JP7626012B2

JP7626012B2 - Toroidal type continuously variable transmission

Info

Publication number: JP7626012B2
Application number: JP2021145242A
Authority: JP
Inventors: 保雄伊東
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2021-09-07
Filing date: 2021-09-07
Publication date: 2025-02-04
Anticipated expiration: 2041-09-07
Also published as: JP2023038485A

Description

本発明は、自動車、航空機の発電機または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 type continuously variable transmission that can be used in generators for automobiles and aircraft, or transmissions for 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９および図１０に示すように構成されている。図９に示すように、ケーシング５０の内側には入力軸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（伝達歯車）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。
入力軸１は、図９中左側に位置する入力側ディスク２とカム板（ローディングカム）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。 For example, a double-cavity toroidal type continuously variable transmission used as an automobile transmission is constructed as shown in Figures 9 and 10. As shown in Figure 9, an input shaft 1 is rotatably supported inside a casing 50, and two input side discs 2, 2 and two output side discs 3, 3 are attached to the outer periphery of this input shaft 1. An output gear (transmission gear) 4 is rotatably supported on the outer periphery of a middle part of the input shaft 1. The output side discs 3, 3 are connected to cylindrical flanges 4a, 4a provided at the center of this output gear 4 by spline coupling.
The input shaft 1 is rotated by a drive shaft 22 via a loading cam type pressing device 12 provided between the input side disk 2 located on the left side in Fig. 9 and a cam plate (loading cam) 7. The output gear 4 is supported in a casing 50 via a partition wall 13 formed by joining two members, which allows the output gear 4 to rotate about the axis O of the input shaft 1 while preventing displacement in the direction of the axis O.

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９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９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ととも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；トラクション面とも言う）２ａ，２ａと出力ディスク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１０参照）が回転自在に挟持されている。 The output side disks 3, 3 are supported rotatably around the axis O of the input shaft 1 by needle bearings 5, 5 interposed between them and the input shaft 1. The input side disk 2 on the left side in FIG. 9 is supported on the input shaft 1 via a ball spline 6, and the input side disk 2 on the right side in FIG. 9 is splined to the input shaft 1, so that these input side disks 2 rotate together with the input shaft 1. A power roller 11 (see FIG. 10) is rotatably sandwiched between the inner surfaces (concave surfaces; also called traction surfaces) 2a, 2a of the input side disks 2, 2 and the inner surfaces (concave surfaces; also called traction surfaces) 3a, 3a of the output disks 3, 3.

図９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９の右面）は、入力軸１の外周面に形成されたネジ部に螺合された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（予圧）を付与する。 The inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 9 is provided with a step 2b, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 abuts against this step 2b, and the back surface of the input side disk 2 (the right surface in FIG. 9) abuts against a loading nut 9 screwed into a threaded portion formed on the outer peripheral surface of the input shaft 1. This essentially prevents the input side disk 2 from displacing in the direction of the axis O relative to the input shaft 1. In addition, a disc spring 8 is provided between the cam plate 7 and the flange portion 1d of the input shaft 1, and this disc spring 8 applies a pressing force (preload) to the contact portion between the concave surfaces 2a, 2a, 3a, 3a of each disk 2, 2, 3, 3 and the peripheral surfaces 11a, 11a of the power rollers 11, 11.

図１０は、図９のＡ－Ａ線に沿う断面図である。図１０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１０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、支持板部１６の長手方向(図１０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。 Figure 10 is a cross-sectional view taken along line A-A in Figure 9. As shown in Figure 10, a pair of trunnions 15, 15 are provided inside the casing 50, which swing about a pair of pivots 14, 14 that are in a twisted position relative to the input shaft 1. Note that the input shaft 1 is not shown in Figure 10. Each trunnion 15, 15 has a pair of bent walls 20, 20 formed at both ends of the support plate 16 in the longitudinal direction (the vertical direction in Figure 10) in a state where the support plate 16 is bent toward the inner surface side of the support plate 16. The bent walls 20, 20 form a concave pocket P in each trunnion 15, 15 for accommodating the power roller 11. The pivots 14, 14 are provided concentrically with each other on the outer surfaces of the bent walls 20, 20.

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 center of the support plate portion 16, and the base end 23a of the displacement shaft 23 is supported in this circular hole 21. The inclination angle of the displacement shaft 23 supported in the center of each trunnion 15 can be adjusted by swinging each trunnion 15 about each pivot 14. The power rollers 11 are rotatably supported around the tip end 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, and each power roller 11 is sandwiched between each input side disk 2 and each output side disk 3. The base end 23a and tip end 23b of each displacement shaft 23 are eccentric to each other.

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１０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１０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５６によって揺動自在に支持されている。 The pivots 14, 14 of each trunnion 15, 15 are supported by a pair of yokes 23A, 23B so as to be freely swingable and displaceable in the axial direction (vertical direction in FIG. 10), and the horizontal movement of the trunnions 15, 15 is restricted by the yokes 23A, 23B. Each yoke 23A, 23B is formed into 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 yoke 23A, 23B, and the pivots 14 provided at both ends of the trunnion 15 are supported in a swingable manner via radial needle bearings 30 in each of the support holes 18. A circular locking hole 19 is provided at the center of the width direction (horizontal direction in FIG. 10) of the yokes 23A, 23B, and the inner peripheral surface of the locking hole 19 is a cylindrical surface, into which the spherical posts 64, 68 are fitted. That is, the upper yoke 23A is supported so as to be freely swingable by a spherical post 64 that is supported on the casing 50 via a fixed member 52, and the lower yoke 23B is supported so as to be freely swingable by a spherical post 68 and the upper cylinder body 56 of the drive cylinder 31 that supports it.

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１０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, 23 provided on each trunnion 15, 15 are provided at positions 180 degrees opposite each other with respect to the input shaft 1. The direction in which the tip end 23b of each of these displacement shafts 23, 23 is eccentric with respect to the base end 23a is the same direction as the direction of rotation of both disks 2, 2, 3, 3 (upside down in Fig. 10). The eccentric direction is approximately perpendicular to the direction in which the input shaft 1 is arranged. Therefore, each power roller 11, 11 is supported so that it 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 based on the thrust load generated by the pressing device 12, this displacement is absorbed without applying excessive force to each component.

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（スラスト軸受）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。 In addition, 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 (thrust bearing) 24, which is a thrust rolling bearing, and a thrust needle bearing 25 are provided in order from the outer surface side of the power roller 11. Of these, the thrust ball bearing 24 supports the thrust load applied to each power roller 11 while allowing each power roller 11 to rotate. Each thrust ball bearing 24 is composed of a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular cage 27 that holds each of the rolling elements 26, 26 so that they can roll freely, and an annular outer ring 28. In addition, the inner ring raceway of each thrust ball bearing 24 is formed on the outer surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner 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 bearings 25 are 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 thrust needle bearings 25 support the thrust load applied from the power rollers 11 to each outer ring 28, while allowing the power rollers 11 and the outer ring 28 to oscillate around the base end portion 23a of each displacement shaft 23.

さらに、各トラニオン１５，１５の一端部(図１０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５６と下側シリンダボディ５７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。 Furthermore, a drive rod (trunnion shaft) 29, 29 is provided at one end of each trunnion 15, 15 (lower end in FIG. 10), and a drive piston (hydraulic piston) 33, 33 is fixed to the outer peripheral surface of the middle part of each drive rod 29, 29. Each of these drive pistons 33, 33 is oil-tightly fitted into a drive cylinder 31 composed of an upper cylinder body 56 and a lower cylinder body 57. Each of these drive pistons 33, 33 and the drive cylinder 31 constitute a drive device 32 that displaces each of the trunnions 15, 15 in the axial direction of the pivots 14, 14 of the trunnions 15, 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、さら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 a toroidal type continuously variable transmission configured in this manner, the rotation of the input shaft 1 is transmitted to each of the input side disks 2, 2 via a pressing device 12. The rotation of these input side disks 2, 2 is then transmitted to each of the output side disks 3, 3 via a pair of power rollers 11, 11, and the rotation of each of the output side disks 3, 3 is further extracted by the output gear 4.

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１０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. With the displacement of each of the drive pistons 33, 33, the pair of trunnions 15, 15 are displaced in opposite directions. For example, the power roller 11 on the left side of Fig. 10 is displaced downward in the figure, and the power roller 11 on the right side of the figure is displaced upward in the figure.
As a result, the direction of the tangential force acting on the contact portions between the peripheral surfaces 11a, 11a of the power rollers 11, 11 and the inner surfaces 2a, 2a, 3a, 3a of the input disks 2, 2 and the output disks 3, 3 changes. Then, with the change in the direction of the force, the trunnions 15, 15 swing (tilt) in opposite directions to each other about the pivots 14, 14 pivotally supported by the yokes 23A, 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 circumferential surface 11a, 11a of each power roller 11, 11 and each inner surface 2a, 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. In addition, 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, each power roller 11, 11 and the outer rings 28, 28 attached to each power roller 11, 11 rotate slightly around the base end 23a, 23a of each displacement shaft 23, 23. Since thrust needle bearings 25, 25 are present between the outer surface of each outer ring 28, 28 and the inner surface of the support plate portion 16 constituting each trunnion 15, 15, the rotation is performed smoothly. Therefore, as described above, only a small force is required to change the inclination angle of each displacement shaft 23, 23.

ところで、上記構成のトロイダル型無段変速機においては、パワーローラ１１を支持するスラスト玉軸受２４に大きなスラスト方向の荷重がかかることから、このスラスト玉軸受２４の転動体２６，２６の周囲に潤滑油を供給する構造を備えている。
従来、このスラスト玉軸受（スラスト軸受）２４への潤滑油の供給は、スラスト玉軸受２４の中央を通るシャフト（支持軸）２３ｂに油孔を形成し、この油孔を介してスラスト玉軸受２４の内側から潤滑油を吐出して行われている。
しかしながら、シャフトの油孔から潤滑油を吐出してスラスト軸受に適切な割合で振り分けるには、油孔の開口部を適切な位置に高精度に形成する必要があるため、シャフトの加工コストが増大するという問題がある。このため、油孔の開口部を高精度に形成しないとすると、スラスト軸受に油孔から潤滑油が適切な量および方向、位置や割合で供給され難いため、例えば特許文献１に記載されるように、シャフト（支持軸）とスラスト軸受との間にリング形状の潤滑油分配部材を設け、この潤滑油分配部材に前記油孔から供給される潤滑油をスラスト転がり軸受の方へ分配して送る複数の分配路を設けることで、スラスト軸受の内輪（パワーローラ）側と外輪側に適切な量を適切な割合で振り分けて潤滑油を供給するようにしている。 Incidentally, in the toroidal type continuously variable transmission configured as described above, since a large thrust load is applied to the thrust ball bearing 24 supporting the power roller 11, a structure is provided for supplying lubricating oil to the periphery of the rolling elements 26, 26 of this thrust ball bearing 24.
Conventionally, lubricating oil is supplied to this thrust ball bearing (thrust bearing) 24 by forming an oil hole in the shaft (support shaft) 23b that passes through the center of the thrust ball bearing 24, and discharging lubricating oil from the inside of the thrust ball bearing 24 through this oil hole.
However, in order to discharge the lubricating oil from the oil hole of the shaft and distribute it to the thrust bearing in an appropriate ratio, it is necessary to form the opening of the oil hole at an appropriate position with high accuracy, which increases the processing cost of the shaft. Therefore, if the opening of the oil hole is not formed with high accuracy, it is difficult to supply the lubricating oil from the oil hole to the thrust bearing in an appropriate amount, direction, position and ratio. For example, as described in Patent Document 1, a ring-shaped lubricating oil distribution member is provided between the shaft (support shaft) and the thrust bearing, and this lubricating oil distribution member is provided with multiple distribution paths that distribute and send the lubricating oil supplied from the oil hole to the thrust rolling bearing, so that the lubricating oil is distributed in an appropriate amount and ratio to the inner ring (power roller) side and the outer ring side of the thrust bearing.

特開２０１２－２２５４７９号公報JP 2012-225479 A

しかしながら、特許文献１に記載の従来のトロイダル型無段変速機では、潤滑油分配部材が樹脂（例えばフッ素樹脂）製である一方、支持軸は焼入れ鋼等の金属製であり、さらに、潤滑油分配部材の固定は、当該潤滑油分配部材を支持軸に圧入しているだけであるので、樹脂製の潤滑油分配部材の締め付け力は低く、潤滑油分配部材が樹脂製であるがために、運転時の高温および振動において変形なども生じる。また、潤滑油分配部材が樹脂製である一方、支持軸は金属製であるため、潤滑油分配部材と支持軸との熱膨張係数（又は線熱膨張係数）の差が大きくなる。このため、運転時に高温となると、支持軸より潤滑油分配部材が大きく膨張してしまう。以上の結果、支持軸と潤滑油分配部材との間に隙間が生じ、潤滑油分配部材が支持軸の軸方向に移動してしまうおそがある。潤滑油分配部材が支持軸の軸方向でパワーローラ側に移動すると、回転するパワーローラとの接触が発生し、動力伝達効率の低下や接触部の摩耗の進行、摩耗粉の発生によるパワーローラ軸受の剥離に至るおそれがある。 However, in the conventional toroidal type continuously variable transmission described in Patent Document 1, the lubricant distribution member is made of resin (e.g., fluororesin), while the support shaft is made of metal such as hardened steel. Furthermore, the lubricant distribution member is fixed by simply pressing the lubricant distribution member into the support shaft, so the tightening force of the resin lubricant distribution member is low, and because the lubricant distribution member is made of resin, deformation occurs due to high temperatures and vibrations during operation. In addition, while the lubricant distribution member is made of resin, the support shaft is made of metal, so the difference in thermal expansion coefficient (or linear thermal expansion coefficient) between the lubricant distribution member and the support shaft becomes large. Therefore, when the temperature becomes high during operation, the lubricant distribution member expands more than the support shaft. As a result, a gap is generated between the support shaft and the lubricant distribution member, and there is a risk that the lubricant distribution member will move in the axial direction of the support shaft. If the lubricant distribution member moves toward the power roller in the axial direction of the support shaft, contact with the rotating power roller will occur, which may lead to a decrease in power transmission efficiency, progression of wear at the contact part, and peeling of the power roller bearing due to the generation of wear powder.

本発明は、前記事情に鑑みてなされたもので、パワーローラを回転可能に支持する支持軸に潤滑油分配部材を強固に固定でき、運転時に潤滑油分配部材の支持軸に対する所定の位置からの移動を防止できるトロイダル型無段変速機を提供することを目的としている。 The present invention was made in consideration of the above circumstances, and aims to provide a toroidal type continuously variable transmission in which the lubricant distribution member can be firmly fixed to the support shaft that rotatably supports the power roller, and in which the lubricant distribution member can be prevented from moving from a predetermined position relative to the support shaft during operation.

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、それぞれの内側面どうしを互いに対向させた状態で互いに同心的にかつ回転自在に設けられた第１ディスクおよび第２ディスクと、
前記第１ディスクと前記第２ディスクとの間に挟持されるパワーローラと、
前記第１ディスクおよび前記第２ディスクの中心軸に対して捻れの位置にある枢軸を中心に傾転し、かつ支持軸を中心に前記パワーローラを回転可能に支持するトラニオンと、
前記パワーローラに加わるスラスト荷重を受けつつ前記パワーローラを回転可能に支持するスラスト軸受と、
前記支持軸の外周面に開口し前記スラスト軸受に向けて潤滑油を送る油孔と、
前記支持軸に通されて前記支持軸と前記スラスト軸受との間に配設され、かつ前記油孔から供給される潤滑油を前記スラスト軸受の方へ分配して送る複数の分配路を有するリング形状の潤滑油分配部材とを備えたトロイダル型無段変速機において、
前記支持軸と前記潤滑油分配部材との双方は、金属製であり、
さらに、前記支持軸の所定の位置から前記潤滑油分配部材が移動するのを防止する移動防止構造を有することを特徴とする。
ここで「所定の位置」とは、潤滑油分配部材が支持軸に設計とおりに固定される部位のことである。 In order to achieve the above object, the toroidal type continuously variable transmission of the present invention comprises a first disk and a second disk, the first disk and the second disk being concentrically and rotatably disposed with their inner surfaces facing each other;
a power roller sandwiched between the first disc and the second disc;
a trunnion that tilts about a pivot axis that is in a twisted position with respect to central axes of the first disk and the second disk and supports the power roller rotatably about a support shaft;
a thrust bearing that rotatably supports the power roller while receiving a thrust load applied to the power roller;
an oil hole that opens to an outer peripheral surface of the support shaft and supplies lubricating oil toward the thrust bearing;
a ring-shaped lubricant oil distribution member that is passed through the support shaft and disposed between the support shaft and the thrust bearing, and that has a plurality of distribution paths that distribute and send lubricant oil supplied from the oil hole toward the thrust bearing,
Both the support shaft and the lubricant distribution member are made of metal;
The lubricant distribution member may further include a movement prevention structure for preventing the lubricant distribution member from moving from a predetermined position on the support shaft.
Here, the "predetermined position" refers to the location where the lubricant distribution member is fixed to the support shaft as designed.

本発明においては、支持軸と前記潤滑油分配部材との双方が金属製であり、前記支持軸の所定の位置からの潤滑油分配部材の移動を防止する移動防止構造を有するので、支持軸に潤滑油分配部材を強固に固定でき、高温高回転および高い振動が発生する運転時に潤滑油分配部材が支持軸の所定の位置から移動するのを防止できる。 In the present invention, both the support shaft and the lubricant distribution member are made of metal and have a movement prevention structure that prevents the lubricant distribution member from moving from a specified position on the support shaft, so that the lubricant distribution member can be firmly fixed to the support shaft and the lubricant distribution member can be prevented from moving from a specified position on the support shaft during operation at high temperatures, high rotation speeds, and high vibrations.

本発明の前記構成において、前記移動防止構造は、前記潤滑油分配部材を前記支持軸に焼き嵌め固定した構造、または前記支持軸を前記潤滑油分配部材に冷やし嵌め固定した構造であってもよい。 In the above-described configuration of the present invention, the movement prevention structure may be a structure in which the lubricant distribution member is shrink-fitted to the support shaft, or a structure in which the support shaft is cold-fitted to the lubricant distribution member.

ここで、焼き嵌め固定した構造とは、焼き嵌めする前（常温時）の潤滑油分配部材の内径寸法を、支持軸の外径仕上げ加工寸法に対し小さい値とし、そして、潤滑油分配部材を温め内径寸法が支持軸の仕上げ加工寸法より大きくなるよう膨張させて、支持軸へ嵌めこんだ後、冷却することによって、潤滑油分配部材を支持軸に固定する構造のことを言う。
また、冷やし嵌め固定した構造とは、冷やし嵌めする前（常温時）の支持軸の外径仕上げ加工寸法を、潤滑油分配部材の内径寸法に対し大きい値とし、そして、支持軸を冷やして、支持軸の外径寸法が潤滑油分配部材の内径寸法より小さくなるように収縮させて、当該支持軸を潤滑油分配部材に嵌め込んだ後、常温に戻すことによって、潤滑油分配部材を支持軸に固定する構造のことを言う。 Here, the shrink-fitted structure refers to a structure in which the inner diameter dimension of the lubricant distribution member before shrink-fitting (at room temperature) is made smaller than the outer diameter finish dimension of the support shaft, and the lubricant distribution member is heated to expand so that the inner diameter dimension becomes larger than the finish dimension of the support shaft, and then the lubricant distribution member is fitted onto the support shaft and then cooled to fix the lubricant distribution member to the support shaft.
In addition, the term "cold-fit fixed structure" refers to a structure in which the outer diameter finishing dimension of the support shaft before cold fitting (at room temperature) is made larger than the inner diameter dimension of the lubricant distribution member, the support shaft is cooled and contracted so that the outer diameter dimension of the support shaft is smaller than the inner diameter dimension of the lubricant distribution member, the support shaft is fitted into the lubricant distribution member, and then returned to room temperature, thereby fixing the lubricant distribution member to the support shaft.

また、本発明に前記構成において、前記支持軸が当該支持軸の先端側ほど大径となるようなテーパ構造を有していてもよい。 In addition, in the above-mentioned configuration of the present invention, the support shaft may have a tapered structure in which the diameter becomes larger toward the tip side of the support shaft.

ここで、テーパ構造としては、例えば、支持軸の上側（内輪軸受け支持用ニードル軸受け側（パワーローラ側））の外径寸法を支持軸の下側（基端部側）の外径寸法より少々（数μm）大きくし、潤滑油分配部材の上側の締付力を下側より大きくすることで潤滑油分配部材の移動防止（支持軸の軸方向への移動防止）を行えばよい。 Here, the tapered structure can be achieved, for example, by making the outer diameter of the upper side of the support shaft (the inner ring bearing supporting needle bearing side (power roller side)) slightly (a few μm) larger than the outer diameter of the lower side (base end side) of the support shaft, and by making the tightening force of the upper side of the lubricant distribution member greater than that of the lower side, movement of the lubricant distribution member (prevention of axial movement of the support shaft) can be prevented.

また、本発明の前記構成において、前記支持軸の外周部に、前記潤滑油分配部材のパワーローラ側の端面に当接する段付き部が形成されていてもよい。 In addition, in the above-mentioned configuration of the present invention, a stepped portion may be formed on the outer periphery of the support shaft, which abuts against the end face of the lubricant distribution member on the power roller side.

ここで、支持軸の外周部に段付き部を形成する場合、支持軸外径部に潤滑油分配部材が嵌る幅分の径を小さくするように周溝を形成してもよいし、支持軸の上側（内輪軸受け支持用ニードル軸受け側（パワーローラ側））の径を広げように環状のフランジ部を形成してもよい。
また、前記潤滑油分配部材を前記支持軸に焼き嵌め固定するが、温め膨張した潤滑油分配部材の内径寸法は、段付き部の径より大きくなり、支持軸の段付き部より小径側でも締め代は保たれる。そして運転時に高温になり潤滑油分配部材の内径は膨張するが、支持軸も膨張するため段付き部の径よりは大きくならない。したがって潤滑油分配部材が支持軸の所定の位置から移動するのを防止できる。 Here, when forming a stepped portion on the outer periphery of the support shaft, a circumferential groove may be formed to reduce the diameter of the outer diameter portion of the support shaft by the width into which the lubricant distribution member fits, or an annular flange portion may be formed to widen the diameter of the upper side of the support shaft (the needle bearing side for supporting the inner ring bearing (power roller side)).
In addition, the lubricant distribution member is fixed to the support shaft by shrink fitting, and the inner diameter of the lubricant distribution member that expands when heated becomes larger than the diameter of the stepped portion, and the interference is maintained even on the smaller diameter side of the stepped portion of the support shaft. During operation, the lubricant distribution member becomes hot and expands in inner diameter, but the support shaft also expands, so the inner diameter does not become larger than the diameter of the stepped portion. Therefore, the lubricant distribution member can be prevented from moving from its designated position on the support shaft.

また、本発明の前記構成において、前記移動防止構造は、前記潤滑油分配部材を前記支持軸に加締め固定した構造であってもよい。 In addition, in the above-mentioned configuration of the present invention, the movement prevention structure may be a structure in which the lubricant distribution member is crimped and fixed to the support shaft.

ここで、潤滑油分配部材の上側（内輪軸受け支持用ニードル軸受け側（パワーローラ側））に加締め部（段差）を設けるのが好ましい。これは、潤滑油分配部材を外径部で加締めると潤滑油分配部材が薄肉リング状であるため、変形するおそれがあるからである。
また、潤滑油分配部材の内径寸法は、支持軸に段付き部を形成した場合に、当該段付き部の外径寸法よりわずかに大きくすることで、常温においても潤滑油分配部材を支持軸に嵌めることができる。また、潤滑油分配部材の内径寸法を支持軸の外径より小さくし、焼き嵌めにて潤滑油分配部材を支持軸に固定することもできる。
その後、潤滑油分配部材の上側に設けた加締め部を加締めて固定する。
支持軸に段付き部を形成した場合、当該段付き部に加締め部がかみ合い、潤滑油分配部材が支持軸の所定の位置から移動するのを防止できる。 Here, it is preferable to provide a crimped portion (step) on the upper side (the inner ring bearing support needle bearing side (power roller side)) of the lubricant distribution member. This is because if the lubricant distribution member is crimped at the outer diameter portion, it may be deformed because the lubricant distribution member is a thin ring-shaped member.
In addition, when a stepped portion is formed on the support shaft, the inner diameter of the lubricant distribution member can be made slightly larger than the outer diameter of the stepped portion so that the lubricant distribution member can be fitted to the support shaft even at room temperature. Also, the inner diameter of the lubricant distribution member can be made smaller than the outer diameter of the support shaft so that the lubricant distribution member can be fixed to the support shaft by shrink fitting.
Thereafter, the crimping portion provided on the upper side of the lubricant distribution member is crimped and fixed.
When a stepped portion is formed on the support shaft, the crimped portion engages with the stepped portion, preventing the lubricant distribution member from moving from a predetermined position on the support shaft.

また、本発明の前記構成において、前記移動防止構造は、前記支持軸に段差溝が周方向に沿って形成され、前記段差溝に前記潤滑油分配部材を加締め固定した構造であってもよい。 In the above-mentioned configuration of the present invention, the movement prevention structure may be a structure in which a stepped groove is formed in the support shaft along the circumferential direction, and the lubricant distribution member is fixed to the stepped groove by crimping.

ここで、段差溝の溝幅を潤滑油分配部材の幅（潤滑油分配部材の軸方向の幅）とほぼ等しく設定するのが好ましい。このようにすると、段差溝に潤滑油分配部材がかみ合って加締め固定される。 Here, it is preferable to set the groove width of the stepped groove to be approximately equal to the width of the lubricant distribution member (the axial width of the lubricant distribution member). In this way, the lubricant distribution member engages with the stepped groove and is fixed by crimping.

また、本発明の前記構成において、前記加締め固定した構造では、前記潤滑油分配部材が前記支持軸に焼き嵌め固定されるか、または前記支持軸が前記潤滑油分配部材に冷やし嵌め固定されていてもよい。 In addition, in the above-mentioned configuration of the present invention, in the crimped structure, the lubricant distribution member may be shrink-fitted to the support shaft, or the support shaft may be cold-fitted to the lubricant distribution member.

また、本発明の前記構成において、前記移動防止構造は、前記支持軸の外周部に形成された凹部に前記外周部から突出するように嵌め込まれた突出部材が、前記潤滑油分配部材のパワーローラ側の端面に当接した構造であってもよい。 In the above-mentioned configuration of the present invention, the movement prevention structure may be a structure in which a protruding member is fitted into a recess formed on the outer periphery of the support shaft so as to protrude from the outer periphery and abuts against the end face of the lubricant distribution member on the power roller side.

ここで、凹部は支持軸の外周部に周方向に所定間隔で形成された孔や溝であってもよいし、周方向に沿って連続的に形成された周溝であってもよい。 Here, the recesses may be holes or grooves formed at a predetermined interval in the circumferential direction on the outer periphery of the support shaft, or may be circumferential grooves formed continuously along the circumferential direction.

また、本発明の前記構成において、前記凹部が前記支持軸の外周方向に沿って連続的に形成された周溝であり、前記突出部材が前記周溝に嵌め込まれた止め輪であってもよい。 In the above configuration of the present invention, the recess may be a circumferential groove formed continuously along the outer periphery of the support shaft, and the protruding member may be a retaining ring fitted into the circumferential groove.

また、本発明の前記構成において、前記潤滑油分配部材が前記支持軸に焼き嵌め固定されるか、または前記支持軸が前記潤滑油分配部材に冷やし嵌め固定されていてもよい。 In addition, in the above-described configuration of the present invention, the lubricant distribution member may be fixed to the support shaft by shrink fitting, or the support shaft may be fixed to the lubricant distribution member by cold fitting.

また、本発明の前記構成において、前記潤滑油分配部材は、前記支持軸と熱膨張係数が等しいか、近い値の金属で形成されていてもよい。
ここで、熱膨張係数が近い値とは、支持軸と潤滑油分配部材を形成する金属の熱膨張係数の差が２５（１０^－６／Ｋ（ｍ））以内であると規定する。
この場合、支持軸を形成する金属の方が潤滑油分配部材を形成する金属より熱膨張係数が大きいのが好ましい。 In the above-described configuration of the present invention, the lubricant distribution member may be formed of a metal having a thermal expansion coefficient equal to or close to that of the support shaft.
Here, the thermal expansion coefficients being close to each other are defined as the difference in the thermal expansion coefficients of the metals forming the support shaft and the lubricant distribution member being within 25 (10 ⁻⁶ /K(m)).
In this case, it is preferable that the metal forming the support shaft has a greater thermal expansion coefficient than the metal forming the lubricant distribution member.

このような構成によれば、潤滑油分配部材が支持軸と熱膨張係数が等しいか、近い値の金属製であるので、運転時に高温となって潤滑油分配部材の内径が膨張しても、支持軸も同様に膨張するため両者の嵌合態様（固定状態）は維持される。このため、より確実に潤滑油分配部材が支持軸の所定の位置から移動するのを防止できる。 With this configuration, the lubricant distribution member is made of a metal with a thermal expansion coefficient equal to or close to that of the support shaft. Therefore, even if the inner diameter of the lubricant distribution member expands due to high temperatures during operation, the support shaft also expands in the same way, so the fitting state (fixed state) of the two is maintained. This makes it possible to more reliably prevent the lubricant distribution member from moving from its designated position on the support shaft.

本発明によれば、パワーローラを回転可能に支持する支持軸に潤滑油分配部材を強固に固定でき、運転時に潤滑油分配部材の支持軸に対する所定の位置からの移動を防止できる。 According to the present invention, the lubricant distribution member can be firmly fixed to the support shaft that rotatably supports the power roller, and the lubricant distribution member can be prevented from moving from a predetermined position relative to the support shaft during operation.

本発明の第１の実施形態を示すもので、パワーローラを備えたトラニオンを示す断面図である。FIG. 1 is a cross-sectional view showing a trunnion equipped with a power roller, according to a first embodiment of the present invention. 同、パワーローラを備えたパワーローラユニットを示す断面図である。FIG. 2 is a cross-sectional view showing a power roller unit including a power roller according to the first embodiment. 同、（ａ）は潤滑油分配部材の正面図、（ｂ）は潤滑油分配部材平面図である。1A is a front view of a lubricant distribution member, and FIG. 1B is a plan view of the lubricant distribution member. 同、パワーローラの支持軸を示す断面図である。FIG. 4 is a cross-sectional view showing the support shaft of the power roller according to the first embodiment. 本発明の第２の実施形態を示すもので、パワーローラの支持軸を示す断面図である。FIG. 11 is a cross-sectional view showing a support shaft of a power roller according to a second embodiment of the present invention. 本発明の第３の実施形態を示すもので、パワーローラの支持軸を示す断面図である。FIG. 10 is a cross-sectional view showing a support shaft of a power roller according to a third embodiment of the present invention. 本発明の第４の実施形態を示すもので、パワーローラの支持軸を示す断面図である。FIG. 10 is a cross-sectional view showing a support shaft of a power roller according to a fourth embodiment of the present invention. 本発明の第５の実施形態を示すもので、パワーローラの支持軸を示す断面図である。FIG. 13 is a cross-sectional view showing a support shaft of a power roller according to a fifth embodiment of the present invention. 従来のトロイダル型無段変速機の一例を示す断面図である。FIG. 1 is a cross-sectional view showing an example of a conventional toroidal type continuously variable transmission. 図９におけるＡ－Ａ線に沿う断面図である。10 is a cross-sectional view taken along line AA in FIG. 9.

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、パワーローラ１１のスラスト軸受２４に適切な量を適切な割合で振り分けて潤滑油を供給する潤滑油分配部材の材質および移動防止構造にあり、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。そのため、以下においては、本発明の特徴部分について説明し、従来と同一構成には同一符号を付してその説明を省略することもある。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
The present invention is characterized by the material and movement prevention structure of the lubricant distribution member that distributes an appropriate amount of lubricant at an appropriate ratio to the thrust bearing 24 of the power roller 11, and the other configurations and functions are the same as those of the conventional configurations and functions described above. Therefore, in the following, the characteristic parts of the present invention will be described, and the same reference numerals will be used to designate the same configurations as the conventional configurations, and the description thereof may be omitted.

（第１の実施形態）
図１～図３は、第１の実施形態を示すもので、図１はパワーローラ１１を備えたトラニオン１５を示す断面図、図２はパワーローラ１１を備えたパワーローラユニットＰＵを示す断面図、図３は潤滑油分配部材を示す図、図４は外輪１１ｂを含む変位軸２３の断面図である。
図１に示すように、トラニオン１５は、上下に長尺な支持板部１６と、この支持板部１６の両端部（上下端部）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。この折れ曲がり壁部２０，２０によって、トラニオン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が形成されている。また、各折れ曲がり壁部２０，２０の外側面には、枢軸１４，１４が互いに同心的に設けられている。 (First embodiment)
Figures 1 to 3 show a first embodiment, in which Figure 1 is a cross-sectional view showing a trunnion 15 equipped with a power roller 11, Figure 2 is a cross-sectional view showing a power roller unit PU equipped with a power roller 11, Figure 3 is a diagram showing a lubricant distribution member, and Figure 4 is a cross-sectional view of a displacement shaft 23 including an outer ring 11b.
1, the trunnion 15 has a vertically long support plate portion 16 and a pair of bent wall portions 20, 20 formed at both ends (upper and lower ends) of the support plate portion 16 in a state of being bent toward the inner surface side of the support plate portion 16. The bent wall portions 20, 20 form a concave pocket portion P in the trunnion 15 for accommodating the power roller 11. In addition, pivot shafts 14, 14 are provided concentrically with each other on the outer surface of each of the bent wall portions 20, 20.

図１および図２に示すように、パワーローラ１１は、スラスト軸受２４の内輪１１ｃによって構成されている。内輪１１ｃ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、内輪１１ｃ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（スラスト軸受）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、パワーローラ１１（内輪１１ｃ）に加わるスラスト方向の荷重を支承しつつ、パワーローラ１１（内輪１１ｃ）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は複数の玉（以下、転動体という）２６と、これら転動体２６を転動自在に保持する円環状の保持器２７と、パワーローラ１１である内輪１１ｃと、円環状の外輪１１ｂとから構成されている。また、スラスト玉軸受２４の内輪軌道は内輪１１ｃの外側面（大端面）に、外輪軌道は外輪１１ｂの内側面にそれぞれ形成されている。 1 and 2, the power roller 11 is configured by an inner ring 11c of a thrust bearing 24. Between the outer surface of the inner ring 11c and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (thrust bearing) 24, which is a thrust rolling bearing, and a thrust needle bearing 25 are provided in this order from the outer surface side of the inner ring 11c.
Of these, the thrust ball bearing 24 supports the thrust load applied to the power roller 11 (inner ring 11c) while allowing the power roller 11 (inner ring 11c) to rotate. Such a thrust ball bearing 24 is composed of a plurality of balls (hereinafter referred to as rolling elements) 26, an annular cage 27 that holds the rolling elements 26 so that they can roll freely, the inner ring 11c which is the power roller 11, and an annular outer ring 11b. The inner ring raceway of the thrust ball bearing 24 is formed on the outer surface (large end surface) of the inner ring 11c, and the outer ring raceway is formed on the inner surface of the outer ring 11b.

また、支持板部１６の中央部には円孔が形成され、この円孔には変位軸２３の基端部２３ａが軸回りに回転可能に挿入されている。この変位軸２３の先端部は支持軸２３ｂとなっており、この支持軸２３ｂには、パワーローラ１１が回転可能支持されている。すなわち、パワーローラ１１には孔１１ｄが形成され、この孔１１ｄにラジアルニードル軸受２３ｇが挿入され、このラジアルニードル軸受２３ｇに支持軸２３ｂが回転可能に支持されている。 A circular hole is formed in the center of the support plate portion 16, and the base end portion 23a of the displacement shaft 23 is inserted into this hole so as to be rotatable around its axis. The tip portion of this displacement shaft 23 is the support shaft 23b, and the power roller 11 is rotatably supported by this support shaft 23b. That is, a hole 11d is formed in the power roller 11, a radial needle bearing 23g is inserted into this hole 11d, and the support shaft 23b is rotatably supported by this radial needle bearing 23g.

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１１ｂの外側面との間に挟持されており、トラニオン１５の支持板部１６の内側面に添って配置された平板状のレース２５ａと、ポケット穴を周方向に所定間隔をあけて形成した円盤形状の保持器２５ｂと、ポケット穴に収納されている複数のニードル２５ｃとを備えている。 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 11b, and is equipped with a flat race 25a arranged along the inner surface of the support plate portion 16 of the trunnion 15, a disk-shaped retainer 25b with pocket holes formed at predetermined intervals in the circumferential direction, and multiple needles 25c housed in the pocket holes.

また、支持軸２３ｂには油路７４が設けられている。この油路７４は支持軸２３ｂの内部にその軸方向に沿って延びて設けられており、この油路７４には、支持軸２３ｂの軸方向と直交する方向に延び、かつ周方向に所定間隔で設けられた複数の油路７５の基端部が接続されている。油路７５の先端部は支持軸２３ｂの外周面に開口した油孔７５ａとなっており、この油孔７５ａからスラスト軸受２４に向けて潤滑油を吐出して送るようになっている。
また、支持軸２３ｂの油路７４には、トラニオン１５の油路７６が油路７７，７８を介して連結され、この油路７６に油路７９が連結されている。また、油路７９には油路８０が連結されている。そして、油路８０に油孔８０ａから潤滑油が供給され、油路７９，７６，７７，７８を介して油路７４に供給される。
なお、支持軸２３ｂの油路７４まで潤滑油を供給する構成は、上記の構成に制限されるものではなく、様々な構成を適用可能である。 Further, an oil passage 74 is provided in the support shaft 23b. This oil passage 74 is provided inside the support shaft 23b and extends along its axial direction, and the base ends of a plurality of oil passages 75 that extend in a direction perpendicular to the axial direction of the support shaft 23b and are provided at predetermined intervals in the circumferential direction are connected to this oil passage 74. The tip ends of the oil passages 75 are oil holes 75a that open into the outer circumferential surface of the support shaft 23b, and lubricating oil is discharged and sent from this oil hole 75a toward the thrust bearing 24.
Furthermore, an oil passage 76 of the trunnion 15 is connected to the oil passage 74 of the support shaft 23b via oil passages 77 and 78, and an oil passage 79 is connected to this oil passage 76. Furthermore, an oil passage 80 is connected to the oil passage 79. Lubricating oil is supplied to the oil passage 80 from an oil hole 80a, and is supplied to the oil passage 74 via the oil passages 79, 76, 77, and 78.
The configuration for supplying lubricating oil to the oil passage 74 of the support shaft 23b is not limited to the above configuration, and various configurations can be applied.

前記支持軸２３ｂとスラスト軸受２４の保持器２７との間には、リング状の潤滑油分配部材１００が支持軸２３ｂに通されて設けられている。この潤滑油分配部材１００は、前記油孔７５ａから供給される潤滑油をスラスト軸受２４の方へ分配して送るためものものであり、複数の分配路１００ａを有している。これら分配路１００ａは潤滑油分配部材１００の軸に対して傾斜している。潤滑油分配部材１００の内径側には、凹所１００ｆが周方向に沿って形成され、この凹所１００ｆの底面に分配路１００ａの基端部が開口している。 A ring-shaped lubricant distribution member 100 is provided between the support shaft 23b and the retainer 27 of the thrust bearing 24, passing through the support shaft 23b. This lubricant distribution member 100 distributes and sends the lubricant supplied from the oil hole 75a to the thrust bearing 24, and has multiple distribution paths 100a. These distribution paths 100a are inclined with respect to the axis of the lubricant distribution member 100. A recess 100f is formed along the circumferential direction on the inner diameter side of the lubricant distribution member 100, and the base end of the distribution path 100a opens to the bottom surface of this recess 100f.

潤滑油分配部材１００は、図３に示すように、円形リング状に形成されており、外周面は、潤滑油分配部材１００の軸方向に対して傾斜する円錐台状の２つの傾斜面１００ｂ，１００ｃと、当該傾斜面１００ｂ，１００ｃを繋ぎ、かつ潤滑油分配部材１００の軸方向と平行な円筒状の平行面１００ｄとから構成されている。傾斜面１００ｂは潤滑油分配部材１００の上面側に形成され、傾斜面１００ｃは潤滑油分配部材１００の下面側に形成されている。
複数の分配路１００ａの先端部は傾斜面１００ｂ，１００ｃに開口しており、傾斜面１００ｂに開口する分配路１００ａからスラスト軸受２４の内輪１１ｃ（パワーローラ１１）側に潤滑油が吐出され、傾斜面１００ｃに開口する分配路１００ａから外輪１１ｂ側に潤滑油が吐出される。
また、潤滑油分配部材１００は「鉄鋼（鋼、ステンレスなど）、非鉄金属（アルミ、銅、チタンなど）」等の金属で形成されており、このような金属製の潤滑油分配部材１００は、移動防止構造によって支持軸２３ｂの所定の位置からの移動が防止されている。
ここで「所定の位置」とは、潤滑油分配部材１００が支持軸２３ｂに設計とおりに固定される部位のことであり、例えば図４に示すように、支持軸２３ｂの後述する大径軸部２３ｄの部位である。
また、潤滑油分配部材１００は、支持軸２３ｂと熱膨張係数（又は線熱膨張係数）が等しいか、近い値の金属で形成されており、例えば潤滑油分配部材１００が炭素鋼である場合、支持軸２３ｂも炭素鋼とするのが好ましい。また、潤滑油分配部材１００と支持軸２３ｂとを異なる金属で形成してもよいが、熱膨張係数は等しいか近い値（例えば熱膨張係数の差が２５（１０^－６／Ｋ（ｍ））以内）の方が好ましい。この場合、支持軸２３ｂを形成する金属の方が潤滑油分配部材１００を形成する金属より熱膨張係係数が大きいのが好ましい。
なお、後述する第２～５の実施形態でも、潤滑油分配部材１００は、支持軸２３ｂと熱膨張係数（又は線熱膨張係数）が等しいか、近い値の金属で形成されている。
また、支持軸２３ｂは変位軸２３の先端部を構成しているが、当該支持軸２３ｂは外輪１１ｂおよび変位軸２３の基端部２３ａと一体的に形成されているので、外輪１１ｂおよび基端部２３ａも支持部２３ｂと同じ金属で形成されている。 3, the lubricant distribution member 100 is formed in a circular ring shape, and the outer circumferential surface is composed of two truncated cone-shaped inclined surfaces 100b, 100c inclined with respect to the axial direction of the lubricant distribution member 100, and a cylindrical parallel surface 100d connecting the inclined surfaces 100b, 100c and parallel to the axial direction of the lubricant distribution member 100. The inclined surface 100b is formed on the upper surface side of the lubricant distribution member 100, and the inclined surface 100c is formed on the lower surface side of the lubricant distribution member 100.
The tips of the multiple distribution passages 100a open to the inclined surfaces 100b, 100c, and lubricating oil is discharged from the distribution passage 100a opening to the inclined surface 100b to the inner ring 11c (power roller 11) side of the thrust bearing 24, and lubricating oil is discharged from the distribution passage 100a opening to the inclined surface 100c to the outer ring 11b side.
In addition, the lubricant distribution member 100 is formed from metals such as "steel (steel, stainless steel, etc.) and non-ferrous metals (aluminum, copper, titanium, etc.)", and such metal lubricant distribution members 100 are prevented from moving from a predetermined position on the support shaft 23b by an anti-movement structure.
Here, the "predetermined position" refers to the portion where the lubricant distribution member 100 is fixed to the support shaft 23b as designed, for example, the portion of the large diameter shaft portion 23d of the support shaft 23b, which will be described later, as shown in Figure 4.
The lubricant distribution member 100 is formed of a metal having a thermal expansion coefficient (or linear thermal expansion coefficient) equal to or close to that of the support shaft 23b. For example, when the lubricant distribution member 100 is made of carbon steel, it is preferable that the support shaft 23b is also made of carbon steel. The lubricant distribution member 100 and the support shaft 23b may be formed of different metals, but it is preferable that the thermal expansion coefficients are equal to or close to each other (for example, the difference in thermal expansion coefficient is within 25 (10 ^-6 /K (m))). In this case, it is preferable that the thermal expansion coefficient of the metal forming the support shaft 23b is larger than that of the metal forming the lubricant distribution member 100.
In the second to fifth embodiments described later, the lubricant distribution member 100 is also made of a metal having a thermal expansion coefficient (or linear thermal expansion coefficient) equal to or close to that of the support shaft 23b.
In addition, the support shaft 23b constitutes the tip portion of the displacement shaft 23, but since the support shaft 23b is formed integrally with the outer ring 11b and the base end portion 23a of the displacement shaft 23, the outer ring 11b and the base end portion 23a are also formed from the same metal as the support portion 23b.

第１の実施形態の移動防止構造は、図４に示すように、潤滑油分配部材１００を支持軸２３ｂに焼き嵌め固定した構造（焼き嵌め固定構造）、または支持軸２３ｂを潤滑油分配部材１００に冷やし嵌め固定した構造（冷やし嵌め固定構造）である。支持軸２３ｂは、外輪１１ｂに一体的に形成された大径軸部２３ｄと、この大径軸部２３ｄより小径でかつ大径軸部２３ｄと同軸に一体形成された小径軸部２３ｅとから構成され、小径軸部２３ｅによってパワーローラ１１（内輪１１ｃ）がラジアルニードル軸受２３ｇを介して回転可能に支持されている（図２参照）。 As shown in FIG. 4, the movement prevention structure of the first embodiment is a structure in which the lubricant distribution member 100 is shrink-fitted to the support shaft 23b (shrink-fitted structure), or a structure in which the support shaft 23b is cold-fitted to the lubricant distribution member 100 (cold-fitted structure). The support shaft 23b is composed of a large-diameter shaft portion 23d formed integrally with the outer ring 11b, and a small-diameter shaft portion 23e that is smaller in diameter than the large-diameter shaft portion 23d and is formed integrally and coaxially with the large-diameter shaft portion 23d, and the power roller 11 (inner ring 11c) is rotatably supported by the small-diameter shaft portion 23e via a radial needle bearing 23g (see FIG. 2).

また、支持軸２３ｂの大径軸部２３ｄに潤滑油分配部材１００が焼き嵌め固定されている。この焼き嵌め固定した構造では、焼き嵌めする前（常温時）の潤滑油分配部材１００の内径寸法を、支持軸２３ｂの大径軸部２３ｄの外径仕上げ加工寸法に対し小さい値とし、そして、潤滑油分配部材１００を温め内径寸法が大径軸部２３ｄの仕上げ加工寸法より大きくなるよう膨張させて、大径軸部２３ｄへ嵌めこんだ後、冷却することによって、潤滑油分配部材１００を大径軸部２３ｄに固定する。
また、大径軸部２３ｄの外輪１１ｂの上面（支持軸２３ｂが設けられる上面）１１ｅからの高さ寸法ｈ１は、潤滑油分配部材１００の軸方向の高さ寸法ｈ２より長くなっており、潤滑油分配部材１００の下端面が上面１１ｅに当接されている。したがって、潤滑油分配部材１００の上端面は大径軸部２３ｄの上面より低くなるので、潤滑油分配部材１００の内径面全体が大径軸部２３ｄの外径面に焼き嵌め固定されている。 The lubricant distribution member 100 is shrink-fitted to the large-diameter shaft portion 23d of the support shaft 23b. In this shrink-fitted structure, the inner diameter of the lubricant distribution member 100 before shrink-fitting (at room temperature) is set to a value smaller than the outer diameter finish dimension of the large-diameter shaft portion 23d of the support shaft 23b, and the lubricant distribution member 100 is heated to expand so that the inner diameter dimension becomes larger than the finish dimension of the large-diameter shaft portion 23d, and then the lubricant distribution member 100 is fitted to the large-diameter shaft portion 23d, and then cooled to fix the lubricant distribution member 100 to the large-diameter shaft portion 23d.
In addition, the height h1 of the large diameter shaft portion 23d from the upper surface 11e of the outer ring 11b (the upper surface on which the support shaft 23b is provided) is longer than the axial height h2 of the lubricant distribution member 100, and the lower end surface of the lubricant distribution member 100 abuts against the upper surface 11e. Therefore, the upper end surface of the lubricant distribution member 100 is lower than the upper surface of the large diameter shaft portion 23d, and the entire inner diameter surface of the lubricant distribution member 100 is shrink-fitted and fixed to the outer diameter surface of the large diameter shaft portion 23d.

また、冷やし嵌め固定した構造では、冷やし嵌めする前（常温時）の支持軸２３ｂの大径軸部２３ｄの外径仕上げ加工寸法を、潤滑油分配部材１００の内径寸法に対し大きい値とし、そして、大径軸部２３ｄを冷やして、大径軸部２３ｄの外径寸法が潤滑油分配部材１００の内径寸法より小さくなるように収縮させて、当該大径軸部２３ｄを潤滑油分配部材１００に嵌め込んだ後、常温に戻すことによって、潤滑油分配部材１００を大径軸部２３ｄに固定する。
なお、大径軸部２３ｄを冷やす場合、外輪１１ｂを含む変位軸２３の全体を冷やしてもよいし、大径軸部２３ｄを含む支持軸２３ｂを冷やしてもよいし、大径軸部２３ｄだけを冷やしてもよい。 In addition, in the cold-fit fixed structure, the outer diameter finishing dimension of the large diameter shaft portion 23d of the support shaft 23b before cold-fitting (at room temperature) is made larger than the inner diameter dimension of the lubricant distribution member 100, and the large diameter shaft portion 23d is cooled to shrink the outer diameter dimension of the large diameter shaft portion 23d to be smaller than the inner diameter dimension of the lubricant distribution member 100.The large diameter shaft portion 23d is then fitted into the lubricant distribution member 100, and then returned to room temperature, thereby fixing the lubricant distribution member 100 to the large diameter shaft portion 23d.
When cooling the large diameter shaft portion 23d, the entire displacement shaft 23 including the outer ring 11b may be cooled, the support shaft 23b including the large diameter shaft portion 23d may be cooled, or only the large diameter shaft portion 23d may be cooled.

第１の実施形態によれば、支持軸２３ｂと潤滑油分配部材１００との双方が金属製であり、支持軸２３ｂの大径軸部２３ｄからの潤滑油分配部材１００の移動を防止する移動防止構造（焼き嵌め固定構造または冷やし嵌め固定構造）を有するので、支持軸２３ｂに潤滑油分配部材１００を強固に固定でき、高温高回転および高い振動が発生する運転時に潤滑油分配部材１００が支持軸２３の所定の位置（大径軸部２３ｄ）から移動することがない。
また、潤滑油分配部材１００が支持軸２３ｂと熱膨張係数が等しいか、近い値の金属で形成されているので、運転時に高温となって潤滑油分配部材１００の内径が膨張しても、支持軸２３ｂも同様に膨張するため両者の嵌合態様（固定状態）は維持される。このため、より確実に潤滑油分配部材２００が支持軸２３ｂの所定の位置から移動するのを防止できる。 According to the first embodiment, both the support shaft 23b and the lubricant distribution member 100 are made of metal and have a movement prevention structure (shrink-fit fixing structure or cold-fit fixing structure) that prevents the lubricant distribution member 100 from moving from the large diameter shaft portion 23d of the support shaft 23b. Therefore, the lubricant distribution member 100 can be firmly fixed to the support shaft 23b, and the lubricant distribution member 100 will not move from its designated position (large diameter shaft portion 23d) on the support shaft 23 during operation at high temperatures, high rotation speeds, and high vibrations.
In addition, since the lubricant distribution member 100 is made of a metal with a thermal expansion coefficient equal to or close to that of the support shaft 23b, even if the inner diameter of the lubricant distribution member 100 expands due to high temperatures during operation, the support shaft 23b also expands in the same manner, so that the fitting state (fixed state) of the two is maintained. Therefore, it is possible to more reliably prevent the lubricant distribution member 200 from moving from the specified position on the support shaft 23b.

（第２の実施形態）
第２の実施形態の移動防止構造は、図５に示すように、前記支持軸２３ｂの大径軸部２３ｄが、支持軸２３ｂの先端側ほど大径となるようなテーパ構造を有している。なお、第２の実施形態から第５の実施形態において、第１の実施形態と同一構成には同一符号を付してその説明を省略する。
テーパ構造としては、例えば、支持軸２３ｂの大径軸部２３ｄの上側（小径軸部２３ｅ側）の外径寸法ｄ１を大径軸部２３ｄ支持軸の下側（基端部側）の外径寸法ｄ２より少々（数μm）大きくするとともに、大径軸部２３ｄの外周面を軸方向と交差するテーパ面に形成する。このように、大径軸部２３ｄの外周面をテーパ面とすることによって、潤滑油分配部材１００の上側の締付力を下側より大きくすることで、潤滑油分配部材１００の移動を防止する移動防止構造としている。
なお、第２の実施形態の移動防止構造においても、第１の実施形態と同様に、焼き嵌め固定構造または冷やし嵌め固定構造を有している。 Second Embodiment
5, the movement prevention structure of the second embodiment has a tapered structure in which the large diameter shaft portion 23d of the support shaft 23b has a larger diameter toward the tip side of the support shaft 23b. In the second to fifth embodiments, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted.
As the tapered structure, for example, the outer diameter dimension d1 of the upper side (small diameter shaft portion 23e side) of the large diameter shaft portion 23d of the support shaft 23b is made slightly (several μm) larger than the outer diameter dimension d2 of the lower side (base end side) of the large diameter shaft portion 23d support shaft, and the outer peripheral surface of the large diameter shaft portion 23d is formed into a tapered surface that intersects with the axial direction. In this way, by making the outer peripheral surface of the large diameter shaft portion 23d a tapered surface, the tightening force of the upper side of the lubricant distribution member 100 is made larger than that of the lower side, thereby forming a movement prevention structure that prevents the lubricant distribution member 100 from moving.
The movement prevention structure of the second embodiment also has a shrink-fit fixing structure or a cold-fit fixing structure, similar to the first embodiment.

第２の実施形態によれば、焼き嵌め固定構造または冷やし嵌め固定構造に加えて、潤滑油分配部材１００の上側の締付力が下側より大きくなるので、第１の実施形態よりも潤滑油分配部材１００の固定強度を高めることができる。 According to the second embodiment, in addition to the shrink-fit or cold-fit fixing structure, the clamping force on the upper side of the lubricant distribution member 100 is greater than that on the lower side, so that the fixing strength of the lubricant distribution member 100 can be increased more than in the first embodiment.

（第３の実施形態）
第３の実施形態の移動防止構造では、図６に示すように、前記支持軸２３ｂの大径軸部２３ｄの外周部に、潤滑油分配部材１００のパワーローラ側の端面に当接する段付き部１１０が形成されている。
大径軸部２３ｄの外周部に段付き部１１０を形成する場合、大径軸部２３ｄの外径部に潤滑油分配部材が嵌る幅分の径を小さくするように周溝１１１を形成してもよいし、大径軸部２３ｄの上側（小径軸部２３ｅ側）の径を広げるように環状のフランジ部１１２を形成してもよい。周溝１１１を形成する場合、図４に示す第１の実施形態の大径軸部２３ｄの外径寸法より、周溝１１１が形成された部分の外径寸法が小さいので、その分、潤滑油分配部材１００の内径寸法を小さくする。また、フランジ部１１２を形成する場合、潤滑油分配部材１００の内径寸法を若干大きくする。 Third Embodiment
In the third embodiment of the movement prevention structure, as shown in Figure 6, a stepped portion 110 that abuts on the end face of the lubricant distribution member 100 on the power roller side is formed on the outer periphery of the large diameter shaft portion 23d of the support shaft 23b.
When forming the stepped portion 110 on the outer periphery of the large diameter shaft portion 23d, a circumferential groove 111 may be formed to reduce the diameter of the outer diameter of the large diameter shaft portion 23d by the width where the lubricant distribution member fits, or an annular flange portion 112 may be formed to widen the diameter of the upper side (small diameter shaft portion 23e side) of the large diameter shaft portion 23d. When forming the circumferential groove 111, the outer diameter of the portion where the circumferential groove 111 is formed is smaller than the outer diameter of the large diameter shaft portion 23d of the first embodiment shown in Figure 4, so the inner diameter of the lubricant distribution member 100 is reduced accordingly. Also, when forming the flange portion 112, the inner diameter of the lubricant distribution member 100 is slightly increased.

また、第１の実施形態と同様に、潤滑油分配部材１００を支持軸２３ｂの大径軸部２３ｄに焼き嵌め固定するが、温め膨張した潤滑油分配部材１００の内径寸法は、段付き部１１０の径より大きくなり、大径軸部２３ｄの段付き部１１０より小径側でも締め代は保たれる。
そして運転時に高温になり潤滑油分配部材１００の内径は膨張するが、支持軸２３ｂの大径軸部２３ｄも同様に膨張するため両者の嵌合態様（固定状態）は維持され、また潤滑油分配部材１００の内径は段付き部１１０の径よりは大きくならない。したがって潤滑油分配部材１００が支持軸２３ｂの所定の位置（大径軸部２３ｄ）から移動するのを防止防止できる。
つまり、潤滑油分配部材１００の焼き嵌め時は、潤滑油分配部材１００の内径寸法が段付き部１１０の外径寸法より大きく、冷却時は潤滑油分配部材１００の内径寸法が段付き部１１０の外径寸法より小さくなるので、潤滑油分配部材１００が支持軸２３ｂの所定の位置（大径軸部２３ｄ）から移動するのを防止でき、さらに、運転時には潤滑油分配部材１００の内径は膨張するが、支持軸２３ｂの大径軸部２３ｄも膨張するため潤滑油分配部材１００の内径は、段付き部１１０の径よりは大きくならない。したがって潤滑油分配部材１００が支持軸２３ｂの大径軸部２３ｄから移動するのを防止できる。 As in the first embodiment, the lubricant distribution member 100 is shrink-fitted and fixed to the large diameter shaft portion 23d of the support shaft 23b, but the inner diameter dimension of the lubricant distribution member 100 which has been heated and expanded becomes larger than the diameter of the stepped portion 110, and the tightening margin is maintained even on the smaller diameter side of the stepped portion 110 of the large diameter shaft portion 23d.
During operation, the lubricant distribution member 100 becomes hot and its inner diameter expands, but the large diameter shaft portion 23d of the support shaft 23b also expands, so the fitted state (fixed state) of the two is maintained, and the inner diameter of the lubricant distribution member 100 does not become larger than the diameter of the stepped portion 110. Therefore, the lubricant distribution member 100 can be prevented from moving from the specified position (large diameter shaft portion 23d) of the support shaft 23b.
That is, when the lubricant distribution member 100 is shrink-fitted, the inner diameter of the lubricant distribution member 100 is larger than the outer diameter of the stepped portion 110, and when cooled, the inner diameter of the lubricant distribution member 100 is smaller than the outer diameter of the stepped portion 110, so that the lubricant distribution member 100 can be prevented from moving from the predetermined position (large diameter shaft portion 23d) of the support shaft 23b, and further, although the inner diameter of the lubricant distribution member 100 expands during operation, the large diameter shaft portion 23d of the support shaft 23b also expands, so that the inner diameter of the lubricant distribution member 100 does not become larger than the diameter of the stepped portion 110. Therefore, the lubricant distribution member 100 can be prevented from moving from the large diameter shaft portion 23d of the support shaft 23b.

（第４の実施形態）
第４の実施形態の移動防止構造は、図７に示すように、潤滑油分配部材１００を支持軸２３ｂの大径軸部２３ｄに加締め固定した構造となっている。
本実施形態では、潤滑油分配部材１００の上側（小径軸部２３ｅ側）に加締め部（段差）１００ｋが設けられている。この加締め部１００ｋは潤滑油分配部材１００の上側部分を断面Ｌ形に切り欠くことで段差を形成したものであり、これによって加締め部１００ｋの外径寸法は、当該加締め部１００ｋより下側（外輪１１ｂ側）の外径寸法より小さくなっている。したがって、加締め部１００ｋは、径方向の肉厚が小さくなり、加締め易くなっている。これに対し、加締め部１００ｋを設けずに、潤滑油分配部材１００を外径部で加締めると潤滑油分配部材１００が薄肉リング状であるため、変形するおそれや、この変形によって分配路１００ａが変形したり潰れたりするおそれがあるが、加締め部１１０ｋを設けることによって、このようなおそれがない。 (Fourth embodiment)
As shown in FIG. 7, the movement prevention structure of the fourth embodiment has a structure in which a lubricant distribution member 100 is fixed to the large diameter shaft portion 23d of the support shaft 23b by crimping.
In this embodiment, a crimped portion (step) 100k is provided on the upper side (small diameter shaft portion 23e side) of the lubricant distribution member 100. This crimped portion 100k is formed by cutting out the upper part of the lubricant distribution member 100 in an L-shaped cross section to form a step, so that the outer diameter dimension of the crimped portion 100k is smaller than the outer diameter dimension below the crimped portion 100k (outer ring 11b side). Therefore, the crimped portion 100k has a small radial thickness and is easy to crimp. On the other hand, if the lubricant distribution member 100 is crimped at the outer diameter portion without providing the crimped portion 100k, the lubricant distribution member 100 is a thin ring-shaped member, so there is a risk of deformation, and the distribution passage 100a may be deformed or crushed due to this deformation, but by providing the crimped portion 110k, such a risk does not occur.

また、潤滑油分配部材１００の内径寸法は、支持軸２３ｂの大径軸部２３ｄに段付き部１１０を形成した場合に、当該段付き部１１０の外径寸法よりわずかに大きくすることで、常温においても潤滑油分配部材１００を大径軸部２３ｄに嵌めることができる。
また、大径軸部２３ｄに段付き部１１０を形成することによって、当該段付き部１１０の下面と外輪１１ｂの上面との間に段差溝１１５が周方向に沿って形成され、当該段差溝１１５に潤滑油分配部材１００を加締め固定してもよい。この場合、段差溝１１５の上下幅寸法（支持軸２３ｂの軸方向の幅寸法）と潤滑油分配部材１００の軸方向の幅寸法とをほぼ等しくすることによって、常温においても潤滑油分配部材１００を段差溝１１５に嵌めることができる。その後、潤滑油分配部材１００を加締めることによって、段差溝１１５に潤滑油分配部材１００がかみ合って強固に加締め固定される。 In addition, when a stepped portion 110 is formed on the large diameter shaft portion 23d of the support shaft 23b, the inner diameter dimension of the lubricant distribution member 100 is made slightly larger than the outer diameter dimension of the stepped portion 110, so that the lubricant distribution member 100 can be fitted into the large diameter shaft portion 23d even at room temperature.
In addition, by forming a stepped portion 110 on the large diameter shaft portion 23d, a stepped groove 115 is formed between the lower surface of the stepped portion 110 and the upper surface of the outer ring 11b along the circumferential direction, and the lubricant distribution member 100 may be crimped and fixed to the stepped groove 115. In this case, by making the vertical width dimension of the stepped groove 115 (the axial width dimension of the support shaft 23b) and the axial width dimension of the lubricant distribution member 100 approximately equal, the lubricant distribution member 100 can be fitted into the stepped groove 115 even at room temperature. Thereafter, by crimping the lubricant distribution member 100, the lubricant distribution member 100 engages with the stepped groove 115 and is firmly crimped and fixed.

また、潤滑油分配部材１００の内径寸法を大径軸部２３ｄの外径より小さくし、焼き嵌めにて潤滑油分配部材１００を大径軸部２３ｄに固定することもできるし、支持軸２３ｂの大径軸部２３ｄの外径仕上げ加工寸法を、潤滑油分配部材１００の内径寸法に対し大きい値とし、冷やし嵌めにて潤滑油分配部材１００を大径軸部２３ｄに固定することもできる。
その後、潤滑油分配部材１００のリング上部に設けた加締め部１００ｋを加締めて大径軸部２３ｄに固定する。
大径軸部２３ｄに段付き部１１０を形成した場合、当該段付き部１１０に加締め部１００ｄがかみ合い、潤滑油分配部材１００が大径軸部２３ｄから抜けるのを防止できる。 In addition, the inner diameter dimension of the lubricant distribution member 100 can be made smaller than the outer diameter of the large diameter shaft portion 23d, and the lubricant distribution member 100 can be fixed to the large diameter shaft portion 23d by shrink fitting, or the outer diameter finishing dimension of the large diameter shaft portion 23d of the support shaft 23b can be made larger than the inner diameter dimension of the lubricant distribution member 100, and the lubricant distribution member 100 can be fixed to the large diameter shaft portion 23d by cold fitting.
Thereafter, the crimping portion 100k provided on the upper portion of the ring of the lubricant distribution member 100 is crimped to fix it to the large diameter shaft portion 23d.
When the stepped portion 110 is formed on the large diameter shaft portion 23d, the crimped portion 100d engages with the stepped portion 110, thereby preventing the lubricant distribution member 100 from coming off the large diameter shaft portion 23d.

なお、本実施形態では、支持軸２３ｂの大径軸部２３ｄに段付き部１１０を形成したが、段付き部１１０を形成することなく、大径軸部２３ｄに潤滑油分配部材１００を加締め固定してもよい。 In this embodiment, the stepped portion 110 is formed on the large diameter shaft portion 23d of the support shaft 23b, but the lubricant distribution member 100 may be fixed to the large diameter shaft portion 23d by crimping without forming the stepped portion 110.

（第５の実施形態）
第５の実施形態の移動防止構造では、図８に示すように、支持軸２３ｂの大径軸部２３ｄの外周部に形成された凹部１１６に外周部から突出するように嵌め込まれた突出部材１１７が、潤滑油分配部材１００のパワーローラ側の端面に当接した構造となっている。 Fifth Embodiment
In the fifth embodiment of the movement prevention structure, as shown in Figure 8, a protruding member 117 is fitted into a recess 116 formed on the outer periphery of the large diameter shaft portion 23d of the support shaft 23b so as to protrude from the outer periphery, and abuts against the end face of the lubricant distribution member 100 on the power roller side.

ここで、凹部１１６は大径軸部２３ｄの外周部に周方向に所定間隔で形成された孔や溝であってもよいし、周方向に沿って連続的に形成された周溝であってもよいが、本実施形態では、凹部１１６が大径軸部２３ｄの外周方向に沿って連続的に形成された周溝１１６となっており、突出部材１１７が周溝１１６に嵌め込まれた止め輪１１７となっている。
周溝１１６は断面コ字形に形成されており、この周溝１１６の下壁面１１６ａと外輪１１ｂの上面との間の上下方向の寸法は、潤滑油分配部材１００の軸方向の幅寸法とほぼ等しくなっている。したがって、潤滑油分配部材１００を大径軸部２３ｄに嵌め込むとともに、潤滑油分配部材１００の下端面を外輪１１ｂの上面に当接すると、潤滑油分配部材１００の上端面と周溝１１６の下壁面１１６ａとがほぼ面一となる。 Here, the recess 116 may be a hole or groove formed at a predetermined interval in the circumferential direction on the outer periphery of the large diameter shaft portion 23d, or it may be a circumferential groove formed continuously along the circumferential direction; however, in this embodiment, the recess 116 is a circumferential groove 116 formed continuously along the outer periphery of the large diameter shaft portion 23d, and the protruding member 117 is a retaining ring 117 fitted into the circumferential groove 116.
The circumferential groove 116 is formed to have a U-shaped cross section, and the vertical dimension between the lower wall surface 116a of this circumferential groove 116 and the upper surface of the outer ring 11b is approximately equal to the axial width dimension of the lubricant distribution member 100. Therefore, when the lubricant distribution member 100 is fitted onto the large diameter shaft portion 23d and the lower end surface of the lubricant distribution member 100 abuts against the upper surface of the outer ring 11b, the upper end surface of the lubricant distribution member 100 and the lower wall surface 116a of the circumferential groove 116 become approximately flush with each other.

止め輪１１７はスチールやステンレス等の金属によって円形リング状に形成され、その内径側が周溝１１６に嵌め込まれている。止め輪１１７の外径側は大径軸部２３ｄの外周面から径方向に突出しており、この突出した部分が潤滑油分配部材１００の上端面に当接し、これによって、潤滑油分配部材１００の支持軸２３ｂの大径軸部２３ｄの軸方向への移動が防止されている。 The retaining ring 117 is made of a metal such as steel or stainless steel and is formed into a circular ring shape, with its inner diameter side fitted into the circumferential groove 116. The outer diameter side of the retaining ring 117 protrudes radially from the outer circumferential surface of the large diameter shaft portion 23d, and this protruding portion abuts against the upper end surface of the lubricant distribution member 100, thereby preventing axial movement of the large diameter shaft portion 23d of the support shaft 23b of the lubricant distribution member 100.

また、本実施形態において、止め輪１１７を設置する前に、潤滑油分配部材１００を上述したような、焼き嵌めや冷やし嵌めによって、支持軸２３ｂの大径軸部２３ｄに固定してもよく、さらに隙間嵌めによって嵌め込んでもよい。
なお、本実施形態では、凹部としての周溝１１６に、突出部材としてのリング状の止め輪１１７を嵌め込んだが、凹部を大径軸部２３ｄの周方向に所定間隔で形成し、各凹部に棒状や板状の突出部材を嵌め込んでもよい。この場合、凹部からの突出部材の抜け出を防止するために、突出部材を凹部に圧入したり、圧入と接着剤を併用することによって、突出部材を凹部に強固に嵌込み固定する。
さらには、大径軸部２３ｄに凹部に代えて貫通孔を形成し、当該貫通孔にスプリングピンを打ち込むことで、潤滑油分配部材１００の軸部２３ｂの軸方向への移動を防止してもよい。 In addition, in this embodiment, before installing the retaining ring 117, the lubricant distribution member 100 may be fixed to the large diameter shaft portion 23d of the support shaft 23b by shrink fitting or cold fitting as described above, or may be further fitted by a clearance fit.
In this embodiment, the ring-shaped retaining ring 117 serving as the protruding member is fitted into the circumferential groove 116 serving as the recess, but recesses may be formed at predetermined intervals in the circumferential direction of the large diameter shaft portion 23d, and a rod-shaped or plate-shaped protruding member may be fitted into each recess. In this case, in order to prevent the protruding member from slipping out of the recess, the protruding member is firmly fitted and fixed into the recess by press-fitting the protruding member into the recess or by using a combination of press-fitting and adhesive.
Furthermore, a through hole may be formed in the large diameter shaft portion 23d instead of a recess, and a spring pin may be driven into the through hole to prevent the shaft portion 23b of the lubricant oil distribution member 100 from moving in the axial direction.

なお、本実施形態では本発明を、ダブルキャビティ型のハーフトロイダル型無段変速機に適用する場合を例にとって説明したが、これに限ることなく、本発明はダブルキャビティ型のフルトロイダル型無段変速機にも適用でき、さらに、シングルキャビティ型のハーフトロイダル型無段変速機や、シングルキャビティ型のフルトロイダル型無段変速機にも適用できる。 In this embodiment, the present invention has been described by taking as an example a case where it is applied to a double-cavity half-toroidal type continuously variable transmission, but the present invention is not limited to this, and can also be applied to a double-cavity full-toroidal type continuously variable transmission, and further, can also be applied to a single-cavity half-toroidal type continuously variable transmission and a single-cavity full-toroidal type continuously variable transmission.

また、本実施形態では、軸を入力軸１、第１ディスクを入力側ディスク２、第２ディスクを出力側ディスク３とした場合を例にとって説明したが、トロイダル型無段変速機では、入力側ディスクと出力側ディスクの入出力関係を逆にする場合もある。したがって、軸を出力軸、第１ディスクを出力側ディスク３、第２ディスクを入力側ディスク２とした場合にも適用できる。 In addition, in this embodiment, the shaft is the input shaft 1, the first disk is the input side disk 2, and the second disk is the output side disk 3. However, in a toroidal type continuously variable transmission, the input/output relationship between the input side disk and the output side disk may be reversed. Therefore, the present invention can also be applied to a case where the shaft is the output shaft, the first disk is the output side disk 3, and the second disk is the input side disk 2.

１入力軸（軸）
２入力側ディスク（第１ディスク）
３出力側ディスク（第２ディスク）
１１（１１ｃ）パワーローラ（内輪）
１５トラニオン
２３ｂ支持軸
２４スラスト軸受
７５ａ油孔
１００潤滑油分配部材
１００ａ分配路
１１６周溝（凹部）
１１７突出部材（止め輪） 1 Input shaft (shaft)
2 Input disk (first disk)
3 Output disk (second disk)
11 (11c) Power roller (inner ring)
15 Trunnion 23b Support shaft 24 Thrust bearing 75a Oil hole 100 Lubricant oil distribution member 100a Distribution passage 116 Circumferential groove (recess)
117 Protruding member (retaining ring)

Claims

a first disk and a second disk arranged concentrically and rotatably with their respective inner surfaces facing each other;
a power roller sandwiched between the first disc and the second disc;
a trunnion that tilts about a pivot axis that is in a twisted position with respect to central axes of the first disk and the second disk and supports the power roller rotatably about a support shaft;
a thrust bearing that rotatably supports the power roller while receiving a thrust load applied to the power roller;
an oil hole that opens to an outer peripheral surface of the support shaft and supplies lubricating oil toward the thrust bearing;
a ring-shaped lubricant oil distribution member that is passed through the support shaft and disposed between the support shaft and the thrust bearing, and that has a plurality of distribution paths that distribute and send lubricant oil supplied from the oil hole toward the thrust bearing,
Both the support shaft and the lubricant distribution member are made of metal;
The lubricant distribution member is provided with a movement prevention structure for preventing the lubricant distribution member from moving from a predetermined position on the support shaft ,
The movement prevention structure is a structure in which the lubricant distribution member is fixed to the support shaft by shrink fitting, or a structure in which the support shaft is fixed to the lubricant distribution member by cold fitting,
1. A toroidal type continuously variable transmission, wherein the support shaft has a tapered structure in which the diameter of the support shaft increases toward the tip end thereof .

2. The toroidal type continuously variable transmission according to claim 1 , wherein a stepped portion is formed on an outer periphery of the support shaft, the stepped portion being brought into contact with an end face of the lubricant oil distribution member on the power roller side.

The toroidal type continuously variable transmission according to claim 1, characterized in that the movement prevention structure is a structure in which the lubricant distribution member is fixed to the support shaft by crimping.

The toroidal type continuously variable transmission according to claim 1, characterized in that the movement prevention structure is a structure in which a stepped groove is formed in the support shaft along the circumferential direction, and the lubricant distribution member is fixed to the stepped groove by crimping.

The toroidal type continuously variable transmission according to claim 3 or 4, characterized in that in the crimped structure, the lubricant distribution member is shrink-fitted to the support shaft, or the support shaft is cold-fitted to the lubricant distribution member .

The toroidal type continuously variable transmission according to claim 1, characterized in that the movement prevention structure is a structure in which a protruding member that is fitted into a recess formed on the outer periphery of the support shaft so as to protrude from the outer periphery abuts against the end face of the lubricant distribution member on the power roller side.

7. The toroidal type continuously variable transmission according to claim 6 , wherein the recess is a circumferential groove formed continuously along an outer circumferential direction of the support shaft, and the protruding member is a retaining ring fitted into the circumferential groove.

8. The toroidal type continuously variable transmission according to claim 6 or 7 , wherein the lubricant distribution member is fixed to the support shaft by shrink fitting, or the support shaft is fixed to the lubricant distribution member by cold fitting.

9. The toroidal type continuously variable transmission according to claim 1, wherein the lubricant distribution member is formed of a metal having a thermal expansion coefficient equal to or close to that of the support shaft.