JPH0659785B2 - Power transmission device - Google Patents
Power transmission deviceInfo
- Publication number
- JPH0659785B2 JPH0659785B2 JP61137013A JP13701386A JPH0659785B2 JP H0659785 B2 JPH0659785 B2 JP H0659785B2 JP 61137013 A JP61137013 A JP 61137013A JP 13701386 A JP13701386 A JP 13701386A JP H0659785 B2 JPH0659785 B2 JP H0659785B2
- Authority
- JP
- Japan
- Prior art keywords
- oil pump
- shaft
- planetary gear
- output shaft
- case
- 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 - Lifetime
Links
Description
【発明の詳細な説明】 産業上の利用分野 本発明は入力軸と出力軸との相対回転数に応じて自動的
にトルク伝達を行う動力伝達装置、特に４輪駆動車のト
ランスファ装置や差動制限装置として好適な動力伝達装
置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device that automatically transmits torque in accordance with the relative rotational speed between an input shaft and an output shaft, and more particularly to a transfer device and a differential device for a four-wheel drive vehicle. The present invention relates to a power transmission device suitable as a limiting device.
従来技術とその問題点 従来、入力軸と出力軸との両軸の相対回転数に応じて駆
動されるオイルポンプを介して連結し、該オイルポンプ
の駆動抵抗によってトルクを伝達する動力伝達装置が特
開昭60-116525号公報にて公知となっている。この動力
伝達装置は、オイルポンプの駆動抵抗のみでトルクを伝
達するものであるため、容量の大きなポンプを高圧で使
用する必要があり、装置が大型化するとともに、高圧で
使用するため耐久性の面で不利であるなどの欠点があ
る。Conventional technology and its problems Conventionally, there has been a power transmission device that is connected via an oil pump driven according to the relative rotational speeds of both the input shaft and the output shaft, and that transmits torque by the drive resistance of the oil pump. It is known from JP-A-60-116525. Since this power transmission device transmits torque only by the drive resistance of the oil pump, it is necessary to use a pump with a large capacity at high pressure, and the size of the device becomes large, and since it is used at high pressure, durability is high. There are drawbacks such as disadvantages in terms of aspect.
また、この動力伝達装置を４輪駆動車のトランスファ装
置として使用した場合、入出力軸の相対回転数は1000rp
m以下であるため、高い油圧を発生するためにはオイル
ポンプの種類が限定されるだけでなく、高い寸法精度が
要求され、結局高価となる欠点がある。When this power transmission device is used as a transfer device for a four-wheel drive vehicle, the relative rotation speed of the input / output shaft is 1000 rp.
Since it is m or less, not only the type of oil pump is limited to generate a high hydraulic pressure, but also high dimensional accuracy is required, which is expensive after all.
発明の目的 本発明はかかる従来の問題点に鑑みてなされたもので、
その目的は、オイルポンプの小型化、高寿命化を図り、
かつ安価に構成できる動力伝達装置を提供すことにあ
る。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems,
The purpose is to reduce the size of the oil pump and extend its life.
Another object of the present invention is to provide a power transmission device that can be configured at low cost.
発明の構成 上記目的を達成すために、本発明は、入力軸と出力軸と
の相対回転数の大きさに応じたトルク伝達を行う動力伝
達装置において、入力軸又は出力軸の一方と一体回転
し、内部に作動油を封入したケースと、ケース内に入力
軸および出力軸と同軸上に配置された中間軸と、ケース
内に収容され、リングギヤがケースと連結され、キャリ
ヤが入力軸又は出力軸の他方と連結され、サンギヤが中
間軸と連結され、入力軸と出力軸との相対回転を増速し
て中間軸を駆動する遊星歯車機構と、ケース内に遊星歯
車機構と軸方向に並列に収容され、中間軸によって駆動
されるオイルポンプと、オイルポンプの吐出口と遊星歯
車機構の収容室との間に形成され、オイルポンプに駆動
抵抗を発生させるオリフィスとを備え、オイルポンプか
ら吐出された作動油はオリフィスを通って遊星歯車機構
の収容室に入り、遠心力によって遊星歯車機構の外径側
へ流れた後、オイルポンプの吸収口へ吸い込まれるよう
にケース内を循環するようにしたものである。To achieve the above object, the present invention provides a power transmission device that transmits torque according to the magnitude of the relative rotation speed between an input shaft and an output shaft, and rotates integrally with one of the input shaft and the output shaft. Then, a case with hydraulic oil sealed inside, an intermediate shaft arranged coaxially with the input shaft and output shaft in the case, housed in the case, the ring gear is connected to the case, the carrier is the input shaft or the output. The planetary gear mechanism, which is connected to the other side of the shaft and the sun gear is connected to the intermediate shaft, drives the intermediate shaft by accelerating the relative rotation between the input shaft and the output shaft, and the planetary gear mechanism in the case in parallel with the axial direction. The oil pump driven by the intermediate shaft and an orifice formed between the discharge port of the oil pump and the storage chamber of the planetary gear mechanism to generate driving resistance in the oil pump. It The operating oil that has flowed through the orifice enters the storage chamber of the planetary gear mechanism, flows to the outer diameter side of the planetary gear mechanism by centrifugal force, and then circulates in the case so that it is sucked into the absorption port of the oil pump. It was done.
実施例の説明 第１図は本発明の動力伝達装置を例えば４輪駆動車のト
ランスファ装置に適用した一例を示し、入力軸１は例え
ば前輪に結合され、出力軸２は後輪に結合されている。
出力軸２にはケース３が一体に結合されており、このケ
ース３の端部は軸受４を介して入力軸１により支持され
ている。また、ケース３と入力軸１との間にオイルシー
ル５が配置されており、これによりケース３の内部に充
填された作動油の油漏れを防止している。DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows an example in which the power transmission device of the present invention is applied to, for example, a transfer device of a four-wheel drive vehicle, in which an input shaft 1 is connected to a front wheel and an output shaft 2 is connected to a rear wheel. There is.
A case 3 is integrally connected to the output shaft 2, and an end portion of the case 3 is supported by the input shaft 1 via a bearing 4. Further, an oil seal 5 is arranged between the case 3 and the input shaft 1 to prevent the hydraulic oil filled in the case 3 from leaking.
上記入力軸１の端部にはキャリヤ６が一体に形成されて
おり、このキャリヤ６にはピン７を介して複数のプラネ
タリギヤ８が回転自在に支持されている。このプラネタ
リギヤ８は、上記ケース３の内周面に一体形成されたリ
ングギヤ９と噛み合っている。上記入力軸１と出力軸２
との間には中間軸10が同軸上に回転自在に支持されてお
り、この中間軸10の左端部近傍には上記プラネタリギヤ
８と噛み合うサンギヤ11が一体形成され、上記キャリヤ
６，プラネタリギヤ８，リングギヤ９，サンギヤ11によ
って遊星歯車機構Ａを構成している。A carrier 6 is integrally formed at the end of the input shaft 1, and a plurality of planetary gears 8 are rotatably supported on the carrier 6 via pins 7. The planetary gear 8 meshes with a ring gear 9 formed integrally with the inner peripheral surface of the case 3. Input shaft 1 and output shaft 2
An intermediate shaft 10 is rotatably supported coaxially between and, and a sun gear 11 that meshes with the planetary gear 8 is integrally formed near the left end of the intermediate shaft 10, and the carrier 6, planetary gear 8, ring gear 9, the sun gear 11 constitutes a planetary gear mechanism A.
上記中間軸10の右端部近傍にはスプライン12が形成され
ており、このスプライン12には第２図に示すトロコイド
型オイルポンプＢの外歯ギヤ13がスプライン係合してい
る。また、上記外歯ギヤ13と噛み合う内歯ギヤ14はケー
ス３の内側に固定されたオイルポンプボデー15内に偏心
状態でかつ摺動自在に嵌合している。上記オイルポンプ
Ｂと遊星歯車機構Ａとの間にはケース３の内側に固定さ
れた隔壁16が設けられており、この隔壁16にはオイルポ
ンプＢが第２図矢印方向に駆動された時の吸込口17（逆
駆動時には吐出口となる）と吐出口18（逆駆動時には吸
込口となる）とが形成されている。上記吸込口17と吐出
口18にはそれぞれオリフィス19,20と一方弁21,22とが設
けられており、オイルポンプＢが正逆いずれの方向に駆
動されても作動油を循環させることができる。例えば、
オイルポンプＢが第２図矢印方向に駆動されると、遊星
歯車機構Ａを収容した室に充填された作動油は一方弁21
を介して吸込口17に吸い込まれ、吐出口18のオリフィス
20を通って遊星歯車機構Ａを収容した室へと吐出され、
遊星歯車機構Ａを潤滑した後、再び吸込口17の一方弁21
からオイルポンプＢへ戻される。A spline 12 is formed near the right end of the intermediate shaft 10, and an external gear 13 of a trochoidal oil pump B shown in FIG. 2 is spline-engaged with the spline 12. An internal gear 14 that meshes with the external gear 13 is eccentrically and slidably fitted in an oil pump body 15 fixed inside the case 3. A partition wall 16 fixed inside the case 3 is provided between the oil pump B and the planetary gear mechanism A. The partition wall 16 has a partition wall when the oil pump B is driven in the direction of the arrow in FIG. A suction port 17 (which serves as a discharge port during reverse driving) and a discharge port 18 (which serves as a suction port during reverse driving) are formed. The suction port 17 and the discharge port 18 are provided with orifices 19 and 20 and one-way valves 21 and 22, respectively, so that hydraulic oil can be circulated regardless of whether the oil pump B is driven in the forward or reverse direction. . For example,
When the oil pump B is driven in the direction of the arrow shown in FIG. 2, the hydraulic oil filled in the chamber accommodating the planetary gear mechanism A has a one-way valve 21.
Is sucked into the suction port 17 via the
It is discharged through 20 to the chamber containing the planetary gear mechanism A,
After lubricating the planetary gear mechanism A, one valve 21 of the suction port 17 is again provided.
Is returned to the oil pump B.
なお、キャリヤ６と隔壁16との間にはスラストワッシャ
23が配置されている。A thrust washer is provided between the carrier 6 and the partition wall 16.
23 are arranged.
作動の説明 上記構成の動力伝達装置の作動を説明する。まず前輪と
後輪とが同一速度で回転し、入力軸１と出力軸２との間
に相対回転がない時には、遊星歯車機構Ａを構成するキ
ャリヤ６，プラネタリギヤ８，リングギヤ９，サンギヤ
11は一体回転し、中間軸10も入，出力軸１，２と一体回
転するため、オイルポンプＢは何ら駆動されず、吐出油
圧は零である。そのため、駆動抵抗は発生せず、入力軸
１のトルクは出力軸２へ伝達されない。Description of Operation The operation of the power transmission device having the above configuration will be described. First, when the front wheels and the rear wheels rotate at the same speed and there is no relative rotation between the input shaft 1 and the output shaft 2, the carrier 6, the planetary gear 8, the ring gear 9, and the sun gear that constitute the planetary gear mechanism A are formed.
Since 11 rotates integrally, the intermediate shaft 10 also rotates integrally with the output shafts 1 and 2, the oil pump B is not driven at all, and the discharge hydraulic pressure is zero. Therefore, no drive resistance is generated and the torque of the input shaft 1 is not transmitted to the output shaft 2.
いま前輪にスリップなどが発生して入力軸１と出力軸２
との間に相対回転差が生じると、プラネタリギヤ８はキ
ャリヤ６及びリングギヤ９とは逆方向に自転し、そのた
めサンギヤ11は入力軸１と同方向に回転する。いま、入
力軸１の回転数をＮ１、出力軸２の回転数をＮ２、リン
グギヤ９の歯数をＺＬ、サンギヤ11の歯数をＺＳとする
と、中間軸10の回転数Ｎｍは次式で表される。The front shaft is now slipping and the input shaft 1 and output shaft 2
When there is a relative rotation difference between the planetary gear 8 and the ring gear 9, the planetary gear 8 rotates in the direction opposite to that of the carrier 6 and the ring gear 9, so that the sun gear 11 rotates in the same direction as the input shaft 1. Now, assuming that the number of revolutions of the input shaft 1 is N 1 , the number of revolutions of the output shaft 2 is N 2 , the number of teeth of the ring gear 9 is Z L , and the number of teeth of the sun gear 11 is Z S , the number of revolutions N m of the intermediate shaft 10 is N m. Is expressed by the following equation.
したがって、中間軸10と出力軸２との相対回転数は次式
で与えられる。 Therefore, the relative rotational speed between the intermediate shaft 10 and the output shaft 2 is given by the following equation.
上式から明らかなように、中間軸10と出力軸２との相対
回転数は入力軸１と出力軸２との相対回転数（Ｎ１−Ｎ
２）の（１＋ＺＬ／ＺＳ）倍である。ここで、ＺＬ／Ｚ
Ｓは１よりかなり大きい数であるので、結局、中間軸10
と出力軸２との相対回転によって駆動されるオイルポン
プＢは入力軸１と出力軸２との相対回転数（Ｎ１−
Ｎ２）を増速して駆動されることになる。したがって、
オイルポンプＢは入，出力軸１，２の相対回転数が小さ
くても大きな駆動抵抗を発生し、入力軸１の余ったトル
クが出力軸２に伝達されるので、出力軸２の回転数は入
力軸１の回転数に近づく。出力軸２の回転数が入力軸１
の回転数に近づくと、これに伴ってオイルポンプＢの吐
出油圧も低くなり、伝達トルクは減少する。 As is clear from the above equation, the relative rotational speed between the intermediate shaft 10 and the output shaft 2 is the relative rotational speed between the input shaft 1 and the output shaft 2 (N 1 -N
2 ) times (1 + Z L / Z S ). Where Z L / Z
Since S is a number that is considerably larger than 1, after all, the intermediate axis 10
The oil pump B driven by the relative rotation between the input shaft 1 and the output shaft 2 has a relative rotational speed (N 1 −
N 2 ) will be accelerated and it will be driven. Therefore,
The oil pump B generates a large drive resistance even if the relative rotational speeds of the input and output shafts 1 and 2 are small, and the surplus torque of the input shaft 1 is transmitted to the output shaft 2. Therefore, the rotational speed of the output shaft 2 is The rotation speed of the input shaft 1 approaches. The rotation speed of the output shaft 2 is the input shaft 1
When the rotation speed approaches, the discharge hydraulic pressure of the oil pump B also decreases and the transmission torque decreases.
また、上記オイルポンプＢによる伝達トルクだけでな
く、遊星歯車機構Ａのプラネタリギヤ８からリングギヤ
９を介して出力軸２にトルクが伝達され、この伝達トル
クはむしろオイルポンプＢを経て伝達されるトルクより
大きいため、オイルポンプＢの負担を軽減できる。した
がって、オイルポンプＢを小型としても動力伝達装置全
体として大きな伝達トルクを確保でき、しかもオイルポ
ンプＢの負担を軽減できる分、オイルポンプＢの吐出油
圧を低減でき、寿命向上を実現できる。Further, not only the torque transmitted by the oil pump B but also the torque transmitted from the planetary gear 8 of the planetary gear mechanism A to the output shaft 2 via the ring gear 9, and this transmitted torque is rather than the torque transmitted via the oil pump B. Since it is large, the load on the oil pump B can be reduced. Therefore, even if the oil pump B is small, a large transmission torque can be secured in the entire power transmission device, and the load on the oil pump B can be reduced, so that the discharge hydraulic pressure of the oil pump B can be reduced and the life can be improved.
なお、上記実施例では、１を入力軸とし、２を出力軸と
したが、これとは逆に２を入力軸とし、１を出力軸とし
てもよい。即ち、入力軸１を遊星歯車機構Ａのリングギ
ヤと連結し、キャリヤを出力軸２と連結すればよい。In the above embodiment, 1 is the input shaft and 2 is the output shaft, but conversely, 2 may be the input shaft and 1 may be the output shaft. That is, the input shaft 1 may be connected to the ring gear of the planetary gear mechanism A, and the carrier may be connected to the output shaft 2.
また、オイルポンプＢとしてはトロコイドポンプに限ら
ず、内接ギヤポンプ、ベーンポンプなど従来公知のオイ
ルポンプで代用できる。Further, the oil pump B is not limited to the trochoid pump, and a conventionally known oil pump such as an internal gear pump or a vane pump can be used instead.
発明の効果 以上の説明で明らかなように、本発明によれば入力軸又
は出力軸とオイルポンプとの間、及び入力軸と出力軸と
の間に遊星歯車機構を配置し、入力軸と出力軸との相対
回転を増速してオイルポンプを駆動するようにしたの
で、オイルポンプを小型化しても効率良く油を吐出で
き、入力軸と出力軸の相対回転が小さくても大きなトル
クを伝達できる。また、伝達トルクの大部分は遊星歯車
機構を介して伝達されるため、オイルポンプにかかる負
担を軽減でき、オイルポンプの寿命を向上させることが
できる。さらに、オイルポンプの種類や寸法精度の制約
がないので、既存の安価なオイルポンプを使用できる。
さらにまた、ケースの内部に遊星歯車機構とオイルポン
プとを軸方向に並列に収容し、ケースの内部に作動油を
封入して循環させるようにしたので、極めてコンパクト
に動力伝達装置を構成でき、しかも外部に油漏れをきた
さないので、プラペラシャフトやドライブシャフトの途
中にも配置でき、配置の自由度が高い。As is apparent from the above description, according to the present invention, the planetary gear mechanism is arranged between the input shaft or the output shaft and the oil pump, and between the input shaft and the output shaft, and the input shaft and the output shaft are arranged. Since the oil pump is driven by speeding up the relative rotation with the shaft, oil can be discharged efficiently even if the oil pump is downsized, and large torque is transmitted even if the relative rotation between the input shaft and the output shaft is small. it can. Further, since most of the transmission torque is transmitted via the planetary gear mechanism, the load on the oil pump can be reduced and the life of the oil pump can be improved. Furthermore, since there is no restriction on the type or dimensional accuracy of the oil pump, the existing inexpensive oil pump can be used.
Furthermore, since the planetary gear mechanism and the oil pump are accommodated in parallel in the axial direction inside the case and the working oil is enclosed and circulated in the case, the power transmission device can be configured extremely compactly, Moreover, since it does not leak oil to the outside, it can be placed in the middle of the propeller shaft or drive shaft, giving a high degree of freedom in placement.
第１図は本発明に係る動力伝達装置の一例の断面図、第
２図は第１図のII−II線断面図である。 １…入力軸、２…出力軸、３…ケース、６…キャリヤ、
８…プラネタリギヤ、９…リングギヤ、10…中間軸、11
…サンギヤ、19,20…オリフィス、21,22…一方弁、Ａ…
遊星歯車機構、Ｂ…オイルポンプ。FIG. 1 is a sectional view of an example of a power transmission device according to the present invention, and FIG. 2 is a sectional view taken along line II-II of FIG. 1 ... Input shaft, 2 ... Output shaft, 3 ... Case, 6 ... Carrier,
8 ... Planetary gear, 9 ... Ring gear, 10 ... Intermediate shaft, 11
... Sun gear, 19,20 ... Orifice, 21,22 ... One-way valve, A ...
Planetary gear mechanism, B ... Oil pump.
Claims (1)
応じたトルク伝達を行う動力伝達装置において、 入力軸又は出力軸の一方と一体回転し、内部に作動油を
封入したケースと、 ケース内に入力軸および出力軸と同軸上に配置された中
間軸と、 ケース内に収容され、リングギヤがケースと連結され、
キャリヤが入力軸又は出力軸の他方と連結され、サンギ
ヤが中間軸と連結され、入力軸と出力軸との相対回転を
増速して中間軸を駆動する遊星歯車機構と、 ケース内に遊星歯車機構と軸方向に並列に収容され、中
間軸によって駆動されるオイルポンプと、 オイルポンプの吐出口と遊星歯車機構の収容室との間に
形成され、オイルポンプに駆動抵抗を発生させるオリフ
ィスとを備え、 オイルポンプから吐出された作動油はオリフィスを通っ
て遊星歯車機構の収容室に入り、遠心力によって遊星歯
車機構の外径側へ流れた後、オイルポンプの吸込口へ吸
い込まれるようにケース内を循環することを特徴とする
動力伝達装置。1. A power transmission device for transmitting torque according to a relative rotational speed between an input shaft and an output shaft, the case rotating integrally with one of the input shaft and the output shaft and having hydraulic oil sealed inside. And an intermediate shaft arranged coaxially with the input shaft and the output shaft in the case, and housed in the case, the ring gear is connected to the case,
The carrier is connected to the other of the input shaft or the output shaft, the sun gear is connected to the intermediate shaft, the planetary gear mechanism that accelerates the relative rotation between the input shaft and the output shaft to drive the intermediate shaft, and the planetary gear in the case. An oil pump that is housed in parallel with the mechanism in the axial direction and that is driven by an intermediate shaft; and an orifice that is formed between the discharge port of the oil pump and the housing chamber of the planetary gear mechanism and that generates drive resistance for the oil pump. A case where the hydraulic oil discharged from the oil pump enters the accommodation chamber of the planetary gear mechanism through the orifice, flows to the outer diameter side of the planetary gear mechanism by centrifugal force, and is then sucked into the suction port of the oil pump. A power transmission device characterized by circulating inside.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61137013A JPH0659785B2 (en) | 1986-06-12 | 1986-06-12 | Power transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61137013A JPH0659785B2 (en) | 1986-06-12 | 1986-06-12 | Power transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62292530A JPS62292530A (en) | 1987-12-19 |
| JPH0659785B2 true JPH0659785B2 (en) | 1994-08-10 |
Family
ID=15188777
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61137013A Expired - Lifetime JPH0659785B2 (en) | 1986-06-12 | 1986-06-12 | Power transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0659785B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE521149C2 (en) * | 2002-02-14 | 2003-10-07 | Volvo Lastvagnar Ab | Lubrication device for stepped gearbox |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60174629U (en) * | 1984-04-27 | 1985-11-19 | 三菱自動車工業株式会社 | 4-wheel drive drive coupling device |
| AT384283B (en) * | 1984-08-30 | 1987-10-27 | Steyr Daimler Puch Ag | DRIVE ARRANGEMENT FOR MOTOR VEHICLES WITH TWO DRIVE AXLES |
-
1986
- 1986-06-12 JP JP61137013A patent/JPH0659785B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62292530A (en) | 1987-12-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| SE9403711D0 (en) | Reversible power wrench | |
| JP6904214B2 (en) | Vehicle drive | |
| JP4700163B2 (en) | Automatic transmission for automobile | |
| GB860546A (en) | Improvements in and relating to motor-vehicle transmission systems | |
| US6533695B2 (en) | Hydromechanical transmission | |
| JP4369038B2 (en) | Hydraulic mechanical transmission | |
| US4756210A (en) | Torque converter bypass for an automatic transmission mechanism | |
| JPH0659785B2 (en) | Power transmission device | |
| JP2007051720A (en) | Oil pump drive mechanism for vehicular power unit | |
| US5127888A (en) | Differential gear for use in an automotive vehicle | |
| GB2187824A (en) | Fluid coupling transmission | |
| US6358177B1 (en) | Power transfer assembly equipped with a coplanar gear assembly | |
| CN114930050A (en) | Double differential ultrahigh speed reducing transmission | |
| JPWO2022065411A5 (en) | ||
| JP2513927B2 (en) | Pump drive | |
| JPH0544467A (en) | Water pump for engine | |
| GB2110759A (en) | Rotary positive-displacement fluid-machines | |
| JPH039155A (en) | Drive connecting device for four-wheel drive | |
| JPH0728450Y2 (en) | Power transmission device | |
| JP2837632B2 (en) | transmission | |
| FI84200C (en) | Gearbox | |
| JP4617708B2 (en) | Power transmission device | |
| RU2099614C1 (en) | Precession drive | |
| JP2001074125A (en) | Differential device | |
| JPH0670458B2 (en) | Lubrication device for four-wheel drive transfer |