JP5803584B2

JP5803584B2 - Toroidal-type continuously variable transmission and processing method for parts thereof

Info

Publication number: JP5803584B2
Application number: JP2011243612A
Authority: JP
Inventors: 将司横山
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2011-11-07
Filing date: 2011-11-07
Publication date: 2015-11-04
Anticipated expiration: 2031-11-07
Also published as: JP2013100842A

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およびその部品の加工方法に関する。 The present invention relates to a toroidal-type continuously variable transmission that can be used in transmissions of automobiles and various industrial machines, and a method for processing parts thereof.

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７および図８に示すように構成されている（図７に２つのキャビティ２２１，２２２が示される）。図７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. 7 and 8 (two cavities 221 and 222 are shown in FIG. 7). As shown in FIG. 7, 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、これにより、入力軸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. . The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O. Directional displacement 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と出力側ディスク３，３の内側面（凹面；トラクション面とも言う）３ａ，３ａとの間には、パワーローラ１１（図８参照）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. A power roller 11 (FIG. 8) is provided between the inner side surfaces (concave surfaces) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output side disks 3 and 3. (See below) is rotatably held.

図７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７の右面）がローディングナット９に突き当てられている。これによって、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 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 7, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (the right surface in FIG. 7) of the input side disk 2 is abutted against the loading nut 9. Thereby, the displacement of the input side 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８は、図７のＥ−Ｅ線に沿う断面図である。図８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８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、パワーローラ１１を支持する支持板部１６の長手方向(図８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一対の折れ曲がり壁部２０，２０を有している。そして、この折れ曲がり壁部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。また、各折れ曲がり壁部２０，２０の外側面には、各枢軸１４，１４が互いに同心的に設けられている。 FIG. 8 is a cross-sectional view taken along line EE in FIG. As shown in FIG. 8, a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In addition, illustration of the input shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is a pair of bent portions formed on the inner surface side of the support plate 16 at both ends in the longitudinal direction (vertical direction in FIG. 8) of the support plate 16 that supports the power roller 11. It has the bent wall parts 20 and 20. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

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（軸部）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、ラジアルニードル軸受９９を介して各パワーローラ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 (shaft) 23 supported at the center of each trunnion 15, 15 can be adjusted. It has become. In addition, each power roller 11 is rotatably supported via a radial needle bearing 99 around the distal end portion 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output 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８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７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の内周面は円筒面として、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およ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。 The pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and displaceable in the axial direction (vertical direction in FIG. 8) with respect to the pair of yokes 23A and 23B, respectively. 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 </ b> A and 23 </ b> 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 and right direction in FIG. 7). The inner peripheral surface of the locking hole 19 is a cylindrical 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 supported by 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８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, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of the both disks 2, 2, 3, 3 (up and down in FIG. 8). (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（以下、転動体という）２６，２６と、これら各転動体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 that is a thrust rolling bearing, and a thrust needle bearing, in order 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 such thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds the rolling elements 26, 26 in a freely rolling manner, And an annular outer ring 28. 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８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, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 8) of the trunnions 15 and 15, respectively, and a driving 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、入力軸１の回転は、押圧装置１２を介して、各入力側ディスク２，２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 input shaft 1 is transmitted to the input side disks 2 and 2 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. 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８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（傾転）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. 8 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 (tilt) 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（トラクション面）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との間の変速比が変化する。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およ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 (traction surfaces) 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the gear ratio between the input shaft 1 and the output gear 4 changes. To do. 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 slightly rotate 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、上述の様なトロイダル型無段変速機の運転時には、動力の伝達に供される各部材、すなわち入力側ディスク２、出力側ディスク３およびパワーローラ１１等が、押圧装置１２が発生する押圧力（推力）に基づいて弾性変形する。この弾性変形に伴って、各ディスク２，３が軸方向に変位する。また、押圧装置１２が発生する押圧力は、トロイダル型無段変速機により伝達するトルクが大きくなる程大きくなり、それに伴って各部材の弾性変形量も多くなる。したがって、上記トルクの変動に拘らず、入力側、出力側各内側面２ａ、３ａと各パワーローラ１１の周面１１ａとの接触状態を適正に維持するために、これら各パワーローラ１１を上記各トラニオン１５に対し、上記各ディスク２，３の軸方向に変位させる機構が必要になる。 By the way, during the operation of the toroidal type continuously variable transmission as described above, the members used for power transmission, that is, the input side disk 2, the output side disk 3, the power roller 11, and the like are pushed by the pressing device 12. Elastically deforms based on pressure (thrust). Along with this elastic deformation, the disks 2 and 3 are displaced in the axial direction. Further, the pressing force generated by the pressing device 12 increases as the torque transmitted by the toroidal-type continuously variable transmission increases, and the amount of elastic deformation of each member increases accordingly. Accordingly, in order to properly maintain the contact state between the input-side and output-side inner side surfaces 2a, 3a and the peripheral surface 11a of each power roller 11 regardless of the torque fluctuation, A mechanism for displacing the trunnion 15 in the axial direction of each of the disks 2 and 3 is required.

上述の例では、パワーローラ１１が、トラニオン１５に対して変位軸２３の基端部２３ａを中心に揺動可能な構成になっていることにより、パワーローラ１１をトラニオン１５に対して各ディスク２，３の軸方向に変位させることができる。 In the above example, the power roller 11 is configured to be swingable with respect to the trunnion 15 about the proximal end portion 23 a of the displacement shaft 23, so that the power roller 11 can be moved from the trunnion 15 to each disk 2. , 3 can be displaced in the axial direction.

また、変位軸２３を用いない別の構造として、図１０に示すように、支持板部１６を有するトラニオン１５に代えて、パワーローラ側に向かって凸になる円筒状凸面３４を有する支持梁部１６Ａを備えるトラニオン１５Ａを備え、且つ、上述の外輪２８に代えて、円筒状凸面３４に係合される円筒状凹面３８を備える外輪２８Ａを備えているトロイダル型無段変速機が提案されている（例えば、特許文献１参照）。 Further, as another structure not using the displacement shaft 23, as shown in FIG. 10, instead of the trunnion 15 having the support plate portion 16, a support beam portion having a cylindrical convex surface 34 convex toward the power roller side. A toroidal continuously variable transmission that includes a trunnion 15A including 16A and includes an outer ring 28A including a cylindrical concave surface 38 that is engaged with the cylindrical convex surface 34 instead of the outer ring 28 described above has been proposed. (For example, refer to Patent Document 1).

前記円筒状凸面３４の中心軸は、枢軸１４の中心軸と平行でかつ当該枢軸１４の中心軸より入力側ディスク２および出力側ディスク３の中心軸（回転軸）から離れた位置に配置されている。また、円筒状凹面３８は、円筒状凸面３４に略当接可能な曲率半径を有するものになっている。
また、外輪２８Ａには、上述の変位軸２３の先端部２３ｂに相当する支持軸２３Ａが一体に設けられ、この支持軸２３Ａがパワーローラ１１の回転中心部を貫通して配置されている。
また、図示を省略するが、図８の場合と同様に、支持軸２３Ａとパワーローラ１１の支持軸２３Ａが貫通する貫通孔の間には、支持軸２３Ａに対してパワーローラ１１を回転自在に支持するラジアル軸受が配置されている。また、パワーローラ１１を貫通した支持軸２３Ａの先端部には、パワーローラ１１の抜け止用のＣリングが固定され、スラスト玉軸受２４を構成する外輪２８Ａ、保持器２７、転動体２６、内輪としてのパワーローラ１１がそれぞれ分解せずに互いに回転自在に接合された状態に支持されている。 The central axis of the cylindrical convex surface 34 is arranged parallel to the central axis of the pivot 14 and at a position away from the central axes (rotation axes) of the input side disk 2 and the output side disk 3 from the central axis of the pivot 14. Yes. Further, the cylindrical concave surface 38 has a radius of curvature that can substantially contact the cylindrical convex surface 34.
Further, the outer ring 28A is integrally provided with a support shaft 23A corresponding to the tip portion 23b of the displacement shaft 23, and the support shaft 23A is disposed so as to penetrate the rotation center portion of the power roller 11.
Although not shown, the power roller 11 is rotatable with respect to the support shaft 23A between the support shaft 23A and the through-hole through which the support shaft 23A of the power roller 11 passes, as in the case of FIG. A supporting radial bearing is arranged. Further, a C-ring for preventing the power roller 11 from coming off is fixed to the tip of the support shaft 23A that penetrates the power roller 11, and the outer ring 28A, the retainer 27, the rolling element 26, and the inner ring that constitute the thrust ball bearing 24. The power rollers 11 are supported in a state where they are joined to each other so as not to be disassembled.

このようなトラニオン１５Ａおよび外輪２８Ａを有するトロイダル型無段変速機においては、上述のように押圧装置の押圧力によりに入力側ディスク２、出力側ディスク３、パワーローラ１１等が弾性変形するとともに、これらが伝達するトルクの変化に対応して弾性変形量が変化した場合に、トラニオン１５Ａの支持梁部１６Ａの円筒状凸面３４に対して、外輪２８Ａがパワーローラ１１と一体に両ディスク２，３の軸方向に関する揺動変位することによって、入力側ディスク２の内側面２ａ、出力側ディスク３の内側面３ａとパワーローラ１１の周面１１ａとの接触状態を適正に維持することができる。 In the toroidal type continuously variable transmission having the trunnion 15A and the outer ring 28A, the input side disk 2, the output side disk 3, the power roller 11 and the like are elastically deformed by the pressing force of the pressing device as described above. When the amount of elastic deformation changes corresponding to the change in torque transmitted by these, the outer ring 28A is integrated with the power roller 11 with respect to the cylindrical convex surface 34 of the support beam portion 16A of the trunnion 15A. Thus, the contact state between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3 and the peripheral surface 11a of the power roller 11 can be properly maintained.

ところで、以上のようなトロイダル型無段変速機の運転時には、パワーローラ１１に作用するスラスト力Ｆｐｒ（図１０参照）によりトラニオン１５Ａがポケット部Ｐを閉じる方向に弾性変形し（図１０の矢印Ｘ参照）、また、パワーローラ１１と各ディスク２，３との間で動力を伝達するためのトラクション接触部Ｃ１，Ｃ２にそれぞれ、図８および図９に示すような接線方向の力Ｆｔが発生し、これら２点での力Ｆｔを合わせた力２Ｆｔがパワーローラ１１に作用する（図１０参照）。 By the way, during operation of the toroidal type continuously variable transmission as described above, the trunnion 15A is elastically deformed in the direction of closing the pocket portion P by the thrust force Fpr (see FIG. 10) acting on the power roller 11 (arrow X in FIG. 10). Further, a tangential force Ft as shown in FIGS. 8 and 9 is generated in the traction contact portions C1 and C2 for transmitting power between the power roller 11 and the disks 2 and 3, respectively. A force 2Ft obtained by adding the forces Ft at these two points acts on the power roller 11 (see FIG. 10).

したがって、従来構造では、これらの荷重による変形を考慮して、トラニオン１５Ａとパワーローラ１１との間に隙間を設けつつ（通常、パワーローラ外輪２８Ａの外周部とトラニオン１５Ａの内端面との間には、トラニオン１５Ａの変形を考慮して隙間が設けられる）、パワーローラ１１をトラニオン１５Ａに対して支持するようにしている。 Therefore, in the conventional structure, considering the deformation due to these loads, a gap is provided between the trunnion 15A and the power roller 11 (usually between the outer peripheral portion of the power roller outer ring 28A and the inner end surface of the trunnion 15A). The clearance is provided in consideration of deformation of the trunnion 15A), and the power roller 11 is supported with respect to the trunnion 15A.

例えば特許文献１では、図１１に示すように、トラニオン１５Ａのポケット部Ｐの内側に設けた段差部１００と外輪２８Ａの外周部とを当接させて支持する構造となっており、そのため、トラニオン１５Ａのポケット部Ｐを閉じる方向の弾性変形（図１１の矢印Ｘ参照）に伴って外輪２８Ａの外周部がトラニオン１５Ａにより挟み込まれないように、トラニオン１５Ａの内端面幅（左右の段差部１００間の距離）Ｗ（図１１の（ａ）参照）が外輪２８Ａの外径に対して大きく設定されている。 For example, in Patent Document 1, as shown in FIG. 11, the stepped portion 100 provided inside the pocket portion P of the trunnion 15 </ b> A is in contact with and supported by the outer peripheral portion of the outer ring 28 </ b> A. The inner end face width of the trunnion 15A (between the left and right step portions 100) so that the outer peripheral portion of the outer ring 28A is not sandwiched between the trunnions 15A due to elastic deformation in the direction of closing the pocket portion P of the 15A (see arrow X in FIG. 11). ) W (see FIG. 11A) is set larger than the outer diameter of the outer ring 28A.

特開２００８−２５８２１号公報JP 2008-25821 A

しかしながら、図１１に示すように、トラニオン１５Ａのポケット部Ｐの内側に設けた段差部１００と外輪２８Ａの外周部とを当接させて支持する構造では、スラスト力Ｆｐｒがパワーローラ１１に殆ど作用しない無負荷に近い状態において、外輪２８Ａの外周部とトラニオン１５Ａの段差部１００との間に隙間が生じる（トラニオン１５Ａの内端面幅Ｗが外輪２８Ａの外径に対して大きく設定されていることに起因する）ため、外輪２８Ａ（パワーローラ１１）とトラニオン１５Ａとの間の相対的な位置ずれにより、変速の安定性が損なわれる（変速比制御に悪影響が及ぶ）虞がある。 However, as shown in FIG. 11, in the structure in which the stepped portion 100 provided inside the pocket portion P of the trunnion 15A and the outer peripheral portion of the outer ring 28A are in contact and supported, the thrust force Fpr almost acts on the power roller 11. In a state close to no load, a gap is generated between the outer peripheral portion of the outer ring 28A and the stepped portion 100 of the trunnion 15A (the inner end face width W of the trunnion 15A is set larger than the outer diameter of the outer ring 28A). For this reason, there is a risk that the stability of the speed change is impaired (the speed ratio control is adversely affected) due to the relative displacement between the outer ring 28A (power roller 11) and the trunnion 15A.

また、特許文献１で提案されるように、トラニオン１５Ａの支持梁部１６Ａに凸部を設けるとともにパワーローラ外輪２８Ａに凹溝を設けることによりこの凹凸係合部で力２Ｆｔを支持する構造では、トラニオン１５Ａおよび外輪２８ＡのそれぞれのＦｐｒ支持面および２Ｆｔ支持面の直角度を厳しく管理しないと、組立不良が発生する虞がある。また、十分な管理には多大なコストがかかるため、直角度の管理を甘くしつつ、ある程度の組立精度を得ようとすると、各部品の公差を緩和しなければならず、結局、外輪２８Ａとトラニオン１５Ａ内端面との間の隙間が大きくなり、変速の安定性が損なわれる結果となる。 In addition, as proposed in Patent Document 1, in the structure in which a convex portion is provided on the support beam portion 16A of the trunnion 15A and a concave groove is provided in the power roller outer ring 28A, the force 2Ft is supported by this concave and convex engaging portion. If the perpendicularity of the Fpr support surface and the 2Ft support surface of the trunnion 15A and the outer ring 28A is not strictly managed, assembly failure may occur. In addition, since sufficient cost is required for sufficient management, tolerance of each part must be relaxed when trying to obtain a certain degree of assembly accuracy while making the management of the squareness easy, and eventually the outer ring 28A and A gap between the inner end face of the trunnion 15A is increased, resulting in a loss of shifting stability.

本発明は、前記事情に鑑みて為されたものであり、作用する荷重の状態によらず、トラニオンの軸方向に関して、外輪（パワーローラ）とトラニオンとの間の相対的な位置ずれをなくすことができ、安定した変速比制御を行なうことができるトロイダル型無段変速機およびその部品の加工方法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 eliminates the relative displacement between the outer ring (power roller) and the trunnion in the axial direction of the trunnion, regardless of the state of the applied load. It is an object of the present invention to provide a toroidal-type continuously variable transmission capable of performing stable gear ratio control and a method for processing parts thereof.

前記目的を達成するために、本発明は、互いの内側面同士を対向させた状態で互いに同心的に且つ回転自在に支持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間に挟持される複数のパワーローラと、前記入力側ディスクおよび前記出力側ディスクの中心軸に対して捻れの位置にあり且つ互いに同心的に設けられた一対の枢軸を中心に傾転するとともに、前記各パワーローラをスラスト軸受を介して回転自在に支持する複数のトラニオンとを備え、前記スラスト軸受は、前記パワーローラによって形成される内輪と、外輪と、これらの内輪と外輪との間で転動する転動体を備え、前記トラニオンは、前記パワーローラ側を向く面に円筒状凸面が形成され、前記円筒状凸面の中心軸が、前記枢軸の中心軸と平行でかつ当該枢軸の中心軸より前記入力側ディスクおよび前記出力側ディスクの中心軸から離れた位置に配置され、前記外輪は、外側面に設けられた円筒状凹面と前記トラニオンの円筒状凸面とを係合させることにより前記トラニオンに対し、前記入力側ディスクおよび前記出力側ディスクの中心軸方向に関する揺動変位を可能に支持されているトロイダル型無段変速機において、互いに対向する前記トラニオンの内端面と前記外輪の外端面とにはそれぞれ、前記トラニオンの軸方向の両側に、前記トラニオンの内端面と前記外輪の外端面とを凹凸嵌合させるように互いに当接して前記トラニオンと前記外輪との間の相対的な軸方向移動を規制する当接支持面が設けられることを特徴とする。 In order to achieve the above object, the present invention provides an input disk and an output disk that are supported concentrically and rotatably with their inner surfaces facing each other, and are sandwiched between these two disks. And a plurality of power rollers that are tilted about a pair of pivots that are concentrically provided with respect to the center axis of the input side disk and the output side disk, A plurality of trunnions that rotatably support the rollers via thrust bearings, the thrust bearings comprising an inner ring formed by the power roller, an outer ring, and a roller that rolls between the inner ring and the outer ring. The trunnion is formed with a cylindrical convex surface on the surface facing the power roller, and the central axis of the cylindrical convex surface is parallel to the central axis of the pivot and the trunnion The outer ring engages the cylindrical concave surface provided on the outer surface and the cylindrical convex surface of the trunnion, which is disposed at a position away from the central axis of the input side disk and the output side disk from the central axis of the shaft. Thus, in the toroidal-type continuously variable transmission that is supported so as to be able to swing and displace with respect to the center axis direction of the input side disk and the output side disk with respect to the trunnion, the inner end face of the trunnion and the outer ring facing each other The outer end surface of each of the trunnions is in contact with each other so that the inner end surface of the trunnion and the outer end surface of the outer ring are fitted in an uneven manner on both sides in the axial direction of the trunnion, and the relative between the trunnion and the outer ring An abutting support surface that restricts general axial movement is provided.

上記構成によれば、トラニオンの内端面および外輪の外端面のそれぞれの両側に、トラニオンの内端面と外輪の外端面とを凹凸嵌合させるように互いに当接してトラニオンと外輪との間の相対的な軸方向移動を規制する当接支持面が設けられるため、作用するスラスト力等の状態によらず、トラニオンの軸方向（図１０参照）に関して、組み付け時に外輪（パワーローラ）とトラニオンとの間の相対的な位置ずれをなくすことができ、安定した変速比制御を行なうことができる。 According to the above configuration, the inner end surface of the trunnion and the outer end surface of the outer ring are respectively brought into contact with each other so that the inner end surface of the trunnion and the outer end surface of the outer ring are fitted in a concave-convex manner. Since a contact support surface for restricting the axial movement is provided, the outer ring (power roller) and the trunnion are not assembled with each other in the axial direction of the trunnion (see FIG. 10) regardless of the state of the acting thrust force or the like. The relative displacement between the two can be eliminated, and stable gear ratio control can be performed.

上記構成において、当接支持面がトーラス状の凹凸面として或いは傾斜面として形成されてもよい。また、上記構成において、外輪の当接支持面がトラニオンの内端面を両側から挟み込むように支持してもよく、あるいは、トラニオンの当接支持面が外輪の外端面を両側から挟み込むように支持してもよい。そのようにすると、パワーローラとトラニオンとの間の相対的な位置ずれを確実に防止でき、確実で適正な組み付けを行なうことができる。 In the above configuration, the contact support surface may be formed as a torus-shaped uneven surface or an inclined surface. In the above configuration, the abutment support surface of the outer ring may be supported so as to sandwich the inner end surface of the trunnion from both sides, or the abutment support surface of the trunnion may be supported so as to sandwich the outer end surface of the outer ring from both sides. May be. By doing so, it is possible to reliably prevent relative displacement between the power roller and the trunnion, and to perform reliable and proper assembly.

また、上記構成において、円筒状の面を成す円筒部が当接支持面に隣接して設けられることが好ましい。この場合には、当接支持面の径方向寸法の管理がし易くなり有益である。特に、円筒部と当接支持面とを同時に加工すると、円筒部の外径または内径寸法を代替特性として管理することが可能となり、加工に際して高度な測定をせずに済む。 In the above configuration, it is preferable that a cylindrical portion forming a cylindrical surface is provided adjacent to the contact support surface. In this case, the radial dimension of the contact support surface can be easily managed, which is beneficial. In particular, when the cylindrical portion and the abutting support surface are processed at the same time, the outer diameter or inner diameter dimension of the cylindrical portion can be managed as an alternative characteristic, and high-level measurement is not required during processing.

また、上記構成において、前記トラニオンの内端面と前記外輪の外端面とにはそれぞれ、軸方向の中央部位に、潤滑油を供給するための油穴が形成され、該油穴が形成される前記トラニオンおよび前記外輪の部位を円筒状の突出部として形成して互いに当接させることにより互いの油穴同士を隙間なく連通させて成ることが好ましい。このようにすると、組み付け時に、油穴周辺の隙間を高精度に小さく設定できるため、潤滑油の漏れを小さくでき、パワーローラを回転可能に支持する軸受部分を十分に潤滑することができる。 Further, in the above configuration, the inner end surface of the trunnion and the outer end surface of the outer ring are each formed with an oil hole for supplying lubricating oil at a central portion in the axial direction, and the oil hole is formed. It is preferable that the trunnion and the outer ring are formed as cylindrical protrusions and brought into contact with each other so that the oil holes communicate with each other without a gap. In this way, the gap around the oil hole can be set small with high accuracy during assembly, so that the leakage of the lubricating oil can be reduced, and the bearing portion that rotatably supports the power roller can be sufficiently lubricated.

また、本発明では、トロイダル型無段変速機の部品の加工方法、具体的には、トラニオンおよび外輪の加工方法が提供される。この加工方法では、トラニオンまたは外輪の両側の一対の当接支持面が同時に加工される。また、該加工方法は、円筒状の面を成す円筒部を前記当接支持面に隣接して形成するステップであって、前記円筒部と前記当接支持面とを同時に加工するステップを更に含むことが好ましい。更に、本加工方法は、前記トラニオンの内端面および前記外輪の外端面のそれぞれの軸方向中央部位に潤滑油を供給するための油穴を形成し、該油穴が形成される前記トラニオンおよび前記外輪の部位を円筒状の突出部として形成するステップであって、前記突出部と前記当接支持面とを同時に加工するステップを更に含むことが好ましい。このような同時加工により、円筒部や突出部の外径または内径寸法を代替特性として管理することが可能となり、加工に際して高度な測定をせずに済む。また、このような加工は総形研削砥石によってなされることが好ましい。総形研削砥石で加工すると、支持当接面同士の距離（トラニオン軸方向ピッチ）を一定に保つことが可能となり、組み高さ精度を更に向上させることができる。 In addition, the present invention provides a method for processing parts of a toroidal type continuously variable transmission, specifically, a method for processing trunnions and outer rings. In this processing method, the pair of contact support surfaces on both sides of the trunnion or the outer ring are processed simultaneously. The processing method further includes a step of forming a cylindrical portion forming a cylindrical surface adjacent to the contact support surface, and the step of simultaneously processing the cylindrical portion and the contact support surface. It is preferable. Further, the present processing method forms an oil hole for supplying lubricating oil to each axially central portion of the inner end surface of the trunnion and the outer end surface of the outer ring, the trunnion in which the oil hole is formed, and the trunnion Preferably, the method further includes the step of forming the outer ring portion as a cylindrical protrusion, and simultaneously processing the protrusion and the contact support surface. By such simultaneous processing, it is possible to manage the outer diameter or inner diameter dimension of the cylindrical portion or the protruding portion as an alternative characteristic, and it is not necessary to perform advanced measurement at the time of processing. Moreover, it is preferable that such a process is performed with a general grinding wheel. Processing with the general grinding wheel makes it possible to keep the distance between the support contact surfaces (pitch in the trunnion axial direction) constant, and to further improve the assembly height accuracy.

本発明によれば、トラニオンの内端面および外輪の外端面のそれぞれの両側に、トラニオンの内端面と外輪の外端面とを凹凸嵌合させるように互いに当接してトラニオンと外輪との間の相対的な軸方向移動を規制する当接支持面が設けられている。そのため、作用する荷重の状態によらず、トラニオンの軸方向に関して、組み付け時に外輪（パワーローラ）とトラニオンとの間の相対的な位置ずれをなくすことができ、安定した変速比制御を行なうことができる。 According to the present invention, the inner end surface of the trunnion and the outer end surface of the outer ring are respectively brought into contact with each other so that the inner end surface of the trunnion and the outer end surface of the outer ring are concavo-convexly fitted to each other. An abutment support surface that restricts general axial movement is provided. For this reason, relative positional deviation between the outer ring (power roller) and the trunnion can be eliminated during assembly with respect to the axial direction of the trunnion regardless of the applied load state, and stable gear ratio control can be performed. it can.

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）は外輪の斜視図、（ｃ）はトラニオンと外輪とを組み付けた状態を示す斜視図、（ｄ）はトラニオンと外輪とを組み付けた状態の断面図、（ｅ）は（ｄ）のＡ部拡大図である。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the 1st Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is a perspective view of an outer ring, (c) is a perspective view which shows the state which assembled | attached the trunnion and the outer ring, (D) is sectional drawing of the state which assembled | attached the trunnion and the outer ring | wheel, (e) is the A section enlarged view of (d). （ａ）は当接支持面に斜線が付された図１の外輪の斜視図、（ｂ）は当接支持面に斜線が付された図１のトラニオンの斜視図、（ｃ）は円筒部および突出部に斜線が付された図１の外輪の斜視図、（ｄ）は円筒部および突出部に斜線が付された図１のトラニオンの斜視図である。1A is a perspective view of the outer ring of FIG. 1 with the abutting support surface hatched, FIG. 1B is a perspective view of the trunnion of FIG. 1 with the abutting support surface hatched, and FIG. FIG. 2 is a perspective view of the outer ring of FIG. 1 with a hatched portion on the protrusion and FIG. 1D is a perspective view of the trunnion of FIG. 1 with a hatched portion on the cylindrical portion and the protrusion. （ａ）は図１のトラニオンの総形研削加工ステップを示す断面図、（ｂ）は図１の外輪の総形研削加工ステップを示す断面図である。(A) is sectional drawing which shows the general shape grinding process step of the trunnion of FIG. 1, (b) is sectional drawing which shows the general shape grinding process step of the outer ring | wheel of FIG. 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）はトラニオンと外輪とを組み付けた状態の断面図、（ｃ）は（ｂ）のＢ部拡大図である。It is a figure which shows the 2nd Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is sectional drawing of the state which assembled | attached the trunnion and the outer ring | wheel, (c) is B part of (b). It is an enlarged view. 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）はトラニオンと外輪とを組み付けた状態の断面図、（ｃ）は（ｂ）のＣ部拡大図である。It is a figure which shows the 3rd Embodiment of this invention, Comprising: (a) is a perspective view of a trunnion, (b) is sectional drawing of the state which assembled | attached the trunnion and the outer ring | wheel, (c) is C section of (b). It is an enlarged view. 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）はトラニオンと外輪とを組み付けた状態の断面図、（ｃ）は（ｂ）のＤ部拡大図である。It is a figure which shows the 4th Embodiment of this invention, (a) is a perspective view of a trunnion, (b) is sectional drawing of the state which assembled | attached the trunnion and the outer ring | wheel, (c) is D section of (b). It is an enlarged view. 従来から知られているハーフ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 half toroidal type continuously variable transmission conventionally known. 図７のＥ−Ｅ線に沿う断面図である。It is sectional drawing which follows the EE line | wire of FIG. ディスクとパワーローラとの位置関係を模式的に示す従来例の平面図である。It is a top view of the prior art example which shows typically the positional relationship of a disk and a power roller. トラニオンおよびパワーローラに作用する力及びそれに伴う変形を概略的に示す断面図である。It is sectional drawing which shows roughly the force which acts on a trunnion and a power roller, and a deformation | transformation accompanying it. （ａ）は従来例に係るトラニオンの断面図、（ｂ）はトラニオンと外輪とを組み付けた状態の断面図である。(A) is sectional drawing of the trunnion which concerns on a prior art example, (b) is sectional drawing of the state which assembled | attached the trunnion and the outer ring | wheel.

以下、図面を参照して本発明の実施の形態を説明する。
なお、本発明の特徴は、パワーローラ外輪とトラニオンとの組み付け構造にあり、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７〜図１１と同一の符号を付して簡潔に説明するに留める。 Embodiments of the present invention will be described below with reference to the drawings.
The feature of the present invention lies in the assembly structure of the power roller outer ring and the trunnion, and the other configurations and operations are the same as the conventional configurations and operations described above. Therefore, only the features of the present invention will be described below. Reference is made to the other parts, and the same reference numerals as those in FIGS.

図１〜図３は、本発明の第１の実施形態を示している。特に図１に示すように、本実施形態のトロイダル型無段変速機のトラニオン１５Ａは、組み付け時にスラスト玉軸受２４の外輪２８Ａの外端面２８ａと対向する内端面（ポケット部Ｐを形成する内側奥端の面）１５ａを有する。また、内端面１５ａ（支持梁部１６Ａの内側面）は軸方向の略全長にわたって円筒面状に形成されている。そして、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとにはそれぞれ、トラニオン１５Ａの軸方向（図１の（ｄ）の矢印の方向）の両側に、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとを凹凸嵌合させる（トラニオン１５Ａの内端面１５ａの凹部２００内に外輪２８Ａの外端面２８ａの凸部２０２を嵌合させる・・・図１の（ｄ）参照）ように互いに当接してトラニオン１５Ａと外輪２８Ａとの間の相対的な軸方向移動を規制する当接支持面１５ｂ，２８ｂが設けられる。また、トラニオン１５Ａの内端面１５ａの凹部２００内に外輪２８Ａの外端面２８ａの凸部２０２が嵌合して当接支持面１５ｂ，２８ｂ同士が当接する組み付け状態（図１の（ｃ），（ｄ）の状態）では、荷重Ｆｐｒ，２Ｆｔに伴う変形を考慮して、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとの間およびトラニオン１５Ａの内側面と外輪２８Ａの外周端面との間に若干の隙間Ｇ１，Ｇ２が設けられる。すなわち、隙間Ｇ１，Ｇ２は、図１０に矢印Ｘで示す方向にトラニオン１５Ａが変形した状態でも、トラニオン１５Ａの内側面と外輪２８Ａの外周端面が接触することがないように設定される。 1 to 3 show a first embodiment of the present invention. In particular, as shown in FIG. 1, the trunnion 15A of the toroidal type continuously variable transmission according to the present embodiment has an inner end surface (an inner rear surface that forms a pocket portion P) that faces the outer end surface 28a of the outer ring 28A of the thrust ball bearing 24 during assembly. End surface) 15a. The inner end surface 15a (the inner surface of the support beam portion 16A) is formed in a cylindrical surface over substantially the entire length in the axial direction. The inner end face 15a of the trunnion 15A and the outer end face 28a of the outer ring 28A are respectively provided on both sides of the trunnion 15A in the axial direction (the direction of the arrow in FIG. 1 (d)). And the outer end surface 28a of the trunnion 15A are engaged with each other (the convex portion 202 of the outer end surface 28a of the outer ring 28A is fitted into the concave portion 200 of the inner end surface 15a of the trunnion 15A, as shown in FIG. 1 (d)). Abutting support surfaces 15b and 28b that abut and restrict relative axial movement between the trunnion 15A and the outer ring 28A are provided. Further, an assembled state in which the convex portion 202 of the outer end surface 28a of the outer ring 28A is fitted in the concave portion 200 of the inner end surface 15a of the trunnion 15A and the contact support surfaces 15b and 28b are in contact with each other ((c) in FIG. In the state d), taking into account the deformation accompanying the loads Fpr and 2Ft, between the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A and between the inner side surface of the trunnion 15A and the outer peripheral end surface of the outer ring 28A. A slight gap G1, G2 is provided. That is, the gaps G1 and G2 are set so that the inner surface of the trunnion 15A and the outer peripheral end surface of the outer ring 28A do not contact even when the trunnion 15A is deformed in the direction indicated by the arrow X in FIG.

また、本実施形態において、当接支持面１５ｂ，２８ｂはトーラス状の凹凸面（円弧状の曲面）として形成されている。また、トラニオン１５Ａの当接支持面１５ｂが外輪２８Ａの外端面２８ａを両側から挟み込むように支持している。 In the present embodiment, the contact support surfaces 15b and 28b are formed as torus-like uneven surfaces (arc-shaped curved surfaces). Further, the abutment support surface 15b of the trunnion 15A supports the outer end surface 28a of the outer ring 28A so as to sandwich it from both sides.

ところで、荷重Ｆｐｒおよび２Ｆｔを支持する当接支持面１５ｂ，２８ｂの仕上げ加工精度は、トラニオン１５Ａと外輪２８Ａ（パワーローラ１１）とを組み付けた際の組み高さに影響を与える（トラニオン１５Ａの枢軸（傾転軸）１４に対するパワーローラ１１の組み高さのばらつきも変速における安定性の低下や耐久性の低下をもたらす）ため、当接支持面１５ｂ，２８ｂを研削加工等により高精度に仕上げることが好ましい（図２の（ａ），（ｂ）の斜線部参照）。そのため、本実施形態では、当接支持面１５ｂ，２８ｂの径方向の管理をし易くするため、円筒面状に形成された円筒部２２０，２４０が当接支持面１５ｂ，２８ｂに隣接して設けられる（図２の（ｃ），（ｄ）の斜線部参照）。また、円筒部２２０の外径または内径寸法を代替特性として管理できるようにし且つ加工時の高度な測定を不要にするため、本実施形態では、後述するように、円筒部２２０と当接支持面１５ｂとが同時に加工され、円筒部２４０と当接支持面２８ｂとが同時に加工される。 By the way, the finishing accuracy of the contact support surfaces 15b and 28b that support the loads Fpr and 2Ft affects the assembly height when the trunnion 15A and the outer ring 28A (power roller 11) are assembled (the pivot of the trunnion 15A). (Variation in the assembly height of the power roller 11 with respect to the (tilting axis) 14 also causes a decrease in stability and a decrease in durability), so that the contact support surfaces 15b and 28b are finished with high accuracy by grinding or the like. Is preferable (see the hatched portions in FIGS. 2A and 2B). Therefore, in this embodiment, in order to easily manage the radial direction of the contact support surfaces 15b and 28b, the cylindrical portions 220 and 240 formed in a cylindrical surface shape are provided adjacent to the contact support surfaces 15b and 28b. (Refer to the hatched portions in FIGS. 2C and 2D). Further, in order to be able to manage the outer diameter or inner diameter dimension of the cylindrical portion 220 as an alternative characteristic and eliminate the need for advanced measurement during processing, in this embodiment, as will be described later, the cylindrical portion 220 and the contact support surface 15b is processed at the same time, and the cylindrical portion 240 and the contact support surface 28b are processed at the same time.

また、本実施形態において、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとにはそれぞれ、軸方向の中央部位に、潤滑油を供給するための油穴１５ｃ，２８ｃが形成されており、該油穴１５ｃ，２８ｃが形成されるトラニオン１５Ａおよび外輪２８Ａの部位は円筒面状の突出部２３０，２５０（図２の（ｃ），（ｄ）の斜線部参照）として形成されて互いに当接されることにより互いの油穴１５ｃ，２８ｃ同士が隙間なく連通されるようになっている（図１の（ｄ）参照）。 Further, in the present embodiment, oil holes 15c and 28c for supplying lubricating oil are formed in the central portion in the axial direction on the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A, The portions of the trunnion 15A and the outer ring 28A in which the oil holes 15c and 28c are formed are formed as cylindrical projecting portions 230 and 250 (see hatched portions in FIGS. 2C and 2D) and contact each other. As a result, the oil holes 15c and 28c communicate with each other without a gap (see (d) of FIG. 1).

図３は、トラニオン１５Ａおよび外輪２８Ａの加工方法の一例を示している。この加工方法では、総形研削砥石３００（３００Ａ）を用いて当接支持面１５ｂ（２８ｂ）と突出部２３０（２５０）と円筒部２２０（２４０）とがワンチャックで同時に加工される。 FIG. 3 shows an example of a processing method for the trunnion 15A and the outer ring 28A. In this processing method, the abutting support surface 15b (28b), the protruding portion 230 (250), and the cylindrical portion 220 (240) are simultaneously processed with a single chuck using the overall grinding wheel 300 (300A).

図３の（ａ）は、総形研削砥石３００を用いて、トラニオン１５Ａの当接支持面１５ｂと突出部２３０と円筒部２２０とがワンチャックで同時に加工される様子を概略的に示している。図示のように、工作物であるトラニオン１５Ａを回転軸Ｏを中心に低速回転Ｖ２で旋回送りしつつ、逃げ部２０３を有する総形研削砥石３００を高速回転Ｖ１させながらトラニオン１５Ａの対応する内端面部位に当てることにより研削加工する。このとき、旋回位置決めを行なうインデックステーブル（図示せず）上のチャッキング治具５００で工作物であるトラニオン１５Ａを把持し、ワンチャックで当接支持面１５ｂと突出部２３０と円筒部２２０とが同時に加工される（逃げ部２０３を除く砥石３００の外周面部位が工作物を加工する）。 FIG. 3A schematically shows a state where the contact support surface 15b of the trunnion 15A, the projecting portion 230, and the cylindrical portion 220 are simultaneously processed with a single chuck using the overall grinding wheel 300. FIG. . As shown in the figure, the trunnion 15A, which is a workpiece, is pivotally fed around the rotation axis O at a low speed rotation V2, and the corresponding inner end face of the trunnion 15A is rotated at a high speed V1 while the general grinding wheel 300 having the escape portion 203 is rotated at a high speed V1. Grind by touching the part. At this time, the trunnion 15A, which is a workpiece, is gripped by a chucking jig 500 on an index table (not shown) that performs turning positioning, and the abutting support surface 15b, the protruding portion 230, and the cylindrical portion 220 are brought together with one chuck. It is processed at the same time (the outer peripheral surface portion of the grindstone 300 excluding the relief portion 203 processes the workpiece).

一方、図３の（ｂ）は、総形研削砥石３００Ａを用いて、外輪２８Ａの当接支持面２８ｂと突出部２５０と円筒部２４０とがワンチャックで同時に加工される様子を概略的に示している。図示のように、工作物である外輪２８Ａをチャッキング治具５００Ａで把時しつつ、逃げ部３０３を有する総形研削砥石３００Ａを高速回転Ｖ１させながら外輪２８Ａの対応する外端面部位に当てることにより研削加工する。このとき、インデックステーブル（図示せず）上のチャッキング治具５００Ａで工作物である外輪２８Ａを把持し、ワンチャックで当接支持面２８ｂと突出部２５０と円筒部２４０とが同時に加工される（逃げ部３０３を除く砥石３００Ａの外周面部位が工作物を加工する）。 On the other hand, FIG. 3B schematically shows a state in which the contact support surface 28b, the protruding portion 250, and the cylindrical portion 240 of the outer ring 28A are simultaneously processed with one chuck using the overall grinding wheel 300A. ing. As shown in the figure, while gripping the outer ring 28A, which is a workpiece, with the chucking jig 500A, the entire grinding wheel 300A having the relief portion 303 is applied to the corresponding outer end surface portion of the outer ring 28A while rotating at high speed V1. Grind by. At this time, the outer ring 28A, which is a workpiece, is gripped by a chucking jig 500A on an index table (not shown), and the contact support surface 28b, the protruding portion 250, and the cylindrical portion 240 are simultaneously processed with one chuck. (The outer peripheral surface portion of the grindstone 300A excluding the escape portion 303 processes the workpiece).

以上説明したように、本実施形態によれば、トラニオン１５Ａの内端面１５ａおよび外輪２８Ａの外端面２８ａのそれぞれの両側に、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとを凹凸嵌合させるように互いに当接してトラニオン１５Ａと外輪２８Ａとの間の相対的な軸方向移動を規制する当接支持面１５ｂ，２８ｂが設けられるため、荷重Ｆｐｒ、２Ｆｔの状態によらず、トラニオン１５Ａの軸方向（図１０参照）に関して、組み付け時に外輪２８Ａ（パワーローラ１１）とトラニオン１５Ａとの間の相対的な位置ずれをなくすことができ、安定した変速比制御を行なうことができる。 As described above, according to the present embodiment, the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are unevenly fitted on both sides of the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A. Since the contact support surfaces 15b and 28b that contact each other so as to restrict relative axial movement between the trunnion 15A and the outer ring 28A are provided, the trunnion 15A of the trunnion 15A does not depend on the state of the loads Fpr and 2Ft. With respect to the axial direction (see FIG. 10), the relative positional deviation between the outer ring 28A (power roller 11) and the trunnion 15A can be eliminated during assembly, and stable gear ratio control can be performed.

また、本実施形態では、トラニオン１５Ａの当接支持面１５ｂが外輪２８Ａの外端面２８ａを両側から挟み込むように支持している。そのため、外輪２８Ａ（パワーローラ１１）とトラニオン１５Ａとの間の相対的な位置ずれを確実に防止でき、確実で適正な組み付けを行なうことができる。 In the present embodiment, the abutment support surface 15b of the trunnion 15A supports the outer end surface 28a of the outer ring 28A so as to sandwich it from both sides. Therefore, a relative positional shift between the outer ring 28A (power roller 11) and the trunnion 15A can be surely prevented, and reliable and proper assembly can be performed.

また、本実施形態では、円筒状の面を成す円筒部２２０，２４０が当接支持面１５ｂ，２８ｂに隣接して設けられているため、当接支持面１５ｂ，２８ｂの径方向寸法の管理がし易くなり有益である。特に、円筒部２２０，２４０（突出部２３０，２５０も）と当接支持面１５ｂ，２８ｂとを同時に加工するため、円筒部２２０，２４０（突出部２３０，２５０）の外径または内径寸法を代替特性として管理することが可能となり、加工に際して高度な測定をせずに済む。 In the present embodiment, since the cylindrical portions 220 and 240 forming cylindrical surfaces are provided adjacent to the contact support surfaces 15b and 28b, the radial dimensions of the contact support surfaces 15b and 28b can be managed. It is easy to do and is beneficial. In particular, since the cylindrical portions 220 and 240 (also projecting portions 230 and 250) and the contact support surfaces 15b and 28b are processed simultaneously, the outer diameter or inner diameter dimension of the cylindrical portions 220 and 240 (projecting portions 230 and 250) is replaced. It can be managed as a characteristic, and it is not necessary to perform advanced measurement during processing.

また、本実施形態において、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとにはそれぞれ、軸方向の中央部位に、潤滑油を供給するための油穴１５ｃ，２８ｃが形成され、該油穴１５ｃ，２８ｃが形成されるトラニオン１５Ａおよび外輪２８Ａの部位を円筒状の突出部２３０，２５０として形成して互いに当接させることにより互いの油穴１５ｃ，２８ｃ同士を隙間なく連通させている。そのため、組み付け時に、油穴１５ｃ，２８ｃ周辺の隙間を高精度に小さく設定できるため、潤滑油の漏れを小さくでき、パワーローラ１１を回転可能に支持する軸受２４部分を十分に潤滑することができる。 In the present embodiment, the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are respectively formed with oil holes 15c and 28c for supplying lubricating oil at the central portion in the axial direction. The portions of the trunnion 15A and the outer ring 28A in which the holes 15c and 28c are formed are formed as cylindrical projecting portions 230 and 250 and brought into contact with each other so that the oil holes 15c and 28c communicate with each other without any gap. Therefore, since the clearance around the oil holes 15c and 28c can be set small with high accuracy during assembly, the leakage of the lubricating oil can be reduced, and the bearing 24 portion that rotatably supports the power roller 11 can be sufficiently lubricated. .

図４は、本発明の第２の実施形態を示している。図示のように、本実施形態のトロイダル型無段変速機のトラニオン１５Ａも、組み付け時にスラスト玉軸受２４の外輪２８Ａの外端面２８ａと対向する内端面（ポケット部Ｐを形成する内側奥端の面）１５ａを有する。トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとにはそれぞれ、トラニオン１５Ａの軸方向の両側に、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとを凹凸嵌合させるように互いに当接してトラニオン１５Ａと外輪２８Ａとの間の相対的な軸方向移動を規制する当接支持面１５ｂ，２８ｂが設けられる。これらの当接支持面１５ｂ，２８ｂも第１の実施形態と同様にトーラス状の凹凸面（円弧状の曲面）として形成されるが、外輪２８Ａの当接支持面２８ｂがトラニオン１５Ａの内端面１５ａを両側から挟み込むように支持する点が第１の実施形態と異なる。なお、それ以外は第１の実施形態と同様である。したがって、このような構成によっても第１の実施形態と同様の作用効果を得ることができる。 FIG. 4 shows a second embodiment of the present invention. As shown in the figure, the trunnion 15A of the toroidal-type continuously variable transmission according to the present embodiment also has an inner end surface (an inner rear end surface that forms the pocket portion P) that faces the outer end surface 28a of the outer ring 28A of the thrust ball bearing 24 when assembled. ) 15a. The inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are respectively in contact with each other so that the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are concavo-convexly fitted on both sides in the axial direction of the trunnion 15A. Abutting support surfaces 15b and 28b are provided that contact and regulate relative axial movement between the trunnion 15A and the outer ring 28A. These contact support surfaces 15b and 28b are also formed as torus-like uneven surfaces (arc-shaped curved surfaces) as in the first embodiment, but the contact support surface 28b of the outer ring 28A is the inner end surface 15a of the trunnion 15A. The point which supports so that it may be inserted | pinched from both sides differs from 1st Embodiment. The rest is the same as in the first embodiment. Accordingly, even with such a configuration, it is possible to obtain the same operational effects as those of the first embodiment.

図５は、本発明の第３の実施形態を示している。図示のように、本実施形態のトロイダル型無段変速機のトラニオン１５Ａも、組み付け時にスラスト玉軸受２４の外輪２８Ａの外端面２８ａと対向する内端面（ポケット部Ｐを形成する内側奥端の面）１５ａを有する。トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとにはそれぞれ、トラニオン１５Ａの軸方向の両側に、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとを凹凸嵌合させるように互いに当接してトラニオン１５Ａと外輪２８Ａとの間の相対的な軸方向移動を規制する当接支持面１５ｂ，２８ｂが設けられる。これらの当接支持面１５ｂ，２８ｂは傾斜面（テーパ面）として形成されており、トラニオン１５Ａの当接支持面１５ｂが外輪２８Ａの外端面２８ａを両側から挟み込むように支持している。なお、それ以外は第１の実施形態と同様である。したがって、このような構成によっても第１の実施形態と同様の作用効果を得ることができる。 FIG. 5 shows a third embodiment of the present invention. As shown in the figure, the trunnion 15A of the toroidal-type continuously variable transmission according to the present embodiment also has an inner end surface (an inner rear end surface that forms the pocket portion P) that faces the outer end surface 28a of the outer ring 28A of the thrust ball bearing 24 when assembled. ) 15a. The inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are respectively in contact with each other so that the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are concavo-convexly fitted on both sides in the axial direction of the trunnion 15A. Abutting support surfaces 15b and 28b are provided that contact and regulate relative axial movement between the trunnion 15A and the outer ring 28A. These contact support surfaces 15b and 28b are formed as inclined surfaces (tapered surfaces), and the contact support surface 15b of the trunnion 15A supports the outer end surface 28a of the outer ring 28A so as to sandwich it from both sides. The rest is the same as in the first embodiment. Accordingly, even with such a configuration, it is possible to obtain the same operational effects as those of the first embodiment.

図６は、本発明の第４の実施形態を示している。図示のように、本実施形態のトロイダル型無段変速機のトラニオン１５Ａも、組み付け時にスラスト玉軸受２４の外輪２８Ａの外端面２８ａと対向する内端面（ポケット部Ｐを形成する内側奥端の面）１５ａを有する。トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとにはそれぞれ、トラニオン１５Ａの軸方向の両側に、トラニオン１５Ａの内端面１５ａと外輪２８Ａの外端面２８ａとを凹凸嵌合させるように互いに当接してトラニオン１５Ａと外輪２８Ａとの間の相対的な軸方向移動を規制する当接支持面１５ｂ，２８ｂが設けられる。これらの当接支持面１５ｂ，２８ｂは傾斜面（テーパ面）として形成されており、外輪２８Ａの当接支持面２８ｂがトラニオン１５Ａの内端面１５ａを両側から挟み込むように支持している。なお、それ以外は第１の実施形態と同様である。したがって、このような構成によっても第１の実施形態と同様の作用効果を得ることができる。 FIG. 6 shows a fourth embodiment of the present invention. As shown in the figure, the trunnion 15A of the toroidal-type continuously variable transmission according to the present embodiment also has an inner end surface (an inner rear end surface that forms the pocket portion P) that faces the outer end surface 28a of the outer ring 28A of the thrust ball bearing 24 when assembled. ) 15a. The inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are respectively in contact with each other so that the inner end surface 15a of the trunnion 15A and the outer end surface 28a of the outer ring 28A are concavo-convexly fitted on both sides in the axial direction of the trunnion 15A. Abutting support surfaces 15b and 28b are provided that contact and regulate relative axial movement between the trunnion 15A and the outer ring 28A. These contact support surfaces 15b and 28b are formed as inclined surfaces (tapered surfaces), and the contact support surface 28b of the outer ring 28A supports the inner end surface 15a of the trunnion 15A so as to sandwich it from both sides. The rest is the same as in the first embodiment. Accordingly, even with such a configuration, it is possible to obtain the same operational effects as those of the first 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.

２入力側ディスク
３出力側ディスク
１１パワーローラ
１４枢軸
１５Ａトラニオン
１５ａ内端面
１５ｂ当接支持面
１５ｃ油穴
１６Ａ支持梁部
２４スラスト玉軸受（軸受）
２６転動体
２７保持器
２８Ａ外輪
２８ａ外端面
２８ｂ当接支持面
２８ｃ油穴
２２０，２４０円筒部
２３０，２５０突出部 2 Input side disk 3 Output side disk 11 Power roller 14 Axis 15A Trunnion 15a Inner end face 15b Abutting support face 15c Oil hole 16A Support beam 24 Thrust ball bearing (bearing)
26 Rolling element 27 Cage 28A Outer ring 28a Outer end surface 28b Abutting support surface 28c Oil hole 220, 240 Cylindrical portion 230, 250 Projection

Claims

An input-side disk and an output-side disk that are supported concentrically and rotatably with their inner surfaces facing each other, a plurality of power rollers sandwiched between these two disks, and the input-side disk And tilting about a pair of pivots concentrically provided with respect to the center axis of the output-side disk, and rotatably supporting each power roller via a thrust bearing A plurality of trunnions, and the thrust bearing includes an inner ring formed by the power roller, an outer ring, and rolling elements that roll between the inner ring and the outer ring, and the trunnion is disposed on the power roller side. A cylindrical convex surface is formed on the surface facing the cylindrical surface, and the central axis of the cylindrical convex surface is parallel to the central axis of the pivot and the input side disc is more than the central axis of the pivot. The outer ring is disposed at a position away from the center axis of the output side disk, and the outer ring engages the trunnion with a cylindrical concave surface provided on an outer surface and the trunnion cylindrical convex surface. In the toroidal type continuously variable transmission that is supported so as to be capable of swinging displacement in the direction of the central axis of the side disk and the output side disk,
The inner end surface of the trunnion and the outer end surface of the outer ring facing each other are in contact with each other so that the inner end surface of the trunnion and the outer end surface of the outer ring are concavo-convexly fitted on both sides in the axial direction of the trunnion. A toroidal continuously variable transmission is provided with a contact support surface for restricting relative axial movement between the trunnion and the outer ring.

The toroidal continuously variable transmission according to claim 1, wherein the contact support surface is formed as a torus-shaped uneven surface.

The toroidal continuously variable transmission according to claim 1, wherein the contact support surface is formed as an inclined surface.

The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein the contact support surface of the outer ring supports the inner end surface of the trunnion from both sides.

The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein the abutment support surface of the trunnion supports the outer end surface of the outer ring so as to sandwich the outer ring from both sides.

The toroidal continuously variable transmission according to any one of claims 1 to 5, wherein a cylindrical portion forming a cylindrical surface is provided adjacent to the contact support surface.

An oil hole for supplying lubricating oil is formed in an axial central portion on each of the inner end surface of the trunnion and the outer end surface of the outer ring, and the trunnion and the outer ring portions where the oil holes are formed. The toroidal type according to any one of claims 1 to 6, wherein the oil holes are communicated with each other without any gaps by forming them as cylindrical projections and abutting each other. Continuously variable transmission.

An input-side disk and an output-side disk that are supported concentrically and rotatably with their inner surfaces facing each other, a plurality of power rollers sandwiched between these two disks, and the input-side disk And tilting about a pair of pivots concentrically provided with respect to the center axis of the output-side disk, and rotatably supporting each power roller via a thrust bearing A plurality of trunnions, and the thrust bearing includes an inner ring formed by the power roller, an outer ring, and rolling elements that roll between the inner ring and the outer ring, and the trunnion is disposed on the power roller side. A cylindrical convex surface is formed on the surface facing the cylindrical surface, and the central axis of the cylindrical convex surface is parallel to the central axis of the pivot and the input side disc is more than the central axis of the pivot. The outer ring is disposed at a position away from the center axis of the output side disk, and the outer ring engages the trunnion with a cylindrical concave surface provided on an outer surface and the trunnion cylindrical convex surface. The side disc and the output side disc are supported so as to be able to swing and displace in the direction of the central axis, and the inner end surface of the trunnion and the outer end surface of the outer ring facing each other are respectively on both sides in the axial direction of the trunnion. A toroidal provided with an abutment support surface that abuts against each other so that the inner end surface of the trunnion and the outer end surface of the outer ring are concavo-convexly fitted to restrict relative axial movement between the trunnion and the outer ring A processing method for the trunnion and outer ring of a continuously variable transmission,
A processing method comprising the step of simultaneously processing a pair of contact support surfaces on both sides of the trunnion or the outer ring.

The method further comprises the step of forming a cylindrical portion forming a cylindrical surface adjacent to the abutting support surface, wherein the step further includes processing the cylindrical portion and the abutting support surface simultaneously. 8. The processing method according to 8.

An oil hole for supplying lubricating oil is formed in each axial center portion of the inner end surface of the trunnion and the outer end surface of the outer ring, and the trunnion and the outer ring portion in which the oil hole is formed are formed in a cylindrical shape. 10. The processing method according to claim 8, further comprising a step of forming the protrusion and the contact support surface at the same time.

The processing method according to any one of claims 8 to 10, wherein the processing is performed with a general grinding wheel.