JP2014055653A - Planetary gear speed reduction mechanism - Google Patents
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Abstract
Description
本発明は、遊星歯車減速機構に関するものである。 The present invention relates to a planetary gear reduction mechanism.
従来、いわゆる３Ｋ型の遊星歯車減速機構として種々のものが提案されている。例えば特許文献１に記載された遊星歯車減速機構は、図６に示すように、第１歯車部９１及び該第１歯車部９１よりも小径の第２歯車部９２を有する段付遊星歯車９０を備えている。そして、第１歯車部９１及び第２歯車部９２の歯数が同等に、即ちそれらの歯数差が零に設定されている。従って、第１歯車部９１に噛合する太陽歯車を入力軸とし、第２歯車部９２に噛合する可動リングギヤを出力軸とした場合、太陽歯車の回転速度を著しく減速させて可動リングギヤから出力できることが期待される。 Conventionally, various types of so-called 3K type planetary gear reduction mechanisms have been proposed. For example, the planetary gear speed reduction mechanism described in Patent Document 1 includes a stepped planetary gear 90 having a first gear portion 91 and a second gear portion 92 having a smaller diameter than the first gear portion 91 as shown in FIG. I have. The first gear portion 91 and the second gear portion 92 have the same number of teeth, that is, the difference in the number of teeth is set to zero. Therefore, when the sun gear meshed with the first gear portion 91 is used as the input shaft and the movable ring gear meshed with the second gear portion 92 is used as the output shaft, the rotational speed of the sun gear can be significantly reduced and output from the movable ring gear. Be expected.
ところで、特許文献１の段付遊星歯車９０は、第１歯車部９１及び第２歯車部９２の歯数が同等に設定されていることで、小径側の第２歯車部９２の歯の大きさ、いわゆるモジュールが相対的に小さくなって、第２歯車部９２の歯の強度が低くなっている。一方、例えば入力側の回転速度を十分に減速して出力（以下、「高減速化」ともいう）しようとすると、これに伴う出力トルクの増加に対応して第２歯車部９２の歯の強度を高くすることが必須である。 Incidentally, in the stepped planetary gear 90 of Patent Document 1, the number of teeth of the first gear portion 91 and the second gear portion 92 is set to be equal, so that the tooth size of the second gear portion 92 on the small diameter side is set. The so-called module is relatively small, and the strength of the teeth of the second gear portion 92 is low. On the other hand, for example, when the rotational speed on the input side is sufficiently decelerated and output (hereinafter also referred to as “higher speed reduction”), the strength of the teeth of the second gear portion 92 corresponding to the increase in the output torque associated therewith. It is essential to increase the value.
特許文献１では、第２歯車部９２の歯を含めて段付遊星歯車９０全体の強度を高くするため、金属製の薄板歯車を位相を合わせて積層して段付遊星歯車９０を構成することが併せて提案されている。しかしながら、このような段付遊星歯車９０は、構造が複雑であるとともに、第１歯車部９１及び第２歯車部９２を同相に配置するための高精度な組付けが要求される。 In Patent Document 1, in order to increase the strength of the entire stepped planetary gear 90 including the teeth of the second gear portion 92, the stepped planetary gear 90 is configured by stacking metal thin plate gears in phase. Has also been proposed. However, such a stepped planetary gear 90 has a complicated structure and requires high-precision assembly for arranging the first gear portion 91 and the second gear portion 92 in the same phase.
また、第１歯車部９１及び第２歯車部９２の歯数差が零であることで、高減速化し過ぎると、歯の相互間の滑りが増加して効率が低下することになる。
なお、特許文献２に記載された遊星歯車減速機構では、ピッチ円の直径及び歯数が共に同等に設定された第１歯車部及び第２歯車部を有する段付遊星歯車が提案されている。そして、第１歯車部に噛合する固定リングギヤ及び第２歯車部に噛合する可動リングギヤの歯数差が「１」に設定されている。
Further, since the difference in the number of teeth between the first gear portion 91 and the second gear portion 92 is zero, if the speed is reduced too much, slippage between teeth increases and efficiency decreases.
In the planetary gear speed reduction mechanism described in Patent Document 2, a stepped planetary gear having a first gear portion and a second gear portion in which both the diameter and the number of teeth of a pitch circle are set to be equal has been proposed. The difference in the number of teeth between the fixed ring gear meshing with the first gear portion and the movable ring gear meshing with the second gear portion is set to “1”.
この場合、第１歯車部及び第２歯車部のモジュールが同等に設定されていることで、それらの強度も同等になる。また、固定リングギヤ及び可動リングギヤの歯数差を「１」に設定したことで、第１歯車部に噛合する太陽歯車を入力軸とし、第２歯車部に噛合する可動リングギヤを出力軸とした場合、太陽歯車の回転速度を著しく減速させて可動リングギヤから出力できることが期待される。さらに、段付遊星歯車の個数が「４」に設定されていることで、高減速化に伴い出力トルクが増加したとしても、所要の強度が確保される。 In this case, since the modules of the first gear unit and the second gear unit are set to be equal, their strengths are also equal. In addition, when the difference in the number of teeth between the fixed ring gear and the movable ring gear is set to “1”, the sun gear meshing with the first gear portion is used as the input shaft, and the movable ring gear meshing with the second gear portion is used as the output shaft. It is expected that the rotational speed of the sun gear can be significantly reduced and output from the movable ring gear. Furthermore, since the number of stepped planetary gears is set to “4”, the required strength is ensured even if the output torque increases as the speed is reduced.
しかしながら、通常、固定リングギヤ及び可動リングギヤの歯数差は、遊星歯車の個数の整数倍に設定される。特許文献２では、固定リングギヤ及び可動リングギヤの歯数差を「１」で実現するために、４つの段付遊星歯車の全てが固定リングギヤ及び可動リングギヤに噛合するように各々の第１歯車部及び第２歯車部間に位相差が設定されている。具体的には、４つの段付遊星歯車における各々の第１歯車部及び第２歯車部間の位相差は、「０」、「１／４」、「２／４」、「３／４」に設定されている。 However, the number of teeth difference between the fixed ring gear and the movable ring gear is usually set to an integral multiple of the number of planetary gears. In Patent Document 2, in order to realize the difference in the number of teeth of the fixed ring gear and the movable ring gear by “1”, the first gear portions and the four stepped planetary gears are respectively engaged with the fixed ring gear and the movable ring gear. A phase difference is set between the second gear portions. Specifically, the phase difference between the first gear portion and the second gear portion of the four stepped planetary gears is “0”, “1/4”, “2/4”, “3/4”. Is set to
従って、これら４つの段付遊星歯車の製造自体に高精度が要求されるとともに、４つの段付遊星歯車を所定の位置に配置するための高精度な組付けが要求される。なお、第１歯車部及び第２歯車部の歯数差が零で高減速化し過ぎると、歯の相互間の滑りが増加して効率が低下することは特許文献１と同様である。 Therefore, high precision is required for the manufacture of these four stepped planetary gears, and high precision assembly for arranging the four stepped planetary gears at predetermined positions is required. As in Patent Document 1, if the difference in the number of teeth between the first gear portion and the second gear portion is zero and the gear is excessively decelerated, slippage between teeth increases and efficiency decreases.
本発明の目的は、強度を損ねることなく、より簡易な構造で高減速化を実現することができる遊星歯車減速機構を提供することにある。 An object of the present invention is to provide a planetary gear speed reduction mechanism that can realize high speed reduction with a simpler structure without impairing strength.
上記問題点を解決するために、請求項１に記載の発明は、入力軸となる太陽歯車と、前記太陽歯車と同軸に配置された固定リングギヤと、前記太陽歯車と前記固定リングギヤとに噛合する第１歯車部、及び該第１歯車部よりも小径の第２歯車部を有する段付遊星歯車と、前記段付遊星歯車を回転自在に支持するとともに前記段付遊星歯車を前記太陽歯車の周囲で公転自在に支持するキャリアと、前記太陽歯車と同軸に配置され、前記第２歯車部と噛合して出力軸となる可動リングギヤとを備え、前記第１歯車部及び前記第２歯車部の歯数差を「４」に設定したことを要旨とする。 In order to solve the above problems, the invention according to claim 1 is engaged with a sun gear serving as an input shaft, a fixed ring gear disposed coaxially with the sun gear, and the sun gear and the fixed ring gear. A stepped planetary gear having a first gear part and a second gear part having a smaller diameter than the first gear part; and the stepped planetary gear is rotatably supported around the sun gear. And a movable ring gear which is arranged coaxially with the sun gear and meshes with the second gear portion to serve as an output shaft, and has teeth of the first gear portion and the second gear portion. The gist is that the number difference is set to “4”.
このタイプの遊星歯車減速機構（いわゆる３Ｋ型の遊星歯車減速機構）では、前記太陽歯車を入力軸とし、前記可動リングギヤを出力軸とした場合、前記第１歯車部及び前記第２歯車部の歯数差が少ないほど、前記太陽歯車の回転速度を著しく減速させて前記可動リングギヤから出力することが可能である。同構成によれば、前記第１歯車部及び前記第２歯車部の歯数差を「４」に設定したことで、前記太陽歯車の回転速度を十分に減速させて前記可動リングギヤから出力することができる。また、前記第１歯車部及び前記第２歯車部の歯数差が「４」であることで、小径側である前記第２歯車部の歯のモジュールが小さくなることを抑えることができ、該第２歯車部の強度が低くなることを抑えることができる。また、前記段付遊星歯車は、歯数差が「４」に設定された前記第１歯車部及び前記第２歯車部の２段構造であって、従来形態のように強度確保のために金属製の薄板歯車を位相を合わせて積層したり、複数の段付遊星歯車の各々の第１歯車部及び第２歯車部間に複雑な位相差を設定したりする必要もない。 In this type of planetary gear reduction mechanism (so-called 3K type planetary gear reduction mechanism), when the sun gear is used as an input shaft and the movable ring gear is used as an output shaft, teeth of the first gear portion and the second gear portion are used. As the number difference is smaller, the rotational speed of the sun gear can be remarkably reduced and output from the movable ring gear. According to the same configuration, the difference in the number of teeth of the first gear portion and the second gear portion is set to “4”, so that the rotational speed of the sun gear is sufficiently reduced and output from the movable ring gear. Can do. Further, since the difference in the number of teeth of the first gear portion and the second gear portion is “4”, it is possible to suppress the tooth module of the second gear portion on the small diameter side from being reduced, It can suppress that the intensity | strength of a 2nd gear part becomes low. Further, the stepped planetary gear has a two-stage structure of the first gear portion and the second gear portion in which the difference in the number of teeth is set to “4”. There is no need to stack thin plate gears made of the same phase or set a complicated phase difference between the first gear portion and the second gear portion of each of the plurality of stepped planetary gears.
請求項２に記載の発明は、請求項１に記載の遊星歯車減速機構において、前記第１歯車部の歯元円の直径は、前記第２歯車部の歯先円の直径以上に設定されていることを要旨とする。 According to a second aspect of the present invention, in the planetary gear speed reduction mechanism according to the first aspect, the diameter of the root circle of the first gear portion is set to be greater than or equal to the diameter of the tip circle of the second gear portion. It is a summary.
同構成によれば、前記第１歯車部の歯及び前記第２歯車部の歯が、前記段付遊星歯車の軸線方向に重なって配置されることがない。従って、前記段付遊星歯車の構造をより簡素化することができ、その製造工数を削減することができる。 According to this configuration, the teeth of the first gear portion and the teeth of the second gear portion are not arranged so as to overlap in the axial direction of the stepped planetary gear. Therefore, the structure of the stepped planetary gear can be further simplified, and the number of manufacturing steps can be reduced.
請求項３に記載の発明は、請求項１又は２に記載の遊星歯車減速機構において、前記段付遊星歯車の個数は「２」又は「４」であることを要旨とする。
同構成によれば、例えば前記段付遊星歯車の個数が「２」である場合には、部品点数を削減することができる。一方、前記段付遊星歯車の個数が「４」である場合には、出力トルクが大きいときにもこれら４個の段付遊星歯車の協働で所要の強度を確保することができる。
The gist of the invention described in claim 3 is that, in the planetary gear reduction mechanism according to claim 1 or 2, the number of the stepped planetary gears is “2” or “4”.
According to this configuration, for example, when the number of stepped planetary gears is “2”, the number of parts can be reduced. On the other hand, when the number of stepped planetary gears is “4”, the required strength can be ensured by the cooperation of the four stepped planetary gears even when the output torque is large.
請求項４に記載の発明は、請求項３に記載の遊星歯車減速機構において、前記第１歯車部の歯数及び前記第２歯車部の歯数が共に「４」の整数倍に設定されており、前記第１歯車部の歯及び前記第２歯車部の歯の位相が一致する、前記段付遊星歯車の軸線を中心とする周方向に等角度間隔で配置される四箇所のうちの少なくとも一箇所に、組付け時の位相合わせ用の被係合部を設けたことを要旨とする。 According to a fourth aspect of the present invention, in the planetary gear speed reduction mechanism according to the third aspect, the number of teeth of the first gear portion and the number of teeth of the second gear portion are both set to an integral multiple of “4”. And at least of the four positions arranged at equiangular intervals in the circumferential direction around the axis of the stepped planetary gear, the phases of the teeth of the first gear portion and the teeth of the second gear portion coincide with each other. The gist is that an engaged portion for phase alignment at the time of assembly is provided at one place.
同構成によれば、前記キャリアに支持された２個又は４個の前記段付遊星歯車を前記固定リングギヤ又は前記可動リングギヤに組み付ける際、例えばそれらの位相合わせ用のジグに設けられた係合部を全ての前記段付遊星歯車の前記被係合部に係合させることで、これら段付遊星歯車の位相をそろえて前記キャリア部材を組み付けることができる。このため、前記キャリア部材の組付性を向上させることができる。特に、各段付遊星歯車の複数箇所に前記被係合部を配設する場合、位相合わせ用のジグに設けられた係合部を任意の前記被係合部に係合させるための位置調整に要する前記段付遊星歯車の回転量を減らすことができる。 According to this configuration, when assembling the two or four stepped planetary gears supported by the carrier to the fixed ring gear or the movable ring gear, for example, the engaging portion provided in the phase matching jig Is engaged with the engaged portions of all the stepped planetary gears, so that the carrier members can be assembled with the phases of these stepped planetary gears aligned. For this reason, the assembling property of the carrier member can be improved. In particular, when the engaged portions are disposed at a plurality of locations on each stepped planetary gear, the position adjustment for engaging the engaging portions provided on the phase matching jig with any of the engaged portions. The amount of rotation of the stepped planetary gear required for the above can be reduced.
本発明では、強度を損ねることなく、より簡易な構造で高減速化を実現することができる遊星歯車減速機構を提供することができる。 According to the present invention, it is possible to provide a planetary gear speed reduction mechanism that can realize a high speed reduction with a simpler structure without impairing strength.
図１〜図５を参照して本発明の一実施形態について説明する。
図１に示すように、いわゆる３Ｋ型の遊星歯車減速機構１０は、入力軸となる太陽歯車１１と、該太陽歯車１１と同軸に配置された固定リングギヤ１２と、キャリア部材１３と、太陽歯車１１と同軸に配置され出力軸となる可動リングギヤ１４とを備えて構成される。
An embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, a so-called 3K type planetary gear reduction mechanism 10 includes a sun gear 11 serving as an input shaft, a fixed ring gear 12 arranged coaxially with the sun gear 11, a carrier member 13, and a sun gear 11. And a movable ring gear 14 which is arranged coaxially and serves as an output shaft.
太陽歯車１１は、その軸線方向に沿って中心線の延びる略円柱状に成形されており、その先端部に外歯車１１ａが形成されている。この太陽歯車１１は、例えばモータ等の駆動部材（図示略）に駆動連結されている。 The sun gear 11 is formed in a substantially cylindrical shape having a center line extending along the axial direction, and an external gear 11a is formed at the tip of the sun gear 11. The sun gear 11 is drivingly connected to a driving member (not shown) such as a motor.
固定リングギヤ１２は、その軸線方向に沿って中心線の延びる略円筒状に成形されており、その軸線方向一側（太陽歯車１１に近い側）の内周部には内歯車１２ａが形成されている。また、図２に併せ示すように、固定リングギヤ１２の軸線方向他側（太陽歯車１１から遠い側）の内周部には、段差１２ｂを介して拡開された軸受部１２ｃが形成されている。なお、軸線方向において、内歯車１２ａの位置は、太陽歯車１１の外歯車１１ａの位置に略一致している。 The fixed ring gear 12 is formed in a substantially cylindrical shape having a center line extending along the axial direction, and an internal gear 12a is formed on an inner peripheral portion on one side in the axial direction (side closer to the sun gear 11). Yes. In addition, as shown in FIG. 2, a bearing portion 12 c that is expanded via a step 12 b is formed on the inner peripheral portion on the other side in the axial direction of the fixed ring gear 12 (the side far from the sun gear 11). . Note that, in the axial direction, the position of the internal gear 12 a substantially coincides with the position of the external gear 11 a of the sun gear 11.
図１に示すように、キャリア部材１３は、太陽歯車１１の軸線を中心とする互いに相反する径方向の位置に配置された２個の段付遊星歯車２０と、これら段付遊星歯車２０を回転自在に支持するとともに該段付遊星歯車２０を太陽歯車１１の周囲で公転自在に支持する一対のキャリア２３，２４とを備える。そして、各段付遊星歯車２０は、その軸線方向一側及び他側（太陽歯車１１に近い側及びその反対側）に第１歯車部２１及び該第１歯車部２１よりも小径の第２歯車部２２を有する。軸線方向において、第１歯車部２１の位置は、太陽歯車１１の外歯車１１ａ（及び固定リングギヤ１２の内歯車１２ａ）の位置に略一致しており、第１歯車部２１は、外歯車１１ａ及び内歯車１２ａに噛合する。なお、軸線方向において、第２歯車部２２の位置は、固定リングギヤ１２の軸受部１２ｃの位置に含まれている。 As shown in FIG. 1, the carrier member 13 rotates two stepped planetary gears 20 arranged at mutually opposite radial positions around the axis of the sun gear 11, and these stepped planetary gears 20. A pair of carriers 23 and 24 that support the stepped planetary gear 20 in a freely revolving manner around the sun gear 11 are provided. Each stepped planetary gear 20 includes a first gear portion 21 and a second gear having a smaller diameter than the first gear portion 21 on one side and the other side in the axial direction (the side close to the sun gear 11 and the opposite side). Part 22. In the axial direction, the position of the first gear portion 21 substantially coincides with the position of the external gear 11a of the sun gear 11 (and the internal gear 12a of the fixed ring gear 12), and the first gear portion 21 includes the external gear 11a and It meshes with the internal gear 12a. In the axial direction, the position of the second gear portion 22 is included in the position of the bearing portion 12 c of the fixed ring gear 12.
両キャリア２３，２４は、太陽歯車１１の軸線方向に重ねられて、例えばボルト−ナットからなる締結具２５により締結されており、各々の有する略蝶型の支持壁部２３ａ，２４ａにより各段付遊星歯車２０をその軸線方向に沿って挟み込む。そして、各段付遊星歯車２０は、両支持壁部２３ａ，２４ａと共にその軸線方向に支持軸２６が貫通することで、キャリア２３，２４に回転自在に支持されている。 Both carriers 23 and 24 are overlapped in the axial direction of the sun gear 11 and fastened by a fastener 25 made of, for example, a bolt-nut, and each stepped by the substantially butterfly-shaped support wall portions 23a and 24a. The planetary gear 20 is sandwiched along the axial direction. Each stepped planetary gear 20 is rotatably supported by the carriers 23 and 24 by the support shaft 26 passing through the support wall portions 23a and 24a in the axial direction thereof.
可動リングギヤ１４は、その軸線方向に沿って中心線の延びる有底略円筒状に成形されており、その外径は固定リングギヤ１２の軸受部１２ｃの内径と同等に設定されている。この可動リングギヤ１４は、固定リングギヤ１２の軸受部１２ｃに回転自在に装着されている。可動リングギヤ１４の内周部には、内歯車１４ａが形成されている。軸線方向において、内歯車１４ａの位置は、段付遊星歯車２０の第２歯車部２２の位置に略一致しており、内歯車１４ａは、第２歯車部２２に噛合する。 The movable ring gear 14 is formed in a substantially bottomed cylindrical shape whose center line extends along the axial direction, and the outer diameter thereof is set to be equal to the inner diameter of the bearing portion 12 c of the fixed ring gear 12. The movable ring gear 14 is rotatably mounted on the bearing portion 12 c of the fixed ring gear 12. An internal gear 14 a is formed on the inner peripheral portion of the movable ring gear 14. In the axial direction, the position of the internal gear 14 a substantially coincides with the position of the second gear portion 22 of the stepped planetary gear 20, and the internal gear 14 a meshes with the second gear portion 22.
なお、可動リングギヤ１４には、その軸線方向に沿って略柱状の出力部１４ｂが突設されている。可動リングギヤ１４は、出力部１４ｂにおいて、適宜の被駆動部材（図示略）に連結されている。 The movable ring gear 14 is provided with a substantially columnar output portion 14b protruding along the axial direction. The movable ring gear 14 is connected to an appropriate driven member (not shown) at the output portion 14b.
そして、太陽歯車１１が駆動されると、その回転がキャリア部材１３を介して可動リングギヤ１４へと伝達される。これにより、太陽歯車１１の回転速度が十分に減速されて、可動リングギヤ１４から出力される。 When the sun gear 11 is driven, the rotation is transmitted to the movable ring gear 14 through the carrier member 13. As a result, the rotational speed of the sun gear 11 is sufficiently reduced and output from the movable ring gear 14.
ここで、太陽歯車１１、固定リングギヤ１２、第１歯車部２１、第２歯車部２２及び可動リングギヤ１４の歯数についてその一例を説明する。
図３に示すように、本実施形態では、太陽歯車１１の歯数は「１４」に、固定リングギヤ１２（内歯車１２ａ）の歯数は「７２」に、第１歯車部２１の歯数は「２８」に、第２歯車部２２の歯数は「２４」に、可動リングギヤ１４の歯数は「６８」に設定されている。つまり、太陽歯車１１、固定リングギヤ１２、第１歯車部２１、第２歯車部２２及び可動リングギヤ１４の歯数が全て「２」の整数倍に設定されている。より厳密には、太陽歯車１１以外の歯数が全て「４」の整数倍に設定されている。また、第１歯車部２１及び第２歯車部２２の歯数差は「４（＝２８−２４）」に設定されている。
Here, an example of the number of teeth of the sun gear 11, the fixed ring gear 12, the first gear portion 21, the second gear portion 22, and the movable ring gear 14 will be described.
As shown in FIG. 3, in this embodiment, the number of teeth of the sun gear 11 is “14”, the number of teeth of the fixed ring gear 12 (internal gear 12a) is “72”, and the number of teeth of the first gear portion 21 is “28”, the number of teeth of the second gear portion 22 is set to “24”, and the number of teeth of the movable ring gear 14 is set to “68”. That is, the number of teeth of the sun gear 11, the fixed ring gear 12, the first gear portion 21, the second gear portion 22, and the movable ring gear 14 are all set to an integer multiple of “2.” More precisely, the number of teeth other than the sun gear 11 is set to an integral multiple of “4”. The difference in the number of teeth between the first gear portion 21 and the second gear portion 22 is set to “4 (= 28−24)”.
なお、太陽歯車１１、固定リングギヤ１２、第１歯車部２１、第２歯車部２２及び可動リングギヤ１４の歯は、標準歯車相当で互いに同一のモジュールとなっている。そして、第１歯車部２１は正転位されており、第２歯車部２２は負転位されている。これにより、標準歯車相当で互いに同一のモジュールとなる第１歯車部２１及び第２歯車部２２の歯数差が「４」であっても、第１歯車部２１の歯元円の直径は、第２歯車部２２の歯先円の直径以上に設定されている。従って、第１歯車部２１の歯及び第２歯車部２２の歯が、段付遊星歯車２０の軸線方向に重なって配置されることはない。 The teeth of the sun gear 11, the fixed ring gear 12, the first gear portion 21, the second gear portion 22, and the movable ring gear 14 are equivalent to standard gears and are the same module. And the 1st gear part 21 is forward-shifted, and the 2nd gear part 22 is negatively shifted. Thereby, even if the difference in the number of teeth of the first gear portion 21 and the second gear portion 22 corresponding to the standard gear and the same module is “4”, the diameter of the root circle of the first gear portion 21 is The diameter is set to be equal to or larger than the diameter of the tip circle of the second gear portion 22. Accordingly, the teeth of the first gear portion 21 and the teeth of the second gear portion 22 are not arranged in the axial direction of the stepped planetary gear 20.
次に、本実施形態の作用について説明する。
本実施形態では、第１歯車部２１及び第２歯車部２２の歯数差を「４」に設定したことで、太陽歯車１１の回転速度を十分に減速させて可動リングギヤ１４から出力することができる。すなわち、図３に示した歯数の設定により、ギヤ比６６．４の高減速化が実現されている。
Next, the operation of this embodiment will be described.
In this embodiment, by setting the difference in the number of teeth of the first gear portion 21 and the second gear portion 22 to “4”, the rotational speed of the sun gear 11 can be sufficiently reduced and output from the movable ring gear 14. it can. That is, a high speed reduction with a gear ratio of 66.4 is realized by setting the number of teeth shown in FIG.
なお、例えば歯数差が「５」であれば、標準歯車相当で段付遊星歯車の第１歯車部の歯及び第２歯車部の歯のモジュールが同一であっても、それらが段付遊星歯車の軸線方向に重なることはなくなるが、段付遊星歯車が５個必要になってしまう。一方、段付遊星歯車の個数を「３」にするためには歯数差が「６」になってしまう。歯数差が「６」の場合、例えば太陽歯車の歯数が「１８」に、固定リングギヤの歯数が「７２」に、第１歯車部の歯数が「２７」に、第２歯車部の歯数が「２１」に、可動リングギヤの歯数が「６６」に設定されていると、ギヤ比３３になってしまう。また、歯数差が「３」以下の場合には、標準歯車相当で段付遊星歯車の第１歯車部の歯よりも第２歯車部の歯のモジュールを小さくしない限り、第１歯車部の歯及び第２歯車部の歯が段付遊星歯車の軸線方向に重なってしまう。また、歯数差が小さい分、高減速化可能であるが、歯の相互間の滑りが増加して効率が低下することになる。 For example, if the difference in the number of teeth is “5”, even if the module of the tooth of the first gear portion and the tooth of the second gear portion of the stepped planetary gear is the same as that of the standard gear, they are the stepped planetary gears. Although it does not overlap in the axial direction of the gear, five stepped planetary gears are required. On the other hand, in order to set the number of stepped planetary gears to “3”, the difference in the number of teeth becomes “6”. When the difference in the number of teeth is “6”, for example, the number of teeth of the sun gear is “18”, the number of teeth of the fixed ring gear is “72”, the number of teeth of the first gear portion is “27”, and the second gear portion. If the number of teeth is set to “21” and the number of teeth of the movable ring gear is set to “66”, the gear ratio is 33. Further, when the difference in the number of teeth is “3” or less, unless the tooth module of the second gear portion is made smaller than the teeth of the first gear portion of the stepped planetary gear corresponding to the standard gear, The teeth and the teeth of the second gear portion overlap in the axial direction of the stepped planetary gear. Further, although the difference in the number of teeth is small, high speed reduction is possible, but the slip between the teeth increases and the efficiency is lowered.
次に、本実施形態の組付方法について説明する。
既述のように、第１歯車部２１の歯数及び第２歯車部２２の歯数が共に「４」の整数倍であり、第１歯車部２１及び第２歯車部２２の歯数差が「４」であることで、図４に示すように、第１歯車部２１の歯及び第２歯車部２２の歯は、段付遊星歯車２０の軸線を中心とする周方向に等角度（９０°）間隔で配置される四箇所で位相が一致している。
Next, the assembly method of this embodiment will be described.
As described above, the number of teeth of the first gear portion 21 and the number of teeth of the second gear portion 22 are both integer multiples of “4”, and the difference in the number of teeth of the first gear portion 21 and the second gear portion 22 is as follows. By being “4”, as shown in FIG. 4, the teeth of the first gear portion 21 and the teeth of the second gear portion 22 are equiangular in the circumferential direction around the axis of the stepped planetary gear 20 (90 °) The phase is in agreement at the four locations arranged at intervals.
従って、両段付遊星歯車２０において、位相の一致する第１歯車部２１の歯及び第２歯車部２２の歯が、太陽歯車１１の軸線を中心とする径方向に最も離れて配置されているとき、太陽歯車１１は、当該径方向に沿って外歯車１１ａの歯溝が配置されることで両段付遊星歯車２０（第１歯車部２１）に噛合可能である。同様に、固定リングギヤ１２は、当該径方向に沿って内歯車１２ａの歯溝が配置されることで両段付遊星歯車２０（第１歯車部２１）に噛合可能であり、可動リングギヤ１４は、当該径方向に沿って内歯車１４ａの歯溝が配置されることで両段付遊星歯車２０（第２歯車部２２）に噛合可能である。つまり、キャリア部材１３は、第１歯車部２１の歯及び第２歯車部２２の歯の位相の一致する箇所の角度位置を利用して両段付遊星歯車２０の位置決めをしておくことで、可動リングギヤ１４等への組付けがより円滑化される。 Therefore, in the two-stage planetary gear 20, the teeth of the first gear portion 21 and the teeth of the second gear portion 22 that are in phase with each other are arranged farthest in the radial direction around the axis of the sun gear 11. At this time, the sun gear 11 can mesh with the stepped planetary gear 20 (the first gear portion 21) by arranging the tooth groove of the external gear 11a along the radial direction. Similarly, the fixed ring gear 12 can mesh with both stepped planetary gears 20 (first gear portion 21) by arranging the tooth grooves of the internal gear 12a along the radial direction. By arranging the tooth groove of the internal gear 14a along the radial direction, it is possible to mesh with the two-stage planetary gear 20 (second gear portion 22). In other words, the carrier member 13 positions the planetary gear 20 with the two steps by using the angular position of the position where the teeth of the first gear portion 21 and the teeth of the second gear portion 22 match. Assembly to the movable ring gear 14 or the like is further smoothed.
本実施形態の段付遊星歯車２０には、第１歯車部２１の歯及び第２歯車部２２の歯の位相の一致する前記四箇所の角度位置に合わせて、第１歯車部２１側から４つの被係合部としての略円形の位相決め用穴２７が形成されている。これら位相決め用穴２７は、段付遊星歯車２０の軸線方向と平行に延びている。また、位相決め用穴２７は、キャリア部材１３（太陽歯車１１）の軸線を中心とする径方向に最も離れて配置されているとき、キャリア２３（支持壁部２３ａ）から露出している。 In the stepped planetary gear 20 of the present embodiment, 4 from the first gear portion 21 side according to the angular positions of the four positions where the teeth of the first gear portion 21 and the teeth of the second gear portion 22 match. A substantially circular phasing hole 27 is formed as one engaged portion. These phasing holes 27 extend in parallel to the axial direction of the stepped planetary gear 20. Further, the phase determining hole 27 is exposed from the carrier 23 (supporting wall portion 23a) when the phase determining hole 27 is disposed farthest in the radial direction around the axis of the carrier member 13 (sun gear 11).
ここで、キャリア部材１３を可動リングギヤ１４に組み付ける際には、図５（ａ）に示す略円筒状の位相決め用ジグ３０が利用される。この位相決め用ジグ３０は、キャリア部材１３（太陽歯車１１）の軸線を中心とする径方向に最も離れて配置される位相決め用穴２７に合わせてその外径及び内径がそれぞれ設定されており、両段付遊星歯車２０の当該位相決め用穴２７に嵌入可能な２つの係合部としての略円柱状の位相決め用ピン３１が突設されている。 Here, when the carrier member 13 is assembled to the movable ring gear 14, a substantially cylindrical phasing jig 30 shown in FIG. 5A is used. The phasing jig 30 has an outer diameter and an inner diameter set in accordance with a phasing hole 27 that is arranged farthest in the radial direction around the axis of the carrier member 13 (sun gear 11). A substantially cylindrical phasing pin 31 is protruded as two engaging portions that can be fitted into the phasing hole 27 of the stepped planetary gear 20.
そして、キャリア部材１３の組付けに際しては、両段付遊星歯車２０の一つの位相決め用穴２７がキャリア部材１３の軸線を中心とする径方向に最も離れるようにそれぞれ配置するとともに、キャリア部材１３の軸線方向及び位相決め用ジグ３０の軸線方向を一致させる。そして、当該軸線方向と平行に両段付遊星歯車２０の位相決め用穴２７及び位相決め用ジグ３０の両位相決め用ピン３１を対向させた状態で、キャリア部材１３及び位相決め用ジグ３０が近付くようにそれらを軸線方向に相対移動させる。 When the carrier member 13 is assembled, the carrier member 13 is arranged so that one phase determining hole 27 of the stepped planetary gear 20 is farthest away in the radial direction around the axis of the carrier member 13. And the axis direction of the phasing jig 30 are made to coincide with each other. The carrier member 13 and the phasing jig 30 are in a state where the phasing holes 27 of the stepped planetary gear 20 and the phasing pins 31 of the phasing jig 30 are opposed to each other in parallel to the axial direction. They are moved relative to each other in the axial direction so as to approach.
これにより、両段付遊星歯車２０の該当の位相決め用穴２７に、位相決め用ジグ３０の両位相決め用ピン３１が嵌入し、図５（ｂ）に示すように、両キャリア２３，２４に対する両段付遊星歯車２０の回転が共に係止される。このとき、両段付遊星歯車２０は、第１歯車部２１の歯及び第２歯車部２２の歯の位相の一致する一箇所が、キャリア部材１３の軸線を中心とする径方向に最も離れた状態で保持されることはいうまでもない。つまり、両段付遊星歯車２０は、位相決め用ジグ３０により位相が合わされた状態で保持されている。 As a result, the both phase determining pins 31 of the phase determining jig 30 are fitted into the corresponding phase determining holes 27 of the two-stage planetary gear 20, and as shown in FIG. The rotation of both stepped planetary gears 20 with respect to is locked together. At this time, in the two-stage planetary gear 20, one position where the teeth of the first gear portion 21 and the teeth of the second gear portion 22 coincide is most distant in the radial direction centered on the axis of the carrier member 13. Needless to say, it is held in a state. That is, the two-stage planetary gear 20 is held in a state in which the phases are matched by the phasing jig 30.
続いて、位相決め用ジグ３０に保持されたキャリア部材１３の軸線方向を可動リングギヤ１４の軸線方向に一致させるとともに、前記径方向に沿って内歯車１４ａの歯溝を配置させる。この状態で、キャリア部材１３及び可動リングギヤ１４が近付くようにそれらを軸線方向に相対移動させると、両段付遊星歯車２０（第２歯車部２２）の該当の歯が、対向する内歯車１４ａの歯溝に嵌合して、第２歯車部２２及び内歯車１４ａ（可動リングギヤ１４）が噛合する。 Subsequently, the axial direction of the carrier member 13 held by the phasing jig 30 is made to coincide with the axial direction of the movable ring gear 14, and the tooth grooves of the internal gear 14a are arranged along the radial direction. In this state, when the carrier member 13 and the movable ring gear 14 are relatively moved in the axial direction so as to approach each other, the corresponding teeth of the two-stage planetary gear 20 (second gear portion 22) are moved to the opposite inner gear 14a. The second gear portion 22 and the internal gear 14a (movable ring gear 14) are engaged with each other in the tooth gap.
その後、図５（ｃ）に示すように、キャリア部材１３から位相決め用ジグ３０を取り外すと、キャリア部材１３は、両キャリア２３，２４に対して両段付遊星歯車２０が回転可能な状態で可動リングギヤ１４に連結される。なお、太陽歯車１１及び固定リングギヤ１２は、可動リングギヤ１４に連結されたキャリア部材１３は前述の位相合わせで位相が合っているので、位相決め用ジグ３０を取外しても、該キャリア部材１３（及び可動リングギヤ１４）に円滑に組み付けることが可能である。 After that, when the phasing jig 30 is removed from the carrier member 13 as shown in FIG. 5 (c), the carrier member 13 is in a state in which the two-stage planetary gear 20 is rotatable with respect to both the carriers 23 and 24. Connected to the movable ring gear 14. The sun gear 11 and the fixed ring gear 12 are in phase with the carrier member 13 connected to the movable ring gear 14 by the above-described phase alignment. Therefore, even if the phase determination jig 30 is removed, the carrier member 13 (and It can be smoothly assembled to the movable ring gear 14).
以上詳述したように、本実施形態によれば、以下に示す効果が得られるようになる。
（１）本実施形態では、段付遊星歯車２０の第１歯車部２１及び第２歯車部２２の歯数差を「４」に設定したことで、太陽歯車１１の回転速度を十分に減速させて可動リングギヤ１４から出力することができる。また、第１歯車部２１及び第２歯車部２２の歯数差が「４」であることで、小径側である第２歯車部２２の歯のモジュールが小さくなることを抑えることができ、該第２歯車部２２の強度が低くなることを抑えることができる。また、段付遊星歯車２０は、歯数差が「４」に設定された第１歯車部２１及び第２歯車部２２の２段構造であって、従来形態のように強度確保のために金属製の薄板歯車を位相を合わせて積層したり、複数の段付遊星歯車の各々の第１歯車部及び第２歯車部間に複雑な位相差を設定したりする必要もない。
As described above in detail, according to the present embodiment, the following effects can be obtained.
(1) In this embodiment, by setting the difference in the number of teeth of the first gear portion 21 and the second gear portion 22 of the stepped planetary gear 20 to “4”, the rotational speed of the sun gear 11 is sufficiently reduced. Can be output from the movable ring gear 14. Further, since the difference in the number of teeth of the first gear portion 21 and the second gear portion 22 is “4”, it is possible to suppress the tooth module of the second gear portion 22 on the small diameter side from being reduced, It can suppress that the intensity | strength of the 2nd gear part 22 becomes low. Further, the stepped planetary gear 20 has a two-stage structure including a first gear portion 21 and a second gear portion 22 in which the difference in the number of teeth is set to “4”. There is no need to stack thin plate gears made of the same phase or set a complicated phase difference between the first gear portion and the second gear portion of each of the plurality of stepped planetary gears.
（２）本実施形態では、第１歯車部２１の歯元円の直径は、第２歯車部２２の歯先円の直径以上に設定されていることで、第１歯車部２１及び第２歯車部２２の歯が、段付遊星歯車２０の軸線方向に重なって配置されることがない。従って、段付遊星歯車２０の構造をより簡素化することができ、その製造工数を削減することができる。 (2) In the present embodiment, the diameter of the root circle of the first gear portion 21 is set to be equal to or larger than the diameter of the tip circle of the second gear portion 22, so that the first gear portion 21 and the second gear are set. The teeth of the portion 22 are not arranged overlapping the axial direction of the stepped planetary gear 20. Therefore, the structure of the stepped planetary gear 20 can be further simplified, and the number of manufacturing steps can be reduced.
特に、段付遊星歯車２０の工法として、型の片側で位相が決められる工法（樹脂射出成形・焼結）を選択することができる。従って、第１歯車部２１及び第２歯車部２２の位相を型で決めることができ、精度確保を容易に実現することができる。 In particular, as the construction method of the stepped planetary gear 20, a construction method (resin injection molding / sintering) in which the phase is determined on one side of the mold can be selected. Therefore, the phases of the first gear portion 21 and the second gear portion 22 can be determined by the mold, and accuracy can be easily ensured.
以上により、製造コストを削減することができる。
また、第１歯車部２１及び第２歯車部２２の位相を型で決めた場合、仮に第１歯車部２１及び第２歯車部２２の位相がずれていたとしても、当該ずれは全ての段付遊星歯車２０で共通であることで、該段付遊星歯車２０等の作動・性能への影響は実質的に皆無である。
As described above, the manufacturing cost can be reduced.
In addition, when the phases of the first gear portion 21 and the second gear portion 22 are determined by the mold, even if the phases of the first gear portion 21 and the second gear portion 22 are shifted, the shift is all stepped. Since it is common to the planetary gears 20, there is substantially no influence on the operation and performance of the stepped planetary gears 20 and the like.
（３）本実施形態では、段付遊星歯車２０の個数が「２」であることで、部品点数を削減することができ、ひいてはコストを削減することができる。
（４）本実施形態では、第１歯車部２１の歯及び第２歯車部２２の歯の位相が一致する、段付遊星歯車２０の軸線を中心とする周方向に等角度間隔（９０°）で配置される四箇所の全ての角度位置に合わせて、組付け時の位相合わせ用の位相決め用穴２７を設けた。従って、キャリア２３，２４に支持された２個の段付遊星歯車２０を可動リングギヤ１４に組み付ける際、位相決め用ジグ３０に設けられた２個の位相決め用ピン３１を両段付遊星歯車２０の位相決め用穴２７に係合させることで、これら段付遊星歯車２０の位相をそろえてキャリア部材１３を組み付けることができる。このため、キャリア部材１３の組付性を向上させることができる。
(3) In this embodiment, since the number of stepped planetary gears 20 is “2”, the number of parts can be reduced, and the cost can be reduced.
(4) In the present embodiment, equiangular intervals (90 °) in the circumferential direction centering on the axis of the stepped planetary gear 20 in which the teeth of the first gear portion 21 and the teeth of the second gear portion 22 match. The phase determining holes 27 for phase alignment at the time of assembling are provided in accordance with all the angular positions of the four positions arranged in FIG. Accordingly, when the two stepped planetary gears 20 supported by the carriers 23 and 24 are assembled to the movable ring gear 14, the two phase determining pins 31 provided on the phase determining jig 30 are connected to the two stepped planetary gears 20 respectively. The carrier member 13 can be assembled by aligning the phases of the stepped planetary gears 20 by engaging with the phase determining holes 27. For this reason, the assembling property of the carrier member 13 can be improved.
特に、各段付遊星歯車２０の四箇所に位相決め用穴２７を配設したことで、位相決め用ジグ３０に設けられた位相決め用ピン３１を任意の位相決め用穴２７に係合させるための位置調整に要する段付遊星歯車２０の回転量を減らすことができる。具体的には、例えば各段付遊星歯車２０の一箇所にのみ位相決め用穴２７を設けた場合には、位置調整に要する段付遊星歯車２０の回転量が最大で略１８０°になるのに対し、各段付遊星歯車２０の四箇所に位相決め用穴２７を配設したことで位置調整に要する段付遊星歯車２０の回転量が最大で略４５°に抑えられる。 In particular, since the phase determining holes 27 are provided at four locations of each stepped planetary gear 20, the phase determining pins 31 provided in the phase determining jig 30 are engaged with the arbitrary phase determining holes 27. Therefore, the amount of rotation of the stepped planetary gear 20 required for position adjustment can be reduced. Specifically, for example, when the phase determining hole 27 is provided only at one position of each stepped planetary gear 20, the rotation amount of the stepped planetary gear 20 required for position adjustment is approximately 180 ° at the maximum. On the other hand, the rotation amount of the stepped planetary gear 20 required for position adjustment is suppressed to about 45 ° at the maximum by arranging the phase determining holes 27 at the four positions of each stepped planetary gear 20.
（５）本実施形態では、位相決め用ジグ３０の位相決め用ピン３１を嵌入させる各段付遊星歯車２０の位相決め用穴２７を四箇所から選択できるため、両段付遊星歯車２０の位相合わせを円滑に行うことができる。 (5) In this embodiment, the phase determining hole 27 of each stepped planetary gear 20 into which the phase determining pin 31 of the phase determining jig 30 is fitted can be selected from four locations. Matching can be performed smoothly.
（６）本実施形態では、段付遊星歯車２０の第１歯車部２１を正転位したことでその歯の切下げを抑えることができ、第２歯車部２２を負転位したことでその歯の歯先尖りを抑えることができる。 (6) In the present embodiment, the first gear portion 21 of the stepped planetary gear 20 has been forwardly displaced, so that the teeth can be prevented from being cut down, and the second gear portion 22 has been negatively displaced, the teeth of the teeth. Sharpness can be suppressed.
なお、上記実施形態は以下のように変更してもよい。
・前記実施形態においては、段付遊星歯車２０の第１歯車部２１を正転位し、第２歯車部２２を負転位した。これに対し、第１歯車部２１の歯元円の直径が、第２歯車部２２の歯先円の直径以上になるのであれば、第１歯車部２１のみを正転位するようにしてもよいし、第２歯車部２２のみを負転位するようにしてもよい。あるいは、第１歯車部２１の転位量の方が第２歯車部２２の転位量よりも大きくなるように第１歯車部２１及び第２歯車部２２を共に正転位してもよい。
In addition, you may change the said embodiment as follows.
In the above-described embodiment, the first gear portion 21 of the stepped planetary gear 20 is forwardly shifted and the second gear portion 22 is negatively shifted. On the other hand, if the diameter of the root circle of the first gear portion 21 is equal to or larger than the diameter of the tip circle of the second gear portion 22, only the first gear portion 21 may be forwardly shifted. Only the second gear portion 22 may be negatively displaced. Alternatively, both the first gear portion 21 and the second gear portion 22 may be forwardly shifted so that the shift amount of the first gear portion 21 is larger than the shift amount of the second gear portion 22.
・前記実施形態において、位相決め用穴２７は、第１歯車部２１の歯及び第２歯車部２２の歯の位相が一致する、段付遊星歯車２０の軸線を中心とする周方向に等角度間隔（９０°）で配置される四箇所のうちの少なくとも一箇所の角度位置に合わせて設ければよい。この場合であっても、キャリア２３，２４に支持された２個の段付遊星歯車２０を可動リングギヤ１４に組み付ける際、位相決め用ジグ３０に設けられた２個の位相決め用ピン３１を両段付遊星歯車２０の当該位相決め用穴２７に係合させることで、これら段付遊星歯車２０の位相をそろえてキャリア部材１３を組み付けることができる。 -In the said embodiment, the phase determination hole 27 is equiangular in the circumferential direction centering on the axis line of the stepped planetary gear 20 with which the phase of the tooth | gear of the 1st gear part 21 and the tooth | gear of the 2nd gear part 22 corresponds. What is necessary is just to provide according to the angle position of at least one place of four places arrange | positioned by a space | interval (90 degrees). Even in this case, when the two stepped planetary gears 20 supported by the carriers 23 and 24 are assembled to the movable ring gear 14, the two phasing pins 31 provided on the phasing jig 30 are both attached. By engaging with the phase determining hole 27 of the stepped planetary gear 20, the carrier member 13 can be assembled with the phases of the stepped planetary gears 20 aligned.
なお、各段付遊星歯車２０の二箇所に位相決め用穴２７を配設する場合には、当該段付遊星歯車２０の軸線を中心とする径方向で対向する二箇所であることがより好ましい。これは、位相決め用ジグ３０に設けられた位相決め用ピン３１を任意の位相決め用穴２７に係合させるための位置調整に要する段付遊星歯車２０の回転量を減らすためである。 In the case where the phase determining holes 27 are provided at two locations on each stepped planetary gear 20, it is more preferable that the two locations are opposed in the radial direction around the axis of the stepped planetary gear 20. . This is to reduce the amount of rotation of the stepped planetary gear 20 required for position adjustment for engaging the phase determination pin 31 provided in the phase determination jig 30 with the arbitrary phase determination hole 27.
・前記実施形態においては、段付遊星歯車２０に位相決め用穴２７を設け、位相決め用ジグ３０に位相決め用ピン３１を設けた。これに対し、段付遊星歯車２０に被係合部としての位相決め用ピンを設け、位相決め用ジグ３０に位相決め用ピンの嵌入可能な係合部としての位相決め用穴を設けてもよい。 In the above-described embodiment, the phase determining hole 27 is provided in the stepped planetary gear 20, and the phase determining pin 31 is provided in the phase determining jig 30. On the other hand, the stepped planetary gear 20 may be provided with a phasing pin as an engaged portion, and the phasing jig 30 may be provided with a phasing hole as an engaging portion into which the phasing pin can be fitted. Good.
・前記実施形態においては、位相決め用ジグ３０により両キャリア２３，２４に対する両段付遊星歯車２０の回転が共に係止された状態のキャリア部材１３を、可動リングギヤ１４に組み付けた後に固定リングギヤ１２等を組み付けるようにした。これに対して、位相決め用ジグにより両キャリア２３，２４に対する両段付遊星歯車２０の回転が共に係止された状態のキャリア部材１３を、固定リングギヤ１２に組み付けた後に可動リングギヤ１４等を組み付けるようにしてもよい。ただし、キャリア部材１３を保持する位相決め用ジグは、固定リングギヤ１２との干渉を避けるために第２歯車部２２側から両段付遊星歯車２０の回転を係止することがより好ましい。 In the above embodiment, the fixed ring gear 12 is assembled after the carrier member 13 in a state where the rotation of the two-stage planetary gears 20 with respect to both the carriers 23 and 24 is locked together by the phasing jig 30 is assembled to the movable ring gear 14. And so on. On the other hand, the carrier member 13 in a state where the rotation of the two-stage planetary gears 20 with respect to both the carriers 23 and 24 is locked together by the phasing jig is assembled to the fixed ring gear 12, and then the movable ring gear 14 and the like are assembled. You may do it. However, it is more preferable that the phasing jig for holding the carrier member 13 stops the rotation of the two-stage planetary gear 20 from the second gear portion 22 side in order to avoid interference with the fixed ring gear 12.
・前記実施形態において、段付遊星歯車の個数は「４」であってもよい。ただし、この場合、太陽歯車、固定リングギヤ、第１歯車部、第２歯車部及び可動リングギヤの歯数が全て「４」の整数倍に設定されている必要がある。これにより、太陽歯車の回転を、等角度（９０°）間隔に配設された４個の段付遊星歯車等を介して可動リングギヤから出力することができる。この場合、出力トルクが大きいときにもこれら４個の段付遊星歯車の協働で所要の強度を確保することができる。 In the embodiment, the number of stepped planetary gears may be “4”. However, in this case, the number of teeth of the sun gear, the fixed ring gear, the first gear portion, the second gear portion, and the movable ring gear must all be set to an integer multiple of “4”. As a result, the rotation of the sun gear can be output from the movable ring gear via the four stepped planetary gears and the like disposed at equiangular (90 °) intervals. In this case, even when the output torque is large, the required strength can be ensured by the cooperation of these four stepped planetary gears.
なお、キャリア部材の組付けに際し、位相決め用ジグによりキャリアに対する４個の段付遊星歯車の全ての回転を係止する場合には、これら４個の段付遊星歯車の一つの位相決め用穴がキャリア部材の軸線を中心とする径方向に最も離れるようにそれぞれ配置する。そして、これら位相決め用穴に対応して位相決め用ジグに配設された４個の位相決め用ピンを該当の位相決め用穴に嵌入すればよい。段付遊星歯車及び位相決め用ジグと、位相決め用穴及び位相決め用ピンの配置関係は逆であってもよい。 When the carrier member is assembled, when the rotation of the four stepped planetary gears relative to the carrier is locked by the phase determination jig, one phase determination hole of the four stepped planetary gears is used. Are arranged so as to be farthest in the radial direction around the axis of the carrier member. Then, the four phasing pins arranged in the phasing jig corresponding to these phasing holes may be inserted into the phasing holes. The arrangement relationship between the stepped planetary gear and the phasing jig, the phasing hole and the phasing pin may be reversed.
・前記実施形態において、標準歯車相当で第１歯車部２１及び第２歯車部２２が互いに同一のモジュールとなるのであれば、第１歯車部２１の歯及び第２歯車部２２の歯が、段付遊星歯車２０の軸線方向に重なって配置されていてもよい。 In the above embodiment, if the first gear portion 21 and the second gear portion 22 are equivalent to a standard gear and are in the same module, the teeth of the first gear portion 21 and the teeth of the second gear portion 22 are stepped. It may be arranged so as to overlap the axial direction of the attached planetary gear 20.
・前記実施形態において、太陽歯車、固定リングギヤ、第１歯車部、第２歯車部及び可動リングギヤの歯数の設定は一例である。
次に、上記実施形態及び別例から把握できる技術的思想について以下に追記する。
-In the said embodiment, the setting of the number of teeth of a sun gear, a fixed ring gear, a 1st gear part, a 2nd gear part, and a movable ring gear is an example.
Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
（イ）請求項１又は２に記載の遊星歯車減速機構において、
前記太陽歯車、前記固定リングギヤ、前記第１歯車部、前記第２歯車部及び前記可動リングギヤの全ての歯数が「４」の整数倍に設定されていることを特徴とする遊星歯車減速機構。同構成によれば、前記段付遊星歯車の個数として、「２」又は「４」を選択することができる。そして、前記段付遊星歯車の個数として「２」を選択した場合には部品点数を削減することができ、「４」を選択した場合にはこれら４個の段付遊星歯車の協働で所要の強度を確保することができる。
(A) In the planetary gear reduction mechanism according to claim 1 or 2,
The planetary gear speed reduction mechanism, wherein the number of teeth of the sun gear, the fixed ring gear, the first gear portion, the second gear portion, and the movable ring gear is set to an integral multiple of “4”. According to this configuration, “2” or “4” can be selected as the number of the stepped planetary gears. When “2” is selected as the number of the stepped planetary gears, the number of parts can be reduced. When “4” is selected, the four stepped planetary gears cooperate with each other. The strength of the can be ensured.
（ロ）請求項１又は２に記載の遊星歯車減速機構において、
前記太陽歯車、前記固定リングギヤ、前記第１歯車部、前記第２歯車部及び前記可動リングギヤの全ての歯数が「２」の整数倍（「４」の非整数倍）に設定されていることを特徴とする遊星歯車減速機構。同構成によれば、前記段付遊星歯車の個数は「２」となり、部品点数を削減することができる。
(B) In the planetary gear reduction mechanism according to claim 1 or 2,
The number of teeth of the sun gear, the fixed ring gear, the first gear portion, the second gear portion, and the movable ring gear is set to an integer multiple of “2” (non-integer multiple of “4”). Planetary gear reduction mechanism characterized by this. According to this configuration, the number of stepped planetary gears is “2”, and the number of parts can be reduced.
１０…遊星歯車減速機構、１１…太陽歯車、１２…固定リングギヤ、１４…可動リングギヤ、２０…段付遊星歯車、２１…第１歯車部、２２…第２歯車部、２３，２４…キャリア、２７…位相決め用穴（被係合部）、３０…位相決め用ジグ、３１…位相決め用ピン（係合部）。 DESCRIPTION OF SYMBOLS 10 ... Planetary gear reduction mechanism, 11 ... Sun gear, 12 ... Fixed ring gear, 14 ... Movable ring gear, 20 ... Stepped planetary gear, 21 ... First gear part, 22 ... Second gear part, 23, 24 ... Carrier, 27 ... phase determining hole (engaged portion), 30 ... phase determining jig, 31 ... phase determining pin (engaging portion).
Claims (4)
前記太陽歯車と同軸に配置された固定リングギヤと、
前記太陽歯車と前記固定リングギヤとに噛合する第１歯車部、及び該第１歯車部よりも小径の第２歯車部を有する段付遊星歯車と、
前記段付遊星歯車を回転自在に支持するとともに前記段付遊星歯車を前記太陽歯車の周囲で公転自在に支持するキャリアと、
前記太陽歯車と同軸に配置され、前記第２歯車部と噛合して出力軸となる可動リングギヤとを備え、
前記第１歯車部及び前記第２歯車部の歯数差を「４」に設定したことを特徴とする遊星歯車減速機構。 A sun gear as an input shaft,
A fixed ring gear arranged coaxially with the sun gear;
A stepped planetary gear having a first gear portion meshing with the sun gear and the fixed ring gear, and a second gear portion having a smaller diameter than the first gear portion;
A carrier that rotatably supports the stepped planetary gear and supports the stepped planetary gear so as to revolve around the sun gear;
A movable ring gear disposed coaxially with the sun gear and meshing with the second gear portion to serve as an output shaft;
A planetary gear reduction mechanism, wherein a difference in the number of teeth of the first gear portion and the second gear portion is set to “4”.
前記第１歯車部の歯元円の直径は、前記第２歯車部の歯先円の直径以上に設定されていることを特徴とする遊星歯車減速機構。 The planetary gear reduction mechanism according to claim 1,
The planetary gear speed reduction mechanism, wherein a diameter of a root circle of the first gear portion is set to be equal to or larger than a diameter of a tip circle of the second gear portion.
前記段付遊星歯車の個数は「２」又は「４」であることを特徴とする遊星歯車減速機構。 In the planetary gear reduction mechanism according to claim 1 or 2,
The planetary gear speed reduction mechanism, wherein the number of stepped planetary gears is “2” or “4”.
前記第１歯車部の歯数及び前記第２歯車部の歯数が共に「４」の整数倍に設定されており、
前記第１歯車部の歯及び前記第２歯車部の歯の位相が一致する、前記段付遊星歯車の軸線を中心とする周方向に等角度間隔で配置される四箇所のうちの少なくとも一箇所に、組付け時の位相合わせ用の被係合部を設けたことを特徴とする遊星歯車減速機構。 The planetary gear reduction mechanism according to claim 3,
The number of teeth of the first gear portion and the number of teeth of the second gear portion are both set to an integer multiple of “4”,
At least one of the four positions arranged at equiangular intervals in the circumferential direction centering on the axis of the stepped planetary gear, the phases of the teeth of the first gear portion and the teeth of the second gear portion match. A planetary gear reduction mechanism characterized in that an engaged portion for phase alignment at the time of assembly is provided.
Priority Applications (1)
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| JP2012201934A JP6136154B2 (en) | 2012-09-13 | 2012-09-13 | Planetary gear reduction mechanism |
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| JP2012201934A JP6136154B2 (en) | 2012-09-13 | 2012-09-13 | Planetary gear reduction mechanism |
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| JP6136154B2 JP6136154B2 (en) | 2017-05-31 |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106224481A (en) * | 2016-08-26 | 2016-12-14 | 江门市江海区柏健电器制造有限公司 | A kind of gear-box |
| CN106763533A (en) * | 2017-03-23 | 2017-05-31 | 深圳市创晶辉精密塑胶模具有限公司 | Electronic lock planetary speed reducer with small tooth number difference |
| CN106763629A (en) * | 2017-03-17 | 2017-05-31 | 深圳市创晶辉精密塑胶模具有限公司 | Rear view mirror driver and its small teeth number difference planet gear box transmission mechanism |
| WO2018170844A1 (en) * | 2017-03-23 | 2018-09-27 | 深圳市创晶辉精密塑胶模具有限公司 | Electronic lock small teeth difference planetary reducer |
| CN110206855A (en) * | 2019-06-14 | 2019-09-06 | 保定启晨传动科技有限公司 | A kind of large transmission ratio retarding method and device |
| JP2020016300A (en) * | 2018-07-26 | 2020-01-30 | 富士ゼロックス株式会社 | Planetary gear mechanism and image formation device |
| CN114123645A (en) * | 2022-01-28 | 2022-03-01 | 北京动思创新科技有限公司 | Differential speed reducer and brushless motor with same |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08147811A (en) * | 1994-11-24 | 1996-06-07 | Aiwa Co Ltd | Gear device |
| JP2001140995A (en) * | 1999-11-12 | 2001-05-22 | Otics Corp | Planetary gear device |
| JP2001271893A (en) * | 2000-01-21 | 2001-10-05 | Seiko Epson Corp | Gear box |
| JP2002122444A (en) * | 2000-10-17 | 2002-04-26 | Harmonic Drive Syst Ind Co Ltd | Absolute sensor |
| JP2007170507A (en) * | 2005-12-21 | 2007-07-05 | Tigers Polymer Corp | Synthetic resin cylindrical toothed product |
-
2012
- 2012-09-13 JP JP2012201934A patent/JP6136154B2/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08147811A (en) * | 1994-11-24 | 1996-06-07 | Aiwa Co Ltd | Gear device |
| JP2001140995A (en) * | 1999-11-12 | 2001-05-22 | Otics Corp | Planetary gear device |
| JP2001271893A (en) * | 2000-01-21 | 2001-10-05 | Seiko Epson Corp | Gear box |
| JP2002122444A (en) * | 2000-10-17 | 2002-04-26 | Harmonic Drive Syst Ind Co Ltd | Absolute sensor |
| JP2007170507A (en) * | 2005-12-21 | 2007-07-05 | Tigers Polymer Corp | Synthetic resin cylindrical toothed product |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106224481A (en) * | 2016-08-26 | 2016-12-14 | 江门市江海区柏健电器制造有限公司 | A kind of gear-box |
| CN106224481B (en) * | 2016-08-26 | 2019-02-22 | 江门市江海区柏健电器制造有限公司 | A kind of gear-box |
| CN106763629A (en) * | 2017-03-17 | 2017-05-31 | 深圳市创晶辉精密塑胶模具有限公司 | Rear view mirror driver and its small teeth number difference planet gear box transmission mechanism |
| CN106763629B (en) * | 2017-03-17 | 2021-04-20 | 深圳市创晶辉精密塑胶模具有限公司 | Rearview mirror surface driver and small tooth difference planetary gear box transmission mechanism thereof |
| CN106763533A (en) * | 2017-03-23 | 2017-05-31 | 深圳市创晶辉精密塑胶模具有限公司 | Electronic lock planetary speed reducer with small tooth number difference |
| WO2018170844A1 (en) * | 2017-03-23 | 2018-09-27 | 深圳市创晶辉精密塑胶模具有限公司 | Electronic lock small teeth difference planetary reducer |
| CN106763533B (en) * | 2017-03-23 | 2020-04-28 | 深圳市创晶辉精密塑胶模具有限公司 | Electronic lock small tooth difference planetary speed reducer |
| JP2020016300A (en) * | 2018-07-26 | 2020-01-30 | 富士ゼロックス株式会社 | Planetary gear mechanism and image formation device |
| CN110206855A (en) * | 2019-06-14 | 2019-09-06 | 保定启晨传动科技有限公司 | A kind of large transmission ratio retarding method and device |
| CN110206855B (en) * | 2019-06-14 | 2021-08-20 | 保定启晨传动科技有限公司 | Large-transmission-ratio speed reduction method and device |
| CN114123645A (en) * | 2022-01-28 | 2022-03-01 | 北京动思创新科技有限公司 | Differential speed reducer and brushless motor with same |
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