JP2011133059A - Continuously variable transmission - Google Patents

Continuously variable transmission Download PDF

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JP2011133059A
JP2011133059A JP2009293844A JP2009293844A JP2011133059A JP 2011133059 A JP2011133059 A JP 2011133059A JP 2009293844 A JP2009293844 A JP 2009293844A JP 2009293844 A JP2009293844 A JP 2009293844A JP 2011133059 A JP2011133059 A JP 2011133059A
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continuously variable
carrier
variable transmission
disk
planetary gear
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JP5397216B2 (en
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Akihiro Fukuda
晃大 福田
Yuji Shimomura
祐二 下村
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NSK Ltd
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NSK Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission which imparts loading force in part of a disk where deformation rigidity is high, prevents the deterioration of transmission efficiency, prevents the occurrence of fretting, and reduces bending stress. <P>SOLUTION: A protrusion 113 is formed on an inside diameter side surface of a first connecting part 103 of a carrier 102 toward an input side disk 112 which is an outside disk of the toroidal type continuously variable transmission 111, and a recess 114 is formed on an outside surface of the input side disk 112 in a position corresponding to the protrusion 113 so as to be fitted to the protrusion 113. The outside diameter of a sun gear 109 is larger than the inside diameter of the first connecting part 103. In this embodiment, the outside diameter part 117 of a flange part 116 provided on one end of an input shaft 115 and the inside diameter part 118 of a second connecting part 104 of the carrier 102 are formed into a spigot shape so as to be fitted with each other, and are spline-joined, and are rotated together, and are integrated by welding (beam welding). <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

本発明は、自動車用自動変速装置、あるいは、各種産業機械の運転速度を調節するための変速装置として利用するトロイダル型無段変速機と遊星歯車式変速機とを組み合わせた無段変速装置に関するものである。   The present invention relates to a continuously variable transmission in which a toroidal continuously variable transmission and a planetary gear transmission are used as an automatic transmission for automobiles or a transmission for adjusting the operating speed of various industrial machines. It is.

自動車用自動変速装置としてトロイダル型無段変速機を使用する事が研究され、一部で実施されている。又、トロイダル型無段変速機と遊星歯車式変速機とを組み合わせて無段変速装置を構成する事が、特許文献に記載されている様に、従来から提案されている。図2は、このうちの特許文献1に記載された無段変速装置を示している。この無段変速装置は、トロイダル型無段変速機1と遊星歯車式変速機2とを組み合わせて成る。このうちのトロイダル型無段変速機1は、入力軸3と、1対の入力側ディスク4、4と出力側ディスク5と、複数のパワーローラ6、6とを備える。   The use of a toroidal continuously variable transmission as an automatic transmission for automobiles has been studied and implemented in part. In addition, as described in the patent literature, it has been conventionally proposed to configure a continuously variable transmission by combining a toroidal type continuously variable transmission and a planetary gear type transmission. FIG. 2 shows the continuously variable transmission described in Patent Document 1 among them. This continuously variable transmission is formed by combining a toroidal type continuously variable transmission 1 and a planetary gear type transmission 2. Of these, the toroidal continuously variable transmission 1 includes an input shaft 3, a pair of input side disks 4, 4, an output side disk 5, and a plurality of power rollers 6, 6.

又、上記遊星歯車式変速機2は、上記入力軸3及び一方(図2の右方)の入力側ディスク4に結合固定されたキャリア7を備える。このキャリア7の径方向中間部に、その両端部にそれぞれ遊星歯車8、9を固設した第一伝達軸10を、回転自在に支持している。又、上記キャリア7を挟んで上記入力軸3と反対側に、その両端部に太陽歯車11、12を固設した第二伝達軸13を、上記入力軸3と同心に、回転自在に支持している。そして、上記各遊星歯車8、9と、上記出力側ディスク5にその基端部(図2の左端部)を結合した中空回転軸14の先端部(図2の右端部)に固設した太陽歯車15又は上記第二伝達軸13の一端部(図2の左端部)に固設した太陽歯車11とを、それぞれ噛合させている。又、一方(図2の左方)の遊星歯車8を、別の遊星歯車16を介して、上記キャリア7の周囲に回転自在に設けたリング歯車17に噛合させている。   The planetary gear type transmission 2 includes a carrier 7 coupled and fixed to the input shaft 3 and one input side disk 4 (right side in FIG. 2). A first transmission shaft 10 having planetary gears 8 and 9 fixed to both ends of the carrier 7 in the radial direction intermediate portion is rotatably supported. Further, a second transmission shaft 13 having sun gears 11 and 12 fixed to both ends thereof is supported on the opposite side of the input shaft 3 with the carrier 7 interposed therebetween, and is rotatably supported concentrically with the input shaft 3. ing. The planetary gears 8 and 9 and the sun fixed to the distal end portion (the right end portion in FIG. 2) of the hollow rotary shaft 14 whose base end portion (the left end portion in FIG. 2) is coupled to the output side disk 5. The gear 15 or the sun gear 11 fixed to one end portion (left end portion in FIG. 2) of the second transmission shaft 13 is engaged with each other. Further, one (left side in FIG. 2) planetary gear 8 is meshed with a ring gear 17 rotatably provided around the carrier 7 via another planetary gear 16.

一方、上記第二伝達軸13の他端部(図2の右端部)に固設した太陽歯車12の周囲に設けた第二キャリア18に遊星歯車19、20を、回転自在に支持している。尚、この第二キャリア18は、上記入力軸3及び第二伝達軸13と同心に配置された、出力軸21の基端部(図2の左端部)に固設されている。又、上記各遊星歯車19、20は、互いに噛合すると共に、一方の遊星歯車19が上記太陽歯車12に、他方の遊星歯車20が、上記第二キャリア18の周囲に回転自在に設けた第二リング歯車22に、それぞれ噛合している。又、上記リング歯車17と上記第二キャリア18とを低速用クラッチ23により係脱自在とすると共に、上記第二リング歯車22とハウジング等の固定の部分とを、高速用クラッチ24により係脱自在としている。   On the other hand, planetary gears 19 and 20 are rotatably supported on a second carrier 18 provided around the sun gear 12 fixed to the other end portion (the right end portion in FIG. 2) of the second transmission shaft 13. . The second carrier 18 is fixed to the proximal end portion (left end portion in FIG. 2) of the output shaft 21 that is disposed concentrically with the input shaft 3 and the second transmission shaft 13. The planetary gears 19 and 20 mesh with each other, and one planetary gear 19 is provided in the sun gear 12 and the other planetary gear 20 is provided around the second carrier 18 so as to be rotatable. The ring gears 22 mesh with each other. The ring gear 17 and the second carrier 18 can be freely engaged and disengaged by a low speed clutch 23, and the second ring gear 22 and a fixed portion such as a housing can be freely disengaged by a high speed clutch 24. It is said.

又、特許文献2には、図3に示す様な無段変速装置が開示されている。この図3に示した無段変速装置は、前述の図2に示した従来から知られている無段変速装置と同様の機能を有するものであるが、遊星歯車式変速機2a部分の構造を工夫する事により、この遊星歯車式変速機2a部分の組立性を向上させている。入力軸3及び1対の入力側ディスク4a、4bと共に回転するキャリア7aの両側面に、それぞれ1対ずつの遊星歯車25a、25b、26a、26bを、回転自在に支持している。そして、上記キャリア7aの各側面に支持した各遊星歯車25a、25b同士、各遊星歯車26a、26b同士を、互いに噛合させると共に、内径側の遊星歯車25a、26aを、出力側ディスク5にその基端部(図3の左端部)を結合した中空回転軸14aの先端部(図3の右端部)及び伝達軸27の一端部(図3の左端部)にそれぞれ固設した第一、第二太陽歯車28、29に、外径側の遊星歯車25b、26bをリング歯車30に、それぞれ噛合させている。   Patent Document 2 discloses a continuously variable transmission as shown in FIG. The continuously variable transmission shown in FIG. 3 has the same function as that of the conventionally known continuously variable transmission shown in FIG. 2, but the structure of the planetary gear type transmission 2a is the same. By devising, the assemblability of the planetary gear type transmission 2a is improved. A pair of planetary gears 25a, 25b, 26a, and 26b are rotatably supported on both side surfaces of the carrier 7a that rotates together with the input shaft 3 and the pair of input side disks 4a and 4b. Then, the planetary gears 25a and 25b supported on the side surfaces of the carrier 7a and the planetary gears 26a and 26b are meshed with each other, and the planetary gears 25a and 26a on the inner diameter side are connected to the output side disk 5 with the base. First and second fixed respectively to the distal end portion (right end portion in FIG. 3) of the hollow rotary shaft 14a to which the end portion (left end portion in FIG. 3) is coupled and one end portion (left end portion in FIG. 3) of the transmission shaft 27. The planetary gears 25b and 26b on the outer diameter side are engaged with the ring gear 30 and the sun gears 28 and 29, respectively.

一方、上記伝達軸27の他端部(図3の右端部)に固設した第三太陽歯車31の周囲に設けた第二キャリア18aに遊星歯車32a、32bを、回転自在に支持している。尚、この第二キャリア18aは、上記入力軸3と同心に配置された出力軸21aの基端部(図3の左端部)に固設されている。又、上記各遊星歯車32a、32bは、互いに噛合すると共に、内径側の遊星歯車32aを上記第三太陽歯車31に、外径側の遊星歯車32bを、上記第二キャリア18aの周囲に回転自在に設けた第二リング歯車22aに、それぞれ噛合させている。又、上記リング歯車30と上記第二キャリア18aとを低速用クラッチ23aにより係脱自在とすると共に、上記第二リング歯車22aとハウジング等の固定の部分とを、高速用クラッチ24aにより係脱自在としている。   On the other hand, the planetary gears 32a and 32b are rotatably supported by the second carrier 18a provided around the third sun gear 31 fixed to the other end portion (the right end portion in FIG. 3) of the transmission shaft 27. . The second carrier 18a is fixed to the base end portion (left end portion in FIG. 3) of the output shaft 21a arranged concentrically with the input shaft 3. The planetary gears 32a and 32b mesh with each other, and the planetary gear 32a on the inner diameter side is rotatable around the third sun gear 31 and the planetary gear 32b on the outer diameter side is rotatable around the second carrier 18a. Are respectively meshed with the second ring gear 22a. Further, the ring gear 30 and the second carrier 18a can be engaged and disengaged by a low speed clutch 23a, and the second ring gear 22a and a fixed part such as a housing can be engaged and disengaged by a high speed clutch 24a. It is said.

この様に構成する改良された無段変速装置の場合、上記低速用クラッチ23aを接続し、上記高速用クラッチ24aの接続を断った状態では、上記入力軸3の動力が、上記リング歯車30を介して上記出力軸21aに伝えられる。そして、トロイダル型無段変速機1の変速比を変える事により、無段変速装置全体としての変速比、即ち、上記入力軸3と上記出力軸21aとの間の変速比が変化する。これに対して、上記低速用クラッチ23aの接続を断ち、上記高速用クラッチ24aを接続した状態では、上記入力軸3の動力が、前記各遊星歯車25a、25b、上記リング歯車30、前記各遊星歯車26a、26b、前記伝達軸27、前記各遊星歯車32a、32b、上記第二キャリア18aを介して、上記出力軸21aに伝えられる。そして、上記トロイダル型無段変速機1の変速比を変える事により、無段変速装置全体としての変速比が変化する。   In the case of the improved continuously variable transmission configured as described above, the power of the input shaft 3 causes the ring gear 30 to be driven when the low speed clutch 23a is connected and the high speed clutch 24a is disconnected. Via the output shaft 21a. By changing the gear ratio of the toroidal-type continuously variable transmission 1, the gear ratio of the continuously variable transmission, that is, the gear ratio between the input shaft 3 and the output shaft 21a changes. On the other hand, when the low speed clutch 23a is disconnected and the high speed clutch 24a is connected, the power of the input shaft 3 is applied to the planetary gears 25a, 25b, the ring gear 30, and the planetary gears. It is transmitted to the output shaft 21a through the gears 26a and 26b, the transmission shaft 27, the planetary gears 32a and 32b, and the second carrier 18a. And the gear ratio as the whole continuously variable transmission changes by changing the gear ratio of the toroidal type continuously variable transmission 1.

尚、次述する図4〜5に示す様に、外径側の遊星歯車25として、軸方向寸法が長いものを使用すると共に、この長い遊星歯車25を内径側の遊星歯車25a、26a及びリング歯車30aに噛合させる構造を採用しても、同様の機能を発揮できる。この場合には、直径の大きなリング歯車30aの軸方向寸法を短縮して、遊星歯車式変速機2bの軽量化を図れる。   As shown in FIGS. 4 to 5 to be described below, an outer planetary gear 25 having a long axial dimension is used, and this long planetary gear 25 is used as an inner planetary gear 25a, 26a and a ring. The same function can be exhibited even if a structure for meshing with the gear 30a is employed. In this case, the axial dimension of the ring gear 30a having a large diameter can be shortened to reduce the weight of the planetary gear type transmission 2b.

前述した図2及び上述した図3の構造は、原理的なもので、具体的な構造を示したものではない。これに対して図4〜6は、先に考えた無段変速装置の具体的構造の1例を示している。尚、この構造では、上述した様に、外径側の遊星歯車25として軸方向寸法が長いものを使用すると共に、この長い遊星歯車25を、内径側の遊星歯車25a、26a及びリング歯車30aに噛合させている。   The above-described structures of FIG. 2 and FIG. 3 described above are fundamental and do not indicate a specific structure. 4 to 6 show an example of a specific structure of the continuously variable transmission considered above. In this structure, as described above, the planetary gear 25 on the outer diameter side having a long axial dimension is used, and the long planetary gear 25 is used as the planetary gears 25a and 26a and the ring gear 30a on the inner diameter side. Meshing.

ハウジング33内の所定位置に1対の支柱34、34を、連結板35とバルブボディー36とを介して支持固定している。このバルブボディー36は、トロイダル型無段変速機1の変速比を制御する為の制御弁装置を内蔵している。又、上記各支柱34、34の両端部には、パワーローラ6、6(図2参照)を支持するトラニオンの両端部を揺動及び軸方向の変位自在に支持する為の支持板37、37を支持している。又、環状に形成した上記各支柱34、34の中間部同士の間に出力側ディスク5を、1対の転がり軸受38、38により、回転自在に支持している。そして、上記出力側ディスク5の内径側に中空回転軸14aの基半部(図4の左半部)を、スプライン係合に基づき、回転伝達自在に結合している。   A pair of support columns 34 are supported and fixed at predetermined positions in the housing 33 via a connecting plate 35 and a valve body 36. The valve body 36 incorporates a control valve device for controlling the gear ratio of the toroidal type continuously variable transmission 1. Further, support plates 37 and 37 for supporting both ends of the trunnion for supporting the power rollers 6 and 6 (see FIG. 2) in a swingable and axially displaceable manner at both ends of each of the columns 34 and 34, respectively. Support. Further, the output side disk 5 is rotatably supported by a pair of rolling bearings 38, 38 between the intermediate portions of the respective pillars 34, 34 formed in an annular shape. And the base half part (the left half part of FIG. 4) of the hollow rotating shaft 14a is coupled to the inner diameter side of the output side disk 5 based on the spline engagement so as to be able to transmit the rotation.

そして上記中空回転軸14aの内側に、入力軸3aを挿通している。この入力軸3aの中間部基端寄り部分に一方(図4の左方)の入力側ディスク4aを、ボールスプライン39を介して支持すると共に、油圧式の押圧装置40により上記入力側ディスク4aを、上記出力側ディスク5に向け、押圧自在としている。これに対して他方(図4の右方)の入力側ディスク4bは上記中空回転軸14aの中間部先端寄り(図4の右寄り)部分の周囲に、ラジアルニードル軸受41により、回転及び軸方向の変位自在に支持している。そして、上記他方の入力側ディスク4bと上記入力軸3aとを、キャリア7aを介して結合している。従って、上記出力側ディスク5を軸方向両側から挟む位置に設けた1対の入力側ディスク4a、4bは、上記入力軸3aと上記キャリア7aとを介して、同期して回転する。   The input shaft 3a is inserted inside the hollow rotary shaft 14a. One input side disk 4a (on the left side in FIG. 4) is supported by a ball spline 39 near the base end portion of the input shaft 3a, and the input side disk 4a is supported by a hydraulic pressing device 40. The output side disk 5 can be pressed freely. On the other hand, the other input side disk 4b (on the right side in FIG. 4) is rotated and axially moved by a radial needle bearing 41 around a portion near the tip of the middle part (right side in FIG. 4) of the hollow rotating shaft 14a. Supports displaceability. The other input side disk 4b and the input shaft 3a are coupled via a carrier 7a. Accordingly, the pair of input side disks 4a and 4b provided at the positions sandwiching the output side disk 5 from both sides in the axial direction rotate synchronously via the input shaft 3a and the carrier 7a.

上記キャリア7aは、図5〜6に詳示する様に、断面L字形で全体を円環状とした中間支持板42と、それぞれが円輪状に形成された第一、第二両連結板43、44との間に、それぞれ複数本ずつ(例えば3本ずつ)の第一、第二各遊星軸45、46を、上記第一、第二両連結板43、44同士の間に複数本(例えば3本)の第三遊星軸47を、それぞれ掛け渡して成る。又、これら各遊星軸45〜47の周囲に前記各遊星歯車25a、26a、25を、それぞれラジアルニードル軸受48a、48b、48cを介して、回転自在に支持している。そして、外径側の遊星歯車25と内径側の各遊星歯車25a、26aとを互いに噛合させると共に、内径側の遊星歯車25a、26aを、上記中空回転軸14aの先端部(図4〜5の右端部)に固設した第一太陽歯車28又は伝達軸27の基端部に固設した第二太陽歯車29に、外径側の遊星歯車25を前記リング歯車30aに、それぞれ噛合させている。   As shown in detail in FIGS. 5 to 6, the carrier 7 a includes an intermediate support plate 42 having an L-shaped cross section and an annular shape as a whole, and first and second connecting plates 43 each formed in an annular shape, A plurality of (for example, three) first and second planetary shafts 45 and 46 are respectively provided between the first and second connecting plates 43 and 44 (for example, three). 3) third planetary shafts 47 are spanned over each other. The planetary gears 25a, 26a, 25 are rotatably supported around the planetary shafts 45-47 via radial needle bearings 48a, 48b, 48c, respectively. Then, the planetary gear 25 on the outer diameter side and the planetary gears 25a and 26a on the inner diameter side are engaged with each other, and the planetary gears 25a and 26a on the inner diameter side are connected to the distal end portion of the hollow rotary shaft 14a (see FIGS. 4 to 5). The planetary gear 25 on the outer diameter side is meshed with the ring gear 30a to the first sun gear 28 fixed to the right end portion) or the second sun gear 29 fixed to the base end portion of the transmission shaft 27, respectively. .

又、上記中間支持板42の中心に設けた円筒部49は、上記入力軸3aの中間部先端寄り部分にスプライン係合させ、ローディングナット50により抑え付けている。尚、図6に示す様に、上記中間支持板42の円輪部51と上記第一、第二各連結板43、44とは、前記各遊星歯車25a、26a、25から円周方向に外れた位置に設けた連結部57、57により、互いに連結している。図示の例の場合、上記キャリア7aを構成する上記中間支持板42と第一、第二各連結板43、44とを、一体に形成している。そしてこの構成により、上記キャリア7aの、回転伝達方向の力に対する強度及び剛性を確保している。又、前記他方の入力側ディスク4bと上記キャリア7aとの間での回転伝達を行なわせるべく、この他方の入力側ディスク4bの外側面複数個所に形成した凸部52と、上記第一連結板43の外周縁部に形成した切り欠き53とを係合させている。又、運転時には、駆動軸54により上記入力軸3aを回転駆動する。同時に、前記押圧装置40に油圧を導入して、各入力側ディスク4a、4b及び出力側ディスク5の側面と各パワーローラ6、6の周面との転がり接触部(トラクション部)の面圧を確保する。   A cylindrical portion 49 provided at the center of the intermediate support plate 42 is spline-engaged with a portion closer to the front end of the intermediate portion of the input shaft 3 a and is held down by a loading nut 50. As shown in FIG. 6, the annular portion 51 of the intermediate support plate 42 and the first and second connecting plates 43, 44 are disengaged from the planetary gears 25a, 26a, 25 in the circumferential direction. They are connected to each other by connecting portions 57, 57 provided at different positions. In the case of the illustrated example, the intermediate support plate 42 and the first and second connecting plates 43 and 44 constituting the carrier 7a are integrally formed. And by this structure, the intensity | strength and rigidity with respect to the force of the rotation transmission direction of the said carrier 7a are ensured. Further, in order to transmit the rotation between the other input side disk 4b and the carrier 7a, convex portions 52 formed at a plurality of locations on the outer side surface of the other input side disk 4b, and the first connecting plate A notch 53 formed on the outer peripheral edge portion of 43 is engaged. Further, during operation, the input shaft 3a is rotationally driven by the drive shaft 54. At the same time, hydraulic pressure is introduced into the pressing device 40, and the surface pressure of the rolling contact portion (traction portion) between the side surfaces of the input side disks 4a, 4b and the output side disk 5 and the peripheral surfaces of the power rollers 6, 6 is adjusted. Secure.

上述の様な図4〜6に示す無段変速装置の場合、他方の入力側ディスク4bとキャリア7aとの間の回転伝達を、凸部52と切り欠き53との凹凸係合により行なっている。又、トラクション部の面圧を確保する為に押圧装置40の発生する推力は、入力軸3a及びこの入力軸3aに固定したキャリア7aを構成する中間支持板42、第一連結板43を介して、上記他方の入力側ディスク4bに加わる。言い換えれば、この他方の入力側ディスク4bの外側面(図4〜6の右側面)と第一連結板43の片側面(図4〜6の左側面)との当接部である、これら入力側ディスク4b及び第一連結板43の径方向中間部(図5にwで表わす部分を入力側ディスク4b及び第一連結板43の中心軸αを中心に回転させてできる円輪状部分)に、上記押圧装置40の発生する推力に基づく力が加わる。   In the case of the continuously variable transmission shown in FIGS. 4 to 6 as described above, the rotation transmission between the other input side disk 4 b and the carrier 7 a is performed by the concave and convex engagement between the convex portion 52 and the notch 53. . Further, the thrust generated by the pressing device 40 in order to ensure the surface pressure of the traction portion is transmitted through the input shaft 3a and the intermediate support plate 42 and the first connecting plate 43 constituting the carrier 7a fixed to the input shaft 3a. To the other input side disk 4b. In other words, these inputs are the contact portions between the outer side surface (the right side surface in FIGS. 4 to 6) of the other input side disk 4b and one side surface (the left side surface in FIGS. 4 to 6) of the first connecting plate 43. In the radial intermediate portion of the side disk 4b and the first connecting plate 43 (a ring-shaped portion formed by rotating the portion represented by w in FIG. 5 around the central axis α of the input side disk 4b and the first connecting plate 43), A force based on the thrust generated by the pressing device 40 is applied.

一方、上記他方の入力側ディスク4bは、上記押圧装置40の発生する推力に基づく上記パワーローラ6、6から受ける力に基づいて、図7に誇張して示す様に、この入力側ディスク4bの外径寄り部分が上記第一連結板43の片側面に近付く方向(軸方向)に弾性変形する。即ち、運転時に上記推力に基づき上記他方の入力側ディスク4bに加わる力は、トロイダル型無段変速機の運転時に最大で5t(トン)程度となり、この様な力に基づく入力側ディスク4bの軸方向に関する弾性変形量は、コンマ数mm(10分の数mm)程度と無視できない量となる。そして、この様に他方の入力側ディスク4bが軸方向に弾性変形すると、この他方の入力側ディスク4bの外側面外径寄り部分と上記第一連結板43の片側面とが断続的に繰り返し当接する事で互いに擦れ合い、当該部分でフレッチング摩耗が生じる可能性がある。特に、上記入力ディスク4bが弾性変形する円周方向位置は、上記各パワーローラ6、6により押し付けられる部分が変化するのに伴って常に変化する。この為、上記擦れ合いの周波数は相当に高く(例えば百数十Hzに)なり、フレッチング摩耗発生の面からはかなり厳しい条件となる。   On the other hand, the other input side disk 4b is formed on the input side disk 4b as shown in an exaggerated manner in FIG. 7 based on the force received from the power rollers 6 and 6 based on the thrust generated by the pressing device 40. The portion closer to the outer diameter is elastically deformed in a direction (axial direction) approaching one side surface of the first connecting plate 43. That is, the force applied to the other input side disk 4b based on the thrust during operation is about 5 t (tons) at the maximum during the operation of the toroidal continuously variable transmission, and the shaft of the input side disk 4b based on such a force. The amount of elastic deformation related to the direction is a comma number of mm (a few tenths of a millimeter) and cannot be ignored. When the other input side disk 4b is elastically deformed in the axial direction in this way, the outer surface of the other input side disk 4b and the one side surface of the first connecting plate 43 are repeatedly and repeatedly applied. When they come into contact with each other, they rub against each other, and there is a possibility that fretting wear will occur at those portions. In particular, the circumferential position at which the input disk 4b is elastically deformed always changes as the portions pressed by the power rollers 6 and 6 change. For this reason, the frequency of the rubbing is considerably high (for example, hundreds of tens Hz), which is a severe condition in terms of occurrence of fretting wear.

この様なフレッチング摩耗は、上記キャリア7aを所定位置から軸方向にずらせたり、剥離等の損傷の起点となる可能性がある。又、上記キャリア7aを構成する上記第一連結板43は、上記入力側ディスク4bに比べて比較的軟らかい金属で造られている。この為、上記入力側ディスク4bの弾性変形に伴って、この第一連結板43も同様に弾性変形する可能性がある。この様な第一連結板43の弾性変形は、この第一連結板43に支持した各遊星軸45〜47を傾かせ、これら各遊星軸45〜47に回転自在に支持した遊星歯車25a、26a、25とリング歯車30a及び太陽歯車28、29との噛合状態を悪化させる原因となる。そして、この様に噛合状態が悪化すると、これら各歯車25a、26a、25、30a、28、29の耐久性が低下すると共に、遊星歯車式変速機2bの伝達効率が低下する可能性がある。特に、本発明の対象となる無段変速装置の場合、上記遊星歯車式変速機2bの伝達効率がこの無段変速装置全体の伝達効率に大きな影響を及ぼす為、この遊星歯車式変速機2bの伝達効率が低下する事は好ましくない。又、生じた摩耗粉により、潤滑油(トラクションオイル)が汚染され、各部の潤滑状態を不良にする可能性も生じる。   Such fretting wear may cause the carrier 7a to shift in the axial direction from a predetermined position, or may be a starting point of damage such as peeling. The first connecting plate 43 constituting the carrier 7a is made of a relatively soft metal as compared with the input side disk 4b. For this reason, with the elastic deformation of the input side disk 4b, the first connecting plate 43 may be similarly elastically deformed. Such elastic deformation of the first connecting plate 43 tilts the planetary shafts 45 to 47 supported by the first connecting plate 43, and planetary gears 25a and 26a rotatably supported on the planetary shafts 45 to 47. , 25 and the ring gear 30a and the sun gears 28, 29 are deteriorated. If the meshing state deteriorates in this way, the durability of each of the gears 25a, 26a, 25, 30a, 28, 29 may be reduced, and the transmission efficiency of the planetary gear type transmission 2b may be reduced. In particular, in the case of a continuously variable transmission that is an object of the present invention, the transmission efficiency of the planetary gear transmission 2b greatly affects the transmission efficiency of the entire continuously variable transmission. It is not preferable that the transmission efficiency decreases. Further, the generated wear powder contaminates the lubricating oil (traction oil), which may cause the lubrication state of each part to be poor.

上記問題を改良するものとして、特許文献3に記載された無段変速装置がある。この無段変速装置は、図8に示すように、上記第一連結版43aの片側面と上記入力側ディスク4bの外側面とを、これら第一連結版43a及び入力側ディスク4bの径方向に関して内径側で当接させると共に、同じく外径側では隙間を介して対向させる。この結果、上記入力側ディスク4bの弾性変形が上記第一連結板43aに伝わりにくくなり、上記課題を解決できる。或いは、上記両側面同士を、キャリア7aのうちで軸方向の剛性が低い部分でのみ当接させたり、これら両側面に摩耗を防止する為の被膜を形成したり、潤滑油を溜める為の凹部を形成したものである。   As a means for improving the above problem, there is a continuously variable transmission described in Patent Document 3. As shown in FIG. 8, the continuously variable transmission is configured such that one side surface of the first connection plate 43a and the outer surface of the input side disk 4b are connected to each other in the radial direction of the first connection plate 43a and the input side disk 4b. While abutting on the inner diameter side, the outer diameter side is also opposed through a gap. As a result, the elastic deformation of the input side disk 4b is hardly transmitted to the first connecting plate 43a, and the above problem can be solved. Alternatively, the two side surfaces are brought into contact with only a portion of the carrier 7a having a low axial rigidity, a coating for preventing wear is formed on both side surfaces, or a recess for storing lubricating oil. Is formed.

特開2000−220719号公報JP 2000-220719 A 特開2004−225888号公報JP 2004-225888 A 特開2005−249181号公報JP 2005-249181 A

しかしながら、この先行技術には、キャリアを中間支持板の円輪部と連結板とを連結して構成しているため、キャリアの剛性が低く、その為、ディスクの変形により、キャリアが追従して変形してしまい、各遊星軸を傾かせてしまい、伝達効率が低下するという問題が有った。   However, in this prior art, since the carrier is configured by connecting the ring portion of the intermediate support plate and the connecting plate, the rigidity of the carrier is low, so that the carrier follows by the deformation of the disk. As a result, the planetary shafts are deformed and the transmission efficiency is lowered.

本発明は、上記問題を解決するために、互いに同心に配置された、入力軸と、トロイダル型無段変速機と、遊星歯車式変速機とを備え、このうちトロイダル型無段変速機は、内側ディスクと、内側ディスクの両側に、内側ディスクと同心に、且つ、内側ディスクとは独立した回転を自在として支持された1対の外側ディスクと、この内側ディスクの両側面と前記外側ディスクの側面との間にそれぞれ複数個ずつ挟持されたパワーローラとを備え、前記遊星歯車機構は、前記入力軸の周囲に、太陽歯車と、太陽歯車の周囲に配置されるリング歯車と、太陽歯車とリング歯車との間に配置される遊星歯車と、前記遊星歯車を支持するキャリアとを備え、これらトロイダル型無段変速機と遊星歯車式変速機とは、トロイダル型無段変速機を構成する外側ディスクと遊星歯車式変速機を構成するキャリアとを隣接させると共に、これら一方の外側ディスクとキャリアとが同期して回転する状態に組み合わされた無段変速装置において、前記入力軸に径方向外側に延びるフランジ部を設け、そのフランジ部と前記キャリアとを回転不動に係合し、前記外側ディスクに隣接する側の前記キャリアの内径より、前記太陽歯車の外径が大きく、また、軸方向に関して前記フランジ部の先端の前記外側ディスク側に段部を設け、その段部に係合する係合部をキャリアに設け、周方向に関して前記フランジ部と前記キャリアを凹凸係合し、さらに、前記フランジ部と前記キャリアを溶接した事を特徴とする。   In order to solve the above problem, the present invention includes an input shaft, a toroidal continuously variable transmission, and a planetary gear type transmission, which are arranged concentrically with each other. An inner disk, a pair of outer disks supported on both sides of the inner disk, concentrically with the inner disk, and independently of the inner disk so as to freely rotate, both side surfaces of the inner disk, and side surfaces of the outer disk And the planetary gear mechanism includes a sun gear around the input shaft, a ring gear arranged around the sun gear, a sun gear, and a ring. A planetary gear disposed between the gear and a carrier that supports the planetary gear, and the toroidal continuously variable transmission and the planetary gear type transmission constitute a toroidal continuously variable transmission. In the continuously variable transmission in which the side disk and the carrier constituting the planetary gear type transmission are adjacent to each other and the one outer disk and the carrier are rotated in synchronization with each other, the input shaft has a radially outer side. A flange portion extending to the outer disk, the flange portion and the carrier are non-rotatably engaged, and the outer diameter of the sun gear is larger than the inner diameter of the carrier on the side adjacent to the outer disk. A step portion is provided on the outer disk side of the end of the flange portion, an engagement portion that engages with the step portion is provided on the carrier, the flange portion and the carrier are engaged with each other in the circumferential direction, and the flange is further provided. The part and the carrier are welded.

本発明によれば、ディスクの変形剛性が高いところでローディング力を付与でき、伝達効率の低下を防止し、また、フレッチングの発生の防止や曲げ応力を低減するという効果が有る。   According to the present invention, it is possible to apply a loading force when the deformation rigidity of the disk is high, thereby preventing a decrease in transmission efficiency, and preventing the occurrence of fretting and reducing bending stress.

本発明の実施の形態の断面形状を示す図である。It is a figure which shows the cross-sectional shape of embodiment of this invention. 従来から知られている無段変速装置を示す略断面図である。It is a schematic sectional drawing which shows the continuously variable transmission conventionally known. 従来から知られている無段変速装置を示す略断面図である。It is a schematic sectional drawing which shows the continuously variable transmission conventionally known. 従来から知られている無段変速装置の具体的構造を示す略断面図である。It is a schematic sectional drawing which shows the specific structure of the continuously variable transmission conventionally known. 図4のB部に相当する拡大断面図である。It is an expanded sectional view equivalent to the B section of Drawing 4. キャリアを取り出して示す斜視図である。It is a perspective view which takes out and shows a carrier. 入力側ディスクの弾性変形を誇張して示す断面図である。It is sectional drawing exaggeratingly showing the elastic deformation of an input side disk. 従来の改良された無段変速装置を示す断面図である。It is sectional drawing which shows the conventional improved continuously variable transmission.

図1は、本発明の実施の形態の1例を示している。
本実施の形態は、遊星歯車式変速機101のキャリア102が、それぞれが円輪状に形成された第一、第二両連結部103,104の間に、複数本の遊星軸105を掛け渡して成る。そして、これら遊星軸の周囲に遊星歯車106を、ラジアルニードル軸受107を介して、回転自在に支持している。そして、遊星歯車106を、中空軸108の先端部に固設した太陽歯車109とリング歯車110に、それぞれ噛合させている。
FIG. 1 shows an example of an embodiment of the present invention.
In this embodiment, the carrier 102 of the planetary gear type transmission 101 spans a plurality of planetary shafts 105 between the first and second connecting portions 103 and 104 each formed in a ring shape. Become. A planetary gear 106 is rotatably supported around the planetary shaft via a radial needle bearing 107. Then, the planetary gear 106 is meshed with a sun gear 109 and a ring gear 110 fixed at the tip of the hollow shaft 108, respectively.

又、前記キャリア102の第一連結部103の内径側側面に、トロイダル型無段変速機111の外側ディスクである入力側ディスク112に向けて、凸部113を形成し、その凸部113に係合するように、前記入力側ディスク112の外側面に、凸部113に対応する位置に凹部114を形成する。第一連結部103の内径より、太陽歯車109の外径を大きくしている。   Further, a convex portion 113 is formed on the inner side surface of the first connecting portion 103 of the carrier 102 toward the input side disc 112 which is an outer disc of the toroidal type continuously variable transmission 111, and the convex portion 113 is engaged with the convex portion 113. A concave portion 114 is formed on the outer surface of the input side disk 112 at a position corresponding to the convex portion 113 so as to match. The outer diameter of the sun gear 109 is made larger than the inner diameter of the first connecting portion 103.

又、本実施の形態の場合、入力軸115の一端部に設けたフランジ部116の外径部117とキャリア102の第二連結部104の内径部118を互いに嵌合するように軸方向にインロウ形状に形成し、また、周方向にスプライン結合され、共に回転するようになっており、さらに溶接(ビーム溶接等)により一体としている。   In the case of the present embodiment, the outer diameter portion 117 of the flange portion 116 provided at one end portion of the input shaft 115 and the inner diameter portion 118 of the second connecting portion 104 of the carrier 102 are inserted in the axial direction so as to fit each other. It is formed into a shape, is splined in the circumferential direction, rotates together, and is further integrated by welding (beam welding or the like).

上述の様に構成する本実施の形態の場合には、第一連結部103の内径より、太陽歯車109の外径を大きくしているので、運転時により変形の少ない前記入力側ディスク112の外側面の内径寄り部分と前記キャリア102の第一連結部3の内径側側面を当接させることができるので、この入力側ディスク112と第一連結部103とが互いに擦れ合う事によるフレッチング摩耗を防止すると共に、第一連結部103と第二連結部104とから成るキャリア102を一体に形成しているので、連結部を互いに連結し一体とした場合に比べ、剛性を高めることができ、遊星軸105を支持する支持孔119,119も第一連結部103と第二連結部104とを同時に加工することで、支持孔119,119の同心度を良くでき、遊星軸105の傾きやずれを防止でき、遊星歯車式変速機101の伝達効率の低下を防止でき、入力軸115に設けたフランジ部116とキャリア102をインロウ形状でスプライン結合しているので、ローディングナットが必要なくなり、部品点数の減少となり、コスト削減をすることができる。   In the case of the present embodiment configured as described above, since the outer diameter of the sun gear 109 is made larger than the inner diameter of the first connecting portion 103, the outer side of the input side disk 112 that is less deformed during operation. Since the portion closer to the inner diameter of the side surface and the inner diameter side surface of the first connecting portion 3 of the carrier 102 can be brought into contact with each other, fretting wear caused by friction between the input side disk 112 and the first connecting portion 103 is prevented. In addition, since the carrier 102 composed of the first connecting portion 103 and the second connecting portion 104 is integrally formed, the rigidity can be increased compared to the case where the connecting portions are connected to each other and integrated, and the planetary shaft 105 The support holes 119 and 119 for supporting the first connection part 103 and the second connection part 104 can be processed at the same time, so that the concentricity of the support holes 119 and 119 can be improved. Inclination and deviation can be prevented, transmission efficiency of the planetary gear type transmission 101 can be prevented from being lowered, and the flange portion 116 provided on the input shaft 115 and the carrier 102 are spline-coupled in an in-row shape, so that a loading nut is not necessary. As a result, the number of parts is reduced, and the cost can be reduced.

尚、本実施の形態の場合、入力軸115とキャリア102の係合位置を太陽歯車の外径より外側とする。この様な位置関係とすることで、太陽歯車109をキャリア102内に挿入することができる。   In the present embodiment, the engagement position between the input shaft 115 and the carrier 102 is outside the outer diameter of the sun gear. With such a positional relationship, the sun gear 109 can be inserted into the carrier 102.

トロイダル型無段変速機と遊星歯車式変速機とを組み合せた無段変速装置として利用できる。   The present invention can be used as a continuously variable transmission that combines a toroidal type continuously variable transmission and a planetary gear type transmission.

1 トロイダル型無段変速機
2、2a、2b 遊星歯車式変速機
3、3a 入力軸
4、4a、4b 入力側ディスク
5 出力側ディスク
6 パワーローラ
7、7a キャリア
8 遊星歯車
9 遊星歯車
10 第一伝達軸
11 太陽歯車
12 太陽歯車
13 第二伝達軸
14、14a 中空回転軸
15 太陽歯車
16 遊星歯車
17 リング歯車
18、18a 第二キャリア
19 遊星歯車
20 遊星歯車
21、21a 出力軸
22、22a 第二リング歯車
23、23a 低速用クラッチ
24、24a 高速用クラッチ
25、25a、25b 遊星歯車
26a、26b 遊星歯車
27 伝達軸
28 第一太陽歯車
29 第二太陽歯車
30、30a リング歯車
31 第三太陽歯車
32a、32b 遊星歯車
33 ハウジング
34 支柱
35 連結板
36 バルブボディー
37 支持板
38 転がり軸受
39 ボールスプライン
40 押圧装置
41 ラジアルニードル軸受
42 中間支持板
43、43a、43b、43c 第一連結板
44 第二連結板
45 第一遊星軸
46 第二遊星軸
47 第三遊星軸
48a、48b、48c ラジアルニードル軸受
49 円筒部
50 ローディングナット
51 円輪部
52 凸部
53 切り欠き
54 駆動軸
55、55a 凹部
56、56a 凸部
57 連結部
58 凸部
59 凸部
60 凹部
61 間部分
62a、62b 皮膜
63 微小凹部
64 凹溝
65a、65b 環状凹溝
66 放射状凹溝
101 遊星歯車式変速機
102 キャリア
103 第一連結部
104 第二連結部
105 遊星軸
106 遊星歯車
107 ラジアルニードル軸受
108 中空軸
109 太陽歯車
100 リング歯車
111 トロイダル型無段変速機
112 入力側ディスク
113 凸部
114 凹部
115 入力軸
116 フランジ部
117 フランジ部外径部
118 第二連結部内径部
119 支持孔
1 Toroidal continuously variable transmission 2, 2a, 2b Planetary gear type transmission 3, 3a Input shaft 4, 4a, 4b Input side disk 5 Output side disk 6 Power roller 7, 7a Carrier 8 Planetary gear 9 Planetary gear 10 First Transmission shaft 11 Sun gear 12 Sun gear 13 Second transmission shaft 14, 14a Hollow rotating shaft 15 Sun gear 16 Planet gear 17 Ring gear 18, 18a Second carrier 19 Planet gear 20 Planet gear 21, 21a Output shaft 22, 22a Second Ring gear 23, 23a Low speed clutch 24, 24a High speed clutch 25, 25a, 25b Planetary gear 26a, 26b Planetary gear 27 Transmission shaft 28 First sun gear 29 Second sun gear 30, 30a Ring gear 31 Third sun gear 32a , 32b Planetary gear 33 Housing 34 Strut 35 Connecting plate 36 Valve body 37 Support plate 38 Rolling Receptacle 39 Ball spline 40 Press device 41 Radial needle bearing 42 Intermediate support plates 43, 43a, 43b, 43c First connection plate 44 Second connection plate 45 First planetary shaft 46 Second planetary shaft 47 Third planetary shafts 48a, 48b, 48c Radial needle bearing 49 Cylindrical portion 50 Loading nut 51 Annulus portion 52 Protruding portion 53 Notch 54 Drive shaft 55, 55a Concavity portion 56, 56a Convex portion 57 Connecting portion 58 Convex portion 59 Convex portion 60 Concavity portion 61 62a, 62b Film 63 Minute recessed portion 64 Groove groove 65a, 65b Annular groove 66 Radial groove 101 Planetary gear type transmission 102 Carrier 103 First connecting portion 104 Second connecting portion 105 Planetary shaft 106 Planetary gear 107 Radial needle bearing 108 Hollow shaft 109 Sun gear 100 ring gear 111 toroidal type continuously variable transmission 112 input side disc 113 convex portion 114 concave portion 115 input shaft 116 flange 117 flange outer diameter 118 second connection portion inner diameter portion 119 supporting hole

Claims (3)

互いに同心に配置された、入力軸と、トロイダル型無段変速機と、遊星歯車式変速機とを備え、このうちトロイダル型無段変速機は、内側ディスクと、内側ディスクの両側に、内側ディスクと同心に、且つ、内側ディスクとは独立した回転を自在として支持された1対の外側ディスクと、この内側ディスクの両側面と前記外側ディスクの側面との間にそれぞれ複数個ずつ挟持されたパワーローラとを備え、前記遊星歯車機構は、前記入力軸の周囲に、太陽歯車と、太陽歯車の周囲に配置されるリング歯車と、太陽歯車とリング歯車との間に配置される遊星歯車と、前記遊星歯車を支持するキャリアとを備え、これらトロイダル型無段変速機と遊星歯車式変速機とは、トロイダル型無段変速機を構成する外側ディスクと遊星歯車式変速機を構成するキャリアとを隣接させると共に、これら一方の外側ディスクとキャリアとが同期して回転する状態に組み合わされた無段変速装置において、前記入力軸に径方向外側に延びるフランジ部を設け、そのフランジ部と前記キャリアとを回転不動に係合し、前記外側ディスクに隣接する側の前記キャリアの内径より、前記太陽歯車の外径が大きい事を特徴とする無段変速装置。   An input shaft, a toroidal-type continuously variable transmission, and a planetary gear-type transmission, which are arranged concentrically with each other, include a toroidal-type continuously variable transmission, an inner disk and inner disks on both sides of the inner disk. A pair of outer disks supported concentrically and independently of the inner disk so as to freely rotate, and a plurality of powers sandwiched between both side surfaces of the inner disk and the side surfaces of the outer disk. The planetary gear mechanism includes a sun gear around the input shaft, a ring gear arranged around the sun gear, and a planetary gear arranged between the sun gear and the ring gear; A carrier for supporting the planetary gear, and these toroidal-type continuously variable transmission and planetary gear-type transmission constitute an outer disk and a planetary gear-type transmission constituting the toroidal-type continuously variable transmission. In the continuously variable transmission in which the one outer disk and the carrier rotate in synchronization with each other, a flange portion extending radially outward is provided on the input shaft, and the flange portion The continuously variable transmission is characterized in that the outer diameter of the sun gear is larger than the inner diameter of the carrier on the side adjacent to the outer disk. 軸方向に関して前記フランジ部の先端の前記外側ディスク側に段部を設け、その段部に係合する係合部をキャリアに設け、周方向に関して前記フランジ部と前記キャリアを凹凸係合する事を特徴とする請求項1に記載の無段変速装置。   A step portion is provided on the outer disk side at the tip of the flange portion with respect to the axial direction, an engagement portion that engages with the step portion is provided on the carrier, and the flange portion and the carrier are unevenly engaged with each other in the circumferential direction. The continuously variable transmission according to claim 1, wherein: 前記フランジ部と前記キャリアを溶接した事を特徴とする請求項1乃至2に記載の無段変速装置。   The continuously variable transmission according to claim 1, wherein the flange portion and the carrier are welded.
JP2009293844A 2009-12-25 2009-12-25 Continuously variable transmission Expired - Fee Related JP5397216B2 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10206204A1 (en) * 2002-02-15 2003-08-28 Daimler Chrysler Ag Toroidal variator system for transmission of road vehicle has ball and roller bearings for intermediate shaft carrying disks for toroidal drive and accommodating input shaft on further roller bearings
JP2004293683A (en) * 2003-03-27 2004-10-21 Nsk Ltd Continuously variable transmission
JP2005016717A (en) * 2003-06-02 2005-01-20 Nsk Ltd Continuously variable transmission device
JP2005325971A (en) * 2004-05-17 2005-11-24 Nsk Ltd Toroidal continuously variable transmission
JP2009197891A (en) * 2008-02-21 2009-09-03 Nsk Ltd Continuously variable transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10206204A1 (en) * 2002-02-15 2003-08-28 Daimler Chrysler Ag Toroidal variator system for transmission of road vehicle has ball and roller bearings for intermediate shaft carrying disks for toroidal drive and accommodating input shaft on further roller bearings
JP2004293683A (en) * 2003-03-27 2004-10-21 Nsk Ltd Continuously variable transmission
JP2005016717A (en) * 2003-06-02 2005-01-20 Nsk Ltd Continuously variable transmission device
JP2005325971A (en) * 2004-05-17 2005-11-24 Nsk Ltd Toroidal continuously variable transmission
JP2009197891A (en) * 2008-02-21 2009-09-03 Nsk Ltd Continuously variable transmission

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