JP2017133524A - Reduction gear - Google Patents
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- JP2017133524A JP2017133524A JP2016011293A JP2016011293A JP2017133524A JP 2017133524 A JP2017133524 A JP 2017133524A JP 2016011293 A JP2016011293 A JP 2016011293A JP 2016011293 A JP2016011293 A JP 2016011293A JP 2017133524 A JP2017133524 A JP 2017133524A
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Abstract
Description
本発明は、遊星歯車機構を備える減速機に関し、詳しくは、遊星軸と遊星歯車との間に設けられている軸受に潤滑油を補給する構造を有する減速機に関する。 The present invention relates to a reduction gear provided with a planetary gear mechanism, and more particularly to a reduction gear having a structure for supplying lubricating oil to a bearing provided between a planetary shaft and a planetary gear.
この種の減速機における遊星歯車機構は、複数の遊星歯車が夫々太陽歯車と噛み合って自転運動を行うと共に、各遊星歯車を回転自在に支承するキャリアが回転することで公転運動を行う様に構成される。 The planetary gear mechanism in this type of reduction gear is configured such that a plurality of planetary gears mesh with the sun gears to rotate, and revolve when the carrier that rotatably supports each planetary gear rotates. Is done.
キャリアは、遊星軸を介して遊星歯車を回転自在に支持している。遊星軸と遊星歯車との間には、軸受が介在されている。この軸受には、遊星歯車の自転運動に伴う回転トルクが付与される。このため、遊星歯車を支持する軸受けと遊星軸との間の潤滑が十分に得られていない場合には、焼付け等が発生して円滑な遊星歯車の回転が行われなくなるおそれがある。 The carrier rotatably supports the planetary gear via the planetary shaft. A bearing is interposed between the planetary shaft and the planetary gear. A rotational torque accompanying the rotation of the planetary gear is applied to the bearing. For this reason, when the lubrication between the bearing that supports the planetary gear and the planetary shaft is not sufficiently obtained, seizure or the like may occur, and smooth planetary gear rotation may not be performed.
例えば、建設機械の旋回装置等に採用される減速機においては、潤滑油が充填されたケーシングに遊星歯車機構が収容されている。これによって、遊星歯車と遊星軸との間の軸受けや遊星軸は、常に潤滑油に浸漬された状態で作動される。 For example, in a reduction gear employed in a turning device of a construction machine or the like, a planetary gear mechanism is accommodated in a casing filled with lubricating oil. As a result, the bearing between the planetary gear and the planetary shaft and the planetary shaft are always operated while being immersed in the lubricating oil.
そして更に、遊星軸の内部に油路を形成することで、遊星軸から軸受への潤滑油の供給を行うようにしたものが知られている（特許文献１参照）。遊星軸の内部に形成されている油路は、遊星軸の軸線に沿って延びて上端で上向きに開口する縦孔と、縦孔の下端から遊星軸の軸線に直交する方向に延びて外方端が軸受に連通する横孔とによって構成される。これによれば、ケーシングに充填されている潤滑油が縦孔の開口から油路に入り、横孔を経て軸受に供給される。 Further, there has been known one in which lubricating oil is supplied from the planetary shaft to the bearing by forming an oil passage inside the planetary shaft (see Patent Document 1). The oil passage formed inside the planetary shaft extends along the axis of the planetary shaft and opens upward at the upper end, and extends outward from the lower end of the vertical hole in a direction perpendicular to the axis of the planetary shaft. The end is constituted by a lateral hole communicating with the bearing. According to this, the lubricating oil filled in the casing enters the oil passage from the opening of the vertical hole, and is supplied to the bearing through the horizontal hole.
しかし、遊星軸の縦孔は、キャリアの回転方向、即ち、遊星歯車の公転方向に対して垂直な方向に配置された構成となっているため、キャリアの回転が停止しているときには重力の作用によって周囲にある潤滑油が縦孔内に入り込むものの、キャリアが回転しているときには潤滑油が縦孔内に送り込まれることは期待できない。このため、遊星歯車が回転中の軸受には十分な量の潤滑油が供給されないおそれがある。 However, since the vertical hole of the planetary shaft is arranged in a direction perpendicular to the rotation direction of the carrier, that is, the revolution direction of the planetary gear, the action of gravity is applied when the rotation of the carrier is stopped. Although the surrounding lubricating oil enters the vertical hole, the lubricating oil cannot be expected to be fed into the vertical hole when the carrier is rotating. For this reason, there is a possibility that a sufficient amount of lubricating oil may not be supplied to the bearing in which the planetary gear is rotating.
そこで、このような油浴潤滑が採用されている遊星歯車機構において、遊星軸の縦孔に連通して潤滑油を取り込む油取り込み口を、キャリアの回転方向を向いた開口として形成することにより、油路への潤滑油の供給を強制的に行うようにしたものが提案されている（特許文献２参照）。 Therefore, in the planetary gear mechanism in which such oil bath lubrication is adopted, by forming an oil intake port that communicates with the vertical hole of the planetary shaft and takes in the lubricant as an opening facing the rotation direction of the carrier, There has been proposed one forcibly supplying lubricating oil to the oil passage (see Patent Document 2).
しかし、特許文献２における構成を採用したとき、キャリアの正転方向に向けて油取り込み口を開口させたとき、キャリアが正転したときには、油路内への潤滑油の取り込みがキャリアの回転に伴って強制的に行われるが、キャリアが逆転したときには、油路内に潤滑油を取り込むことは殆どできず、軸受の潤滑が不十分になる不都合がある。 However, when the configuration in Patent Document 2 is adopted, when the oil intake port is opened in the forward rotation direction of the carrier, and when the carrier rotates forward, the intake of the lubricating oil into the oil passage becomes the rotation of the carrier. However, when the carrier is reversed, the lubricating oil can hardly be taken into the oil passage, and there is a disadvantage that the lubrication of the bearing becomes insufficient.
上記の点に鑑み、本発明は、潤滑油に浸漬された遊星歯車機構における遊星軸と遊星歯車と遊星軸との間の軸受に潤滑油を強制的に供給することにより遊星歯車の円滑な回転を得ることができる減速機を提供することを目的とする。 In view of the above points, the present invention provides a smooth rotation of the planetary gear by forcibly supplying the lubricant to the planetary shaft in the planetary gear mechanism immersed in the lubricant and the bearing between the planetary gear and the planetary shaft. An object of the present invention is to provide a reduction gear capable of obtaining the following.
かかる目的を達成するために、本発明は、潤滑油が充填されたケーシングに遊星歯車機構が収容され、該遊星歯車機構のキャリアに設けられた遊星軸に軸受を介して遊星歯車が支持されてなる減速機であって、前記潤滑油を前記遊星軸を介して前記軸受に補給する補給油路を備えるものにおいて、前記補給油路は、前記遊星軸の軸線に沿って形成された軸部流路と、前記ケーシング内の潤滑油を前記軸部流路の上流端に案内する上流案内部と、前記軸部流路内の潤滑油を該軸部流路の下流端から前記軸受に案内する下流案内部とを備え、前記上流案内部は、前記軸部流路から前記キャリアの回転中心に向かって延設され、前記下流案内部は、前記軸部流路から前記キャリアの径方向外側に向かって延設されていることを特徴とする。 In order to achieve such an object, according to the present invention, a planetary gear mechanism is accommodated in a casing filled with lubricating oil, and the planetary gear is supported via a bearing on a planetary shaft provided on a carrier of the planetary gear mechanism. A reduction gear comprising a supply oil path for supplying the lubricating oil to the bearing via the planetary shaft, wherein the supply oil path is an axial flow formed along the axis of the planetary axis. A passage, an upstream guide for guiding the lubricating oil in the casing to the upstream end of the shaft passage, and the lubricating oil in the shaft passage from the downstream end of the shaft passage to the bearing. A downstream guide portion, wherein the upstream guide portion extends from the shaft passage toward the rotation center of the carrier, and the downstream guide portion extends radially outward from the shaft passage. It is characterized by being extended toward.
本発明によれば、前記上流案内部が前記軸部流路から前記キャリアの回転中心に向かって延設されているので、上流案内部内の潤滑油は、キャリアが回転したときの遠心力により軸部流路の上流端に向かって流動して前記軸部流路に入り込む。更に、前記下流案内部は、前記軸部流路から前記キャリアの径方向外側に向かって延設されているので、前記軸部流路に入り込んだ潤滑油は、キャリアが回転したときの遠心力により、軸受に供給される。このように、上流案内部及び下流案内部は、何れも、キャリアが回転したときに遠心力が生じる方向に沿って形成されているので、キャリアの回転方向が正転か逆転かに影響を受けることなく、潤滑油を強制的に軸受に供給することができる。よって、軸受の潤滑が十分に行われ、遊星歯車の円滑な回転を得ることができる。 According to the present invention, since the upstream guide portion extends from the shaft passage toward the center of rotation of the carrier, the lubricating oil in the upstream guide portion is shafted by centrifugal force when the carrier rotates. It flows toward the upstream end of the partial flow path and enters the shaft flow path. Further, since the downstream guide portion extends from the shaft portion flow path toward the outside in the radial direction of the carrier, the lubricating oil that has entered the shaft portion flow passage is centrifugal force when the carrier rotates. Is supplied to the bearing. As described above, since both the upstream guide portion and the downstream guide portion are formed along the direction in which the centrifugal force is generated when the carrier rotates, the rotation direction of the carrier is affected by whether it is forward rotation or reverse rotation. Without this, the lubricating oil can be forcibly supplied to the bearing. Therefore, the bearing is sufficiently lubricated and the planetary gear can be smoothly rotated.
また、本発明において、前記補給油路の前記上流案内部が、前記キャリア及び前記遊星軸の外側面に形成された溝状の流路によって構成されたものを態様の一つとして挙げることができる。 Further, in the present invention, the upstream guide portion of the replenishing oil passage may be configured by a groove-like flow path formed on the outer surface of the carrier and the planetary shaft. .
これによれば、キャリアの回転が停止した状態でも溝状の開放側から上流案内部の内部に潤滑油が充填された状態となり、殆ど抵抗なく潤滑油を上流案内部に取り込むことができるので、潤滑油を円滑に軸受に供給することができる。しかも、上流案内部がキャリア及び遊星軸に溝状の流路として設けられるので、キャリア及び遊星軸を軽量化することができる。更に、キャリア及び遊星軸の外側露出面を溝状に加工して上流案内部を形成することができるので、製造容易であり、上流案内部を設けることによるコストの増加を抑えることができる。 According to this, even when the rotation of the carrier is stopped, the lubricating oil is filled from the groove-shaped opening side into the upstream guiding portion, and the lubricating oil can be taken into the upstream guiding portion with almost no resistance. Lubricating oil can be smoothly supplied to the bearing. In addition, since the upstream guide portion is provided as a groove-like flow path in the carrier and the planetary shaft, the carrier and the planetary shaft can be reduced in weight. Further, since the upstream guide portion can be formed by processing the outer exposed surfaces of the carrier and the planetary shaft into a groove shape, it is easy to manufacture, and an increase in cost due to the provision of the upstream guide portion can be suppressed.
また、本発明において、前記補給油路の前記上流案内部は、前記キャリアに形成された孔状の流路によって構成されていてもよい。 Moreover, in this invention, the said upstream guide part of the said replenishment oil path may be comprised by the hole-shaped flow path formed in the said carrier.
これによれば、上流案内部を溝状に形成した場合に比べ、上流案内部を流動する潤滑油のの抵抗は多少大きくなるが、溝状の上流案内部の全長にわたる開放側からの潤滑油の逃げがなく、上流案内部に取り込まれた潤滑油を確実に軸受に供給することができる。しかも、上流案内部が孔状であることによりキャリア及び遊星軸を軽量化することができる。 According to this, although the resistance of the lubricating oil flowing in the upstream guide portion is somewhat larger than when the upstream guide portion is formed in a groove shape, the lubricating oil from the open side over the entire length of the groove-shaped upstream guide portion The lubricating oil taken into the upstream guide portion can be reliably supplied to the bearing. In addition, the carrier and the planetary shaft can be reduced in weight because the upstream guide portion has a hole shape.
本発明の一実施形態を図面に基づいて説明する。本実施形態の減速機１は、建設機械の旋回装置に用いられ、図１に示すように、ケーシング２と、上段に位置する第１減速機構部３と、下段に位置する第２減速機構部４とによって構成された遊星歯車機構５を備えている。第１減速機構部３と第２減速機構部４とは潤滑油が充填されたケーシング２の内部に収容されている。 An embodiment of the present invention will be described with reference to the drawings. The speed reducer 1 of this embodiment is used for a turning device of a construction machine. As shown in FIG. 1, as shown in FIG. 1, a casing 2, a first speed reduction mechanism portion 3 positioned at an upper stage, and a second speed reduction mechanism section positioned at a lower stage. 4 is provided. The first reduction mechanism 3 and the second reduction mechanism 4 are accommodated in the casing 2 filled with lubricating oil.
第１減速機構部３は、第１キャリア６と、複数（本実施形態では３つ）の第１遊星歯車７と、第１太陽歯車８とを備えている。第１遊星歯車７は、第１キャリア６が備える第１遊星軸９に軸受１０を介して回転自在に支持されている。 The first speed reduction mechanism unit 3 includes a first carrier 6, a plurality (three in this embodiment) of first planetary gears 7, and a first sun gear 8. The first planetary gear 7 is rotatably supported by a first planetary shaft 9 provided in the first carrier 6 via a bearing 10.
第１太陽歯車８は各第１遊星軸９に内側から噛み合う。第１キャリア６は、第１太陽歯車８と同一軸線回りに回転する。 The first sun gear 8 meshes with each first planetary shaft 9 from the inside. The first carrier 6 rotates about the same axis as the first sun gear 8.
第２減速機構部４は、第２キャリア１１と、複数（本実施形態では４つ）の第２遊星歯車１２と、第２太陽歯車１３とを備えている。第２遊星歯車１２は、第２キャリア１１が備える第２遊星軸１４に軸受１５を介して回転自在に支持されている。 The second speed reduction mechanism unit 4 includes a second carrier 11, a plurality (four in this embodiment) of second planetary gears 12, and a second sun gear 13. The second planetary gear 12 is rotatably supported by a second planetary shaft 14 provided in the second carrier 11 via a bearing 15.
第２太陽歯車１３は各第２遊星軸１４に内側から噛み合う。第２キャリア１１は、第２太陽歯車１３と同一軸線回りに回転する。 The second sun gear 13 meshes with each second planetary shaft 14 from the inside. The second carrier 11 rotates about the same axis as the second sun gear 13.
第１遊星歯車７と第２遊星歯車１２とは、その外側が内歯車１６に噛み合っている。内歯車１６は、ケーシング２の内面に設けられて回転が固定されている。 The outer sides of the first planetary gear 7 and the second planetary gear 12 mesh with the internal gear 16. The internal gear 16 is provided on the inner surface of the casing 2 and its rotation is fixed.
第２太陽歯車１３は第１キャリア６の内歯に噛み合っている。また、第２キャリア１１は出力軸１７とスプライン係合されている。第２太陽歯車１３は図外のモータにより回転駆動される。 The second sun gear 13 meshes with the internal teeth of the first carrier 6. Further, the second carrier 11 is spline-engaged with the output shaft 17. The second sun gear 13 is driven to rotate by a motor (not shown).
以上の構成による減速機１は、次のように作動する。即ち、モータの駆動により第１太陽歯車８が回転すると、第１太陽歯車８に噛み合っている第１遊星歯車７が回転する。第１遊星歯車７は回転が固定された内歯車１６と噛み合っているため、第１遊星歯車７が回転すると、その反力により第１キャリア６が回転する。 The speed reducer 1 having the above configuration operates as follows. That is, when the first sun gear 8 is rotated by driving the motor, the first planetary gear 7 meshed with the first sun gear 8 is rotated. Since the first planetary gear 7 meshes with the internal gear 16 whose rotation is fixed, when the first planetary gear 7 rotates, the first carrier 6 rotates due to the reaction force.
第１キャリア６が回転すると、第１キャリア６に噛み合っている第２太陽歯車１３が回転する。そして、第２太陽歯車１３が回転することにより、第２遊星歯車１２が回転する。 When the first carrier 6 rotates, the second sun gear 13 meshing with the first carrier 6 rotates. Then, as the second sun gear 13 rotates, the second planetary gear 12 rotates.
これに伴い、第２キャリア１１が回転し、第２キャリア１１とスプライン係合された出力軸１７が回転する。 Accordingly, the second carrier 11 rotates, and the output shaft 17 that is spline-engaged with the second carrier 11 rotates.
ところで、上記のように第１遊星歯車７及び第２遊星歯車１２が回転するとき、各軸受１０，１５に対して十分な量の潤滑油を供給する必要がある。 By the way, when the first planetary gear 7 and the second planetary gear 12 rotate as described above, it is necessary to supply a sufficient amount of lubricating oil to the bearings 10 and 15.
そこで、本実施形態の減速機１における遊星歯車機構５は、図２に示すように、各遊星軸９，１４を介して夫々の軸受１０，１５に潤滑油を補給する補給油路１８，１９を備えている。 Therefore, the planetary gear mechanism 5 in the speed reducer 1 of the present embodiment is, as shown in FIG. 2, supply oil passages 18 and 19 for supplying lubricating oil to the respective bearings 10 and 15 through the planetary shafts 9 and 14. It has.
第２減速機構部４の補給油路１９は、第２遊星軸１４の軸線に沿って形成された孔状の軸部流路２０と、軸部流路２０の上端（上流端）に連続する溝状の上流案内部２１と、軸部流路２０の下端（下流端）に連続して軸受１５の内周で開口する孔状の下流案内部２２とを備えている。 The replenishment oil passage 19 of the second speed reduction mechanism portion 4 is continuous with a hole-shaped shaft portion passage 20 formed along the axis of the second planetary shaft 14 and an upper end (upstream end) of the shaft portion passage 20. A groove-shaped upstream guide portion 21 and a hole-shaped downstream guide portion 22 that is continuous with the lower end (downstream end) of the shaft portion flow path 20 and opens at the inner periphery of the bearing 15 are provided.
各上流案内部２１は、図３に示すように、第２キャリア１１の上面（外側面）から第２遊星軸１４の上端部にかけて溝状に形成され、軸部流路２０から第２キャリア１１の回転中心に向かって延びている。即ち、各上流案内部２１は、第２キャリア１１の内周縁側から第２遊星軸１４に向かって放射状に形成されている。 As shown in FIG. 3, each upstream guide portion 21 is formed in a groove shape from the upper surface (outer surface) of the second carrier 11 to the upper end portion of the second planetary shaft 14, and from the shaft portion flow path 20 to the second carrier 11. Extending toward the center of rotation. That is, each upstream guide portion 21 is formed radially from the inner peripheral edge side of the second carrier 11 toward the second planetary shaft 14.
更に、図２に示すように、第２遊星軸１４の上端部には上下方向に広がる面による内壁２３が形成されており、この内壁２３が各上流案内部２１の下流端に位置している。 Further, as shown in FIG. 2, an inner wall 23 is formed at the upper end portion of the second planetary shaft 14 by a surface extending in the vertical direction, and this inner wall 23 is located at the downstream end of each upstream guide portion 21. .
また、各下流案内部２２は、各第２遊星軸１４の内部に形成され、第２キャリア１１の径方向外側に向かって延設されている。 Each downstream guide portion 22 is formed inside each second planetary shaft 14 and extends outward in the radial direction of the second carrier 11.
第２減速機構部４の補給油路１９による軸受１５への潤滑油の補給は次のようにして行われる。各上流案内部２１に入った潤滑油は、第２キャリア１１の回転による遠心力で第２キャリア１１の径方向外側に向かって流れる。そして、各上流案内部２１の下流端に流れた潤滑油は内壁２３に突き当る。内壁２３に突き当った潤滑油は軸部流路２０に入り込み、下流案内部２２へ向かう。一方、第２キャリア１１の回転による遠心力は各下流案内部２２内部の潤滑油にも作用する。これにより、各下流案内部２２の潤滑油に軸受１５に向かう流れが形成し、軸部流路２０の潤滑油が下流案内部２２を経て軸受１５に供給される。 Lubricating oil is replenished to the bearing 15 through the replenishing oil passage 19 of the second reduction mechanism unit 4 as follows. The lubricating oil that has entered each upstream guide portion 21 flows toward the outside in the radial direction of the second carrier 11 due to the centrifugal force generated by the rotation of the second carrier 11. Then, the lubricating oil that has flowed to the downstream end of each upstream guide portion 21 hits the inner wall 23. The lubricating oil that has hit the inner wall 23 enters the shaft channel 20 and travels toward the downstream guide unit 22. On the other hand, the centrifugal force generated by the rotation of the second carrier 11 also acts on the lubricating oil inside each downstream guide portion 22. Thereby, a flow toward the bearing 15 is formed in the lubricating oil of each downstream guide portion 22, and the lubricating oil of the shaft portion flow path 20 is supplied to the bearing 15 through the downstream guide portion 22.
このように、第２キャリア１１が回転することにより、第２減速機構部４の補給油路１９から軸受１５への潤滑油の補給が強制的に行われ、第２遊星歯車１２の円滑な回転を得ることができる。 In this way, when the second carrier 11 rotates, the lubricating oil is forcibly replenished from the replenishing oil passage 19 of the second reduction mechanism unit 4 to the bearing 15, and the second planetary gear 12 rotates smoothly. Can be obtained.
第１減速機構部３の補給油路１８は、図２に示すように、第１遊星軸９の軸線に沿って形成された孔状の軸部流路２４と、軸部流路２４の下端（上流端）に連続する溝状の上流案内部２５と、軸部流路２４の上端（下流端）に連続して軸受１０の内周で開口する孔状の下流案内部２６とを備えている。 As shown in FIG. 2, the replenishment oil passage 18 of the first speed reduction mechanism unit 3 includes a hole-shaped shaft channel 24 formed along the axis of the first planetary shaft 9 and a lower end of the shaft channel 24. A groove-shaped upstream guide portion 25 continuous to the (upstream end), and a hole-shaped downstream guide portion 26 that opens to the inner periphery of the bearing 10 continuously to the upper end (downstream end) of the shaft passage 24. Yes.
各上流案内部２５は、図４に示すように、第１キャリア６の下面（外側面）から第１遊星軸９の下端部にかけて溝状に形成され、軸部流路２４から第１キャリア６の回転中心に向かって延びている。即ち、各上流案内部２５は、第１キャリア６の内周縁側から第１遊星軸９に向かって放射状に形成されている。 As shown in FIG. 4, each upstream guide portion 25 is formed in a groove shape from the lower surface (outer surface) of the first carrier 6 to the lower end portion of the first planetary shaft 9, and from the shaft portion flow path 24 to the first carrier 6. Extending toward the center of rotation. That is, each upstream guide portion 25 is formed radially from the inner peripheral edge side of the first carrier 6 toward the first planetary shaft 9.
更に、図２に示すように、第１遊星軸９の下端部には上下方向に広がる面による内壁２７が形成されており、この内壁２７が各上流案内部２５の下流端に位置している。 Further, as shown in FIG. 2, an inner wall 27 is formed at the lower end portion of the first planetary shaft 9 by a surface extending in the vertical direction, and this inner wall 27 is located at the downstream end of each upstream guide portion 25. .
また、各下流案内部２６は、各第１遊星軸９の内部に形成され、第１キャリア６の径方向外側に向かって延設されている。 Each downstream guide portion 26 is formed inside each first planetary shaft 9 and extends outward in the radial direction of the first carrier 6.
第１減速機構部３の補給油路１８による軸受１０への潤滑油の補給は次のようにして行われる。各上流案内部２１に入った潤滑油は、第１キャリア６の回転による遠心力で第１キャリア６の径方向外側に向かって流れる。そして、各上流案内部２５の下流端に流れた潤滑油は内壁２７に突き当る。内壁２７に突き当った潤滑油は軸部流路２４に入り込み、下流案内部２６へ向かう。一方、第１キャリア６の回転による遠心力は各下流案内部２６内部の潤滑油にも作用する。これにより、各下流案内部２６の潤滑油に軸受１０に向かう流れが形成し、軸部流路２４の潤滑油が下流案内部２６を経て軸受１０に供給される。 Lubricating oil is replenished to the bearing 10 through the replenishing oil passage 18 of the first speed reduction mechanism 3 as follows. The lubricating oil that has entered each upstream guide portion 21 flows toward the outside in the radial direction of the first carrier 6 due to the centrifugal force generated by the rotation of the first carrier 6. The lubricating oil that has flowed to the downstream end of each upstream guide portion 25 strikes the inner wall 27. The lubricating oil that hits the inner wall 27 enters the shaft channel 24 and travels toward the downstream guide 26. On the other hand, the centrifugal force generated by the rotation of the first carrier 6 also acts on the lubricating oil inside each downstream guide portion 26. As a result, a flow toward the bearing 10 is formed in the lubricating oil in each downstream guide portion 26, and the lubricating oil in the shaft portion flow path 24 is supplied to the bearing 10 through the downstream guide portion 26.
第１減速機構部３の補給油路１８における各上流案内部２５は、第１キャリア６の下面に形成されている。これにより、ケーシング２に充填された潤滑油の油面が低下して第１遊星軸９の上端側が潤滑油の油面から露出した場合でも、潤滑油に浸漬された状態にある第１キャリア６の下面から補給油路１８に潤滑油を取り込むことができる。 Each upstream guide portion 25 in the replenishment oil passage 18 of the first speed reduction mechanism portion 3 is formed on the lower surface of the first carrier 6. Thereby, even when the oil level of the lubricating oil filled in the casing 2 is lowered and the upper end side of the first planetary shaft 9 is exposed from the oil level of the lubricating oil, the first carrier 6 in the state immersed in the lubricating oil. Lubricating oil can be taken into the replenishing oil passage 18 from the lower surface.
また、図２に示すように、第２減速機構部４の第２キャリア１１の上面には、第１減速機構部３の第１キャリア６の下面が対向する。 As shown in FIG. 2, the lower surface of the first carrier 6 of the first reduction mechanism unit 3 faces the upper surface of the second carrier 11 of the second reduction mechanism unit 4.
このとき、図示しないが、第１キャリア６の平面視形状が第２キャリア１１の平面視形状と同一であると、第２キャリア１１の上面に形成されている上流案内部２１や第２遊星軸１４の軸部流路２０の上端開口が第１キャリア６に常に覆われた状態となって、第２遊星軸１４の軸部流路２０への潤滑油の取り込みが阻害されるおそれがある。 At this time, although not shown in the drawing, when the plan view shape of the first carrier 6 is the same as the plan view shape of the second carrier 11, the upstream guide portion 21 and the second planetary shaft formed on the upper surface of the second carrier 11. There is a possibility that the upper end opening of the 14 shaft passages 20 is always covered with the first carrier 6, and the intake of the lubricating oil into the shaft passage 20 of the second planetary shaft 14 may be hindered.
そこで、図４及び図５に示すように、第１キャリア６は、その平面視形状が、各第１遊星歯車７間に位置する部分を切欠いた形状（本実施形態では、円形の一部をそぎ落とした略三角形状）とされている。これによれば、図５に示すように、第１キャリア６の回転により第２遊星軸１４の軸部流路２０の上端開口が露出する機会が生じ、軸部流路２０に滞りなく潤滑油を取り込むことができる。 Therefore, as shown in FIGS. 4 and 5, the first carrier 6 has a shape in plan view in which a portion located between the first planetary gears 7 is cut out (in this embodiment, a part of a circle is formed). It is said that it is a substantially triangular shape. According to this, as shown in FIG. 5, the rotation of the first carrier 6 causes an opportunity to expose the upper end opening of the shaft portion channel 20 of the second planetary shaft 14, and the lubricating oil is not stagnated in the shaft portion channel 20. Can be imported.
更に、第１キャリア６と第２キャリア１１との対向面の夫々に溝状の上流案内部２５，２１を形成したことにより、第１キャリア６と第２キャリア１１との対向面間の間隔が比較的狭くても、潤滑油を軸部流路２４，２０に向かって確実に案内することができる。 Further, the groove-shaped upstream guide portions 25 and 21 are formed on the opposing surfaces of the first carrier 6 and the second carrier 11, respectively, so that the distance between the opposing surfaces of the first carrier 6 and the second carrier 11 is increased. Even if it is relatively narrow, the lubricating oil can be reliably guided toward the shaft channels 24 and 20.
これによれば、軸受１５，１０の良好な潤滑を得ながら、第１キャリア６と第２キャリア１１との対向面間の間隔を狭くして減速機１の小型化を図ることが可能となる。 According to this, it is possible to reduce the size of the reduction gear 1 by narrowing the interval between the opposed surfaces of the first carrier 6 and the second carrier 11 while obtaining good lubrication of the bearings 15 and 10. .
また、上流案内部２５，２１は、第１キャリア６と第２キャリア１１との外面に溝を刻設することによって形成することができ、上流案内部２５，２１を設けることに伴う製造コストの増加も抑えることができる。しかも、上流案内部２５，２１を形成することにより第１キャリア６及び第２キャリア１１の軽量化を図ることもできる。 Further, the upstream guide portions 25 and 21 can be formed by engraving grooves on the outer surfaces of the first carrier 6 and the second carrier 11, and the manufacturing cost associated with the provision of the upstream guide portions 25 and 21 is reduced. The increase can also be suppressed. In addition, the first guide 6 and the second carrier 11 can be reduced in weight by forming the upstream guide portions 25 and 21.
なお、上記の実施形態においては、第１キャリア６と第２キャリア１１との外面に溝状の上流案内部２５，２１を設けた例を示したが、これ以外に、第２減速機構部４においては、図６に示すように、第２キャリア１１に孔状の上流案内部２８を設けてもよい。 In the above-described embodiment, the example in which the groove-shaped upstream guide portions 25 and 21 are provided on the outer surfaces of the first carrier 6 and the second carrier 11 has been described. In FIG. 6, a hole-shaped upstream guide portion 28 may be provided in the second carrier 11 as shown in FIG.
上流案内部２８は、第２キャリア１１の内周端の開口を潤滑油の取り込み口として第２遊星軸１４に向かって延びて軸部流路２０に連通するように形成される。 The upstream guide portion 28 is formed so as to extend toward the second planetary shaft 14 and communicate with the shaft portion flow path 20 with the opening at the inner peripheral end of the second carrier 11 as an intake port for the lubricating oil.
これによっても、第２キャリア１１の回転による遠心力が、孔状の上流案内部２８の内部の潤滑油を強制的に流動させるので、軸受１５への潤滑油の補給を確実に行うことができる。 Also by this, the centrifugal force due to the rotation of the second carrier 11 forcibly causes the lubricating oil inside the hole-shaped upstream guide portion 28 to flow, so that the lubricating oil can be reliably supplied to the bearing 15. .
１…減速機、２…ケーシング、５…遊星歯車機構、６…第１キャリア（キャリア）、７…第１遊星歯車（遊星歯車）、９…第１遊星軸（遊星軸）１０，１５…軸受、１１…第２キャリア（キャリア）、１２…第２遊星歯車（遊星歯車）、１４…第２遊星軸（遊星軸）、１８，１９…補給油路、２０，２４…軸部流路、２１，２５，２８…上流案内部、２２，２６…下流案内部。
DESCRIPTION OF SYMBOLS 1 ... Reduction gear, 2 ... Casing, 5 ... Planetary gear mechanism, 6 ... 1st carrier (carrier), 7 ... 1st planetary gear (planetary gear), 9 ... 1st planetary shaft (planetary shaft) 10,15 ... Bearing , 11 ... second carrier (carrier), 12 ... second planetary gear (planetary gear), 14 ... second planetary shaft (planetary shaft), 18, 19 ... supply oil passage, 20, 24 ... shaft portion passage, 21 , 25, 28 ... upstream guide part, 22, 26 ... downstream guide part.
Claims (3)
前記補給油路は、前記遊星軸の軸線に沿って形成された軸部流路と、前記ケーシング内の潤滑油を前記軸部流路の上流端に案内する上流案内部と、前記軸部流路内の潤滑油を該軸部流路の下流端から前記軸受に案内する下流案内部とを備え、
前記上流案内部は、前記軸部流路から前記キャリアの回転中心に向かって延設され、
前記下流案内部は、前記軸部流路から前記キャリアの径方向外側に向かって延設されていることを特徴とする減速機。 A planetary gear mechanism is accommodated in a casing filled with lubricating oil, and the planetary gear is supported via a bearing on a planetary shaft provided on a carrier of the planetary gear mechanism, wherein the lubricating oil is In what has a replenishment oil passage for replenishing the bearing via a planetary shaft,
The replenishing oil passage includes an axial passage formed along the axis of the planetary shaft, an upstream guide portion that guides lubricating oil in the casing to an upstream end of the axial passage, and the axial flow. A downstream guide portion for guiding the lubricating oil in the passage from the downstream end of the shaft passage to the bearing;
The upstream guide portion extends from the shaft channel toward the rotation center of the carrier,
The said downstream guide part is extended toward the radial direction outer side of the said carrier from the said axial part flow path, The speed reducer characterized by the above-mentioned.
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| JPS61157750U (en) * | 1985-03-22 | 1986-09-30 | ||
| JPH04128556U (en) * | 1991-05-17 | 1992-11-24 | 本田技研工業株式会社 | Pinion shaft fixing structure for planetary gears |
| JP2006177394A (en) * | 2004-12-21 | 2006-07-06 | Daihatsu Motor Co Ltd | Planetary gear device lubricating structure |
| JP2009014148A (en) * | 2007-07-06 | 2009-01-22 | Aisin Aw Co Ltd | Lubricant supply device for automatic transmission |
| JP2009079627A (en) * | 2007-09-25 | 2009-04-16 | Komatsu Ltd | Reduction gear |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61157750U (en) * | 1985-03-22 | 1986-09-30 | ||
| JPH04128556U (en) * | 1991-05-17 | 1992-11-24 | 本田技研工業株式会社 | Pinion shaft fixing structure for planetary gears |
| JP2006177394A (en) * | 2004-12-21 | 2006-07-06 | Daihatsu Motor Co Ltd | Planetary gear device lubricating structure |
| JP2009014148A (en) * | 2007-07-06 | 2009-01-22 | Aisin Aw Co Ltd | Lubricant supply device for automatic transmission |
| JP2009079627A (en) * | 2007-09-25 | 2009-04-16 | Komatsu Ltd | Reduction gear |
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