JPH09264393A - Planetary roller type power transmission - Google Patents
Planetary roller type power transmissionInfo
- Publication number
- JPH09264393A JPH09264393A JP7734496A JP7734496A JPH09264393A JP H09264393 A JPH09264393 A JP H09264393A JP 7734496 A JP7734496 A JP 7734496A JP 7734496 A JP7734496 A JP 7734496A JP H09264393 A JPH09264393 A JP H09264393A
- Authority
- JP
- Japan
- Prior art keywords
- carrier
- planetary roller
- output shaft
- input shaft
- power transmission
- 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.)
- Withdrawn
Links
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、遊星ローラがキャ
リアとすべり接触することにより遊星ローラの公転をキ
ャリアに伝達する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 for transmitting the revolution of a planetary roller to a carrier when the planetary roller comes into sliding contact with the carrier.
【０００２】[0002]
【従来の技術】従来から知られている遊星ローラ式動力
伝達装置として、図１０に示すものがある。この遊星ロ
ーラ式動力伝達装置は、原動機軸（図示せず）と連結さ
れる入力軸１と、入力軸１の外周面上に円周等間隔に配
置された複数（例えば４個）の遊星ローラ２と、円筒部
に円周等間隔に設けた複数（遊星ローラ２と同数）のキ
ャリアポケット部３ａにそれぞれ遊星ローラ２を回転自
在に保持するキャリア３と、入力軸１と同心状に固定さ
れ、入力軸１との間に各遊星ローラ２を転がり摩擦接触
状態に介装させる固定輪４とからなり、原動機軸により
入力軸１が回転することによって、それぞれの遊星ロー
ラ２が入力軸１との転がり摩擦接触により自転および公
転し、これによってキャリア３が遊星ローラ２とのすべ
り接触により遊星ローラ２の公転回転数をもって回転す
ることで出力軸５へ動力伝達を行なうようになってい
る。2. Description of the Related Art A conventionally known planetary roller type power transmission device is shown in FIG. This planetary roller type power transmission device includes an input shaft 1 connected to a prime mover shaft (not shown), and a plurality of (for example, four) planetary rollers arranged at equal intervals on the outer peripheral surface of the input shaft 1. 2, a carrier 3 that holds the planetary rollers 2 rotatably in a plurality of carrier pockets 3a (same number as the planetary rollers 2) provided at equal intervals around the cylinder, and fixed concentrically with the input shaft 1. , A fixed wheel 4 interposing each planetary roller 2 in rolling contact with the input shaft 1, and by rotating the input shaft 1 by the prime mover shaft, each planetary roller 2 becomes the input shaft 1. The rolling frictional contact causes the carrier 3 to rotate and revolve, whereby the carrier 3 rotates with the revolution speed of the planetary roller 2 due to the sliding contact with the planetary roller 2, thereby transmitting power to the output shaft 5.
【０００３】従来、上記遊星ローラ式動力伝達装置で
は、図１１に示すように、遊星ローラ２を保持すること
を目的としているキャリア３と出力軸５とが一体に形成
されている。Conventionally, in the planetary roller type power transmission device, as shown in FIG. 11, a carrier 3 for holding the planetary roller 2 and an output shaft 5 are integrally formed.
【０００４】[0004]
【発明が解決しようとする課題】図１０に示される遊星
ローラ２がキャリア３とすべり接触することで遊星ロー
ラ２の公転をキャリア３に伝達するタイプの遊星ローラ
式動力伝達装置において、潤滑に関する設計上で問題と
なるのは、遊星ローラ２とキャリア３のすべり接触部で
ある。In the planetary roller type power transmission device of the type shown in FIG. 10 in which the planetary roller 2 is in sliding contact with the carrier 3 to transmit the revolution of the planetary roller 2 to the carrier 3, a design related to lubrication is provided. The above problem is the sliding contact portion between the planetary roller 2 and the carrier 3.
【０００５】図１０に示される遊星ローラ式動力伝達装
置においては、通常、入力軸１と出力軸５がそれぞれ軸
受で支持されて使用される。したがって、図１１に示す
ように、キャリア３と出力軸５が一体であるならば、入
力軸１と出力軸５との軸心が一致するときのみ、遊星ロ
ーラ２は、図１２に示すように、キャリア３の転走面３
ａ1 の中央部付近で接触し、遊星ローラ２とキャリア３
のすべり接触部の接触面圧値は最も低くなる条件で使用
することができる。しかしながら、入力軸１と出力軸５
の軸心がずれると、遊星ローラ２とキャリア３の接触点
が転走面３ａ1 の中央からはずれることになり、その結
果、トルク伝達に対して無効な半径方向力が遊星ローラ
２とキャリア３の接触点における法線力に含まれるよう
になるか、または、遊星ローラ２とキャリア３の接触点
からキャリア３の軸心まで距離が減少する。そのため、
伝達トルクが一定であっても遊星ローラ２とキャリア３
の接触点における法線力が増加し、その結果、接触面圧
値が増加するとともに、遊星ローラ２とキャリア３のす
べり接触部のすべりによる動力損失も増加する。そし
て、入力軸１と出力軸５の軸心のずれが大きいと、図１
３に示すように、遊星ローラ２とキャリア３は片当たり
の状態となり、キャリア３の摩耗量が著しく増加し、固
定輪４と遊星ローラ２の接触部や入力軸１と遊星ローラ
２の接触部に磨耗粉が噛み込まれることによる作動不能
が引き起こされる可能性がある。The planetary roller type power transmission device shown in FIG.
In general, the input shaft 1 and the output shaft 5 are each a shaft.
Used by being supported by a receiver. Therefore, as shown in FIG.
If the carrier 3 and the output shaft 5 are integrated,
Only when the axes of force shaft 1 and output shaft 5 are aligned
The carrier 2 is a rolling surface 3 of the carrier 3 as shown in FIG.
a1 Contacting near the central part of the planetary roller 2 and carrier 3
Used under the condition that the contact surface pressure value of the sliding contact part is the lowest
can do. However, input shaft 1 and output shaft 5
If the axis center of is shifted, the contact point between the planetary roller 2 and the carrier 3
Is rolling surface 3a1 Will be off the center of the
As a result, an ineffective radial force for torque transmission is applied to the planet roller.
To be included in the normal force at the contact point between 2 and carrier 3.
Or the contact point between the planetary roller 2 and the carrier 3
To the axis of the carrier 3 decreases. for that reason,
Even if the transmission torque is constant, the planetary roller 2 and carrier 3
The normal force at the contact point of the
As the value increases, the planetary roller 2 and carrier 3
The power loss due to the slip of the slip contact part also increases. Soshi
If there is a large misalignment between the input shaft 1 and the output shaft 5,
As shown in Fig. 3, the planetary roller 2 and the carrier 3 are one-sided
And the amount of wear of the carrier 3 is significantly increased,
Contact part between fixed wheel 4 and planetary roller 2, input shaft 1 and planetary roller
Inoperable due to abrasion powder being caught in the contact part of 2
Can be caused.
【０００６】しかしながら、遊星ローラ式動力伝達装置
の入力軸１と出力軸５の同軸度は、入力軸１・出力軸５
（キャリア３）等の構成部材やハウジングの製作精度お
よびそれらの組立精度に依存するため、図１２に示すよ
うな遊星ローラ２とキャリア３の最適な接触状態を得る
ためには、高精度な加工精度および組立精度が要求さ
れ、コストが上昇する。However, the coaxiality between the input shaft 1 and the output shaft 5 of the planetary roller type power transmission device is the same as the input shaft 1 and the output shaft 5.
Since it depends on the manufacturing precision of the components such as (carrier 3) and the housing and their assembling precision, in order to obtain the optimum contact state between the planetary roller 2 and the carrier 3 as shown in FIG. Precision and assembling precision are required, and cost increases.
【０００７】また、遊星ローラ２の曲率半径をｒ1 、キ
ャリア３の転走面３ａ1 の曲率半径をｒ2 とし、遊星ロ
ーラ２とキャリア３の接触部にジャーナル軸受の理論を
適用すると、（ｒ2 −ｒ1 ）／ｒ1 ＝１／１０００〜１
／５００とするのが潤滑上好ましいとされている。しか
しながら、このような曲率半径ｒ2 では、入力軸１と出
力軸５の軸心が０．００１ｒ1 のオーダー分ずれるだけ
で、図１３に示すように、遊星ローラ２とキャリア３は
片当たりを起こしてしまう。このような遊星ローラ２と
キャリア３の片当たりを防ぐためには、曲率半径ｒ2 は
上述の最適値よりも大きくしなければならず、このこと
によりさらに接触面圧が上昇することになる。The radius of curvature of the planetary roller 2 is r 1 , Rolling surface 3a 1 of carrier 3 The radius of curvature of r 2 If the theory of journal bearing is applied to the contact portion between the planetary roller 2 and the carrier 3, (r 2 -R 1 ) / R 1 = 1 / 1000-1
It is said that / 500 is preferable for lubrication. However, such a radius of curvature r 2 Then, the shaft center of the input shaft 1 and the output shaft 5 is 0.001r 1 However, as shown in FIG. 13, the planetary roller 2 and the carrier 3 have a partial contact with each other. In order to prevent such uneven contact between the planetary roller 2 and the carrier 3, the radius of curvature r 2 Must be larger than the above-mentioned optimum value, which further increases the contact surface pressure.
【０００８】そこで、本発明は、入力軸と出力軸の軸心
がずれても遊星ローラとキャリアとを最適な状態で接触
することを目的とする。Therefore, an object of the present invention is to bring the planet roller and the carrier into contact with each other in an optimum state even if the axes of the input shaft and the output shaft are deviated from each other.
【０００９】[0009]
【課題を解決するための手段】前述した目的を達成する
ため、本発明は、キャリアを出力軸と別体に形成し、キ
ャリアを出力軸に対して半径方向の自由度を持つ結合方
式で取り付けたこと特徴とする遊星ローラ式動力伝達装
置を提供する。In order to achieve the above-mentioned object, according to the present invention, a carrier is formed separately from an output shaft, and the carrier is attached to the output shaft by a coupling method having a radial degree of freedom. Provided is a planetary roller type power transmission device.
【００１０】前記遊星ローラ式動力伝達装置において、
キャリアを潤滑性能の良好な材料で形成するか、キャリ
アの遊星ローラとの転走面に潤滑性能を向上させる表面
処理を施す。In the planetary roller type power transmission device,
The carrier is formed of a material having a good lubricating performance, or the rolling surface of the carrier with the planetary roller is subjected to a surface treatment for improving the lubricating performance.
【００１１】キャリアを出力軸と別体に形成し、キャリ
アを出力軸に対して半径方向の自由度を持つ結合方式で
取り付けたことで、入力軸と出力軸の軸心のずれがキャ
リアと出力軸の結合部分で吸収されてキャリアの軸心が
入力軸の軸心にならい、遊星ローラとキャリアを最適な
接触状態にすることができる。Since the carrier is formed separately from the output shaft and the carrier is attached by the coupling method having the degree of freedom in the radial direction with respect to the output shaft, the deviation of the axis between the input shaft and the output shaft causes the carrier and the output. The shaft center of the carrier is absorbed by the connecting portion of the shaft and follows the shaft center of the input shaft, so that the planet roller and the carrier can be brought into an optimum contact state.
【００１２】キャリアを潤滑性能の良好な材料で形成す
るか、キャリアの遊星ローラとの転走面に潤滑性能を向
上させる表面処理を施すことで、キャリアと遊星ローラ
の間の摩擦係数を低減できる。The friction coefficient between the carrier and the planetary roller can be reduced by forming the carrier with a material having a good lubricating property or by subjecting the rolling surface of the carrier with the planetary roller to a surface treatment for improving the lubricating property. .
【００１３】また、本発明は、キャリアを複数の遊星ロ
ーラを保持する機能を有するキャリアピースから構成
し、各キャリアピースを出力軸に対して自由度を持つ結
合方式で円周等間隔に取り付けたことを特徴とする遊星
ローラ式動力伝達装置を提供する。Further, according to the present invention, the carrier is composed of carrier pieces having a function of holding a plurality of planetary rollers, and the carrier pieces are attached at equal intervals around the circumference by a coupling system having a degree of freedom with respect to the output shaft. A planetary roller type power transmission device is provided.
【００１４】前記遊星ローラ式動力伝達装置において、
キャリアピースを潤滑性能の良好な材料で形成するか、
キャリアピースの遊星ローラとの転走面に潤滑性能を向
上させる表面処理を施す。In the planetary roller type power transmission device,
Either form the carrier piece with a material with good lubrication performance, or
A surface treatment is applied to the rolling surface of the carrier piece with the planetary roller to improve lubrication performance.
【００１５】キャリアを複数の遊星ローラを保持する機
能を有するキャリアピースから構成し、各キャリアピー
スを出力軸に対して自由度を持つ結合方式で円周等間隔
に取り付けることで、入力軸と出力軸の軸心のずれがキ
ャリアピースと出力軸の結合部分で吸収されてキャリア
ピースが遊星ローラにならい、遊星ローラとキャリアピ
ースを最適な接触状態にすることができる。The carrier is composed of a carrier piece having a function of holding a plurality of planetary rollers, and each carrier piece is attached to the output shaft at equal intervals by a coupling method having a degree of freedom with respect to the input shaft and the output shaft. The misalignment of the shaft center is absorbed by the connecting portion between the carrier piece and the output shaft, and the carrier piece follows the planetary roller, so that the planetary roller and the carrier piece can be brought into an optimum contact state.
【００１６】キャリアピースを潤滑性能の良好な材料で
形成するか、キャリアピースの遊星ローラとの転走面に
潤滑性能を向上させる表面処理を施すことで、キャリア
ピースと遊星ローラの間の摩擦係数を低減できる。The coefficient of friction between the carrier piece and the planetary roller is formed by forming the carrier piece with a material having a good lubricating performance or by subjecting the rolling surface of the carrier piece with the planetary roller to a surface treatment for improving the lubricating performance. Can be reduced.
【００１７】[0017]
【発明の実施の形態】以下、本発明の実施の形態につい
て説明する。なお、本発明の遊星ローラ式動力伝達装置
は、基本的な構成要素に関する限り、図１０に示される
ものと同じくするので、実質上同一の部材ないし部分は
すべての図を通じて同一の参照符号で示すこととし、重
複する説明は省略する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below. Note that the planetary roller power transmission device of the present invention is the same as that shown in FIG. 10 as far as the basic constituent elements are concerned, and therefore substantially the same members or portions are denoted by the same reference numerals throughout the drawings. Therefore, duplicate description will be omitted.
【００１８】図１および図２は、本発明の実施の形態に
係る遊星ローラ式動力伝達装置を示している。この遊星
ローラ式動力伝達装置が従来のものと異なるのは、キャ
リア３と出力軸５を別体に形成し、キャリア３が出力軸
５に対して半径方向の自由度を持つ結合方式で取り付け
たことである。1 and 2 show a planetary roller power transmission device according to an embodiment of the present invention. This planetary roller type power transmission device differs from the conventional one in that the carrier 3 and the output shaft 5 are formed separately, and the carrier 3 is attached to the output shaft 5 by a coupling method having a degree of freedom in the radial direction. That is.
【００１９】キャリア３は、遊星ローラ２を回転自在に
保持する複数（遊星ローラと同数）のポケット部３ａを
円周等間隔に設け、かつ、座部３ｂに複数（例えば４
個）の差込孔６を円周等間隔に設けてある。The carrier 3 is provided with a plurality of pocket portions 3a (the same number as the planet rollers) for rotatably holding the planet rollers 2 at equal intervals on the circumference and a plurality of seat portions 3b (for example, 4).
Individual insertion holes 6 are provided at equal intervals around the circumference.
【００２０】出力軸５は、軸端に一体に設けた座部５ａ
に、キャリア３の差込孔６と対向するようにピンを打ち
込むかまたはピン状突起を一体形成した差込部材７が設
けてあり、この差込部材７をキャリア３の差込孔６に差
し込んでキャリア３と結合することにより、遊星ローラ
２の公転が、キャリア３と差込部材７を介して伝達され
るようになっている。The output shaft 5 is a seat portion 5a integrally provided at the shaft end.
In addition, there is provided an insertion member 7 in which a pin is driven or a pin-shaped projection is integrally formed so as to face the insertion hole 6 of the carrier 3, and the insertion member 7 is inserted into the insertion hole 6 of the carrier 3. The planetary roller 2 is revolved by being coupled to the carrier 3 via the carrier 3 and the insertion member 7.
【００２１】この実施の形態の遊星ローラ式動力伝達装
置は、キャリア３と出力軸５を一体に形成せず、キャリ
ア３の差込孔６に出力軸５の差込部材７を差し込んでキ
ャリア３と出力軸５を結合することで、キャリア３に差
込孔６と差込部材７のすきま分による出力軸５に対する
半径方向の自由度が与えられるため、入力軸１・出力軸
５（キャリア３）等の構成部品やハウジングの加工精
度、さらにそれらの組立精度に起因する入力軸１と出力
軸５の軸心のずれがキャリア３と出力軸５の結合部分で
吸収され、キャリア３の軸心が入力軸１の軸心にならう
ことができる。そのため、遊星ローラ２とキャリア３の
間で図１２に示すような最適な接触状態が得られ、接触
面圧値が最も低い状態での運転が可能となる。その結
果、キャリア３または遊星ローラ２の摩耗量を低減する
ことができ、摩耗による損傷・作動不能を防止できる。
また、遊星ローラ２とキャリア３の間の法線力を小さく
できるため、遊星ローラ２とキャリア３の間のすべりに
よる動力損失を低減でき、発熱による潤滑剤の劣化等を
抑えることができる。In the planetary roller type power transmission device of this embodiment, the carrier 3 and the output shaft 5 are not integrally formed, but the insertion member 7 of the output shaft 5 is inserted into the insertion hole 6 of the carrier 3 and the carrier 3 is formed. By coupling the output shaft 5 with the output shaft 5, the carrier 3 is provided with a degree of freedom in the radial direction with respect to the output shaft 5 due to the clearance between the insertion hole 6 and the insertion member 7, so that the input shaft 1 and the output shaft 5 (the carrier 3 ) Etc., the processing accuracy of the components and the housing, and the misalignment of the shaft center of the input shaft 1 and the output shaft 5 due to their assembling accuracy is absorbed by the coupling part of the carrier 3 and the output shaft 5, and the shaft center of the carrier 3 is absorbed. Can follow the axis of the input shaft 1. Therefore, the optimum contact state as shown in FIG. 12 is obtained between the planetary roller 2 and the carrier 3, and the operation can be performed in the state where the contact surface pressure value is the lowest. As a result, the amount of wear of the carrier 3 or the planetary rollers 2 can be reduced, and damage and inoperability due to wear can be prevented.
Further, since the normal force between the planetary roller 2 and the carrier 3 can be reduced, power loss due to slippage between the planetary roller 2 and the carrier 3 can be reduced, and deterioration of the lubricant due to heat generation can be suppressed.
【００２２】なお、上述した実施の形態では、キャリア
３に差込孔６を設け、出力軸５に差込部材７を設けてい
るが、キャリア３に差込部材７を設け、出力軸５に差込
孔６を設けても良い。In the above embodiment, the carrier 3 is provided with the insertion hole 6 and the output shaft 5 is provided with the insertion member 7. However, the carrier 3 is provided with the insertion member 7 and the output shaft 5 is provided with the insertion member 7. The insertion hole 6 may be provided.
【００２３】図３〜図６はキャリア３と出力軸５の各種
の結合方式をそれぞれ示す。3 to 6 show various coupling methods of the carrier 3 and the output shaft 5, respectively.
【００２４】図３に示される結合方式は、キャリア３の
座部３ｂにキー溝８を有する嵌挿孔９を設け、かつ、出
力軸５の軸端にキー１０を設けてあり、キャリア３の嵌
挿孔９に出力軸５の軸端を嵌挿すると同時にキー溝８に
キー１０を嵌め込むことによってキャリア３と出力軸５
は結合され、遊星ローラ２の公転は、キャリア３とキー
１０を介して出力軸５に伝達される。In the coupling system shown in FIG. 3, a seat 3b of the carrier 3 is provided with a fitting hole 9 having a key groove 8 and a key 10 is provided at the shaft end of the output shaft 5, so that the carrier 3 By fitting the shaft end of the output shaft 5 into the fitting hole 9 and fitting the key 10 into the key groove 8 at the same time, the carrier 3 and the output shaft 5
Are coupled, and the revolution of the planetary roller 2 is transmitted to the output shaft 5 via the carrier 3 and the key 10.
【００２５】図４に示される結合方式は、キャリア３の
座部３ｂにスプライン孔１１を設け、かつ、出力軸５の
軸端にスプライン１２を一体に設けてあり、キャリア３
のスプライン孔１１に出力軸５のスプライン１２を嵌挿
することによってキャリア３と出力軸５は結合され、遊
星ローラ２の公転は、キャリア３とスプライン１２を介
して出力軸５に伝達される。In the coupling system shown in FIG. 4, a spline hole 11 is provided in the seat portion 3b of the carrier 3, and a spline 12 is integrally provided at the shaft end of the output shaft 5.
The carrier 3 and the output shaft 5 are coupled by inserting the spline 12 of the output shaft 5 into the spline hole 11 of the above, and the revolution of the planetary roller 2 is transmitted to the output shaft 5 via the carrier 3 and the spline 12.
【００２６】図５に示される結合方式は、キャリア３の
座部３ｂに複数（例えば４個）の半円状溝１３を円周等
間隔に有する嵌挿孔１４を設け、かつ、出力軸５の軸端
に複数（半円状溝１３と同数）の鋼球１５を円周等間隔
に打ち込んで設けてあり、キャリア３の嵌挿孔１４に出
力軸５の軸端を嵌挿すると同時に半円状溝１３に鋼球１
５を嵌め込むことによってキャリア３と出力軸５は結合
され、遊星ローラ２の公転は、キャリア３と鋼球１５を
介して出力軸５に伝達される。In the coupling system shown in FIG. 5, the seat portion 3b of the carrier 3 is provided with fitting insertion holes 14 having a plurality of (for example, four) semicircular grooves 13 at equal intervals around the circumference, and the output shaft 5 is provided. A plurality of steel balls 15 (the same number as the semi-circular groove 13) are driven into the shaft end of the carrier at regular intervals, and the shaft end of the output shaft 5 is fitted into the fitting hole 14 of the carrier 3 at the same time. Steel ball 1 in circular groove 13
The carrier 3 and the output shaft 5 are coupled by fitting 5 and the revolution of the planetary roller 2 is transmitted to the output shaft 5 via the carrier 3 and the steel ball 15.
【００２７】図６に示される結合方式は、キャリア３の
座部３ｂに複数（例えば４個）の半円状溝１３を円周等
間隔に有する嵌挿孔１４を設け、かつ、出力軸５の軸端
に複数（半円状溝１３と同数）のローラ１６を円周等間
隔に打ち込んで設けてあり、キャリア３の嵌挿孔１４に
出力軸５の軸端を嵌挿すると同時に半円状溝１３にロー
ラ１６を嵌め込むことによってキャリア３と出力軸５は
結合され、遊星ローラ２の公転は、キャリア３とローラ
１６を介して出力軸５に伝達される。In the coupling method shown in FIG. 6, the seat portion 3b of the carrier 3 is provided with fitting holes 14 having a plurality of (for example, four) semicircular grooves 13 at equal intervals on the circumference, and the output shaft 5 is provided. A plurality of rollers 16 (same number as the semi-circular groove 13) are provided at the shaft end of the carrier at equal intervals around the circumference, and at the same time when the shaft end of the output shaft 5 is fitted into the fitting hole 14 of the carrier 3, the semi-circle is inserted. By fitting the roller 16 in the groove 13, the carrier 3 and the output shaft 5 are coupled, and the revolution of the planetary roller 2 is transmitted to the output shaft 5 via the carrier 3 and the roller 16.
【００２８】この実施の形態に係る遊星ローラ式動力伝
達装置の変形例として、キャリア３を、潤滑性能の良好
な材料、例えば焼結材料または銅系合金もしくはポリア
ミド（ＰＡ６６）、ポリアセタール（ＰＯＭ）、ポリエ
テールエテールケトン（ＰＥＥＫ）、ポリアミドイミド
（ＰＡＩ）、ポリイミド（ＰＩ）等の樹脂材料で形成す
る。As a modified example of the planetary roller power transmission device according to this embodiment, the carrier 3 is made of a material having a good lubricating performance, such as a sintered material, a copper alloy or polyamide (PA66), polyacetal (POM), It is formed of a resin material such as polyether ether ketone (PEEK), polyamide imide (PAI) or polyimide (PI).
【００２９】キャリア３を潤滑性能の良好な焼結材料ま
たは銅系合金もしくは樹脂材料で形成することで、遊星
ローラ２とキャリア３の間の潤滑性能が向上して摩耗・
発熱のさらなる低減を図れる。By forming the carrier 3 from a sintered material having a good lubricating property, a copper alloy or a resin material, the lubricating performance between the planetary roller 2 and the carrier 3 is improved and wear and wear are prevented.
It is possible to further reduce heat generation.
【００３０】また、他の変形例として、キャリア３の遊
星ローラ２との転走面に、例えば銀メッキ、銅メッキ、
無電解ニッケルメッキ等のメッキあるいは例えばＰＴＦ
Ｅ、グラファイト、ＭｏＳ2 等の固体潤滑剤被膜処理を
施す。Further, as another modification, the rolling surface of the carrier 3 with the planetary roller 2 is, for example, silver plated, copper plated,
Electroless nickel plating or PTF, for example
E, graphite, MoS 2 Solid lubricant film treatment such as.
【００３１】キャリア３の遊星ローラ２との転走面にメ
ッキあるいは固体潤滑剤被膜処理を施すことで、遊星ロ
ーラ２とキャリア３の間の潤滑性能が向上して摩耗・発
熱のさらなる低減を図れる。By plating or rolling the solid lubricant coating on the rolling surface of the carrier 3 with the planetary roller 2, the lubrication performance between the planetary roller 2 and the carrier 3 is improved and wear and heat generation can be further reduced. .
【００３２】また、無電解ニッケルメッキにＰＴＦＥや
ＭｏＳ2 等の固体潤滑剤を含有することで、遊星ローラ
２とキャリア３の間のより一層の摩擦性能の向上を図れ
る。In addition, electroless nickel plating is applied to PTFE or MoS 2 By including such a solid lubricant, it is possible to further improve the friction performance between the planetary roller 2 and the carrier 3.
【００３３】図７および図８は、本発明の他の実施の形
態に係る遊星ローラ式動力伝達装置を示している。この
遊星ローラ式動力伝達装置は、キャリア３を複数（例え
ば４個）の遊星ローラ２を保持する機能を有するキャリ
アピース３ｃから構成し、各キャリアピース３ｃを出力
軸５の軸端に一体形成した座部５ａに円周等間隔にそれ
ぞれ取り付けることによって円周方向に隣り合うキャリ
アピース３ｃ、３ｃ間に遊星ローラ２を回転自在に保持
するキャリアポケット部３ａを円周等間隔に設けたもの
である。キャリアピース３ｃに差込孔１７を設け、か
つ、出力軸５の座部５ａに複数（キャリアピース３ｃと
同数）のピンを打ち込むかまたはピン状突起を一体形成
した差込部材１８が円周等間隔に設けてあり、キャリア
ピース３ｃの差込孔１７を出力軸５の差込部材１８に差
し込んで出力軸５にキャリアピース３ｃを円周等間隔に
それぞれ取り付けてある。そして、遊星ローラ２の公転
は、キャリアピース３ｃと差込部材１８を介して出力軸
５に伝達される。7 and 8 show a planetary roller type power transmission device according to another embodiment of the present invention. In this planetary roller type power transmission device, the carrier 3 is composed of a carrier piece 3c having a function of holding a plurality of (for example, four) planetary rollers 2, and each carrier piece 3c is integrally formed at the shaft end of the output shaft 5. Carrier pockets 3a for rotatably holding the planetary roller 2 are provided at equal intervals between the carrier pieces 3c, 3c adjacent to each other in the circumferential direction by being attached to the seat 5a at equal intervals. . The insertion hole 17 is provided in the carrier piece 3c, and a plurality of (the same number as the carrier piece 3c) pins are driven in the seat portion 5a of the output shaft 5 or the insertion member 18 integrally formed with the pin-shaped projection has a circumference or the like. The carrier pieces 3c are provided at intervals, the insertion holes 17 of the carrier pieces 3c are inserted into the insertion members 18 of the output shaft 5, and the carrier pieces 3c are attached to the output shaft 5 at regular intervals. Then, the revolution of the planetary roller 2 is transmitted to the output shaft 5 via the carrier piece 3c and the insertion member 18.
【００３４】この実施の形態の遊星ローラ式動力伝達装
置は、キャリア３を複数の遊星ローラ２を保持する機能
を有するキャリアピース３ｃから構成し、各キャリアピ
ース３ｃをその差込孔１７を出力軸５の各々の差込部材
１８に差し込んで出力軸５にそれぞれ取り付けること
で、各キャリアピース３ｃに独立して差込孔１７と差込
部材１８のすきま分による自由度と、差込部材１８を中
心に回転できる自由度がそれぞれ与えられるため、入力
軸１・出力軸５（キャリアピース３ｃ）等の構成部品や
ハウジングの加工精度、さらにそれらの組立精度に起因
する入力軸１と出力軸５の軸心のずれが、前述の自由度
の範囲内であれば、キャリアピース３ｃが遊星ローラ２
にならい、遊星ローラ２とキャリアピース３ｃの間で図
１２に示すような最適な接触状態が得られ、接触面圧値
が最も低い状態での運転が可能となる。その結果、キャ
リアピース３ｃまたは遊星ローラ２の摩耗量を低減する
ことができ、摩耗による損傷・作動不能を防止できる。
また、遊星ローラ２とキャリアピース３ｃの間の法線力
を小さくできるため、遊星ローラ２とキャリアピース３
ｃの間のすべりによる動力損失を低減でき、発熱による
潤滑剤の劣化等を抑えることができる。In the planetary roller type power transmission device of this embodiment, the carrier 3 is composed of a carrier piece 3c having a function of holding a plurality of planetary rollers 2, and each carrier piece 3c has its insertion hole 17 in the output shaft. 5 is inserted into each of the insertion members 18 and attached to the output shaft 5, respectively, so that the degree of freedom of the insertion holes 17 and the clearance of the insertion members 18 and the insertion members 18 are independent of each carrier piece 3c. Since each of them has a degree of freedom of rotation about the center, the processing accuracy of the components such as the input shaft 1 and the output shaft 5 (carrier piece 3c) and the housing, and the assembly accuracy of the input shaft 1 and the output shaft 5 are caused. If the deviation of the shaft center is within the range of the above-mentioned degree of freedom, the carrier piece 3c is set to the planetary roller 2
Accordingly, the optimum contact state as shown in FIG. 12 is obtained between the planetary roller 2 and the carrier piece 3c, and the operation can be performed in the state where the contact surface pressure value is the lowest. As a result, the amount of wear of the carrier piece 3c or the planetary roller 2 can be reduced, and damage and inoperability due to wear can be prevented.
Moreover, since the normal force between the planetary roller 2 and the carrier piece 3c can be reduced, the planetary roller 2 and the carrier piece 3c can be reduced.
It is possible to reduce power loss due to slippage between the parts c and suppress deterioration of the lubricant due to heat generation.
【００３５】また、上述のように各キャリアピース３ｃ
に独立して与えられる自由度のため、キャリアピース３
ｃの転走面の曲率半径を潤滑上最適な値にしても、遊星
ローラ２とキャリアピース３ｃの転走面は片当たりを起
こさずに運転することができる。そのため、遊星ローラ
２とキャリアピース３ｃの転走面の接触面圧をさらに低
くすることができ、接触面圧値と動力損失の低減に対し
て有利となる。Further, as described above, each carrier piece 3c
Carrier piece 3 because of the freedom given independently to
Even if the radius of curvature of the rolling surface of c is an optimum value for lubrication, the rolling surfaces of the planetary roller 2 and the carrier piece 3c can be operated without causing one-sided contact. Therefore, the contact surface pressure between the rolling surfaces of the planetary roller 2 and the carrier piece 3c can be further reduced, which is advantageous for reducing the contact surface pressure value and the power loss.
【００３６】図９はキャリアピース３ｃを出力軸５に取
付ける他の例を示し、キャリアピース３ｃに差込孔１７
を２個設け、かつ、出力軸５に差込部材１８を２個ずつ
円周等間隔に設ける。この場合、キャリアピース３ｃに
は差込孔１７と差込部材１８のすきま分による自由度だ
けが与えられる。FIG. 9 shows another example in which the carrier piece 3c is attached to the output shaft 5, and the insertion hole 17 is formed in the carrier piece 3c.
Two of the insertion members 18 are provided on the output shaft 5 at equal intervals around the circumference. In this case, the carrier piece 3c is given only the degree of freedom due to the clearance between the insertion hole 17 and the insertion member 18.
【００３７】なお、上述した実施の形態では、キャリア
ピース３ｃに差込孔１７を設け、出力軸５に差込部材１
８を設けているが、キャリアピース３ｃに差込部材１８
を設け、出力軸５に差込孔１７を設けても良い。In the above-described embodiment, the insertion hole 17 is provided in the carrier piece 3c, and the insertion member 1 is attached to the output shaft 5.
8 is provided, but the insertion member 18 is attached to the carrier piece 3c.
May be provided, and the insertion hole 17 may be provided in the output shaft 5.
【００３８】この実施の形態に係る遊星ローラ式動力伝
達装置の変形例として、キャリアピース３ｃを、潤滑性
能の良好な材料、例えば焼結材料または銅系合金もしく
はポリアミド（ＰＡ６６）、ポリアセタール（ＰＯ
Ｍ）、ポリエテールエテールケトン（ＰＥＥＫ）、ポリ
アミドイミド（ＰＡＩ）、ポリイミド（ＰＩ）等の樹脂
材料で形成する。As a modified example of the planetary roller type power transmission device according to this embodiment, the carrier piece 3c is made of a material having a good lubricating property, such as a sintered material, a copper alloy or polyamide (PA66), polyacetal (PO).
M), polyether ether ketone (PEEK), polyamide imide (PAI), polyimide (PI) or the like.
【００３９】キャリアピース３ｃを潤滑性能の良好な焼
結材料または銅系合金もしくは樹脂材料で形成すること
で、遊星ローラ２とキャリアピース３ｃの間の潤滑性能
が向上して摩耗・発熱のさらなる低減を図れる。By forming the carrier piece 3c from a sintered material having a good lubricating property, a copper alloy or a resin material, the lubricating performance between the planetary roller 2 and the carrier piece 3c is improved, and wear and heat generation are further reduced. Can be achieved.
【００４０】また、他の変形例として、キャリアピース
３ｃの遊星ローラ２との転走面に例えば銀メッキ、銅メ
ッキ、無電解ニッケルメッキ等のメッキあるいは例えば
ＰＴＦＥ、グラファイト、ＭｏＳ2 等の固体潤滑剤被膜
処理を施す。As another modified example, the rolling surface of the carrier piece 3c with the planetary roller 2 is plated with, for example, silver, copper, electroless nickel, or PTFE, graphite, MoS 2 or the like. Solid lubricant film treatment such as.
【００４１】キャリアピース３ｃの遊星ローラ２との転
走面にメッキあるいは固体潤滑剤被膜処理を施すこと
で、遊星ローラ２とキャリアピース３ｃの間の潤滑性能
が向上して摩耗・発熱のさらなる低減を図れる。By plating or rolling the solid lubricant coating on the rolling surface of the carrier piece 3c with the planetary roller 2, the lubrication performance between the planetary roller 2 and the carrier piece 3c is improved, and wear and heat generation are further reduced. Can be achieved.
【００４２】また、無電解ニッケルメッキにＰＴＦＥや
ＭｏＳ2 等の固体潤滑剤を含有することで、遊星ローラ
２とキャリアピース３ｃの間のより一層の潤滑性能の向
上を図れる。Further, electroless nickel plating is applied to PTFE or MoS 2 By including such a solid lubricant, it is possible to further improve the lubricating performance between the planetary roller 2 and the carrier piece 3c.
【００４３】[0043]
【発明の効果】以上説明したように、本発明によれば、
キャリアと出力軸を別体に形成し、キャリアを出力軸に
対して半径方向の自由度を持つ結合方式で取り付けるこ
とにより、入力軸と出力軸の軸心のずれがキャリアと出
力軸の結合部分で吸収されてキャリアの軸心が入力軸の
軸心にならい、遊星ローラとキャリアを最適な接触状態
にすることができる。このように入力軸と出力軸の軸心
がずれても、遊星ローラとキャリアを最適な接触状態に
することができるため、入力軸・出力軸等の構成部品や
ハウジングの加工精度、さらにそれらの組立精度を高水
準にしなくても良く、製造コストの低減が図れる。ま
た、キャリアを潤滑性能の良好な材料で形成するか、キ
ャリアの遊星ローラとの転走面に潤滑性能を向上させる
表面処理を施すことにより、キャリアと遊星ローラの間
の摩耗・発熱のさらなる低減が期待できる。As described above, according to the present invention,
By forming the carrier and output shaft separately and mounting the carrier with a coupling method that has a degree of freedom in the radial direction with respect to the output shaft, the misalignment of the input shaft and output shaft center points causes the carrier and output shaft coupling Is absorbed, and the shaft center of the carrier follows the shaft center of the input shaft, so that the planet roller and the carrier can be brought into an optimum contact state. Even if the axes of the input shaft and output shaft are misaligned in this way, the planetary roller and carrier can be brought into optimum contact, so the processing accuracy of the components such as the input and output shafts and the housing, and their Assembling accuracy does not have to be set to a high level, and the manufacturing cost can be reduced. Further, by forming the carrier with a material with good lubrication performance, or by applying surface treatment to the rolling surface of the carrier with the planetary roller to improve lubrication performance, further reducing wear and heat generation between the carrier and planetary roller. Can be expected.
【００４４】また、本発明によれば、キャリアを複数の
遊星ローラを保持する機能を有するキャリアピースから
構成し、キャリアピースを出力軸に対して自由度を持つ
結合方式で取り付けることにより、入力軸と出力軸の軸
心のずれがキャリアピースと出力軸の結合部分で吸収さ
れてキャリアピースが遊星ローラにならい、遊星ローラ
とキャリアピースを最適な接触状態にすることができ
る。このように入力軸と出力軸の軸心のずれても、遊星
ローラとキャリアピースを最適な接触状態にすることが
できるため、入力軸・出力軸等の構成部品やハウジング
の加工精度、さらにそれらの組立精度を高水準にしなく
ても良く、製造コストの低減が図れる。また、キャリア
ピースを潤滑性能の良好な材料で形成するか、キャリア
ピースの遊星ローラとの転走面に潤滑性能を向上させる
表面処理を施すことにより、キャリアピースと遊星ロー
ラの間の摩耗・発熱のさらなる低減が期待できる。Further, according to the present invention, the carrier is composed of a carrier piece having a function of holding a plurality of planetary rollers, and the carrier piece is attached to the output shaft by a coupling method having a degree of freedom, whereby the input shaft is The deviation of the shaft center of the output shaft is absorbed by the connecting portion between the carrier piece and the output shaft, the carrier piece follows the planetary roller, and the planetary roller and the carrier piece can be brought into an optimum contact state. Even if the input shaft and the output shaft are misaligned in this way, the planetary roller and the carrier piece can be brought into the optimum contact state, so that the processing accuracy of the components such as the input shaft and the output shaft and the housing, and It is not necessary to raise the assembling accuracy to a high level, and the manufacturing cost can be reduced. In addition, wear or heat generated between the carrier piece and the planetary roller can be achieved by forming the carrier piece with a material with good lubrication performance or by applying surface treatment to the rolling surface of the carrier piece with the planetary roller to improve lubrication performance. Can be expected to be further reduced.
【図１】本発明の実施の形態に係る遊星ローラ式動力伝
達装置の要部縦断面図である。FIG. 1 is a vertical cross-sectional view of a main part of a planetary roller power transmission device according to an embodiment of the present invention.
【図２】図１の実施の形態におけるキャリアと出力軸の
結合方式を示す斜視図である。FIG. 2 is a perspective view showing a coupling method of a carrier and an output shaft in the embodiment of FIG.
【図３】図１の実施の形態におけるキャリアと出力軸の
結合方式の変形例を示す斜視図である。FIG. 3 is a perspective view showing a modified example of the coupling system of the carrier and the output shaft in the embodiment of FIG.
【図４】図１の実施の形態におけるキャリアと出力軸の
結合方式の変形例を示す斜視図である。FIG. 4 is a perspective view showing a modification of the coupling system of the carrier and the output shaft in the embodiment of FIG.
【図５】図１の実施の形態におけるキャリアと出力軸の
結合方式の変形例を示す斜視図である。5 is a perspective view showing a modified example of the coupling system of the carrier and the output shaft in the embodiment of FIG. 1. FIG.
【図６】図１の実施の形態におけるキャリアと出力軸の
結合方式の変形例を示す斜視図である。FIG. 6 is a perspective view showing a modification of the coupling system of the carrier and the output shaft in the embodiment of FIG.
【図７】本発明の他の実施の形態に係る遊星ローラ式動
力伝達装置の要部縦断面図である。FIG. 7 is a vertical cross-sectional view of a main part of a planetary roller power transmission device according to another embodiment of the present invention.
【図８】図７の実施の形態におけるキャリアピースと出
力軸の結合方式を示す斜視図である。FIG. 8 is a perspective view showing a method of coupling the carrier piece and the output shaft in the embodiment of FIG.
【図９】図７の実施の形態におけるキャリアピースと出
力軸の結合方式の変形例を示す斜視図である。9 is a perspective view showing a modified example of the coupling method of the carrier piece and the output shaft in the embodiment of FIG.
【図１０】遊星ローラ式動力伝達装置を示し、（ａ）は
正面図、（ｂ）は（ａ）のＡ−Ｏ−Ｂ線に沿った断面図
である。FIG. 10 shows a planetary roller power transmission device, (a) is a front view and (b) is a cross-sectional view taken along the line A-O-B of (a).
【図１１】従来のキャリアと出力軸を示す斜視図であ
る。FIG. 11 is a perspective view showing a conventional carrier and an output shaft.
【図１２】入力軸と出力軸の軸心が一致する場合のキャ
リアと遊星ローラの接触状態を示す図面である。FIG. 12 is a drawing showing a contact state between a carrier and a planetary roller when the axes of the input shaft and the output shaft coincide with each other.
【図１３】入力軸と出力軸の軸心がずれる場合のキャリ
アと遊星ローラの接触状態を示す図面である。FIG. 13 is a drawing showing a contact state between a carrier and a planetary roller when the axes of the input shaft and the output shaft are displaced from each other.
１ 入力軸 ２ 遊星ローラ ３ キャリア ３ａ キャリアポケット部 ３ｃ キャリアピース ４ 固定輪 ５ 出力軸 1 input shaft 2 planetary roller 3 carrier 3a carrier pocket 3c carrier piece 4 fixed ring 5 output shaft
Claims (6)
間隔に配置された複数の遊星ローラと、遊星ローラの公
転を出力軸に伝達するキャリアと、入力軸と同心状に固
定され、入力軸との間に各遊星ローラを転がり摩擦接触
状態に介装させる固定輪とからなり、 キャリアを出力軸と別体に形成し、キャリアを出力軸に
対して半径方向の自由度を持つ結合方式で取り付けこと
を特徴とする遊星ローラ式動力伝達装置。1. An input shaft, a plurality of planet rollers arranged at equal intervals on the outer peripheral surface of the input shaft, a carrier for transmitting the revolution of the planet rollers to the output shaft, and concentric with the input shaft. It consists of a fixed wheel that is fixed and that interposes each planetary roller in rolling frictional contact with the input shaft.The carrier is formed separately from the output shaft, and the carrier has radial freedom with respect to the output shaft. A planetary roller type power transmission device characterized by being attached by a coupling method having
たは銅系合金もしくは樹脂材料で形成したことを特徴と
する請求項１の遊星ローラ式動力伝達装置。2. The planetary roller type power transmission device according to claim 1, wherein the carrier is formed of a sintered material having a good lubricating property, a copper alloy or a resin material.
性能の良好なメッキまたは固体潤滑剤被膜処理を施した
ことを特徴とする請求項１の遊星ローラ式動力伝達装
置。3. The planetary roller type power transmission device according to claim 1, wherein the rolling surface of the carrier with respect to the planetary roller is plated or has a solid lubricant film treated to have good lubricating performance.
間隔に配置された複数の遊星ローラと、遊星ローラの公
転を出力軸に伝達するキャリアと、入力軸と同心状に固
定され、入力軸との間に各遊星ローラを転がり摩擦接触
状態に介装させる固定輪とからなり、 キャリアを複数の遊星ローラを保持する機能を有するキ
ャリアピースから構成し、各キャリアピースを出力軸に
対して自由度を持つ結合方式で円周等間隔に取り付けた
ことを特徴とする遊星ローラ式動力伝達装置。4. An input shaft, a plurality of planet rollers arranged on the outer peripheral surface of the input shaft at equal circumferential intervals, a carrier for transmitting the revolution of the planet rollers to the output shaft, and concentric with the input shaft. It consists of a fixed wheel that is fixed and inserts each planetary roller into rolling contact with the input shaft in a frictional contact state.The carrier is composed of a carrier piece that holds multiple planetary rollers and outputs each carrier piece. A planetary roller type power transmission device characterized by being mounted at equal intervals on the circumference by a coupling system having a degree of freedom with respect to the shaft.
材料または銅系合金もしくは樹脂材料で形成したことを
特徴とする請求項４の遊星ローラ式動力伝達装置。5. The planetary roller type power transmission device according to claim 4, wherein the carrier piece is formed of a sintered material, a copper alloy or a resin material having a good lubricating performance.
に潤滑性能の良好なメッキまたは固体潤滑剤被膜処理を
施したことを特徴とする請求項４の遊星ローラ式動力伝
達装置。6. The planetary roller type power transmission device according to claim 4, wherein the rolling surface of the carrier piece with respect to the planetary roller is plated or has a solid lubricant coating treatment with good lubrication performance.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7734496A JPH09264393A (en) | 1996-03-29 | 1996-03-29 | Planetary roller type power transmission |
| US08/825,056 US5851163A (en) | 1996-03-29 | 1997-03-27 | Planetary roller type power transmission device |
| DE19713083A DE19713083A1 (en) | 1996-03-29 | 1997-03-27 | Planetary transmission transfer device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7734496A JPH09264393A (en) | 1996-03-29 | 1996-03-29 | Planetary roller type power transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09264393A true JPH09264393A (en) | 1997-10-07 |
Family
ID=13631312
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7734496A Withdrawn JPH09264393A (en) | 1996-03-29 | 1996-03-29 | Planetary roller type power transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09264393A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1036954A2 (en) * | 1999-03-16 | 2000-09-20 | Sumitomo Heavy Industries, Ltd. | Oscillating internally meshing planetary gear unit and planetary roller mechanism |
| JP2001271897A (en) * | 2000-03-28 | 2001-10-05 | Nsk Ltd | Friction roller type transmission |
| JP2013082370A (en) * | 2011-10-12 | 2013-05-09 | Nissan Motor Co Ltd | Axle coupling structure |
| CN109372971A (en) * | 2018-11-27 | 2019-02-22 | 浙江双环传动机械股份有限公司 | The harmonic gear transmission device of PFPE and Ag solid lubricating film mixed lubrication |
| US11473585B2 (en) | 2020-12-07 | 2022-10-18 | Kabushiki Kaisha Toyota Jidoshokki | Transmission and centrifugal compressor |
-
1996
- 1996-03-29 JP JP7734496A patent/JPH09264393A/en not_active Withdrawn
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1036954A2 (en) * | 1999-03-16 | 2000-09-20 | Sumitomo Heavy Industries, Ltd. | Oscillating internally meshing planetary gear unit and planetary roller mechanism |
| EP1036954A3 (en) * | 1999-03-16 | 2002-11-13 | Sumitomo Heavy Industries, Ltd. | Oscillating internally meshing planetary gear unit and planetary roller mechanism |
| JP2001271897A (en) * | 2000-03-28 | 2001-10-05 | Nsk Ltd | Friction roller type transmission |
| JP2013082370A (en) * | 2011-10-12 | 2013-05-09 | Nissan Motor Co Ltd | Axle coupling structure |
| CN109372971A (en) * | 2018-11-27 | 2019-02-22 | 浙江双环传动机械股份有限公司 | The harmonic gear transmission device of PFPE and Ag solid lubricating film mixed lubrication |
| US11473585B2 (en) | 2020-12-07 | 2022-10-18 | Kabushiki Kaisha Toyota Jidoshokki | Transmission and centrifugal compressor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20030603 |