JPH04151028A - Driving power transmission device - Google Patents
Driving power transmission deviceInfo
- Publication number
- JPH04151028A JPH04151028A JP27429190A JP27429190A JPH04151028A JP H04151028 A JPH04151028 A JP H04151028A JP 27429190 A JP27429190 A JP 27429190A JP 27429190 A JP27429190 A JP 27429190A JP H04151028 A JPH04151028 A JP H04151028A
- Authority
- JP
- Japan
- Prior art keywords
- housing
- rotor
- piston
- revolution
- inclined surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 28
- 239000012530 fluid Substances 0.000 claims abstract description 17
- 230000004043 responsiveness Effects 0.000 abstract description 4
- 239000007788 liquid Substances 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 229920002545 silicone oil Polymers 0.000 description 1
Landscapes
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明は、相対回転可能な２軸の間に配置され両輪の間
で駆動力を伝達する駆動力伝達装置に関するものである
。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a driving force transmission device that is disposed between two relatively rotatable shafts and transmits driving force between both wheels.
〈従来の技術〉
一般に、前、後輪間でトルクを伝達する４輪駆動用の駆
動力伝達装置においては、トルク伝達用のクラッチ手段
と、このクラッチ手段を作動するピストンと、前、後輪
あるいは左、右輪の差動回転に応じた圧力を発生する圧
力発生部を備え、この発生圧力をピストンに作用してク
ラッチ手段を摩擦係合させるようになっている。<Prior Art> Generally, in a four-wheel drive drive power transmission device that transmits torque between the front and rear wheels, a clutch means for transmitting torque, a piston that operates this clutch means, and a drive force transmission device for transmitting torque between the front and rear wheels. Alternatively, it is provided with a pressure generating section that generates pressure according to the differential rotation of the left and right wheels, and applies this generated pressure to the piston to frictionally engage the clutch means.
ところで、４輪駆動用の駆動力伝達装置の要求される機
能は、前後輪の差動に応じて駆動トルクを伝達すること
は勿論であるが、併せて４輪駆動特有の循環トルクを吸
収し、走行過程での前後輪の回転位相差に伴う振動およ
びこもり音を防止するとともに、ＡＢＳ（アンチロック
ブレーキシステム）制御時における外乱を低減すること
にある。By the way, the required function of a four-wheel drive drive force transmission device is not only to transmit drive torque according to the differential between the front and rear wheels, but also to absorb the circulating torque unique to four-wheel drive. The object of the present invention is to prevent vibrations and muffled noise caused by the rotational phase difference between the front and rear wheels during driving, and to reduce disturbances during ABS (anti-lock braking system) control.
〈発明が解決しようとする課題〉
このような問題点を解決するものとして、特開平２−２
１０３８号公報に記載されているように正トルク伝達時
と逆トルク伝達時とでトルク伝達特性が異なる駆動力伝
達装置が提供されている。<Problem to be solved by the invention> As a solution to such problems, Japanese Patent Application Laid-Open No. 2002-2
As described in Japanese Patent Application No. 1038, a driving force transmission device is provided that has different torque transmission characteristics during forward torque transmission and reverse torque transmission.
かかる駆動力伝達装置においては、ブレードの形状を細
工するだけで上記した機能を達成できる利点があるが、
ブレードの数が円周上２〜３程度であるため、ブレード
間の距離が長くなり、差動回転方向が反転する場合にエ
アが一方のブレード側から他方のブレード側に移行する
まで僅かではあるが時間を要し、差動回転方向が反転す
る際の圧力の応答性に時間遅れを生ずることがあった。Such a driving force transmission device has the advantage that the above functions can be achieved simply by modifying the shape of the blade.
Since the number of blades is about 2 to 3 on the circumference, the distance between the blades is long, and when the differential rotation direction is reversed, it is only a small amount until the air moves from one blade side to the other blade side. This takes time and may cause a time delay in pressure response when the differential rotation direction is reversed.
〈課題を解決するための手段〉
本発明は、上記した従来の問題点を解消するためになさ
れたもので、相対回転可能な２軸の間に配置され両輪の
間で駆動力を伝達するクラッチ手段を備えた駆動力伝達
装置において、前記２軸の一方にハウジングを連結し、
他方にこのハウジングに回転可能に軸承された回転軸を
連結し、前記ハウジング内に前記クラッチ手段を押圧す
るピストンを収納し、このピストンの側方に空間部を設
け、この空間部に高粘性流体を封入し、また前記空間部
に前記２軸の差動回転により高粘性流体を移動させてそ
の粘性摩擦により２軸の差動回転に応じた圧力を発生さ
せるロータを収納し、このロータに円周上多数の凹部を
設け、これら凹部の回転方向片側には回転方向にくさび
部を形成する傾斜面を設け、回転方向他側には前記くさ
び部より埋没したエア溜まりを設けたものである。<Means for Solving the Problems> The present invention has been made to solve the above-mentioned conventional problems, and provides a clutch that is arranged between two relatively rotatable shafts and transmits driving force between both wheels. In a driving force transmission device comprising means for connecting a housing to one of the two shafts,
A rotating shaft rotatably supported by the housing is connected to the other, a piston for pressing the clutch means is housed in the housing, a space is provided on the side of the piston, and a high viscosity fluid is placed in the space. Further, a rotor is housed in the space that moves a high viscosity fluid by the differential rotation of the two axes and generates pressure according to the differential rotation of the two axes by the viscous friction. A large number of recesses are provided on the circumference, an inclined surface forming a wedge in the rotational direction is provided on one side of the recess in the rotational direction, and an air pocket buried below the wedge is provided on the other side in the rotational direction.
〈作用〉
上記した構成により、正トルク伝達時においては、ロー
タ凹部のくさび部側に高粘性流体が移動され、エアはエ
ア溜まりに封じ込められるため、くさび部のくさび効果
により差動回転に応じた圧力が高められ、この圧力によ
りピストンが押圧され、クラッチ手段が係合されて２軸
間でトルクが伝達され、４輪駆動状態に保持される。<Function> With the above configuration, when positive torque is transmitted, the high viscosity fluid is moved to the wedge side of the rotor recess and the air is confined in the air pocket, so the wedge effect of the wedge allows the fluid to respond to the differential rotation. The pressure is increased, the piston is pushed by this pressure, the clutch means is engaged, torque is transmitted between the two axles, and the four-wheel drive state is maintained.
これに対し、逆トルク伝達時においては、ロータ凹部の
エア溜まり側に高粘性流体が移動され、エアはくさび部
に封じ込められるため、くさび部のくさび効果は期待で
きな（なり、正トルク伝達時に比較して発生圧力が低く
なり、クラッチ手段の係合力が小さくなって伝達トルク
が抑制される。On the other hand, when transmitting reverse torque, the highly viscous fluid is moved to the air reservoir side of the rotor recess and the air is confined in the wedge, so the wedge effect of the wedge cannot be expected (and when transmitting positive torque In comparison, the generated pressure is lower, the engagement force of the clutch means is reduced, and the transmitted torque is suppressed.
〈実施例〉 以下本発明の実施例を図面に基づいて説明する。<Example> Embodiments of the present invention will be described below based on the drawings.
第１図および第２図において、２０は相対回転可能な２
軸（前後輪軸）１５．１６の間に配置される駆動力伝達
装置を示し、この駆動力伝達装置２０は、ハウジング２
１と、このハウジング２１内を縦貫して回転可能に軸承
された回転軸２２と、これらハウジング２１と回転軸２
２との差動回転に応じた圧力を発生する圧力発生部２３
と、この圧力発生部２３にて発生した圧力が作用される
ピストン２４と、このピストン２４の押圧力によって摩
擦係合されるクラッチ手段２５とによって主に構成され
ている。1 and 2, 20 is a relatively rotatable 2
A driving force transmitting device disposed between the shafts (front and rear wheel axles) 15 and 16 is shown, and this driving force transmitting device 20 is connected to the housing 2.
1, a rotating shaft 22 that extends vertically through the housing 21 and is rotatably supported, and the housing 21 and the rotating shaft 2.
A pressure generating section 23 that generates pressure according to the differential rotation with 2.
, a piston 24 to which the pressure generated by the pressure generating section 23 is applied, and a clutch means 25 that is frictionally engaged by the pressing force of the piston 24.
前記ハウジング２１の一端は前記２軸の一方１５に一体
的に結合され、また前記回転軸２２内には前記２軸の他
方１６がスプライン係合されている。ハウジング２１に
は、その一端より有底円筒状の中空穴２６が形成され、
この中空穴２６の底面側に前記ピストン２４が摺動可能
に収納され、このピストン２４はハウジング２１の内周
に形成されたスプラインに係合して回り止めされている
。One end of the housing 21 is integrally connected to one 15 of the two shafts, and the other shaft 16 of the two shafts is spline-engaged within the rotating shaft 22. A hollow cylindrical hole 26 with a bottom is formed in the housing 21 from one end thereof,
The piston 24 is slidably housed on the bottom side of the hollow hole 26, and is prevented from rotating by engaging with a spline formed on the inner circumference of the housing 21.
前記ハウジング２１の底壁とピストン２４の端壁との間
には、軸線方向幅が制限された円筒状の空間部４０が形
成され、この空間部４０にその幅寸法より僅かに小さな
肉厚のロータ４１が摺接可能に収納されている。ロータ
４１は中心部を前記回転軸２２の外周にスプライン係合
されている。A cylindrical space 40 with a limited axial width is formed between the bottom wall of the housing 21 and the end wall of the piston 24, and a wall with a wall thickness slightly smaller than the width is formed in this space 40. A rotor 41 is housed in a slidable manner. The rotor 41 has a center portion engaged with the outer periphery of the rotating shaft 22 by a spline.
かかるロータ４１の両端面には、第３図および第４図に
詳細図示するように円周上多数の凹部４２が形成され、
これら凹部４２の回転方向片側には回転方向に沿って傾
斜面４３が形成され、回転方向他側にはその傾斜面４３
の底部より埋没したエア溜まり４４が形成されている。A large number of recesses 42 are formed on the circumference of both end surfaces of the rotor 41, as shown in detail in FIGS. 3 and 4.
An inclined surface 43 is formed along the rotational direction on one side of the recesses 42 in the rotational direction, and the inclined surface 43 is formed on the other side in the rotational direction.
An air pocket 44 is formed which is buried from the bottom.
これによって前記ロータ４１の両端面とハウジング２１
の底壁およびピストン２４の端壁との各間には、第４図
に示すように回転方向に細長く伸びかつ回転方向片側に
向かって幅が次第に小さくなるくさび部４３Ａが形成さ
れ、このくさび部４３Ａによるくさび効果により圧力が
増大されるようになる。As a result, both end surfaces of the rotor 41 and the housing 21
A wedge portion 43A is formed between the bottom wall of the piston 24 and the end wall of the piston 24, as shown in FIG. The pressure is increased due to the wedge effect caused by 43A.
前記各凹部４２には、シリコンオイル等の高粘性流体４
５が充填されており、しかして温度上昇に伴う高粘性流
体４５の体積膨張を考慮して、前記各凹部４２には数％
のエアが封入されている。Each of the recesses 42 is filled with a highly viscous fluid 4 such as silicone oil.
5, and considering the volumetric expansion of the highly viscous fluid 45 as the temperature rises, each of the recesses 42 is filled with several percent
of air is sealed.
上記した円筒状空間部４０に収納されたロータ４１およ
び高粘性流体４５により前記圧力発生部２３を構成して
いる。The pressure generating section 23 is constituted by the rotor 41 and the high viscosity fluid 45 housed in the cylindrical space 40 described above.
前記ハウジング２１の中空穴２６の開口端にはエンドカ
バー２８が装着され、このエンドカバー２８と前記ピス
トン２４との間に密閉された潤滑油チャンバ２７が形成
され、この潤滑油チャンバ２７に潤滑油が封入されてい
る。潤滑油チャンバ２７内には多板クラッチからなるク
ラッチ手段２５を構成する複数のアウタプレート３７と
インナプレート３８が交互に配置されており、アウタプ
レート３７はハウジング２１の内周にスプライン係合さ
れ、インナプレート３８は回転軸２２の外周に取付けら
れたクラッチハブ３９にスプライン係合されている。An end cover 28 is attached to the open end of the hollow hole 26 of the housing 21, and a sealed lubricating oil chamber 27 is formed between the end cover 28 and the piston 24, and the lubricating oil chamber 27 is filled with lubricating oil. is included. Inside the lubricating oil chamber 27, a plurality of outer plates 37 and inner plates 38 constituting the clutch means 25 consisting of a multi-plate clutch are arranged alternately, and the outer plates 37 are spline engaged with the inner periphery of the housing 21. The inner plate 38 is splined to a clutch hub 39 attached to the outer periphery of the rotating shaft 22.
次に上記した構成における駆動力伝達装置２０の動作に
ついて説明する。Next, the operation of the driving force transmission device 20 in the above configuration will be explained.
前記２軸１５．１６が相対回転して前記ロータ４１がハ
ウジング２１内で相対回転すると、凹部４２に充填され
た高粘性流体４５も回転速度差に応じた流速で強制移動
される。その際、ハウジング２１の底面およびピストン
２４の端面の両壁面に対する粘性摩擦作用により、凹部
４２内にロータ４１の相対回転速度差に比例した内圧が
発生する。この場合、ハウジング２１に対するロータ４
１の回転方向により、凹部４２内に発生する圧力に差異
がもたらされる。When the two shafts 15 and 16 rotate relative to each other and the rotor 41 rotates relatively within the housing 21, the high viscosity fluid 45 filled in the recess 42 is also forcibly moved at a flow rate corresponding to the rotational speed difference. At this time, an internal pressure proportional to the relative rotational speed difference of the rotor 41 is generated in the recess 42 due to viscous friction on both wall surfaces of the bottom surface of the housing 21 and the end surface of the piston 24 . In this case, the rotor 4 relative to the housing 21
The direction of rotation of 1 causes a difference in the pressure generated within the recess 42.
すなわち、例えばロータ４工が回転ハウジング２１に対
して時計まわり（矢印方向）に相対回転する場合（以下
これを正トルク伝達時という）には、高粘性流体４５が
ロータ４１の回転方向後方のくさび部４３Ａ側に移動さ
れ、高粘性流体４５に混入したエアはエア溜まり４４側
に逃げ、そこに封し込められる。That is, for example, when the rotor 4 rotates clockwise (in the direction of the arrow) relative to the rotary housing 21 (hereinafter referred to as positive torque transmission), the high viscosity fluid 45 flows into the wedge at the rear of the rotor 41 in the rotational direction. The air moved to the part 43A side and mixed into the high viscosity fluid 45 escapes to the air reservoir 44 side and is sealed there.
従ってくさび部４３Ａにおけるくさび効果により凹部４
２内に発生する内圧が高くなり、その圧力にてピストン
２４が押圧される。これにより複数のアウタプレート３
７とインナプレート３８がピストン２４に作用する圧力
に応じた押圧力で摩擦係合され、クラッチ手段２５を介
して２軸１５１６間に十分な回転トルクが伝達される。Therefore, due to the wedge effect in the wedge portion 43A, the recess 4
The internal pressure generated within the piston 2 increases, and the piston 24 is pressed by this pressure. This allows multiple outer plates 3
7 and the inner plate 38 are frictionally engaged with each other with a pressing force corresponding to the pressure acting on the piston 24, and sufficient rotational torque is transmitted between the two shafts 1516 via the clutch means 25.
すなわち、差動回転に対する伝達トルクは第５図の実線
Ａに示すように高めの特性となる。That is, the transmission torque for differential rotation has a higher characteristic as shown by solid line A in FIG.
これに対してロータ４１が回転ハウジング２１に対して
反時計まわりに相対回転する場合（以下これを逆トルク
伝達時という）には、高粘性流体４５がロータ４１の回
転方向後方のエア溜まり４４側に移動されるのに対し、
高粘性流体４５に混入したエアはくさび部４３Ａ側に逃
げるため、（さび部４３Ａによるくさび効果は期待でき
な（なり、凹部４２に発生する圧力は低くなる。 その
結果、クラッチ手段２５の係合力が小さくなり、差動回
転に対する伝達トルクは第５図の実線Ｂに示すように低
めの特性となる。On the other hand, when the rotor 41 rotates counterclockwise relative to the rotating housing 21 (hereinafter referred to as "reverse torque transmission"), the high viscosity fluid 45 flows toward the air pocket 44 at the rear of the rotor 41 in the rotational direction. whereas it is moved to
Since the air mixed in the high viscosity fluid 45 escapes to the wedge portion 43A side, the wedge effect due to the wedge portion 43A cannot be expected (and the pressure generated in the recess 42 becomes low. As a result, the engagement force of the clutch means 25 becomes smaller, and the transmission torque for differential rotation has a lower characteristic as shown by the solid line B in FIG.
しかも圧力を発生する凹部４２がロータ４１の円周上に
多数設けられているため、差動回転の反転時におけるエ
アの移動距離が短くなり、差動回転の反転時におけるエ
アの移動時間が短くなって圧力の立ち上がりが良好とな
り、トルク伝達の応答性が高められるようになる。Moreover, since a large number of recesses 42 that generate pressure are provided on the circumference of the rotor 41, the distance that the air moves when the differential rotation is reversed is shortened, and the time that the air moves when the differential rotation is reversed is shortened. As a result, the pressure rises better and the responsiveness of torque transmission is improved.
〈発明の効果〉
以上述べたように本発明によれば、正トルク伝達時と逆
トルク伝達時とで伝達特性を異にでき、逆トルク伝達特
性を正トルク伝達特性時に比べて低くできることから、
循環トルクを吸収でき、走行過程での前後輪の回転位相
差に伴う振動およびこもり音が防止できるとともに、Ａ
ＢＳｌｉｌＪ１１時における外乱を低減することができ
る利点がある。<Effects of the Invention> As described above, according to the present invention, the transmission characteristics can be made different between the forward torque transmission and the reverse torque transmission, and the reverse torque transmission characteristic can be lowered compared to the positive torque transmission characteristic.
It can absorb circulating torque, prevent vibrations and muffled noise caused by the rotational phase difference between the front and rear wheels during driving, and
There is an advantage that the disturbance at the time of BSlilJ11 can be reduced.
しかもロータの円周上に多数の凹部を形成して差動回転
の反転時におけるエアの移動距離を短くしたので、差動
回転の反転時における圧力の立ち上がりが良好となり、
トルク伝達の応答性を高め得る効果がある。Moreover, by forming a large number of recesses on the circumference of the rotor to shorten the distance that air travels when the differential rotation is reversed, the pressure rises well when the differential rotation is reversed.
This has the effect of increasing the responsiveness of torque transmission.
図面は本発明の実施例を示すもので、第１図は駆動力伝
達装置の断面図、第２図は第１図の■−■線断面図、第
３図はロータの凹部を示す部分的な斜視図、第４図は第
３図のＩＶ−ＩＶ線断面図、第５図は差動回転に対する
伝達トルク特性を示す線図である。
１５．１６・・・軸、２１・・・ハウジング、２２・・
・回転軸、２４・・・ピストン、２５・・・・クラッチ
手段、４１・・・ロータ、４２・・・凹部、４３・・・
傾斜面、４３Ａ・・・くさび部。The drawings show an embodiment of the present invention, and FIG. 1 is a sectional view of the driving force transmission device, FIG. 2 is a sectional view taken along the line ■-■ in FIG. FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3, and FIG. 5 is a diagram showing transmission torque characteristics with respect to differential rotation. 15.16...shaft, 21...housing, 22...
- Rotating shaft, 24... Piston, 25... Clutch means, 41... Rotor, 42... Recess, 43...
Inclined surface, 43A... wedge part.
Claims (1)
動力を伝達するクラッチ手段を備えた駆動力伝達装置に
おいて、前記２軸の一方にハウジングを連結し、他方に
このハウジングに回転可能に軸承された回転軸を連結し
、前記ハウジング内に前記クラッチ手段を押圧するピス
トンを収納し、このピストンの側方に空間部を設け、こ
の空間部に高粘性流体を封入し、また前記空間部に前記
２軸の差動回転により高粘性流体を移動させてその粘性
摩擦により２軸の差動回転に応じた圧力を発生させるロ
ータを収納し、このロータに円周上多数の凹部を設け、
これら凹部の回転方向片側には回転方向にくさび部を形
成する傾斜面を設け、回転方向他側には前記くさび部よ
り埋没したエア溜まりを設けてなる駆動力伝達装置。(1) In a driving force transmission device equipped with a clutch means disposed between two relatively rotatable shafts and transmitting driving force between the two shafts, a housing is connected to one of the two shafts, and the housing is connected to the other shaft. A rotating shaft rotatably supported by the housing is connected, a piston for pressing the clutch means is housed in the housing, a space is provided on the side of the piston, and a high viscosity fluid is sealed in the space, Further, a rotor that moves a high viscosity fluid by the differential rotation of the two axes and generates pressure according to the differential rotation of the two axes by the viscous friction is housed in the space, and this rotor has a large number of Provide a recess,
A driving force transmission device in which an inclined surface forming a wedge portion in the rotational direction is provided on one side of the recessed portions in the rotational direction, and an air pocket buried from the wedge portion is provided on the other side in the rotational direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2274291A JP2796417B2 (en) | 1990-10-11 | 1990-10-11 | Driving force transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2274291A JP2796417B2 (en) | 1990-10-11 | 1990-10-11 | Driving force transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04151028A true JPH04151028A (en) | 1992-05-25 |
| JP2796417B2 JP2796417B2 (en) | 1998-09-10 |
Family
ID=17539600
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2274291A Expired - Lifetime JP2796417B2 (en) | 1990-10-11 | 1990-10-11 | Driving force transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2796417B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5899306A (en) * | 1996-11-07 | 1999-05-04 | Toyoda Koki Kabushiki Kaisha | Drive force transmission apparatus |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109114870B (en) * | 2018-08-20 | 2020-11-06 | 义乌市鼎莎针织有限公司 | Baffle positioner who uses in refrigerator |
-
1990
- 1990-10-11 JP JP2274291A patent/JP2796417B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5899306A (en) * | 1996-11-07 | 1999-05-04 | Toyoda Koki Kabushiki Kaisha | Drive force transmission apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2796417B2 (en) | 1998-09-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0221038A (en) | Driving force transmission gear | |
| JPH0237034A (en) | Drive force distributor | |
| JPH02209629A (en) | Power transmission mechanism | |
| JPH04231730A (en) | Drive force transmitting device | |
| JP2579644B2 (en) | Hydraulic control device | |
| JPH02120530A (en) | Driving force transmission | |
| JPH02120529A (en) | Driving force transmission | |
| JPH0251626A (en) | Device for transmitting driving force | |
| JPH0514014Y2 (en) | ||
| JPH04151028A (en) | Driving power transmission device | |
| JPH0221037A (en) | Driving force transmission gear | |
| JP3287903B2 (en) | Driving force transmission device | |
| JP2522810B2 (en) | Driving force transmission device | |
| JP2974357B2 (en) | Driving force transmission device for four-wheel drive vehicles | |
| JP2831089B2 (en) | Driving force transmission device | |
| JPH0533819A (en) | Drive force transmission device | |
| JPH05106656A (en) | Drive power transmitting device | |
| JPH04145239A (en) | Driving force transmission device | |
| JP2909342B2 (en) | Driving force transmission device | |
| JPH0533818A (en) | Drive force transmission device | |
| JPH0738743Y2 (en) | Driving force transmission device | |
| JP2557083B2 (en) | Driving force transmission device | |
| JPH0293129A (en) | Driving force transmitting device | |
| JP2510134Y2 (en) | Power transmission device | |
| JP2661217B2 (en) | Power transmission mechanism |