JP2007321931A - Toroidal type continuously variable transmission - Google Patents

Toroidal type continuously variable transmission Download PDF

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JP2007321931A
JP2007321931A JP2006155261A JP2006155261A JP2007321931A JP 2007321931 A JP2007321931 A JP 2007321931A JP 2006155261 A JP2006155261 A JP 2006155261A JP 2006155261 A JP2006155261 A JP 2006155261A JP 2007321931 A JP2007321931 A JP 2007321931A
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disk
oil passage
disks
output side
continuously variable
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Japanese (ja)
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Yutaka Ishibashi
豊 石橋
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0487—Friction gearings
    • F16H57/049—Friction gearings of the toroid type

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  • Friction Gearing (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of efficiently cooling disks. <P>SOLUTION: This toroidal type continuously variable transmission comprises two toroidal transmission units 200, 201. Each of the toroidal transmission units 200, 201 comprises an input side disk 2, an output side disk 3, and two power rollers 11, 11 held between them. Back faces 3c, 3c of both output side disks 3, 3 are arranged to face each other with a partition wall 13 fixed to a casing 50 held between. The partition wall 13 has an oil passage 40. The oil passage 40 comprises a base side oil passage 40a connected to an oil passage 50a on the casing 50 side, and tip side oil passages 41, 42 branching in two from the base side oil passage 40a and opening discharge ports toward the respective back faces 3c of the output side disks 3, 3. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

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

例えば自動車用変速機として用いるダブルキャビティ式トロイダル型無段変速機は、図３および図４に示すように構成されている。図３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 an automobile transmission is configured as shown in FIGS. As shown in FIG. 3, an input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is 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（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（中間壁）１３に対しアンギュラ軸受１０７を介して支持されるとともに、この仕切壁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 driven to rotate by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in the drawing. It has become. The output gear 4 is supported via an angular bearing 107 on a partition wall (intermediate wall) 13 formed by coupling two members, and is supported in the casing 50 via the partition wall 13. Thus, while being able to rotate around the axis O of the input shaft 1, displacement in the direction of the axis O is prevented.

出力側ディスク３，３は、入力軸１との間に介在されたニードル軸受５，５によって、入力軸１の軸線Ｏを中心に回転自在に支持されている。また、図中左側の入力側ディスク２は、入力軸１にボールスプライン６を介して支持され、図中右側の入力側ディスク２は、入力軸１にスプライン結合されており、これら入力側ディスク２は入力軸１と共に回転するようになっている。また、入力側ディスク２，２の内側面（凹面；トラクション面とも言う）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４参照）が回転自在に挟持されている。   The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. Further, there is power between the inner side surfaces (concave surface; also referred to as a traction surface) 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. A roller 11 (see FIG. 4) is rotatably held.

図３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３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を付与する。   A step portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 3, and the step portion 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step portion 2b. At the same time, the back surface (right surface in FIG. 3) of the input side disk 2 is abutted against a loading nut 9 screwed into a screw portion formed on the outer peripheral surface of the input shaft 1. 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３のＡ−Ａ線に沿う断面図である図４に示すように、ケーシング５０の内側であって、出力側ディスク３，３の側方位置には、両ディスク３，３を両側から挟む状態で一対のヨーク２３Ａ，２３Ｂが支持されている。これら一対のヨーク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。そして、後述するトラニオン１５の両端部に設けられた枢軸１４を揺動自在に支持するため、ヨーク２３Ａ，２３Ｂの四隅には、円形の支持孔１８が設けられるとともに、ヨーク２３Ａ，２３Ｂの幅方向の中央部には、円形の係止孔１９が設けられている。   As shown in FIG. 4, which is a cross-sectional view taken along the line AA in FIG. 3, both the disks 3 and 3 are sandwiched from both sides inside the casing 50 and at the side positions of the output side disks 3 and 3. The pair of yokes 23A and 23B is supported in the state. The pair of yokes 23A and 23B are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support pivots 14 provided at both ends of the trunnion 15 to be described later in a swingable manner, circular support holes 18 are provided at the four corners of the yokes 23A and 23B, and the width direction of the yokes 23A and 23B. A circular locking hole 19 is provided at the center of the.

一対のヨーク２３Ａ，２３Ｂは、ケーシング５０の内面の互いに対向する部分に形成された支持ポスト６４，６８により、支持ポスト６４，６８を支点として揺動できるように支持されている。これらの支持ポスト６４，６８はそれぞれ、入力側ディスク２の内側面２ａと出力側ディスク３の内側面３ａとの間にある第１キャビティ２２１および第２キャビティ２２２にそれぞれ対向する状態で設けられている。   The pair of yokes 23A and 23B is supported by support posts 64 and 68 formed on the inner surface of the casing 50 so as to be able to swing around the support posts 64 and 68 as fulcrums. These support posts 64 and 68 are provided so as to face the first cavity 221 and the second cavity 222, respectively, between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3. Yes.

したがって、ヨーク２３Ａ，２３Ｂは、各支持ポスト６４，６８に支持された状態で、その一端部が第１キャビティ２２１の外周部分に対向するとともに、その他端部が第２キャビティ２２２の外周部分に対向している。   Therefore, the yokes 23 </ b> A and 23 </ b> B are supported by the support posts 64 and 68, and one end thereof faces the outer peripheral portion of the first cavity 221, and the other end faces the outer peripheral portion of the second cavity 222. is doing.

第１および第２のキャビティ２２１，２２２は同一構造であるため、以下、第１キャビティ２２１のみについて説明する。   Since the first and second cavities 221 and 222 have the same structure, only the first cavity 221 will be described below.

図４に示すように、ケーシング５０の内側において、第１キャビティ２２１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４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、その本体部である支持板部１６の長手方向(図４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。   As shown in FIG. 4, inside the casing 50, the first cavity 221 is provided with a pair of trunnions 15 and 15 that swing about a pair of pivots 14 and 14 that are twisted with respect to the input shaft 1. It has been. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of bent portions formed in a state where the trunnions 15, 15 are bent toward the inner side surface of the support plate 16 at both ends in the longitudinal direction (vertical direction in FIG. 4) of the support plate 16. Wall portions 20 and 20 are provided. 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（第１の軸部）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（第２の軸部）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 portion of the support plate portion 16, and a base end portion (first shaft portion) 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft 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、前述したように、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４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。前述したように、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（傾転軸受）３０を介して揺動自在（傾転自在）に支持されている。また、前述したように、ヨーク２３Ａ，２３Ｂの幅方向（図４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、支持ポスト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状の支持ポスト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、球面状の支持ポスト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。   As described above, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable with respect to the pair of yokes 23A and 23B and displaceable in the axial direction (vertical direction in FIG. 4). The trunnions 15 and 15 are restricted from moving in the horizontal direction by the yokes 23A and 23B. As described above, four circular support holes 18 are provided at the four corners of each of the yokes 23A and 23B, and the pivot shafts 14 provided at both ends of the trunnion 15 are respectively provided in the support holes 18 with radial needle bearings ( A tilting bearing 30 is supported so as to be swingable (tiltable). Further, as described above, the 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. 4), and the inner peripheral surface of the locking hole 19 is cylindrical. Support posts 64 and 68 are internally fitted as surfaces. That is, the upper yoke 23A is swingably supported by the spherical support post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical support post 68. The upper cylinder body 61 of the drive cylinder 31 that supports this 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４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 both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

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

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

さらに、各トラニオン１５，１５の一端部(図４の下端部)にはそれぞれ駆動ロッド（枢軸１４から延びる軸部）２９，２９が設けられており、各駆動ロッド２９，２９の中間部外周面に駆動ピストン（油圧ピストン）３３，３３が固設されている。そして、これら各駆動ピストン３３，３３はそれぞれ、上側シリンダボディ６１と下側シリンダボディ６２とによって構成された駆動シリンダ３１内に油密に嵌装されている。これら各駆動ピストン３３，３３と駆動シリンダ３１とで、各トラニオン１５，１５を、これらトラニオン１５，１５の枢軸１４，１４の軸方向に変位させる駆動装置３２を構成している。   Further, drive rods (shaft portions extending from the pivot shaft) 29 and 29 are respectively provided at one end portions (lower end portions in FIG. 4) of the trunnions 15 and 15, and outer peripheral surfaces of intermediate portions of the drive rods 29 and 29. The drive pistons (hydraulic pistons) 33, 33 are fixedly provided. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

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

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

その結果、各パワーローラ１１，１１の周面１１ａ，１１ａと各内側面２ａ，３ａとの当接位置が変化し、入力軸１と出力歯車４との間の回転速度比が変化する。また、これら入力軸１と出力歯車４との間で伝達するトルクが変動し、各構成部材の弾性変形量が変化すると、各パワーローラ１１，１１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 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 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、上記構成のトロイダル型無段変速機のケーシング内には、トラクション接触部の動力伝達と各ディスク２，３の冷却のために、各ディスク２，３に潤滑油を供給する。潤滑油を供給するための具体的な構造としては、例えば、特許文献１〜特許文献９に記載されている技術が挙げられる。
特許文献１〜６に記載の技術は、支持ポスト６４に設けられた油路から入力側ディスク２および出力側ディスク３の内側面（トラクション面）２ａ，３ａに向けて潤滑油を噴射するものである。特許文献７に記載の技術は、入力軸１の内部に形成した油路より、ディスク２，３の背面や内側面２ａ，３ａに潤滑油を供給するものである。また、特許文献８、９に記載の技術は両方の供給構造を備えるものである。 By the way, in the casing of the toroidal-type continuously variable transmission having the above-described configuration, lubricating oil is supplied to the disks 2 and 3 for power transmission of the traction contact portion and cooling of the disks 2 and 3. As a specific structure for supplying the lubricating oil, for example, techniques described in Patent Documents 1 to 9 can be cited.
The techniques described in Patent Documents 1 to 6 inject lubricating oil from the oil passage provided in the support post 64 toward the inner side surfaces (traction surfaces) 2a and 3a of the input side disk 2 and the output side disk 3. is there. The technique described in Patent Document 7 supplies lubricating oil to the back surfaces of the disks 2 and 3 and the inner side surfaces 2 a and 3 a from an oil passage formed inside the input shaft 1. The techniques described in Patent Documents 8 and 9 are provided with both supply structures.

特開平６−２８０９６０号公報Japanese Patent Laid-Open No. 6-280960 特開平１０−１３２０４５号公報JP-A-10-132045 特開２００３−２０７０１１号公報JP 2003-207011 A 特開２００４−３０８８６８号公報JP 2004-308868 A 特開２００４−３０８８７６号公報JP 2004-308876 A 特許３５９２０９３号公報Japanese Patent No. 3520993 特開２００４−１５６７５８号公報JP 2004-156758 A 特開平１１−３３６８６８号公報JP 11-336868 A 特許３７２６６７０号公報Japanese Patent No. 3726670

しかしながら、特許文献１〜６，８，９のように、支持ポスト６４の油路から入力側ディスク２、出力側ディスク３の内側面（トラクション面）２ａ，３ａに油を供給しても、ディスク２，３の回転時に発生する遠心力により潤滑油が飛ばされてしまい、ディスク２，３を効率良く冷却できない。
また、特許文献７〜９のように、入力軸１内部の油路からディスク２，３側に潤滑油を供給する構造では、油路となる穴を数ヶ所形成し、潤滑油をこれら幾つもの穴を通ってディスクに供給するため、潤滑油の量を制御することが難しいうえに、油路の途中で他の構成要素から熱を奪い、ディスク２，３に到達するころには温度が上昇し、ディスク２，３を効率よく冷却できない虞がある。 However, even if oil is supplied from the oil passage of the support post 64 to the inner side surfaces (traction surfaces) 2a, 3a of the input side disc 2 and the output side disc 3 as in Patent Documents 1-6, 8, 9 Lubricating oil is blown off by the centrifugal force generated during rotations 2 and 3, and the disks 2 and 3 cannot be cooled efficiently.
Further, as in Patent Documents 7 to 9, in the structure in which the lubricating oil is supplied from the oil passage inside the input shaft 1 to the discs 2 and 3, the oil passages are formed in several places, and the lubricating oil is supplied in several places. Since it is difficult to control the amount of lubricating oil because it is supplied to the disk through the hole, the temperature rises when it reaches the disks 2 and 3 by taking heat away from other components in the oil passage. However, the disks 2 and 3 may not be efficiently cooled.

本発明は、前記事情に鑑みて為されたもので、効率良くディスクを冷却することが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する。   The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal continuously variable transmission that can cool a disk efficiently.

前記目的を達成するために、請求項１に記載のトロイダル型無段変速機は、ケーシングの内側で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、これらの入力側ディスクと出力側ディスクとの間に挟持されるパワーローラとを備えたトロイダル伝動ユニットが２つ、両出力側ディスクの背面または両入力側ディスクの背面が前記ケーシングに固定された中間壁を挟んで対向するように配置されているトロイダル型無段変速機において、前記中間壁には、前記ディスクの前記背面に潤滑油を供給する油路が設けられていることを特徴とする。   In order to achieve the above object, the toroidal continuously variable transmission according to claim 1 is configured such that the input sides are concentrically and rotatably supported with the inner surfaces facing each other inside the casing. Two toroidal transmission units with a disk and an output disk, and a power roller sandwiched between the input disk and the output disk, the back of both output disks or the back of both input disks In the toroidal-type continuously variable transmission arranged so as to face each other with an intermediate wall fixed to the casing, an oil passage for supplying lubricating oil to the back surface of the disk is provided on the intermediate wall. It is characterized by being.

この請求項１に記載された発明においては、２個のトロイダル伝動ユニットの両出力側ディスクの両背面の間または両入力側ディスクの両背面の間に位置する中間壁に油路が設けられているので、この油路から出力側ディスクの背面または入力側ディスクの背面に潤滑油を直接供給することができるため、潤滑油の量を制御することが容易である。
また、ケーシングに固定された中間壁という固定要素に油路を設けているので、入力軸等の回転する部材などに設けられた油路から潤滑油を供給する場合のように回転速度に影響されるということがなく、潤滑油を供給することができ、また供給する潤滑油が途中で周囲の部材の熱を奪って温度が上がるということも抑制できるとともに、ディスクへの潤滑油の当て方を油路の吐出口の形状や角度によって簡単に制御でき、効率的なディスクの冷却を行うことができる。
したがって、制御装置等で設定した温度や供給量の潤滑油を安定して供給し易い。例えば、低温で必要量を安定して供給することもできるし、運転状態に応じて温度や供給量を変更することも容易となる。また、このような変更が可能になるということは、ディスクと潤滑油との温度差による表面張力で潤滑不足になることも防ぐことが可能となる。 In the first aspect of the present invention, the oil passage is provided in the intermediate wall located between the two back surfaces of the two output side disks or between the two back surfaces of the two input side disks of the two toroidal transmission units. Therefore, since the lubricating oil can be directly supplied from the oil path to the back surface of the output side disk or the back surface of the input side disk, it is easy to control the amount of the lubricating oil.
In addition, since the oil passage is provided in a fixed element called an intermediate wall fixed to the casing, it is affected by the rotational speed as in the case of supplying lubricating oil from an oil passage provided in a rotating member such as an input shaft. It is possible to supply lubricating oil, and it is possible to prevent the supplied lubricating oil from taking heat from surrounding members and raising the temperature, and to apply the lubricating oil to the disk. It can be easily controlled by the shape and angle of the discharge port of the oil passage, and efficient disk cooling can be performed.
Therefore, it is easy to stably supply the lubricating oil at the temperature and supply amount set by the control device or the like. For example, the required amount can be stably supplied at a low temperature, and the temperature and the supply amount can be easily changed according to the operating state. In addition, the fact that such a change is possible also makes it possible to prevent insufficient lubrication due to the surface tension due to the temperature difference between the disk and the lubricating oil.

さらに、ディスクの内側面（トラクション面）にポストに設けられた油路などを用いて潤滑油を吹き付ける構造を備えたトロイダル型無段変速機の場合には、このポストの油路と中間壁の油路とに同じ潤滑油供給源から潤滑油を供給することにより、ディスクのトラクション面と背面から同じ温度の潤滑油を供給することができ、ディスク内の温度むらを抑制することができる。   Furthermore, in the case of a toroidal type continuously variable transmission having a structure in which lubricating oil is sprayed using an oil passage provided on the post on the inner surface (traction surface) of the disc, the oil passage and intermediate wall of the post are provided. By supplying the lubricating oil to the oil passage from the same lubricating oil supply source, the lubricating oil having the same temperature can be supplied from the traction surface and the back surface of the disk, and temperature unevenness in the disk can be suppressed.

また、請求項２に記載されたトロイダル型無段変速機は、請求項１に記載された発明において、前記ディスクの前記背面には、フィンが設けられていることを特徴とする。   According to a second aspect of the present invention, the toroidal continuously variable transmission according to the first aspect is characterized in that fins are provided on the back surface of the disk.

この請求項２に記載された発明においては、ディスク２の背面にフィンが設けられているので、冷却効率を向上させることができるうえ、のフィンに潤滑油を吹き付けることにより、冷却効率をさらに向上させることができる。この場合、ケーシングに固定された中間壁という固定要素に油路を設けているので、ディスクのフィンへの潤滑油の当て方（量、角度など）を油路の吐出口の形状や角度によって簡単に制御できるため、このような効率的なディスクの冷却を行うことができる。   In the invention described in claim 2, since the fins are provided on the back surface of the disk 2, the cooling efficiency can be improved and the cooling efficiency can be further improved by spraying lubricating oil onto the fins. Can be made. In this case, since the oil passage is provided in the fixed element called the intermediate wall fixed to the casing, the way (amount, angle, etc.) of lubricating oil applied to the fins of the disc can be easily determined by the shape and angle of the discharge outlet of the oil passage. Therefore, such efficient disk cooling can be performed.

また、ディスクの背面と中間壁との間の間隙は、トロイダル型無段変速機を出来る限りコンパクトにするために、通常狭く設定されているので、この空間に潤滑油が滞留し易いが、ディスクの回転に伴ってこのフィンが回転し、このディスクの背面と中間壁との間の前記間隙の潤滑油が掻き出されるように、フィンの配置を設定することにより、このフィンにより潤滑油を掻き出すことができ、冷却効率を向上させることができるとともに、油抵抗を低減することができる。   In addition, the gap between the rear surface of the disk and the intermediate wall is normally set narrow so that the toroidal continuously variable transmission can be made as compact as possible. The fin rotates so that the lubricating oil in the gap between the back surface and the intermediate wall of the disk is scraped out, and the lubricating oil is scraped out by the fin by setting the arrangement of the fins. It is possible to improve cooling efficiency and reduce oil resistance.

本発明のトロイダル型無段変速機によれば、ケーシングに固定された中間壁に、ディスクの背面に潤滑油を供給する油路が設けられているので、ディスクを効率的に冷却することができる。   According to the toroidal continuously variable transmission of the present invention, an oil passage for supplying lubricating oil to the back surface of the disk is provided on the intermediate wall fixed to the casing, so that the disk can be efficiently cooled. .

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、中間壁に設けられた油路による潤滑構造にあり、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３および図４と同一の符号を付して簡潔に説明するに留める。
図１および図２は本発明の実施の形態を示している。図１に示すように、このトロイダル型無段変速機は、ダブルキャビティ式のトロイダル型無段変速機であり、２つのトロイダル伝動ユニット２００，２０１を備えている。各トロイダル伝動ユニット２００，２０１は、入力側ディスク２および出力側ディスク３とこれらの間に挟持される２つのパワーローラ１１，１１（図４参照）とを備えている。両出力側ディスク３，３の背面（外側面）３ｃ，３ｃは、ケーシング５０に固定された仕切壁（中間壁）１３を挟んで対向するように配置されている。両出力側ディスク３，３の背面３ｃ，３ｃはそれぞれ、仕切壁１３の両側面に僅かに隙間を隔てて対向している。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the lubrication structure by the oil passage provided in the intermediate wall, and other configurations and operations are the same as the conventional configurations and operations described above. Only the above will be referred to, and the other parts will be simply described with the same reference numerals as those in FIGS.
1 and 2 show an embodiment of the present invention. As shown in FIG. 1, the toroidal continuously variable transmission is a double cavity type toroidal continuously variable transmission, and includes two toroidal transmission units 200 and 201. Each toroidal transmission unit 200, 201 includes an input side disk 2 and an output side disk 3, and two power rollers 11, 11 (see FIG. 4) sandwiched therebetween. The rear surfaces (outer surfaces) 3c and 3c of the output side disks 3 and 3 are arranged so as to face each other with a partition wall (intermediate wall) 13 fixed to the casing 50 interposed therebetween. The back surfaces 3c and 3c of the output side disks 3 and 3 are opposed to both side surfaces of the partition wall 13 with a slight gap therebetween.

これらの出力側ディスク３，３はそれぞれ、対応する入力側ディスク２，２と対向するように入力軸１の中央部に位置し、出力歯車４および仕切壁１３を介して、ケーシング５０に支持されている。また、入力軸１は、回転トルクが入力される端部１ｄと、これと反対側に位置する端部１ｅとを有するとともに、これら端部１ｄ，１ｅに配置される軸受１００，１０１と、端部１ｄ，１ｅ間の中央部（出力歯車４のフランジ部４ａに隣接して各出力側ディスク３の内周面）に配置される軸受５，５とにより支持されている。   These output side disks 3 and 3 are respectively positioned in the center of the input shaft 1 so as to face the corresponding input side disks 2 and 2, and are supported by the casing 50 via the output gear 4 and the partition wall 13. ing. The input shaft 1 has an end 1d to which rotational torque is input and an end 1e positioned on the opposite side, and bearings 100 and 101 disposed on these ends 1d and 1e, and an end It is supported by bearings 5 and 5 arranged on the central part between the parts 1d and 1e (the inner peripheral surface of each output side disk 3 adjacent to the flange part 4a of the output gear 4).

また、端部１ｄに隣接する図中左側に位置する入力側ディスク２とカム板７との間には皿ばね８が設けられ、端部１ｅに隣接する図中右側に位置する入力側ディスク２とローディングナット９との間には皿ばね１０が設けられている。これらの皿ばね８，１０は、各ディスク２，２，３，３の内側面２ａ，２ａ，３ａ，３ａとパワーローラ１１，１１の周面（トラクション面）１１ａ，１１ａ（図４参照）との当接部に押圧力を付与する。   Also, a disc spring 8 is provided between the input side disk 2 located on the left side in the figure adjacent to the end 1d and the cam plate 7, and the input side disk 2 located on the right side in the figure adjacent to the end 1e. And a loading nut 9 is provided with a disc spring 10. These disc springs 8 and 10 include inner surfaces 2a, 2a, 3a and 3a of the disks 2, 2, 3 and 3 and peripheral surfaces (traction surfaces) 11a and 11a (see FIG. 4) of the power rollers 11 and 11, respectively. A pressing force is applied to the contact portion.

また、一対の出力側ディスク３，３間に挟まれた出力歯車４は、軸受１０７，１０７を介して仕切壁１３によりケーシング５０に支持されている。出力歯車４を支持する軸受１０７，１０７には、一般にアンギュラ玉軸受が用いられる。また、出力歯車４としては、強度確保やノイズを小さくするため、一般に、はすば歯車が使用される。   The output gear 4 sandwiched between the pair of output side disks 3 and 3 is supported on the casing 50 by the partition wall 13 through bearings 107 and 107. An angular ball bearing is generally used for the bearings 107 and 107 that support the output gear 4. As the output gear 4, a helical gear is generally used in order to ensure strength and reduce noise.

そして、本実施の形態においては、入力側ディスク２，２、出力側ディスク３，３の潤滑および冷却のために、ケーシング５０側には油路５０ａが設けられており、この油路５０ａから分岐された２つの経路で潤滑油がこれらの各ディスク２，３に供給される。このケーシング５０側の油路５０ａは、油圧ポンプ等の潤滑油供給源に接続されている。
第１の経路は、両支持ポスト６４，６４にそれぞれ設けられ、先端に噴射ノズル（図示せず）を有する油路６４ａ，６４ａである。潤滑油は、各油路６４ａ，６４ａを通って先端の噴射ノズルから、入力側ディスク２、２の内側面２ａ、２ａ、出力側ディスク３、３の内側面３ａ，３ａ、およびパワーローラ１１，１１の周面１１ａ，１１ａに吹き付けられ、トラクション面に必要な油膜を形成すると共に、これらを冷却する。 In the present embodiment, an oil passage 50a is provided on the casing 50 side for lubrication and cooling of the input side disks 2 and 2 and the output side disks 3 and 3, and branches from the oil path 50a. The lubricating oil is supplied to each of these disks 2 and 3 through the two paths. The oil passage 50a on the casing 50 side is connected to a lubricating oil supply source such as a hydraulic pump.
The first paths are oil paths 64a and 64a provided on both support posts 64 and 64, respectively, and having injection nozzles (not shown) at their tips. Lubricating oil passes through the oil passages 64a and 64a from the tip injection nozzle, the inner side surfaces 2a and 2a of the input side disks 2 and 2, the inner side surfaces 3a and 3a of the output side disks 3 and 3, and the power roller 11, 11 is sprayed on the peripheral surfaces 11a and 11a to form a necessary oil film on the traction surface and cool these.

一方、第２の経路として、仕切壁１３に油路４０が設けられている。油路４０は、ケーシング５０側の油路５０ａと接続している基部側油路４０ａと、この基部側油路４０ａから２つに分岐し、各出力側ディスク３，３の各背面３ｃに向けて吐出口を開口している先端側油路４１，４２とを備えている。   On the other hand, an oil passage 40 is provided in the partition wall 13 as a second route. The oil passage 40 is branched into two from the base-side oil passage 40a connected to the oil passage 50a on the casing 50 side, and from the base-side oil passage 40a toward the back surfaces 3c of the output-side disks 3 and 3. And tip side oil passages 41 and 42 that open the discharge port.

図２に示すように、各出力側ディスク３の背面３ｃには、仕切壁１３側に向かって突出する複数のフィン３ｂが設けられている。各フィン３ｂは、長方形の薄板状に形成され、周方向に等角度間隔で放射状に配置されている。
先端側油路４１，４２の吐出口の形状や角度は、潤滑油を回転中の出力側ディスク３の各フィン３ｂに当てることができるように設定するのが好ましい。例えば、先端側油路４１側の出力側ディスク３の回転方向を矢印Ｐで示すと、先端側油路４１の吐出口からの潤滑油の供給角度は矢印Ｑで示す方向であり、このようにすることで、回転中の出力側ディスク３の各フィン３ｂに次々に潤滑油を吹き付けることができ、冷却効率を高めることができる。各フィン３ｂは、出力側ディスク３とともに回転することにより、出力側ディスク３の背面３ｃと仕切壁１３の側面と間の狭い間隙（空間）内の潤滑油を、この空間から掻き出している。 As shown in FIG. 2, a plurality of fins 3 b that protrude toward the partition wall 13 are provided on the back surface 3 c of each output-side disk 3. Each fin 3b is formed in a rectangular thin plate shape, and is arranged radially at equal angular intervals in the circumferential direction.
It is preferable to set the shape and angle of the discharge ports of the tip side oil passages 41 and 42 so that the lubricating oil can be applied to the fins 3b of the rotating output side disk 3. For example, when the rotation direction of the output side disk 3 on the tip side oil passage 41 side is indicated by an arrow P, the supply angle of the lubricating oil from the discharge port of the tip side oil passage 41 is the direction indicated by the arrow Q. By doing so, lubricating oil can be sprayed one after another to each fin 3b of the output side disk 3 in rotation, and cooling efficiency can be improved. Each fin 3b rotates together with the output side disk 3 to scrape out the lubricating oil in a narrow gap (space) between the back surface 3c of the output side disk 3 and the side surface of the partition wall 13 from this space.

以上のように構成されたトロイダル型無段変速機にあっては、２個のトロイダル伝動ユニット２００，２０１の両出力側ディスク３，３の両背面３ｃ，３ｃの間に位置する仕切壁１３に油路４０が設けられているので、この油路４０から出力側ディスク３，３の背面３ｃ、３ｃは入力側ディスクの背面３ｃ、３ｃに潤滑油を直接供給することができるため、潤滑油の量を制御することが容易である。
また、ケーシング５０に固定された仕切壁１３という固定要素に油路４０が設けられているので、入力軸１等の回転する部材などに設けられたに油路から潤滑油を供給する場合のように回転速度に影響されるということがなく、潤滑油を供給することができる。また、供給する潤滑油が途中で周囲の部材の熱を奪って温度が上がるということも抑制できるとともに、出力側ディスク３への潤滑油の当て方を油路４０（４１，４２）の吐出口の形状や角度を適度に設定することにより簡単に制御でき、効率的な出力側ディスク３の冷却を行うことができる。
したがって、制御装置等で設定した温度や供給量の潤滑油を安定して供給し易い。例えば、低温で必要量を安定して供給することもできるし、運転状態に応じて温度や供給量を変更することも容易となる。また、このような変更が可能になるということは、出力側ディスク３と潤滑油との温度差による表面張力で潤滑不足になることも防ぐことが可能になる。 In the toroidal-type continuously variable transmission configured as described above, the partition wall 13 positioned between the two back surfaces 3c, 3c of the output side disks 3, 3 of the two toroidal transmission units 200, 201 is provided. Since the oil path 40 is provided, the back surfaces 3c and 3c of the output side disks 3 and 3 can be directly supplied from the oil path 40 to the back surfaces 3c and 3c of the input side disk. It is easy to control the amount.
In addition, since the oil passage 40 is provided in the fixed element called the partition wall 13 fixed to the casing 50, the lubricating oil is supplied from the oil passage to the rotating member such as the input shaft 1 or the like. The lubricating oil can be supplied without being affected by the rotational speed. Further, it is possible to prevent the supplied lubricating oil from depriving the surrounding members of the heat and raising the temperature, and the way to apply the lubricating oil to the output side disk 3 is the discharge port of the oil passage 40 (41, 42). By appropriately setting the shape and angle, the output side disk 3 can be efficiently cooled.
Therefore, it is easy to stably supply the lubricating oil at the temperature and supply amount set by the control device or the like. For example, the required amount can be stably supplied at a low temperature, and the temperature and the supply amount can be easily changed according to the operating state. In addition, the fact that such a change is possible makes it possible to prevent insufficient lubrication due to the surface tension due to the temperature difference between the output side disk 3 and the lubricating oil.

さらに、出力側ディスク３の内側面（トラクション面）３ａに潤滑油を吹き付けるための支持ポスト（ポスト）６４に設けられた油路６４ａと、仕切壁１３の油路４０とに、同じ潤滑油供給源に接続された油路５０ａから潤滑油を供給しているので、出力側ディスク３の内側面（トラクション面）３ａと背面３ｃから同じ温度の潤滑油を供給することができるため、出力側ディスク３内の温度むらを抑制することができる。   Further, the same lubricating oil is supplied to the oil passage 64a provided in the support post (post) 64 for spraying the lubricating oil to the inner side surface (traction surface) 3a of the output side disk 3 and the oil passage 40 of the partition wall 13. Since the lubricating oil is supplied from the oil passage 50a connected to the power source, the lubricating oil having the same temperature can be supplied from the inner surface (traction surface) 3a and the rear surface 3c of the output side disk 3, so that the output side disk 3 can suppress temperature unevenness.

また、出力側ディスク３の背面３ｃにフィン３ｂが設けられているので、冷却効率を向上させることができ、そのうえこのフィン３ｂに潤滑油を吹き付けているので、冷却効率をさらに向上させることができる。この場合、ケーシング５０に固定された仕切壁１３という固定要素に油路４０を設けているので、出力ディスク３のフィン３ｂへの潤滑油の当て方（量、角度など）を油路４１，４２の吐出口の形状や角度によって簡単に制御できるため、このような効率的なディスクの冷却を容易に行うことができる。   Further, since the fins 3b are provided on the back surface 3c of the output side disk 3, the cooling efficiency can be improved, and furthermore, since the lubricating oil is sprayed on the fins 3b, the cooling efficiency can be further improved. . In this case, since the oil passage 40 is provided in the fixed element called the partition wall 13 fixed to the casing 50, the oil passages 41 and 42 indicate how to apply the lubricating oil (the amount, the angle, etc.) to the fins 3 b of the output disk 3. Since it can be easily controlled by the shape and angle of the discharge port, such efficient disk cooling can be easily performed.

さらに、出力側ディスク３の背面３ｃと仕切壁１３との間の狭き間隙に潤滑油が滞留し易いが、出力側ディスク３の回転に伴ってフィン３ｂが回転し、このフィン３ｂにより潤滑油を掻き出すことができるので、冷却効率を向上させることができるとともに、油抵抗を低減することができる。   Further, the lubricating oil tends to stay in a narrow gap between the back surface 3c of the output side disk 3 and the partition wall 13, but the fin 3b rotates as the output side disk 3 rotates, and the lubricating oil is supplied by the fin 3b. Since it can be scraped, the cooling efficiency can be improved and the oil resistance can be reduced.

なお、前述の実施の形態では、両出力側ディスク３，３の背面３ｃ，３ｃがケーシング５０に固定された仕切壁（中間壁）１３を挟んで対向するように配置されているトロイダル型無段変速機に本発明を適用した場合について説明したが、本発明は、両入力側ディスクと出力側ディスクの位置が入れ替わり、両入力側ディスクの両背面がケーシングに固定された仕切壁（中間壁）を挟んで対向するように配置されているトロイダル型無段変速機にも適用することができる。   In the above-described embodiment, the toroidal type continuously variable in which the rear surfaces 3c and 3c of the output side disks 3 and 3 are arranged so as to face each other with the partition wall (intermediate wall) 13 fixed to the casing 50 interposed therebetween. Although the case where the present invention is applied to the transmission has been described, the present invention relates to a partition wall (intermediate wall) in which the positions of both the input side disk and the output side disk are interchanged and both the back surfaces of both the input side disks are fixed to the casing. The present invention can also be applied to a toroidal-type continuously variable transmission that is disposed so as to face each other.

本発明は、種々のハーフトロイダル型無段変速機のほか、フルトロイダル型無段変速機にも適用することができる。   The present invention can be applied not only to various half-toroidal continuously variable transmissions but also to full toroidal continuously variable transmissions.

本発明の実施の形態に係るトロイダル型無段変速機の要部断面図である。It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on embodiment of this invention. 同、出力側ディスクを背面側から見た斜視図である。It is the perspective view which looked at the output side disk from the back side. 従来から知られているトロイダル型無段変速機の具体的構造の一例を示す断面図である。It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. 図３のＡ−Ａ線に沿う断面図である。It is sectional drawing which follows the AA line of FIG.

符号の説明Explanation of symbols

１ 入力軸
２ 入力側ディスク
３ 出力側ディスク
３ｂ フィン
３ｃ 背面
１１ パワーローラ
１３ 仕切壁（中間壁）
４０ 油路
４０ａ 基部端側油路
４１，４２ 先端側油路
５０ ケーシング
２００，２０１ トロイダル伝動ユニット DESCRIPTION OF SYMBOLS 1 Input shaft 2 Input side disk 3 Output side disk 3b Fin 3c Back surface 11 Power roller 13 Partition wall (intermediate wall)
40 Oil passage 40a Base end side oil passage 41, 42 Tip side oil passage 50 Casing 200, 201 Toroidal transmission unit

Claims (2)

ケーシングの内側で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、これらの入力側ディスクと出力側ディスクとの間に挟持されるパワーローラとを備えたトロイダル伝動ユニットが２つ、両出力側ディスクの背面または両入力側ディスクの背面が前記ケーシングに固定された中間壁を挟んで対向するように配置されているトロイダル型無段変速機において、
前記中間壁には、前記ディスクの前記背面に潤滑油を供給する油路が設けられていることを特徴とするトロイダル型無段変速機。 An input side disk and an output side disk supported concentrically and rotatably with the inner side surfaces facing each other inside the casing, and are sandwiched between these input side disk and output side disk Two toroidal transmission units equipped with a power roller, and arranged so that the back surfaces of both output side disks or the back surfaces of both input side disks face each other across an intermediate wall fixed to the casing. In a step transmission,
A toroidal continuously variable transmission characterized in that an oil passage for supplying lubricating oil to the back surface of the disk is provided in the intermediate wall. 前記ディスクの前記背面には、フィンが設けられていることを特徴とする請求項１に記載のトロイダル型無段変速機。   The toroidal continuously variable transmission according to claim 1, wherein fins are provided on the back surface of the disk.
JP2006155261A 2006-06-02 2006-06-02 Toroidal type continuously variable transmission Withdrawn JP2007321931A (en)

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