JPS6363780B2 - - Google Patents
Info
- Publication number
- JPS6363780B2 JPS6363780B2 JP58067539A JP6753983A JPS6363780B2 JP S6363780 B2 JPS6363780 B2 JP S6363780B2 JP 58067539 A JP58067539 A JP 58067539A JP 6753983 A JP6753983 A JP 6753983A JP S6363780 B2 JPS6363780 B2 JP S6363780B2
- Authority
- JP
- Japan
- Prior art keywords
- housing
- input shaft
- planetary gear
- shaft
- carrier
- 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
Links
- 230000007246 mechanism Effects 0.000 claims description 26
- 230000005540 biological transmission Effects 0.000 claims description 10
- 239000003566 sealing material Substances 0.000 description 5
- POIUWJQBRNEFGX-XAMSXPGMSA-N cathelicidin Chemical compound C([C@@H](C(=O)N[C@@H](CCCNC(N)=N)C(=O)N[C@@H](CCCCN)C(=O)N[C@@H](CO)C(=O)N[C@@H](CCCCN)C(=O)N[C@@H](CCC(O)=O)C(=O)N[C@@H](CCCCN)C(=O)N[C@@H]([C@@H](C)CC)C(=O)NCC(=O)N[C@@H](CCCCN)C(=O)N[C@@H](CCC(O)=O)C(=O)N[C@@H](CC=1C=CC=CC=1)C(=O)N[C@@H](CCCCN)C(=O)N[C@@H](CCCNC(N)=N)C(=O)N[C@@H]([C@@H](C)CC)C(=O)N[C@@H](C(C)C)C(=O)N[C@@H](CCC(N)=O)C(=O)N[C@@H](CCCNC(N)=N)C(=O)N[C@@H]([C@@H](C)CC)C(=O)N[C@@H](CCCCN)C(=O)N[C@@H](CC(O)=O)C(=O)N[C@@H](CC=1C=CC=CC=1)C(=O)N[C@@H](CC(C)C)C(=O)N[C@@H](CCCNC(N)=N)C(=O)N[C@@H](CC(N)=O)C(=O)N[C@@H](CC(C)C)C(=O)N[C@@H](C(C)C)C(=O)N1[C@@H](CCC1)C(=O)N[C@@H](CCCNC(N)=N)C(=O)N[C@@H]([C@@H](C)O)C(=O)N[C@@H](CCC(O)=O)C(=O)N[C@@H](CO)C(O)=O)NC(=O)[C@H](CC=1C=CC=CC=1)NC(=O)[C@H](CC(O)=O)NC(=O)CNC(=O)[C@H](CC(C)C)NC(=O)[C@@H](N)CC(C)C)C1=CC=CC=C1 POIUWJQBRNEFGX-XAMSXPGMSA-N 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/06—Endless member is a belt
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pulleys (AREA)
- Control Of Transmission Device (AREA)
Description
【発明の詳細な説明】
本発明は自動変速装置に関し、特に入力側と出
力側との間に、遊星歯車機構、一方向クラツチお
よび遠心クラツチを備え、入力側が低速回転のと
きには入、出力間が直結され、高速回転時には入
力側の回転トルクが減速して出力側に伝わるよう
にした自動変速装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an automatic transmission, and more particularly, it includes a planetary gear mechanism, a one-way clutch, and a centrifugal clutch between an input side and an output side, and when the input side rotates at a low speed, the transmission changes between the input and output sides. The present invention relates to an automatic transmission device that is directly connected to the vehicle and is configured to reduce rotational torque on the input side and transmit it to the output side during high-speed rotation.
従来、かかる自動変速装置では、第３図で示す
ように、入力軸６と、出力部材としてのプーリ７
との間に、遊星歯車機構Gpが介装され、該遊星
歯車機構Gpの内歯歯車４４と固定部材５４との
間に一方向クラツチCoが介装されるとともに、
入力軸６と内歯歯車４４との間に遠心クラツチ
Ccが介装される。また遊星歯車機構Gpの太陽歯
車４５は入力軸６に固定され、遊星歯車４６を保
持するキヤリヤ４７はプーリ７に一体化されてい
る。このような従来の自動変速装置では、入力軸
６の回転数が予め設定した値よりも低いときに
は、遠心クラツチCcにより入力軸６と内歯歯車
４４とが結合され、一方向クラツチCoは内歯歯
車４４の入力軸６と同一方向の回転を許容する。
したがつて、入力軸６とプーリ７とが直結状態と
なり、入力軸６の回転速度がプーリ７にそのまま
伝わることになる。また、入力軸６の回転速度が
前記設定値以上となつたときには、遠心クラツチ
Ccは入力軸６および内歯歯車４４間の結合状態
を解除する。一方、入力軸６から太陽歯車４５お
よび遊星歯車４６を介して、内歯歯車４４には入
力軸６と逆方向の回転トルクを与えられることに
なるので、一方向クラツチCoはその内歯歯車４
４の入力軸６とは逆方向の回転動作を制止して内
歯歯車４４を固定部材５４に結合する。したがつ
て、遊星歯車機構Gpにおいては、静止した内歯
歯車４４に噛合しながら遊星歯車４６が太陽歯車
４５すなわち入力軸６と同一方向に公転移動し、
キヤリア４７を介してプーリ７が減速駆動され
る。 Conventionally, such an automatic transmission has an input shaft 6 and a pulley 7 as an output member, as shown in FIG.
A planetary gear mechanism Gp is interposed between the planetary gear mechanism Gp, and a one-way clutch Co is interposed between the internal gear 44 of the planetary gear mechanism Gp and the fixed member 54,
A centrifugal clutch is provided between the input shaft 6 and the internal gear 44.
Cc is interposed. Further, the sun gear 45 of the planetary gear mechanism Gp is fixed to the input shaft 6, and the carrier 47 holding the planetary gear 46 is integrated with the pulley 7. In such a conventional automatic transmission, when the rotation speed of the input shaft 6 is lower than a preset value, the input shaft 6 and the internal gear 44 are coupled by the centrifugal clutch Cc, and the one-way clutch Co is connected to the internal gear 44. Rotation of the gear 44 in the same direction as the input shaft 6 is allowed.
Therefore, the input shaft 6 and the pulley 7 are directly connected, and the rotational speed of the input shaft 6 is directly transmitted to the pulley 7. Furthermore, when the rotational speed of the input shaft 6 exceeds the set value, the centrifugal clutch is activated.
Cc releases the coupling state between the input shaft 6 and the internal gear 44. On the other hand, since rotational torque in the opposite direction to the input shaft 6 is applied to the internal gear 44 from the input shaft 6 via the sun gear 45 and the planetary gear 46, the one-way clutch Co
The internal gear 44 is coupled to the fixing member 54 by inhibiting rotational movement in the opposite direction to the input shaft 6 of the internal gear 44. Therefore, in the planetary gear mechanism Gp, the planetary gear 46 revolves in the same direction as the sun gear 45, that is, the input shaft 6, while meshing with the stationary internal gear 44,
The pulley 7 is driven to reduce speed via the carrier 47.
ところが、このような従来の自動変速装置で
は、入力軸６の低速運転時に遊星歯車機構Gpの
各歯車４４，４５，４６の噛合部に、プーリ７に
よつて駆動される負荷のトルクが作用している。
特にプーリ７によつて、自動車のパワーステアリ
ング用油圧ポンプを駆動する場合には、エンジン
の低速回転時すなわち入力軸６とプーリ７との直
結時に、その駆動トルクが大きい。また空気調和
装置用コンプレツサをプーリによつて駆動する場
合にはエンジンの低速回転時にトルク変動が大き
く、しかもエンジン自身のトルク変動も大きい。
さらに、歯車には歯車同志の円滑な噛合を得るた
めにバツクラツシが設けられている。このよう
に、入力軸６の低速回転時に、(a)駆動トルクが大
であること、(b)トルク変動が大であること、(c)歯
車にバツクラツシが設けてあること、特に起因し
て、遊星歯車機構Gpにおける各歯車４４，４５，
４６は相互の噛合位置で振動する。したがつて騒
音が発生するとともに、叩かれ摩耗が増大して遊
星歯車機構Gpの耐久性能が低下する。特に、プ
ーリ７によりオン・オフ制御式空気調和装置用コ
ンプレツサ等を駆動している場合において、歯車
のバツクラツシが比較的大きいときには、そのコ
ンプレツサ始動時に加わる衝撃トルクにより、耐
久性能が一層低下する。 However, in such a conventional automatic transmission, when the input shaft 6 is operated at low speed, the torque of the load driven by the pulley 7 acts on the meshing portions of the gears 44, 45, and 46 of the planetary gear mechanism Gp. ing.
In particular, when the pulley 7 drives a hydraulic pump for power steering of an automobile, the driving torque is large when the engine rotates at low speed, that is, when the input shaft 6 and the pulley 7 are directly connected. Furthermore, when a compressor for an air conditioner is driven by a pulley, torque fluctuations are large when the engine rotates at low speed, and the torque fluctuation of the engine itself is also large.
Further, the gears are provided with backlashes to ensure smooth meshing between the gears. In this way, when the input shaft 6 rotates at low speed, (a) the driving torque is large, (b) the torque fluctuation is large, and (c) the gear is provided with backlash, especially due to , each gear 44, 45 in the planetary gear mechanism Gp,
46 vibrate in mutual meshing positions. As a result, noise is generated, and the wear caused by hitting increases, resulting in a decrease in the durability of the planetary gear mechanism Gp. In particular, when the pulley 7 is used to drive an on/off controlled compressor for an air conditioner or the like, when the backlash of the gear is relatively large, the impact torque applied when starting the compressor further deteriorates the durability.
本発明は、そのような従来の技術的課題を解決
すべくなされたものであり、耐久性能を向上する
とともに騒音が発生することを抑制した、構造簡
単な自動変速装置を提供することを目的とし、そ
の特徴は、中空固定軸に第１の軸受を介して回転
自在に支承されたハウジングの外周に出力部が一
体的に設けられ、前記固定軸の中空部を回転自在
に貫通してハウジング内に突入した入力軸の端部
と、前記ハウジングとの間には第２の軸受が介装
され、入力軸およびハウジング間には、入力軸の
低速回転時に入力軸およびハウジングを結合しか
つ入力軸の高速回転時に前記結合状態を解除する
遠心クラツチと、入力軸の回転トルクを減速して
ハウジングに伝える遊星歯車機構とが互いに並列
に介装され、該遊星歯車機構は、前記入力軸に一
体的に回転するよう連結される内歯歯車と、前記
固定軸に固設した太陽歯車と、前記両歯車に噛合
する遊星歯車とを備え、その遊星歯車を軸支する
キヤリヤと前記ハウジングとの間には、キヤリヤ
のハウジングに対する、入力軸と同一方向の相対
回転移動を阻止する一方向クラツチが介装される
ことにある。 The present invention was made to solve such conventional technical problems, and aims to provide an automatic transmission device with a simple structure that improves durability and suppresses noise generation. , the feature is that an output part is integrally provided on the outer periphery of a housing that is rotatably supported on a hollow fixed shaft via a first bearing, and that the output part is rotatably penetrated through the hollow part of the fixed shaft and inserted into the housing. A second bearing is interposed between the end of the input shaft that has entered the input shaft and the housing, and a second bearing is provided between the input shaft and the housing to connect the input shaft and the housing when the input shaft rotates at low speed. A centrifugal clutch that releases the coupling state when the input shaft rotates at high speed, and a planetary gear mechanism that decelerates the rotational torque of the input shaft and transmits it to the housing are interposed in parallel with each other, and the planetary gear mechanism is integrally connected to the input shaft. an internal gear connected to rotate with the fixed shaft, a sun gear fixed to the fixed shaft, and a planetary gear meshing with both the gears, and between a carrier that pivotally supports the planetary gear and the housing. The advantage is that a one-way clutch is interposed to prevent the carrier from rotating relative to the housing in the same direction as the input shaft.
以下、図面により本発明の実施例について説明
すると、先ず本発明装置を自動車の補機駆動用と
してエンジンに装着したときの一実施例を示す第
１図および第２図において、エンジンＥのクラン
ク軸１は、シリンダブロツク２に軸受３およびシ
ール部材４を介して回転自在に支承され、端部を
シリンダブロツク２の外方に突出する。その突出
端部が本発明に従う自動変速装置５の入力軸６と
して機能する。この入力軸６は、外周に出力部と
してのプーリ７を一体的に備えるハウジング８内
に突入されており、入力軸６とハウジング８との
間には遠心クラツチCcが介装される。またハウ
ジング８は固定軸１０に回転自在に支承されてお
り、この固定軸１０と入力軸６の間には遊星歯車
機構Gpが介装され、さらに遊星歯車機構Gpのキ
ヤリヤ４６とハウジング８との間には一方向クラ
ツチCoが介装される。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. First, in FIGS. 1 and 2, which show an embodiment of the present invention when the device of the present invention is mounted on an engine for driving auxiliary equipment of an automobile, a crankshaft of an engine E is shown. 1 is rotatably supported by a cylinder block 2 via a bearing 3 and a seal member 4, and has an end projecting outward from the cylinder block 2. The protruding end portion functions as the input shaft 6 of the automatic transmission 5 according to the present invention. The input shaft 6 is inserted into a housing 8 that is integrally provided with a pulley 7 as an output portion on its outer periphery, and a centrifugal clutch Cc is interposed between the input shaft 6 and the housing 8. Further, the housing 8 is rotatably supported by a fixed shaft 10, and a planetary gear mechanism Gp is interposed between the fixed shaft 10 and the input shaft 6, and the carrier 46 of the planetary gear mechanism Gp and the housing 8 are A one-way clutch Co is interposed between them.
ハウジング８は、入力軸６と同心に配置されそ
の底部に孔１３が同心に穿設された有底円筒部１
４と、有底円筒部１４の開放端にシール材１５を
介して嵌着されるリング状のカバー１６と、シー
ル材１７を介して前記孔１３を閉塞するキヤツプ
１８とから成る。このハウジング８においてカバ
ー１６およびプーリ７はねじ部材１１によつて有
底円筒部１４の開放端部に固着され、プーリ７に
は、パワーステアリング用油圧ポンプや空気調和
装置用コンプレツサなどの補機（図示せず）を駆
動するための無端状ベルト１９が巻回される。 The housing 8 has a bottomed cylindrical part 1 arranged concentrically with the input shaft 6 and having a hole 13 concentrically bored in the bottom thereof.
4, a ring-shaped cover 16 that is fitted onto the open end of the bottomed cylindrical portion 14 via a sealing material 15, and a cap 18 that closes the hole 13 via a sealing material 17. In this housing 8, a cover 16 and a pulley 7 are fixed to the open end of the bottomed cylindrical part 14 by a screw member 11, and the pulley 7 is attached to auxiliary equipment such as a hydraulic pump for power steering or a compressor for an air conditioner. (not shown) is wound around an endless belt 19 for driving the motor.
入力軸６のシリンダブロツク２寄りの部分に
は、キー溝２０が穿設されており、このキー溝２
０に嵌合されるキー２１を介してハウジング８の
外方でタイミングベルトプーリ２２が入力軸６に
固定されるとともに、入力軸６にシール材１２を
介して嵌挿されてハウジング８内に突入する円筒
状回転軸２３が入力軸６に固定される。タイミン
グベルトプーリ２２には無端状タイミングベルト
２４が巻回される。回転軸２３のキヤツプ１８側
の端部は、軸受２５を介してハウジング８の孔１
３の内面で回転自在に支承される。また、回転軸
２３の前記端部から入力軸６にはボルト２６が同
心に螺着されており、このボルト２６には、クラ
ンク軸１および入力軸６内に同心に穿設された通
気孔２７に通なる通気孔２８が穿設されている。
これらの通気孔２７，２８はハウジング８内部
を、エンジンＥのクランク室と同圧にする働きを
する。 A keyway 20 is bored in a portion of the input shaft 6 near the cylinder block 2.
A timing belt pulley 22 is fixed to the input shaft 6 on the outside of the housing 8 through a key 21 that is fitted into the key 21, and is inserted into the input shaft 6 through a sealing material 12 and protrudes into the housing 8. A cylindrical rotating shaft 23 is fixed to the input shaft 6. An endless timing belt 24 is wound around the timing belt pulley 22. The end of the rotating shaft 23 on the cap 18 side is connected to the hole 1 of the housing 8 via the bearing 25.
It is rotatably supported on the inner surface of 3. Further, a bolt 26 is screwed concentrically from the end of the rotating shaft 23 to the input shaft 6, and this bolt 26 has a ventilation hole 27 formed concentrically in the crankshaft 1 and the input shaft 6. A ventilation hole 28 is bored through the hole.
These vent holes 27 and 28 function to make the inside of the housing 8 at the same pressure as the crank chamber of the engine E.
固定軸１０は、回転軸２３を外囲する円筒状に
形成されており、固定軸１０および回転軸２３間
には軸受２９および潤滑油の流出を防ぐシール材
３０が介装される。この固定軸１０には、シリン
ダブロツク２側に延びる支持腕３１が一体的に設
けられており、この支持腕３１の端部に設けられ
た弾性材３２には、シリンダブロツク２に植設し
たピン３３が挿通される。したがつて、第１固定
軸１０はその軸線まわりの回転動作を阻止されて
いる。固定軸１０の外周面と、ハウジング８にお
けるカバー１６の内周縁との間には、軸受３４お
よびシール材３５が介装される。 The fixed shaft 10 is formed in a cylindrical shape surrounding the rotating shaft 23, and a bearing 29 and a sealing material 30 for preventing leakage of lubricating oil are interposed between the fixed shaft 10 and the rotating shaft 23. A support arm 31 extending toward the cylinder block 2 is integrally provided on the fixed shaft 10, and an elastic member 32 provided at the end of the support arm 31 has a pin implanted in the cylinder block 2. 33 is inserted. Therefore, the first fixed shaft 10 is prevented from rotating about its axis. A bearing 34 and a sealing material 35 are interposed between the outer peripheral surface of the fixed shaft 10 and the inner peripheral edge of the cover 16 in the housing 8 .
ハウジング８における有底円筒部１４の底部寄
りで、回転軸２３には半径方向に延びる円板状の
フランジ部３６が一体的に設けられており、この
フランジ部３６の外周端には、フランジ部３６の
軸方向両側に延びる円筒部３７が一体的に設けら
れる。 A radially extending disk-shaped flange portion 36 is integrally provided on the rotating shaft 23 near the bottom of the bottomed cylindrical portion 14 in the housing 8 . A cylindrical portion 37 extending on both sides of 36 in the axial direction is integrally provided.
遠心クラツチCcは、有底円筒部１４の底部側
でフランジ部３６の半径方向に沿つて移動自在の
複数の重錘３８と、重錘３８および円筒部３７間
にそれぞれ介装される複数のばね３９と、フラン
ジ部３６の半径方向に沿つて各重錘３８の内方端
にそれぞれ貼設された摩擦シユー４０と、ハウジ
ング８における有底円筒部１４の孔１３の周囲に
一体的に設けられた前記各摩擦シユー４０が摩擦
係合可能なドラム４１とを含む。各重錘３８に
は、フランジ部３６の半径方向に沿つて延びる長
孔４２が穿設されており、各長孔４２にはフラン
ジ部３６に植設されたピン４３が係合される。し
たがつて、各重錘３８はフランジ部３６の面に沿
つて半径方向に摺動自在に、フランジ部３６に支
承されている。 The centrifugal clutch Cc includes a plurality of weights 38 that are movable along the radial direction of the flange portion 36 on the bottom side of the bottomed cylindrical portion 14, and a plurality of springs interposed between the weights 38 and the cylindrical portion 37, respectively. 39, a friction shoe 40 attached to the inner end of each weight 38 along the radial direction of the flange portion 36, and a friction shoe 40 provided integrally around the hole 13 of the bottomed cylindrical portion 14 in the housing 8. Each of the friction shoes 40 includes a drum 41 that can be frictionally engaged. Each weight 38 has a long hole 42 extending along the radial direction of the flange portion 36, and a pin 43 implanted in the flange portion 36 is engaged with each long hole 42. Therefore, each weight 38 is supported by the flange portion 36 so as to be slidable in the radial direction along the surface of the flange portion 36.
このような遠心クラツチCcでは、各重錘３８
がばね３９のばね力によりフランジ部３６の半径
方向内方、すなわち各摩擦シユー４０がドラム４
１に摩擦係合する方向に付勢されている。したが
つて、フランジ部３６の回転速度すなわち入力軸
６の回転速度に対応して各重錘３８に作用する遠
心力が、ばね３９のばね力よりも弱いときには、
各摩擦シユー４０がドラム４１に摩擦係合する。
その結果、ハウジング８と、入力軸６とが遠心ク
ラツチCcを介して直接結合されることになる。
ところが、入力軸６の回転速度が大になり、各重
錘３８に作用する遠心力がばね３９のばね力より
も大になると、各摩擦シユー４０はドラム４１か
ら離反し、入力軸６から遠心クラツチCcを介し
てのハウジング８へのトルクの伝達は行なわれな
くなる。 In such a centrifugal clutch Cc, each weight 38
Due to the spring force of the spring 39, the radially inward portion of the flange portion 36, that is, each friction shoe 40 is moved against the drum 4.
1 in the direction of frictional engagement. Therefore, when the centrifugal force acting on each weight 38 corresponding to the rotational speed of the flange portion 36, that is, the rotational speed of the input shaft 6, is weaker than the spring force of the spring 39,
Each friction shoe 40 frictionally engages a drum 41.
As a result, the housing 8 and the input shaft 6 are directly coupled via the centrifugal clutch Cc.
However, when the rotational speed of the input shaft 6 increases and the centrifugal force acting on each weight 38 becomes greater than the spring force of the spring 39, each friction shoe 40 separates from the drum 41, and the centrifugal force acts on each weight 38. Torque is no longer transmitted to the housing 8 via the clutch Cc.
遊星歯車機構Gpは、内歯歯車４４と、太陽歯
車４５と、両歯車４４，４５に噛合すべく周方向
に間隔をあけて配設された複数の遊星歯車４６
と、各遊星歯車４６を保持するキヤリヤ４７とか
ら成る。内歯歯車４４は、前記円筒部３７のエン
ジンＥ寄りの端部に設けられる。また太陽歯車４
５は固定軸１０の端部に設けられる。キヤリヤ４
７は、遊星歯車４６を回転自在に軸支する軸５１
と、その軸５１が支持される支持板５０とから成
り、支持板５０とハウジング８との間には一方向
クラツチCoが介装される。この一方向クラツチ
Coは、ハウジング８に対してキヤリヤ４７の入
力軸６と同一方向の相対回転移動を阻止する。し
たがつて、ハウジング８に回転トルクが与えられ
ていないときにキヤリヤ４７に前記入力軸６と同
一方向の回転トルクが与えられると、ハウジング
８とキヤリヤ４７とは一方向クラツチCoによつ
て結合される。それとは逆に、ハウジング８の入
力軸６と同一方向の回転速度が、キヤリヤ４７の
回転速度と同一あるいは高いときには、一方向ク
ラツチCoによるハウジング８とキヤリヤ４７と
の結合状態は解除される。 The planetary gear mechanism Gp includes an internal gear 44, a sun gear 45, and a plurality of planetary gears 46 disposed at intervals in the circumferential direction so as to mesh with both gears 44 and 45.
and a carrier 47 that holds each planetary gear 46. The internal gear 44 is provided at the end of the cylindrical portion 37 closer to the engine E. Also sun gear 4
5 is provided at the end of the fixed shaft 10. carrier 4
7 is a shaft 51 that rotatably supports the planetary gear 46;
and a support plate 50 on which the shaft 51 is supported, and a one-way clutch Co is interposed between the support plate 50 and the housing 8. This one-way clutch
Co prevents relative rotational movement of the carrier 47 in the same direction as the input shaft 6 with respect to the housing 8 . Therefore, when rotational torque is applied to the carrier 47 in the same direction as the input shaft 6 while no rotational torque is applied to the housing 8, the housing 8 and the carrier 47 are coupled by the one-way clutch Co. Ru. On the contrary, when the rotational speed of the housing 8 in the same direction as the input shaft 6 is the same as or higher than the rotational speed of the carrier 47, the connection between the housing 8 and the carrier 47 by the one-way clutch Co is released.
次にこの実施例の作用について説明すると、エ
ンジンＥのクランク軸１すなわち入力軸６の回転
速度が遅いときには、遠心クラツチCcを介して
入力軸６およびハウジング８は直結されており、
入力軸６の回転トルクは、遠心クラツチCc、ハ
ウジング８およびプーリ７からベルト１９を介し
て補機に伝えられる。この際、遊星歯車機構Gp
においては、内歯歯車４４から遊星歯車４６を介
してキヤリヤ４７に、入力軸６と同一方向の回転
トルクが与えられるが、ハウジング８は入力軸６
と同一方向に回転しているので、一方向クラツチ
Coはハウジング８およびキヤリヤ４７を結合し
ない。したがつて遊星歯車機構Gpに負荷トルク
は作用せず、内歯歯車４４、遊星歯車４６および
太陽歯車４５のバツクラツシが比較的大きかつた
としても、各歯車４４，４５，４６の噛合部に負
荷トルクによる振動が生じることはない。その結
果、騒音が生じることが防止されるとともに、叩
かれ摩耗が生じることもなく、さらに衝撃トルク
があつてとしても、各歯車４４，４５，４６の耐
久性能が低下することもない。 Next, the operation of this embodiment will be explained. When the rotational speed of the crankshaft 1 of the engine E, that is, the input shaft 6 is slow, the input shaft 6 and the housing 8 are directly connected via the centrifugal clutch Cc.
The rotational torque of the input shaft 6 is transmitted from the centrifugal clutch Cc, the housing 8 and the pulley 7 to the auxiliary equipment via the belt 19. At this time, the planetary gear mechanism Gp
, rotational torque in the same direction as the input shaft 6 is applied from the internal gear 44 to the carrier 47 via the planetary gear 46, but the housing 8 is
is rotating in the same direction as the one-way clutch.
Co does not connect housing 8 and carrier 47. Therefore, no load torque acts on the planetary gear mechanism Gp, and even if the backlash of the internal gear 44, planetary gear 46, and sun gear 45 is relatively large, no load is applied to the meshing portions of the gears 44, 45, and 46. No vibrations occur due to torque. As a result, noise is prevented from being generated, and wear due to knocking does not occur, and even if impact torque is applied, the durability of the gears 44, 45, and 46 does not deteriorate.
次に入力軸６の回転速度が大となり、遠心クラ
ツチCcによる入力軸６とハウジング８との直結
状態が解除されると、遊星歯車機構Gpにおいて
は、内歯歯車４４から遊星歯車４６を介してキヤ
リヤ４７に入力軸６と同一方向の回転トルクが与
えられるのに対し、ハウジング８にはそのような
回転トルクが与えられていない。したがつて一方
向クラツチCoの働きにより、キヤリヤ４７およ
びハウジング８は結合され、入力軸６の回転トル
クが遊星歯車機構Gpに固有の減速比をもつてハ
ウジング８すなわちプーリ７に伝達されることに
なり、補機に必要以上の回転速度で駆動力が与え
られることはない。 Next, when the rotational speed of the input shaft 6 becomes high and the direct connection between the input shaft 6 and the housing 8 by the centrifugal clutch Cc is released, in the planetary gear mechanism Gp, While the carrier 47 is given a rotational torque in the same direction as the input shaft 6, the housing 8 is not given such a rotational torque. Therefore, by the action of the one-way clutch Co, the carrier 47 and the housing 8 are coupled, and the rotational torque of the input shaft 6 is transmitted to the housing 8, that is, the pulley 7, with a reduction ratio specific to the planetary gear mechanism Gp. Therefore, driving force is not applied to the auxiliary equipment at a rotation speed higher than necessary.
以上のように本発明によれば、中空固定軸に第
１の軸受を介して回転自在に支承されたハウジン
グの外周に出力部が一体的に設けられ、前記固定
軸の中空部を回転自在に貫通してハウジング内に
突入した入力軸の端部と、前記ハウジングとの間
には第２の軸受が介装され、入力軸およびハウジ
ング間には、入力軸の低速回転時に入力軸および
ハウジングを結合しかつ入力軸の高速回転時に前
記結合状態を解除する遠心クラツチと、入力軸の
回転トルクを減速してハウジングに伝える遊星歯
車機構とが互いに並列に介装され、該遊星歯車機
構は、前記入力軸に一体的に回転するよう連結さ
れる内歯歯車と、前記固定軸に固設した太陽歯車
と、前記両歯車に噛合する遊星歯車とを備え、そ
の遊星歯車を軸支するキヤリヤと前記ハウジング
との間には、キヤリヤのハウジングに対する、入
力軸と同一方向の相対回転移動を阻止する一方向
クラツチが介装されるので、入力軸を駆動するエ
ンジンの低速回転時には、入力軸とハウジング間
が遠心クラツチを介して直結されて、遊星歯車機
構の各歯車の噛合部に負荷トルクが作用しなくな
り、その結果、エンジンの上記低速回転時に大き
くなるトルク変動等によつても各歯車の噛合部に
振動が生じる惧れはなく、その噛合部に叩かれ摩
耗が生じることが防止されて遊星歯車機構の耐久
性能が向上するとともに、騒音の発生が防止され
る。また一方向クラツチは遊星歯車機構のキヤリ
ヤとハウジングとの間に介装されるので、比較的
大型に形成できて大きなトルクを伝達することが
可能であり、しかもその遊星キヤリヤを一方向ク
ラツチのクラツチ要素に兼用させることができて
構造の簡単化に寄与し得る。 As described above, according to the present invention, the output portion is integrally provided on the outer periphery of the housing rotatably supported by the hollow fixed shaft via the first bearing, and the output portion is provided rotatably in the hollow portion of the fixed shaft. A second bearing is interposed between the end of the input shaft that penetrates into the housing and the housing, and a second bearing is provided between the input shaft and the housing to prevent the input shaft and the housing from rotating at low speeds. A centrifugal clutch that connects and releases the connected state when the input shaft rotates at high speed, and a planetary gear mechanism that decelerates the rotational torque of the input shaft and transmits it to the housing are interposed in parallel with each other, and the planetary gear mechanism an internal gear connected to the input shaft so as to integrally rotate; a sun gear fixed to the fixed shaft; and a planetary gear meshing with both the gears; A one-way clutch is installed between the carrier and the housing to prevent relative rotational movement in the same direction as the input shaft. are directly connected via the centrifugal clutch, so that no load torque acts on the meshing parts of each gear of the planetary gear mechanism, and as a result, the meshing parts of each gear are There is no risk of vibration occurring, and the meshing portions are prevented from being hit and worn, improving the durability of the planetary gear mechanism and preventing the generation of noise. Furthermore, since the one-way clutch is interposed between the carrier of the planetary gear mechanism and the housing, it can be made relatively large and can transmit large torque. It can also be used as an element, contributing to the simplification of the structure.
第１図および第２図は本発明の第１実施例を示
すもので、第１図は構造を具体的に示す縦断面
図、第２図はその概要図、第３図は従来の構成を
示す概要図である。
５…自動変速装置、６…入力軸、７…出力部と
してのプーリ、８…ハウジング、１０…固定軸、
４４…内歯歯車、４５…太陽歯車、４６…遊星歯
車、４７…キヤリア、Cc…遠心クラツチ、Co…
一方向クラツチ、Gp…遊星歯車機構。
Figures 1 and 2 show a first embodiment of the present invention, with Figure 1 being a vertical sectional view specifically showing the structure, Figure 2 being a schematic diagram thereof, and Figure 3 showing the conventional configuration. FIG. 5... Automatic transmission, 6... Input shaft, 7... Pulley as output section, 8... Housing, 10... Fixed shaft,
44... Internal gear, 45... Sun gear, 46... Planetary gear, 47... Carrier, Cc... Centrifugal clutch, Co...
One-way clutch, Gp...planetary gear mechanism.
Claims (1)
転自在に支承されたハウジング８の外周に出力部
７が一体的に設けられ、前記固定軸１０の中空部
を回転自在に貫通してハウジング８内に突入した
入力軸６の端部と、前記ハウジング８との間には
第２の軸受２５が介装され、入力軸６およびハウ
ジング８間には、入力軸６の低速回転時に入力軸
６およびハウジング８を結合しかつ入力軸６の高
速回転時に前記結合状態を解除する遠心クラツチ
Ccと、入力軸６の回転トルクを減速してハウジ
ング８に伝える遊星歯車機構Gpとが互いに並列
に介装され、該遊星歯車機構Gpは、前記入力軸
６に一体的に回転するよう連結される内歯歯車４
４と、前記固定軸１０に固設した太陽歯車４５
と、前記両歯車４４，４５に噛合する遊星歯車４
６とを備え、その遊星歯車４６を軸支するキヤリ
ヤ４７と前記ハウジング８との間には、キヤリヤ
４７のハウジング８に対する、入力軸６と同一方
向の相対回転移動を阻止する一方向クラツチCo
が介装されることを特徴とする、自動変速装置。1. An output part 7 is integrally provided on the outer periphery of a housing 8 which is rotatably supported by a hollow fixed shaft 10 via a first bearing 34, and is rotatably penetrated through the hollow part of the fixed shaft 10 to form a housing. A second bearing 25 is interposed between the end of the input shaft 6 protruding into the housing 8 and the housing 8. a centrifugal clutch that connects the input shaft 6 and the housing 8 and releases the connected state when the input shaft 6 rotates at high speed;
Cc and a planetary gear mechanism Gp that decelerates the rotational torque of the input shaft 6 and transmits it to the housing 8 are interposed in parallel with each other, and the planetary gear mechanism Gp is connected to the input shaft 6 so as to rotate integrally therewith. Internal gear 4
4, and a sun gear 45 fixedly attached to the fixed shaft 10.
and a planetary gear 4 that meshes with both gears 44 and 45.
A one-way clutch Co is provided between the carrier 47 which pivotally supports the planetary gear 46 and the housing 8, and which prevents relative rotational movement of the carrier 47 with respect to the housing 8 in the same direction as the input shaft 6.
An automatic transmission device characterized by being equipped with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6753983A JPS59194153A (en) | 1983-04-15 | 1983-04-15 | Automatic speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6753983A JPS59194153A (en) | 1983-04-15 | 1983-04-15 | Automatic speed change gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59194153A JPS59194153A (en) | 1984-11-02 |
| JPS6363780B2 true JPS6363780B2 (en) | 1988-12-08 |
Family
ID=13347875
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6753983A Granted JPS59194153A (en) | 1983-04-15 | 1983-04-15 | Automatic speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59194153A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3119567B2 (en) * | 1995-01-13 | 2000-12-25 | 日本電気株式会社 | Semiconductor measurement method |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61228162A (en) * | 1985-04-01 | 1986-10-11 | Mitsubishi Electric Corp | Driving device of auxiliary machine for engine |
| US5113296A (en) * | 1988-11-07 | 1992-05-12 | Hitachi, Ltd. | Mechanism for winding a tape from a tape cassette onto a rotatable cylinder of a VCR |
| FR2701746B1 (en) * | 1993-02-18 | 1995-05-19 | Roumen Antonov | Transmission with soft start device, in particular for vehicle. |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5025965A (en) * | 1973-07-11 | 1975-03-18 | ||
| JPS5715142A (en) * | 1980-06-23 | 1982-01-26 | Citroen Sa | Driving device for attachment of automobile |
-
1983
- 1983-04-15 JP JP6753983A patent/JPS59194153A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5025965A (en) * | 1973-07-11 | 1975-03-18 | ||
| JPS5715142A (en) * | 1980-06-23 | 1982-01-26 | Citroen Sa | Driving device for attachment of automobile |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3119567B2 (en) * | 1995-01-13 | 2000-12-25 | 日本電気株式会社 | Semiconductor measurement method |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59194153A (en) | 1984-11-02 |
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