JPS5913165A - Lubricating device of speed change gear - Google Patents
Lubricating device of speed change gearInfo
- Publication number
- JPS5913165A JPS5913165A JP3555683A JP3555683A JPS5913165A JP S5913165 A JPS5913165 A JP S5913165A JP 3555683 A JP3555683 A JP 3555683A JP 3555683 A JP3555683 A JP 3555683A JP S5913165 A JPS5913165 A JP S5913165A
- Authority
- JP
- Japan
- Prior art keywords
- lubricating oil
- oil
- hole
- transmission
- lubricating
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
【発明の詳細な説明】 本発明は変速装置の潤滑装置に関する。[Detailed description of the invention] The present invention relates to a lubricating device for a transmission.
入力側部材と出力側部材との間に変速機構を配設し、該
変速機構を出力側部材に接続される回転ハウジング内に
収納すると共に該回転ハウジング内に潤滑油を封入して
なる変速装置において、潤滑油は変速装置の回転遠心力
でハウジングの外周部方向に押しやられ、ハウジングの
中心部附近に収納されるギヤ、クラッチ、ベアリング等
の転動部、摺動部等の潤滑が不十分になり易く、発熱、
フリクシミン増加による伝達効率の低下、異常摩耗によ
る耐久性の劣化等の問題が生じると共に経時に伴う潤滑
油の汚濁が問題となる。A transmission device in which a transmission mechanism is disposed between an input side member and an output side member, the transmission mechanism is housed in a rotating housing connected to the output side member, and lubricating oil is sealed in the rotating housing. In this case, the lubricating oil is pushed toward the outer periphery of the housing by the rotational centrifugal force of the transmission, resulting in insufficient lubrication of the rolling and sliding parts of gears, clutches, bearings, etc. stored near the center of the housing. prone to fever,
Problems such as a decrease in transmission efficiency due to an increase in friximin and a decrease in durability due to abnormal wear occur, and contamination of the lubricating oil over time also becomes a problem.
本発明は上述の問題点に鑑みてなされたもので。The present invention has been made in view of the above-mentioned problems.
オイルポンプとオイルタンクを備えるエンジンに連結す
る入力側部材と出力側部材との間に変速機構を配設し、
該変速機構を出方側部材に接続される回転ハウジング内
に収納してなる変速装置において、該回転ハウジング内
に潤滑油流送装置を配設し、該オイルポンプによりオイ
ルタンクがら該回転ハウジング内に潤滑油を供給し、該
回転ハウジング外周部方向に流動した潤滑油を該潤滑油
流送装置により回転中心方向に強制的に流送してオイル
タンクに戻すようにし、清浄な潤滑油で変速装置の転動
部、摺動部等の潤滑をむらなく十分に行ない、潤滑不良
による発熱、ブリクシュンの増加による動力達効率の低
下、異常摩耗等による耐久性の劣化等の発生をなくす変
速装置の潤滑装置を提供することを目的とする。A transmission mechanism is disposed between an input side member and an output side member connected to an engine including an oil pump and an oil tank,
In a transmission device in which the transmission mechanism is housed in a rotating housing connected to an output side member, a lubricating oil flow device is disposed in the rotating housing, and the oil pump moves the oil tank from the inside of the rotating housing. The lubricating oil flowing toward the outer periphery of the rotating housing is forcibly flowed toward the center of rotation by the lubricating oil flow device and returned to the oil tank, and the clean lubricating oil is used to shift gears. A transmission system that lubricates the rolling and sliding parts of the equipment evenly and sufficiently to eliminate heat generation due to poor lubrication, decrease in power delivery efficiency due to increased friction, and deterioration of durability due to abnormal wear, etc. The purpose is to provide a lubricating device.
以下本発明を補機駆動用変速装置に用いた実施例を図面
を参照して説明する。Embodiments in which the present invention is applied to a transmission for driving auxiliary equipment will be described below with reference to the drawings.
第１図はエンジンのクランク軸先端に取り付けた補機駆
動用変速装置の垂直縦断面図、第２図は変速装置内部の
変速、機構である遊早ギヤ装置を利用した潤滑油流送装
置の構成図である。Figure 1 is a vertical cross-sectional view of a transmission for driving auxiliary equipment attached to the tip of the engine's crankshaft, and Figure 2 shows the speed change inside the transmission and the lubricating oil flow system using an idle gear mechanism. FIG.
入力側部材であるエンジン１のクランク軸２にはエンジ
ン内部の各摺動部に潤滑油を供給するオイルポンプ３が
接続され、クランク軸２の先端部２ａにはタイミングベ
ルト用のプーリ４がキー５を介して嵌合固定されると共
に、変速装置６の入３−
力価であるインプットフランジ７がキーＴ−８，及びボ
ルト９によって固定されている１、変速装置６の出力側
に接続され外側に出力側部材であるプーリ１０が嵌合さ
れる回転ハウジング１１のボス部ｊｌａはベアリング１
２を介してインプットフランジ７の軸部７ａ先端部に支
持されている。い。An oil pump 3 that supplies lubricating oil to each sliding part inside the engine is connected to the crankshaft 2 of the engine 1, which is an input side member, and a timing belt pulley 4 is connected to the tip 2a of the crankshaft 2. 5, and the input flange 7 of the transmission 6 is connected to the output side of the transmission 6. The boss part jla of the rotary housing 11 to which the pulley 10, which is the output side member, is fitted is the bearing 1.
2 at the tip of the shaft portion 7a of the input flange 7. stomach.
クランク軸２の先端部２ａの回転中心部にはオイルポン
プ３の潤滑油吐出孔１３に連通ずる潤滑油孔２ｂが穿設
され、該油孔２ｂはボルト９の中心に穿設された潤滑油
孔９ａと連通している。該油孔９ａはポル、ト９の頭部
側において拡径され、この拡径された潤滑油孔９ｂ内に
はプラグ９ｃが嵌合されている。プラグ９ｃの外面部に
は、軸方向の切欠轡９ｄが全長に亘って形成され、千の
切欠き９ｄを介して油孔９ｂのポル８９頭部側聞口部と
油孔９ａとが連通されると共に切欠き９ｄは絞りの作用
をするようになっている。油孔２ｂ、９ａに４１潤滑油
導管９ｆが貫通され、油孔？ａと導管９ｆとの間隙によ
って絞り１４が形成され、導管９ｆの一端はプラグ９ｃ
の内部に穿設された潤滑油孔９ｅに一４＝
嵌合され、導管９ｆの他端はオイルタンク１５に連通す
る嵌合孔２ｃに嵌合されている。またボルト９には油孔
９ａ及び油孔９ｅと夫々連通する半径方向の潤滑油孔９
ｇ、９ｈが穿設され、クランク軸２の先端部２ａにはこ
れら油孔９ｇ＊９ｈと夫々ボルト９の外周に刻設された
環状溝９ｉ、９ｊを介して連通ずる半径方向の潤滑油孔
２ｄ、２ｇが穿設されている。さらにインプットプラン
ジ７の軸部７ａには油孔２ｄ、２ｅと夫々先端部２ａ外
周に形成された環状溝２ｆ、 ２ｇを介して連通ずる半
径方向の潤滑油孔７ｂ、 ７ｃが穿設されている。A lubricating oil hole 2b that communicates with the lubricating oil discharge hole 13 of the oil pump 3 is formed in the rotational center of the tip 2a of the crankshaft 2, and the lubricating oil hole 2b is connected to the lubricating oil hole 2b that is connected to the lubricating oil discharge hole 13 of the oil pump 3. It communicates with hole 9a. The oil hole 9a is enlarged in diameter on the head side of the port 9, and a plug 9c is fitted into the enlarged lubricating oil hole 9b. An axial notch 9d is formed over the entire length of the outer surface of the plug 9c, and the oil hole 9a is communicated with the port 89 on the head side of the oil hole 9b through the 9d notch 9d. At the same time, the notch 9d functions as a diaphragm. The 41 lubricating oil conduit 9f is passed through the oil holes 2b and 9a, and the oil hole ? A throttle 14 is formed by the gap between the conduit 9f and the conduit 9f, and one end of the conduit 9f is connected to the plug 9c.
The other end of the conduit 9f is fitted into a fitting hole 2c communicating with the oil tank 15. The bolt 9 also has radial lubricating oil holes 9 that communicate with the oil holes 9a and 9e, respectively.
radial lubricating oil holes are formed in the tip 2a of the crankshaft 2 and communicate with these oil holes 9g*9h via annular grooves 9i and 9j carved in the outer periphery of the bolt 9, respectively. 2d and 2g are drilled. Further, the shaft portion 7a of the input plunger 7 is provided with radial lubricating oil holes 7b and 7c that communicate with the oil holes 2d and 2e via annular grooves 2f and 2g formed on the outer periphery of the tip portion 2a, respectively. .
、 インプットフランジ７の外周ドラム７ｄには内歯ギ
ヤを有するリングギヤ１６が圧入嵌合され、またインプ
ットフランジ７の一側面に遠心クラッチ１７が取り付け
られている。この遠心クラッチ１７は、エンジン回転数
が所定回転数以下のときはインプットフランジ７とクラ
ッチドラム１８とを摩擦係合し、エンジン回転数が所定
数を越えたときこの係合を解除するようになっている。A ring gear 16 having an internal gear is press-fitted into the outer peripheral drum 7d of the input flange 7, and a centrifugal clutch 17 is attached to one side of the input flange 7. The centrifugal clutch 17 frictionally engages the input flange 7 and the clutch drum 18 when the engine speed is below a predetermined speed, and releases this engagement when the engine speed exceeds a predetermined speed. ing.
なお、クラッチドラム１８の内周面と回転ハウジング１
１のボス部１１ａの外周面との接触部に開口する潤滑油
孔１１ｂがボス部１１ａに穿設されている。Note that the inner peripheral surface of the clutch drum 18 and the rotating housing 1
A lubricating oil hole 11b is formed in the boss portion 11a, and the lubricating oil hole 11b is opened at a contact portion with the outer circumferential surface of the boss portion 11a.
リングギヤ１６の外周部に形成された入力側ドラム１６
ａ及び回転ハウジング１１に液密に固定されたりャカバ
ー１１ｃの内面に形成された出力側ドラムＩｌｄの外周
面に正方形乃至矩形断面のスプリング材料を多重コイル
にしたランプスプリング１９が弛緩状態で嵌合され、弛
緩状態のときラップスプリング１９の内周面と入力側１
くラム１６ａ及び出力側ドラムＩ’ｄの外周面との間に
は所定の間隔が形成される。このラップスプリング１９
の入力端１９ａはクラッチドラム１８の係合孔１８ａと
係合し、出力端１９ｂはリヤカバー１１ｃの係合孔１１
ｅと係合している。そして、入力端１９ａから出力端１
９ｂへ回転が伝えられるとき、ラップスプリング１９が
巻き締められ、クラッチドラム１８．入力側ドラム１６
ａ、出力側ドラムｌｌｄ及び回転ハウジング１１が一体
化されるようになっている。An input drum 16 formed on the outer periphery of the ring gear 16
A lamp spring 19 made of multiple coils of spring material with a square or rectangular cross section is fitted in a relaxed state on the outer circumferential surface of the output drum Ild formed on the inner surface of the carrier cover 11c which is liquid-tightly fixed to the rotating housing 11. , the inner peripheral surface of the wrap spring 19 and the input side 1 in the relaxed state
A predetermined interval is formed between the drum 16a and the outer peripheral surface of the output drum I'd. This wrap spring 19
The input end 19a of is engaged with the engagement hole 18a of the clutch drum 18, and the output end 19b is engaged with the engagement hole 11 of the rear cover 11c.
It is engaged with e. Then, from the input end 19a to the output end 1
When rotation is transmitted to clutch drum 18.9b, wrap spring 19 is tightened and clutch drum 18. Input side drum 16
a. The output side drum lld and the rotating housing 11 are integrated.
エンジン１のシリンダケース１ａに弾性材２０を介して
ボルト２１により締着固定されている固定腕２２の中空
軸２２ａ内面には、ベアリング２３及びオイルシール２
４を介してクランク軸２の先端部２ａに嵌挿されたイン
プットフランジ７の軸部７ａが支持される。さらに、サ
ンギヤ２５のボス部２５ａが中空軸２２ａの内周面にス
プライン結合２６によって嵌合固定され、ボス部２５ａ
はベアリング２７を介して軸部７ａに支持されている。A bearing 23 and an oil seal 2 are provided on the inner surface of the hollow shaft 22a of the fixed arm 22, which is fastened to the cylinder case 1a of the engine 1 with a bolt 21 via an elastic member 20.
4, a shaft portion 7a of an input flange 7 that is fitted into the tip portion 2a of the crankshaft 2 is supported. Further, the boss portion 25a of the sun gear 25 is fitted and fixed to the inner peripheral surface of the hollow shaft 22a by a spline connection 26, and the boss portion 25a
is supported by the shaft portion 7a via a bearing 27.
また、ベアリング２３側のボス部２５ａ端部と軸部７ａ
との間にはオイルシール２８が介装され、ベアリング２
３の位置に開口する油孔７ｂとベアリング２７付近に開
口する油孔７ｃとの連通が遮断されている。In addition, the end of the boss portion 25a on the side of the bearing 23 and the shaft portion 7a
An oil seal 28 is interposed between the bearing 2 and the bearing 2.
Communication between the oil hole 7b that opens at position 3 and the oil hole 7c that opens near the bearing 27 is cut off.
リングギヤ１６とサンギヤ２５との間には、これ等に噛
合する３個のピニオンギヤ２９が配設され、これ等のピ
ニオンギヤ２９は夫々支軸３０及びベアリング３１によ
り回転自在にキャリア３２に軸支されている。支軸３０
には軸心及び半径方向に沿う潤滑油路３０ａが穿設され
、潤滑油路３０ａを通じてベアリング３１に潤滑油が供
給されるよ一７＝
うになっている。またキャリア３２と中空軸２２ａの外
周部との間にはベアリング３３が介装され、キャリア３
２とリヤカバー１１ｃとの間には一方面クラッチ３４が
配設される。この一方向クラッチ３４は、変速装置６が
変速伝動時のときキャリア３２とリヤカバー１１ｃとを
係合してキャリア３２の回転運動を回転ハウジング１１
に伝達し、直結伝動時にはりャカバー１１ｃとキャリア
３２の回転差に基づいて空転するようになっている。Three pinion gears 29 are disposed between the ring gear 16 and the sun gear 25 and mesh with them, and each of these pinion gears 29 is rotatably supported by a carrier 32 by a support shaft 30 and a bearing 31. There is. Support shaft 30
A lubricating oil passage 30a is bored along the axis and radial direction, and lubricating oil is supplied to the bearing 31 through the lubricating oil passage 30a. Further, a bearing 33 is interposed between the carrier 32 and the outer circumference of the hollow shaft 22a, and the carrier 33
A one-sided clutch 34 is disposed between the rear cover 11c and the rear cover 11c. This one-way clutch 34 engages the carrier 32 and the rear cover 11c when the transmission 6 is transmitting a speed change, and transfers the rotational movement of the carrier 32 to the rotating housing 11.
During direct transmission, the carrier cover 11c and the carrier 32 rotate idly based on the rotation difference between the carrier cover 11c and the carrier 32.
リヤカバーｌｉｅはベアリング３５及びオイルシール３
６を介して中空軸２２ａの外周部に回転自在かつ液密に
支持されている。Rear cover lie has bearing 35 and oil seal 3
6, it is rotatably and liquid-tightly supported on the outer circumference of the hollow shaft 22a.
回転ハウジング１１内に配設される潤滑油流送装置３７
はリングギヤ１６．サンギヤ２５．ピニオンギヤ２９及
びキャリア３２から成る遊星ギヤ装置を利用して設ける
もので、中心側に配されるサンギヤ２５とこれに噛合う
外側の３個のピニオンギヤ２９との噛合い側、即ち第２
図においてリングギヤ１６が矢線方向に回転される場合
、ピニオンギヤ２９はやはり同方向に自転しながら不動
８−
のサンギヤ２５の周囲を同じく同方向に公転するから、
サンギヤ２５に対しピニオンギヤ２９を上位にして両ギ
ヤの左側に両ギヤの外周に沿って潤滑油案内壁３’２ａ
がキャリア３２に設けられる。Lubricating oil flow device 37 disposed within the rotating housing 11
is ring gear 16. Sun gear 25. It is provided using a planetary gear device consisting of a pinion gear 29 and a carrier 32, and is provided on the meshing side of the sun gear 25 disposed at the center and the three outer pinion gears 29 meshing with it, that is, the second
When the ring gear 16 is rotated in the arrow direction in the figure, the pinion gear 29 also rotates in the same direction and revolves around the stationary sun gear 25 in the same direction.
With the pinion gear 29 placed above the sun gear 25, a lubricating oil guide wall 3'2a is placed on the left side of both gears along the outer periphery of both gears.
is provided on the carrier 32.
サンギヤ２５は歯車の各谷部に潤滑油孔２５ｂ・・・が
半径方向に穿設され、サンギヤ２５の内孔には支軸３０
の反キャリア３１側を支持し、ピニオンギヤ２９とサン
ギヤ２５の側端面を覆う側板３８のボス部３８ａが嵌合
されている。このボス部３８ａは、各支軸２９に対向す
る位置に夫々油孔３８ｂが穿設され、キャリア３２の回
転に伴ないサンギヤ２５の油孔２５ｂと油孔３８ｂとが
順次合致する環状の回転ポートを形成している。ボス部
３８ａとその内周部にＯリング３９を介して嵌合される
インプットフランジ７の軸部７ａとの間に環状潤滑油路
４０が形成され、油路４０はインプットフランジ７の軸
部７ａに穿設されている半径方向の油孔７ｃと連通して
いる。尚、Ｏリング３９は油路４０に在る潤滑油がイン
プットフランジ７側に流出しないように設けるものであ
る。そして、オイルポンプ３の吸入側はオイルフィルタ
４１を介してオイルタンク１５に接続されている。The sun gear 25 has lubricating oil holes 25b... drilled in the radial direction in each valley of the gear, and a support shaft 30 in the inner hole of the sun gear 25.
A boss portion 38a of a side plate 38 that supports the side opposite to the carrier 31 and covers the side end surfaces of the pinion gear 29 and sun gear 25 is fitted. This boss portion 38a is an annular rotation port in which an oil hole 38b is formed at a position facing each support shaft 29, and the oil hole 25b of the sun gear 25 and the oil hole 38b sequentially match as the carrier 32 rotates. is formed. An annular lubricating oil passage 40 is formed between the boss portion 38a and the shaft portion 7a of the input flange 7, which is fitted to the inner peripheral portion of the boss portion 38a via an O-ring 39. It communicates with a radial oil hole 7c bored in the radial direction. The O-ring 39 is provided to prevent lubricating oil present in the oil passage 40 from flowing out to the input flange 7 side. The suction side of the oil pump 3 is connected to the oil tank 15 via an oil filter 41.
以上のように構成される本発明装置の実施例の作動につ
いて次に説明する。The operation of the embodiment of the apparatus of the present invention constructed as described above will now be described.
エンジン１のクランク軸２の回転と共にインプットフラ
ンジ７が回転し、この回転が低速のときは、インプット
フランジ７に設けられた遠心クラッチ１７がクラッチド
ラム１８と摩擦係合し、クラッチドラム１８に係合され
ているラップスプリング１９が巻き締められてクランク
軸２の回転は回転ハウジング１１及びプーリｌＯに１対
ｌに伝達される。この時リングギヤ１６の回転によりピ
ニオンギヤ２９はリングギヤ１６と同方向に自転と公転
を行い、この公転運動はキャリア３２に減速回転を与え
る。ここでクランク軸２の回転に対し減速されたキャリ
ア３２の回転はクランク軸２に直結されたりャカバー１
１ｃの回転より当然遅いので、この回転の差はキャリア
３２とリヤカバー１１ｃとの間に設けた一方向クラッチ
３４の空転によって逃がされる。 −
次にエンジンｌの回転が所定回転数以上になると、遠心
クラッチ１７に鋤らく遠心力により遠心クラッチ１７が
解離しインプットフランジ７とクラッチドラム１８との
係合が解け、ラップスプリング１９は自身の復元力と回
転により働らく遠心力のため弛緩し、入力側ドラム１６
ａと出力側ドラムｌｉｄとの結合が離れる。このためク
ランク軸２と一体に回転するリングギヤ１６の回転によ
りピニオンギヤ２９がリングギヤ１６と同方向に自転と
公転を行い、この公転運動と共に減速回転をしているキ
ャリア３２の回転は一方向クラッチ３４の噛合によりハ
ウジングＩＩに伝えられ、つまりエンジン１の回転はこ
の遊星ギヤ装置個有の減速比でプーリ１０を減速回転さ
せる。The input flange 7 rotates with the rotation of the crankshaft 2 of the engine 1, and when this rotation is at a low speed, the centrifugal clutch 17 provided on the input flange 7 frictionally engages with the clutch drum 18. The wrap spring 19 is tightened, and the rotation of the crankshaft 2 is transmitted to the rotating housing 11 and the pulley lO in a one-to-l ratio. At this time, the rotation of the ring gear 16 causes the pinion gear 29 to rotate and revolve in the same direction as the ring gear 16, and this revolution gives the carrier 32 decelerated rotation. Here, the rotation of the carrier 32, which is decelerated with respect to the rotation of the crankshaft 2, is directly connected to the crankshaft 2.
Since the rotation is naturally slower than that of the rear cover 11c, this difference in rotation is released by idling the one-way clutch 34 provided between the carrier 32 and the rear cover 11c. - Next, when the rotation of the engine l exceeds a predetermined rotation speed, the centrifugal clutch 17 is disengaged due to the centrifugal force exerted on the centrifugal clutch 17, the engagement between the input flange 7 and the clutch drum 18 is released, and the wrap spring 19 is released from its own The input side drum 16 relaxes due to the centrifugal force exerted by the restoring force and rotation.
The connection between a and the output drum lid is separated. Therefore, the rotation of the ring gear 16 that rotates together with the crankshaft 2 causes the pinion gear 29 to rotate and revolve in the same direction as the ring gear 16, and the rotation of the carrier 32, which is rotating at a reduced speed along with this orbital movement, is caused by the rotation of the one-way clutch 34. The rotation of the engine 1 is transmitted to the housing II through meshing, and the rotation of the engine 1 is reduced to rotate the pulley 10 at a reduction ratio unique to this planetary gear device.
クランク軸２の回転によって上述の様に変速装置６が駆
動される共にオイルポンプ３が駆動され、オイルポンプ
３はオイルタンク１５内の潤滑油をオイルフィルタ４１
を介して吸入し、清浄化された潤滑油を変速装置６内に
流送する。この潤滑油は潤滑油孔２ｂ、と潤滑油導管９
ｆとの間隙を通り。The rotation of the crankshaft 2 drives the transmission 6 as described above and also drives the oil pump 3, which transfers the lubricating oil in the oil tank 15 to the oil filter 41.
The lubricating oil is sucked in through the lubricating oil, and the cleaned lubricating oil is sent into the transmission 6. This lubricating oil is passed through the lubricating oil hole 2b and the lubricating oil conduit 9.
Pass through the gap with f.
−１】−
さらにボルト９の潤滑油孔９ａと導管９ｆとの間隙を通
り絞り１４によって減、圧され、以後２つの潤滑油流動
経路を主として、回転遠心力によって回転ハウジング１
１の外周壁方向に流動する。。。-1]- Further, the lubricating oil is passed through the gap between the lubricating oil hole 9a of the bolt 9 and the conduit 9f, and the pressure is reduced by the throttle 14, and thereafter the rotating housing 1 is
Flows toward the outer peripheral wall of No. 1. . .
一方の潤滑油流動経時を流動する潤滑油は、油孔９ ｇ
＋環状溝９ｉ、油孔２ｄ９．環状溝ネｆ、及び油孔７
ｂを通ってベアリング２３．オイルシール２４．２８を
潤滑し、さらにスプライン結合２６を通ってベアリング
３３，３５．、オイルシール３６を潤滑し、その後文・
軸３０の油路３０ａを通ってベアリング３１を潤滑する
と共に一方向クラッチ３４を潤滑してハウジング１１の
外周壁内面に至りラップバブリング１９を潤滑する。他
方の潤滑油流動経路を流動する潤滑油は、切欠き９ｄを
通ってさらに減圧され、次に油孔９ｂを通りベアリング
１２を潤滑すると共に油孔１１ｂを通ってクラッチドラ
ム１８とボス部１１ａの接触部を潤滑し、その後遠心ク
ラッチ１７の摺動部を潤滑してハウジング１１の外周壁
内面に至る。The lubricating oil flowing through one lubricating oil flow has an oil hole of 9 g.
+Annular groove 9i, oil hole 2d9. Annular groove f and oil hole 7
bearing 23 through b. It lubricates the oil seals 24, 28 and further passes through the spline connection 26 to the bearings 33, 35. , lubricate the oil seal 36, and then
The oil passes through the oil passage 30a of the shaft 30 to lubricate the bearing 31, the one-way clutch 34, and reaches the inner surface of the outer peripheral wall of the housing 11 to lubricate the lap bubbling 19. The lubricating oil flowing through the other lubricating oil flow path passes through the notch 9d and is further depressurized, then passes through the oil hole 9b to lubricate the bearing 12, and passes through the oil hole 11b to lubricate the clutch drum 18 and the boss portion 11a. The contact portion is lubricated, and then the sliding portion of the centrifugal clutch 17 is lubricated to reach the inner surface of the outer peripheral wall of the housing 11.
このように変速装置６の回転遠心力で回転ハウ１２−
リング１１の外周壁内面に集められた潤滑油のうち１、
キャリア３２の案内壁３２ａとピニオンギヤ２９との間
に補集された潤滑油はピニオンギヤ２９及びサンギヤ２
５の噛合い部に案内され、ここでサンギヤ２５の谷部に
穿設された潤滑油孔２５ｂに強制的に流入される。本実
施例における遊星ギヤ装置の場合、リングギヤ１６が第
２図における矢線方向に回転するとピニオンギヤ２９が
不動のサンギヤ２５の周囲をやはり同方向に自転しなが
ら公転する。従ってピニオンギヤ２９とサンギヤ２５と
の噛合い部の移動につれて潤滑油の流入されるサンギヤ
２５の潤滑油孔２５ｂは順次移動し、またキャリア３２
はピニオンギヤ２９の公転と一体に回転するから、サン
ギヤ２５の内孔に嵌合された側板３８のボス部３８ａの
油孔３８ｂはピニオンギヤ２・９の公転と共に順次上記
潤滑油の流入されるサンギヤ２５の潤滑油孔２５ｂと断
続的に合致していく。そして、サンギヤ２５の潤滑油孔
２５ｂに流入された潤滑油は、ボス部３８ａの油孔３８
ｂを、通って環状油路４０に流送される。環状油路４０
に流送された潤滑油はベアリング２７．オイルシール３
９，２８を潤滑し、その後油孔７ｃ、環状溝２ｇ、浦孔
２ｅ、環状溝９ｊ、油孔９ ｈ 、 ・、プラグ９ｃの
油孔９ ｅ ＋潤滑油導管９ｆを通じて潤滑油流送装置
３７の吐出力によりオイルタンク１５に戻される。この
ようにして、変速装置６の潤滑油か循環される。In this way, one of the lubricating oils collected on the inner surface of the outer circumferential wall of the rotating howe 12-ring 11 due to the centrifugal force of the rotation of the transmission 6,
The lubricating oil collected between the guide wall 32a of the carrier 32 and the pinion gear 29 is transferred to the pinion gear 29 and the sun gear 2.
5, where it is forced to flow into the lubricant hole 25b formed in the valley of the sun gear 25. In the case of the planetary gear device in this embodiment, when the ring gear 16 rotates in the direction of the arrow in FIG. 2, the pinion gear 29 revolves around the stationary sun gear 25 while also rotating in the same direction. Therefore, as the meshing portion between the pinion gear 29 and the sun gear 25 moves, the lubricating oil hole 25b of the sun gear 25 into which the lubricating oil flows sequentially moves, and the carrier 32
rotates together with the revolution of the pinion gear 29, so the oil hole 38b of the boss portion 38a of the side plate 38 fitted into the inner hole of the sun gear 25 is connected to the sun gear 25 through which the lubricating oil sequentially flows as the pinion gears 2 and 9 revolve. The lubricating oil hole 25b of FIG. The lubricating oil that has flowed into the lubricating oil hole 25b of the sun gear 25 is then transferred to the oil hole 38 of the boss portion 38a.
b, and is sent to the annular oil passage 40. Annular oil passage 40
The lubricating oil flowed to the bearing 27. oil seal 3
9, 28, and then the lubricating oil flow device 37 through the oil hole 7c, the annular groove 2g, the hole 2e, the annular groove 9j, the oil hole 9h, the oil hole 9e of the plug 9c + the lubricating oil conduit 9f. is returned to the oil tank 15 by the discharge force. In this way, the lubricating oil of the transmission 6 is circulated.
次に第３図に示す本発明装置の油圧系統の概略を第１図
及び第２図に基づいて説明する。Next, the outline of the hydraulic system of the apparatus of the present invention shown in FIG. 3 will be explained based on FIGS. 1 and 2.
変速装置６内の潤滑油流送装置３７は、遠心クラッチ１
７の作動にかかわらず、回転ハウジング１１の外周壁内
面に集められた潤滑油４２のうちキャリア３２の潤滑油
案内壁３２ａのレベルを超した油量をエンジン１側のオ
イルタンク１５に戻すようになっている。そして、エン
ジン回転数の上Ｍに伴って増大する変速装置６内に供給
される油量よりエンジン回転数の上昇に伴って増大する
潤滑油流送装置３７の吐出量の方が大きくなるように絞
り１４が調整されている。このため、回転ノ１ウリング
１１内のレベルは変速装置６の変速状態（直結、変速）
に関係なく常に一定量に保たれる。エンジン１側のオイ
ルタンク１５内の冷却された潤滑油４４がオイルフィル
タ旧を介して清浄されオイルポンプ３に吸い込まれ、ポ
ンプ３がエンジン１の各摺動部４５に潤滑油を供給する
と共に変速装置６に供給し変速装Ｗ６の各摺動部４６を
潤滑し、その後前述のように、潤滑油流送装置３７によ
り潤滑油がエンジン１側のオイルタンク１５に戻される
。また、エンジン１の回転数上昇に伴い上述した潤滑油
の循環サイクルを循環する油量が増大し、変速装置６の
回転に対応した潤滑油量が清浄化冷却化された状態で変
速装置６内を循環する。The lubricating oil flow device 37 in the transmission 6 is connected to the centrifugal clutch 1
Regardless of the operation of 7, the amount of lubricating oil 42 collected on the inner surface of the outer circumferential wall of the rotating housing 11 that exceeds the level of the lubricating oil guide wall 32a of the carrier 32 is returned to the oil tank 15 on the engine 1 side. It has become. The amount of oil supplied to the transmission 6 increases as the engine speed increases, so that the amount of oil discharged from the lubricating oil delivery device 37 increases as the engine speed increases. Aperture 14 has been adjusted. For this reason, the level in the rotating no. 1 ring 11 indicates the gear shift state of the transmission 6 (direct connection, gear shift).
It is always kept at a constant amount regardless of the The cooled lubricating oil 44 in the oil tank 15 on the engine 1 side is cleaned through the oil filter and sucked into the oil pump 3, and the pump 3 supplies lubricating oil to each sliding part 45 of the engine 1 and shifts gears. The lubricating oil is supplied to the device 6 to lubricate each sliding portion 46 of the transmission W6, and then, as described above, the lubricating oil is returned to the oil tank 15 on the engine 1 side by the lubricating oil flow device 37. Further, as the rotational speed of the engine 1 increases, the amount of oil circulating in the above-mentioned lubricating oil circulation cycle increases, and the amount of lubricating oil corresponding to the rotation of the transmission 6 is cleaned and cooled inside the transmission 6. cycle.
尚、上記実施例において、潤滑油流送装置を遊星ギヤ装
置を利用して設けた例について説明したが１本発明はこ
れに限定されず、回転ハウジング内に別個にオイルポン
プを設け、これに」二連の潤滑油流送装置の作動をさせ
てもよく、さらに、本実施例は補機駆動用変速装置を用
いた実施例としたが、これに限定されることなく、補機
以外の変速装置に本装置を利用することも可能である。In the above embodiment, an example was explained in which the lubricating oil flow device was provided using a planetary gear device, but the present invention is not limited to this. "Two lubricating oil flow devices may be operated.Furthermore, although this embodiment uses a transmission device for driving auxiliary equipment, the present invention is not limited to this. It is also possible to use this device in a transmission.
−１５＝
以上説明したように本発明では、オイルポンプとオイル
タンクを備えるエンジンに連結する入力側部材と出力側
部材との間に変速機構を配設し。-15= As explained above, in the present invention, a transmission mechanism is disposed between an input side member and an output side member connected to an engine including an oil pump and an oil tank.
該変速機構を出力側部材に接続される回転ハウジング内
に収納してなる変速装置において、該回転ハウジング内
に潤滑油流送装置を配設し、該オイルポンプによりオイ
ルタンクから該回転ハウジング内に潤滑油を供給し、該
回転ハウジング外周部方向に流動した潤滑油を該潤滑油
流送装置により回転中心方向に強制的に流送してオイル
タンクに戻すようにしたので、変速装置の転動部、摺動
部等をむらなく潤滑でき、変速機の駆動ロスを抑制でき
るので潤滑不良による発熱、フリクションの増加による
動力伝達効率の低下、異常摩耗による耐久性の劣化等の
発生を防止することができると共に、エンジンと変速機
との間で潤滑油の循環が成されることにより回転ハウジ
ング内に潤滑油を封入した場合に発生する経時に伴う潤
滑油の汚濁を減少させる事ができる効果を有する。In a transmission device in which the transmission mechanism is housed in a rotating housing connected to an output side member, a lubricating oil flow device is disposed in the rotating housing, and the oil pump transfers oil from the oil tank into the rotating housing. The lubricating oil is supplied, and the lubricating oil flowing toward the outer circumference of the rotating housing is forcibly flowed toward the center of rotation by the lubricating oil flow device and returned to the oil tank, thereby preventing rolling of the transmission. It can evenly lubricate parts, sliding parts, etc., and suppress drive loss in the transmission, thereby preventing heat generation due to poor lubrication, decrease in power transmission efficiency due to increased friction, and deterioration of durability due to abnormal wear. At the same time, by circulating the lubricating oil between the engine and the transmission, it has the effect of reducing the contamination of the lubricating oil that occurs over time when lubricating oil is sealed in the rotating housing. have
１６−
第１図は本発明の一実施例を適用した変速装置の垂直縦
断面図、第２図は第１図に示す変速装置内部の遊星ギヤ
装置を利用した潤滑油流送装置の構成図、第３図は本発
明装置の油圧系統を説明する概略図である。
１・・・エンジン、２・・・クランク軸（入力側部材）
。
３・・・オイルポンプ、６・・・変速装置、１０・・・
プーリ、（出力側部材）、１１・・・回転ハウジング、
１５・・・オイルタンク、１６，２５，２９．３２・
・・変速機構、３７・・・潤滑油流送装置。
出願人 本田技研工業株式会社
代理人 弁理士 渡部敏彦
秦３日16- Fig. 1 is a vertical cross-sectional view of a transmission to which an embodiment of the present invention is applied, and Fig. 2 is a configuration diagram of a lubricating oil flow device using a planetary gear device inside the transmission shown in Fig. 1. , FIG. 3 is a schematic diagram illustrating the hydraulic system of the apparatus of the present invention. 1...Engine, 2...Crankshaft (input side member)
. 3...Oil pump, 6...Transmission device, 10...
Pulley, (output side member), 11... rotating housing,
15...Oil tank, 16, 25, 29.32.
...speed change mechanism, 37...lubricating oil flow device. Applicant Honda Motor Co., Ltd. Agent Patent Attorney Toshihiko Watanabe Hata 3rd
Claims (1)
連結する入力側部材と出力側部材との間に変速機構を配
設し、該変速機構を出力側部材に接続される回転ハウジ
ング内に収納してなる変速装置において、該回転ハウジ
ング内に潤滑油流送装置を配設し、該オイルポンプによ
りオイルタンクから該回転ハウジング内に潤滑油を供給
し、該回転ハウジング外周部方向に流動した潤滑油を該
潤滑油流送装置により回転中心方向に強制的に流送して
オイルタンクに戻すようにしたことを特徴とする変速装
置の潤滑装置。 ２、 前記潤滑油流送装置は、前記変速機構の中心側動
力伝達ギヤと外側動力伝達ギヤとの噛合い側に有り少な
くとも外側動力伝達ギヤの外周に部分的に沿う潤滑油案
内壁、前記中心側動力伝達ギヤの噛合部に穿設された半
径方向の潤滑油孔及び前記中心側動力伝達ギヤの軸部内
孔に嵌合し、前記変速装置の回転に応じて前記潤滑油孔
と断続的に連通ずる油孔を設けた環状の回転ボートを有
し前記中心側及び外側の両動力伝達ギヤの噛合い運動に
より前記回転ハウジングの外周部方向に流動した前記潤
滑油を強制的に回転中心方向に流送するようにしたこと
を特徴とする特許請求の範囲第１項記載の変速装置の潤
滑装置。 ３、 オイルポンプ（３）の吐出孔（１３）に連通ずる
変速装置中心部のボルト（９）の中心に穿設された潤滑
油孔（９ａ）と該潤滑油孔（９ａ）内を貫通する潤滑油
導管（９ｆ）との間の絞り（１４）、及びボルト（９）
の頭部側の潤滑油孔（９ｂ）と該潤滑油孔（９ｂ）内に
嵌合されたプラグ（９Ｃ）との間の絞りを介して変速装
置内に流入し、プラグ（９ｃ）内部の潤滑油孔（９ｅ）
と前記潤滑油導管（９ｆ）によってオイルタンクへ流出
され、流入路と流出路が別経路となっていることを特徴
とする特許請求の範囲第１項又は第２項記載の変速装置
の潤滑装置。[Claims] 1. A rotating housing in which a transmission mechanism is disposed between an input side member and an output side member connected to an engine including an oil pump and an oil tank, and the transmission mechanism is connected to the output side member. In the transmission device housed in the rotary housing, a lubricating oil flow device is disposed within the rotary housing, and the oil pump supplies lubricating oil from the oil tank into the rotary housing, and the lubricating oil is supplied to the rotary housing in the direction of the outer circumference of the rotary housing. A lubrication device for a transmission, characterized in that the fluidized lubricating oil is forcibly flowed toward the center of rotation by the lubricating oil flow device and returned to the oil tank. 2. The lubricating oil flow device is located on the meshing side of the center side power transmission gear and the outer power transmission gear of the transmission mechanism, and includes a lubricating oil guide wall that extends at least partially along the outer periphery of the outer power transmission gear; A radial lubricating oil hole drilled in a meshing part of the side power transmission gear and a shaft inner hole of the center side power transmission gear are fitted, and the lubricating oil hole is intermittently connected to the lubricating oil hole in accordance with the rotation of the transmission. An annular rotating boat is provided with a communicating oil hole, and the lubricating oil flowing toward the outer periphery of the rotating housing is forced toward the center of rotation by the meshing motion of both the center and outer power transmission gears. A lubricating device for a transmission according to claim 1, characterized in that the lubricating device is adapted to be flow-fed. 3. A lubricating oil hole (9a) drilled in the center of the bolt (9) in the center of the transmission that communicates with the discharge hole (13) of the oil pump (3) and passing through the lubricating oil hole (9a). Restriction (14) and bolt (9) between lubricating oil conduit (9f)
The oil flows into the transmission through the restriction between the lubricating oil hole (9b) on the head side of the lubricating oil hole (9b) and the plug (9C) fitted in the lubricating oil hole (9b), and the inside of the plug (9c) flows into the transmission. Lubricating oil hole (9e)
A lubricating device for a transmission according to claim 1 or 2, wherein the lubricating oil is discharged to an oil tank through the lubricating oil conduit (9f), and the inflow path and outflow path are separate paths. .
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3555683A JPS5913165A (en) | 1983-03-04 | 1983-03-04 | Lubricating device of speed change gear |
| GB08405425A GB2137708B (en) | 1983-03-01 | 1984-03-01 | Lubrication of a speed-change mechanism |
| US06/585,007 US4573373A (en) | 1983-03-01 | 1984-03-01 | Lubrication system for auxiliary equipment transmission |
| DE19843407613 DE3407613A1 (en) | 1983-03-01 | 1984-03-01 | LUBRICATION SYSTEM FOR A SPEED CHANGE MECHANISM |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3555683A JPS5913165A (en) | 1983-03-04 | 1983-03-04 | Lubricating device of speed change gear |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11950282A Division JPS5913164A (en) | 1982-07-09 | 1982-07-09 | Lubricating oil feeder of gear device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5913165A true JPS5913165A (en) | 1984-01-23 |
Family
ID=12444998
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3555683A Pending JPS5913165A (en) | 1983-03-01 | 1983-03-04 | Lubricating device of speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5913165A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63195469A (en) * | 1987-02-06 | 1988-08-12 | Suzuki Motor Co Ltd | Engine |
| JPH0571529U (en) * | 1991-06-13 | 1993-09-28 | ジャトコ株式会社 | Hydraulic supply for automatic transmission |
| KR20040035260A (en) * | 2002-10-19 | 2004-04-29 | 현대자동차주식회사 | Oil rotation system for power steering and auto transmission |
-
1983
- 1983-03-04 JP JP3555683A patent/JPS5913165A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63195469A (en) * | 1987-02-06 | 1988-08-12 | Suzuki Motor Co Ltd | Engine |
| JPH0571529U (en) * | 1991-06-13 | 1993-09-28 | ジャトコ株式会社 | Hydraulic supply for automatic transmission |
| KR20040035260A (en) * | 2002-10-19 | 2004-04-29 | 현대자동차주식회사 | Oil rotation system for power steering and auto transmission |
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