JP2016031081A - Differential gear - Google Patents

Differential gear Download PDF

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JP2016031081A
JP2016031081A JP2014152275A JP2014152275A JP2016031081A JP 2016031081 A JP2016031081 A JP 2016031081A JP 2014152275 A JP2014152275 A JP 2014152275A JP 2014152275 A JP2014152275 A JP 2014152275A JP 2016031081 A JP2016031081 A JP 2016031081A
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differential
cycloid
teeth
input member
central axis
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隆憲 野口
Takanori Noguchi
隆憲 野口
濱田　哲郎
Tetsuo Hamada
哲郎 濱田
翔平 坂田
Shohei Sakata
翔平 坂田
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Musashi Seimitsu Industry Co Ltd
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Musashi Seimitsu Industry Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a differential gear which can increase the strength of each tooth by setting the module of each tooth large without causing tooth profile interference, and is compact.SOLUTION: A differential gear comprises: an eccentric shaft 18 which is arranged to be relatively rotatable to an input member 7, is situated on an eccentric axis X2 eccentric from a center axis X1 and is integrally connected to a first output shaft 11; a first differential member 16 which is adjacent to the input member 7 and can revolve around the center axis X1 while rotating on the eccentric shaft 18; and a second differential member 17 integrally connected to a second output shaft 12 adjacently to the first differential member 16. The input member 7 is formed with first cycloid internal teeth 21, and first cycloid outer teeth 22 for meshing with the first cycloid internal teeth 21 are formed on one side part of the first differential member 16. Second cycloid internal teeth 24 are formed on the other side part of the first differential member 16, and second cycloid outer teeth 25 for meshing with the second cycloid internal teeth 24 are formed on the second differential member 17.SELECTED DRAWING: Figure 1

Description

本発明は，入力部材の回転を中心軸線上に相対回転可能に並ぶ第１出力軸及び第２出力軸に分配する差動装置の改良に関する。   The present invention relates to an improvement of a differential device that distributes rotation of an input member to a first output shaft and a second output shaft that are arranged so as to be relatively rotatable on a central axis.

ベベルギヤを用いた従来一般の差動装置（下記特許文献１参照）では，各ギヤの歯の強度を高めるべく，各ギヤのモジュールを大きくしようとすれば，差動装置の大型化や歯形干渉の問題が発生する。   In a conventional differential device using a bevel gear (see Patent Document 1 below), if the gear module is made larger in order to increase the gear strength of each gear, the differential device is increased in size and tooth profile interference. A problem occurs.

特開２０１２−６７８８９号公報JP 2012-67889 A

本発明は，かゝる事情に鑑みてなされたもので，歯形干渉を生じることなく各歯形のモジュールを大きく設定して各歯の強度を高めることができ，しかもコンパクトな差動装置を提供することを目的とする。   The present invention has been made in view of such circumstances, and can provide a compact differential device that can increase the strength of each tooth by setting a large module for each tooth profile without causing tooth profile interference. For the purpose.

上記目的を達成するために，本発明は，入力部材の回転を中心軸線上に相対回転可能に並ぶ第１出力軸及び第２出力軸に分配する差動装置において，前記中心軸線上に回転可能に配置される前記入力部材と，前記中心軸線上に前記入力部材と相対回転可能に配置され，前記中心軸線から偏心した偏心軸線上に位置しつゝ前記中心軸線周りに公転し得るように前記第１出力軸に一体的に連結される偏心軸と，前記入力部材の一側に隣接して配置され，前記偏心軸上で自転しながら前記中心軸線周りに公転し得る第１差動部材と，この第１差動部材の一側に隣接して前記中心軸線上で回転し得るように前記第２出力軸に一体的に連結される第２差動部材とを備え，前記入力部材には第１サイクロイド内歯を形成し，この第１サイクロイド内歯に噛合する第１サイクロイド外歯を前記第１差動部材の一側部に形成し，前記第１差動部材の他側部には第２サイクロイド内歯を形成し，この第２サイクロイド内歯に噛合する第２サイクロイド外歯を前記第２差動部材に形成し，前記第１サイクロイド内歯の歯数をＺ１，前記第１サイクロイド外歯の歯数をＺ２，前記第２サイクロイド内歯の歯数をＺ３，前記第２サイクロイド外歯の歯数をＺ４としたとき，
（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２
上式を成立させることを第１の特徴とする。 In order to achieve the above object, the present invention is capable of rotating on a central axis in a differential device that distributes rotation of an input member to a first output shaft and a second output shaft arranged in a relatively rotatable manner on the central axis. The input member disposed on the central axis so as to be rotatable relative to the input member on the central axis, and positioned on an eccentric axis eccentric from the central axis so as to revolve around the central axis. An eccentric shaft integrally connected to the first output shaft, a first differential member disposed adjacent to one side of the input member, and capable of revolving around the central axis while rotating on the eccentric shaft; A second differential member integrally connected to the second output shaft so as to be rotatable on the central axis adjacent to one side of the first differential member, Forms the first cycloid internal teeth and bites the first cycloid internal teeth A first cycloid external tooth is formed on one side of the first differential member, a second cycloid internal tooth is formed on the other side of the first differential member, and meshed with the second cycloid internal tooth Second cycloid external teeth are formed on the second differential member, the number of teeth of the first cycloid internal teeth is Z1, the number of teeth of the first cycloidal external teeth is Z2, and the number of teeth of the second cycloidal internal teeth Is Z3, and the number of teeth of the second cycloid external teeth is Z4,
(Z1 / Z2) × (Z3 / Z4) = 2
The first characteristic is to establish the above equation.

また本発明は，第１の特徴に加えて，前記（Ｚ１／Ｚ２）を４／３とすると共に前記（Ｚ３／Ｚ４）を３／２とし，又は前記（Ｚ１／Ｚ２）を３／２とすると共に，前記（Ｚ３／Ｚ４）を４／３とすることを第２の特徴とする。   In addition to the first feature of the present invention, the (Z1 / Z2) is 4/3 and the (Z3 / Z4) is 3/2, or the (Z1 / Z2) is 3/2. In addition, the second feature is that (Z3 / Z4) is set to 4/3.

さらに本発明は，前記入力部材をミッションケースに回転自在に支承し，この入力部材に，前記ミッションケースに回転自在に支承されて前記第１及び第２差動部材を覆うカバーを結合してデフケースを構成することを第３の特徴とする。   In the present invention, the input member is rotatably supported on a transmission case, and a cover that is rotatably supported on the transmission case and covers the first and second differential members is coupled to the input member. The third feature is to constitute

本発明の第１の特徴によれば，第１及び第２出力軸の負荷の変化に応じて，第１差動部材の自転量及び公転量が無段階に変化し，第１及び第２出力軸の回転数の平均値が入力部材の回転数と等しくなり，入力部材の回転を，第１及び第２出力軸に分配することができ，しかも従来一般のベベルギヤ式に比して，差動装置全体をその軸方向にコンパクトに構成することができ，特に軸方向寸法の短縮化を効果的に図ることができる。また第１サイクロイド内歯，第１サイクロイド外歯，第２サイクロイド内歯，第２サイクロイド外歯の採用により，歯形干渉を防ぎながら，各歯形のモジュールを大きく設定して各歯の強度を高め，高負荷用の差動装置を提供することができる。   According to the first feature of the present invention, the amount of rotation and the amount of revolution of the first differential member change steplessly in response to changes in the loads of the first and second output shafts, and the first and second outputs. The average value of the rotation speed of the shaft becomes equal to the rotation speed of the input member, and the rotation of the input member can be distributed to the first and second output shafts. The entire apparatus can be configured compactly in the axial direction, and in particular, the axial dimension can be shortened effectively. In addition, by adopting the first cycloid internal teeth, the first cycloid external teeth, the second cycloid internal teeth, and the second cycloid external teeth, while preventing tooth profile interference, each tooth profile module is set large to increase the strength of each tooth. A differential device for high load can be provided.

本発明の第２の特徴によれば，（Ｚ１／Ｚ２）＝４／３，（Ｚ３／Ｚ４）＝３／２とし，又は（Ｚ１／Ｚ２）＝３／２，（Ｚ３／Ｚ４）＝４／３とすることにより，各歯形のモジュールを最大にして，各歯の強度を効果的に高めことができる。   According to the second aspect of the invention, (Z1 / Z2) = 4/3, (Z3 / Z4) = 3/2, or (Z1 / Z2) = 3/2, (Z3 / Z4) = 4. By setting / 3, the module of each tooth profile can be maximized and the strength of each tooth can be effectively increased.

本発明の第３の特徴によれば，デフケースの一側壁を入力部材が兼用することになり，デフケースの構造を簡素化すると共に，その軽量化を図ることができる。   According to the third feature of the present invention, the input member also serves as one side wall of the differential case, so that the structure of the differential case can be simplified and the weight thereof can be reduced.

本発明の第１実施形態に係る差動装置の縦断正面図。1 is a longitudinal front view of a differential according to a first embodiment of the present invention. 図１の２−２矢視断面図。FIG. 2 is a sectional view taken along arrow 2-2 in FIG. 1. 図１の３−３矢視断面図。FIG. 3 is a cross-sectional view taken along arrow 3-3 in FIG. 1.

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

先ず，図１において，自動車のミッションケース１内に変速装置と共に差動装置Ｄが収容される。この差動装置は，変速装置の出力部材，即ち駆動ギヤ２から駆動されるリングギヤ３の回転を，中心軸線Ｘ１上に相対回転可能に並ぶ左右の駆動車軸Ｓ１，Ｓ２に分配する。   First, in FIG. 1, a differential device D is housed in a transmission case 1 of an automobile together with a transmission. This differential device distributes the rotation of the output member of the transmission, that is, the ring gear 3 driven from the drive gear 2, to the left and right drive axles S1, S2 arranged on the central axis X1 so as to be relatively rotatable.

図１及び図２に示すように，差動装置Ｄは，中心軸線Ｘ１上で第１及び第２軸受４，５を介してミッションケース１に回転可能に支持されるデフケース６を備えており，このデフケース６は，第１軸受４を介して支持される入力部材７と，この入力部材７にリングギヤ３と共にボルト９により固着されるカバー８とで構成され，このカバー８は，第２軸受５を介してミッションケース１に支持される。   As shown in FIGS. 1 and 2, the differential device D includes a differential case 6 that is rotatably supported by the transmission case 1 via first and second bearings 4 and 5 on a central axis X1. The differential case 6 includes an input member 7 supported via a first bearing 4 and a cover 8 fixed to the input member 7 together with the ring gear 3 by a bolt 9. The cover 8 is configured by the second bearing 5. It is supported by the mission case 1 via.

入力部材７には，差動装置Ｄの第１出力軸１１が，中心軸線Ｘ１上の第３軸受１３を介して回転可能に支持され，この第１出力軸１１に左方の駆動車軸Ｓ１がスプライン結合される。またカバー８には，差動装置Ｄの第２出力軸１２が，中心軸線Ｘ１上の第４軸受１４を介して回転可能に支持され，この第２出力軸１２に右方の駆動車軸Ｓ２がスプライン結合される。   A first output shaft 11 of the differential device D is rotatably supported by the input member 7 via a third bearing 13 on the center axis X1, and a left driving axle S1 is supported on the first output shaft 11. Spline combined. Further, the cover 8 supports a second output shaft 12 of the differential device D so as to be rotatable via a fourth bearing 14 on the center axis X1, and a right drive axle S2 is supported on the second output shaft 12. Spline combined.

カバー８内には，入力部材７の一側に隣接する第１差動部材１６と，この第１差動部材１６の一側に隣接する第２差動部材１７とが収容される。   A first differential member 16 adjacent to one side of the input member 7 and a second differential member 17 adjacent to one side of the first differential member 16 are accommodated in the cover 8.

第１出力軸１１には偏心軸１８が一体に連結されており，この偏心軸１８は，中心軸線Ｘ１から一定距離ｅだけ偏心した偏心軸線Ｘ２上に位置しつゝ中心軸線Ｘ１周りに公転し得るようになっている。この偏心軸１８に前記第１差動部材１６が第５軸受１９を介して相対回転可能に支持される。以上により，第１差動部材１６は，偏心軸１８周りに自転しながら中心軸線Ｘ１周りに公転することができる。   An eccentric shaft 18 is integrally connected to the first output shaft 11, and the eccentric shaft 18 revolves around the central axis X1 that is positioned on the eccentric axis X2 that is eccentric by a predetermined distance e from the central axis X1. To get. The first differential member 16 is supported on the eccentric shaft 18 via a fifth bearing 19 so as to be relatively rotatable. As described above, the first differential member 16 can revolve around the central axis X <b> 1 while rotating around the eccentric shaft 18.

図１〜図３に示すように，入力部材７の一側部には第１サイクロイド内歯２１が形成され，この第１サイクロイド内歯２１に噛合する，その歯数より少ない歯数を有する第１サイクロイド外歯２２が第１差動部材１６の一側部に形成され，第１差動部材１６の他側部には第２サイクロイド内歯２４が形成される。この第２サイクロイド内歯２４に噛合する，その歯数より少ない第２サイクロイド外歯２５が第２差動部材１７に形成される。したがって，第１サイクロイド内歯２１及び第２サイクロイド外歯２５は，中心軸線Ｘ１を中心に持ち，第１サイクロイド外歯２２及び第２サイクロイド内歯２４は，偏心軸線Ｘ２を中心に持つことになる。   As shown in FIGS. 1 to 3, a first cycloid internal tooth 21 is formed on one side of the input member 7, and meshes with the first cycloid internal tooth 21 and has a smaller number of teeth than the number of teeth. A first cycloid external tooth 22 is formed on one side of the first differential member 16, and a second cycloid internal tooth 24 is formed on the other side of the first differential member 16. Second cycloid outer teeth 25 smaller than the number of teeth that mesh with the second cycloid inner teeth 24 are formed on the second differential member 17. Therefore, the first cycloid inner teeth 21 and the second cycloid outer teeth 25 have the center axis X1 as the center, and the first cycloid outer teeth 22 and the second cycloid inner teeth 24 have the eccentric axis X2. .

而して，第１サイクロイド内歯２１の歯数をＺ１，第１サイクロイド外歯２２の歯数をＺ２，第２サイクロイド内歯２４の歯数をＺ３，第２サイクロイド外歯２５の歯数をＺ４としたとき，下記式が成立するように，各内歯２１，２４及び各外歯２２，２５は形成される。   Thus, the number of teeth of the first cycloid internal teeth 21 is Z1, the number of teeth of the first cycloid external teeth 22 is Z2, the number of teeth of the second cycloid internal teeth 24 is Z3, and the number of teeth of the second cycloid external teeth 25 is When Z4 is set, the inner teeth 21 and 24 and the outer teeth 22 and 25 are formed so that the following formula is established.

（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２
望ましくは，中心軸線Ｘ１に対する偏心軸線Ｘ２の偏心量を前述のようにｅとして，第１サイクロイド内歯２１，第１サイクロイド外歯２２，第２サイクロイド内歯２４，第２サイクロイド外歯２５の基準ピッチ円半径を，それぞれＲ１，Ｐ１，Ｒ２，Ｐ２としたとき，ｅ：Ｒ１：Ｐ１：Ｒ２：Ｐ２＝１：４：３：３：２とすると共に，図示例のように，Ｚ１＝４，Ｚ２＝３，Ｚ３＝３，Ｚ４＝２とするか，又はｅ：Ｒ１：Ｐ１：Ｒ２：Ｐ２＝１：３：２：４：３とすると共に，Ｚ１＝３，Ｚ２＝２，Ｚ３＝４，Ｚ４＝３とするとよい。 (Z1 / Z2) × (Z3 / Z4) = 2
Desirably, the amount of eccentricity of the eccentric axis X2 with respect to the central axis X1 is set to e as described above, and the reference of the first cycloid internal tooth 21, the first cycloid external tooth 22, the second cycloid internal tooth 24, and the second cycloid external tooth 25 is used. When the pitch circle radii are R1, P1, R2 and P2, respectively, e: R1: P1: R2: P2 = 1: 4: 3: 3: 2 and Z1 = 4 as in the illustrated example. Z2 = 3, Z3 = 3, Z4 = 2, or e: R1: P1: R2: P2 = 1: 3: 2: 4: 3 and Z1 = 3, Z2 = 2, Z3 = 4 , Z4 = 3.

尚，図１中，符号２７はオイルシールである。   In FIG. 1, reference numeral 27 denotes an oil seal.

次に，この実施形態の作用について説明する。   Next, the operation of this embodiment will be described.

いま，左方の駆動車軸Ｓ１を固定することで，第１出力軸１１及び偏心軸１８を固定した状態において，駆動ギヤ２からリングギヤ３を駆動して入力部材７を中心軸線Ｘ１周りに回転させると，第１サイクロイド内歯２１が第１サイクロイド外歯２２を駆動することにより，第１差動部材１６が不動の偏心軸１８周りに回転し，第２サイクロイド内歯２４が第２サイクロイド外歯２５を駆動することにより，第２差動部材１７，したがって第２出力軸１２が回転する。   Now, by fixing the left driving axle S1, in the state where the first output shaft 11 and the eccentric shaft 18 are fixed, the ring gear 3 is driven from the driving gear 2 to rotate the input member 7 around the central axis X1. When the first cycloid internal teeth 21 drive the first cycloid external teeth 22, the first differential member 16 rotates around the stationary eccentric shaft 18, and the second cycloidal internal teeth 24 become the second cycloidal external teeth. By driving 25, the second differential member 17, and thus the second output shaft 12, rotates.

ところで，図示例では（Ｚ１／Ｚ２）＝４／３，（Ｚ３／Ｚ４）＝３／２としてあるので，入力部材７が４／３の増速比をもって第１差動部材１６を駆動し，第１差動部材１６が３／２の増速比をもって第２差動部材１７，即ち第２出力軸１２を駆動することになり，その結果，入力部材７は，（４／３）×（３／２）＝２の増速比をもって第２出力軸１２を駆動することになる。   In the illustrated example, (Z1 / Z2) = 4/3 and (Z3 / Z4) = 3/2, so that the input member 7 drives the first differential member 16 with a speed increasing ratio of 4/3, The first differential member 16 drives the second differential member 17, that is, the second output shaft 12 with a speed increasing ratio of 3/2. As a result, the input member 7 is (4/3) × ( The second output shaft 12 is driven with a speed increasing ratio of 3/2) = 2.

また右方の駆動車軸Ｓ２を固定することで，第２出力軸１２及び第２差動部材１７を固定した状態において，入力部材７を回転させると，第１サイクロイド内歯２１の第１サイクロイド外歯２２に対する駆動と，第２サイクロイド外歯２５の第２サイクロイド内歯２４に対する駆動反力とにより，第１差動部材１６は，偏心軸１８周りに自転しつゝ，不動の第２差動部材１７周りに公転して，偏心軸１８を中心軸線Ｘ１周りに駆動する。その結果，入力部材７は，２倍の増速比をもって第１出力軸１１を駆動することになる。   Further, when the input member 7 is rotated in a state where the second output shaft 12 and the second differential member 17 are fixed by fixing the right drive axle S2, the first cycloid internal teeth 21 are outside the first cycloid. The first differential member 16 rotates around the eccentric shaft 18 due to the driving with respect to the teeth 22 and the driving reaction force of the second cycloidal outer teeth 25 with respect to the second cycloidal inner teeth 24, and the second differential that does not move. Revolving around the member 17, the eccentric shaft 18 is driven around the central axis X1. As a result, the input member 7 drives the first output shaft 11 with a double speed increasing ratio.

而して，第１及び第２出力軸１１，１２の負荷がバランスしたり，相互に変化したりすると，第１差動部材１６の自転量及び公転量が無段階に変化し，両出力軸１１，１２の回転数の平均値が入力部材７の回転数と等しくなる。こうして，入力部材７の回転は，第１及び第２出力軸１１，１２に分配され，したがってリングギヤ３の回転を左右の駆動車軸Ｓ１，Ｓ２に分配することができる。   Thus, when the loads of the first and second output shafts 11 and 12 are balanced or changed with each other, the amount of rotation and the amount of revolution of the first differential member 16 change steplessly, and both output shafts The average value of the rotational speeds 11 and 12 is equal to the rotational speed of the input member 7. Thus, the rotation of the input member 7 is distributed to the first and second output shafts 11 and 12, and therefore the rotation of the ring gear 3 can be distributed to the left and right drive axles S1 and S2.

ところで，この差動装置Ｄは，前述のように，入力部材７と，この入力部材７の一側に隣接する第１差動部材１６と，この第１差動部材１６の一側に隣接する第２差動部材１７とを備えるので，従来一般のベベルギヤ式の差動装置に比して，全体をコンパクトに構成することができ，特に軸方向寸法の短縮化を効果的に図ることができる。   By the way, as described above, the differential device D is adjacent to the input member 7, the first differential member 16 adjacent to one side of the input member 7, and one side of the first differential member 16. Since the second differential member 17 is provided, the overall configuration can be made more compact than a conventional general bevel gear type differential device, and in particular, the axial dimension can be effectively shortened. .

また第１サイクロイド内歯２１，第１サイクロイド外歯２２，第２サイクロイド内歯２４，第２サイクロイド外歯２５の採用により，歯形干渉を容易に防ぎながら，各歯形のモジュールを大きく設定して各歯の強度を高め，高負荷用の差動装置Ｄを提供することができる。   Further, by adopting the first cycloid inner teeth 21, the first cycloid outer teeth 22, the second cycloid inner teeth 24, and the second cycloid outer teeth 25, each tooth profile module is set to be large while easily preventing tooth profile interference. The tooth | gear intensity | strength can be raised and the differential gear D for high loads can be provided.

特に，前述のように，（Ｚ１／Ｚ２）＝４／３，（Ｚ３／Ｚ４）＝３／２とするか，又は（Ｚ１／Ｚ２）＝３／２，（Ｚ３／Ｚ４）＝４／３とすることにより，各歯形のモジュールを最大にして，各歯の強度を効果的に高めことができる。   In particular, as described above, (Z1 / Z2) = 4/3, (Z3 / Z4) = 3/2, or (Z1 / Z2) = 3/2, (Z3 / Z4) = 4/3 By maximizing the module of each tooth profile, the strength of each tooth can be effectively increased.

またデフケース６は，第１軸受４を介してミッションケース１に支持される入力部材７と，ミッションケース１に回転自在に支承されると共に入力部材７に結合されて，第１及び第２差動部材１６，１７を覆うカバー８とで構成されるので，デフケース６の一側壁を入力部材７が兼用することになり，デフケース６の構造を簡素化すると共に，その軽量化を図ることができる。   The differential case 6 has an input member 7 supported by the transmission case 1 via the first bearing 4 and is rotatably supported by the transmission case 1 and coupled to the input member 7 so that the first and second differential members 6 are supported. Since it is comprised with the cover 8 which covers the members 16 and 17, the input member 7 will also serve as one side wall of the differential case 6, and the structure of the differential case 6 can be simplified and the weight can be reduced.

以上，本発明の実施形態を説明したが，本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である。例えば，差動装置Ｄを，前，後輪駆動車両における前，後輪伝動系に適用することもできる。   As mentioned above, although embodiment of this invention was described, this invention can perform various design changes in the range which does not deviate from the summary. For example, the differential device D can be applied to front and rear wheel transmission systems in front and rear wheel drive vehicles.

１・・・・ミッションケース
６・・・・デフケース
７・・・・入力部材
８・・・・カバー
１１・・・第１出力軸
１２・・・第２出力軸
１６・・・第１差動部材
１７・・・第２差動部材
１８・・・偏心軸
２１・・・第１サイクロイド内歯
２２・・・第１サイクロイド外歯
２４・・・第２サイクロイド内歯
２５・・・第２サイクロイド外歯
Ｘ１・・・中心軸線
Ｘ２・・・偏心軸線 DESCRIPTION OF SYMBOLS 1 ... Mission case 6 ... Differential case 7 ... Input member 8 ... Cover 11 ... First output shaft 12 ... Second output shaft 16 ... First differential Member 17 ... Second differential member 18 ... Eccentric shaft 21 ... First cycloid internal tooth 22 ... First cycloid external tooth 24 ... Second cycloid internal tooth 25 ... Second cycloid External teeth X1 ... Center axis X2 ... Eccentric axis

Claims (3)

入力部材（７）の回転を中心軸線（Ｘ１）上に相対回転可能に並ぶ第１出力軸（１１）及び第２出力軸（１２）に分配する差動装置において，
前記中心軸線（Ｘ１）上に回転可能に配置される前記入力部材（７）と，前記中心軸線（Ｘ１）上に前記入力部材（７）と相対回転可能に配置され，前記中心軸線（Ｘ１）から偏心した偏心軸線（Ｘ２）上に位置しつゝ前記中心軸線（Ｘ１）周りに公転し得るように前記第１出力軸（１１）に一体的に連結される偏心軸（１８）と，前記入力部材（７）の一側に隣接して配置され，前記偏心軸（１８）上で自転しながら前記中心軸線（Ｘ１）周りに公転し得る第１差動部材（１６）と，この第１差動部材（１６）の一側に隣接して前記中心軸線（Ｘ１）上で回転し得るように前記第２出力軸（１２）に一体的に連結される第２差動部材（１７）とを備え，
前記入力部材（７）には第１サイクロイド内歯（２１）を形成し，この第１サイクロイド内歯（２１）に噛合する第１サイクロイド外歯（２２）を前記第１差動部材（１６）の一側部に形成し，前記第１差動部材（１６）の他側部には第２サイクロイド内歯（２４）を形成し，この第２サイクロイド内歯（２４）に噛合する第２サイクロイド外歯（２５）を前記第２差動部材（１７）に形成し，
前記第１サイクロイド内歯（２１）の歯数をＺ１，前記第１サイクロイド外歯（２２）の歯数をＺ２，前記第２サイクロイド内歯（２４）の歯数をＺ３，前記第２サイクロイド外歯（２５）の歯数をＺ４としたとき，
（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２
上式を成立させることを特徴とする差動装置。 In the differential device that distributes the rotation of the input member (7) to the first output shaft (11) and the second output shaft (12) arranged in a relatively rotatable manner on the central axis (X1),
The input member (7) rotatably disposed on the central axis (X1) and the input member (7) rotatably disposed on the central axis (X1), and the central axis (X1) An eccentric shaft (18) integrally connected to the first output shaft (11) so as to revolve around the central axis (X1), which is positioned on the eccentric axis (X2) deviated from A first differential member (16) disposed adjacent to one side of the input member (7) and capable of revolving around the central axis (X1) while rotating on the eccentric shaft (18); A second differential member (17) integrally connected to the second output shaft (12) so as to be rotatable on the central axis (X1) adjacent to one side of the differential member (16); With
A first cycloid internal tooth (21) is formed on the input member (7), and a first cycloid external tooth (22) meshing with the first cycloid internal tooth (21) is provided as the first differential member (16). A second cycloid internal tooth (24) formed on one side of the first differential member (16) and meshed with the second cycloid internal tooth (24). Forming external teeth (25) on the second differential member (17);
The number of teeth of the first cycloid internal tooth (21) is Z1, the number of teeth of the first cycloid external tooth (22) is Z2, the number of teeth of the second cycloid internal tooth (24) is Z3, and the second cycloid external When the number of teeth of the tooth (25) is Z4,
(Z1 / Z2) × (Z3 / Z4) = 2
A differential device characterized by satisfying the above equation. 請求項１に記載の差動装置において，
前記（Ｚ１／Ｚ２）を４／３とすると共に前記（Ｚ３／Ｚ４）を３／２とし，又は前記（Ｚ１／Ｚ２）を３／２とすると共に，前記（Ｚ３／Ｚ４）を４／３とすることを特徴とする差動装置。 The differential device according to claim 1,
The (Z1 / Z2) is 4/3 and the (Z3 / Z4) is 3/2, or the (Z1 / Z2) is 3/2 and the (Z3 / Z4) is 4/3. A differential device characterized by that. 請求項１に記載の差動装置において，
前記入力部材（７）をミッションケース（１）に回転自在に支承し，この入力部材（７）に，前記ミッションケース（１）に回転自在に支承されて前記第１及び第２差動部材（１６，１７）を覆うカバー（８）を結合してデフケース（６）を構成することを特徴とする差動装置。 The differential device according to claim 1,
The input member (7) is rotatably supported by the transmission case (1), and the input member (7) is rotatably supported by the transmission case (1) and the first and second differential members ( 16. A differential device characterized in that a differential case (6) is formed by coupling a cover (8) covering 16 and 17).
JP2014152275A 2014-07-25 2014-07-25 Differential gear Pending JP2016031081A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106801736A (en) * 2017-04-02 2017-06-06 凌子龙 A kind of differential mechanism
CN108691981A (en) * 2017-04-07 2018-10-23 凌子龙 Double cycloid differential mechanism
WO2019135831A1 (en) * 2018-01-08 2019-07-11 Schaeffler Technologies AG & Co. KG Hyper-cycloidal differential
US10359098B1 (en) 2018-01-08 2019-07-23 Schaeffler Technologies AG & Co. KG Hypo-cycloidal differential
US10359099B1 (en) 2018-01-08 2019-07-23 Schaeffler Technologies AG & Co. KG Cycloidal differential

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106801736A (en) * 2017-04-02 2017-06-06 凌子龙 A kind of differential mechanism
CN106801736B (en) * 2017-04-02 2023-01-10 凌子龙 Differential mechanism
CN108691981A (en) * 2017-04-07 2018-10-23 凌子龙 Double cycloid differential mechanism
CN108691981B (en) * 2017-04-07 2023-06-23 凌子龙 Double cycloid differential mechanism
WO2019135831A1 (en) * 2018-01-08 2019-07-11 Schaeffler Technologies AG & Co. KG Hyper-cycloidal differential
US10359098B1 (en) 2018-01-08 2019-07-23 Schaeffler Technologies AG & Co. KG Hypo-cycloidal differential
US10359099B1 (en) 2018-01-08 2019-07-23 Schaeffler Technologies AG & Co. KG Cycloidal differential
US10563729B2 (en) 2018-01-08 2020-02-18 Schaeffler Technologies AG & Co. KG Hyper-cycloidal differential

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