JP2007162897A

JP2007162897A - Toroidal type continuously variable transmission

Info

Publication number: JP2007162897A
Application number: JP2005362874A
Authority: JP
Inventors: Yasunori Oishi; 保徳大石
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2005-12-16
Filing date: 2005-12-16
Publication date: 2007-06-28

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission for supporting the disc axial slide of a power roller without complicating machining processes (with a sliding bearing having no crossing angle) in such a manner that its supporting structure is hardly influenced by the elastic deformation of a trunnion. SOLUTION: A bearing 100 for supporting an outer ring 28 movably in a direction O" perpendicular to a second axis O' is provided between a supporting plate portion 16 of the trunnion 15 extending approximately parallel to the second axis O' and the outer ring 28. A pair of pins 104 extending from the trunnion 15 engages with a long hole 102 of the outer ring 28. The long hole 102 and the pins 104 are relatively movable along the direction O" perpendicular to the second axis O', and tangential force generated between the power roller 11 and each of discs 2, 3 is supported between the pin 104 and the long hole 102. COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、自動車や各種産業機械の変速機などに利用可能なトロイダル型無段変速機に関する。 The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

例えば自動車用変速機として用いるダブルキャビティ式トロイダル型無段変速機は、図１３及び図１４に示すように構成されている。図１３に示すように、ケーシング５０の内側には入力軸（中心軸）１が回転自在に支持されており、この入力軸１の外周には、２つの入力側ディスク２，２と２つの出力側ディスク３，３とが取り付けられている。また、入力軸１の中間部の外周には出力歯車４が回転自在に支持されている。この出力歯車４の中心部に設けられた円筒状のフランジ部４ａ，４ａには、出力側ディスク３，３がスプライン結合によって連結されている。 For example, a double cavity toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. As shown in FIG. 13, an input shaft (center shaft) 1 is rotatably supported inside the casing 50, and two input-side disks 2, 2 and two outputs are provided on the outer periphery of the input shaft 1. Side disks 3 and 3 are attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

入力軸１は、図中左側に位置する入力側ディスク２とカム板７との間に設けられたローディングカム式の押圧装置１２を介して、駆動軸２２により回転駆動されるようになっている。また、出力歯車４は、２つの部材の結合によって構成された仕切壁１３を介してケーシング５０内に支持されており、この構成により、入力軸１の軸線（第１の軸線）Ｏを中心に回転できる一方で、軸線Ｏ方向の変位が阻止されている。 The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate 7 located on the left side in the drawing. . Further, the output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members. With this configuration, the output gear 4 is centered on the axis (first axis) O of the input shaft 1. While being able to rotate, displacement in the direction of the axis O is prevented.

出力側ディスク３，３は、入力軸１との間に介在されたニードル軸受５，５によって、入力軸１の軸線Ｏを中心に回転自在に支持されている。また、図中左側の入力側ディスク２は、入力軸１にボールスプライン６を介して支持され、図中右側の入力側ディスク２は、入力軸１にスプライン結合されており、これら入力側ディスク２は入力軸１と共に回転するようになっている。また、入力側ディスク２，２の内側面（凹面）２ａ，２ａと出力ディスク３，３の内側面（凹面）３ａ，３ａとの間には、パワーローラ１１（図１４参照）が回転自在に挟持されている。 The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. Further, the power roller 11 (see FIG. 14) is rotatable between the inner side surfaces (concave surfaces) 2a, 2a of the input side disks 2, 2 and the inner side surfaces (concave surfaces) 3a, 3a of the output disks 3, 3. It is pinched.

図１３中右側に位置する入力側ディスク２の内周面２ｃには、段差部２ｂが設けられ、この段差部２ｂに、入力軸１の外周面１ａに設けられた段差部１ｂが突き当てられるとともに、入力側ディスク２の背面（図１３の右面）がローディングナット９に突き当てられている。この構成によって、入力側ディスク２の入力軸１に対する軸線Ｏ方向の変位が実質的に阻止されている。また、カム板７と入力軸１の鍔部１ｄとの間には、皿ばね８が設けられており、この皿ばね８は、各ディスク２，２，３，３の凹面２ａ，２ａ，３ａ，３ａとパワーローラ１１，１１の周面１１ａ，１１ａとの当接部に押圧力を付与する。 A step portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 13, and the step portion 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step portion 2b. At the same time, the back surface (right surface in FIG. 13) of the input side disk 2 is abutted against the loading nut 9. With this configuration, the displacement of the input disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

図１４は、図１３のＡ−Ａ線に沿う断面図である。図１４に示すように、ケーシング５０の内側には、入力軸１に対し捻れの位置にある一対の枢軸１４，１４（以下、この枢軸１４の中心軸Ｏ’を第２の軸線という）を中心として揺動する一対のトラニオン１５，１５が設けられている。なお、図１４においては、入力軸１の図示は省略している。各トラニオン１５，１５は、第２の軸線Ｏ’と略平行に延びる本体部を成す支持板部１６と、支持板部１６の長手方向(図１４の上下方向)の両端部に、この支持板部１６の内側面側に折れ曲がる状態で形成された（支持板部１６の両端部から第２の軸線に対して傾斜して延びる）一対の折れ曲がり壁部２０，２０と、これらの折れ曲がり壁部２０，２０の外側面から第２の軸線Ｏ’に沿って互いに同心的に外方に延びる前記枢軸１４，１４とを有している。そして、折れ曲がり壁部２０，２０によって、各トラニオン１５，１５には、パワーローラ１１を収容するための凹状のポケット部Ｐが形成される。 14 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 14, a pair of pivot shafts 14 and 14 (hereinafter, the central axis O ′ of the pivot shaft 14 is referred to as a second axis) centered on the input shaft 1 is centered inside the casing 50. A pair of trunnions 15, 15 that swing is provided. In FIG. 14, the input shaft 1 is not shown. Each trunnion 15, 15 has a support plate portion 16 constituting a main body portion extending substantially parallel to the second axis O ′, and support plates at both ends in the longitudinal direction (vertical direction in FIG. 14) of the support plate portion 16. A pair of bent wall portions 20, 20 formed in a state of being bent toward the inner side surface of the portion 16 (extending from both ends of the support plate portion 16 with an inclination with respect to the second axis), and these bent wall portions 20. , 20 and the pivot shafts 14, 14 extending concentrically outward along the second axis O ′. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15.

支持板部１６の中央部には円孔２１が形成され、この円孔２１には変位軸２３の基端部２３ａが支持されている。そして、各枢軸１４，１４を中心として各トラニオン１５，１５を揺動させることにより、これら各トラニオン１５，１５の中央部に支持された変位軸２３の傾斜角度を調節できるようになっている。また、各トラニオン１５，１５の内側面から突出する変位軸２３の先端部２３ｂの周囲には、各パワーローラ１１，１１が回転自在に支持されており、各パワーローラ１１，１１は、各入力側ディスク２，２および各出力側ディスク３，３の間に挟持されている。なお、各変位軸２３，２３の基端部２３ａと先端部２３ｂとは、互いに偏心している。 A circular hole 21 is formed in the central portion of the support plate portion 16, and the base end portion 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. Further, the power rollers 11 and 11 are rotatably supported around the distal end portion 23b of the displacement shaft 23 protruding from the inner side surfaces of the trunnions 15 and 15. The power rollers 11 and 11 It is sandwiched between the side disks 2 and 2 and the output side disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

また、各トラニオン１５，１５の枢軸１４，１４はそれぞれ、一対のヨーク２３Ａ，２３Ｂに対して揺動自在および軸方向(図１４の上下方向)に変位自在に支持されており、各ヨーク２３Ａ，２３Ｂにより、トラニオン１５，１５はその水平方向の移動を規制されている。各ヨーク２３Ａ，２３Ｂは鋼等の金属のプレス加工あるいは鍛造加工により矩形状に形成されている。各ヨーク２３Ａ，２３Ｂの四隅には円形の支持孔１８が４つ設けられており、これら支持孔１８にはそれぞれ、トラニオン１５の両端部に設けた枢軸１４がラジアルニードル軸受３０を介して揺動自在に支持されている。また、ヨーク２３Ａ，２３Ｂの幅方向（図１４の左右方向）の中央部には、円形の係止孔１９が設けられており、この係止孔１９の内周面は球状凹面として、球面ポスト６４，６８を内嵌している。すなわち、上側のヨーク２３Ａは、ケーシング５０に固定部材５２を介して支持されている球面ポスト６４によって揺動自在に支持されており、下側のヨーク２３Ｂは、球面ポスト６８及びこれを支持する駆動シリンダ３１の上側シリンダボディ６１によって揺動自在に支持されている。 Further, the pivot shafts 14, 14 of the trunnions 15, 15 are supported so as to be swingable with respect to the pair of yokes 23A, 23B and displaceable in the axial direction (vertical direction in FIG. 14). The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 A and 23 B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left-right direction in FIG. 14), and the inner peripheral surface of the locking hole 19 is a spherical concave surface, and is a spherical post. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder 31 is swingably supported.

なお、各トラニオン１５，１５に設けられた各変位軸２３，２３は、入力軸１に対し、互いに１８０度反対側の位置に設けられている。また、これらの各変位軸２３，２３の先端部２３ｂが基端部２３ａに対して偏心している方向は、両ディスク２，２，３，３の回転方向に対して同方向(図１４で上下逆方向)となっている。また、偏心方向は、入力軸１の配設方向に対して略直交する方向となっている。したがって、各パワーローラ１１，１１は、入力軸１の長手方向に若干変位できるように支持される。その結果、押圧装置１２が発生するスラスト荷重に基づく各構成部材の弾性変形等に起因して、各パワーローラ１１，１１が入力軸１の軸方向に変位する傾向となった場合でも、各構成部材に無理な力が加わらず、この変位が吸収される。 The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23 and 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3 and 3 (up and down in FIG. 14). (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

また、パワーローラ１１の外側面とトラニオン１５の支持板部１６の内側面との間には、パワーローラ１１の外側面の側から順に、スラスト転がり軸受であるスラスト玉軸受２４と、スラストニードル軸受２５とが設けられている。このうち、スラスト玉軸受２４は、各パワーローラ１１に加わるスラスト方向の荷重を支承しつつ、これら各パワーローラ１１の回転を許容するものである。このようなスラスト玉軸受２４はそれぞれ、複数個ずつの玉２６，２６と、これら各玉２６，２６を転動自在に保持する円環状の保持器２７と、円環状の外輪２８とから構成されている。また、各スラスト玉軸受２４の内輪軌道は各パワーローラ１１の外側面（大端面）に、外輪軌道は各外輪２８の内側面にそれぞれ形成されている。 Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing 24, which is a thrust rolling bearing, and a thrust needle bearing are sequentially arranged from the outer surface side of the power roller 11. 25. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of the thrust ball bearings 24 is composed of a plurality of balls 26, 26, an annular retainer 27 for holding the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. ing. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

また、スラストニードル軸受２５は、トラニオン１５の支持板部１６の内側面と外輪２８の外側面との間に挟持されている。このようなスラストニードル軸受２５は、パワーローラ１１から各外輪２８に加わるスラスト荷重を支承しつつ、これらパワーローラ１１および外輪２８が各変位軸２３の基端部２３ａを中心として揺動することを許容する。 The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

さらに、各トラニオン１５，１５の一端部(図１４の下端部)にはそれぞれ駆動ロッド（トラニオン軸）２９，２９が設けられており、各駆動ロッド２９，２９の中間部外周面に駆動ピストン（油圧ピストン）３３，３３が固設されている。そして、これら各駆動ピストン３３，３３はそれぞれ、上側シリンダボディ６１と下側シリンダボディ６２とによって構成された駆動シリンダ３１内に油密に嵌装されている。これら各駆動ピストン３３，３３と駆動シリンダ３１とで、各トラニオン１５，１５を、これらトラニオン１５，１５の枢軸１４，１４の軸方向に変位させる駆動装置３２を構成している。 Further, drive rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 14) of the trunnions 15 and 15 respectively, and a drive piston ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

このように構成されたトロイダル型無段変速機の場合、駆動軸２２の回転は、押圧装置１２を介して、各入力側ディスク２，２および入力軸１に伝えられる。そして、これら入力側ディスク２，２の回転が、一対のパワーローラ１１，１１を介して各出力側ディスク３，３に伝えられ、更にこれら各出力側ディスク３，３の回転が、出力歯車４より取り出される。 In the case of the toroidal continuously variable transmission configured as described above, the rotation of the drive shaft 22 is transmitted to the input side disks 2 and 2 and the input shaft 1 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

入力軸１と出力歯車４との間の回転速度比を変える場合には、一対の駆動ピストン３３，３３を互いに逆方向に変位させる。これら各駆動ピストン３３，３３の変位に伴って、一対のトラニオン１５，１５が互いに逆方向に変位する。例えば、図１４の左側のパワーローラ１１が同図の下側に、同図の右側のパワーローラ１１が同図の上側にそれぞれ変位する。その結果、これら各パワーローラ１１，１１の周面１１ａ，１１ａと各入力側ディスク２，２および各出力側ディスク３，３の内側面２ａ，２ａ，３ａ，３ａとの当接部に作用する接線方向の力の向きが変化する。そして、この力の向きの変化に伴って、各トラニオン１５，１５が、ヨーク２３Ａ，２３Ｂに枢支された枢軸１４，１４を中心として、互いに逆方向に揺動する。 When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 14 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

その結果、各パワーローラ１１，１１の周面１１ａ，１１ａと各内側面２ａ，３ａとの当接位置が変化し、入力軸１と出力歯車４との間の回転速度比が変化する。また、これら入力軸１と出力歯車４との間で伝達するトルクが変動し、各構成部材の弾性変形量が変化すると、各パワーローラ１１，１１及びこれら各パワーローラ１１，１１に付属の外輪２８，２８が、各変位軸２３，２３の基端部２３ａ，２３ａを中心として僅かに回動する。これら各外輪２８，２８の外側面と各トラニオン１５，１５を構成する支持板部１６の内側面との間には、それぞれスラストニードル軸受２５，２５が存在するため、前記回動は円滑に行われる。したがって、前述のように各変位軸２３，２３の傾斜角度を変化させるための力が小さくて済む。 As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 are slightly rotated around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

ところで、このようなトロイダル型無段変速機において、パワーローラ１１と入出力側ディスク２，３との動力伝達は、これらの部材表面の損傷を防止するべく、油膜を介したトラクション力により非接触で行なわれる（油膜によって形成されるパワーローラ１１と入出力側ディスク２，３との間の界面をトラクション面という）。そのため、パワーローラ１１と入出力側ディスク２，３との間に形成されるトラクション面には、トルクを非接触で伝達するための油膜を形成できる十分な量の潤滑油（トラクション油）を供給する必要がある。 By the way, in such a toroidal-type continuously variable transmission, power transmission between the power roller 11 and the input / output side disks 2 and 3 is non-contact by a traction force through an oil film in order to prevent damage to the surface of these members. (The interface between the power roller 11 formed by the oil film and the input / output side disks 2 and 3 is called a traction surface). Therefore, a sufficient amount of lubricating oil (traction oil) that can form an oil film for transmitting torque in a non-contact manner is supplied to the traction surface formed between the power roller 11 and the input / output side disks 2 and 3. There is a need to.

また、このようなトロイダル型無段変速機においては、変位軸２３の基端部２３ａと先端部２３ｂとが互いに偏心しているため、その加工が難しく、部品コストが高くなるとともに、支持剛性を確保するためにトラニオン１５が大型化、重量化するという問題がある。そこで、例えば、特許文献１ないし特許文献５には、パワーローラ１１をトラニオン１５に対して揺動軸線Ｏ’と直交する方向に平行移動可能に支持する（パワーローラ１１のディスク軸方向スライドを支持する）ことにより、パワーローラ１１の両ディスク２，３に対する位置を調整する直動式の支持機構が開示されている。 Further, in such a toroidal type continuously variable transmission, since the base end portion 23a and the tip end portion 23b of the displacement shaft 23 are eccentric from each other, it is difficult to process them, and the cost of parts is increased, and the support rigidity is ensured. Therefore, there is a problem that the trunnion 15 is increased in size and weight. Therefore, for example, in Patent Documents 1 to 5, the power roller 11 is supported so as to be movable in a direction perpendicular to the swing axis O ′ with respect to the trunnion 15 (supporting the disk axial slide of the power roller 11). Thus, a direct-acting support mechanism for adjusting the position of the power roller 11 with respect to both the disks 2 and 3 is disclosed.

これは、図１５に示すように、トラニオン１５のパワーローラ１１を収納するポケットＰ側の面に、トラニオン１５の長手方向において互いに傾斜が逆向きとなる一対の斜面２１５ａ，２１５ａを形成し、一方、パワーローラ１１を回転自在に支持する外輪２８の背面にも、これらの斜面２１５ａ，２１５ａと平行な一対の斜面２１５ｂ，２１５ｂを形成し、これらの対向する斜面間に転動体（ころ）２１７を配置して（すなわち、トラニオン１５の折れ曲がり壁部２０と外輪２８との間に転動体２１７を配置して）、一対の直動軸受２１８を構成している。この構成により、パワーローラ１１はトラニオン１５の幅方向（紙面に直交する方向）に移動自在となり、トラニオン１５の傾転に伴う構成部品の相対変位や部品の弾性変形に伴うパワーローラ１１と両ディスク２，３間の位置ずれが調整される。また、互いに逆向きに傾斜した一対の直動軸受２１８により、入力側および出力側ディスク２，３からパワーローラ１１に負荷されるスラスト方向（図において上下方向）およびトラニオン１５の長手方向（図において左右方向）に作用する力の両方を受けることができる。 As shown in FIG. 15, a pair of inclined surfaces 215a and 215a whose inclinations are opposite to each other in the longitudinal direction of the trunnion 15 are formed on the surface of the trunnion 15 on the pocket P side in which the power roller 11 is accommodated. A pair of slopes 215b and 215b parallel to the slopes 215a and 215a are also formed on the back surface of the outer ring 28 that rotatably supports the power roller 11, and a rolling element (roller) 217 is disposed between the opposing slopes. A pair of linear bearings 218 is formed by disposing (that is, disposing the rolling elements 217 between the bent wall portion 20 of the trunnion 15 and the outer ring 28). With this configuration, the power roller 11 can move in the width direction of the trunnion 15 (a direction orthogonal to the paper surface), and the power roller 11 and both disks according to the relative displacement of the components and the elastic deformation of the components as the trunnion 15 tilts. The positional deviation between 2 and 3 is adjusted. In addition, a pair of linear bearings 218 inclined in opposite directions from each other causes a thrust direction (vertical direction in the figure) applied to the power roller 11 from the input side and output side disks 2 and 3 and a longitudinal direction of the trunnion 15 (in the figure). It is possible to receive both forces acting in the left and right direction.

特開２００１−１２５７４号公報JP 2001-12574 A 特開２００２−２３５８２６号公報JP 2002-235826 A 特開２００３−２９４０９９号公報JP 2003-294099 A 特開２００４−１３８２４９号公報JP 2004-138249 A 特開２００４−１６９７８５号公報JP 2004-169785 A

前記直動軸受２１８は、パワーローラ１１に生じるスラスト力のみならず、トラクション力も保持する。このトラクション力は、パワーローラ１１を傾転軸（枢軸１４）方向にずらすように作用し、このずれが生じると、パワーローラ１１が中心軸からずれ、サイドスリップが発生し、設定した変速比がずれてしまうという問題が生じる（これを一般にトルクシフトという）。この結果、変速制御が難しくなるだけでなく、操縦性にも悪影響が及ぶことが懸念されるが、直動軸受２１８を設けたものは、従来からあるピボットシャフト（変位軸２３）型に対して軸受の隙間がないため、トルクシフトに対して有利である。 The linear motion bearing 218 holds not only the thrust force generated in the power roller 11 but also the traction force. This traction force acts to shift the power roller 11 in the direction of the tilt axis (pivot axis 14). When this shift occurs, the power roller 11 shifts from the central axis, side slip occurs, and the set gear ratio becomes There arises a problem of shifting (this is generally referred to as torque shift). As a result, it is feared that not only the speed change control becomes difficult but also the maneuverability is adversely affected. However, the one provided with the linear motion bearing 218 is different from the conventional pivot shaft (displacement shaft 23) type. There is no bearing clearance, which is advantageous for torque shift.

しかしながら、この直動軸受タイプのパワーローラユニットは、図１５に示すように、パワーローラ１１のトラクション動力接触部にかかる接線力を支持するため、２つの直動軸受２１８，２１８に交角を持たせている（２つの直動軸受２１８，２１８が互いに逆方向に傾斜する斜面上に配置されている）。そのため、以下のような幾つかの問題が生じる。 However, this linear motion bearing type power roller unit, as shown in FIG. 15, supports the tangential force applied to the traction power contact portion of the power roller 11 so that the two linear motion bearings 218 and 218 have an angle of intersection. (Two linear motion bearings 218, 218 are arranged on slopes inclined in opposite directions to each other). As a result, the following problems occur.

すなわち、このように２つの直動軸受２１８，２１８に交角を持たせる場合には、その角度精度を厳しくしないと、直動軸受２１８，２１８が軌道面に正しく接触しないため、角度精度を上げるための加工工程が複雑になり、コストが高くなってしまう。また、パワーローラ１１には大きなスラスト荷重が作用するが、このスラスト荷重によりトラニオン１５が弾性変形し、その弾性変形により交角が正しく保てなくなる場合もある。更に、接線力が作用すると、図１６に示すように、モーメントＭが発生して、パワーローラ１１自体が傾いてしまい（倒れてしまう）、パワーローラ１１が中心軸からずれて、トルクシフトが発生してしまう虞がある。 That is, when the two linear motion bearings 218 and 218 have an angle of intersection in this way, the linear motion bearings 218 and 218 do not properly contact the raceway surface unless the angular accuracy is strict, so that the angular accuracy is increased. The machining process becomes complicated and the cost becomes high. Further, a large thrust load acts on the power roller 11, but the trunnion 15 is elastically deformed by the thrust load, and the crossing angle may not be maintained correctly due to the elastic deformation. Further, when a tangential force acts, as shown in FIG. 16, a moment M is generated, the power roller 11 itself tilts (falls), and the power roller 11 deviates from the central axis, thereby generating a torque shift. There is a risk of it.

なお、特許文献１には、２つの直動軸受に交角を持たせない構造が開示されているが、直動軸受に交角を持たせないだけの構造では、トラニオンの弾性変形時にパワーローラの上下の部分が大きく変形する際、直動軸受が弾性変形の影響を受け易くなる。 Patent Document 1 discloses a structure in which two linear motion bearings do not have an angle of intersection. However, in a structure in which the linear motion bearing does not have an angle of intersection, the upper and lower sides of the power roller are deformed when the trunnion is elastically deformed. When this portion is greatly deformed, the linear motion bearing is easily affected by elastic deformation.

本発明は、前記事情に鑑みて為されたもので、加工工程を複雑化することなく（交角を持たないスライド軸受で）パワーローラのディスク軸方向スライドを支持できるとともに、その支持構造がトラニオンの弾性変形の影響を受け難いトロイダル型無段変速機を提供することを目的とする。 The present invention has been made in view of the above circumstances, and can support the disk axial slide of the power roller without complicating the machining process (with a slide bearing having no crossing angle), and the support structure of the trunnion An object of the present invention is to provide a toroidal type continuously variable transmission that is not easily affected by elastic deformation.

前記目的を達成するために、本発明のトロイダル型無段変速機は、第１の軸線と同軸に且つこの第１の軸線方向に対向して配置された入力側ディスクおよび出力側ディスクと、これらの両ディスクの間に挟持されたパワーローラと、前記両ディスクの間において前記第１の軸線に対して捩れの位置にある第２の軸線を中心に揺動自在に設けられたトラニオンと、このトラニオンの前記第２の軸線方向中央部に設けられたポケット部に収容されるとともに、前記パワーローラを回転自在に支持する外輪とを備えたトロイダル型無段変速機であって、前記トラニオンは、前記第２の軸線と略平行に延びる本体部と、この本体部の両端部から延びる折れ曲がり壁部と、これらの折れ曲がり壁部から前記第２の軸線に沿って外方に延びる枢軸とから成り、前記本体部の前記第２の軸線方向中央部には、前記第２の軸線と直交する方向に沿って一対のピンが設けられ、前記トラニオンの前記本体部と前記外輪との間には、前記外輪を前記第２の軸線と直交する方向に移動自在に支持する軸受が設けられ、前記外輪は、前記パワーローラを回転自在に支持する軸部と、前記第２の軸線と直交する方向に沿って延び且つ前記一対のピンと係合する長穴とを有し、前記第２の軸線と直交する方向に沿って前記長穴と前記ピンとが相対的に移動可能であるとともに、前記パワーローラと前記両ディスクとの間で生じる接線力を前記ピンと前記長穴との間で支持することを特徴とする。 In order to achieve the above object, a toroidal-type continuously variable transmission according to the present invention includes an input side disk and an output side disk that are arranged coaxially with the first axis and opposed to the first axis. A power roller sandwiched between the two disks, a trunnion provided between the disks so as to be swingable around a second axis that is twisted with respect to the first axis, A toroidal continuously variable transmission that is housed in a pocket provided in the second axial center portion of the trunnion and has an outer ring that rotatably supports the power roller, wherein the trunnion is A main body portion extending substantially parallel to the second axis, a bent wall portion extending from both ends of the main body portion, and a pivot extending outwardly from the bent wall portion along the second axis. A pair of pins are provided along the direction perpendicular to the second axis at the second axial center of the main body, and between the main body of the trunnion and the outer ring, A bearing is provided to support the outer ring so as to be movable in a direction orthogonal to the second axis, and the outer ring has a shaft portion that rotatably supports the power roller, and a direction orthogonal to the second axis. An elongated hole extending along the pair and engaging with the pair of pins, the elongated hole and the pin being relatively movable along a direction orthogonal to the second axis, and the power roller; A tangential force generated between the two disks is supported between the pin and the elongated hole.

なお、上記構成においては、長穴が前記トラニオンの前記本体部に設けられ、一対のピンが前記外輪に設けられても良い。また、一対のピンがキーに取って代えられても構わない。また、前記ピンと前記長穴との間にニードル軸受が介挿されていても良い。 In the above configuration, a long hole may be provided in the main body portion of the trunnion, and a pair of pins may be provided in the outer ring. Further, the pair of pins may be replaced with keys. A needle bearing may be interposed between the pin and the elongated hole.

本発明のトロイダル型無段変速機においては、外輪を第２の軸線と直交する方向に移動自在に支持する軸受が、第２の軸線と略平行に延びるトラニオンの本体部と外輪との間に設けられており、また、トラニオンから延びる一対のピンが外輪の長穴と係合し、第２の軸線と直交する方向に沿って長穴とピンとが相対的に移動可能であるとともに、パワーローラと両ディスクとの間で生じる接線力が前記ピンと前記長穴との間で支持されるようになっており、したがって、軸受に交角をつける必要がないため、トラニオンの加工工程を簡略化することができ、その結果、製造コストを低減することができる。また、トラニオンの弾性変形の影響を軸受が受け難い。また、従来のようなピボットシャフト（変位軸）を使用していないため、外輪の加工が簡単になるとともに、パワーローラのディスク軸方向移動に対し、パワーローラのトラニオン軸方向移動がなくなり、それに起因するトルクシフトを緩和することができる。また、一対のピンまたはキーによって外輪の自転を抑制できるため、前記外輪を前記第２の軸線と直交する方向に移動自在に支持する前記軸受は純転がりすることができる。 In the toroidal-type continuously variable transmission of the present invention, the bearing that supports the outer ring movably in the direction orthogonal to the second axis is between the trunnion main body and the outer ring that extends substantially parallel to the second axis. A pair of pins extending from the trunnion is engaged with the elongated hole of the outer ring, the elongated hole and the pin are relatively movable along a direction orthogonal to the second axis, and the power roller The tangential force generated between the disc and the two discs is supported between the pin and the elongated hole, and therefore it is not necessary to make an angle of intersection with the bearing, thereby simplifying the trunnion processing process. As a result, the manufacturing cost can be reduced. Further, the bearing is not easily affected by the elastic deformation of the trunnion. In addition, since the conventional pivot shaft (displacement axis) is not used, the outer ring can be easily machined, and the power roller does not move in the trunnion axis relative to the disk movement in the disk axis. Torque shift can be mitigated. In addition, since the rotation of the outer ring can be suppressed by a pair of pins or keys, the bearing that supports the outer ring so as to be movable in a direction orthogonal to the second axis can be purely rolled.

以下、図面を参照しながら、本発明の実施形態について説明する。なお、本発明の特徴は、トラニオンの揺動軸すなわち第２の軸線と直交する方向に外輪を移動自在に支持する支持構造にあり、その他の構成および作用は前述した従来の構成および作用と同様であるため、以下においては、本発明の特徴部分についてのみ言及し、それ以外の部分については、図１３〜図１６と同一の符号を付して簡潔に説明するに留める。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the support structure for movably supporting the outer ring in the direction orthogonal to the swing axis of the trunnion, that is, the second axis, and the other configurations and operations are the same as the conventional configurations and operations described above. Therefore, hereinafter, only the characteristic part of the present invention will be referred to, and other parts will be simply described with the same reference numerals as in FIGS.

図１は本発明の第１の実施形態を示している。図示のように、本実施形態において、トラニオン１５は、第２の軸線Ｏ’と略平行に延びる本体部としての支持板部１６と、この支持板部１６の両端部から第２の軸線Ｏ’に対して傾斜して延びる折れ曲がり壁部２０と、これらの折れ曲がり壁部２０から第２の軸線Ｏ’に沿って外方に延びる枢軸１４とから成る。また、支持板部１６の長手方向（第２の軸線方向）の略中央部には、第２の軸線Ｏ’と直交する方向Ｏ”に沿って一対のピン穴１０９，１０９が形成されており、これらのピン穴１０９，１０９に一対のピン１０４が対応して圧入等により固定されるようになっている。 FIG. 1 shows a first embodiment of the present invention. As illustrated, in the present embodiment, the trunnion 15 includes a support plate portion 16 as a main body portion extending substantially parallel to the second axis O ′, and a second axis O ′ from both ends of the support plate portion 16. Are bent wall portions 20 extending obliquely with respect to each other, and a pivot shaft 14 extending outward from the bent wall portions 20 along the second axis O ′. Further, a pair of pin holes 109 and 109 are formed in a substantially central portion in the longitudinal direction (second axial direction) of the support plate portion 16 along a direction O ″ orthogonal to the second axial line O ′. The pair of pins 104 correspond to these pin holes 109 and 109 and are fixed by press fitting or the like.

トラニオン１５の支持板部１６と外輪２８との間には、外輪２８を第２の軸線Ｏ’と直交する方向Ｏ”に移動自在に支持する軸受１００が設けられている。この軸受１００は、支持板部１６の内面１６ａ（外輪２８と対向する側の面；スラスト面）を転がり軌道としており、ピン穴１０９，１０９の両側で第２の軸線Ｏ’と直交する方向Ｏ”に沿って配列され且つスラスト方向の力を支持する直動型のスラストニードル軸受として形成されている。 Between the support plate portion 16 of the trunnion 15 and the outer ring 28, there is provided a bearing 100 that supports the outer ring 28 so as to be movable in a direction O ″ orthogonal to the second axis O ′. The inner surface 16a (surface facing the outer ring 28; thrust surface) of the support plate portion 16 is a rolling track, and is arranged along the direction O ″ orthogonal to the second axis O ′ on both sides of the pin holes 109 and 109. And a direct acting type thrust needle bearing that supports a thrust force.

トラニオン１５のポケットＰ内に配置される外輪２８は、パワーローラ１１を回転自在に支持する軸部１０６とスラスト玉軸受の軌道面を一方側の面に有している。また、支持板部１６の内面１６ａと対向する他方側の面２８ａ（スラスト面）には、第２の軸線Ｏ’と直交する方向Ｏ”に沿って延び且つピン１０４と係合する一対の長穴１０２が形成されている（図１の（ｃ）参照）。この場合、各長穴１０２は、第２の軸線Ｏ’と直交する方向Ｏ”に所定の遊度（移動空間）をもってピン１０４と係合している。なお、長穴１０２は各ピン１０４に対応して２つ設けられている必要はなく、図１の（ｅ）に示すように一対のピン１０４と同時に係合する１つの長穴１０２Ａが形成されても良い。また、長穴１０２とピン１０４との間には、第２の軸線Ｏ’の方向で微小な隙間Ｓ（例えば５０μｍ以下）が確保されている（図１の（ｄ）参照）。また、第１の軸部１０６、外輪２８と一体に形成されていても良く、あるいは、外輪２８と別体に形成されて外輪２８に取り付けられるようになっていても良い。更に、ピン１０４も、トラニオン１５と一体に形成されていても良く、本実施形態のようにトラニオン１５と別体に形成されてトラニオン１５に取り付けられるようになっていても良い。 The outer ring 28 disposed in the pocket P of the trunnion 15 has a shaft portion 106 that rotatably supports the power roller 11 and a raceway surface of a thrust ball bearing on one surface. Further, on the other surface 28 a (thrust surface) facing the inner surface 16 a of the support plate portion 16, a pair of lengths extending along a direction O ″ perpendicular to the second axis O ′ and engaging with the pin 104. (See FIG. 1C.) In this case, each elongated hole 102 has a predetermined degree of play (moving space) in the direction O ″ perpendicular to the second axis O ′. Is engaged. Two elongated holes 102 do not need to be provided corresponding to each pin 104, and one elongated hole 102A that is engaged simultaneously with the pair of pins 104 is formed as shown in FIG. May be. Further, a minute gap S (for example, 50 μm or less) is secured between the elongated hole 102 and the pin 104 in the direction of the second axis O ′ (see FIG. 1D). Further, the first shaft portion 106 and the outer ring 28 may be formed integrally, or may be formed separately from the outer ring 28 and attached to the outer ring 28. Further, the pin 104 may be formed integrally with the trunnion 15, or may be formed separately from the trunnion 15 and attached to the trunnion 15 as in the present embodiment.

以上のような構成では、第２の軸線Ｏ’と直交する方向Ｏ”に沿って長穴１０２とピン１０４とが相対的に移動可能であるとともに、パワーローラ１１とディスク２，３との間で生じる接線力がピン１０４と長穴１０２との間で支持されるようになる。パワーローラ１１がディスク軸方向Ｘに動く際には、長穴１０２の中をピン１０４が移動する状態となる。そのため、フリクションが小さくて済む。 In the configuration as described above, the elongated hole 102 and the pin 104 are relatively movable along the direction O ″ orthogonal to the second axis O ′, and between the power roller 11 and the disks 2 and 3. The tangential force generated in the above is supported between the pin 104 and the long hole 102. When the power roller 11 moves in the disk axial direction X, the pin 104 moves in the long hole 102. Therefore, the friction is small.

このように、本実施形態では、外輪２８を第２の軸線Ｏ’と直交する方向Ｏ”に移動自在に支持する軸受１００が、第２の軸線Ｏ’と略平行に延びるトラニオン１５の支持板部１６と外輪２８との間に設けられている。また、本実施形態では、トラニオン１５から延びる一対のピン１０４が外輪２８の長穴１０２と係合し、第２の軸線Ｏ’と直交する方向Ｏ”に沿って長穴１０２とピン１０４とが相対的に移動可能であるとともに、パワーローラ１１とディスク２，３との間で生じる接線力がピン１０４と長穴１０２との間で支持されるようになっている。そのため、軸受１００に交角をつける必要がなくなる。したがって、トラニオン１５の加工工程を簡略化することができ、製造コストを低減することができる。また、トラニオン１５の弾性変形の影響を軸受１００が受け難い。また、本実施形態の場合、従来のようなピボットシャフト（変位軸）を使用していないため、外輪２８の加工が簡単になるとともに、パワーローラ１１のディスク軸方向Ｘへの移動に対し、パワーローラ１１のトラニオン軸方向移動がなくなり、それに起因するトルクシフトを緩和することができる。また、一対のピン１０４によって外輪２８の自転を抑制できるため、外輪２８を第２の軸線Ｏ’と直交する方向Ｏ”に移動自在に支持する軸受１００は純転がりすることができる。 As described above, in the present embodiment, the bearing 100 that supports the outer ring 28 movably in the direction O ″ orthogonal to the second axis O ′ is a support plate for the trunnion 15 that extends substantially parallel to the second axis O ′. It is provided between the part 16 and the outer ring | wheel 28. Moreover, in this embodiment, a pair of pin 104 extended from the trunnion 15 engages with the long hole 102 of the outer ring | wheel 28, and is orthogonal to 2nd axis line O '. The long hole 102 and the pin 104 are relatively movable along the direction O ″, and a tangential force generated between the power roller 11 and the disks 2 and 3 is supported between the pin 104 and the long hole 102. It has come to be. Therefore, there is no need to make an angle of intersection with the bearing 100. Therefore, the processing steps of the trunnion 15 can be simplified, and the manufacturing cost can be reduced. Further, the bearing 100 is not easily affected by the elastic deformation of the trunnion 15. In the case of this embodiment, since the conventional pivot shaft (displacement axis) is not used, the processing of the outer ring 28 is simplified, and the power roller 11 moves with respect to the movement in the disk axial direction X. The trunnion axial movement of the roller 11 is eliminated, and the torque shift caused by the movement can be reduced. Further, since the rotation of the outer ring 28 can be suppressed by the pair of pins 104, the bearing 100 that supports the outer ring 28 movably in the direction O ″ orthogonal to the second axis O ′ can be purely rolled.

図２は本発明の第２の実施形態を示している。図示のように、本実施形態においては、一対の長穴１０２（または、１つの長穴１０２Ａ・・・図２の（ｅ）参照）がトラニオン１５側に設けられ、一対のピン１０４（ピン穴１０９，１０９）が外輪２８側に設けられているものであり、その他の構成は第１の実施形態と同一である。このような構成でも、第１の実施形態と同様の作用効果を得ることができる。 FIG. 2 shows a second embodiment of the present invention. As shown in the figure, in the present embodiment, a pair of long holes 102 (or one long hole 102A... See FIG. 2E) is provided on the trunnion 15 side, and a pair of pins 104 (pin holes) 109, 109) are provided on the outer ring 28 side, and other configurations are the same as those of the first embodiment. Even with such a configuration, the same effects as those of the first embodiment can be obtained.

図３は本発明の第３の実施形態を示している。図示のように、本実施形態においては、第１の実施形態の構造において、ピン１０４と長穴１０２Ｂとの間にラジアル方向の力を支持する円環状のラジアルニードル軸受（ラジアル軸受）１２３が介挿されている。この場合、一対の長穴１０２Ｂ（または、１つの長穴１０２Ｃ・・・図３の（ｅ）参照）は、軸受１２３に合わせて幅が大きく形成されている。また、長穴１０２とラジアルニードル軸受１２３との間には、第１の実施形態と同様に微小な隙間Ｓ（例えば５０μｍ以下）が確保されている（図３の（ｄ）参照）。なお、それ以外の構成は第１の実施形態と同一である。 FIG. 3 shows a third embodiment of the present invention. As illustrated, in the present embodiment, in the structure of the first embodiment, an annular radial needle bearing (radial bearing) 123 for supporting a radial force is interposed between the pin 104 and the elongated hole 102B. It is inserted. In this case, the pair of long holes 102 B (or one long hole 102 C... See FIG. 3E) is formed to have a large width in accordance with the bearing 123. Further, a minute gap S (for example, 50 μm or less) is secured between the elongated hole 102 and the radial needle bearing 123 (see FIG. 3D), as in the first embodiment. Other configurations are the same as those in the first embodiment.

このように長穴１０２とピン１０４との間にラジアルニードル軸受１２３を設けると、長穴１０２とピン１０４との間の滑り接触がなくなるため、フリクションを小さくできる。 When the radial needle bearing 123 is provided between the long hole 102 and the pin 104 in this manner, the sliding contact between the long hole 102 and the pin 104 is eliminated, so that the friction can be reduced.

図４は本発明の第４の実施形態を示している。図示のように、本実施形態においては、第２の実施形態の構造において、ピン１０４と長穴１０２Ｂとの間にラジアル方向の力を支持する円環状のラジアルニードル軸受（ラジアル軸受）１２３が介挿されている。この場合、長穴１０２Ｂは、軸受１２３に合わせて幅が大きく形成されている。また、長穴１０２Ｂとラジアルニードル軸受１２３との間には、第２の実施形態と同様に微小な隙間Ｓ（例えば５０μｍ以下）が確保されている（図４の（ｃ）参照）。なお、それ以外の構成は第２の実施形態と同一である。 FIG. 4 shows a fourth embodiment of the present invention. As shown in the drawing, in the present embodiment, in the structure of the second embodiment, an annular radial needle bearing (radial bearing) 123 that supports a radial force is interposed between the pin 104 and the elongated hole 102B. It is inserted. In this case, the long hole 102 B is formed to have a large width in accordance with the bearing 123. In addition, a minute gap S (for example, 50 μm or less) is secured between the elongated hole 102B and the radial needle bearing 123 (see FIG. 4C), as in the second embodiment. Other configurations are the same as those of the second embodiment.

図５は本発明の第５の実施形態を示している。図示のように、本実施形態においては、第１の実施形態の構造において、ピン１０４がキー１２９にとって代えられ、長穴１０２がキー溝（長穴）１１９に取って代えられている。この場合、キー溝１１９とキー１２９との間には、第１の実施形態と同様に微小な隙間Ｓ（例えば５０μｍ以下）が確保されている（図５の（ｄ）参照）。なお、それ以外の構成は第１の実施形態と同一である。 FIG. 5 shows a fifth embodiment of the present invention. As shown in the figure, in the present embodiment, in the structure of the first embodiment, the pin 104 is replaced with a key 129 and the long hole 102 is replaced with a key groove (long hole) 119. In this case, a minute gap S (for example, 50 μm or less) is secured between the keyway 119 and the key 129 (see FIG. 5D), as in the first embodiment. Other configurations are the same as those in the first embodiment.

図６は本発明の第６の実施形態を示している。図示のように、本実施形態においては、第２の実施形態の構造において、ピン１０４がキー１２９にとって代えられ、長穴１０２がキー溝（長穴）１１９に取って代えられている。この場合、キー溝１１９とキー１２９との間には、第１の実施形態と同様に微小な隙間Ｓ（例えば５０μｍ以下）が確保されている（図６の（ｄ）参照）。なお、それ以外の構成は第２の実施形態と同一である。 FIG. 6 shows a sixth embodiment of the present invention. As illustrated, in the present embodiment, in the structure of the second embodiment, the pin 104 is replaced with a key 129 and the long hole 102 is replaced with a key groove (long hole) 119. In this case, a minute gap S (for example, 50 μm or less) is secured between the keyway 119 and the key 129 (see FIG. 6D), as in the first embodiment. Other configurations are the same as those of the second embodiment.

図７は本発明の第７の実施形態を示している。図示のように、本実施形態においては、第１の実施形態の構造において、軸受１００が円盤状のスラスト軸受（滑り軸受）１００Ａに取って代えられている。この軸受１００Ａにはピン１０４が挿通される一対の通孔１９７，１９７が設けられている。なお、それ以外の構成は第１の実施形態と同一である。 FIG. 7 shows a seventh embodiment of the present invention. As illustrated, in the present embodiment, the bearing 100 is replaced with a disk-shaped thrust bearing (sliding bearing) 100A in the structure of the first embodiment. The bearing 100A is provided with a pair of through holes 197 and 197 through which the pins 104 are inserted. Other configurations are the same as those in the first embodiment.

図８は本発明の第８の実施形態を示している。図示のように、本実施形態においては、第２の実施形態の構造において、軸受１００が円盤状のスラスト軸受（滑り軸受）１００Ａに取って代えられている。この軸受１００Ａにはピンと係合する一対の長穴１９８，１９８（長穴１０２，１０２に対応する穴）が設けられている。なお、それ以外の構成は第２の実施形態と同一である。 FIG. 8 shows an eighth embodiment of the present invention. As shown in the drawing, in the present embodiment, the bearing 100 is replaced with a disk-shaped thrust bearing (sliding bearing) 100A in the structure of the second embodiment. The bearing 100A is provided with a pair of long holes 198 and 198 (holes corresponding to the long holes 102 and 102) that engage with the pins. Other configurations are the same as those of the second embodiment.

図９は本発明の第９の実施形態を示している。図示のように、本実施形態においては、第３の実施形態の構造において、軸受１００が円盤状のスラスト軸受（滑り軸受）１００Ａに取って代えられている。この軸受１００Ａにはピン１０４が挿通される一対の通孔１９７，１９７が設けられている。なお、それ以外の構成は第３の実施形態と同一である。 FIG. 9 shows a ninth embodiment of the present invention. As shown in the figure, in the present embodiment, the bearing 100 is replaced with a disc-shaped thrust bearing (sliding bearing) 100A in the structure of the third embodiment. The bearing 100A is provided with a pair of through holes 197 and 197 through which the pins 104 are inserted. Other configurations are the same as those of the third embodiment.

図１０は本発明の第１０の実施形態を示している。図示のように、本実施形態においては、第４の実施形態の構造において、軸受１００が円盤状のスラスト軸受（滑り軸受）１００Ａに取って代えられている。この軸受１００Ａには軸受１２３と係合する一対の長穴２０７，２０７（長穴１０２Ｂ，１０２Ｂに対応する穴）が設けられている。なお、それ以外の構成は第４の実施形態と同一である。 FIG. 10 shows a tenth embodiment of the present invention. As illustrated, in the present embodiment, the bearing 100 is replaced with a disk-shaped thrust bearing (sliding bearing) 100A in the structure of the fourth embodiment. The bearing 100A is provided with a pair of elongated holes 207 and 207 (holes corresponding to the elongated holes 102B and 102B) that engage with the bearing 123. Other configurations are the same as those in the fourth embodiment.

図１１は本発明の第１１の実施形態を示している。図示のように、本実施形態においては、第５の実施形態の構造において、軸受１００が円盤状のスラスト軸受（滑り軸受）１００Ａに取って代えられている。この軸受１００Ａにはキー１２９と嵌合する（キー１２９と対応する形状を有する）キー穴２１８が設けられている。なお、それ以外の構成は第５の実施形態と同一である。 FIG. 11 shows an eleventh embodiment of the present invention. As illustrated, in the present embodiment, in the structure of the fifth embodiment, the bearing 100 is replaced with a disk-shaped thrust bearing (sliding bearing) 100A. The bearing 100A is provided with a key hole 218 that fits with the key 129 (having a shape corresponding to the key 129). Other configurations are the same as those of the fifth embodiment.

図１２は本発明の第１２の実施形態を示している。図示のように、本実施形態においては、第６の実施形態の構造において、軸受１００が円盤状のスラスト軸受（滑り軸受）１００Ａに取って代えられている。この軸受１００Ａにはキー溝１１９と対応する形状を有するキー溝２３１が設けられている。なお、それ以外の構成は第６の実施形態と同一である。 FIG. 12 shows a twelfth embodiment of the present invention. As illustrated, in the present embodiment, in the structure of the sixth embodiment, the bearing 100 is replaced with a disk-shaped thrust bearing (sliding bearing) 100A. The bearing 100A is provided with a key groove 231 having a shape corresponding to the key groove 119. Other configurations are the same as those of the sixth embodiment.

本発明は、シングルキャビティ型やダブルキャビティ型などの様々なハーフトロイダル型無段変速機に適用することができる。 The present invention can be applied to various half-toroidal continuously variable transmissions such as a single cavity type and a double cavity type.

本発明の第１の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）は外輪をパワーローラ側から見た斜視図、（ｃ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｄ）は長穴の形状を示す平面図、（ｅ）は外輪の変形例を示す斜視図である。It is a figure which shows the 1st Embodiment of this invention, (a) is a perspective view of a trunnion, (b) is a perspective view which looked at the outer ring from the power roller side, (c) is a trunnion side (thrust surface) of the outer ring (D) is a plan view showing the shape of the elongated hole, and (e) is a perspective view showing a modified example of the outer ring. 本発明の第２の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）は外輪をパワーローラ側から見た斜視図、（ｃ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｄ）は長穴の形状を示す平面図、（ｅ）はトラニオンの変形例を示す斜視図である。It is a figure which shows the 2nd Embodiment of this invention, (a) is the perspective view of a trunnion, (b) is the perspective view which looked at the outer ring from the power roller side, (c) is the trunnion side (thrust surface) of the outer ring (D) is a plan view showing the shape of the elongated hole, and (e) is a perspective view showing a modification of the trunnion. 本発明の第３の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）は外輪をパワーローラ側から見た斜視図、（ｃ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｄ）は長穴の形状を示す平面図、（ｅ）は外輪の変形例を示す斜視図である。It is a figure which shows the 3rd Embodiment of this invention, Comprising: (a) is the perspective view of a trunnion, (b) is the perspective view which looked at the outer ring from the power roller side, (c) is the trunnion side (thrust surface) of the outer ring (D) is a plan view showing the shape of the elongated hole, and (e) is a perspective view showing a modified example of the outer ring. 本発明の第４の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）は外輪をパワーローラ側から見た斜視図、（ｃ）は長穴の形状を示す平面図、（ｄ）はトラニオンの変形例を示す斜視図である。It is a figure which shows the 4th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view which looked at the outer ring | wheel from the power roller side, (c) is a plane which shows the shape of an elongate hole FIG. 4D is a perspective view showing a modification of the trunnion. 本発明の第５の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）は外輪をパワーローラ側から見た斜視図、（ｃ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｄ）は長穴の形状を示す平面図である。It is a figure which shows the 5th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view which looked at the outer ring from the power roller side, (c) is a trunnion side (thrust surface) (D) is a top view which shows the shape of an elongate hole. 本発明の第６の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）は外輪をパワーローラ側から見た斜視図、（ｃ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｄ）は長穴の形状を示す平面図である。It is a figure which shows the 6th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view which looked at the outer ring from the power roller side, (c) is a trunnion side (thrust surface) (D) is a top view which shows the shape of an elongate hole. 本発明の第７の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）はスラスト軸受の斜視図、（ｃ）は外輪をパワーローラ側から見た斜視図、（ｄ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｅ）は外輪の変形例を示す斜視図である。It is a figure which shows the 7th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view of a thrust bearing, (c) is a perspective view which looked at the outer ring from the power roller side, d) is a perspective view of the outer ring viewed from the trunnion side (thrust surface side), and (e) is a perspective view showing a modification of the outer ring. 本発明の第８の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）はスラスト軸受の斜視図、（ｃ）は外輪をパワーローラ側から見た斜視図、（ｄ）は外輪をトラニオン側（スラスト面側）から見た斜視図、（ｅ）はトラニオンの変形例を示す斜視図である。It is a figure which shows the 8th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view of a thrust bearing, (c) is a perspective view which looked at the outer ring | wheel from the power roller side, d) is a perspective view of the outer ring viewed from the trunnion side (thrust surface side), and (e) is a perspective view showing a modification of the trunnion. 本発明の第９の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）はスラスト軸受の斜視図、（ｃ）は外輪をパワーローラ側から見た斜視図、（ｄ）は外輪をトラニオン側（スラスト面側）から見た斜視図である。It is a figure which shows the 9th Embodiment of this invention, (a) is a perspective view of a trunnion, (b) is a perspective view of a thrust bearing, (c) is a perspective view which looked at the outer ring from the power roller side, d) is a perspective view of the outer ring viewed from the trunnion side (thrust surface side). 本発明の第１０の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）はスラスト軸受の斜視図、（ｃ）は外輪をパワーローラ側から見た斜視図、（ｄ）は外輪をトラニオン側（スラスト面側）から見た斜視図である。It is a figure which shows the 10th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view of a thrust bearing, (c) is a perspective view which looked at the outer ring from the power roller side, d) is a perspective view of the outer ring viewed from the trunnion side (thrust surface side). 本発明の第１１の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）はスラスト軸受の斜視図、（ｃ）は外輪をパワーローラ側から見た斜視図、（ｄ）は外輪をトラニオン側（スラスト面側）から見た斜視図である。It is a figure which shows 11th Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view of a thrust bearing, (c) is a perspective view which looked at the outer ring | wheel from the power roller side, d) is a perspective view of the outer ring viewed from the trunnion side (thrust surface side). 本発明の第１２の実施形態を示す図であって、（ａ）はトラニオンの斜視図、（ｂ）はスラスト軸受の斜視図、（ｃ）は外輪をパワーローラ側から見た斜視図、（ｄ）は外輪をトラニオン側（スラスト面側）から見た斜視図である。It is a figure which shows the 12th Embodiment of this invention, (a) is a perspective view of a trunnion, (b) is a perspective view of a thrust bearing, (c) is a perspective view which looked at the outer ring from the power roller side, d) is a perspective view of the outer ring viewed from the trunnion side (thrust surface side). 従来から知られているトロイダル型無段変速機の具体的構造の一例を示す断面図である。It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. 図１３のＡ−Ａ線に沿う断面図である。It is sectional drawing which follows the AA line of FIG. 直動軸受を有するトロイダル型無段変速機の要部断面図である。It is principal part sectional drawing of the toroidal type continuously variable transmission which has a linear motion bearing. 図１５の構成においてトルクシフトが生じた状態を示す要部断面図である。FIG. 16 is a main part cross-sectional view showing a state where a torque shift has occurred in the configuration of FIG. 15.

Explanation of symbols

１入力軸
２入力側ディスク
３出力側ディスク
７カム板（ローディングカム）
１１パワーローラ
１４枢軸
１５トラニオン
１６本体部
２０折れ曲がり壁部
２８外輪
１００，１００Ａ軸受
１０４ピン
１０２，１０２Ａ，１０２Ｂ，１０２Ｃ長穴
１０６軸部
１１９キー溝
１２３ニードル軸受
１２９キー
Ｐポケット部 1 Input shaft 2 Input disk 3 Output disk 7 Cam plate (loading cam)
DESCRIPTION OF SYMBOLS 11 Power roller 14 Axis 15 Trunnion 16 Main body part 20 Bending wall part 28 Outer ring 100,100A Bearing 104 Pin 102,102A, 102B, 102C Long hole 106 Shaft part 119 Key groove 123 Needle bearing 129 Key P Pocket part

Claims

Between the input disk and the output disk arranged coaxially with the first axis and facing the first axis direction, a power roller sandwiched between the two disks, and the two disks A trunnion provided swingably around a second axis that is twisted with respect to the first axis, and a pocket provided at the center in the second axial direction of the trunnion. And a toroidal continuously variable transmission provided with an outer ring that rotatably supports the power roller,
The trunnion includes a main body portion extending substantially parallel to the second axis, a bent wall portion extending from both ends of the main body portion, and a pivot extending outwardly from the bent wall portion along the second axis. A pair of pins is provided along the direction perpendicular to the second axis at the second axial center of the main body,
Between the main body portion of the trunnion and the outer ring, a bearing is provided for supporting the outer ring movably in a direction orthogonal to the second axis,
The outer ring includes a shaft portion that rotatably supports the power roller, and an elongated hole that extends along a direction orthogonal to the second axis and engages with the pair of pins.
The elongated hole and the pin are relatively movable along a direction orthogonal to the second axis, and a tangential force generated between the power roller and the two disks is applied to the pin and the elongated hole. A toroidal-type continuously variable transmission characterized by being supported between.

The toroidal continuously variable transmission according to claim 1, wherein a needle bearing is inserted between the pin and the elongated hole.

Between the input disk and the output disk arranged coaxially with the first axis and facing the first axis direction, a power roller sandwiched between the two disks, and the two disks A trunnion provided swingably around a second axis that is twisted with respect to the first axis, and a pocket provided at the center in the second axial direction of the trunnion. And a toroidal continuously variable transmission provided with an outer ring that rotatably supports the power roller,
The trunnion includes a main body portion extending substantially parallel to the second axis, a bent wall portion extending from both ends of the main body portion, and a pivot extending outwardly from the bent wall portion along the second axis. In the center portion of the second axial direction of the main body portion, an elongated hole extending along a direction perpendicular to the second axis is provided,
Between the main body portion of the trunnion and the outer ring, a bearing is provided for supporting the outer ring movably in a direction orthogonal to the second axis,
The outer ring includes a shaft portion that rotatably supports the power roller, and a pair of pins that extend along a direction perpendicular to the second axis and engage with the elongated hole,
The elongated hole and the pin are relatively movable along a direction orthogonal to the second axis, and a tangential force generated between the power roller and the two disks is applied between the pin and the elongated hole. A toroidal-type continuously variable transmission characterized by being supported between.

The toroidal continuously variable transmission according to claim 3, wherein a needle bearing is interposed between the pin and the elongated hole.

Between the input disk and the output disk arranged coaxially with the first axis and facing the first axis direction, a power roller sandwiched between the two disks, and the two disks A trunnion provided swingably around a second axis that is twisted with respect to the first axis, and a pocket provided at the center in the second axial direction of the trunnion. And a toroidal continuously variable transmission provided with an outer ring that rotatably supports the power roller,
The trunnion includes a main body portion extending substantially parallel to the second axis, a bent wall portion extending from both ends of the main body portion, and a pivot extending outwardly from the bent wall portion along the second axis. A key extending along a direction orthogonal to the second axis is provided at the second axial center of the main body,
Between the main body portion of the trunnion and the outer ring, a bearing is provided for supporting the outer ring movably in a direction orthogonal to the second axis,
The outer ring includes a shaft portion that rotatably supports the power roller, and a long hole that extends along a direction orthogonal to the second axis and engages with the key.
The elongated hole and the key are relatively movable along a direction orthogonal to the second axis, and a tangential force generated between the power roller and the disks is applied to the key and the elongated hole. A toroidal-type continuously variable transmission characterized by being supported between

Between the input disk and the output disk arranged coaxially with the first axis and facing the first axis direction, a power roller sandwiched between the two disks, and the two disks A trunnion provided swingably around a second axis that is twisted with respect to the first axis, and a pocket provided at the center in the second axial direction of the trunnion. And a toroidal continuously variable transmission provided with an outer ring that rotatably supports the power roller,
The trunnion includes a main body portion extending substantially parallel to the second axis, a bent wall portion extending from both ends of the main body portion, and a pivot extending outwardly from the bent wall portion along the second axis. In the center portion of the second axial direction of the main body portion, an elongated hole extending along a direction perpendicular to the second axis is provided,
Between the main body portion of the trunnion and the outer ring, a bearing is provided for supporting the outer ring movably in a direction orthogonal to the second axis,
The outer ring includes a shaft portion that rotatably supports the power roller, and a key that extends along a direction orthogonal to the second axis and engages with the elongated hole,
The elongated hole and the key are relatively movable along a direction orthogonal to the second axis, and a tangential force generated between the power roller and the disks is applied to the key and the elongated hole. A toroidal-type continuously variable transmission characterized by being supported between