237810
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP60063730A Expired - Lifetime JP2575615B2 (en) | 1985-03-29 | 1985-03-29 | Damping gear |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2575615B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6880249B2 (en) * | 2002-01-15 | 2005-04-19 | John W. Long | Molded plastic blade holder |
EP1748226A1 (en) * | 2005-07-28 | 2007-01-31 | Rudolf Schwarz GmbH & Co. KG | Gear with backlash compensation |
JP2010204100A (en) * | 2009-03-03 | 2010-09-16 | Montres Jaquet Droz Sa | Uncoupling device for timepiece mechanism, and timepiece having the same |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4417851Y1 (en) * | 1965-07-30 | 1969-08-02 | ||
JPS51108151A (en) * | 1975-03-07 | 1976-09-25 | Gd Spa | |
JPS5793652U (en) * | 1980-11-28 | 1982-06-09 |
-
1985
- 1985-03-29 JP JP60063730A patent/JP2575615B2/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4417851Y1 (en) * | 1965-07-30 | 1969-08-02 | ||
JPS51108151A (en) * | 1975-03-07 | 1976-09-25 | Gd Spa | |
JPS5793652U (en) * | 1980-11-28 | 1982-06-09 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6880249B2 (en) * | 2002-01-15 | 2005-04-19 | John W. Long | Molded plastic blade holder |
EP1748226A1 (en) * | 2005-07-28 | 2007-01-31 | Rudolf Schwarz GmbH & Co. KG | Gear with backlash compensation |
JP2010204100A (en) * | 2009-03-03 | 2010-09-16 | Montres Jaquet Droz Sa | Uncoupling device for timepiece mechanism, and timepiece having the same |
Also Published As
Publication number | Publication date |
---|---|
JP2575615B2 (en) | 1997-01-29 |
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