JPH0634005A - Planetary roller type power transmitting device - Google Patents
Planetary roller type power transmitting deviceInfo
- Publication number
- JPH0634005A JPH0634005A JP18515892A JP18515892A JPH0634005A JP H0634005 A JPH0634005 A JP H0634005A JP 18515892 A JP18515892 A JP 18515892A JP 18515892 A JP18515892 A JP 18515892A JP H0634005 A JPH0634005 A JP H0634005A
- Authority
- JP
- Japan
- Prior art keywords
- planetary
- outer ring
- planetary roller
- rollers
- type power
- 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
Landscapes
- Friction Gearing (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、遊星ローラ式動力伝達
装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary roller type power transmission device.
【０００２】[0002]
【従来の技術】遊星ローラ式動力伝達装置は、図４およ
び図５に示すように、ハウジング２１に固定の外輪２２
と、この外輪２２の内側に同心に配置された太陽軸２３
と、太陽軸２３と外輪２２との間に圧接状に介装された
遊星ローラ２４の群と、ローラ群の各遊星ローラ２４の
公転に連動して回転するキャリア２５とからなるもので
ある。各遊星ローラ２４は、キャリア２５に突設された
遊星軸２６に回転自在に取り付けられている。2. Description of the Related Art A planetary roller type power transmission device, as shown in FIGS. 4 and 5, has an outer ring 22 fixed to a housing 21.
And the sun shaft 23 arranged concentrically inside the outer ring 22
And a group of planetary rollers 24 interposed between the sun shaft 23 and the outer ring 22 in pressure contact with each other, and a carrier 25 that rotates in association with the revolution of each planetary roller 24 of the roller group. Each planet roller 24 is rotatably attached to a planet shaft 26 provided on a carrier 25.
【０００３】増減速が一段の装置では、太陽軸２３が高
速側の入出力軸となり、キャリア２５には低速側の入出
力軸が直結される。In an apparatus having a single stage of acceleration / deceleration, the sun shaft 23 serves as a high speed side input / output shaft, and the low speed side input / output shaft is directly connected to the carrier 25.
【０００４】[0004]
【発明が解決しようとする課題】ところで、上記のよう
な動力伝達装置において変速比を大きく設定しようとす
ると、その変速比に応じて遊星ローラ２４の径と太陽軸
２３の径の比を大きくする必要がある。そして、遊星ロ
ーラ２４が大径になると、遊星ローラ２４どうしの干渉
を考慮しなければならなくなり、使用可能な遊星ローラ
２４の個数が減少する。例えば、変速比が６．９以上の
場合、使用しうる遊星ローラ２４の個数は三個になる。By the way, when the gear ratio is set to be large in the above power transmission device, the ratio of the diameter of the planetary roller 24 and the diameter of the sun shaft 23 is increased in accordance with the gear ratio. There is a need. When the planetary rollers 24 have a large diameter, interference between the planetary rollers 24 must be taken into consideration, and the number of usable planetary rollers 24 decreases. For example, when the gear ratio is 6.9 or more, the number of planet rollers 24 that can be used is three.
【０００５】このように、遊星ローラ２４の使用個数が
減少すると、材料力学的に、同じ圧接力を加えた場合で
も、遊星ローラ２４の個数が少なくなると外輪２２の変
形量は大きくなる。さらに、これら遊星ローラ２４の群
と外輪２２との間に滑りが生じないように、外輪２２に
対する遊星ローラ２４のしめしろを大きくしなければな
らない。その結果、外輪２２には、数少ない遊星ローラ
２４との接触個所に大きな圧接力が作用することにな
り、遊星ローラ２４の圧接による外輪２２の変形量が増
大し、これによって、回転むらが大きくなる。As described above, when the number of planet rollers 24 used decreases, the amount of deformation of the outer ring 22 increases when the number of planet rollers 24 decreases even when the same pressure contact force is applied in terms of material mechanics. Further, the interference of the planetary rollers 24 with respect to the outer ring 22 must be increased so that slippage does not occur between the group of these planetary rollers 24 and the outer ring 22. As a result, a large pressure contact force acts on the outer ring 22 at the contact points with the few planetary rollers 24, and the amount of deformation of the outer ring 22 due to the pressure contact of the planetary rollers 24 increases, thereby increasing the rotational unevenness. .
【０００６】これに対しては、外輪２２の肉厚を厚くし
て、その変形量をできるだけ少なくすることで、回転む
らを防止することができるが、その場合、外輪２２の肉
厚が非常に厚くなり、そのために、装置全体の外形寸法
が大きくなる、といった不都合が生じる。On the other hand, the unevenness of rotation can be prevented by increasing the thickness of the outer ring 22 and reducing the amount of deformation of the outer ring 22, but in this case, the thickness of the outer ring 22 is extremely large. As a result, the device becomes thicker, which results in an increase in the external dimensions of the entire device.
【０００７】本発明は、かかる従来の問題点に鑑み、外
輪の肉厚を厚くすることなく、充分に大きな変速比で回
転むらのない変速が行えるようにすることを課題とす
る。In view of the above-mentioned conventional problems, it is an object of the present invention to make it possible to perform a gear shift without rotational unevenness at a sufficiently large gear ratio without increasing the thickness of the outer ring.
【０００８】[0008]
【課題を解決するための手段】本発明は、上記の課題を
達成するために、固定の外輪と、この外輪の内側に同心
に配置された太陽軸と、太陽軸と外輪との間に圧接状に
介装された遊星ローラ群と、遊星ローラの公転に連動し
て回転するキャリアとからなる遊星ローラ式動力伝達装
置において、遊星ローラ群は、周方向交互に配置された
少なくとも二組の遊星ローラからなり、一方の組の遊星
ローラが他方の組の遊星ローラに対して太陽軸を共有し
つつ軸方向に偏位している構成とした。In order to achieve the above object, the present invention provides a fixed outer ring, a sun shaft concentrically arranged inside the outer ring, and a pressure contact between the sun shaft and the outer ring. In a planetary roller-type power transmission device including a planetary roller group that is interleaved and a carrier that rotates in association with the revolution of the planetary roller, the planetary roller group includes at least two sets of planets arranged alternately in the circumferential direction. The planetary rollers of one set are configured to be axially offset with respect to the other set of planetary rollers while sharing the sun axis.
【０００９】[0009]
【作用】上記の構成において、周方向に隣合う遊星ロー
ラは、互いに軸方向位置がずれているから、その周方向
間隔を狭めても干渉が生じない。したがって、多数の遊
星ローラを使用することができ、遊星ローラの個数が増
えることで、外輪は変形しにくくなる。In the above structure, the planet rollers that are adjacent to each other in the circumferential direction are displaced from each other in the axial direction, so that interference does not occur even if the circumferential interval is narrowed. Therefore, a large number of planet rollers can be used, and the number of planet rollers increases, so that the outer ring is less likely to be deformed.
【００１０】[0010]
【実施例】以下、本発明の詳細を図１ないし図３に示す
実施例に基づいて説明する。このうち、図１および図２
は本発明の第１実施例に係り、図１は、遊星ローラ式動
力伝達装置の軸方向に沿った断面図、図２は、その軸直
交方向に沿った断面図である。DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the present invention will be described below with reference to the embodiments shown in FIGS. Of these, FIG. 1 and FIG.
1 relates to a first embodiment of the present invention. FIG. 1 is a sectional view taken along an axial direction of a planetary roller power transmission device, and FIG. 2 is a sectional view taken along a direction orthogonal to the axis.
【００１１】図１および図２に示すように、この実施例
の遊星ローラ式動力伝達装置は、基本的に、従来の装置
と同様に、ハウジング１に固定の外輪２と、この外輪２
の内側に同心に配置された太陽軸３と、太陽軸３と外輪
２との間に圧接状に介装された遊星ローラ４，５（５
Ａ，５Ｂ）の群と、ローラ群の各遊星ローラ４，５の公
転に連動して回転するキャリア６とから構成されたもの
であり、各遊星ローラ４，５は、キャリア６に突設され
た遊星軸７，８にそれぞれ回転自在に取り付けられてい
る。As shown in FIGS. 1 and 2, the planetary roller type power transmission device of this embodiment is basically an outer ring 2 fixed to a housing 1 and this outer ring 2 similarly to the conventional device.
And a planetary roller 4, 5 (5) interposed between the sun shaft 3 and the outer ring 2 in a pressure contact manner.
A, 5B) and a carrier 6 that rotates in conjunction with the revolution of each planet roller 4, 5 of the roller group. Each planet roller 4, 5 is provided on the carrier 6 so as to project therefrom. The planetary shafts 7 and 8 are rotatably attached.
【００１２】この実施例の遊星ローラ式動力伝達装置が
従来のものと異なるのは、遊星ローラ４，５の群が、第
１および第２の二組の遊星ローラ４，５からなり、これ
ら両組の遊星ローラ４，５は、周方向に沿って等間隔で
交互に配置されており、第１組の遊星ローラ４が第２組
の遊星ローラ５に対して軸方向に偏位していることであ
る。The planetary roller type power transmission device of this embodiment differs from the conventional one in that the group of planetary rollers 4, 5 comprises two sets of first and second planetary rollers 4, 5. The planetary rollers 4 and 5 of the set are alternately arranged at equal intervals along the circumferential direction, and the planetary roller 4 of the first set is axially offset from the planetary roller 5 of the second set. That is.
【００１３】図示例では、第１組を構成するのは、三個
の比較的広幅の遊星ローラ４である。第２組を構成する
のは、同一の遊星軸８上に間隔をおいて設けられた二個
の細幅の遊星ローラ５Ａ，５Ｂを一対として、その三対
である。そして、第１組の遊星ローラ４に対して、ほぼ
そのローラ幅の分だけ軸方向前後にずれた位置に、第２
組の各対の遊星ローラ５Ａ，５Ｂが配置され、軸方向に
は、第２組の一対の遊星ローラ５Ａ，５Ｂの間に、第１
組の遊星ローラ４が位置する。In the illustrated example, the first set comprises three relatively wide planetary rollers 4. The second set is composed of two pairs of two narrow width planetary rollers 5A and 5B provided on the same planetary shaft 8 at intervals, and three pairs thereof. Then, with respect to the first set of planetary rollers 4, a second roller is provided at a position that is shifted in the axial direction by approximately the roller width.
A pair of planet rollers 5A, 5B is arranged, and a first pair of planet rollers 5A, 5B is axially arranged between the pair of planet rollers 5A, 5B.
A set of planet rollers 4 is located.
【００１４】上記の構成において、第１組の遊星ローラ
４は、第２組の遊星ローラ５と周方向に隣合うが、この
ように隣合う遊星ローラ４，５は、互いに軸方向位置が
ずれていて、食い違い状に位置するから、軸間の間隔が
狭くても、干渉が生じない。したがって、従来の装置で
は三個の遊星ローラしか使用できなかったところに、そ
れに倍する数の遊星ローラ４，５を設けることができ
る。In the above structure, the planetary rollers 4 of the first set are circumferentially adjacent to the planetary rollers 5 of the second set, and the planetary rollers 4 and 5 adjacent to each other in this way are axially displaced from each other. However, since the shafts are staggered, interference does not occur even if the distance between the shafts is narrow. Therefore, in the conventional device, only three planetary rollers can be used, but the number of planetary rollers 4 and 5 can be doubled.
【００１５】このように、従来の装置に比べ、遊星ロー
ラ４，５の使用個数が増加するから、遊星ローラ４，５
の圧接による外輪２の変形量が減少し、これによって、
回転むらは極めて小さくなる。As described above, the number of the planetary rollers 4 and 5 used is increased as compared with the conventional apparatus, so that the planetary rollers 4 and 5 are used.
The amount of deformation of the outer ring 2 due to the pressure contact of
Rotational unevenness is extremely small.
【００１６】上記の実施例では、一方の遊星ローラ５の
組（第２組）に、同一の遊星軸８上に設けた二個一対の
遊星ローラ５Ａ，５Ｂを用いたが、このような遊星ロー
ラを両組に用いてもよいし、また、図３に示す実施例の
ように、全く用いなくてもよい。In the above embodiment, one pair of planet rollers 5 (second group) is provided with a pair of two planet rollers 5A and 5B provided on the same planet shaft 8. Rollers may be used for both sets, or none at all, as in the embodiment shown in FIG.
【００１７】図３は、本発明の第２実施例に係る遊星ロ
ーラ式動力伝達装置の軸方向に沿った断面図である。な
お、その軸直交方向に沿った断面形状は、図２に示した
形状とほぼ同様であるので、その図示は省略する。FIG. 3 is a sectional view taken along the axial direction of a planetary roller power transmission device according to a second embodiment of the present invention. The cross-sectional shape along the direction orthogonal to the axis is almost the same as the shape shown in FIG. 2, and therefore its illustration is omitted.
【００１８】この第２実施例では、第１組の遊星ローラ
４も、第２組の遊星ローラ５も、いずれも三個の比較的
広幅のローラである。両組の遊星ローラ４，５は、周方
向に沿って等間隔で交互に配置されており、第１組の遊
星ローラ４に対して、ほぼそのローラ幅の分だけ軸方向
にずれた位置に、第２組の遊星ローラ５が位置してい
る。その他の構造は、第１実施例と同じであるので、対
応する部分には同一の符号を付して、詳細な説明は省略
する。In the second embodiment, both the first set of planetary rollers 4 and the second set of planetary rollers 5 are three relatively wide rollers. The planetary rollers 4 and 5 of both sets are alternately arranged at equal intervals along the circumferential direction, and are located at positions axially displaced from the planetary rollers 4 of the first set by about the roller width. , The second set of planetary rollers 5 is located. Since the other structure is the same as that of the first embodiment, the corresponding portions are designated by the same reference numerals and detailed description thereof will be omitted.
【００１９】この実施例でも、従来の装置に比べ、遊星
ローラの個数が２倍になるので、外輪２の変形量が減少
し、回転むらが小さくなる点は、第１実施例の場合と同
じである。Also in this embodiment, the number of planetary rollers is doubled as compared with the conventional device, so that the deformation amount of the outer ring 2 is reduced and the uneven rotation is reduced, which is the same as the case of the first embodiment. Is.
【００２０】なお、上記各実施例では、各組の遊星ロー
ラを三個もしくは三対としたが、各組の遊星ローラの個
数はこれに限定されるものではなく、変速比の値によっ
ては、各組の遊星ローラを二個もしくは二対としてもよ
いし、また、四個もしくは四対以上とすることも可能で
ある。In each of the above-mentioned embodiments, the number of planetary rollers of each set is three or three, but the number of planetary rollers of each set is not limited to this, and depending on the value of the gear ratio, There may be two or two pairs of planet rollers in each set, or four or more pairs of planet rollers.
【００２１】[0021]
【発明の効果】以上述べたように、本発明によれば、多
数の遊星ローラを使用することが可能で、多数の遊星ロ
ーラにより、遊星ローラの圧接による外輪の変形量を少
なくし、回転むらを防止することができ、大きな変速比
での変速が可能になる。したがって、従来のように外輪
の肉厚を厚くする必要がなく、装置の外形寸法の増大を
招来しない。As described above, according to the present invention, it is possible to use a large number of planetary rollers, and the large number of planetary rollers reduces the amount of deformation of the outer ring due to the pressure contact of the planetary rollers, resulting in uneven rotation. Can be prevented, and gear shifting with a large gear ratio is possible. Therefore, it is not necessary to increase the thickness of the outer ring as in the conventional case, and the outer dimension of the device does not increase.
【００２２】また、遊星ローラの外輪に対するしめしろ
が小さくなるので、摩耗が少なくなって寿命が長くなる
ほか、組立も容易になる。Further, since the interference of the planetary roller with respect to the outer ring is small, wear is reduced, the life is extended, and the assembly is facilitated.
【図１】本発明の第１実施例に係る遊星ローラ式動力伝
達装置の軸方向断面図FIG. 1 is an axial sectional view of a planetary roller power transmission device according to a first embodiment of the present invention.
【図２】上記実施例の軸直交方向断面図FIG. 2 is a cross-sectional view in the direction orthogonal to the axis of the above embodiment.
【図３】本発明の第２実施例に係る遊星ローラ式動力伝
達装置の軸方向断面図FIG. 3 is an axial sectional view of a planetary roller type power transmission device according to a second embodiment of the present invention.
【図４】従来の遊星ローラ式動力伝達装置の軸方向断面
図FIG. 4 is an axial sectional view of a conventional planetary roller power transmission device.
【図５】上記従来例の軸直交方向断面図FIG. 5 is a cross-sectional view of the above conventional example in the direction orthogonal to the axis.
１ ハウジング ２ 外輪 ３ 太陽軸 ４ 遊星ローラ（第１組） ５ 遊星ローラ（第２組） ６ キャリア 1 Housing 2 Outer Ring 3 Sun Axis 4 Planetary Roller (1st Set) 5 Planetary Roller (2nd Set) 6 Carrier
Claims (1)
配置された太陽軸と、太陽軸と外輪との間に圧接状に介
装された遊星ローラ群と、遊星ローラの公転に連動して
回転するキャリアとからなる遊星ローラ式動力伝達装置
において、 遊星ローラ群は、周方向交互に配置された少なくとも二
組の遊星ローラからなり、一方の組の遊星ローラが他方
の組の遊星ローラに対して太陽軸を共有しつつ軸方向に
偏位している、ことを特徴とする遊星ローラ式動力伝達
装置。1. A fixed outer ring, a sun shaft concentrically arranged inside the outer ring, a planetary roller group interposed in pressure contact between the sun shaft and the outer ring, and interlocked with the revolution of the planetary roller. In a planetary roller type power transmission device including a rotating carrier, the planetary roller group includes at least two sets of planetary rollers that are alternately arranged in the circumferential direction, and one set of planetary rollers is the other set of planetary rollers. The planetary roller type power transmission device is characterized in that it is offset in the axial direction while sharing the sun axis.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18515892A JPH0634005A (en) | 1992-07-13 | 1992-07-13 | Planetary roller type power transmitting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18515892A JPH0634005A (en) | 1992-07-13 | 1992-07-13 | Planetary roller type power transmitting device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0634005A true JPH0634005A (en) | 1994-02-08 |
Family
ID=16165854
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18515892A Pending JPH0634005A (en) | 1992-07-13 | 1992-07-13 | Planetary roller type power transmitting device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0634005A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1988000387A1 (en) * | 1986-06-27 | 1988-01-14 | Namiki Precision Jewel Co., Ltd. | Process for producing permanent magnets |
| EP0826866A2 (en) | 1996-09-02 | 1998-03-04 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| EP0913557A2 (en) | 1997-10-29 | 1999-05-06 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| US6085707A (en) * | 1997-05-29 | 2000-07-11 | Honda Giken Kogvo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| KR20170113170A (en) * | 2016-03-31 | 2017-10-12 | 가부시키가이샤 도요다 지도숏키 | Speed increaser |
-
1992
- 1992-07-13 JP JP18515892A patent/JPH0634005A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1988000387A1 (en) * | 1986-06-27 | 1988-01-14 | Namiki Precision Jewel Co., Ltd. | Process for producing permanent magnets |
| EP0826866A2 (en) | 1996-09-02 | 1998-03-04 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| US6016779A (en) * | 1996-09-02 | 2000-01-25 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| US6085707A (en) * | 1997-05-29 | 2000-07-11 | Honda Giken Kogvo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| EP0913557A2 (en) | 1997-10-29 | 1999-05-06 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating system in internal combustion engine |
| KR20170113170A (en) * | 2016-03-31 | 2017-10-12 | 가부시키가이샤 도요다 지도숏키 | Speed increaser |
| US10260604B2 (en) | 2016-03-31 | 2019-04-16 | Kabushiki Kaisha Toyota Jidoshokki | Speed increaser |
| DE102017106760B4 (en) | 2016-03-31 | 2022-05-25 | Kabushiki Kaisha Toyota Jidoshokki | SPEED UP |
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