JP2012202449A - Planetary gear device - Google Patents

Planetary gear device Download PDF

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JP2012202449A
JP2012202449A JP2011065794A JP2011065794A JP2012202449A JP 2012202449 A JP2012202449 A JP 2012202449A JP 2011065794 A JP2011065794 A JP 2011065794A JP 2011065794 A JP2011065794 A JP 2011065794A JP 2012202449 A JP2012202449 A JP 2012202449A
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planetary gear
cooling
gear device
oil
hole
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Hiroshi Morishita
比呂志 森下
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements

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  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To improve cooling effects in an outer ring of a bearing for supporting a planetary gear in a planetary gear device.SOLUTION: In the planetary gear device, a cooling hole 29, for making a cooling oil pass through an outer ring 24 integrated with a body portion of a planetary gear 14, is provided in an axial direction, and a cooling oil nozzle 19 corresponding to the cooling hole 29 is installed outside the device. While the cooling oil injected from the cooling oil nozzle 19 passes through the cooling hole 29, the outer ring 24 of a roller bearing 21 supporting the planetary gear 14 is cooled.

Description

この発明は、遊星歯車装置に関し、特に遊星歯車を支持する軸受の冷却構造に関するものである。   The present invention relates to a planetary gear device, and more particularly to a cooling structure for a bearing that supports a planetary gear.

遊星歯車装置において、遊星歯車を支持する転がり軸受は、その外輪が歯車本体と一体化された一体タイプと、外輪と歯車本体が別体に形成され、歯車本体の内径面に外輪が緊密に嵌合された別体タイプがある（特許文献１）。そのいずれのタイプにおいても、遊星歯車は負荷を受けながら自転しつつ公転するため、これと噛み合う太陽歯車及び内歯歯車との摩擦により発熱する。その熱が転がり軸受の外輪部分に伝導されるため、外輪部分と内輪部分の温度差が顕著になり、軸受の予圧が変化する等軸受の諸特性に悪影響を及ぼす。その温度差を小さくする対策として外輪部分を軸受の潤滑油によって冷却する方法が考えられる。   In a planetary gear device, a rolling bearing that supports a planetary gear is an integral type in which the outer ring is integrated with the gear body, and the outer ring and the gear body are formed separately, and the outer ring is tightly fitted to the inner diameter surface of the gear body. There is a combined separate type (Patent Document 1). In any of these types, the planetary gear revolves while rotating under a load, and generates heat due to friction with the sun gear and the internal gear that mesh with the planetary gear. Since the heat is conducted to the outer ring portion of the rolling bearing, the temperature difference between the outer ring portion and the inner ring portion becomes significant, and adversely affects various characteristics of the bearing such as changes in the bearing preload. As a measure for reducing the temperature difference, a method of cooling the outer ring portion with bearing lubricating oil can be considered.

遊星歯車を支持する転がり軸受に対する給油構造として、支持軸に設けた給油通路から軸受の内輪に設けたノズル穴を通して軸受内部に給油する構造が知られている（特許文献１）。また、遊星歯車から軸方向に離れた外部に給油ノズルを設置し、その給油ノズルを軸受幅面に向けるとともに、その給油ノズルから供給される潤滑油が軸受の径方向外部へ逸脱することを防止し軸受内部に向かわせるように、軸受外輪の端面にオイルスクープリングを装着した給油構造も知られている（特許文献２）。   As an oil supply structure for a rolling bearing that supports a planetary gear, a structure is known in which oil is supplied into the bearing through a nozzle hole provided in an inner ring of the bearing from an oil supply passage provided in a support shaft (Patent Document 1). In addition, an oil supply nozzle is installed outside the planetary gear in the axial direction, and the oil supply nozzle faces the bearing width surface, and the lubricant supplied from the oil supply nozzle is prevented from deviating to the outside in the radial direction of the bearing. There is also known an oil supply structure in which an oil scoop ring is attached to an end face of a bearing outer ring so as to face the inside of the bearing (Patent Document 2).

特開平７−３１７８８５号公報JP 7-317885 A 特開平１１−１０１３３３号公報（図４）Japanese Patent Laid-Open No. 11-101333 (FIG. 4)

遊星歯車を支持する転がり軸受の内輪はその支持軸に固定されているため、公転のみを行い、自転をすることがないので遊星歯車の公転中心から見た内輪の向きは常に一定である。このため、特許文献１に開示された給油構造の場合は、軸受内部に供給された潤滑油は公転による遠心力を受け、公転中心から遠い部分に片寄る傾向がある。その結果、給油はもっぱら公転中心から遠い部分の給油穴から行われ、近い部分の給油穴からは十分に給油することができず、その部分に対向した外輪部分の潤滑及び冷却作用は不十分となる問題がある。   Since the inner ring of the rolling bearing that supports the planetary gear is fixed to the support shaft, only the revolution is performed and the rotation is not performed. Therefore, the direction of the inner ring viewed from the center of revolution of the planetary gear is always constant. For this reason, in the case of the oil supply structure disclosed in Patent Document 1, the lubricating oil supplied to the inside of the bearing is subject to centrifugal force due to revolution, and tends to shift to a portion far from the center of revolution. As a result, lubrication is performed exclusively from the lubrication hole in the part far from the center of revolution, and it is not possible to sufficiently lubricate from the lubrication hole in the near part, and the lubrication and cooling action of the outer ring part facing that part is insufficient. There is a problem.

また、特許文献２に開示された給油構造の場合は、潤滑性能の向上には効果的であるが、潤滑油の接触は軌道面に限られるため、軸受外輪の温度上昇を積極的に抑制する冷却効果は小さい。   Further, in the case of the oil supply structure disclosed in Patent Document 2, it is effective for improving the lubrication performance, but since the contact of the lubricant is limited to the raceway surface, the temperature increase of the bearing outer ring is positively suppressed. The cooling effect is small.

そこで、この発明は、遊星歯車を支持する転がり軸受の外輪の冷却効果を高めることを課題とする。   Accordingly, an object of the present invention is to enhance the cooling effect of the outer ring of the rolling bearing that supports the planetary gear.

前記の課題を解決するために、この発明は、太陽歯車、その周りに同芯状態に固定された内歯歯車、前記太陽歯車と内歯歯車の間に介在され両方の歯車と噛み合った遊星歯車、前記遊星歯車の支持軸に連結されたキャリヤとからなり、前記太陽歯車の支持軸と前記キャリヤの支持軸のいずれか一方を入力軸、他方を出力軸とし、前記遊星歯車の本体部の内径面と支持軸の間に転がり軸受が介在された遊星歯車装置において、前記遊星歯車の本体部に冷却油を通過させる冷却穴が軸方向に複数個所設けられ、装置外部に前記冷却穴に対応した冷却油ノズルが設けられた構成としたものである。   In order to solve the above problems, the present invention provides a sun gear, an internal gear fixed around the sun gear, and a planetary gear that is interposed between the sun gear and the internal gear and meshes with both gears. A carrier coupled to a support shaft of the planetary gear, wherein one of the support shaft of the sun gear and the support shaft of the carrier is an input shaft and the other is an output shaft, and the inner diameter of the main body of the planetary gear In the planetary gear device in which a rolling bearing is interposed between the surface and the support shaft, a plurality of cooling holes for allowing the cooling oil to pass through are provided in the main body of the planetary gear in the axial direction, corresponding to the cooling holes outside the device. The cooling oil nozzle is provided.

前記遊星歯車装置の作動中において、冷却油ノズルから噴射される冷却油が冷却穴に流入し、遊星歯車の本体部を軸方向に他端部まで移動して排出される。その移動途中において冷却油が本体部の熱を奪い冷却する。   During the operation of the planetary gear device, the cooling oil injected from the cooling oil nozzle flows into the cooling hole, moves through the main body of the planetary gear to the other end, and is discharged. During the movement, the cooling oil takes the heat of the main body and cools it.

遊星歯車の本体部と転がり軸受の外輪とが一体化されている場合は、本体部を冷却することは、即ち外輪を冷却することになる。本体部と転がり軸受の外輪とが別体である場合は、本体部を通じて外輪が冷却される。前記冷却穴の流入端部に冷却油のガイド部材を設けたり、冷却穴に外向きの勾配をつけたりすることにより、冷却油の通過量を増加させ、冷却効果を高めることができる。   In the case where the main body of the planetary gear and the outer ring of the rolling bearing are integrated, the cooling of the main body, that is, the outer ring is cooled. When the main body and the outer ring of the rolling bearing are separate, the outer ring is cooled through the main body. By providing a cooling oil guide member at the inflow end portion of the cooling hole, or by providing an outward gradient to the cooling hole, it is possible to increase the passage amount of the cooling oil and enhance the cooling effect.

以上のように、この発明によれば、遊星歯車の本体部に設けられた冷却穴に外部に設置された冷却ノズルからの冷却油を供給することにより、前記本体部と一体又はその本体部に嵌合された遊星歯車の転がり軸受の外輪を冷却し、内輪との温度差を少なくすることができる。   As described above, according to the present invention, by supplying the cooling oil from the cooling nozzle installed outside to the cooling hole provided in the main body of the planetary gear, the main body is integrated with the main body. The outer ring of the rolling bearing of the fitted planetary gear can be cooled, and the temperature difference from the inner ring can be reduced.

図１は、実施形態１の遊星歯車減速装置の一部省略断面図である。FIG. 1 is a partially omitted cross-sectional view of the planetary gear speed reducer of the first embodiment. 図２は、図１のＸ１−Ｘ１線の断面図である。2 is a cross-sectional view taken along line X1-X1 of FIG. 図３は、同上の変形例の一部断面図である。FIG. 3 is a partial sectional view of a modification of the above. 図４（ａ）は、実施形態２の一部省略断面図、図４（ｂ）は、図４（ａ）のＸ２−Ｘ２線の断面図、図４（ｃ）は変形例の一部省略断面図である。4A is a partially omitted sectional view of the second embodiment, FIG. 4B is a sectional view taken along line X2-X2 of FIG. 4A, and FIG. 4C is a partially omitted modification. It is sectional drawing. 図５（ａ）は、実施形態３の一部省略断面図、図５（ｂ）は、図５（ａ）のＸ３−Ｘ３線の断面図である。5A is a partially omitted cross-sectional view of the third embodiment, and FIG. 5B is a cross-sectional view taken along line X3-X3 of FIG. 図６（ａ）、図６（ｂ）は、それぞれ他の実施形態の一部省略断面図である。FIG. 6A and FIG. 6B are partially omitted sectional views of other embodiments, respectively.

以下、この発明の実施形態を添付図面に基づいて説明する。   Embodiments of the present invention will be described below with reference to the accompanying drawings.

[実施形態１]
図１及び図２に遊星歯車装置の一例として遊星歯車減速装置を示す。この減速装置は、入力軸１１が太陽歯車１２の支持軸となっている。その太陽歯車１２と、太陽歯車１２の周りに固定された内歯歯車１３との間にこれらの歯車１２、１３と噛み合った遊星歯車１４が複数個所に介在される。各遊星歯車１４の支持軸１５の一端部に径方向のキャリヤ１６が一体化され、そのキャリヤ１６の他端が出力軸１７（図２参照）と一体化されている。出力軸１７がキャリヤ１６の支持軸となっている。出力軸１７は、入力軸１１と同軸状態に設けられる。 [Embodiment 1]
1 and 2 show a planetary gear reduction device as an example of a planetary gear device. In this reduction gear, the input shaft 11 is a support shaft for the sun gear 12. Between the sun gear 12 and an internal gear 13 fixed around the sun gear 12, planetary gears 14 meshing with these gears 12 and 13 are interposed at a plurality of positions. A radial carrier 16 is integrated with one end of the support shaft 15 of each planetary gear 14, and the other end of the carrier 16 is integrated with the output shaft 17 (see FIG. 2). The output shaft 17 is a support shaft for the carrier 16. The output shaft 17 is provided coaxially with the input shaft 11.

前記遊星歯車１４は、その支持軸１５の周りに介在された自動調心型のころ軸受２１により自転しつつ太陽歯車１２の周りを公転し、前記キャリヤ１６を介して出力軸１７をその公転速度で減速回転させる。この場合の減速比は、Ｚｓ／（Ｚｓ＋Ｚｒ）となる。ただし、Ｚｓは太陽歯車１２の歯数、Ｚｒは内歯歯車１３の歯数である。前記の入力と出力を入れ替えると、遊星歯車増速装置として使用することができる。   The planetary gear 14 revolves around the sun gear 12 while rotating around a self-aligning roller bearing 21 interposed around the support shaft 15, and the output shaft 17 is revolved through the carrier 16 at its revolving speed. To decelerate and rotate. The reduction ratio in this case is Zs / (Zs + Zr). However, Zs is the number of teeth of the sun gear 12, and Zr is the number of teeth of the internal gear 13. If the input and output are interchanged, it can be used as a planetary gear speed increasing device.

前記の支持軸１５の一方の端面に入力軸１１側に開放された給油溜り１８が設けられ、その給油溜り１８の開放面に対向した給油ノズル１９が装置外部に設置される。   An oil supply reservoir 18 opened to the input shaft 11 side is provided on one end surface of the support shaft 15, and an oil supply nozzle 19 facing the open surface of the oil supply reservoir 18 is installed outside the apparatus.

前記の自動調心型のころ軸受２１は、内輪２２に二列の軌道溝２３ａ、２３ｂが設けられ、これらに対向して外輪２４に球面の軌道面２５が設けられる。外輪２４の軌道面２５の中心が軸受中心に一致させることにより自動調心機能を付与している。各軌道溝２３ａ、２３ｂと軌道面２５の間に二列のたる形のころ２６が保持器２７によって保持された状態で介在される。   In the self-aligning roller bearing 21, two rows of raceway grooves 23 a and 23 b are provided on the inner ring 22, and a spherical raceway surface 25 is provided on the outer ring 24 so as to face these. A self-aligning function is provided by making the center of the raceway surface 25 of the outer ring 24 coincide with the center of the bearing. Two rows of rollers 26 are interposed between the raceway grooves 23 a and 23 b and the raceway surface 25 while being held by a cage 27.

前記の外輪２４は、遊星歯車１４の本体部と一体化された一体タイプであり、その外輪２４の外径面に遊星歯車１４の歯部１４ａが形成される。図３に示したように、遊星歯車１４の本体部１４ｂと外輪２４を別体に形成し、その外輪２４を本体部１４ｂの内径面に嵌合一体化する場合（別体タイプ）もある。   The outer ring 24 is an integral type integrated with the main body of the planetary gear 14, and a tooth portion 14 a of the planetary gear 14 is formed on the outer diameter surface of the outer ring 24. As shown in FIG. 3, the main body 14b and the outer ring 24 of the planetary gear 14 may be formed separately, and the outer ring 24 may be fitted and integrated with the inner diameter surface of the main body 14b (separate type).

前記の一体タイプ及び別体タイプのいずれの場合にも、外輪２４の両端面間に軸方向に貫通した冷却穴２９が周方向の複数個所に所定の間隔をおいて設けられる。冷却穴２９の前記給油溜り１８の開放側の端部が冷却油の流入端部３１、他方の端部が流出端部３２となっている。   In both the integral type and the separate type, cooling holes 29 penetrating in the axial direction are provided between the both end faces of the outer ring 24 at a plurality of locations in the circumferential direction at predetermined intervals. The end of the cooling hole 29 on the open side of the oil supply reservoir 18 is a cooling oil inflow end 31, and the other end is an outflow end 32.

流入端部３１に比べ流出端部３２の方が相対的に径方向外側に設けられ、冷却穴２９は流入端部３１側から流出端部３２に至るに従い径方向外側へ傾斜する勾配が付与されている。また、前記冷却穴２９の中間部において、径方向外向きに分岐し歯部１４ａの歯底に通じる分岐穴３３が設けられる。   The outflow end portion 32 is provided relatively radially outward as compared to the inflow end portion 31, and the cooling hole 29 is given a gradient that inclines radially outward from the inflow end portion 31 side to the outflow end portion 32. ing. Further, a branch hole 33 is provided in the middle portion of the cooling hole 29 so as to branch outward in the radial direction and communicate with the tooth bottom of the tooth portion 14a.

前記流入端部３１の外径側の外輪２４の端面に沿って、一定長さの円弧状のガイド部材３４が取り付けられる。ガイド部材３４は断面Ｌ形をなし、その脚部３９の屈曲された外縁部３９ａが外輪２４の端面に外周縁に沿って固定される。ガイド部材３４は、装置外部において流入端部３１に向けて設けられた冷却油ノズル３５から噴射される冷却油を流入端部３１に集める作用を行う。また、冷却穴２９が外向きに傾斜していることにより、内部に流入した冷却油に遊星歯車１４の回転に伴う遠心力が作用し、流出端部３２側へ円滑に排出させることができる。前記の冷却油としては、潤滑油を用いることができる。   An arcuate guide member 34 having a fixed length is attached along the end surface of the outer ring 24 on the outer diameter side of the inflow end portion 31. The guide member 34 has an L-shaped cross section, and a bent outer edge portion 39 a of the leg portion 39 is fixed to the end surface of the outer ring 24 along the outer peripheral edge. The guide member 34 collects the cooling oil sprayed from the cooling oil nozzle 35 provided toward the inflow end portion 31 outside the apparatus at the inflow end portion 31. Further, since the cooling hole 29 is inclined outward, the centrifugal force accompanying the rotation of the planetary gear 14 acts on the cooling oil flowing into the inside, and can be smoothly discharged to the outflow end portion 32 side. Lubricating oil can be used as the cooling oil.

なお、前記の給油溜り１８の周壁には、周方向に複数の連通穴３６が設けられ、その連通穴３６と合致する給油穴３７が内輪２２に設けられる。   A plurality of communication holes 36 are provided in the circumferential direction on the peripheral wall of the oil supply reservoir 18, and an oil supply hole 37 that matches the communication hole 36 is provided in the inner ring 22.

実施形態１の遊星歯車装置は以上のようなものであり、次にその作用について説明する。   The planetary gear device of Embodiment 1 is as described above, and the operation thereof will be described next.

入力軸１１に一定回転速度のトルクが入力されると、入力軸１１と一体の太陽歯車１２が回転し、その太陽歯車１２と内歯歯車１３と噛み合った遊星歯車１４が自転しつつ公転し、その支持軸１５と一体のキャリヤ１６及びキャリヤ１６と一体の出力軸１７が前記の公転速度で減速回転する。このようにして入力トルクを出力側へ伝達する間に、遊星歯車１４の歯部１４ａは、太陽歯車１２と内歯歯車１３との噛み合い部分の摩擦によって発熱する。その熱は外輪２４と一体化された本体部に伝導される。   When torque having a constant rotational speed is input to the input shaft 11, the sun gear 12 integral with the input shaft 11 rotates, and the planetary gear 14 meshed with the sun gear 12 and the internal gear 13 revolves while rotating. The carrier 16 integrated with the support shaft 15 and the output shaft 17 integrated with the carrier 16 rotate at a reduced speed at the revolution speed. In this way, while the input torque is transmitted to the output side, the tooth portion 14a of the planetary gear 14 generates heat due to the friction of the meshing portion between the sun gear 12 and the internal gear 13. The heat is conducted to the main body unit integrated with the outer ring 24.

一方、給油ノズル１９から噴射された潤滑油は、給油溜り１８から、連通穴３６及び給油穴３７を経て、遠心力によってころ軸受２１の内部に供給される。また冷却油ノズル３５から噴射される冷却油は、ガイド部材３４によって受け止められ冷却穴２９に導かれる。冷却油は、遠心力の作用を受けて流入端部３１から流出端部３２まで移動し、その移動途中において、外輪２４の熱を奪ってこれを冷却する。   On the other hand, the lubricating oil injected from the oil supply nozzle 19 is supplied from the oil supply reservoir 18 through the communication hole 36 and the oil supply hole 37 into the roller bearing 21 by centrifugal force. The cooling oil sprayed from the cooling oil nozzle 35 is received by the guide member 34 and guided to the cooling hole 29. The cooling oil moves from the inflow end 31 to the outflow end 32 under the action of centrifugal force, and cools the outer ring 24 by taking heat during the movement.

また、冷却穴２９から分岐穴３３を経て歯部１４ａの歯底に供給された冷却油は歯部１４ａを直接冷却する。
[実施形態２] The cooling oil supplied from the cooling hole 29 to the tooth bottom of the tooth portion 14a through the branch hole 33 directly cools the tooth portion 14a.
[Embodiment 2]

次に、実施形態２について図４に基づいて説明する。
図４（ａ）（ｂ）の場合は、ガイド部材３４に沿った外輪２４の端面に油溜めの容積を増やすための溝状凹部３８を設けている。ガイド部材３４の脚部３９は、凹部３８の外周側の内面に挿入固定される。凹部３８の底面に冷却穴２９の流入端部３１が開放される。この凹部３８を設けることにより、冷却油の滞留量が増加し、冷却穴２９を通過する冷却油の増加を図り、冷却効果を向上させることができる。 Next, Embodiment 2 will be described with reference to FIG.
4 (a) and 4 (b), a groove-like recess 38 is provided on the end face of the outer ring 24 along the guide member 34 for increasing the volume of the oil sump. The leg portion 39 of the guide member 34 is inserted and fixed to the inner surface on the outer peripheral side of the recess 38. The inflow end 31 of the cooling hole 29 is opened on the bottom surface of the recess 38. By providing the recess 38, the amount of the cooling oil staying increases, the cooling oil passing through the cooling hole 29 is increased, and the cooling effect can be improved.

図４（ｃ）は、ガイド部材３４に沿った外輪２４の端面に、前記の凹部３８に代えて切欠き部４０を設け、その切欠き部４０に冷却穴２９の流入端部３１を開放している。ガイド部材３４の脚部３９は屈曲され、その外縁部３９ａが外輪２４の対面に固定される。この場合も、切欠き部４０によって前記と同様に冷却油の滞留量を増加させることができる。
[実施形態３] 4C, a notch 40 is provided on the end face of the outer ring 24 along the guide member 34 instead of the recess 38, and the inflow end 31 of the cooling hole 29 is opened in the notch 40. In FIG. ing. The leg portion 39 of the guide member 34 is bent, and the outer edge portion 39 a is fixed to the facing surface of the outer ring 24. Also in this case, the retention amount of the cooling oil can be increased by the notch 40 as described above.
[Embodiment 3]

図５（ａ）（ｂ）に示した実施形態３は、遊星歯車１４を軸方向に挟んでその両側に冷却油ノズル３５、３５ａを設置する場合である。この場合は、周方向に所定の間隔で設けられた前記の冷却穴２９の相互間に、傾斜方向が反対の冷却穴２９ａを所要数設けたものである。冷却穴２９ａの流入端部３１ａ、流出端部３２ａの位置も前記の場合と反対になっており、その流入端部３１ａに沿ってガイド部材３４ａが設けられる。ガイド部材３４ａに沿って凹部３８ａが設けられる。また、冷却穴２９ａの途中に分岐穴３３ａも同様に設けられる。   The third embodiment shown in FIGS. 5 (a) and 5 (b) is a case where the cooling oil nozzles 35 and 35a are installed on both sides of the planetary gear 14 in the axial direction. In this case, a required number of cooling holes 29a having opposite inclination directions are provided between the cooling holes 29 provided at predetermined intervals in the circumferential direction. The positions of the inflow end 31a and the outflow end 32a of the cooling hole 29a are also opposite to those described above, and a guide member 34a is provided along the inflow end 31a. A recess 38a is provided along the guide member 34a. A branch hole 33a is similarly provided in the middle of the cooling hole 29a.

この構成によると、一定の傾斜角の冷却穴２９だけでは冷却できない部分を、逆傾斜角をもった冷却穴２９ａによって冷却できるので、外輪２４の冷却範囲を広げることができる。
[その他の実施形態] According to this configuration, the portion that cannot be cooled only by the cooling hole 29 having a constant inclination angle can be cooled by the cooling hole 29a having the reverse inclination angle, so that the cooling range of the outer ring 24 can be expanded.
[Other embodiments]

図６（ａ）に示したように、ガイド部材３４、凹部３８等を省略した構成をとることもできる。この場合は、流入端部３１に直接流入した潤滑油が流出端部３２から排出される。さらに図６（ｂ）に示したように、冷却穴２９の勾配を無くした構成もとることができる。この場合は、流入端部３１に直接流入した潤滑油が、流入時のエネルギーだけで流出端部３２に達して排出される。   As shown in FIG. 6A, a configuration in which the guide member 34, the recess 38, and the like are omitted can be employed. In this case, the lubricating oil directly flowing into the inflow end portion 31 is discharged from the outflow end portion 32. Furthermore, as shown in FIG. 6B, a configuration in which the gradient of the cooling hole 29 is eliminated can be employed. In this case, the lubricating oil that directly flows into the inflow end portion 31 reaches the outflow end portion 32 and is discharged only by the energy at the time of inflow.

１１ 入力軸
１２ 太陽歯車
１３ 内歯歯車
１４ 遊星歯車
１４ａ 歯部
１４ｂ 本体部
１５ 支持軸
１６ キャリヤ
１７ 出力軸
１８ 給油溜り
１９ 給油ノズル
２１ ころ軸受
２２ 内輪
２３ａ、２３ｂ 軌道溝
２４ 外輪
２５ 軌道面
２６ ころ
２７ 保持器
２９、２９ａ 冷却穴
３１、３１ａ 流入端部
３２、３２ａ 流出端部
３３、３３ａ 分岐穴
３４、３４ａ ガイド部材
３５、３５ａ 冷却油ノズル
３６ 連通穴
３７ 給油穴
３８、３８ａ 凹部
３９ 脚部
３９ａ 外縁部
４０ 切欠き部


DESCRIPTION OF SYMBOLS 11 Input shaft 12 Sun gear 13 Internal gear 14 Planetary gear 14a Tooth part 14b Body part 15 Support shaft 16 Carrier 17 Output shaft 18 Oil supply reservoir 19 Oil supply nozzle 21 Roller bearing 22 Inner ring 23a, 23b Track groove 24 Outer ring 25 Track surface 26 Roller 27 Cage 29, 29a Cooling hole 31, 31a Inflow end 32, 32a Outflow end 33, 33a Branch hole 34, 34a Guide member 35, 35a Cooling oil nozzle 36 Communication hole 37 Oil supply hole 38, 38a Recess 39 Leg 39a Outer edge 40 Notch


Claims (10)

太陽歯車、その周りに同芯状態に固定された内歯歯車、前記太陽歯車と内歯歯車の間に介在され両方の歯車と噛み合った遊星歯車、前記遊星歯車の支持軸に連結されたキャリヤとからなり、前記太陽歯車の支持軸と前記キャリヤの支持軸のいずれか一方を入力軸、他方を出力軸とし、前記遊星歯車の本体部の内径面と支持軸の間に転がり軸受が介在された遊星歯車装置において、前記遊星歯車の本体部に冷却油を通過させる冷却穴が軸方向に複数個所設けられ、装置外部に前記冷却穴に対応した冷却油ノズルが設けられたことを特徴とする遊星歯車装置。   A sun gear, an internal gear fixed around the sun gear, a planetary gear interposed between the sun gear and the internal gear and meshed with both gears, and a carrier connected to a support shaft of the planetary gear And one of the support shaft of the sun gear and the support shaft of the carrier is an input shaft and the other is an output shaft, and a rolling bearing is interposed between the inner diameter surface of the main body of the planetary gear and the support shaft. In the planetary gear device, the planetary gear device is provided with a plurality of cooling holes in the axial direction for allowing the cooling oil to pass through, and a cooling oil nozzle corresponding to the cooling hole is provided outside the device. Gear device. 前記遊星歯車の本体部と転がり軸受の外輪とが一体化されたことを特徴とする請求項１に記載の遊星歯車装置。   The planetary gear device according to claim 1, wherein a main body portion of the planetary gear and an outer ring of a rolling bearing are integrated. 前記遊星歯車の本体部と転がり軸受の外輪とが別体であることを特徴とする請求項１に記載の遊星歯車装置。   The planetary gear device according to claim 1, wherein the planetary gear body and the outer ring of the rolling bearing are separate bodies. 前記冷却穴の流入端部に冷却油のガイド部材を設けたことを特徴とする請求項１から３のいずれかに記載の遊星歯車装置。   4. The planetary gear device according to claim 1, wherein a cooling oil guide member is provided at an inflow end portion of the cooling hole. 前記ガイド部材に沿った部分において、前記冷却穴の流入端部を含む範囲に油溜め凹部が設けられたことを特徴とする請求項４に記載の遊星歯車装置。   5. The planetary gear device according to claim 4, wherein an oil sump concave portion is provided in a range including the inflow end portion of the cooling hole in a portion along the guide member. 前記冷却穴が、流入端部から流出端部に至るに従い外径側へ傾斜する勾配を有することを特徴とする請求項1から５のいずれかに記載の遊星歯車装置。   The planetary gear device according to any one of claims 1 to 5, wherein the cooling hole has a gradient inclined toward the outer diameter side from the inflow end portion to the outflow end portion. 前記冷却穴の途中に遊星歯車の歯底に連通した分岐穴が設けられたことを特徴とする請求項１から６のいずれかに記載の遊星歯車装置。   The planetary gear device according to any one of claims 1 to 6, wherein a branch hole communicating with a tooth bottom of the planetary gear is provided in the middle of the cooling hole. 前記冷却穴の流入端部が遊星歯車の一方の端面に配置された冷却穴と、他方の端面に配置された冷却穴とが混在して、その両側の流入端部に対応して冷却油ノズルが遊星歯車の両側に設けられたことを特徴とする請求項１から７に記載の遊星歯車装置。   A cooling oil nozzle in which the inflow end portion of the cooling hole is disposed on one end surface of the planetary gear and the cooling hole disposed on the other end surface are mixed, corresponding to the inflow end portions on both sides thereof. The planetary gear device according to claim 1, wherein the planetary gear device is provided on both sides of the planetary gear. 前記冷却油として潤滑油を使用したことを特徴とする請求項１から８に記載の遊星歯車装置。   9. The planetary gear device according to claim 1, wherein lubricating oil is used as the cooling oil. 前記遊星歯車の支持軸の端面に軸方向に開放された給油溜りが設けられ、その給油溜りの周壁に内輪の給油穴に通じた連通穴が設けられ、装置外部に設けた給油ノズルを前記給油溜りに臨ませたことを特徴とする請求項１から９のいずれかに記載の遊星歯車装置。




An oil supply reservoir that is opened in the axial direction is provided on an end surface of the support shaft of the planetary gear, a communication hole that communicates with an oil supply hole of an inner ring is provided in a peripheral wall of the oil supply reservoir, and an oil supply nozzle provided outside the device is connected to the oil supply nozzle. The planetary gear device according to any one of claims 1 to 9, wherein the planetary gear device is placed in a pool.




JP2011065794A 2011-03-24 2011-03-24 Planetary gear device Withdrawn JP2012202449A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190293026A1 (en) * 2018-03-20 2019-09-26 Rolls-Royce Deutschland Ltd & Co Kg Gear and gas turbine engine
CN110454509A (en) * 2019-08-30 2019-11-15 福建福清核电有限公司 A kind of pumping over profile shaft holds thrust disc
JP2020120456A (en) * 2019-01-22 2020-08-06 本田技研工業株式会社 Cooler of rotary electric machine
CN112145630A (en) * 2020-09-26 2020-12-29 南京好龙电子有限公司 Planetary gear reducer with planet carrier positioning mechanism

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190293026A1 (en) * 2018-03-20 2019-09-26 Rolls-Royce Deutschland Ltd & Co Kg Gear and gas turbine engine
US11326555B2 (en) * 2018-03-20 2022-05-10 Rolls-Royce Deutschland Ltd & Co Kg Gear and gas turbine engine
JP2020120456A (en) * 2019-01-22 2020-08-06 本田技研工業株式会社 Cooler of rotary electric machine
CN110454509A (en) * 2019-08-30 2019-11-15 福建福清核电有限公司 A kind of pumping over profile shaft holds thrust disc
CN112145630A (en) * 2020-09-26 2020-12-29 南京好龙电子有限公司 Planetary gear reducer with planet carrier positioning mechanism

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