JPH0953690A - Planetary gears - Google Patents
Planetary gearsInfo
- Publication number
- JPH0953690A JPH0953690A JP21044095A JP21044095A JPH0953690A JP H0953690 A JPH0953690 A JP H0953690A JP 21044095 A JP21044095 A JP 21044095A JP 21044095 A JP21044095 A JP 21044095A JP H0953690 A JPH0953690 A JP H0953690A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- planetary
- gears
- meshing
- sun
- 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.)
- Pending
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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Processing (AREA)
- Retarders (AREA)
- Gears, Cams (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、ポンプ、撹拌機、石炭
ミル、圧縮機、航空機、風車等に用いられる遊星歯車装
置に係り、特に振動・騒音の低減に有効な歯形に形成さ
れた遊星歯車装置及びその製造方法に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear unit used in pumps, agitators, coal mills, compressors, aircrafts, wind turbines, etc., and more particularly to a planetary gear having a tooth profile effective for reducing vibration and noise. The present invention relates to a gear device and a manufacturing method thereof.
【０００２】[0002]
【従来の技術】動力伝達用の遊星歯車装置では、遊星歯
車が複数個（Ｎ個）あり、その各遊星歯車と噛み合う太
陽歯車及び内歯車の歯数を各々Ｚｓ、Ｚｉとすると、 （Ｚｓ＋Ｚｉ）／Ｎ ＝ 整数 という関係がある。このとき、ＺｓとＺｉがともにＮの
倍数であると、従来の遊星歯車装置では、平歯車の場合
はもちろん、はすば歯車の場合でも各遊星歯車の歯幅が
等しいため、各遊星歯車と太陽歯車が噛み合い始めるタ
イミング及び噛み合い終るタイミングは、各遊星歯車に
おいて同じになる。各遊星歯車と内歯車の噛み合いで
も、噛み合い始めと噛み合い終りは逆になるが、噛み合
い始めるタイミング及び噛み合い終るタイミングに関し
ては同様なことがいえる。その結果、噛み合い始め及び
噛み合い終りに太陽歯車及び内歯車に加わる衝撃はＮ倍
になり、遊星歯車装置の振動及び騒音が大きくなるとい
った問題点があった。なお、この種のものとして、例え
ば、特開昭６３−１８０７６６号公報が挙げられる。2. Description of the Related Art In a planetary gear device for power transmission, there are a plurality of (N) planetary gears, and if the number of teeth of the sun gear and the internal gear that mesh with each planetary gear are Zs and Zi, respectively, (Zs + Zi) There is a relationship of / N = integer. At this time, when both Zs and Zi are multiples of N, in the conventional planetary gear device, not only in the case of the spur gear but also in the case of the helical gear, the tooth widths of the respective planetary gears are equal, so that The timing at which the sun gears start meshing and the timing at which meshing ends are the same for each planetary gear. Even when the planetary gears and the internal gear mesh with each other, the meshing start and meshing end are opposite, but the same can be said with respect to the meshing start timing and meshing end timing. As a result, the impact applied to the sun gear and the internal gear at the beginning of meshing and at the end of meshing becomes N times, and there is a problem that vibration and noise of the planetary gear device become large. As this type, for example, JP-A-63-180766 can be cited.
【０００３】[0003]
【発明が解決しようとする課題】動力伝達用の遊星歯車
装置では低振動・低騒音化の要求が厳しくなっており、
その実現が大きな課題となっている。その負荷運転中の
騒音の大きさを支配するのは歯車の噛み合い音である。
歯車の噛み合い音を低く抑えることにより、遊星歯車装
置全体の騒音レベルを低くすることができる。歯車の噛
み合い音を低くするためには、歯車の精度を良くするこ
とが最も効果的であることが良く知られている。しか
し、歯車の精度を良くしても負荷運転中の騒音を下げる
には限界がある。これは負荷がかかることにより弾性体
である歯が撓んでスム−ズな回転ができないためであ
る。特に、前記従来技術で説明した遊星歯車装置では、
噛み合い時の衝撃がＮ倍となり、低振動・低騒音化の厳
しい要求に答えるには不十分である。In the planetary gear device for power transmission, there are increasing demands for low vibration and low noise.
The realization of this has become a major issue. It is the meshing noise of gears that controls the noise level during load operation.
By suppressing the gear meshing noise to be low, the noise level of the entire planetary gear device can be lowered. It is well known that improving the precision of gears is the most effective in reducing the gear engagement noise. However, even if the accuracy of the gear is improved, there is a limit in reducing the noise during load operation. This is because the teeth, which are elastic bodies, bend when a load is applied and smooth rotation cannot be performed. Particularly, in the planetary gear device described in the above-mentioned prior art,
The impact at the time of meshing is N times, which is insufficient to meet the strict requirements for low vibration and low noise.
【０００４】本発明の目的は、歯車の噛み合い時に発生
する衝撃振動を低減することにより、振動・騒音の低い
遊星歯車装置及びその製造方法を提供することにある。An object of the present invention is to provide a planetary gear device with low vibration and noise and a method for manufacturing the same by reducing the impact vibration generated when the gears mesh with each other.
【０００５】[0005]
【課題を解決するための手段】上記目的は、太陽歯車、
この太陽歯車と噛み合う複数個の遊星歯車及びこの遊星
歯車と噛み合う内歯車のそれぞれの歯形をインボリュ−
ト曲線で形成するはすば歯車、及びこれらを収納するケ
−スを備え、前記太陽歯車及び内歯車の歯数が遊星歯車
の個数で割り切れる遊星歯車装置において、前記複数個
の各遊星歯車の太陽歯車と噛み合い始める側の歯の側端
面の軸方向位置を順次ずらし、各遊星歯車と太陽歯車が
噛み合い始めるタイミング、及び各遊星歯車と内歯車が
噛み合い終わるタイミングを各遊星歯車において異なる
ようにする、ことにより達成される。The object is to provide a sun gear,
The tooth profile of each of the plurality of planetary gears that mesh with the sun gear and the internal gear that meshes with the planetary gears is involute.
In a planetary gear device that includes a helical gear formed of a curved line and a case that houses them, and the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, The axial positions of the side end faces of the teeth on the side where the sun gear starts to mesh are sequentially shifted so that the timing at which the planet gears and the sun gear start to mesh and the timing at which the planet gears and the internal gear end to mesh are different for each planet gear. It is achieved by
【０００６】又上記目的は、太陽歯車、この太陽歯車と
噛み合う複数個の遊星歯車及びこの遊星歯車と噛み合う
内歯車のそれぞれの歯形をインボリュ−ト曲線で形成す
るはすば歯車、及びこれらを収納するケ−スを備え、前
記太陽歯車及び内歯車の歯数が遊星歯車の個数で割り切
れる遊星歯車装置において、前記複数個の各遊星歯車の
太陽歯車と噛み合い始める側の歯の側端面の軸方向位置
を順次ずらし、各遊星歯車と太陽歯車が噛み合い終わる
タイミング、及び各遊星歯車と内歯車が噛み合い始める
タイミングを各遊星歯車において異なるようにする、こ
とにより達成される。Another object of the present invention is to provide a sun gear, a plurality of planet gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planet gear with an involute curve, and a housing for them. In a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planetary gears, the axial direction of the side end faces of the teeth on the side where the sun gears of the plurality of planetary gears start to mesh. This is achieved by sequentially shifting the positions so that the timing at which the planet gears and the sun gear finish meshing with each other and the timing at which the planet gears and the internal gear start to mesh with each other are different for each planet gear.
【０００７】更に又上記目的は、太陽歯車、この太陽歯
車と噛み合う複数個の遊星歯車及びこの遊星歯車と噛み
合う内歯車のそれぞれの歯形をインボリュ−ト曲線で形
成するはすば歯車、及びこれらを収納するケ−スを備
え、前記太陽歯車及び内歯車の歯数が遊星歯車の個数で
割り切れる遊星歯車装置において、前記複数個の各遊星
歯車の太陽歯車と噛み合い始める側及び噛み合い終わる
側の歯の側端面の軸方向位置を順次ずらし、各遊星歯車
と太陽歯車及び内歯車とが噛み合い始めるタイミング及
び噛み合い終るタイミングを各遊星歯車において異なる
ようにする、ことにより達成される。Still further, the above object is to provide a sun gear, a plurality of planet gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planet gear by an involute curve, and these. In a planetary gear device that has a case to be housed and in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the teeth of the plurality of planet gears on the side that starts meshing with the sun gear and on the side that ends meshing This is achieved by sequentially shifting the axial position of the side end faces so that the timings at which the planetary gears start meshing with the sun gear and the internal gear and the timing at which the meshing ends are different for each planetary gear.
【０００８】更に又上記目的は、太陽歯車、この太陽歯
車と噛み合う複数個の遊星歯車及びこの遊星歯車と噛み
合う内歯車のそれぞれの歯形をインボリュ−ト曲線で形
成するはすば歯車、及びこれらを収納するケ−スを備
え、前記太陽歯車及び内歯車の歯数が遊星歯車の個数で
割り切れる遊星歯車装置において、前記複数個の各遊星
歯車の軸方向の位置をずらして設置し、各遊星歯車と太
陽歯車が噛み合い始めるタイミング及び噛み合い終わる
タイミング及び各遊星歯車と内歯車が噛み合い終わるタ
イミング及び噛み合い始めるタイミングを、各遊星歯車
において異なるようにする、ことにより達成される。Still further, the above object is to provide a sun gear, a plurality of planet gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planet gear by an involute curve, and these. In a planetary gear device including a case to be housed, in which the number of teeth of the sun gear and the internal gear is divisible by the number of planetary gears, the planetary gears are installed by shifting the axial positions of the plurality of planetary gears. And the timing at which the sun gears start meshing with each other and the timing at which they mesh with each other, and the timing at which each planetary gear and the internal gear finishes meshing with each other and the timing at which they start meshing are different for each planetary gear.
【０００９】更に又上記目的は、太陽歯車、この太陽歯
車と噛み合う複数個の遊星歯車及びこの遊星歯車と噛み
合う内歯車のそれぞれ歯形をインボリュ−ト曲線で形成
る平歯車、及びこれらを収納するケ−ス等を備え、前記
太陽歯車及び内歯車の歯数が遊星歯車の個数で割り切れ
る遊星歯車装置において、前記複数個の各遊星歯車の歯
丈を各々異ならせ、各遊星歯車と太陽歯車が噛み合い始
めるタイミング及び各遊星歯車と内歯車が噛み合い終わ
るタイミングを、各遊星歯車において異なるようにす
る、ことにより達成される。Still further, the above object is to provide a sun gear, a plurality of planetary gears that mesh with the sun gear, and a spur gear that forms each tooth profile of an internal gear that meshes with the planetary gear with an involute curve, and a case for housing these. -In a planetary gear device that includes a gear, etc., in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the plurality of planet gears have different tooth lengths, and the planet gears and the sun gear mesh with each other. This is achieved by making the start timing and the timing at which the planetary gears and the internal gears end meshing different for each planetary gear.
【００１０】更に又上記目的は、太陽歯車、この太陽歯
車と噛み合う複数個の遊星歯車及びこの遊星歯車と噛み
合う内歯車のそれぞれの歯形をインボリュ−ト曲線で形
成するはすば歯車、及びこれらを収納するケ−スを備
え、前記太陽歯車及び内歯車の歯数が遊星歯車の個数で
割り切れる遊星歯車装置において、遊星歯車の噛み合い
初めの歯の先端の面取りを行ない、各遊星歯車の面取り
を順次大きくする、ことにより達成される。Still further, the above object is to provide a sun gear, a plurality of planet gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planet gear by an involute curve, and these. In a planetary gear device provided with a case to be housed, in which the number of teeth of the sun gear and the internal gear is divisible by the number of planetary gears, chamfering the tips of the teeth at the beginning of meshing of the planetary gears, and chamfering each planetary gear in order. It is achieved by increasing the size.
【００１１】更に又上記目的は、太陽歯車、この太陽歯
車と噛み合う複数個の遊星歯車及びこの遊星歯車と噛み
合う内歯車のそれぞれの歯形をインボリュ−ト曲線で形
成するはすば歯車、及びこれらを収納するケ−スを備
え、前記太陽歯車及び内歯車の歯数が遊星歯車の個数で
割り切れる遊星歯車装置において、遊星歯車の歯幅を変
えて噛み合うタイミングを順次ずらす、ことにより達成
される。Still further, the above object is to provide a sun gear, a plurality of planet gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planet gear with an involute curve, and these. In a planetary gear device that includes a case to be housed and in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the tooth width of the planet gears is changed to sequentially shift the meshing timing.
【００１２】更に又上記目的は太陽歯、この太陽歯車と
噛み合う複数個の遊星歯車及びこの遊星歯車と噛み合う
内歯車のそれぞれの歯形をインボリュ−ト曲線で形成す
るはすば歯車、及びこれらを収納するケ−スを備え、前
記太陽歯車及び内歯車の歯数が遊星歯車の個数で割り切
れる遊星歯車装置において、遊星歯車の歯幅を全て同じ
にしてセット位置を順次ずらし、噛み合うタイミングを
順次ずらす、ことにより達成される。Still further, the above object is to provide a sun tooth, a plurality of planetary gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planetary gear with an involute curve, and a housing thereof. In a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planetary gears, the planet gears have the same tooth width, and the set positions are sequentially shifted, and the meshing timing is sequentially shifted. It is achieved by
【００１３】[0013]
【作用】はすば歯車からなる遊星歯車装置は、複数個の
遊星歯車の太陽歯車と噛み合い始める側の歯の側端面の
軸方向位置を順次ずらしているので、各遊星歯車と太陽
歯車が噛み合い始めるタイミング、及び各遊星歯車と内
歯車が噛み合い終わるタイミングは各遊星歯車において
異なり、したがって歯車の噛み合い時に発生する衝撃振
動が低減され、装置全体の振動・騒音も低減される。In the planetary gear device composed of helical gears, the axial end positions of the teeth of the planetary gears on the side where they start to mesh with the sun gears are sequentially shifted, so that the planetary gears and the sun gears mesh with each other. The start timing and the timing at which the planetary gears and the internal gears end meshing are different for each planetary gear, and therefore the shock vibration generated when the gears mesh with each other is reduced, and the vibration and noise of the entire device are also reduced.
【００１４】又、はすば歯車からなる遊星歯車装置は、
複数個の遊星歯車の太陽歯車と噛み合い終わる側の歯の
側端面の軸方向位置を順次ずらしているので、各遊星歯
車と太陽歯車が噛み合い終わるタイミング、及び各遊星
歯車と内歯車が噛み合い始めるタイミングは各遊星歯車
において異なり、したがって歯車の噛み合い時に発生す
る衝撃振動を低減でき、装置全体の振動・騒音も低減さ
れる。Further, the planetary gear device consisting of helical gears is
Since the axial positions of the side end surfaces of the teeth of the plurality of planetary gears that end meshing with the sun gear are sequentially shifted, the timing at which each planetary gear and the sun gear end meshing and the timing at which each planetary gear and the internal gear start meshing Is different in each planetary gear, and therefore, shock vibration generated when the gears are meshed can be reduced, and vibration and noise of the entire device can be reduced.
【００１５】更に又、はすば歯車からなる遊星歯車装置
は、複数個の遊星歯車の太陽歯車と噛み合い始める側及
び噛み合い終わる側の歯の側端面の軸方向位置を順次ず
らしているので、各遊星歯車と太陽歯車が噛み合い始め
るタイミングと噛み合い終わるタイミング、及び各遊星
歯車と内歯車が噛み合い終わるタイミングと噛み合い始
めるタイミングは各遊星歯車において異なりしたがっ
て、歯車の噛み合い時に発生する衝撃振動を低減でき、
装置全体の振動・騒音も低減される。Further, in the planetary gear device including helical gears, the axial positions of the side end faces of the teeth of the plurality of planetary gears on the side where the meshing with the sun gear starts and the side where the meshing ends are sequentially shifted. The timing at which the planetary gears and the sun gear start to mesh and the timing at which they mesh, and the timing at which the planetary gears and the internal gear finish meshing and the timing at which they start meshing differ for each planetary gear.
Vibration and noise of the entire device are also reduced.
【００１６】更に又、はすば歯車からなる遊星歯車装置
は、複数個の各遊星歯車の軸方向の位置をずらして設置
し、各遊星歯車と太陽歯車が噛み合い始めるタイミング
と噛み合い終るタイミング及び各遊星歯車と内歯車が噛
み合い終るタイミングと噛み合い始めるタイミングを各
遊星歯車において異なるようにしたので、歯車の噛み合
い時に発生する衝撃振動を低減でき、装置全体の振動・
騒音も低減される。Furthermore, the planetary gear device comprising helical gears is installed by shifting the axial position of each of the plurality of planetary gears, and the timings at which the planetary gears and the sun gears start meshing with each other and the timings at which the meshing ends. The timing at which the planetary gears and the internal gears finish meshing and the timing at which they start meshing are made different for each planetary gear, so shock vibrations that occur during gear meshing can be reduced, and the vibration of the entire device can be reduced.
Noise is also reduced.
【００１７】更に又、平歯車からなる遊星歯車装置は、
複数個の各遊星歯車の歯丈を各々異なるようにしたの
で、各遊星歯車と太陽歯車の噛み合い始めのタイミング
及び各遊星歯車と内歯車の噛み合い終りのタイミングを
ずらせることができ、歯車の噛み合い時に発生する衝撃
振動を低減でき、装置全体の振動・騒音も低減される。Furthermore, a planetary gear device consisting of spur gears,
Since the tooth heights of the multiple planetary gears are made different, it is possible to shift the timing of the start of meshing between each planetary gear and the sun gear and the timing of the end of meshing between each planetary gear and the internal gear. The impact vibration that sometimes occurs can be reduced, and the vibration and noise of the entire device are also reduced.
【００１８】[0018]
【実施例】まず、実施例の説明に先立って基本的な考え
方について説明する。EXAMPLES First, a basic concept will be described prior to the description of examples.
【００１９】図１に示すように、はすば歯車の噛み合い
では、駆動される歯車（遊星減速機の場合、遊星歯車）
には噛み合い初め側の歯の端面の歯の先端に噛み合い線
が現われ、次第に（１）→（２）→（３）→（４）のよ
うに移動し、噛み合い終わり側の歯元の部分で噛み合い
線は振動、騒音の原因となる衝撃は主として、この噛み
合い初めと終わりに起きるから、例えば３個の遊星歯車
がある場合、３個の遊星歯車が同時に噛み合いが始まる
のを避ける。As shown in FIG. 1, in the meshing of helical gears, a driven gear (in the case of a planetary speed reducer, a planetary gear)
A meshing line appears at the tip of the tooth on the end face of the meshing start side, and it gradually moves as (1) → (2) → (3) → (4), and at the tooth base part on the meshing end side. Since the meshing line mainly causes shocks that cause vibration and noise at the beginning and the end of this meshing, for example, when there are three planetary gears, avoiding simultaneous meshing of the three planetary gears.
【００２０】以下、本発明の第一の実施例を図２、図３
及び図４により具体的に説明する。本実施例ははすば歯
車を用いた遊星歯車装置の例である。Hereinafter, the first embodiment of the present invention will be described with reference to FIGS.
A detailed description will be given with reference to FIG. The present embodiment is an example of a planetary gear device using a helical gear.
【００２１】まず、図３によって本実施例の主要部であ
る遊星歯車部の構成について説明する。中心には太陽歯
車１があり、この太陽歯車１は、３個の遊星歯車２ａ、
２ｂ、２ｃと噛み合っている。遊星歯車全体をいう場合
は遊星歯車２と称する。本実施例では最も一般的な遊星
歯車３個の場合を図示しているが、実際には２〜６個の
ものも使用されている。First, the structure of the planetary gear unit, which is the main part of this embodiment, will be described with reference to FIG. At the center is the sun gear 1, which is composed of three planet gears 2a,
It meshes with 2b and 2c. When referring to the entire planetary gear, it is referred to as the planetary gear 2. In this embodiment, the most common case of three planetary gears is shown, but actually two to six gears are also used.
【００２２】遊星歯車２は外側で内歯車５と噛み合って
おり、遊星歯車２はそれぞれ遊星ピン３のまわりを自転
することができる。また、ピン３はキャリヤ−４によ
り、遊星歯車２の個数、本実施例では３等分（または不
等分）に配置されている。太陽歯車１と内歯車５の歯数
の和は３の整数倍であり、太陽歯車１と内歯車５の歯数
は、ともに３の整数倍となっている。The planetary gear 2 meshes with the internal gear 5 on the outer side, and each of the planetary gears 2 can rotate around the planetary pin 3. Further, the pins 3 are arranged by the carrier 4 in the number of the planetary gears 2, that is, in the present embodiment, in three equal parts (or in equal parts). The sum of the number of teeth of the sun gear 1 and the internal gear 5 is an integer multiple of 3, and the number of teeth of the sun gear 1 and the internal gear 5 is an integer multiple of 3.
【００２３】一般の遊星歯車装置では内歯車５はその回
転を固定されており、太陽歯車１を入力軸とするとき
は、遊星歯車２の公転、すなわちキャリヤ−４の回転を
出力軸とする、いわゆる減速機とするか、またはその逆
にキャリヤ−４を入力軸として、太陽歯車１を出力軸と
する増速機として使用する場合がある。In a general planetary gear device, the internal gear 5 has its rotation fixed, and when the sun gear 1 is the input shaft, the revolution of the planetary gear 2, that is, the rotation of the carrier-4 is the output shaft. There is a case where it is used as a so-called speed reducer or, conversely, it is used as a speed increaser which uses the carrier-4 as an input shaft and the sun gear 1 as an output shaft.
【００２４】また他の方法として、キャリヤ−４を固
定、すなわち遊星歯車２は自転のみ行ない公転を行なわ
ない機構も一般的に採用されている。この場合、太陽歯
車１を入力軸とすれば、これと噛み合う遊星歯車２は自
転のみするから、内歯車５が太陽歯車１とは反対方向に
回転し、内歯車５が出力軸となり減速機として機能す
る。逆に内歯車５を入力軸とすれば、太陽歯車１は反対
方向に回転し増速機となる。As another method, a mechanism in which the carrier 4 is fixed, that is, the planetary gear 2 only rotates and does not revolve is generally adopted. In this case, if the sun gear 1 is used as the input shaft, the planetary gear 2 meshing with the sun gear 1 rotates only on its own axis, so that the internal gear 5 rotates in the opposite direction to the sun gear 1, and the internal gear 5 becomes the output shaft and serves as a reduction gear. Function. Conversely, if the internal gear 5 is used as the input shaft, the sun gear 1 rotates in the opposite direction and functions as a gearbox.
【００２５】本発明は回転を固定されるのが内歯車５で
あるか、キャリヤ−４であるか、また、増速機として使
用するか減速機として使用するかは関係なく、いずれの
場合にも適用できる。In the present invention, it is irrelevant whether the rotation is fixed by the internal gear 5 or the carrier-4, and whether it is used as a speed increaser or a speed reducer. Can also be applied.
【００２６】遊星歯車装置全体の構成を図４によって説
明する。図４は一例としてキャリヤ−４を固定した場合
の構造を示したものである。The overall structure of the planetary gear device will be described with reference to FIG. FIG. 4 shows the structure in which the carrier 4 is fixed as an example.
【００２７】前述した如く本発明は減速機として使用す
る場合にも、あるいは増速機として使用する場合にも適
用可能であるが、本実施例では減速機として使用する場
合について説明する。As described above, the present invention can be applied to the case where it is used as a speed reducer or the case where it is used as a speed up gear, but in this embodiment, the case where it is used as a speed reducer will be described.
【００２８】本実施例では太陽歯車１と入力軸６は一体
となっているが、別ピ−スとなっていても差し支えな
い。入力軸６は入力軸受８及びパイロット軸受１１によ
り支持され、その一端にはカップリング（図示せず）を
介し電動機等の原動機（図示せず）が連結されている。
遊星ピン３は前後端をキャリヤ−４に支持され、遊星ピ
ン３には遊星歯車２が回転可能に嵌入されている。この
ため本実施例のような場合には、遊星ピン３と遊星歯車
２の嵌入部にホワイトメタル等が貼ってあり、回転が滑
らかになるように配慮されている。また、この目的のた
め遊星ピン３と遊星歯車２の嵌入部に転がり軸受が使用
される場合もある。In the present embodiment, the sun gear 1 and the input shaft 6 are integrated, but they may be separate pieces. The input shaft 6 is supported by an input bearing 8 and a pilot bearing 11, and a motor (not shown) such as a motor is connected to one end of the input shaft 6 via a coupling (not shown).
The planetary pin 3 is supported at its front and rear ends by the carrier 4, and the planetary gear 2 is rotatably fitted to the planetary pin 3. Therefore, in the case of the present embodiment, white metal or the like is attached to the fitting portions of the planet pins 3 and the planet gears 2 so that the rotation is smooth. For this purpose, a rolling bearing may be used in the fitting portion between the planetary pin 3 and the planetary gear 2.
【００２９】遊星歯車２は外側で内歯車５と噛み合って
いる。内歯車５はその他端を上側では上ケ−ス１３、下
側では下ケ−ス１２に軸受サポ−ト１４とともにボルト
等で可撓的に固定されているため回転することはできな
い。The planetary gear 2 meshes with the internal gear 5 on the outside. The internal gear 5 cannot be rotated because the other end thereof is flexibly fixed to the upper case 13 on the upper side and to the lower case 12 on the lower side together with the bearing support 14 by bolts or the like.
【００３０】キャリヤ−４はノックピン１５とボルト１
６により出力軸７と一体的に固定され、キャリヤ−軸受
１０と出力軸受９により支持されている。従って出力軸
７はキャリヤ−４となり、遊星歯車２の公転を出力とし
て取り出す。The carrier-4 includes a knock pin 15 and a bolt 1
6, is integrally fixed to the output shaft 7 and is supported by the carrier bearing 10 and the output bearing 9. Therefore, the output shaft 7 becomes the carrier-4, and takes out the revolution of the planetary gear 2 as an output.
【００３１】出力軸７の一端にはカップリング（図示せ
ず）を介しポンプ、ファン等の従動機（図示せず）が連
結されている。A driven machine (not shown) such as a pump or a fan is connected to one end of the output shaft 7 via a coupling (not shown).
【００３２】又本実施例には示していないが、この遊星
歯車装置は別に潤滑油供給装置を有しており、太陽歯車
１と遊星歯車２の噛み合い部、遊星歯車２と内歯車５の
噛み合い部、及び全ての軸受や遊星ピン３と遊星歯車２
のすべり面などは強制的に給油され、潤滑されている。Although not shown in this embodiment, this planetary gear device has a lubricating oil supply device separately, and the meshing portion between the sun gear 1 and the planetary gear 2 and the meshing between the planetary gear 2 and the internal gear 5 are provided. Parts and all bearings and planet pins 3 and planet gears 2
The sliding surface is forcibly lubricated and lubricated.
【００３３】本実施例の遊星歯車装置の特徴は、図２に
示すように遊星歯車２ａ、２ｂ、２ｃの歯幅が各々異な
っており、噛み合い終りは同じだが、噛み合い始めの点
が異なっている点である。As shown in FIG. 2, the planetary gear device of this embodiment is characterized in that the tooth widths of the planetary gears 2a, 2b, 2c are different from each other, and the meshing end is the same, but the meshing start point is different. It is a point.
【００３４】次に、本実施例の動作について説明する。Next, the operation of this embodiment will be described.
【００３５】例えば、原動機が電動機、被動機がポンプ
の減速機として使用する場合、電動機によりカップリン
グを介して太陽歯車１を駆動すると、太陽歯車１が遊星
歯車２と噛み合い、遊星歯車２が駆動される。次に遊星
歯車２が内歯車５と噛み合うが、内歯車５は固定されて
いるので、遊星歯車２は自転するとともに、遊星ピン３
及びキャリヤ−４と一緒に公転する。その結果、出力軸
７が回転し、カップリングを介してポンプが駆動され
る。For example, when the prime mover is used as an electric motor and the driven machine is used as a speed reducer for the pump, when the sun gear 1 is driven by the electric motor through the coupling, the sun gear 1 meshes with the planetary gear 2 and the planetary gear 2 is driven. To be done. Next, the planetary gear 2 meshes with the internal gear 5, but since the internal gear 5 is fixed, the planetary gear 2 rotates and the planetary pin 3
And revolve with Carrier-4. As a result, the output shaft 7 rotates and the pump is driven via the coupling.
【００３６】本実施例の遊星歯車装置では、遊星歯車２
ａ、２ｂ、２ｃの太陽歯車１と噛み合い始める側の歯の
側端面の軸方向位置を各々ずらしてある。その結果、各
遊星歯車２ａ、２ｂ、２ｃと太陽歯車１の噛み合い始め
のタイミング及び各遊星歯車２ａ、２ｂ、２ｃと内歯車
５の噛み合い終わりのタイミングがずれることになり、
噛み合い時の衝撃が分散されるので、遊星歯車２、太陽
歯車１及び内歯車５の噛み合い時に発生する衝撃振動が
１／３に低減され、遊星歯車装置全体的にも振動・騒音
が低減される。In the planetary gear device of this embodiment, the planetary gear 2
The axial positions of the side end surfaces of the teeth a, 2b, and 2c on the side where they start to mesh with the sun gear 1 are shifted. As a result, the timing at which the planetary gears 2a, 2b, 2c start meshing with the sun gear 1 and the timing at which the planetary gears 2a, 2b, 2c mesh with the internal gear 5 end are shifted.
Since the impact at the time of meshing is dispersed, the impact vibration generated at the time of meshing of the planetary gear 2, the sun gear 1 and the internal gear 5 is reduced to 1/3, and the vibration and noise of the entire planetary gear device are also reduced. .
【００３７】次に、本発明の第二の実施例を図５によっ
て説明する 本実施例の特徴は図５に示すように、遊星歯車２ａ、２
ｂ、２ｃの太陽歯車１と噛み合い終わり側の歯の側端面
の軸方向位置を各々ずらしてある点である。その他の構
成は前述の第一の実施例と同様である。Next, a second embodiment of the present invention will be described with reference to FIG. 5. The feature of this embodiment is that, as shown in FIG.
b and 2c are points where the axial positions of the side end faces of the teeth on the end side of meshing with the sun gear 1 are shifted. The other structure is similar to that of the first embodiment described above.
【００３８】以上のように構成することにより、各遊星
歯車２ａ、２ｂ、２ｃと太陽歯車１の噛み合い終わりの
タイミング及び各遊星歯車２ａ、２ｂ、２ｃと内歯車５
の噛み合い始めのタイミングがずれることになり、噛み
合い時の衝撃が分散されるので、遊星歯車２、太陽歯車
１及び内歯車５の噛み合い時に発生する衝撃振動が１／
３に低減され、遊星歯車装置全体的にも振動・騒音が低
減される。With the above configuration, the timing of the end of meshing between the planetary gears 2a, 2b, 2c and the sun gear 1 and the planetary gears 2a, 2b, 2c and the internal gear 5 are completed.
Since the timing of the meshing start of the gears is deviated and the shock during the meshing is dispersed, the shock vibration generated when the planetary gear 2, the sun gear 1 and the internal gear 5 mesh with each other is 1 /
The number of vibrations and noises is reduced to 3 as a whole, and the entire planetary gear device is also reduced in vibration and noise.
【００３９】次に、本発明の第三の実施例を図６によっ
て説明する。Next, a third embodiment of the present invention will be described with reference to FIG.
【００４０】本実施例の特徴は図６に示すように、歯幅
が同じ遊星歯車２ａ、２ｂ、２ｃの各々の軸方向位置を
ずらし、太陽歯車１と噛み合い始める側の歯の側端面の
軸方向位置を各々別々にした点である。その他の構成は
前述の第一の実施例と同様である。As shown in FIG. 6, the feature of the present embodiment is that the axial positions of the planetary gears 2a, 2b, 2c having the same tooth width are shifted and the shafts of the side end faces of the teeth on the side where they start to mesh with the sun gear 1 are shifted. This is a point where the directional positions are different from each other. The other structure is similar to that of the first embodiment described above.
【００４１】以上のように構成することにより、各遊星
歯車２ａ、２ｂ、２ｃと太陽歯車１の噛み合い始めと噛
み合い終わりのタイミング及び各遊星歯車２ａ、２ｂ、
２ｃと内歯車５の噛み合い終わりと噛み合い始めのタイ
ミングがずれることになり、噛み合い時の衝撃が分散さ
れるので、遊星歯車２、太陽歯車１及び内歯車５の噛み
合い時に発生する衝撃振動が１／３に低減され、遊星歯
車装置全体的にも振動・騒音が低減される。With the above-mentioned structure, the timings of the meshing start and meshing of the planetary gears 2a, 2b, 2c and the sun gear 1 and the planetary gears 2a, 2b,
Since the timing of the end of meshing between 2c and the internal gear 5 and the timing of the start of meshing are shifted, and the shock at the time of meshing is dispersed, the impact vibration generated at the meshing of the planetary gear 2, the sun gear 1 and the internal gear 5 is 1 / The number of vibrations and noises is reduced to 3 as a whole, and the entire planetary gear device is also reduced in vibration and noise.
【００４２】次に、本発明の第四の実施例を図７によっ
て説明する。Next, a fourth embodiment of the present invention will be described with reference to FIG.
【００４３】本実施例の特徴は図５に示すように、遊星
歯車装置の遊星歯車２００ａ、２００ｂ、２００ｃ及び
太陽歯車１０が平歯車で構成されている点及び遊星歯車
２００ａ、２００ｂ、２０００の歯丈に差をつけてある
点である。その他の構成は前述の第一の実施例と同様で
ある。As shown in FIG. 5, the feature of the present embodiment is that the planetary gears 200a, 200b and 200c of the planetary gear device and the sun gear 10 are spur gears and the teeth of the planetary gears 200a, 200b and 2000. This is the difference in length. The other structure is similar to that of the first embodiment described above.
【００４４】以上のように構成することにより、各遊星
歯車２００ａ、２００ｂ、２００ｃと太陽歯車１００の
噛み合い始めのタイミング及び各遊星歯車２００ａ、２
００ｂ、２００ｃと内歯車５００の噛み合い終わりのタ
イミングがずれることになり、噛み合い時の衝撃が分散
されるので、遊星歯車２００、太陽歯車１００及び内歯
車５００の噛み合い時に発生する衝撃振動が１／３に低
減され、遊星歯車装置全体的にも振動・騒音が低減され
る。With the above-described structure, the timing at which the planetary gears 200a, 200b, 200c start meshing with the sun gear 100 and the planetary gears 200a, 2
00b, 200c and the timing of the end of meshing of the internal gear 500 are shifted, and the impact at the time of meshing is dispersed. Therefore, the impact vibration generated during meshing of the planetary gear 200, the sun gear 100 and the internal gear 500 is 1/3. The vibration and noise are also reduced in the entire planetary gear unit.
【００４５】本発明の第五の実施例を図８によって説明
する。A fifth embodiment of the present invention will be described with reference to FIG.
【００４６】３個の遊星歯車ａ、ｂ、ｃの噛み合い初め
の歯の先端の面取りを行ない、かつ３個の遊星歯車ａ、
ｂ、ｃの面取りを１／３づつ順次大きくする、（２）３
個の遊星歯車の歯幅を変えて噛み合うタイミングを噛み
合い周期の１／３づつ順次ずらす、（３）３個の遊星歯
車の歯幅を全て同じにしてセット位置を順次ずらし、噛
み合うタイミングを噛み合い周期の１／３づつ順次ずら
すなどの手段を採用する。The tip of the tooth at the beginning of meshing of the three planetary gears a, b, c is chamfered, and the three planetary gears a,
Increase chamfering of b and c by 1/3 in sequence, (2) 3
Change the tooth width of each planetary gear and sequentially shift the meshing timing by 1/3 of the meshing cycle. (3) Make the tooth widths of all three planetary gears the same and sequentially shift the set positions to mesh the meshing timing. A method such as sequentially shifting by 1/3 each is adopted.
【００４７】以上のように構成することにより、噛み合
い時の衝撃が分散されるので、遊星歯車、太陽歯車及び
内歯車の噛み合い時に発生する衝撃振動が１／３に低減
し、遊星歯車装置全体的にも振動・騒音が低減される。With the above-mentioned structure, the impact at the time of meshing is dispersed, and the impact vibration generated at the time of meshing of the planetary gear, the sun gear and the internal gear is reduced to 1/3, and the entire planetary gear device is Also, vibration and noise are reduced.
【００４８】本発明の第五の実施例を図９によって説明
する。A fifth embodiment of the present invention will be described with reference to FIG.
【００４９】図は石炭ミル用の減速機の実施例であり、
６０１は入力軸でケ−ス６０２に軸受６０３を介して支
持されており、一端にベベルピニオン６０４が取り付け
られている。６０５はベベルギヤで回転軸６０６に固定
されている。６０７は太陽歯車で、前記回転軸６０６と
ギヤカップリング６０８を介して接続されている。６０
９はキャリヤ−であって遊星ピン６１０によって遊星歯
車６１１を回転可能に支持し、この遊星歯車６１１（３
個で形成）は前記太陽歯車６０７と噛み合っている。６
１２は内歯車であって、前記遊星歯車６１１と噛み合っ
ている。６１３は回転台であって、前記キャリヤ−６０
９に取り付けられている。太陽歯車６０７、遊星歯車６
１１及び内歯車６１２は、各遊星歯車６１１の太陽歯車
６０７と噛み合い始める側の歯の側端面の軸方向位置の
差を、各遊星歯車６１１と太陽歯車が噛み合い始めるタ
イミングの差及び各遊星歯車６１１と内歯車６１２が噛
み合い終わるタイミングの差が噛み合い周期の１／３に
なるように配置されている。The figure shows an example of a speed reducer for a coal mill,
An input shaft 601 is supported by a case 602 via a bearing 603, and a bevel pinion 604 is attached to one end thereof. A bevel gear 605 is fixed to the rotating shaft 606. A sun gear 607 is connected to the rotating shaft 606 via a gear coupling 608. 60
Reference numeral 9 denotes a carrier, which rotatably supports a planetary gear 611 by a planetary pin 610, and the planetary gear 611 (3
(Formed by individual pieces) meshes with the sun gear 607. 6
Reference numeral 12 denotes an internal gear, which meshes with the planetary gear 611. Reference numeral 613 denotes a turntable, which is the carrier-60.
It is attached to 9. Sun gear 607, planetary gear 6
11 and the internal gear 612, the difference in the axial position of the side end faces of the teeth of the planet gears 611 on the side where they start to mesh with the sun gear 607, the difference in the timing at which the planet gears 611 and the sun gear start meshing, and the planet gears 611. The internal gear 612 and the internal gear 612 are arranged so that the difference in the timing at which they mesh with each other is 1/3 of the meshing cycle.
【００５０】以上のように構成することにより、噛み合
い時の衝撃が分散されるので、遊星歯車、太陽歯車及び
内歯車の噛み合い時に発生する衝撃振動が１／３に低減
し、遊星歯車装置全体的にも振動・騒音が低減される。With the above structure, the impact at the time of meshing is dispersed, so that the impact vibration generated at the time of meshing of the planetary gear, the sun gear and the internal gear is reduced to 1/3, and the entire planetary gear system is Also, vibration and noise are reduced.
【００５１】[0051]
【発明の効果】本発明のはすば歯車もしくは平歯車を有
し、太陽歯車及び内歯車の歯数が遊星歯車の個数で割り
切れる遊星歯車装置では、各遊星歯車の太陽歯車と噛み
合い始める側の歯の側端面の軸方向位置を各々ずらして
あり、その結果、各遊星歯車と太陽歯車の噛み合い始め
のタイミング及び各遊星歯車と内歯車の噛み合い終わり
のタイミングがずれることになり、噛み合い時の衝撃が
分散されるので、歯車の噛み合い時に発生する衝撃振動
が低減し（例えば遊星歯車の数をＮとすると１／Ｎ）、
遊星歯車装置全体的にも振動・騒音の低減が図れる。In the planetary gear device having the helical gear or the spur gear of the present invention, in which the number of teeth of the sun gear and the internal gear is divisible by the number of the planet gears, the planet gears on the side where they start to mesh with the sun gears. The axial positions of the side end faces of the teeth are shifted, and as a result, the timing of the start of meshing between the planet gears and the sun gear and the timing of the end of meshing between the planet gears and the internal gear shift, resulting in impact during meshing. Are dispersed, the shock vibration generated when the gears mesh with each other is reduced (for example, 1 / N where N is the number of planetary gears),
Vibration and noise can be reduced in the entire planetary gear unit.
【図１】本発明に係るはすば歯車の噛み合いの説明図で
ある。FIG. 1 is an explanatory diagram of meshing of helical gears according to the present invention.
【図２】本発明の第一の実施例の遊星歯車装置の噛み合
い説明図である。FIG. 2 is an explanatory diagram of meshing of the planetary gear device according to the first embodiment of the present invention.
【図３】本発明の第一の実施例の遊星歯車装置の縦断面
図である。FIG. 3 is a vertical cross-sectional view of the planetary gear device according to the first embodiment of the present invention.
【図４】本発明の第一の実施例のキャリヤ−を固定した
場合の遊星歯車装置の縦断面図である。FIG. 4 is a vertical cross-sectional view of the planetary gear device when the carrier according to the first embodiment of the present invention is fixed.
【図５】本発明の第二の実施例の遊星歯車装置の噛み合
い説明図である。FIG. 5 is an explanatory diagram of meshing of the planetary gear device according to the second embodiment of the present invention.
【図６】本発明の第三の実施例の遊星歯車装置の噛み合
い説明図である。FIG. 6 is a meshing explanatory view of a planetary gear device according to a third embodiment of the present invention.
【図７】本発明の第四の実施例の遊星歯車装置の噛み合
い説明図である。FIG. 7 is a meshing explanatory view of a planetary gear device according to a fourth embodiment of the present invention.
【図８】本発明の第五の実施例の遊星歯車の噛み合い説
明図である。FIG. 8 is an explanatory diagram of meshing of a planetary gear according to a fifth embodiment of the present invention.
【図９】本発明の第六の実施例の遊星歯車の一部切欠き
縦断面図である。FIG. 9 is a partially cutaway vertical sectional view of a planetary gear according to a sixth embodiment of the present invention.
１、１００、６０７…太陽歯車 ２、２００、６１１…遊星歯車 ２ａ、２００ａ…遊星歯車Ａ ２ｂ、２００ｂ…遊星歯車Ｂ ２ｃ、２００ｃ…遊星歯車Ｃ ３…ピン ４、６０９…キャリヤ− ５、５００、６１２…内歯車 ６、６０１…入力軸 ７…出力軸 ８…入力軸受 ９…出力軸受 １０…キャリヤ−軸受 １１…パイロット軸受 １２…下ケ−ス １３…上ケ−ス １４…軸受サポ−ト １５…ノックピン １６…ボルト ６０４…ベベルピニオン ６０５…ベベルギヤ 1, 100, 607 ... Sun gears 2, 200, 611 ... Planetary gears 2a, 200a ... Planetary gears A 2b, 200b ... Planetary gears B 2c, 200c ... Planetary gears C 3 ... Pins 4, 609 ... Carriers-5, 500, 612 ... Internal gear 6, 601 ... Input shaft 7 ... Output shaft 8 ... Input bearing 9 ... Output bearing 10 ... Carrier bearing 11 ... Pilot bearing 12 ... Lower case 13 ... Upper case 14 ... Bearing support 15 … Knock pin 16… Bolt 604… Bevel pinion 605… Bevel gear
Claims (18)
の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれぞ
れの歯形をインボリュ−ト曲線で形成するはすば歯車、
及びこれらを収納するケ−スを備え、前記太陽歯車及び
内歯車の歯数が遊星歯車の個数で割り切れる遊星歯車装
置において、前記複数個の各遊星歯車の太陽歯車と噛み
合い始める側の歯の側端面の軸方向位置を順次ずらし、
各遊星歯車と太陽歯車が噛み合い始めるタイミング、及
び各遊星歯車と内歯車が噛み合い終わるタイミングを各
遊星歯車において異なるように前記太陽歯車、遊星歯車
及び内歯車の歯面を形成することを特徴とする遊星歯車
装置。1. A helical gear in which each tooth profile of a sun gear, a plurality of planet gears meshing with the sun gear, and an internal gear meshing with the planet gear is formed by an involute curve,
And a case for housing them, in a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the tooth side of the plurality of planet gears on the side where the teeth start to mesh with the sun gear. Shift the axial position of the end face sequentially,
The tooth surfaces of the sun gear, the planetary gear and the internal gear are formed so that the timing at which the planetary gears and the sun gear start to mesh with each other and the timing at which the planetary gears and the internal gear end to mesh with each other are different in each planetary gear. Planetary gear unit.
複数個の各遊星歯車の太陽歯車と噛み合い始める側の歯
の側端面の軸方向位置の差を、各遊星歯車と太陽歯車が
噛み合い始めるタイミングの差及び各遊星歯車と内歯車
が噛み合い終わるタイミングの差が噛み合い周期の１／
Ｎ（但しＮは遊星歯車の数）になるように配置すること
を特徴とする遊星歯車装置。2. The planetary gear set according to claim 1, wherein
The difference in the axial position of the side end faces of the teeth on the side where the plurality of planetary gears start to mesh with the sun gear, the difference in the timing at which each planetary gear and the sun gear start to mesh, and the difference between the timing at which each planetary gear and the internal gear finish meshing. The difference is 1 / of the meshing period
A planetary gear device characterized in that it is arranged so as to be N (where N is the number of planetary gears).
の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれぞ
れの歯形をインボリュ−ト曲線で形成するはすば歯車、
及びこれらを収納するケ−スを備え、前記太陽歯車及び
内歯車の歯数が遊星歯車の個数で割り切れる遊星歯車装
置において、前記複数個の各遊星歯車の太陽歯車と噛み
合い始める側の歯の側端面の軸方向位置を順次ずらし、
各遊星歯車と太陽歯車が噛み合い終わるタイミング、及
び各遊星歯車と内歯車が噛み合い始めるタイミングを各
遊星歯車において異なるように前記太陽歯車、遊星歯車
及び内歯車を配置することを特徴とする遊星歯車装置。3. A helical gear in which each tooth profile of a sun gear, a plurality of planet gears meshing with the sun gear and an internal gear meshing with the planet gear is formed by an involute curve,
And a case for housing them, in a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the tooth side of the plurality of planet gears on the side where the teeth start to mesh with the sun gear. Shift the axial position of the end face sequentially,
The planetary gear device, wherein the sun gear, the planetary gear, and the internal gear are arranged so that the timing at which the planetary gears and the sun gears finish meshing with each other and the timing at which the planetary gears and the internal gears start meshing with each other are different. .
複数個の各遊星歯車の太陽歯車と噛み合い終わる側の歯
の側端面の軸方向位置の差を、各遊星歯車と太陽歯車が
噛み合い終わるタイミングの差及び各遊星歯車と内歯車
が噛み合い始めるタイミングの差が噛み合い周期の１／
Ｎ（但しＮは遊星歯車の数）になるように配置すること
を特徴とする遊星歯車装置。4. The planetary gear device according to claim 3,
The difference in the axial position of the side end faces of the teeth of the plurality of planetary gears on the side where the meshing with the sun gear ends, the difference in the timing at which the planetary gears and the sun gears finish meshing, and the timing at which the planetary gears and the internal gear start meshing The difference is 1 / of the meshing period
A planetary gear device characterized in that it is arranged so as to be N (where N is the number of planetary gears).
の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれぞ
れの歯形をインボリュ−ト曲線で形成するはすば歯車、
及びこれらを収納するケ−スを備え、前記太陽歯車及び
内歯車の歯数が遊星歯車の個数で割り切れる遊星歯車装
置において、前記複数個の各遊星歯車の太陽歯車と噛み
合い始める側及び噛み合い終わる側の歯の側端面の軸方
向位置を順次ずらし、各遊星歯車と太陽歯車及び内歯車
とが噛み合い始めるタイミング及び噛み合い終るタイミ
ングを各遊星歯車において異なるように前記太陽歯車、
遊星歯車及び内歯車を配置することを特徴とする遊星歯
車装置。5. A helical gear in which each tooth profile of a sun gear, a plurality of planetary gears meshing with the sun gear and an internal gear meshing with the planetary gear is formed by an involute curve,
And a case that accommodates these, in a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the side on which meshing with the sun gear of each of the plurality of planet gears and the side on which meshing ends The axial positions of the side end surfaces of the teeth of the sun gears are sequentially shifted, so that each planetary gear and the sun gear and the internal gear have different timings at which the planetary gears start and end meshing with each other,
A planetary gear device in which a planetary gear and an internal gear are arranged.
各遊星歯車と太陽歯車及び内歯車とが噛み合い始めるタ
イミング及び噛み合い終るタイミングの差が、噛み合い
周期の１／Ｎ（但しＮは遊星歯車の数）になるよう遊星
歯車の太陽歯車と噛み合い始める側及び噛み合い終わる
側の歯の側端面の軸方向位置に配置することを特徴とす
る遊星歯車装置。6. The planetary gear device according to claim 5,
The side where the planetary gears start meshing with the sun gear and the internal gear and the timing at which the planetary gears start meshing with each other are 1 / N (where N is the number of planetary gears) of the meshing cycle, A planetary gear device, wherein the planetary gear device is arranged at an axial position of a side end surface of a tooth on a side where meshing is completed.
の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれぞ
れの歯形をインボリュ−ト曲線で形成するはすば歯車、
及びこれらを収納するケ−スを備え、前記太陽歯車及び
内歯車の歯数が遊星歯車の個数で割り切れる遊星歯車装
置において、前記複数個の各遊星歯車の軸方向の位置を
ずらして配置し、各遊星歯車と太陽歯車が噛み合い始め
るタイミング及び噛み合い終わるタイミング及び各遊星
歯車と内歯車が噛み合い終わるタイミング及び噛み合い
始めるタイミングを、各遊星歯車において異なるように
前記太陽歯車、遊星歯車及び内歯車を配置することを特
徴とする遊星歯車装置。7. A helical gear in which each tooth profile of a sun gear, a plurality of planetary gears meshing with the sun gear and an internal gear meshing with the planetary gear is formed by an involute curve,
And a case for accommodating them, in a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the axial positions of the plurality of planet gears are displaced from each other. The sun gear, the planetary gear, and the internal gear are arranged so that the timing at which the planetary gears and the sun gear start meshing with each other, the timing at which the planetary gears end meshing, the timing at which the planetary gears and the internal gear end meshing, and the timing at which the planetary gears start meshing are different for each planetary gear. A planetary gear unit characterized by the above.
各遊星歯車と太陽歯車及び内歯車が噛み合い始めるタイ
ミングの差及び噛み合い終るタイミングの差が、噛み合
い周期の１／Ｎ（但しＮは遊星歯車の数）になるよう
に、各々の遊星歯車の軸方向の位置をずらして配置する
ことを特徴とする遊星歯車装置。8. The planetary gear device according to claim 7,
The axial direction of each planetary gear is adjusted so that the difference between the timings at which the planetary gears and the sun gear and the internal gear start to mesh and the timing at which the meshing ends are 1 / N of the meshing cycle (where N is the number of planetary gears). A planetary gear unit characterized in that the positions of and are shifted.
の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれぞ
れ歯形をインボリュ−ト曲線で形成る平歯車、及びこれ
らを収納するケ−ス等を備え、前記太陽歯車及び内歯車
の歯数が遊星歯車の個数で割り切れる遊星歯車装置にお
いて、前記複数個の各遊星歯車の歯丈を各々異ならせ、
各遊星歯車と太陽歯車が噛み合い始めるタイミング及び
各遊星歯車と内歯車が噛み合い終わるタイミングを、各
遊星歯車において異なるように前記太陽歯車、遊星歯車
及び内歯車の歯面を形成することを特徴とする遊星歯車
装置。9. A sun gear, a plurality of planetary gears that mesh with the sun gear, and a spur gear that forms each tooth profile of an internal gear that meshes with the planetary gear with an involute curve, and a case that houses these. In a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the plurality of planet gears have different tooth lengths,
The tooth surfaces of the sun gear, the planetary gear and the internal gear are formed so that the timing at which the planetary gears and the sun gear start to mesh and the timing at which the planetary gears and the internal gear end to mesh with each other are different in each planetary gear. Planetary gear unit.
て、前記複数個の遊星歯車の歯丈の差を各遊星歯車と太
陽歯車が噛み合い始めるタイミングの差及び各遊星歯車
と内歯車とが噛み合い終わるタイミングの差が、噛み合
い周期の１／Ｎ（但しＮは遊星歯車の数）になるように
形成することを特徴とする遊星歯車装置。10. The planetary gear device according to claim 9, wherein the difference in the tooth heights of the plurality of planetary gears is the difference in the timing at which the planetary gears and the sun gear start to mesh with each other, and the planetary gears and the internal gear mesh with each other. A planetary gear device characterized in that the difference in the end timing is 1 / N of the meshing period (where N is the number of planetary gears).
個の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれ
ぞれの歯形をインボリュ−ト曲線で形成するはすば歯
車、及びこれらを収納するケ−スを備え、前記太陽歯車
及び内歯車の歯数が遊星歯車の個数で割り切れる遊星歯
車装置において、遊星歯車の噛み合い初めの歯の先端の
面取りを行ない、各遊星歯車の面取りを順次大きくなる
ように遊星歯車の歯面を形成することを特徴とする遊星
歯車装置。11. A sun gear, a plurality of planetary gears that mesh with the sun gear, and a helical gear that forms each tooth profile of an internal gear that meshes with the planetary gear with an involute curve, and a case that houses them. In a planetary gear device that has a tooth, and the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, chamfer the tips of the teeth at the beginning of meshing of the planet gears so that the chamfer of each planet gear increases in sequence. A planetary gear device characterized by forming a tooth surface of a planetary gear.
て、各遊星歯車の面取りを１／Ｎ（但しＮは遊星歯車の
数）づつ順次大きくして各遊星歯車の面取り量が異なる
ように形成することを特徴とする遊星歯車装置。12. The planetary gear device according to claim 11, wherein the chamfers of the planetary gears are sequentially increased by 1 / N (where N is the number of planetary gears) so that the chamfering amounts of the planetary gears are different. A planetary gear device characterized in that.
個の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれ
ぞれの歯形をインボリュ−ト曲線で形成するはすば歯
車、及びこれらを収納するケ−スを備え、前記太陽歯車
及び内歯車の歯数が遊星歯車の個数で割り切れる遊星歯
車装置において、遊星歯車の歯幅を変えて噛み合うタイ
ミングを順次ずらすように各遊星歯車の面取りを順次大
きくなるように形成することを特徴とする遊星歯車装
置。13. A helical gear, wherein each tooth profile of a sun gear, a plurality of planet gears meshing with the sun gear and an internal gear meshing with the planet gear is formed by an involute curve, and a case for housing them. In a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planetary gears, the chamfer of each planetary gear is sequentially increased so as to sequentially shift the meshing timing by changing the tooth width of the planetary gears. A planetary gear device, characterized in that
て、噛み合うタイミングを噛み合い周期の１／Ｎ（但し
Ｎは遊星歯車の数）づつ順次ずらすして遊星歯車の歯面
を形成ことを特徴とする遊星歯車装置。14. The planetary gear device according to claim 13, wherein the meshing timing is sequentially shifted by 1 / N (where N is the number of planetary gears) of the meshing period to form the tooth surface of the planetary gear. Planetary gearing system.
の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれぞ
れの歯形をインボリュ−ト曲線で形成するはすば歯車、
及びこれらを収納するケ−スを備え、前記太陽歯車及び
内歯車の歯数が遊星歯車の個数で割り切れる遊星歯車装
置において、遊星歯車の歯幅を全て同じにして遊星歯車
各々のセット位置を順次ずらし、噛み合うタイミングを
順次ずらして遊星歯車を配置することを特徴とする遊星
歯車装置。15. A helical gear in which each tooth profile of a sun tooth, a plurality of planetary gears meshing with the sun gear and an internal gear meshing with the planetary gear is formed by an involute curve,
And a case for housing these, in a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, the planet gears have the same tooth width, and the set positions of the planet gears are sequentially set. A planetary gear device in which the planetary gears are arranged with the timings of shifting and meshing being sequentially shifted.
記太陽歯車及び内歯車の歯数が遊星歯車の個数で割り切
れる複数個の遊星歯車及びこの遊星歯車と噛み合う内歯
車のそれぞれの歯形をインボリュ−ト曲線で形成するは
すば歯車、及びこれらを収納するケ−ス、前記太陽歯車
に接続される入力軸もしくは出力軸、前記遊星歯車を回
転可能に支持するキャリア、このキャリアに接続される
出力軸もしくは入力軸を備える遊星歯車装置において、
前記複数個の各遊星歯車の太陽歯車と噛み合い始める側
の歯の側端面の軸方向位置を順次ずらし、各遊星歯車と
太陽歯車が噛み合い始めるタイミング、及び各遊星歯車
と内歯車が噛み合い終わるタイミングが噛み合い周期の
１／Ｎ（但しＮは遊星歯車の数）になるように前記太陽
歯車、遊星歯車及び内歯車の歯面を形成することを特徴
とする遊星歯車装置。16. A sun gear, a plurality of planet gears meshing with the sun gear such that the number of teeth of the sun gear and the internal gear is divisible by the number of planet gears, and the tooth profile of each of the internal gears meshing with the planet gears is involute. Helical gears formed by a curved line, a case for accommodating them, an input shaft or an output shaft connected to the sun gear, a carrier rotatably supporting the planetary gears, and an output connected to the carrier. In a planetary gear unit equipped with a shaft or an input shaft,
The axial positions of the side end surfaces of the teeth on the side where meshing with the sun gears of the plurality of planetary gears are sequentially shifted, the timing at which each planetary gear and the sun gear start to mesh, and the timing at which each planetary gear and the internal gear end A planetary gear device characterized in that the tooth surfaces of the sun gear, the planetary gear and the internal gear are formed so as to be 1 / N of the meshing period (where N is the number of planetary gears).
噛み合うベベルギヤ、一端に前記ベベルギヤが固定され
他端に太陽歯車が固定された回転軸、前記太陽歯車と噛
み合って前記太陽歯車及び内歯車の歯数が遊星歯車の個
数で割り切れる複数個の遊星歯車及びこの遊星歯車と噛
み合う内歯車のそれぞれの歯形をインボリュ−ト曲線で
形成するはすば歯車、及びこれらを収納するケ−ス、前
記ベベルピニオンに接続される入力軸もしくは出力軸、
前記遊星歯車を回転可能に支持するキャリア、このキャ
リアに接続される出力軸もしくは入力軸を備える遊星歯
車装置において、前記複数個の各遊星歯車の太陽歯車と
噛み合い始める側の歯の側端面の軸方向位置を順次ずら
し、各遊星歯車と太陽歯車が噛み合い始めるタイミン
グ、及び各遊星歯車と内歯車が噛み合い終わるタイミン
グが噛み合い周期の１／Ｎ（但しＮは遊星歯車の数）に
なるように前記太陽歯車、遊星歯車及び内歯車の歯面を
形成することを特徴とする遊星歯車装置。17. A bevel pinion, a bevel gear meshing with the bevel pinion, a rotating shaft having the bevel gear fixed at one end and a sun gear fixed at the other end, and the number of teeth of the sun gear and the internal gear meshed with the sun gear. A plurality of planetary gears that are divisible by the number of planetary gears and a helical gear that forms each tooth profile of an internal gear that meshes with the planetary gears with an involute curve, a case that houses these, and a bevel pinion Input or output axis,
In a planetary gear device including a carrier that rotatably supports the planetary gear and an output shaft or an input shaft connected to the carrier, a shaft of a side end surface of a tooth of a side of the plurality of planetary gears that starts to mesh with a sun gear. The directional positions are sequentially shifted so that the timing at which the planet gears and the sun gear start to mesh and the timing at which the planet gears and the internal gear end to mesh are 1 / N (where N is the number of planet gears) of the meshing cycle. A planetary gear device characterized by forming tooth surfaces of a gear, a planetary gear and an internal gear.
個の遊星歯車及びこの遊星歯車と噛み合う内歯車のそれ
ぞれの歯形をインボリュ−ト曲線で形成するはすば歯
車、及びこれらを収納するケ−スを備え、前記太陽歯車
及び内歯車の歯数が遊星歯車の個数で割り切れる遊星歯
車装置の製造方法において、前記複数個の各遊星歯車の
太陽歯車と噛み合い始める側の歯の側端面の軸方向位置
を順次ずらし、各遊星歯車と太陽歯車が噛み合い始める
タイミング、及び各遊星歯車と内歯車が噛み合い終わる
タイミングを各遊星歯車において異なるように前記太陽
歯車、遊星歯車及び内歯車の歯面を製造することを特徴
とする遊星歯車装置の製造方法。18. A helical gear in which the tooth profile of each of the sun gear, a plurality of planetary gears meshing with the sun gear, and an internal gear meshing with the planetary gear is formed by an involute curve, and a case for housing them. In the method for manufacturing a planetary gear device in which the number of teeth of the sun gear and the internal gear is divisible by the number of planetary gears, the axial direction of the side end surface of the teeth on the side where the planetary gears start meshing with the sun gears. The tooth surfaces of the sun gears, the planetary gears, and the internal gears are manufactured so that the planetary gears and the sun gears start meshing with each other and the timing at which the planetary gears and the internal gears finish meshing are different in each planetary gear by sequentially shifting the positions. A method for manufacturing a planetary gear device, comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21044095A JPH0953690A (en) | 1995-08-18 | 1995-08-18 | Planetary gears |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21044095A JPH0953690A (en) | 1995-08-18 | 1995-08-18 | Planetary gears |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0953690A true JPH0953690A (en) | 1997-02-25 |
Family
ID=16589370
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21044095A Pending JPH0953690A (en) | 1995-08-18 | 1995-08-18 | Planetary gears |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0953690A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007057015A (en) * | 2005-08-25 | 2007-03-08 | Aisin Aw Co Ltd | Driving device for vehicle |
| WO2011074332A1 (en) * | 2009-12-15 | 2011-06-23 | 三菱重工業株式会社 | Transmission for wind power generation equipment, and wind power generation device |
| JP2014111985A (en) * | 2012-11-05 | 2014-06-19 | Sumitomo Heavy Ind Ltd | Simple planetary reduction gear |
-
1995
- 1995-08-18 JP JP21044095A patent/JPH0953690A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007057015A (en) * | 2005-08-25 | 2007-03-08 | Aisin Aw Co Ltd | Driving device for vehicle |
| WO2011074332A1 (en) * | 2009-12-15 | 2011-06-23 | 三菱重工業株式会社 | Transmission for wind power generation equipment, and wind power generation device |
| CN102472256A (en) * | 2009-12-15 | 2012-05-23 | 三菱重工业株式会社 | Transmission for wind power generation equipment, and wind power generation device |
| JP2014111985A (en) * | 2012-11-05 | 2014-06-19 | Sumitomo Heavy Ind Ltd | Simple planetary reduction gear |
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