JPS6233462B2 - - Google Patents
Info
- Publication number
- JPS6233462B2 JPS6233462B2 JP54128257A JP12825779A JPS6233462B2 JP S6233462 B2 JPS6233462 B2 JP S6233462B2 JP 54128257 A JP54128257 A JP 54128257A JP 12825779 A JP12825779 A JP 12825779A JP S6233462 B2 JPS6233462 B2 JP S6233462B2
- Authority
- JP
- Japan
- Prior art keywords
- planetary
- gear
- planetary gears
- gears
- sun 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.)
- Expired
Links
- 230000005540 biological transmission Effects 0.000 description 8
- 230000010363 phase shift Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/289—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two or more coaxial and identical sets of orbital gears, e.g. for distributing torque between the coaxial sets
Landscapes
- Gear Transmission (AREA)
- Retarders (AREA)
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は、コンパクトな構成でありながら安定
した動力等配のもとに大きな減速比を得ることが
できる遊星歯車式減速装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a planetary gear type speed reduction device that can obtain a large reduction ratio with stable power distribution even though it has a compact configuration.
ガスタービンのように数万回転／分にも及ぶ超
高速回転をする駆動源から動力を取り出すには、
遊星歯車機構のような大きな減速比を有する減速
装置を使用する必要がる。しかし、いままでの通
常の遊星歯車式減速装置による減速比は、せいぜ
い13.5までが限度であり、それ以上の大きな減速
比を必要とするときは、２台の遊星歯車式減速装
置を直列に接続して使用せざるをえず、減速装置
全体が大型化してしまうことは避けられなかつ
た。
To extract power from a drive source that rotates at ultra-high speeds of tens of thousands of revolutions per minute, such as a gas turbine,
It is necessary to use a reduction gear with a large reduction ratio, such as a planetary gear mechanism. However, the reduction ratio of conventional planetary gear type reduction gears is limited to a maximum of 13.5, and when a larger reduction ratio is required, two planetary gear type reduction gears can be connected in series. Therefore, it was inevitable that the entire speed reduction device would become larger.
上述のように遊星歯車式減速装置の減速比の限
度が13.5であるのは、次のような理由によるもの
である。 The reason why the limit of the reduction ratio of the planetary gear type reduction gear is 13.5 as described above is as follows.
すなわち、周知のように遊星歯車機構は太陽歯
車と内歯車との間に複数個の遊星歯車を配置して
構成されている。この場合、遊星歯車の数を２個
だけにすると、回転中の太陽歯車の中心を定める
こと、すなわち太陽歯車の中心を自動調心させる
ことはできず、そのため複数の遊星歯車に対し駆
動力の等配をすることが困難になるという問題が
ある。このため、現在実用機として使用されてい
る遊星歯車式減速装置では、遊星歯車を２個にす
るものはなく、ほとんどの例が３個か又はそれ以
上になつている。 That is, as is well known, a planetary gear mechanism is constructed by disposing a plurality of planetary gears between a sun gear and an internal gear. In this case, if the number of planetary gears is only two, it is not possible to determine the center of the rotating sun gear, that is, the center of the sun gear can be self-aligned, and therefore, the driving force is applied to multiple planetary gears. There is a problem that it becomes difficult to allocate evenly. For this reason, none of the planetary gear type reduction gears currently used in practical applications have two planetary gears, and most examples have three or more planetary gears.
第１，２図は、３個の遊星歯車を有する従来の
減速装置であり、入力軸７に設けた太陽歯車１に
３個の遊星歯車２，２，２が噛合し、さらにこれ
らの遊星歯車２，２，２が内歯車３に噛合してい
る。この遊星歯車式減速装置では、太陽歯車１に
３個の遊星歯車２，２，２を噛合させているか
ら、太陽歯車１は自動調心作用を行うことがで
き、各遊星歯車２に動力を等配できるようになつ
ている。 Figures 1 and 2 show a conventional speed reduction device having three planetary gears, in which three planetary gears 2, 2, 2 mesh with a sun gear 1 provided on an input shaft 7, and these planetary gears 2, 2, 2 mesh with the internal gear 3. In this planetary gear reduction gear, three planetary gears 2, 2, 2 are meshed with the sun gear 1, so the sun gear 1 can perform a self-aligning action, and power can be applied to each planetary gear 2. It is now possible to distribute them evenly.
ところが、この構成において減速比を大きくす
る場合には、太陽歯車１に対し遊星歯車２の歯数
を多くしなければならない。すなわち、遊星歯車
２の外径を出来るだけ大きくしなければならない
が、その外径は遊星歯車同士が干渉しない範囲ま
でが限度であり、隣接する二つの遊星歯車２，２
の中心間距離O1−O2を越えて大きくすることは
できない。したがつて、上述したように遊星歯車
式減速装置の減速比は、大きくても13.5までが限
界になつてしまうのである。 However, in order to increase the reduction ratio in this configuration, the number of teeth of the planetary gear 2 must be increased relative to the number of teeth of the sun gear 1. In other words, the outer diameter of the planetary gear 2 must be made as large as possible, but the outer diameter is limited to a range where the planetary gears do not interfere with each other, and two adjacent planetary gears 2, 2
cannot be increased beyond the center-to-center distance O 1 −O 2 . Therefore, as mentioned above, the reduction ratio of the planetary gear type reduction gear is limited to 13.5 at most.
一方、遊星歯車の数を２個にすれば、３個の場
合のように外径を制約されないから、さらに大き
な減速比を得ることはできる。しかし、遊星歯車
が２個では、上述したように太陽歯車が自動調心
できなくなるため動力が等配されず、極めて不円
滑な動力伝動になつて激しい振動等を伴うため、
実用性のないものにしかならない。 On the other hand, if the number of planetary gears is two, the outer diameter is not restricted as in the case of three, so a larger reduction ratio can be obtained. However, if there are two planetary gears, as mentioned above, the sun gear will not be able to self-align, and the power will not be distributed evenly, resulting in extremely uneven power transmission and severe vibrations.
It just becomes something impractical.
本発明の目的は、上述のような問題を解消し、
２台もの減速装置を連結するような大型化をする
ことなく、コンパクトな構成で、しかも安定な動
力等配のもとに、13.5を越えるような大きな減速
比を得ることができる遊星歯車式減速装置を提供
することにある。
The purpose of the present invention is to solve the above-mentioned problems,
A planetary gear type reduction gear that can obtain a large reduction ratio exceeding 13.5 with a compact structure and stable power distribution without increasing the size of connecting two reduction gears. The goal is to provide equipment.
上記目的を達成するようにする本発明は、互い
に180度の間隔を以て配置した２個の遊星歯車を
一組とし、その二組の遊星歯車を軸方向に前後に
ずらせると共に回転方向に互いに90度に位相をず
らせて、それぞれキヤリヤ上の遊星軸に回動自在
に軸支し、これら二組の遊星歯車を入力軸と一体
回転する共通の太陽歯車に噛合させる共に、出力
軸と一体回転する共通の内歯車に噛合させたこと
を特徴とするものである。
The present invention aims to achieve the above object by forming a set of two planetary gears arranged at an interval of 180 degrees, and by shifting the two sets of planetary gears back and forth in the axial direction and 90 degrees from each other in the rotational direction. The two sets of planetary gears are rotatably supported on planetary shafts on a carrier, with the phases shifted by degrees, and these two sets of planetary gears are meshed with a common sun gear that rotates integrally with the input shaft, and rotates integrally with the output shaft. It is characterized by meshing with a common internal gear.
以下、本発明を第３，４図に示す実施例により
説明する。 The present invention will be explained below with reference to the embodiments shown in FIGS. 3 and 4.
第３，４図において、７は高速側の入力軸、６
は低速側の出力軸である。入力軸７に一体に設け
た太陽歯車１には、軸方向の手前側に互いに180
度の間隔を以て配置された２個の遊星歯車２ａ，
２ａが噛合し、またその奥側にずれた位置に、同
じく互いに180度の間隔を以て配置された２個の
遊星歯車２ｂ，２ｂが同時に噛合している。しか
も、後者の奥側の遊星歯車２ｂ，２ｂは、前者の
手前側の遊星歯車２ａ，２ａとは回転方向に位相
を90度ずらせて配置されている。 In Figures 3 and 4, 7 is the input shaft on the high-speed side;
is the output shaft on the low speed side. The sun gear 1, which is integrally provided on the input shaft 7, has a 180-
two planetary gears 2a arranged with an interval of
2a meshes with each other, and two planetary gears 2b, 2b, which are also arranged at an interval of 180 degrees from each other, are meshed at the same time at a position shifted to the rear side. Furthermore, the latter planetary gears 2b, 2b on the back side are arranged with a phase shift of 90 degrees in the rotational direction from the former planetary gears 2a, 2a on the near side.
手前側の遊星歯車２ａ，２ａは、それぞれ遊星
軸５，５にベアリングを介して回動自在に軸支さ
れ、かつケーシング上のキヤリア４に支持されて
おり、また同様に奥側の遊星歯車２ｂ，２ｂは、
それぞれ遊星軸５′，５′にベアリングを介して回
動自在に軸支され、かつケーシング上のキヤリア
４に支持されている。また、これら４本の遊星軸
５，５，５′，５′の他端側はそれぞれ共通の固定
板４′に固定されている。 The planetary gears 2a, 2a on the near side are rotatably supported by planetary shafts 5, 5 through bearings, respectively, and supported by a carrier 4 on the casing, and similarly, the planetary gears 2b on the back side are supported by the carrier 4 on the casing. , 2b is
They are rotatably supported by planetary shafts 5', 5' via bearings, respectively, and supported by a carrier 4 on the casing. The other ends of these four planetary shafts 5, 5, 5', 5' are each fixed to a common fixing plate 4'.
上述のように１個の太陽歯車１に軸方向にずれ
て同時噛合する二組の遊星歯車２ａ，２ａと２
ｂ，２ｂとは、また共通の内歯車３に同時に噛合
している。そして、この内歯車３は出力軸６に固
定したアーム８に同心状に連結され、出力軸６と
共に一体になつて回転するようになつている。 As mentioned above, two sets of planetary gears 2a, 2a and 2 mesh with one sun gear 1 at the same time with axial displacement.
b and 2b also mesh with a common internal gear 3 at the same time. The internal gear 3 is concentrically connected to an arm 8 fixed to the output shaft 6, and rotates together with the output shaft 6.
上述した遊星歯車式減速装置によると、太陽歯
車１には二組の合計４個の遊星歯車２ａ，２ａ；
２ｂ，２ｂが同時に噛合しているが、その二組は
軸方向にずれて配置されているから互いに干渉す
ることがなく、かつ一組当たりの遊星歯車は２個
が180度の間隔を以て配置されたものであるか
ら、３個配置する場合に比べて各遊星歯車の外径
を可及的に大きくすることができる。すなわち、
遊星歯車の歯数を出来るだけ多くすることができ
るから、それよつて遊星歯車３個の場合の限界で
ある減速比13.5を越えた大きな減速比を得ること
ができる。しかも、従来のように２台もの減速装
置を連結するものでないから、極めてコンパクト
にすることができる。 According to the planetary gear type reduction gear described above, the sun gear 1 includes two sets of a total of four planetary gears 2a, 2a;
2b and 2b are in mesh at the same time, but the two sets are arranged offset in the axial direction so they do not interfere with each other, and the two planetary gears per set are arranged with an interval of 180 degrees. Therefore, the outer diameter of each planetary gear can be made as large as possible compared to the case where three planetary gears are arranged. That is,
Since the number of teeth of the planetary gear can be increased as much as possible, it is possible to obtain a large reduction ratio exceeding the limit of 13.5 when using three planetary gears. Furthermore, since two reduction gears are not connected as in the conventional case, it can be made extremely compact.
また、共通の太陽歯車１には、90度の間隔で４
個の遊星歯車２ａ，２ａ；２ｂ，２ｂが同時噛合
するから、その太陽歯車は自動調心作用を行うこ
とができ、各遊星歯車に動力の等配を行い極めて
円滑な動力伝達を行うことができる。 In addition, the common sun gear 1 has four gears at 90 degree intervals.
Since the planetary gears 2a, 2a; 2b, 2b mesh simultaneously, the sun gear can perform a self-aligning action, and the power can be equally distributed to each planetary gear to achieve extremely smooth power transmission. can.
また、遊星歯車２ａ，２ａ；２ｂ，２ｂは、そ
れぞれ遊星軸５，５′に回転自在に軸支されてい
るから、動力伝達時には各遊星軸５，５′はトル
ク伝達には寄与することがなく、しかも太陽歯車
１から遊星歯車２ａ、内歯車３への動力伝達と、
太陽歯車１から遊星歯車２ｂ、内歯車３への動力
伝達とは、共にそれぞれが軸方向に直交する同一
平面で行われるから、各遊星軸には転倒モーメン
トを発生することがない。したがつて、各遊星歯
車２ａ，２ａ；２ｂ，２ｂが軸方向に対し傾くよ
うなことはなく、そのため噛合が片当たりになつ
て不円滑な動力伝達になることがない。 Furthermore, since the planetary gears 2a, 2a; 2b, 2b are rotatably supported by the planetary shafts 5, 5', respectively, each planetary shaft 5, 5' does not contribute to torque transmission during power transmission. Moreover, power transmission from the sun gear 1 to the planetary gear 2a and the internal gear 3,
Since power is transmitted from the sun gear 1 to the planetary gears 2b and the internal gears 3 on the same plane perpendicular to the axial direction, no overturning moment is generated on each planetary shaft. Therefore, each of the planetary gears 2a, 2a; 2b, 2b will not be inclined with respect to the axial direction, and therefore the meshing will not be uneven and the power transmission will not be smooth.
また、遊星軸５，５′はトルク伝達を行わない
ので、比較的細い軸であつてもよく、コンパクト
化に一層有利である。 Further, since the planetary shafts 5 and 5' do not transmit torque, they may be relatively thin shafts, which is more advantageous for compactness.
上述したように本発明の遊星歯車式減速装置
は、従来のように大きな減速比にするため２台も
の減速装置を連結するものではないから、全体的
にコンパクトな構成にすることができる。そし
て、互いに180度の間隔を以て配置した２個の遊
星歯車を一組として太陽歯車に噛合させるため、
遊星歯車の外径を互いに干渉させることなく可及
的に大きくし、歯数を多くすることができるか
ら、遊星歯車が３個の場合における減速比の限界
である13.5を越える大きな減速比を得ることがで
きる。
As described above, the planetary gear type speed reduction device of the present invention does not have to connect two speed reduction devices to achieve a large speed reduction ratio as in the prior art, so it can have an overall compact configuration. Then, in order to mesh the sun gear as a set with two planetary gears arranged 180 degrees apart,
Since the outer diameter of the planetary gears can be made as large as possible without interfering with each other and the number of teeth can be increased, a large reduction ratio exceeding 13.5, which is the limit of reduction ratio when there are three planetary gears, can be obtained. be able to.
しかも、上述のような２個配置の遊星歯車を二
組設け、その二組を軸方向に前後にずらせると共
に回転方向に互いに90度の位相をずらせて共通の
太陽歯車に噛合させるため、それによつて４個の
遊星歯車を90度の間隔を以て同時に太陽歯車に噛
合させることになるから、太陽歯車は自動調心作
用を行い、各遊星歯車に動力の等配を行い極めて
円滑な動力伝達を行うことができる。 Moreover, in order to provide two sets of two planetary gears as described above, shift the two sets back and forth in the axial direction, and mesh with a common sun gear with a phase shift of 90 degrees from each other in the rotational direction, Therefore, the four planetary gears are meshed with the sun gear at the same time at 90 degree intervals, so the sun gear performs a self-aligning action, distributing power evenly to each planetary gear and achieving extremely smooth power transmission. It can be carried out.
また、上記構成において、遊星歯車は遊星軸に
対し回動自在にしてあるから、その遊星軸はトル
ク伝達を行わず、転倒モーメントを発生しない。
したがつて、遊星歯車と太陽歯車との噛合並びに
遊星歯車と内歯車との噛合において片当たりにな
ることはなく、極めて円滑な動力伝達を保証する
ようになる。 Furthermore, in the above configuration, since the planetary gear is rotatable relative to the planetary shaft, the planetary shaft does not transmit torque and does not generate an overturning moment.
Therefore, uneven contact will not occur in the meshing between the planetary gear and the sun gear and the meshing between the planetary gear and the internal gear, ensuring extremely smooth power transmission.
第１図は従来の遊星歯車式減速装置の内部正面
図、第２図は第１図の断面図、第３図は本発明の
実施例による遊星歯車式減速装置の内部正面図、
第４図は第３図の断面図である。
１……太陽歯車、２ａ，２ｂ……遊星歯車、３
……内歯車、４……キヤリア、５，５′……遊星
軸、６……出力軸、７……入力軸。
FIG. 1 is an internal front view of a conventional planetary gear type reduction gear, FIG. 2 is a sectional view of FIG. 1, and FIG. 3 is an internal front view of a planetary gear type reduction gear according to an embodiment of the present invention.
FIG. 4 is a sectional view of FIG. 3. 1...Sun gear, 2a, 2b...Planetary gear, 3
... Internal gear, 4 ... Carrier, 5, 5' ... Planetary shaft, 6 ... Output shaft, 7 ... Input shaft.
Claims (1)
星歯車を一組とし、その二組の遊星歯車を軸方向
に前後にずらせると共に回転方向に互いに90度に
位相をずらせて、それぞれキヤリヤ上の遊星軸に
回動自在に軸支し、これら二組の遊星歯車を入力
軸と一体回転する共通の太陽歯車に噛合させる共
に、出力軸と一体回転する共通の内歯車に噛合さ
せたことを特徴とする大きな減速比を取り得る遊
星歯車式減速装置。1 A set of two planetary gears arranged at a spacing of 180 degrees from each other is made, and the two sets of planetary gears are shifted back and forth in the axial direction, and the phases are shifted by 90 degrees from each other in the rotational direction, so that each gear is placed on a carrier. It is characterized by being rotatably supported on a planetary shaft, and these two sets of planetary gears mesh with a common sun gear that rotates integrally with the input shaft, and mesh with a common internal gear that rotates integrally with the output shaft. A planetary gear type reduction gear that can achieve a large reduction ratio.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12825779A JPS5652649A (en) | 1979-10-04 | 1979-10-04 | Planetary-gear type reduction gear capable of obtaining a large reduction ratio |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12825779A JPS5652649A (en) | 1979-10-04 | 1979-10-04 | Planetary-gear type reduction gear capable of obtaining a large reduction ratio |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5652649A JPS5652649A (en) | 1981-05-11 |
| JPS6233462B2 true JPS6233462B2 (en) | 1987-07-21 |
Family
ID=14980373
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12825779A Granted JPS5652649A (en) | 1979-10-04 | 1979-10-04 | Planetary-gear type reduction gear capable of obtaining a large reduction ratio |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5652649A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02108960U (en) * | 1989-02-17 | 1990-08-30 |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63309317A (en) * | 1987-06-09 | 1988-12-16 | Nippon Senjimia Kk | Wiper device |
| DE50000245D1 (en) * | 1999-08-12 | 2002-08-01 | Alpha Getriebebau Gmbh | PLANETARY GEAR TRANSMISSION |
| DE10324362A1 (en) * | 2003-05-27 | 2004-12-16 | A. Friedr. Flender Ag | Gear for driving a rotary tube |
| EP2275705B1 (en) * | 2008-03-13 | 2012-04-25 | Mitsubishi Heavy Industries, Ltd. | Transmission unit and wind power generator |
| BE1018966A3 (en) * | 2009-10-19 | 2011-12-06 | Hansen Transmissions Int | PLANETARY GEAR SYSTEM AND PLANET SUPPORT FOR USE IN SUCH PLANETARY GEAR SYSTEM. |
| ES2635871T3 (en) * | 2013-12-16 | 2017-10-05 | Areva Wind Gmbh | Planetary gear, wind turbine that has a planetary gear and use of a planetary gear |
| JP6227473B2 (en) * | 2014-04-18 | 2017-11-08 | ナブテスコ株式会社 | Reduction gear |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1299007A (en) * | 1969-04-26 | 1972-12-06 | Wuelfel Eisenwerk | Epicyclic gear |
-
1979
- 1979-10-04 JP JP12825779A patent/JPS5652649A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1299007A (en) * | 1969-04-26 | 1972-12-06 | Wuelfel Eisenwerk | Epicyclic gear |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02108960U (en) * | 1989-02-17 | 1990-08-30 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5652649A (en) | 1981-05-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4366727A (en) | Planetary-type of gear and procedure and apparatus for its production | |
| US4090416A (en) | Gear boxes | |
| US4043216A (en) | Compound pinions for use in epicyclic gear boxes | |
| JPS6233462B2 (en) | ||
| JPS5891949A (en) | Transmission gear for motion | |
| US4096763A (en) | Hypocycloidal reduction gearing | |
| US5123882A (en) | Compound planocentric cycloidal gear drives with orthogonal planet arrangements | |
| KR100294461B1 (en) | Reduction gear composed of planetary gear and differential gear set | |
| JPH0541854B2 (en) | ||
| JP2646270B2 (en) | Planetary gear set | |
| JPS62101943A (en) | Reducer | |
| JPH0634005A (en) | Planetary roller type power transmitting device | |
| CN104989791A (en) | Planetary mechanism and planetary reducer | |
| JPS6017560Y2 (en) | Continuously variable transmission capable of forward and reverse rotation | |
| GB1434928A (en) | Power transmissions | |
| US1812877A (en) | Variable speed device | |
| JPS63243549A (en) | Speed increasing/decreasing gear having planetary gear mechanism | |
| WO2023047422A1 (en) | A gear system | |
| US3587349A (en) | Axial gear train | |
| US2663201A (en) | Antivibration gear drive | |
| JP3011647B2 (en) | transmission | |
| JPH0565946A (en) | Speed change gear | |
| JPH0641000Y2 (en) | 3rd forward, 3rd reverse parallel-axis power shift transmission | |
| KR100289995B1 (en) | Reduction gear | |
| SU579480A1 (en) | Differential transmission |