JP2003056662A - Toroidal continuously variable transmission - Google Patents

Toroidal continuously variable transmission

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Publication number
JP2003056662A
JP2003056662A JP2001242718A JP2001242718A JP2003056662A JP 2003056662 A JP2003056662 A JP 2003056662A JP 2001242718 A JP2001242718 A JP 2001242718A JP 2001242718 A JP2001242718 A JP 2001242718A JP 2003056662 A JP2003056662 A JP 2003056662A
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Japan
Prior art keywords
cam
number
disc
continuously variable
toroidal continuously
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Pending
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JP2001242718A
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Japanese (ja)
Inventor
Makoto Fujinami
Kiyotaka Hirata
Hiroshi Ishikawa
清孝 平田
宏史 石川
誠 藤波
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Nsk Ltd
日本精工株式会社
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Priority to JP2001242718A priority Critical patent/JP2003056662A/en
Publication of JP2003056662A publication Critical patent/JP2003056662A/en
Application status is Pending legal-status Critical

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Abstract

PROBLEM TO BE SOLVED: To provide a toroidal continuously variable transmission having excellent durability of a claw engagement part between a drive shaft and a cam disc. SOLUTION: This toroidal continuously variable transmission is provided with p power rollers 4 respectively rolling in contact with traction surfaces 2a and 3a of input/output discs 2 and 3, the cam disc 9 having a cam surface 7b with which a line of the cam rollers 8 rolls in contact, and r grooves 13 provided in the cam disc 9 forming a claw engagement part formed between the cam disc 9 and a drive shaft 14 to input a drive torque. The number of the power rollers 4 is set as 2, the line number of the cam roller 8 is set as 4, and the number of grooves 13 in the cam disc 9 is set as 3. They are arranged in such a way that they will not simultaneously fall on the same rotation position at two or more positions.

Description

【発明の詳細な説明】 【0001】 【発明の属する技術分野】本発明は、入力ディスク及び出力ディスクのトラクション面とパワーローラとが転接する転接部の押し付け力をローディングカム機構によって発生させるトロイダル無段変速機に関する。 BACKGROUND OF THE INVENTION [0001] [Technical Field of the Invention The present invention provides a toroidal be generated by the loading cam mechanism the pressing force of the rolling contact portion traction surfaces of the input disk and output disk and the power rollers are in contact with rolling on the continuously variable transmission. 【0002】 【従来の技術】トロイダル無段変速機51は、図4に示すように入力ディスク52及び出力ディスク53とパワーローラ54を備えている。 [0002] toroidal continuously variable transmission 51 includes an input disc 52 and output disc 53 and the power rollers 54 as shown in FIG. 入力ディスク52と出力ディスク53は、互いに向合うトラクション面52a,5 The input disk 52 output disk 53, the traction surfaces 52a, 5 fit countercurrent to each other
3aを備えている。 It has a 3a. パワーローラ54は、トラクション面52a,53aのそれぞれに転接し、かつ、このトラクション面52a,53aに沿って揺動することで入力ディスク52及び出力ディスク53との転接部52b, Power rollers 54 tractive surface 52a, rolling contact to each 53a, and the rolling contact portion 52b of the input disk 52 and output disk 53 by swinging along the traction surface 52a, 53a,
53bを変化させる。 Changing the 53b. これにより、入力ディスク52と出力ディスク53の転接部52b、53bの回転半径が変わり、入力ディスク52と出力ディスク53の回転速度比が変化する。 Thus, the rolling contact portion 52b of the input disc 52 and output disc 53, is 53b turning radius of the turn, the rotational speed ratio of the input disk 52 and output disk 53 varies. 【0003】また、パワーローラ54と各ディスク5 [0003] In addition, each disk 5 and power roller 54
2,53とが転接している転接部52b,53bにおける摩擦力は、駆動トルクに応じて変化させることが好ましい。 The rolling contact portion 52b in which the 2, 53 are rolling contact, the friction force in 53b, it is preferable to change in response to the driving torque. この摩擦力は、転接部52b,53bにおける押し付け力によって決まる。 The frictional force is determined by the pressing force of the rolling contact portion 52 b, 53b. そこで、この押付け力の発生には、駆動トルクに応じて押し付け力を変化させるローディングカム機構55が好適に採用されている。 Therefore, the generation of the pressing force, the loading cam mechanism 55 for changing the pressing force in accordance with the driving torque is preferably employed. 【0004】このローディングカム機構55は、対面する一対のカム面55a,55bと、その間でそれぞれのカム面55a,55bに転接するカムローラ55cとによって構成されている。 [0004] The loading cam mechanism 55, facing pair of cam surfaces 55a, and 55b, are constituted by a cam roller 55c in contact rolling the respective cam surfaces 55a, 55b therebetween. 通常、一方のカム面55aが、 Usually, the one of the cam surfaces 55a,
入力ディスク52のトラクション面52aと反対の面 Face opposite to the traction surface 52a of the input disk 52
(背面)に一体に形成され、これに対向する他方のカム面55bがカムディスク56に形成されている。 Is formed integrally with the (rear), the other cam surface 55b which faces are formed on the cam disc 56 thereto. カムディスク56は、入力ディスク52がボールスプライン機構57で嵌合している入力軸58の端部58aとアンギュラ玉軸受構造で係合している。 The cam disc 56 has an input disk 52 are engaged by the end portion 58a and the angular ball bearing structure of the input shaft 58 which is fitted in the ball spline mechanism 57. カムディスク56のカム面55bと反対の面には、駆動軸59の爪59aと係合する溝56aが設けられている。 The surface opposite the cam surface 55b of the cam disc 56, the pawl 59a engages grooves 56a of the drive shaft 59 is provided. 駆動軸59の爪59a Claw 59a of the drive shaft 59
及びカムディスク56の溝56aからなる爪係合部は、 And the claw engagement portion consisting of the groove 56a of the cam disc 56,
周方向に等配で複数か所設けられており、この爪59a Are provided a plurality positions at equal intervals in the circumferential direction, the pawl 59a
と溝56aの回転方向に互いに当接する側面59b,5 Side 59b, abutting each other in the rotational direction of the grooves 56a and 5
6bによって駆動トルクの伝達を行っている。 It is carried out transmission of the driving torque by 6b. 【0005】この爪係合部を介してカムディスク56に駆動軸59から駆動トルクが加わると、カム面55a, [0005] When the driving torque from the drive shaft 59 to the cam disk 56 through the claw engaging portion is applied, the cam surfaces 55a,
55bの間に挟まれたカムローラ55cは、カム面55 Cam roller 55c sandwiched between 55b, the cam surface 55
a,55bの間で転動し、これらのカム面55a,55 a, roll between 55b, these cam surfaces 55a, 55
bに回転方向の位相差を生じさせるとともに、カム面5 Together causes a phase difference between the rotational direction b, the cam surface 5
5a,55b間距離(カムディスク56と入力ディスク52の相対距離)を押し広げる。 5a, push the 55b distance (relative distance of the cam disc 56 and the input disk 52). 出力ディスク53は、 Output disk 53,
図示しない軸受あるいは鏡対称に配置された他の出力ディスクによってパワーローラ54から離れる方向に係止されている。 Is engaged in a direction away from the power rollers 54 by other output disk disposed in the bearing or mirror symmetrical (not shown). 【0006】したがって、駆動トルクが加わると、ローディングカム機構55によって、入力ディスク52から離れる方向に付勢されたカムディスク56が入力軸58 Accordingly, when the driving torque is applied, the loading cam mechanism 55, the cam disc 56 which is biased in a direction away from the input disk 52 the input shaft 58
を軸方向に引っ張る。 The pull in the axial direction. そのため、図示しない他端が入力ディスク52と鏡対称に配置された他の入力ディスク、 Therefore, the other input disc and the other end (not shown) is disposed on the input disc 52 and the mirror symmetry,
あるいは軸受によって軸方向の移動が阻止されている入力軸58は、軸方向に弾性変形する。 Alternatively the input shaft 58 to move in the axial direction is prevented by the bearing is elastically deformed in the axial direction. 【0007】すなわち、入力軸59の張力によって、入力ディスク52がパワーローラ54の方向に付勢され、 Namely, by the tension of the input shaft 59, the input disc 52 is urged in the direction of the power roller 54,
入力ディスク52とパワーローラ54の転接部52b、 Rolling contact portion 52b of the input disc 52 and the power rollers 54,
及びパワーローラ54と出力ディスク53の転接部53 And rolling contact portion 53 of the power rollers 54 output disk 53
bの押し付け力が発生している。 b of the pressing force is generated. そして、入力軸58が伸びた分だけカムディスク56が入力ディスク52から離れる方向に移動するので、溝56aが爪59aと深く係合する。 Then, only the cam disk 56 min the input shaft 58 extending so moves away from the input disk 52, a groove 56a is deeper engagement with the pawl 59a. また、入力ディスク52及びカムディスク5 The input disc 52 and the cam disc 5
6は、カムローラ55cに押圧されてわずかに撓む。 6, bent slightly pressed against the cam roller 55c. 【0008】一定の駆動トルクがかかった状態では、カムディスク56と入力ディスク52は、回転方向の位相差が一定に保たれた状態でともに回転し、入力ディスク52から出力ディスク53へパワーローラ54を介して駆動トルクが伝達される。 [0008] In a state in which took constant driving torque, the input disc 52 and cam disc 56 are both rotated in a state where the phase difference of the rotational direction is kept constant, the power rollers 54 from the input disk 52 to the output disc 53 driving torque is transmitted through. 【0009】 【発明が解決しようとする課題】しかしながら、図5に示すように入力ディスク52の外径寄りの位置にパワーローラ54が転接する場合、入力ディスク52は、カムローラ55cによってパワーローラ54の方向に付勢されるとともに、この反力をパワーローラ54との転接部52bから受ける。 [0009] SUMMARY OF THE INVENTION However, if the power rollers 54 to the position outside 径寄Ri of the input disk 52 as shown in FIG. 5 is rolling contact, the input disc 52, the power rollers 54 by the cam roller 55c while being biased in a direction, it receives the reaction force from the rolling contact portion 52b of the power rollers 54. そのため、入力ディスク52は、カムローラ55cの位置で矢印A方向に撓むとともに、パワーローラ54の位置で矢印B方向に撓む。 Therefore, the input disc 52, together with the bend in the direction of arrow A at the position of the cam roller 55c, bent in the direction of arrow B at the position of the power roller 54. 【0010】また、カムローラ55cは、入力ディスク52をパワーローラ54の方向に付勢した状態で入力ディスク52とカムディスク56とともに回転する。 Further, the cam roller 55c is rotated together with the input disk 52 and the cam disk 56 while biasing the input disc 52 in the direction of the power roller 54. そして、カムローラ55cが入力ディスク52を挟んでパワーローラ54と反対側の位置に来たとき、パワーローラ54は、出力ディスク53の内径寄りの位置と転接しているので、カムローラ55cに付勢されて撓んでいた入力ディスク52を押し戻す。 Then, when it came to a position opposite the power roller 54 across the cam roller 55c is input disc 52, the power rollers 54, since the contact position and the rotation of the inner diameter side of the output disk 53 is biased to the cam roller 55c the input disc 52, which had been deflected Te push back. したがって、カムディスク56は、もともとカムローラ55cがある位置で入力ディスク52と反対の方向に撓んでいるが、この入力ディスク52がパワーローラ54によって押し戻されることにより、カムローラ55cを介して付勢されてさらに撓むこととなる。 Thus, the cam disc 56 has deflected in the opposite direction to the input disc 52 is originally the cam roller 55c located by the input disk 52 is pushed back by the power rollers 54, and is biased via a cam roller 55c so that the further bent. また、ローディングカム機構55は、パワーローラ54から反力を受けた状態となり、駆動トルクに対して反対方向のトルクをカムディスク56に伝達する。 Further, the loading cam mechanism 55 is in a state of being subjected to reactive force from the power rollers 54, to transmit torque in the opposite direction to the cam disc 56 relative to the drive torque. 【0011】また、駆動トルクの大きさによってカムローラ55cの列の位置は、回転方向に変化する。 [0011] The position of the row of cam rollers 55c by the size of the drive torque is changed in the direction of rotation. そのため、カムローラ55cの列の位置(位相)が、カムディスク56のカム面55bと反対の面に設けられた溝56 Therefore, the position of the row of cam rollers 55c (phase) is a groove 56 provided on the surface opposite the cam surface 55b of the cam disc 56
aの位置(位相)と一致した場合、カムローラ55cの列がパワーローラ54の位置に一致する。 If a match with the position of a (phase), the column of the cam roller 55c matches the position of the power roller 54. この場合には、カムローラ55cが転接している部分のカムディスク56がパワーローラ54と反対の方向(矢印C)に撓むことで、溝56aが歪むとともに、駆動トルクに対して反対方向のトルクが加わり、溝56aと爪59aの爪係合部に過大負荷がかかる。 In this case, by the cam disk 56 of the portion cam roller 55c is rolling contact is bent in a direction opposite to the power roller 54 (arrow C), with the groove 56a is distorted, the opposite direction of the torque to the driving torque It is added, such an excessive load on the claw engaging portion of the groove 56a and the claw 59a. 【0012】例えば、図6に示すようにカムローラ55 [0012] For example, cam rollers 55 as shown in FIG. 6
cの列が4列、溝が6か所回転方向に等配で設けられ、 Column of c is four rows, the grooves are provided at equal intervals in the six rotational direction,
駆動トルクによってカムディスク56と入力ディスク5 Type cam disc 56 by the driving torque disk 5
2とが相対的に回動してカムローラ55cの列の位相と溝56aの位相が回転軸58に対して点対称となる2か所で一致する場合、この2か所がパワーローラ54の位置と一致すると(D,E)、カムディスク56が撓むことでこの2か所の溝56aが歪む。 If 2 are relatively rotated to cam roller 55c column phase and the groove 56a of the phase matches in two places to be point symmetry with respect to the rotation axis 58, the two at the position of the power roller 54 When consistent with (D, E), the two grooves 56a is distorted by the cam disk 56 is bent. 【0013】溝56aの形状に歪が生じると、図5に示す各爪59aの側面59bと各溝56aの側面56bとがそれぞれ均等に当接しなくなる。 [0013] distortion to the shape of the groove 56a is caused, and the side surface 56b of the side surface 59b and the grooves 56a of each pawl 59a as shown in FIG. 5 not evenly abut respectively. このとき同時に爪係合部に過大負荷がかかると、爪59または溝56が磨耗、変形、あるいは疲労破壊する恐れがある。 When this time-consuming an excessive load on the claw engaging portion simultaneously, the pawl 59 or the groove 56 is worn, deformed, or there is a risk of fatigue failure. そして、 And,
この磨耗や変形、あるいは疲労破壊により、爪59または溝56にかかる負荷が不均一になることで、駆動軸5 The wear or deformation, or by fatigue fracture, that the load on the pawl 59 or the groove 56 is uneven, the drive shaft 5
9からカムディスク56に駆動トルクが伝わり難くなる。 Driving torque is not easily transmitted to the cam disk 56 from 9. その結果、ローディングカム機構55によって入力ディスク52とパワーローラ54の適切な押付け力が得られなくなり、トラクション面52a,53aにすべりが生じる恐れがある。 As a result, an appropriate pressing force of the input disk 52 and power roller 54 is no longer obtained by the loading cam mechanism 55, there is a possibility that the traction surfaces 52a, the sliding 53a occurs. 【0014】そこで、本発明は、駆動軸とカムディスクの爪係合部の耐久性に優れるトロイダル無段変速機を提供することを目的とする。 [0014] Therefore, an object of the present invention is to provide a toroidal continuously variable transmission which is excellent in durability of the claw engaging portion of the drive shaft and the cam disk. 【0015】 【課題を解決するための手段】そこで、本発明は、入力ディスクと、出力ディスクと、これらディスクに形成されたトラクション面のそれぞれに転接するp個のパワーローラと、前記入力ディスクと同じ回転軸を中心に回転するq列のカム転子の列と、このカム転子を入力ディスクとの間に挟んで設けられたカムディスクと、このカムディスクとこのディスクに駆動トルクを入力する駆動軸とを接続するrか所の爪係合部とを備えたトロイダル無段変速機を前提とする。 [0015] Means for Solving the Problems] Therefore, the present invention includes an input disc, an output disc, a p number of power rollers rolling contact with the respective traction surfaces formed on these disks, and the input disk a row of cam rotor of q column rotate about the same axis of rotation, a cam disc which is sandwiched therebetween disposed between the cam rotor of the input disk to input the driving torque and the cam disc in the disc It assumes a toroidal continuously variable transmission that includes a r locations of the claw engagement portion for connecting the drive shaft. そして、p個のパワーローラとq列のカム転子の列とrか所の爪係合部のそれぞれを、 Then, each of the columns and r positions of the claw engaging portion of the cam rotor of p pieces of the power roller and q columns,
回転軸の軸方向に見て2か所以上が同時に同じ回転位置にこないように配置したトロイダル無段変速機とする。 Or two when viewed in the axial direction of the rotating shaft is a toroidal continuously variable transmission which is arranged so as simultaneously not come in the same rotational position. 【0016】また、確実にパワーローラ、カムローラまたはカムボール、係合部のそれぞれ2か所が同時に同じ回転位置とならないようにするために、パワーローラの個数p、カム転子の列数q、及び爪係合部の数rが、2 Further, reliable power roller, cam roller or cam ball, in order to respectively two at the engagement portion does not become the same rotational position at the same time, the number p of the power roller, the number of columns q of the cam rotor, and the number r of the pawl engaging part, 2
以上の公約数を持たない数の組合せとする。 The number of combinations that do not have a common divisor of the above. もしくは、 Or,
パワーローラの個数p、カム転子の列数q、及び爪係合部の数rのうちの少なくともいずれか1つが奇数である数の組合せとするか、パワーローラの数pとカム転子の列数qの内の少なくともいずれか一方を偶数であるときに爪係合部の数rが奇数である数の組合せとするか、爪係合部の数rがカム転子の列数qの整数倍を除く数の組合せとする。 The number of power rollers p, the number of columns q of the cam rotor, and whether at least any one of the number r of pawl engaging portion and the number of combinations is odd, the number p and the cam rotor of the power roller whether the number r of-claw engaging portion at least when it is one or even one of the columns q is the number of combinations is odd, the number r of pawl engaging portion of the column number q of the cam trochanter the number of combinations, except at integer multiples. 【0017】 【発明の実施の形態】本発明の一実施形態について、図1から図3を参照して説明する。 [0017] One embodiment of the embodiment of the present invention will be described with reference to FIGS. 図1に示すトロイダル無段変速機1は、入力ディスク2と出力ディスク3を2 Toroidal continuously variable transmission 1 shown in FIG. 1, the input disc 2 and the output disc 3 2
組備えている。 It has set. これらのディスク2,3は、トロイダル面状に対向して形成されたトラクション面2a,3aを備えている。 These disks 2 and 3 is provided with traction surfaces 2a formed to face the toroidal surface shape, the 3a. 入力ディスク2と出力ディスク3の間には、両方のトラクション面2a,3aにそれぞれ転接するパワーローラ4が2個ずつ配置されている。 Input between the disk 2 and output disk 3, power roller 4 both traction surfaces 2a, the 3a rolling contact respectively are arranged two by two. このパワーローラ4は、トラクション面2a,3aに沿って転接しつつ揺動する。 The power roller 4 is swung traction surface 2a, while rolling contact along 3a. これにより、入力ディスク2に対する出力ディスク3の回転速度比が無段階に変化する。 Thus, the rotational speed ratio of the output disc 3 to the input disc 2 is continuously varied. 入力ディスク2は、入力軸5の両端にボールスプライン機構6で嵌合しており、入力軸5の軸線に沿う方向に移動可能である。 Input disc 2 is fitted in the ball spline mechanism 6 across the input shaft 5 is movable in a direction along the axis of the input shaft 5. また、一方の入力ディスク2のパワーローラ4と反対側には、ローディングカム機構7が設けられている。 Further, on the opposite side of the power roller 4 of one of the input disk 2, a loading cam mechanism 7 it is provided. 【0018】ローディングカム機構7は、対向するカム面7a,7bと、これらカム面7a,7bにそれぞれ転接するカムローラ8(カム転子)を備えている。 The loading cam mechanism 7 is provided with opposed cam surfaces 7a which, 7b, these cam surfaces 7a, the cam roller 8 rolling contact each 7b (the cam trochanter). なお、 It should be noted that,
カム転子には、カムボールを用いることもできる。 The cam rotor, can also be used cam balls. 一方のカム面7aは、入力ディスク2と一体に形成されている。 One of the cam surface 7a is formed integrally with the input disk 2. 他方のカム面7bは、カムディスク9に形成されている。 The other cam surface 7b is formed on the cam disc 9. このカムディスク9は、入力軸5の基端部5aとの間に設けられたアンギュラ玉軸受部10で入力ディスク2から離れる方向の移動が阻止されている。 The cam disc 9 is moved in a direction away from the input disk 2 with angular contact ball bearing unit 10 provided between the base end portion 5a of the input shaft 5 is prevented. 【0019】また、図2に示すようにローディングカム機構7のカムローラ8は、カムディスク9の半径方向に複数個(本実施形態では3個)が一列に並べて設けられ、かつ、その列が保持器11で周方向に4か所等配で配置されている。 Further, the cam roller 8 of the loading cam mechanism 7 as shown in FIG. 2, a plurality (three in this embodiment) are provided in a row in the radial direction of the cam disc 9, and the column is maintained four in vessel 11 in the circumferential direction or the like are arranged in distribution. カムディスク9のカム面7bと反対側の面の中心寄りの位置には、カムディスク9の回転軸を中心とする同心円上に凸部12が形成されている。 The inboard position opposite to the surface with the cam surface 7b of the cam disc 9, the convex portion 12 is formed on a concentric circle around the rotation axis of the cam disc 9. また、凸部12には、この凸部12を横切る半径方向に溝13が複数箇所、具体的には3か所等配に形成されている。 Further, the convex portion 12, radially in the groove 13 is a plurality of locations across the convex portion 12, in particular are formed in distribution three locations, and the like. それぞれの溝13は、動力源の駆動トルクを伝達する駆動軸14に設けられた爪15と係合し、駆動軸14 Each groove 13 engages the pawl 15 provided on the drive shaft 14 for transmitting the driving torque of the power source, the drive shaft 14
の回転方向に互いに当接する側面13a,15aで駆動トルクを伝達する。 Contacting side 13a in the rotational direction to each other, to transmit the driving torque at 15a. 【0020】このように構成されたトロイダル無段変速機1は、駆動軸14の爪15とカムディスク9の溝13 The toroidal continuously variable transmission 1 thus configured, the nail 15 of the drive shaft 14 and the groove 13 of the cam disc 9
とによる爪係合部を介して駆動軸14から駆動トルクがカムディスク9に伝達されると、この駆動トルクによってカムディスク9が入力ディスク2に対して相対的に回動する。 When the drive torque from the drive shaft 14 via a claw engaging portion by is transmitted to the cam disc 9 and the cam disc 9 is relatively rotated with respect to the input disc 2 by the driving torque. これにより、カム面7a,7bに挟まれたカムローラ8が転動し、カム面7a,7b同士、すなわち、 Accordingly, the cam roller 8 which is sandwiched between the cam surfaces 7a, and 7b are rolling, the cam surfaces 7a, 7b to each other, i.e.,
カムディスク9と入力ディスク2との間を相対的に広げる。 Spread relatively between the cam disc 9 and the input disc 2. 【0021】このとき、カムディスク9が、入力軸5の基端部5aでパワーローラ4から離れる方向の動きを阻止されているとともに、入力軸5の先端側に設けられた入力ディスク2が軸線に沿って離れる方向の移動がナット16によって阻止されている。 [0021] At this time, the cam disk 9, the input shaft with being prevented movement away from the power roller 4 with 5 of the base end portion 5a, the input disc 2 is an axial line provided on the tip side of the input shaft 5 moving direction of away along it is blocked by a nut 16. したがって、カムディスク9と入力ディスク2がローディングカム機構7によって互いに離れる方向にそれぞれ押圧されると、入力ディスク2がパワーローラ4の方向に押圧され、入力ディスク2とパワーローラ4の転接部2bでの押付け力が発生する。 Thus, the cam disc 9 and the input disc 2 is respectively pressed in a direction away from each other by the loading cam mechanism 7, the input disc 2 is pressed in the direction of the power roller 4, the input disc 2 and the power roller 4 rolling contact portion 2b pressing force is generated in. そして、駆動トルクが一定の場合、カムローラ8の列は、カムディスク9との相対的回転位置(位相) Then, when the driving torque is constant, the column of the cam roller 8, the relative rotational positions of the cam disk 9 (phase)
を維持した状態でカムディスク9とともに回転する。 It rotates with the cam disc 9 while maintaining the. なお、パワーローラ4と出力ディスク3との押付け力もこのとき同時に発生する。 Incidentally, the pressing force of the power roller 4 and the output disc 3 is also generated at the same time this time. 【0022】パワーローラ4が、トラクション面2a, [0022] The power roller 4, the traction surface 2a,
3aに沿って揺動し、特に、パワーローラ4が、入力ディスク2の外径寄りのトラクション面2a、及び出力ディスク3の内径寄りのトラクション面3aにそれぞれ転接している場合、入力ディスク2は、カムローラ8によってパワーローラ4の方向に押圧されているとともに、 Swings along 3a, in particular, when the power roller 4, the traction surface 2a of the outer 径寄Ri of the input disk 2 and the inner diameter side of the traction surface 3a of the output disc 3 have rolling contact each input disc 2 , together they are pressed in the direction of the power roller 4 by the cam roller 8,
パワーローラ4によって押し返されることで外径寄りの部分がわずかに撓む。 The outer 径寄 Rino partially flexed slightly by being pushed back by the power roller 4. そして、図3に示すように入力ディスク2がカムローラ8とともに回転し、カムローラ8 Then, the input disc 2 as shown in FIG. 3 rotates together with the cam roller 8, the cam roller 8
の列が入力ディスク2を挟んでパワーローラ4と反対の位置に来ると、カムローラ8とパワーローラ4とが互いに入力ディスク2を挟んで押し合う。 Come to a position opposite the power roller 4 rows of across the input discs 2, jostling the cam roller 8 and the power roller 4 and the input disc 2 sandwiched therebetween together. 【0023】このとき、パワーローラ4は、出力ディスク3の内径寄りの位置と転接して支持されているため、 [0023] At this time, the power roller 4, because it is supported in contact position and rotation of the inner diameter side of the output disc 3,
パワーローラ4の方向に撓んでいた入力ディスク2を押し戻す。 Push back the input disk 2 that was deflected in the direction of the power roller 4. したがって、カムディスク9は、このカムローラ8から入力ディスク2に近寄る方向に押圧されてパワーローラ4と反対の方向に撓むか、駆動軸14の駆動トルクに対して反対のトルクを受ける。 Thus, the cam disc 9, or bent in a direction opposite to the power roller 4 is pressed in the direction come close to the input disc 2 from the cam roller 8 receives an opposite torque to the drive torque of the drive shaft 14. 【0024】図3に示すようにカムディスク9の溝13 The groove 13 of the cam disc 9, as shown in FIG. 3
は、パワーローラ4及びカムローラ8の列と2か所以上で同時に同じ回転位置とならない位置、すなわち、パワーローラ4とカムローラ8の列とカムディスク9の溝1 The column and the position at the same time does not become the same rotational position in two or more of the power roller 4 and the cam roller 8, i.e., the grooves 1 of the column and the cam disc 9 of the power roller 4 and the cam roller 8
3が、回転軸を中心として2か所以上で直列に並ばない位置、具体的には、2個のパワーローラ4、4列のカムローラ8の列、3か所のカムディスク9の溝13が、それぞれ等配で配置されている。 3, positions that do not line up in series two or more about the axis of rotation, specifically, the column of the two power rollers 4 and 4 rows of the cam roller 8, the groove 13 of the three places of the cam disc 9 They are disposed respectively equidistant. つまり、カムディスク9 In other words, the cam disk 9
が撓むことによって同じ回転位置にある溝13に歪などを生じるとともに、駆動トルクと反対方向のトルクを生じさせるカムローラ8の列は、ある駆動トルクのときに1箇所発生するに過ぎない。 With causing such distortion in the groove 13 at the same rotational position by flexing the column of the cam roller 8 causing the opposite direction of the torque and the drive torque is only generated one point at a certain drive torque. すなわち、カムディスク9 In other words, the cam disk 9
の溝13が2か所以上で同時に歪などを生じないとともに、駆動トルクに対して反対方向のトルクが2か所以上で同時に作用しない。 With grooves 13 does not occur and at the same time strain at two or more, does not act at the same time two or more torque in the opposite direction to the driving torque. したがって、その他の爪係合部では駆動軸14の爪15の側面15aとカムディスク9の溝13の側面13aとが均一に当接するので、駆動軸1 Thus, since the other claw engagement portion and the side surface 15a of the claw 15 of the drive shaft 14 and the side surface 13a of the groove 13 of the cam disc 9 is uniformly abut the drive shaft 1
4による駆動トルクが、カムディスク9へ伝わりやすい。 Driving torque by 4, easily transmitted to the cam disc 9. また、駆動トルクと反対方向のトルクは1か所でしか作用しないので、爪係合部の各爪15及び溝13に過大な負荷がかかりにくい。 Further, since the torque of the opposite direction of the driving torque it does not act only in one place, hardly consuming an excessive load on each pawl 15 and the groove 13 of the pawl engaging portion. また、前記一実施形態でのパワーローラ4とカムローラ8の列とカムディスク9の溝13のそれぞれの数の組合せは、それぞれの数が少ないので、製造性がよい。 Further, each of the number of combinations of the grooves 13 of the columns and the cam disc 9 of the power roller 4 and the cam roller 8 of the one embodiment, the respective number is small, good manufacturability. 【0025】また、前記構成に代えて、パワーローラ4 Further, instead of the configuration, the power roller 4
の個数をp、カムローラ8の列数をq、係合部(カムディスクの溝13)の数をrとした場合、p、q、rが2 If the number of p, q the number of columns of the cam roller 8, the engaging portion the number of (the groove 13 of the cam disc) was r, p, q, r are 2
以上の公約数を持たない数の関係とすると、駆動トルクに応じてカムローラ8の列の位置が変わっても、パワーローラ4の位置とカムローラ8の列の位置とカムディスク9の溝13の位置とが、2か所以上で同時に一致することは無い。 When more common divisor of the number of relationships that do not have, they change the position of the columns of the cam roller 8 in accordance with the driving torque, the position of the groove 13 of the position of the column position and the cam roller 8 of the power roller 4 and the cam disc 9 theft is, it is not to be met at the same time in two or more locations. したがって、カムディスク9のカム面7b Thus, the cam surface 7b of the cam disc 9
と溝13との位相(相対的な回転位置)を同期させずに任意に加工できるようになるので、製造時の取り扱いが容易になるのでよい。 Since it becomes possible to process in arbitrarily without synchronizing the phase (relative rotational position) of the groove 13 and may than become easy to handle during manufacture. 【0026】また、p、q、rの内の少なくともいずれか1つが奇数となるようにそれぞれ設けるか、pとqの内の少なくともいずれか一方が偶数のときにrが奇数となる、すなわち、p×qが偶数のときにrが奇数(例えば3)となるようにそれぞれ設けるか、rがqの整数倍を除く数となるようにそれぞれ設けることでも上記と同様の効果が得られ、パワーローラ4が入力ディスク2の外径寄りの位置、及び出力ディスク3の内径寄りの位置にそれぞれ転接して駆動トルクを伝達する場合、パワーローラ4の位置にカムローラ8の列、及びカムディスク9と駆動軸14との爪係合部であるカムディスク9側の溝13が、同時に2か所以上で重ならない。 Further, p, q, or at least any one of r respectively provided so as to be odd, p and at least one of the q is r is an odd number when the even number, namely, p × or q is respectively provided such that r when the even an odd (e.g. 3), r similar effects as described above by providing, respectively, as a number other than an integer multiple of q is obtained, power position outside 径寄Ri the roller 4 is input disc 2, and if each rolling contact with the position of the inner diameter side of the output disc 3 to transmit the drive torque, column of the cam roller 8 to the position of the power roller 4, and the cam disc 9 cam disc 9 side of the groove 13 is-claw engaging portion of the drive shaft 14, it does not overlap with two or more simultaneously. つまり、カムディスク9の溝13が2か所以上で同時に歪などを生じないとともに、駆動トルクに対して反対方向のトルクが2か所以上で同時に作用しない。 That, together with the no and simultaneously distortion groove 13 at two or more of the cam disc 9, does not act at the same time two or more torque in the opposite direction to the driving torque. したがって、同時にパワーローラ4とカムローラ8の列とカムディスク9の溝13とが、同じ回転位置となるのは、高だか1か所である。 Therefore, the groove 13 of the column and the cam disc 9 of the power roller 4 and the cam roller 8 at the same time, become the same rotational position is one position or it high. その結果、その他の係合部では、駆動軸14の爪15の側面15aとカムディスク9の溝13の側面13 As a result, the other engaging portion, the side surface of the side surface 15a and the groove 13 of the cam disc 9 of the pawl 15 of the drive shaft 14 13
aとが均一に当接するので、駆動軸14による駆動トルクが、カムディスク9へ伝わりやすい。 Since the a uniform contact, the drive torque by the drive shaft 14 is easily transmitted to the cam disc 9. また、駆動トルクと反対方向のトルクは、1か所で発生するにしか過ぎないので、爪係合部の各爪15及び溝13に過大な負荷がかかりにくい。 The torque of the opposite direction of the driving torque, because only only occur in one place, hardly consuming an excessive load on each pawl 15 and the groove 13 of the pawl engaging portion. 【0027】そして、パワーローラ4が2個、カムローラ8が4列、溝13が3か所である本実施形態は、それぞれが2か所以上で同時に同じ回転位置にならない最も好適な例である。 [0027] Then, the power roller 4 is two, the present embodiment the cam roller 8 is four rows, the grooves 13 are three places is the most preferred example, each not simultaneously in the same rotational position in two or more . 【0028】 【発明の効果】本発明のトロイダル無段変速機によれば、カムローラがパワーローラの位置に一致したときに、カムディスクが撓んで溝が歪んだり、カムディスクが駆動トルクに対して反対方向のトルクを受けて係合部に過大な負荷がかかることを抑制できるので、駆動軸とカムディスクの爪係合部の耐久性を向上できる。 According to the toroidal continuously variable transmission of the present invention, when the cam roller matches the position of the power roller, distorted groove is bent cam disc, against the cam disc drive torque it is possible to suppress an excessive load on the engagement portion receiving the opposite direction torque is applied, it is possible to improve the durability of the claw engaging portion of the drive shaft and the cam disk. 【0029】そして、 [0029] and,

【図面の簡単な説明】 【図1】本発明の第1の実施形態のトロイダル無段変速機を示す断面図。 BRIEF DESCRIPTION OF THE DRAWINGS sectional view showing a toroidal continuously variable transmission of the first embodiment of the present invention; FIG. 【図2】図1に示すトロイダル無段変速機の一部の分解斜視図。 2 is an exploded perspective view of a portion of a toroidal continuously variable transmission shown in FIG. 【図3】図2中のF3−F3で示す方向から見たトロイダル無段変速機のパワーローラとカムローラの列とカムディスクの溝の位置関係を示す図。 3 is a view showing a positional relationship between the power roller and the cam roller of the array and the groove of the cam disk of the toroidal continuously variable transmission as viewed from a direction indicated by F3-F3 in FIG. 【図4】従来のトロイダル無段変速機の断面図。 4 is a cross-sectional view of a conventional toroidal continuously variable transmission. 【図5】図4のトロイダル無段変速機の側面図。 FIG. 5 is a side view of the toroidal continuously variable transmission of FIG. 4. 【図6】図4中のF6−F6で示す方向から見たトロイダル無段変速機のパワーローラとカムローラの列とカムディスクの溝の位置関係を示す図。 6 shows a positional relationship between the power roller and the grooves of the cam roller of the columns and the cam disc in FIG. 4 toroidal continuously variable transmission as viewed from a direction indicated by F6-F6 in. 【符号の説明】 1…トロイダル無段変速機2…入力ディスク3…出力ディスク2a,3a…トラクション面4…パワーローラ7b…カム面8…カムローラ9…カムディスク13…溝(爪係合部) 14…駆動軸15…爪(爪係合部) [Description of Reference Numerals] 1 ... toroidal CVT 2 ... input disc 3 ... output disks 2a, 3a ... traction surface 4 ... power rollers 7b ... cam surface 8 ... cam roller 9 ... cam disc 13 ... groove (claw engaging portion) 14 ... drive shaft 15 ... claw (claw engaging portion)

フロントページの続き (72)発明者 平田 清孝 埼玉県羽生市大沼1丁目1番地 日本精工 株式会社内Fターム(参考) 3J051 AA03 BA03 BE09 CB06 EA06 EB01 EC01 EC02 EC03 Front page of the continuation (72) inventor Kiyotaka Hirata Saitama Prefecture Hanyu Onuma 1-chome 1 address NSK Ltd. in the F-term (reference) 3J051 AA03 BA03 BE09 CB06 EA06 EB01 EC01 EC02 EC03

Claims (1)

  1. 【特許請求の範囲】 【請求項1】入力ディスクと、出力ディスクと、これらディスクに形成されたトラクション面のそれぞれに転接するp個のパワーローラと、前記入力ディスクと同じ回転軸を中心に回転するq列のカム転子の列と、このカム転子を前記入力ディスクとの間に挟んで設けられたカムディスクと、このカムディスクとこのディスクに駆動トルクを入力する駆動軸とを接続するrか所の爪係合部とを備えたトロイダル無段変速機において、 p個の前記パワーローラとq列の前記カム転子の列とr And [claimed 1] input disk, rotates around the output disk, and p number of power rollers rolling contact with the respective traction surfaces formed in these discs, the same rotation shaft and the input disc a row of cam rotor of q columns to be connected to the cam disc which is sandwiched therebetween disposed between the cam rotor and said input disk, and a drive shaft for inputting the driving torque and the cam disc in the disc in the toroidal continuously variable transmission that includes a r locations of the claw engagement portion, the column of the cam rotor of p pieces of the power roller and q columns and r
    か所の前記爪係合部のそれぞれを、前記回転軸の軸方向に見て2か所以上が同時に同じ回転位置にないように配置したことを特徴とするトロイダル無段変速機。 Locations of each of the claw engagement portion, the toroidal continuously variable transmission, characterized in that more than two as viewed in the axial direction is arranged so as not in the same rotational position at the same time of the rotation shaft. 【請求項2】前記パワーローラの個数p、前記カム転子の列数q、及び前記爪係合部の数rが、2以上の公約数を持たないことを特徴とする請求項1に記載のトロイダル無段変速機。 The number of claim 2 wherein said power rollers p, the number of columns q of the cam rotor, and the number r of the pawl engaging portion, according to claim 1, characterized in that no more than one common divisor of the toroidal continuously variable transmission. 【請求項3】前記パワーローラの個数p、前記カム転子の列数q、及び前記爪係合部の数rの内の少なくともいずれか一つが奇数であることを特徴とする請求項1に記載のトロイダル無段変速機。 The number of wherein the power roller p, to claim 1 where the number of columns q of the cam rotor, and at least any one of a number r of the claw engagement portion, characterized in that an odd number toroidal continuously variable transmission according. 【請求項4】前記パワーローラの数pと前記カム転子の列数qの内の少なくともいずれか一方が偶数で、前記爪係合部の数rが奇数であることを特徴とする請求項1に記載のトロイダル無段変速機。 In wherein at least one is an even number of the columns q of the cam rotor to the number p of the power roller, claims, characterized in that the number r of the claw engagement portion is odd toroidal continuously variable transmission according to 1. 【請求項5】前記爪係合部の数rが、前記カム転子の列数qの整数倍を除く数であることを特徴とする請求項1 Claim 1 wherein the number r of the pawl engaging portion, wherein said a number other than an integer multiple of the number of columns q cam trochanter
    に記載のトロイダル無段変速機。 Toroidal continuously variable transmission according to. 【請求項6】前記パワーローラの数が2個、前記カム転子の列数が4列、前記爪係合部が3か所であることを特徴とする請求項1に記載のトロイダル無段変速機。 Two numbers of wherein said power rollers, the number of columns is four columns of the cam rotor, the toroidal continuously variable according to claim 1, wherein the claw engagement portion is three places transmission.
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