JP2012246946A - Rocking difference reduction gear - Google Patents

Rocking difference reduction gear Download PDF

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JP2012246946A
JP2012246946A JP2011116915A JP2011116915A JP2012246946A JP 2012246946 A JP2012246946 A JP 2012246946A JP 2011116915 A JP2011116915 A JP 2011116915A JP 2011116915 A JP2011116915 A JP 2011116915A JP 2012246946 A JP2012246946 A JP 2012246946A
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gear
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output
teeth
internal gear
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Mitsuhiro Koseki
光弘 小関
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TOWAPARTS Inc
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TOWAPARTS Inc
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Abstract

PROBLEM TO BE SOLVED: To obtain a high reduction ratio with a small-sized and simple structure.SOLUTION: A rocking gear body 8 is rotatable in relation to a rocking shaft portion 3c around an axis C2. An outer circumferential part of the rocking gear body 8 is formed with an input side outer gear 9 meshed with an input side inner gear 2, and an output side outer gear 10 meshed with an output side inner gear 6. The input side outer gear 9 is meshed with the input side inner gear 2 by the rotation of a crankshaft 3 around an input shaft portion 3a, and the inside of the input side inner gear 2 is made to rock (revolve). The output side outer gear 10 is integrally rotated with the input side outer gear 9, meshed with the output side inner gear 6, and the inside of the output side inner gear 6 is made to rock (revolve). The difference between the number of the teeth of the input side inner gear 2 and the number of the teeth of the output side inner gear 6 is equal to the difference between the number of the teeth of the input side outer gear 9 and the number of the teeth of the output side outer gear 10.

Description

この発明は、シンプルな構成で高い減速比を得ることができる揺動差分減速機に関するものである。   The present invention relates to a swing differential reducer that can obtain a high reduction ratio with a simple configuration.

従来のベルト式遊星差動減速装置では、入力軸に回転力を与えることにより、入力軸がクランク軸とともに回転され、第１の歯付きベルトを介して第１の歯付き遊星プーリ及び第２の歯付き遊星プーリが入力軸及び出力軸の回りに公転される。このとき、入力側歯付きプーリと第１の歯付き遊星プーリとの歯数差により、第１の歯付き遊星プーリに差動自転が付与され、この自転が第２の歯付き遊星プーリの自転数となる。また、第２の歯付き遊星プーリの自転及び第２の歯付き遊星プーリと出力側歯付きプーリとの歯数差に基づく合成回転が、第２の歯付きベルトを介して出力側歯付きプーリに発生する（例えば、特許文献１参照）。   In the conventional belt-type planetary differential reduction device, the input shaft is rotated together with the crankshaft by applying a rotational force to the input shaft, and the first toothed planetary pulley and the second toothed belt are passed through the first toothed belt. A toothed planetary pulley is revolved around the input and output shafts. At this time, differential rotation is imparted to the first toothed planetary pulley due to the difference in the number of teeth between the input-side toothed pulley and the first toothed planetary pulley, and this rotation is the rotation of the second toothed planetary pulley. Number. Further, the rotation of the second toothed planetary pulley and the combined rotation based on the difference in the number of teeth between the second toothed planetary pulley and the output side toothed pulley are output via the second toothed belt. (For example, see Patent Document 1).

特開２００４−２４５２５６号公報JP 2004-245256 A

上記のような従来のベルト式遊星差動減速装置では、遊星プーリの公転軌道の径が大きく、装置全体が大型化する。また、ベルトを用いているため、十分な強度を確保することが難しく、出力が制限され実用的ではない。   In the conventional belt-type planetary differential reduction device as described above, the diameter of the revolution orbit of the planetary pulley is large, and the entire device is enlarged. Moreover, since a belt is used, it is difficult to ensure sufficient strength, and the output is limited, which is not practical.

この発明は、上記のような課題を解決するためになされたものであり、小型かつシンプルな構成で、高い減速比を得ることができる揺動差分減速機を提供することを目的とする。   The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a swing differential reduction gear capable of obtaining a high reduction ratio with a small and simple configuration.

この発明に係る揺動差分減速機は、ボディに設けられた入力側内歯車、入力側内歯車と同軸の入力軸部と、入力軸部に対してオフセットされた揺動軸部とを有するクランク軸、揺動軸部に回転可能に設けられ、入力軸部を中心としたクランク軸の回転により入力側内歯車と噛み合いながら入力側内歯車の内側を揺動される入力側外歯車、入力軸部と同軸に配置されている出力軸、出力軸に設けられ、かつ入力側内歯車と同軸に配置されており、出力軸と一体に回転される出力側内歯車、及び入力側外歯車と同軸に配置されており、入力側外歯車と一体に回転されて、出力側内歯車と噛み合いながら出力側内歯車の内側を揺動される出力側外歯車を備え、入力側内歯車の歯数と出力側内歯車の歯数とは異なっており、入力側外歯車の歯数と出力側外歯車の歯数とは異なっており、入力側内歯車の歯数と出力側内歯車の歯数との差が、入力側外歯車の歯数と前記出力側外歯車の歯数との差に等しくなっている。   A swing differential reducer according to the present invention includes an input side internal gear provided on a body, an input shaft portion coaxial with the input side internal gear, and a swing shaft portion offset with respect to the input shaft portion. An input-side external gear and an input shaft that are rotatably provided on the shaft and the swinging shaft portion, and are oscillated inside the input-side internal gear while meshing with the input-side internal gear by rotation of the crankshaft centered on the input shaft portion Are arranged coaxially with the output shaft, provided on the output shaft and coaxially with the input-side internal gear, and coaxial with the output-side internal gear and the input-side external gear rotated together with the output shaft. The output-side external gear that is rotated integrally with the input-side external gear and is oscillated inside the output-side internal gear while meshing with the output-side internal gear, and the number of teeth of the input-side internal gear. The number of teeth on the output side internal gear is different from the number of teeth on the input side external gear. It is different from the number of teeth of the external gear, and the difference between the number of teeth on the input side internal gear and the number of teeth on the output side internal gear is the difference between the number of teeth on the input side external gear and the number of teeth on the output side external gear. It is equal to.

この発明の揺動差分減速機は、歯数の異なる４種の歯車の組み合わせによる小型かつシンプルな構成により、高い減速比を得ることができる。   The swing differential reduction gear according to the present invention can obtain a high reduction ratio by a small and simple configuration by combining four kinds of gears having different numbers of teeth.

この発明の実施の形態１による揺動差分減速機の断面図である。It is sectional drawing of the rocking | fluctuation differential reduction gear by Embodiment 1 of this invention. 図１の揺動差分減速機を一部破断して示す斜視図である。FIG. 2 is a perspective view showing a partially broken portion of the swing differential reduction gear of FIG. 1. 図１のＩＩＩ−ＩＩＩ線に沿う断面図である。It is sectional drawing which follows the III-III line of FIG. 図１の揺動差分減速機のギヤ機構を示す構成図である。It is a block diagram which shows the gear mechanism of the rocking | fluctuation difference reduction gear of FIG. 図１の揺動差分減速機による減速比及び減速倍率の設定例を示す説明図である。It is explanatory drawing which shows the example of a setting of the reduction ratio and reduction magnification by the rocking | fluctuation difference reduction gear of FIG. この発明の実施の形態２による揺動差分減速機の入力側内歯車と入力側外歯車との配置を示す構成図である。It is a block diagram which shows arrangement | positioning of the input side internal gear and input side external gear of the rocking | fluctuation differential reduction gear by Embodiment 2 of this invention. 実施の形態２の揺動差分減速機のギヤ機構を示す構成図である。FIG. 6 is a configuration diagram illustrating a gear mechanism of a swing differential reduction gear according to a second embodiment.

以下、この発明を実施するための形態について、図面を参照して説明する。
実施の形態１．
図１はこの発明の実施の形態１による揺動差分減速機の断面図、図２は図１の揺動差分減速機を一部破断して示す斜視図、図３は図１のＩＩＩ−ＩＩＩ線に沿う断面図である。 Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
1 is a cross-sectional view of a swing differential reducer according to Embodiment 1 of the present invention, FIG. 2 is a perspective view showing a partially broken swing differential reducer of FIG. 1, and FIG. 3 is III-III of FIG. It is sectional drawing which follows a line.

図において、ボディ（ハウジング）１は、ボディ円板部１ａと、ボディ円板部１ａの外周部から軸方向一側へ突出したボディ円筒部１ｂとを有している。ボディ円板部１ａの中心には、断面円形の入力軸挿通孔１ｃが設けられている。ボディ円筒部１ｂのボディ円板部１ａ側端部の内周面には、入力側内歯車２が形成されている。入力側内歯車２は、ボディ１に一体加工されている。   In the figure, a body (housing) 1 has a body disc part 1a and a body cylindrical part 1b protruding from the outer peripheral part of the body disc part 1a to one side in the axial direction. An input shaft insertion hole 1c having a circular cross section is provided at the center of the body disk portion 1a. An input-side internal gear 2 is formed on the inner peripheral surface of the body disc portion 1a side end of the body cylindrical portion 1b. The input side internal gear 2 is integrally formed with the body 1.

ボディ１内には、クランク軸３が設けられている。クランク軸３は、第１及び第２の軸端部を有している。クランク軸３の第１の軸端部には、駆動源、例えばモータ（図示せず）の回転が入力される断面円形の入力軸部３ａが設けられている。入力軸部３ａは、入力側内歯車２と同軸に配置されている。クランク軸３の第２の軸端部には、断面円形の延長軸部３ｂが設けられている。延長軸部３ｂは、入力軸部３ａと同軸に配置されている。   A crankshaft 3 is provided in the body 1. The crankshaft 3 has first and second shaft end portions. A first shaft end portion of the crankshaft 3 is provided with an input shaft portion 3a having a circular section in which rotation of a drive source, for example, a motor (not shown) is input. The input shaft portion 3 a is disposed coaxially with the input side internal gear 2. An extension shaft portion 3 b having a circular cross section is provided at the second shaft end portion of the crankshaft 3. The extension shaft portion 3b is disposed coaxially with the input shaft portion 3a.

クランク軸３の中間部には、入力軸部３ａに対してオフセットされた断面円形の揺動軸部（オフセット軸部）３ｃが設けられている。揺動軸部３ｃの軸線Ｃ２は、入力軸部３ａの軸線Ｃ１と平行であり、軸線Ｃ１に対して入力軸部３ａの径方向へ所定量だけオフセットされている。   A swing shaft portion (offset shaft portion) 3c having a circular cross section that is offset with respect to the input shaft portion 3a is provided at an intermediate portion of the crankshaft 3. The axis C2 of the swing shaft portion 3c is parallel to the axis C1 of the input shaft portion 3a, and is offset from the axis C1 by a predetermined amount in the radial direction of the input shaft portion 3a.

入力軸部３ａの軸端部は、入力軸挿通孔１ｃを貫通してボディ１外へ突出している。また、入力軸部３ａの軸端部の中心には、モータのピニオンが噛み合う入力内歯車３ｄが設けられている。クランク軸３は、モータの駆動力により、ボディ１に対して軸線Ｃ１を中心として回転される。このとき、揺動軸部３ｃ（即ち、軸線Ｃ２）は、軸線Ｃ１を中心とした円周上を変位（公転）される。   The shaft end portion of the input shaft portion 3a protrudes out of the body 1 through the input shaft insertion hole 1c. An input internal gear 3d that meshes with a motor pinion is provided at the center of the shaft end of the input shaft 3a. The crankshaft 3 is rotated about the axis C1 with respect to the body 1 by the driving force of the motor. At this time, the swing shaft portion 3c (that is, the axis C2) is displaced (revolved) on the circumference around the axis C1.

出力軸４は、入力軸部３ａと同軸に配置されている。出力軸４は、出力軸本体４ａと、出力軸本体４ａの軸端部から径方向外側に突出した円板状のフランジ部４ｂと、フランジ部４ｂの外周部から軸方向へ突出した出力軸円筒部４ｃとを有している。   The output shaft 4 is disposed coaxially with the input shaft portion 3a. The output shaft 4 includes an output shaft main body 4a, a disk-shaped flange portion 4b projecting radially outward from the shaft end portion of the output shaft main body 4a, and an output shaft cylinder projecting axially from the outer peripheral portion of the flange portion 4b. Part 4c.

出力軸円筒部４ｃの外周面は、ボディ円筒部１ｂの内周面に接している。これにより、出力軸円筒部４ｃは、ボディ円筒部１ｂ内に回転可能に保持されている。出力軸本体４ａの軸端部には、断面円形の凹部４ｄが設けられている。凹部４ｄには、延長軸部３ｂが挿入され回転可能に保持されている。   The outer peripheral surface of the output shaft cylindrical portion 4c is in contact with the inner peripheral surface of the body cylindrical portion 1b. Thus, the output shaft cylindrical portion 4c is rotatably held in the body cylindrical portion 1b. A concave portion 4d having a circular cross section is provided at the shaft end of the output shaft main body 4a. The extension shaft portion 3b is inserted into the recess 4d and is rotatably held.

ボディ円筒部１ｂのボディ円板部１ａとは反対側の軸端部には、出力軸保持部材５が固定されている。出力軸保持部材５の中心には、出力軸挿通孔５ａが設けられている。出力軸挿通孔５ａには、出力軸本体４ａが挿通され回転可能に保持されている。また、出力軸保持部材５は、ボディ円筒部１ｂの開口を塞ぐカバーを兼ねている。   An output shaft holding member 5 is fixed to a shaft end portion of the body cylindrical portion 1b opposite to the body disc portion 1a. An output shaft insertion hole 5 a is provided at the center of the output shaft holding member 5. The output shaft main body 4a is inserted into the output shaft insertion hole 5a and is rotatably held. The output shaft holding member 5 also serves as a cover that closes the opening of the body cylindrical portion 1b.

出力軸円筒部４ｃの内周面には、出力側内歯車６が形成されている。出力側内歯車６は、出力軸４に一体加工されている。   An output side internal gear 6 is formed on the inner peripheral surface of the output shaft cylindrical portion 4c. The output side internal gear 6 is integrally processed with the output shaft 4.

揺動軸部３ｃの外周部には、軸受７を介して円筒状の揺動歯車体８が装着されている。揺動歯車体８は、軸線Ｃ２を中心として揺動軸部３ｃに対して回転可能である。揺動歯車体８の外周部には、入力側内歯車２と噛み合う入力側外歯車９と、出力側内歯車６と噛み合う出力側外歯車１０とが形成されている。即ち、入力側外歯車９及び出力側外歯車１０は、揺動歯車体８に一体加工されている。   A cylindrical oscillating gear body 8 is attached to the outer peripheral portion of the oscillating shaft portion 3 c via a bearing 7. The oscillating gear body 8 is rotatable with respect to the oscillating shaft portion 3c about the axis C2. An input side external gear 9 that meshes with the input side internal gear 2 and an output side external gear 10 that meshes with the output side internal gear 6 are formed on the outer peripheral portion of the oscillating gear body 8. That is, the input-side external gear 9 and the output-side external gear 10 are integrally processed with the swing gear body 8.

入力側外歯車９の径は、入力側内歯車２の径よりも小さい。入力側外歯車９は、入力軸部３ａを中心としたクランク軸３の回転により入力側内歯車２と噛み合いながら入力側内歯車２の内側を揺動（公転）される。即ち、入力側外歯車９は、入力側内歯車２の歯上を転動されながら、軸線Ｃ２を中心として回転されていく。   The diameter of the input side external gear 9 is smaller than the diameter of the input side internal gear 2. The input side external gear 9 is swung (revolved) inside the input side internal gear 2 while meshing with the input side internal gear 2 by rotation of the crankshaft 3 around the input shaft portion 3a. That is, the input side external gear 9 is rotated about the axis C2 while being rolled on the teeth of the input side internal gear 2.

出力側外歯車１０の径は、出力側内歯車６の径よりも小さい。出力側外歯車１０は、入力側外歯車９と一体に回転されて、出力側内歯車６と噛み合いながら出力側内歯車６の内側を揺動（公転）される。即ち、出力側外歯車１０は、出力側内歯車６の歯上を転動されながら、軸線Ｃ２を中心として回転されていく。   The diameter of the output side external gear 10 is smaller than the diameter of the output side internal gear 6. The output-side external gear 10 is rotated integrally with the input-side external gear 9 and is swung (revolved) inside the output-side internal gear 6 while meshing with the output-side internal gear 6. That is, the output-side external gear 10 is rotated about the axis C2 while being rolled on the teeth of the output-side internal gear 6.

図４は図１の揺動差分減速機のギヤ機構を示す構成図である。図４に示すようなギヤの組み合わせを成立させるため、次のような規制が設定されている。即ち、入力側内歯車２の歯数Ａｚと出力側内歯車６の歯数Ｃｚとは異なっている（Ａｚ≠Ｃｚ）。この例では、歯数Ｃｚが歯数Ａｚよりも小さくなっている（Ｃｚ＜Ａｚ）。   FIG. 4 is a block diagram showing a gear mechanism of the swing differential reduction gear of FIG. In order to establish a gear combination as shown in FIG. 4, the following restrictions are set. That is, the number of teeth Az of the input side internal gear 2 is different from the number of teeth Cz of the output side internal gear 6 (Az ≠ Cz). In this example, the number of teeth Cz is smaller than the number of teeth Az (Cz <Az).

また、入力側外歯車９の歯数Ｂｚ（Ｂｚ＜Ａｚ）と出力側外歯車１０の歯数Ｄｚ（Ｄｚ＜Ｃｚ）とは異なっている。この例では、歯数Ｄｚが歯数Ｂｚよりも小さくなっている（Ｄｚ＜Ｂｚ）。   Further, the number of teeth Bz (Bz <Az) of the input side external gear 9 and the number of teeth Dz (Dz <Cz) of the output side external gear 10 are different. In this example, the number of teeth Dz is smaller than the number of teeth Bz (Dz <Bz).

さらに、入力側内歯車２の歯数Ａｚと出力側内歯車６の歯数Ｃｚとの差が、入力側外歯車９の歯数Ｂｚと出力側外歯車１０の歯数Ｄｚとの差に等しくなっている（Ａｚ−Ｃｚ＝Ｂｚ−Ｄｚ）。このため、Ｃｚ＝Ａｚ−（Ｂｚ−Ｄｚ）、Ｄｚ＝Ｂｚ−（Ａｚ−Ｃｚ）である。   Further, the difference between the number of teeth Az of the input side internal gear 2 and the number of teeth Cz of the output side internal gear 6 is equal to the difference between the number of teeth Bz of the input side external gear 9 and the number of teeth Dz of the output side external gear 10. (Az-Cz = Bz-Dz). Therefore, Cz = Az− (Bz−Dz) and Dz = Bz− (Az−Cz).

実際に歯数Ａｚ〜Ｄｚを選択する際には、入力側内歯車２の歯数Ａｚ及び出力側内歯車６の歯数Ｃｚとして、必要な減速比に応じて任意の歯数を選択することができる。また、入力側外歯車９の歯数Ｂｚとして、円滑な回転が望める歯数を選択することができる。そして、出力側外歯車１０の歯数Ｄｚとして、クランク軸３のオフセットを考慮して上記の関係が成立するような歯数を選択することができる。   When actually selecting the number of teeth Az to Dz, select any number of teeth according to the required reduction ratio as the number of teeth Az of the input-side internal gear 2 and the number of teeth Cz of the output-side internal gear 6. Can do. Further, as the number of teeth Bz of the input side external gear 9, the number of teeth that can be smoothly rotated can be selected. The number of teeth that satisfies the above relationship can be selected as the number of teeth Dz of the output-side external gear 10 in consideration of the offset of the crankshaft 3.

このような揺動差分減速機では、入力軸部３ａから出力軸４に回転を伝達するギヤ機構が２段で構成されており、１段目で発生するギヤモーションと２段目で発生するギヤモーションとの差分が出力される。このときの減速比は、１−｛（Ａｚ×Ｄｚ）／（Ｂｚ×Ｃｚ）｝となる。   In such a swing differential reduction gear, the gear mechanism for transmitting the rotation from the input shaft portion 3a to the output shaft 4 is configured in two stages, and the gear motion generated in the first stage and the gear generated in the second stage. The difference with the motion is output. The reduction ratio at this time is 1 − {(Az × Dz) / (Bz × Cz)}.

図５は図１の揺動差分減速機による減速比及び減速倍率の設定例を示す説明図である。このように、歯数の異なる４つの歯車２，６，９，１０の組み合わせによる小型かつシンプルな構成により、コストを抑えつつ、高い減速比を得ることができる。また、２段のギヤ構成により、入出力を同軸とすることができ、高い出力にも耐える十分な強度を確保することができる。さらに、バックラッシュを十分に低減することもできる。   FIG. 5 is an explanatory view showing a setting example of a reduction ratio and a reduction magnification by the swing differential reduction gear of FIG. In this way, a high reduction ratio can be obtained while suppressing costs by a small and simple configuration by combining four gears 2, 6, 9, and 10 having different numbers of teeth. In addition, the two-stage gear configuration allows the input and output to be coaxial, and sufficient strength to withstand high output can be ensured. Furthermore, backlash can be sufficiently reduced.

また、入力側外歯車９及び出力側外歯車１０を共通の揺動歯車体８に一体加工したので、部品点数をさらに削減することができるとともに、バックラッシュをさらに低減することができる。   In addition, since the input-side external gear 9 and the output-side external gear 10 are integrally processed in the common oscillating gear body 8, the number of parts can be further reduced and the backlash can be further reduced.

実施の形態２．
次に、この発明の実施の形態２について説明する。入力側内歯車２の歯数Ａｚと入力側外歯車９の歯数Ｂｚとの差を大きくする場合、例えば図６に示すように、歯数が等しい２個以上（図６では３個）の入力側外歯車９を用いてもよい。このような構成を実現するため、実施の形態２では、遊星ギヤ機構から太陽ギヤをなくした機構を利用する。 Embodiment 2. FIG.
Next, a second embodiment of the present invention will be described. When the difference between the number of teeth Az of the input side internal gear 2 and the number of teeth Bz of the input side external gear 9 is increased, for example, as shown in FIG. 6, two or more teeth (three in FIG. 6) having the same number of teeth are used. The input side external gear 9 may be used. In order to realize such a configuration, the second embodiment uses a mechanism in which the sun gear is eliminated from the planetary gear mechanism.

図７は実施の形態２の揺動差分減速機のギヤ機構を示す構成図であり、図７では、入力側外歯車９及び出力側外歯車１０を１組のみ示している。このような構成では、遊星ギヤ機構の遊星ギヤが入力側外歯車９として機能し、プラネタリボディがクランク軸３として機能する。また、各入力側外歯車９には、入力側外歯車９と一体に回転する出力側外歯車１０が設けられている。歯数Ａｚ〜Ｄｚの条件は、実施の形態１と同様である。   FIG. 7 is a block diagram showing the gear mechanism of the swing differential reduction gear according to the second embodiment. FIG. 7 shows only one set of the input side external gear 9 and the output side external gear 10. In such a configuration, the planetary gear of the planetary gear mechanism functions as the input side external gear 9, and the planetary body functions as the crankshaft 3. Each input-side external gear 9 is provided with an output-side external gear 10 that rotates integrally with the input-side external gear 9. The conditions for the number of teeth Az to Dz are the same as those in the first embodiment.

このような構成によっても、歯数の異なる４種の歯車による小型かつシンプルな構成により、高い減速比を得ることができる。   Even with such a configuration, a high reduction ratio can be obtained by a small and simple configuration using four types of gears having different numbers of teeth.

なお、上記の例では、出力側内歯車６の歯数Ｃｚを入力側内歯車２の歯数Ａｚよりも小さくしたが、出力側内歯車６の歯数Ｃｚを入力側内歯車２の歯数Ａｚよりも大きくしてもよい（Ｃｚ＞Ａｚ）。
また、揺動軸部３ｃの偏心による軸線Ｃ１周りの重量バランスを補正するため、クランク軸３にバランサ（図示せず）を装着してもよい。例えば図１の構成では、クランク軸３と揺動歯車体８との間の空間を利用してバランサを配置することができる。 In the above example, the number of teeth Cz of the output side internal gear 6 is made smaller than the number of teeth Az of the input side internal gear 2, but the number of teeth Cz of the output side internal gear 6 is set to the number of teeth of the input side internal gear 2. It may be larger than Az (Cz> Az).
Further, a balancer (not shown) may be attached to the crankshaft 3 in order to correct the weight balance around the axis C1 due to the eccentricity of the swinging shaft portion 3c. For example, in the configuration of FIG. 1, the balancer can be arranged using the space between the crankshaft 3 and the rocking gear body 8.

１ ボディ、２ 入力側外歯車、３ クランク軸、３ａ 入力軸部、３ｃ 揺動軸部、４ 出力軸、６ 出力側内歯車、９ 入力側外歯車、１０ 出力側外歯車。   DESCRIPTION OF SYMBOLS 1 Body, 2 input side external gear, 3 crankshaft, 3a input shaft part, 3c rocking shaft part, 4 output shaft, 6 output side internal gear, 9 input side external gear, 10 output side external gear

Claims (2)

ボディに設けられた入力側内歯車、
前記入力側内歯車と同軸の入力軸部と、前記入力軸部に対してオフセットされた揺動軸部とを有するクランク軸、
前記揺動軸部に回転可能に設けられ、前記入力軸部を中心とした前記クランク軸の回転により前記入力側内歯車と噛み合いながら前記入力側内歯車の内側を揺動される入力側外歯車、
前記入力軸部と同軸に配置されている出力軸、
前記出力軸に設けられ、かつ前記入力側内歯車と同軸に配置されており、前記出力軸と一体に回転される出力側内歯車、及び
前記入力側外歯車と同軸に配置されており、前記入力側外歯車と一体に回転されて、前記出力側内歯車と噛み合いながら前記出力側内歯車の内側を揺動される出力側外歯車
を備え、
前記入力側内歯車の歯数と前記出力側内歯車の歯数とは異なっており、
前記入力側外歯車の歯数と前記出力側外歯車の歯数とは異なっており、
前記入力側内歯車の歯数と前記出力側内歯車の歯数との差が、前記入力側外歯車の歯数と前記出力側外歯車の歯数との差に等しくなっていることを特徴とする揺動差分減速機。 An input side internal gear provided on the body,
A crankshaft having an input shaft portion coaxial with the input-side internal gear, and a swing shaft portion offset with respect to the input shaft portion;
An input side external gear that is rotatably provided on the swing shaft portion and swings inside the input side internal gear while meshing with the input side internal gear by rotation of the crankshaft about the input shaft portion. ,
An output shaft disposed coaxially with the input shaft portion;
Provided on the output shaft, and disposed coaxially with the input-side internal gear, and disposed coaxially with the output-side internal gear rotated integrally with the output shaft, and the input-side external gear, An output-side external gear that is rotated integrally with the input-side external gear and is oscillated inside the output-side internal gear while meshing with the output-side internal gear;
The number of teeth of the input side internal gear is different from the number of teeth of the output side internal gear,
The number of teeth of the input side external gear is different from the number of teeth of the output side external gear,
The difference between the number of teeth of the input side internal gear and the number of teeth of the output side internal gear is equal to the difference between the number of teeth of the input side external gear and the number of teeth of the output side external gear. The swing differential reducer. 前記揺動軸部に回転可能に設けられた揺動歯車体をさらに備え、
前記入力側外歯車及び前記出力側外歯車は、前記揺動歯車体に一体加工されていることを特徴とする請求項１記載の揺動差分減速機。 A swing gear body rotatably provided on the swing shaft portion;
The swing differential reduction device according to claim 1, wherein the input-side external gear and the output-side external gear are integrally formed on the swing gear body.
JP2011116915A 2011-05-25 2011-05-25 Rocking difference reduction gear Pending JP2012246946A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150040695A1 (en) * 2012-02-14 2015-02-12 Boris Narovlansky Gear assembly and use in cylinder lock
DE102016114818B3 (en) * 2016-08-10 2017-12-21 Pierburg Gmbh Device for phase shifting a rotational angle of a drive part to a driven part

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03223546A (en) * 1990-01-30 1991-10-02 Yashima Eng Kk Speed reducer
JP2004340191A (en) * 2003-05-13 2004-12-02 Sony Corp Geared motor and reduction gear
JP2010174926A (en) * 2009-01-27 2010-08-12 Hitachi Constr Mach Co Ltd Differential gear device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03223546A (en) * 1990-01-30 1991-10-02 Yashima Eng Kk Speed reducer
JP2004340191A (en) * 2003-05-13 2004-12-02 Sony Corp Geared motor and reduction gear
JP2010174926A (en) * 2009-01-27 2010-08-12 Hitachi Constr Mach Co Ltd Differential gear device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150040695A1 (en) * 2012-02-14 2015-02-12 Boris Narovlansky Gear assembly and use in cylinder lock
US9267583B2 (en) * 2012-02-14 2016-02-23 Mul-T-Lock Technologies Ltd. Gear assembly and use in cylinder lock
DE102016114818B3 (en) * 2016-08-10 2017-12-21 Pierburg Gmbh Device for phase shifting a rotational angle of a drive part to a driven part

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