JPH11166605A - Output side disc unit for toroidal continuously variable transmission - Google Patents
Output side disc unit for toroidal continuously variable transmissionInfo
- Publication number
- JPH11166605A JPH11166605A JP33554097A JP33554097A JPH11166605A JP H11166605 A JPH11166605 A JP H11166605A JP 33554097 A JP33554097 A JP 33554097A JP 33554097 A JP33554097 A JP 33554097A JP H11166605 A JPH11166605 A JP H11166605A
- Authority
- JP
- Japan
- Prior art keywords
- output
- continuously variable
- variable transmission
- type continuously
- toroidal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明に係るトロイダル型
無段変速機用出力側ディスクユニットは、例えば自動車
用の変速機として、或は各種産業機械用の変速機とし
て、それぞれ利用するトロイダル型無段変速機の組立作
業を容易にすると共に、精度向上に基づく性能向上を図
るものである。BACKGROUND OF THE INVENTION The output side disk unit for a toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for an automobile or as a transmission for various industrial machines. The present invention facilitates the assembling work of a transmission and improves performance based on improved accuracy.
【０００２】[0002]
【従来の技術】自動車用変速機として、図６〜７に略示
する様なトロイダル型無段変速機を使用する事が研究さ
れている。このトロイダル型無段変速機は、例えば実開
昭６２−７１４６５号公報に開示されている様に、入力
軸１と同心に入力側ディスク２を支持し、この入力軸１
と同心に配置した出力軸３の端部に出力側ディスク４を
固定している。トロイダル型無段変速機を納めたケーシ
ングの内側には、上記入力軸１並びに出力軸３に対して
捻れの位置にある枢軸５、５を中心として揺動するトラ
ニオン６、６を設けている。2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input disk 2 concentrically with an input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open Publication No. 62-71465.
The output side disk 4 is fixed to the end of the output shaft 3 which is arranged concentrically. Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6 and 6 that swing about pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3 are provided.
【０００３】即ち、これら各トラニオン６、６は、それ
ぞれの両端部外面に上記枢軸５、５を、互いに同心に設
けている。又、これら各トラニオン６、６の中間部には
変位軸７、７の基端部を支持し、上記枢軸５、５を中心
として上記各トラニオン６、６を揺動させる事により、
上記各変位軸７、７の傾斜角度の調節を自在としてい
る。上記各トラニオン６、６に支持した変位軸７、７の
周囲には、それぞれパワーローラ８、８を回転自在に支
持している。そして、これら各パワーローラ８、８を、
上記入力側、出力側両ディスク２、４の、互いに対向す
る内側面２ａ、４ａ同士の間に挟持している。これら各
内側面２ａ、４ａは、それぞれ断面が、上記枢軸５を中
心とする円弧を回転させて得られる凹面をなしている。
そして、球状凸面に形成した上記各パワーローラ８、８
の周面８ａ、８ａを、上記内側面２ａ、４ａに当接させ
ている。That is, each of the trunnions 6, 6 has the pivots 5, 5 concentrically provided on the outer surfaces of both ends. In addition, a base end of the displacement shafts 7, 7 is supported at an intermediate portion between the trunnions 6, 6, and the trunnions 6, 6 are pivoted about the pivots 5, 5, whereby
The tilt angles of the displacement shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. And each of these power rollers 8, 8 is
The input side and output side disks 2 and 4 are sandwiched between inner surfaces 2a and 4a facing each other. Each of the inner side surfaces 2a, 4a has a concave section obtained by rotating an arc around the pivot 5 as described above.
Each of the power rollers 8, 8 formed on a spherical convex surface
Are brought into contact with the inner side surfaces 2a, 4a.
【０００４】上記入力軸１と入力側ディスク２との間に
は、ローディングカム式の押圧装置９を設け、この押圧
装置９によって、上記入力側ディスク２を出力側ディス
ク４に向け、弾性的に押圧自在としている。この押圧装
置９は、入力軸１と共に回転するカム板１０と、保持器
１１により転動自在に保持した複数個（例えば４個）の
ローラ１２、１２とから構成している。上記カム板１０
の片側面（図６〜７の左側面）には、円周方向に亙る凹
凸面である駆動側カム面１３を形成し、上記入力側ディ
スク２の外側面（図６〜７の右側面）にも、同様の形状
を有する被駆動側カム面１４を形成している。そして、
上記複数個のローラ１２、１２を、上記入力軸１の中心
に関し放射方向の軸を中心とする回転自在に支持してい
る。[0004] A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by this pressing device 9 so as to be elastic. It can be pressed freely. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1, and a plurality (for example, four) of rollers 12, which are rotatably held by a holder 11. The cam plate 10
On one side surface (left side surface in FIGS. 6 and 7), a drive side cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and the outer side surface of the input side disk 2 (right side surface in FIGS. 6 and 7). Also, a driven cam surface 14 having a similar shape is formed. And
The plurality of rollers 12, 12 are rotatably supported about a radial axis with respect to the center of the input shaft 1.
【０００５】上述の様に構成するトロイダル型無段変速
機の使用時、入力軸１の回転に伴ってカム板１０が回転
すると、駆動側カム面１３が複数個のローラ１２、１２
を、入力側ディスク２の外側面に形成した被駆動側カム
面１４に押圧する。この結果、上記入力側ディスク２
が、上記複数のパワーローラ８、８に押圧されると同時
に、上記駆動側、被駆動側両カム面１３、１４と複数個
のローラ１２、１２との押し付け合いに基づいて、上記
入力側ディスク２が回転する。そして、この入力側ディ
スク２の回転が、前記複数のパワーローラ８、８を介し
て出力側ディスク４に伝達され、この出力側ディスク４
に固定の出力軸３が回転する。When the cam plate 10 rotates with the rotation of the input shaft 1 during use of the toroidal-type continuously variable transmission configured as described above, the driving-side cam surface 13 has a plurality of rollers 12, 12.
Is pressed against the driven cam surface 14 formed on the outer surface of the input disk 2. As a result, the input side disk 2
Is pressed by the plurality of power rollers 8, 8, and at the same time, the input side disk is pressed based on the pressing between the driving side and driven side cam surfaces 13, 14 and the plurality of rollers 12, 12. 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, 8, and the output side disk 4
, The fixed output shaft 3 rotates.
【０００６】入力軸１と出力軸３との回転速度比（変速
比）を変える場合で、先ず入力軸１と出力軸３との間で
減速を行なう場合には、前記各枢軸５、５を中心として
前記各トラニオン６、６を所定方向に揺動させる。そし
て、上記各パワーローラ８、８の周面８ａ、８ａが図６
に示す様に、入力側ディスク２の内側面２ａの中心寄り
部分と出力側ディスク４の内側面４ａの外周寄り部分と
にそれぞれ当接する様に、前記各変位軸７、７を傾斜さ
せる。反対に、増速を行なう場合には、上記枢軸５、５
を中心として上記各トラニオン６、６を反対方向に揺動
させる。そして、上記各パワーローラ８、８の周面８
ａ、８ａが図７に示す様に、入力側ディスク２の内側面
２ａの外周寄り部分と出力側ディスク４の内側面４ａの
中心寄り部分とに、それぞれ当接する様に、上記各変位
軸７、７を傾斜させる。各変位軸７、７の傾斜角度を図
６と図７との中間にすれば、入力軸１と出力軸３との間
で、中間の変速比を得られる。When the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 5 The trunnions 6, 6 are swung in a predetermined direction as a center. The peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG.
As shown in FIG. 5, the displacement shafts 7, 7 are inclined so as to abut against the central portion of the inner surface 2a of the input disk 2 and the outer peripheral portion of the inner surface 4a of the output disk 4, respectively. Conversely, when increasing the speed,
, Each of the trunnions 6 is swung in the opposite direction. The peripheral surface 8 of each of the power rollers 8
As shown in FIG. 7, each of the displacement shafts 7a and 8a comes into contact with a portion of the inner surface 2a of the input disk 2 near the outer periphery and a portion of the inner surface 4a of the output disk 4 near the center. , 7 are tilted. If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 6 and 7, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.
【０００７】又、図８〜９は、実願昭６３−６９２９３
号（実開平１−１７３５５２号）のマイクロフィルムに
記載された、より具体化されたトロイダル型無段変速機
の１例を示している。入力側ディスク２と出力側ディス
ク４とは、請求項の回転軸に相当する円管状の入力軸１
５の周囲に、それぞれが請求項のラジアル転がり軸受に
相当するニードル軸受１６、１６を介して、回転自在に
支持している。即ち、上記入力側ディスク２及び出力側
ディスク４の中心部には断面形状が円形である貫通孔１
７、１７を、それぞれ上記各ディスク２、４の内側面と
外側面とを軸方向（図８の左右方向）に貫通する状態で
形成している。上記各ニードル軸受１６、１６は、上記
各貫通孔１７、１７の内周面と上記入力軸１５の中間部
外周面との間に設けている。又、上記各貫通孔１７、１
７の内側面寄り端部内周面に形成した係止溝１８、１８
には止め輪１９、１９を係止して、上記各ニードル軸受
１６、１６が上記各貫通孔１７、１７から、上記各ディ
スク２、４の内側面側に抜け出る事を防止している。
又、カム板１０は上記入力軸１５の端部（図８の左端
部）外周面にスプライン係合させ、鍔部２０により上記
入力側ディスク２から離れる方向への移動を阻止してい
る。そして、このカム板１０とローラ１２、１２とによ
り、上記入力軸１５の回転に基づいて上記入力側ディス
ク２を、上記出力側ディスク４に向け押圧しつつ回転さ
せる、ローディングカム式の押圧装置９を構成してい
る。上記出力側ディスク４には出力歯車２１を、キー２
２、２２により結合し、これら出力側ディスク４と出力
歯車２１とが同期して回転する様にしている。FIGS. 8 and 9 show Japanese Utility Model Application No. 63-69293.
FIG. 1 shows an example of a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application Publication No. Hei 1-173552. The input-side disk 2 and the output-side disk 4 are a cylindrical input shaft 1 corresponding to a rotating shaft in the claims.
5 are rotatably supported via needle bearings 16, 16 each corresponding to a radial rolling bearing according to the present invention. That is, a through-hole 1 having a circular cross section is formed at the center of the input side disk 2 and the output side disk 4.
7 and 17 are formed so as to penetrate the inner and outer surfaces of the disks 2 and 4 respectively in the axial direction (the left-right direction in FIG. 8). The needle bearings 16 are provided between the inner peripheral surfaces of the through holes 17 and the intermediate outer peripheral surface of the input shaft 15. Further, each of the through holes 17, 1
7, locking grooves 18 formed on the inner peripheral surface near the inner surface
The retaining rings 19, 19 are locked to prevent the needle bearings 16, 16 from coming out of the through holes 17, 17 to the inner side surfaces of the disks 2, 4, respectively.
Further, the cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 8) of the input shaft 15, and is prevented from moving in the direction away from the input side disk 2 by the flange portion 20. The cam plate 10 and the rollers 12, 12 are used to load and rotate the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. Is composed. The output side disk 4 is provided with an output gear 21 and a key 2
The output side disk 4 and the output gear 21 rotate in synchronization with each other.
【０００８】１対のトラニオン６、６の両端部は１対の
支持板２３、２３に、揺動並びに軸方向（図８の表裏方
向、図９の左右方向）に亙る変位自在に支持している。
そして、上記各トラニオン６、６の中間部に形成した円
孔２４、２４部分に、変位軸７、７を支持している。こ
れら各変位軸７、７は、互いに平行で且つ偏心した支持
軸部２５、２５と枢支軸部２６、２６とを、それぞれ有
する。このうちの各支持軸部２５、２５を上記各円孔２
４、２４の内側に、ラジアルニードル軸受２７、２７を
介して、回転自在に支持している。又、上記各枢支軸部
２６、２６の周囲にパワーローラ８、８を、別のラジア
ルニードル軸受２８、２８を介して、回転自在に支持し
ている。Both ends of the pair of trunnions 6, 6 are supported by a pair of support plates 23, 23 so as to be swingable and displaceable in the axial direction (front and back directions in FIG. 8, and left and right directions in FIG. 9). I have.
The displacement shafts 7, 7 are supported in circular holes 24, 24 formed in the middle portions of the trunnions 6, 6, respectively. Each of these displacement shafts 7 has a support shaft 25, 25 and a pivot shaft 26, 26 which are parallel and eccentric to each other. Each of the support shaft portions 25, 25 is connected to each of the circular holes 2
It is rotatably supported inside 4 and 24 via radial needle bearings 27 and 27. The power rollers 8, 8 are rotatably supported around the pivot shafts 26, 26 via other radial needle bearings 28, 28, respectively.
【０００９】尚、上記１対の変位軸７、７は、上記入力
軸１５に対して１８０度反対側位置に設けている。又、
これら各変位軸７、７の各枢支軸部２６、２６が各支持
軸部２５、２５に対し偏心している方向は、上記入力
側、出力側両ディスク２、４の回転方向に関し同方向
（図９で左右逆方向）としている。又、偏心方向は、上
記入力軸１５の配設方向に対しほぼ直交する方向として
いる。従って、上記各パワーローラ８、８は、上記入力
軸１５の配設方向に亙る若干の変位自在に支持される。
この結果、回転力の伝達状態で構成各部材に加わる大き
な荷重に基づく、これら構成各部材の弾性変形に起因し
て、上記各パワーローラ８、８が上記入力軸１５の軸方
向（図８の左右方向、図９の表裏方向）に変位する傾向
となった場合でも、上記構成各部品に無理な力を加える
事なく、この変位を吸収できる。The pair of displacement shafts 7, 7 are provided at positions opposite to the input shaft 15 by 180 degrees. or,
The direction in which the respective pivot shafts 26, 26 of the respective displacement shafts 7, 7 are eccentric with respect to the respective support shafts 25, 25 is the same as the rotation direction of the input side and output side disks 2, 4. (In FIG. 9, the left and right directions are reversed). The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 15 is provided. Accordingly, the power rollers 8 are supported to be slightly displaceable in the direction in which the input shaft 15 is provided.
As a result, the power rollers 8, 8 move in the axial direction of the input shaft 15 (see FIG. 8) due to the elastic deformation of these constituent members based on the large load applied to the constituent members in the state of transmitting the rotational force. Even in the case of displacement in the left-right direction (the front-back direction in FIG. 9), this displacement can be absorbed without applying excessive force to the above-mentioned components.
【００１０】又、上記各パワーローラ８、８の外側面と
上記各トラニオン６、６の中間部内側面との間には、パ
ワーローラ８、８の外側面の側から順に、スラスト玉軸
受２９、２９とスラストニードル軸受３０、３０とを設
けている。このうちのスラスト玉軸受２９、２９は、上
記各パワーローラ８、８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８、８の回転を許容
するものである。又、上記各スラストニードル軸受３
０、３０は、上記各パワーローラ８、８から上記各スラ
スト玉軸受２９、２９を構成する外輪３１、３１に加わ
るスラスト荷重を支承しつつ、前記各枢支軸部２６、２
６及び上記外輪３１、３１が、前記支持軸部２５、２５
を中心に揺動する事を許容する。Further, between the outer surface of each of the power rollers 8, 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6, a thrust ball bearing 29, 29 and thrust needle bearings 30, 30 are provided. Of these, the thrust ball bearings 29, 29 allow rotation of the power rollers 8, 8 while supporting the load in the thrust direction applied to the power rollers 8, 8. Also, each of the above thrust needle bearings 3
0, 30 support the thrust loads applied from the power rollers 8, 8 to the outer races 31, 31 constituting the respective thrust ball bearings 29, 29 while supporting the pivot shaft portions 26, 2,
6 and the outer races 31, 31 are supported by the support shafts 25, 25.
Swing around the center.
【００１１】更に、上記各トラニオン６、６の一端部
（図９の左端部）にはそれぞれ駆動ロッド３２、３２を
結合し、これら各駆動ロッド３２、３２の中間部外周面
に駆動ピストン３３、３３を固設している。そして、こ
れら各駆動ピストン３３、３３を、それぞれ駆動シリン
ダ３４、３４内に油密に嵌装している。Further, drive rods 32, 32 are respectively connected to one end (the left end in FIG. 9) of each of the trunnions 6, 6, and a drive piston 33, 33 is fixed. Each of the drive pistons 33 is fitted in the drive cylinders 34 in an oil-tight manner.
【００１２】上述の様に構成するトロイダル型無段変速
機の場合には、入力軸１５の回転は、押圧装置９を介し
て入力側ディスク２に伝わる。そして、この入力側ディ
スク２の回転が、１対のパワーローラ８、８を介して出
力側ディスク４に伝わり、更にこの出力側ディスク４の
回転が、出力歯車２１より取り出される。入力軸１５と
出力歯車２１との間の回転速度比を変える場合には、上
記１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
て上記１対のトラニオン６、６が、それぞれ逆方向に変
位し、例えば図９の下側のパワーローラ８が同図の右側
に、同図の上側のパワーローラ８が同図の左側に、それ
ぞれ変位する。この結果、これら各パワーローラ８、８
の周面８ａ、８ａと上記入力側ディスク２及び出力側デ
ィスク４の内側面２ａ、４ａ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
変化に伴って上記各トラニオン６、６が、支持板２３、
２３に枢支された枢軸５、５を中心として、互いに逆方
向に揺動する。この結果、前述の図６〜７に示した様
に、上記各パワーローラ８、８の周面８ａ、８ａと上記
各内側面２ａ、４ａとの当接位置が変化し、上記入力軸
１５と出力歯車２１との間の回転速度比が変化する。In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. The rotation of the input disk 2 is transmitted to the output disk 4 via the pair of power rollers 8, 8, and the rotation of the output disk 4 is extracted from the output gear 21. When changing the rotation speed ratio between the input shaft 15 and the output gear 21, the pair of drive pistons 33 are displaced in opposite directions. The pair of trunnions 6, 6 are displaced in opposite directions in accordance with the displacement of the driving pistons 33, 33. For example, the lower power roller 8 in FIG. Are displaced to the left in FIG. As a result, these power rollers 8, 8
The direction of the tangential force acting on the abutting portion between the peripheral surfaces 8a, 8a and the inner surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. Then, with the change in the direction of the force, each of the trunnions 6, 6 is
Swing in opposite directions about pivots 5, 5 pivotally supported by 23. As a result, as shown in FIGS. 6 and 7 described above, the contact positions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a change, and the input shaft 15 The rotation speed ratio with the output gear 21 changes.
【００１３】尚、この様に上記入力軸１５と出力歯車２
１との間で回転力の伝達を行なう際には、構成各部材の
弾性変形に基づいて上記各パワーローラ８、８が、上記
入力軸１５の軸方向に変位し、これら各パワーローラ
８、８を枢支している前記各変位軸７、７が、前記各支
持軸部２５、２５を中心として僅かに回動する。この回
動の結果、前記各スラスト玉軸受２９、２９の外輪３
１、３１の外側面と上記各トラニオン６、６の内側面と
が相対変位する。これら外側面と内側面との間には、前
記各スラストニードル軸受３０、３０が存在する為、こ
の相対変位に要する力は小さい。従って、上述の様に各
変位軸７、７の傾斜角度を変化させる為の力が小さくて
済む。Incidentally, the input shaft 15 and the output gear 2
When transmitting the rotational force between the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7 that pivotally support 8 rotates slightly about each of the support shaft portions 25. As a result of this rotation, the outer ring 3 of each of the thrust ball bearings 29, 29
The outer surfaces of the trunnions 6 and 6 are relatively displaced from each other. Since the thrust needle bearings 30, 30 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, the force for changing the inclination angle of each of the displacement shafts 7 can be small as described above.
【００１４】更に、伝達可能なトルクを増大すべく、図
１０〜１１に示す様に、入力軸１５ａの周囲に入力側デ
ィスク２Ａ、２Ｂと出力側ディスク４、４とを２個ずつ
設け、これら２個ずつの入力側ディスク２Ａ、２Ｂと出
力側ディスク４、４とを動力の伝達方向に関して互いに
並列に配置する構造も、従来から知られている。これら
図１０〜１１に示した構造は何れも、上記入力軸１５ａ
の中間部周囲に出力歯車２１ａを、この入力軸１５ａに
対する回転を自在として支持し、この出力歯車２１ａの
中心部に設けた円筒部の両端部に上記各出力側ディスク
４、４を、スプライン係合させている。そして、これら
各出力側ディスク４、４の内周面と上記入力軸１５ａの
外周面との間にニードル軸受１６、１６を設け、これら
各出力側ディスク４、４を上記入力軸１５ａの周囲に、
この入力軸１５ａに対する回転、並びにこの入力軸１５
ａの軸方向に亙る変位を自在に支持している。又、上記
各入力側ディスク２Ａ、２Ｂは、上記入力軸１５ａの両
端部に、この入力軸１５ａと共に回転自在に支持してい
る。この入力軸１５ａは、駆動軸３５により、ローディ
ングカム式の押圧装置９を介して回転駆動する。尚、こ
の駆動軸３５の先端部（図１０〜１１の左端部）外周面
と上記入力軸１５ａの基端部（図１０〜１１の右端部）
内周面との間には、滑り軸受、ニードル軸受等のラジア
ル軸受３６を設けている。従って、上記駆動軸３５と入
力軸１５ａとは、互いに同心に配置された状態のまま、
回転方向に亙る若干の変位自在に組み合わされている。Further, in order to increase the torque that can be transmitted, two input disks 2A and 2B and two output disks 4 and 4 are provided around the input shaft 15a as shown in FIGS. A structure in which two input-side disks 2A and 2B and two output-side disks 4 and 4 are arranged in parallel with each other in the power transmission direction is also conventionally known. Each of the structures shown in FIGS.
An output gear 21a is supported around the middle of the output gear 21a so as to freely rotate with respect to the input shaft 15a, and the output disks 4 are mounted on both ends of a cylindrical portion provided at the center of the output gear 21a. Have been combined. Needle bearings 16 and 16 are provided between the inner peripheral surface of each of the output side disks 4 and 4 and the outer peripheral surface of the input shaft 15a, and these output side disks 4 and 4 are placed around the input shaft 15a. ,
The rotation with respect to the input shaft 15a and the input shaft 15
a is freely supported in the axial direction. The input side disks 2A and 2B are rotatably supported on both ends of the input shaft 15a together with the input shaft 15a. The input shaft 15a is rotationally driven by a driving shaft 35 via a loading device 9 of a loading cam type. The outer peripheral surface of the distal end portion (left end portion in FIGS. 10 to 11) of the drive shaft 35 and the base end portion of the input shaft 15a (right end portion in FIGS. 10 to 11).
A radial bearing 36 such as a sliding bearing or a needle bearing is provided between the bearing and the inner peripheral surface. Therefore, the drive shaft 35 and the input shaft 15a are arranged concentrically with each other.
They are combined so as to be slightly displaceable in the rotation direction.
【００１５】但し、一方（図１０〜１１の左方）の入力
側ディスク２Ａは、背面（図１０〜１１の左面）をロー
ディングナット３７に、直接（図１１に示した構造の場
合）又は大きな弾力を有する皿板ばね５１を介して（図
１０に示した構造の場合）突き当てて、上記入力軸１５
ａに対する軸方向（図１０〜１１の左右方向）の変位を
実質的に阻止している。これに対して、カム板１０に対
向する入力側ディスク２Ｂは、ボールスプライン３８に
より上記入力軸１５ａに、軸方向に亙る変位自在に支持
している。そして、この入力側ディスク２Ｂの背面（図
１０〜１１の右面）とカム板１０の前面（図１０〜１１
の左面）との間に、皿板ばね３９とスラストニードル軸
受４０とを、互いに直列に設けている。このうちの皿板
ばね３９は、上記各ディスク２Ａ、２Ｂ、４の内側面２
ａ、４ａとパワーローラ８、８の周面８ａ、８ａとの当
接部に予圧を付与する役目を果たす。又、スラストニー
ドル軸受４０は、押圧装置９の作動時に、上記入力側デ
ィスク２Ｂとカム板１０との相対回転を許容する役目を
果たす。However, the input side disk 2A (left side in FIGS. 10 to 11) has a rear surface (left side in FIGS. 10 to 11) directly attached to the loading nut 37 (in the case of the structure shown in FIG. 11) or large. The input shaft 15 is brought into contact with the input shaft 15 through an elastic disc spring 51 (in the case of the structure shown in FIG. 10).
The displacement in the axial direction (the left-right direction in FIGS. 10 to 11) with respect to a is substantially prevented. On the other hand, the input side disk 2B facing the cam plate 10 is supported on the input shaft 15a by a ball spline 38 so as to be freely displaceable in the axial direction. Then, the rear surface of this input side disk 2B (the right surface in FIGS. 10 to 11) and the front surface of the cam plate 10 (FIGS. 10 to 11).
, A disc spring 39 and a thrust needle bearing 40 are provided in series with each other. Of these, the plate spring 39 is provided on the inner surface 2 of each of the disks 2A, 2B, and 4 described above.
a, 4a and serves to apply a preload to the contact portions between the peripheral surfaces 8a, 8a of the power rollers 8, 8. Further, the thrust needle bearing 40 plays a role of allowing relative rotation between the input side disk 2B and the cam plate 10 when the pressing device 9 is operated.
【００１６】又、図１０に示した構造例の場合、前記出
力歯車２１ａはハウジングの内側に設けた仕切壁４１
に、それぞれがアンギュラ型である１対の玉軸受４２、
４２により、軸方向に亙る変位を阻止した状態で、回転
自在に支持している。これに対して図１１に示した構造
例の場合、出力歯車２１ａの軸方向に亙る変位は自在で
ある。尚、上述した図１０〜１１に示した様に、２個ず
つの入力側ディスク２Ａ、２Ｂと出力側ディスク４、４
とを動力の伝達方向に関して互いに並列に配置する、所
謂ダブルキャビティ型のトロイダル型無段変速機が、カ
ム板１０に対向する一方又は双方の入力側ディスク２
Ａ、２Ｂをボールスプライン３８、３８ａにより上記入
力軸１５ａに、軸方向に亙る変位自在に支持している理
由は、これら両ディスク２Ａ、２Ｂの回転を完全に同期
させつつ、上記押圧装置９の作動に伴う構成各部材の弾
性変形に基づいて上記両ディスク２Ａ、２Ｂが、上記入
力軸１５ａに対し軸方向に変位する事を許容する為であ
る。In the case of the structure shown in FIG. 10, the output gear 21a is provided on a partition wall 41 provided inside the housing.
A pair of ball bearings 42 each of which is an angular type;
By 42, it is supported rotatably in a state where displacement in the axial direction is prevented. On the other hand, in the case of the structural example shown in FIG. 11, the displacement of the output gear 21a in the axial direction is free. As shown in FIGS. 10 to 11 described above, two input disks 2A and 2B and two output disks 4
And a so-called double-cavity toroidal-type continuously variable transmission, in which one or both of the input-side disks 2 facing the cam plate 10
A and 2B are supported on the input shaft 15a by the ball splines 38 and 38a so as to be freely displaceable in the axial direction because the rotations of the two disks 2A and 2B are completely synchronized while the pressing device 9 This is to allow the two disks 2A and 2B to be displaced in the axial direction with respect to the input shaft 15a based on the elastic deformation of the constituent members accompanying the operation.
【００１７】[0017]
【発明が解決しようとする課題】上述の様に構成され作
用するトロイダル型無段変速機を組み立てる場合に従来
は、このトロイダル型無段変速機の本体を収納するハウ
ジング４３（図９）の内側に構成各部材を、順番に組み
付ける様にしていた。従って、構成各部材が正しく機能
するか否かは、これら構成各部材を上記ハウジング４３
内に総て組み付けた後でしか確認できなかった。一方、
トロイダル型無段変速機の効率並びに耐久性を確保する
為には、構成各部材が正しく機能しなければならない。
この為、一部の構成部材のみが正しく機能しない場合で
も、上記ハウジング４３内で組み立てたトロイダル型無
段変速機の分解及び再組立を行なわなければならない。
従って、上述の様にしてトロイダル型無段変速機の組立
作業を行なうと、トロイダル型無段変速機の製造作業が
面倒で、コストの低廉化を図れない。本発明のトロイダ
ル型無段変速機用出力側ディスクユニットは、この様な
事情に鑑みて、発明したものである。Conventionally, when assembling a toroidal-type continuously variable transmission constructed and operating as described above, the inside of a housing 43 (FIG. 9) for accommodating the main body of the toroidal-type continuously variable transmission is conventionally known. The components are assembled in order. Therefore, whether or not the constituent members function properly depends on whether the constituent members are connected to the housing 43 or not.
It could only be confirmed after all had been assembled. on the other hand,
In order to ensure the efficiency and durability of the toroidal type continuously variable transmission, the components must function properly.
Therefore, even when only some components do not function properly, the toroidal-type continuously variable transmission assembled in the housing 43 must be disassembled and reassembled.
Therefore, when the assembling work of the toroidal type continuously variable transmission is performed as described above, the manufacturing operation of the toroidal type continuously variable transmission is troublesome, and the cost cannot be reduced. The output side disk unit for a toroidal type continuously variable transmission according to the present invention has been invented in view of such circumstances.
【００１８】[0018]
【課題を解決する為の手段】本発明のトロイダル型無段
変速機用出力側ディスクユニットは、内側面を断面円弧
状の凹面とし、中心部に軸方向に貫通する断面形状が円
形である貫通孔を有し、回転軸の中間部周囲にこの回転
軸に対する回転を自在に支持する出力側ディスクと、上
記貫通孔の内側に配置したラジアル転がり軸受と、この
貫通孔の内周面に形成した係止溝に係止し、このラジア
ル転がり軸受がこの貫通孔から抜け出る事を防止する止
め輪とを、トロイダル型無段変速機への組み付け以前
に、このトロイダル型無段変速機の組立完了後の位置関
係に予め組み立てておく。An output side disk unit for a toroidal type continuously variable transmission according to the present invention has an inner surface having a concave surface having an arcuate cross section and a circular cross section penetrating the center portion in the axial direction. An output side disk having a hole and freely supporting rotation with respect to the rotating shaft around an intermediate portion of the rotating shaft, a radial rolling bearing disposed inside the through hole, and an inner peripheral surface of the through hole. Before assembling to the toroidal type continuously variable transmission, before the assembling to the toroidal type continuously variable transmission, a retaining ring which is locked in the locking groove and prevents this radial rolling bearing from coming out of this through hole is completed. Assemble in advance in the positional relationship described above.
【００１９】[0019]
【作用】上述の様に構成する本発明のトロイダル型無段
変速機用出力側ディスクユニットを含んで構成するトロ
イダル型無段変速機は、前述した従来のトロイダル型無
段変速機と同様の作用に基づき、入力側ディスクと出力
側ディスクとの間で回転力の伝達を行ない、更にトラニ
オンの傾斜角度を変える事により、これら両ディスク同
士の間の回転速度比を変える。The toroidal type continuously variable transmission including the output side disk unit for the toroidal type continuously variable transmission of the present invention configured as described above has the same operation as the above-mentioned conventional toroidal type continuously variable transmission. , The torque is transmitted between the input side disk and the output side disk, and the rotation speed ratio between these two disks is changed by changing the inclination angle of the trunnion.
【００２０】特に、本発明のトロイダル型無段変速機用
出力側ディスクユニットの場合には、互いに別体の部材
である出力側ディスクとラジアル転がり軸受と止め輪と
を、トロイダル型無段変速機への組み付け以前に、この
トロイダル型無段変速機の組立完了後の位置関係に予め
組み立てている。この為、構成各部材が正しく機能する
か否かを、これら構成各部材をハウジング内に組み付け
る以前に確認できる。従って、トロイダル型無段変速機
全体を分解、再組立する等の面倒な作業を要する事な
く、トロイダル型無段変速機の効率並びに耐久性を確保
すべく、構成各部材同士の位置関係を高精度に維持でき
る。In particular, in the case of the output side disk unit for a toroidal type continuously variable transmission according to the present invention, the output side disk, the radial rolling bearing and the retaining ring, which are separate members, are connected to each other by the toroidal type continuously variable transmission. Prior to assembling the toroidal-type continuously variable transmission, the toroidal-type continuously variable transmission is assembled in a positional relationship after assembly is completed. Therefore, it can be confirmed whether or not the constituent members function properly before assembling these constituent members in the housing. Accordingly, the positional relationship between the constituent members is increased to secure the efficiency and durability of the toroidal-type continuously variable transmission without requiring troublesome work such as disassembling and reassembling the entire toroidal-type continuously variable transmission. Accuracy can be maintained.
【００２１】[0021]
【発明の実施の形態】図１〜３は、本発明の実施の形態
の第１例を示している。尚、本発明の特徴は、トロイダ
ル型無段変速機を構成する出力側ディスク４の内側に、
ニードル軸受１６及び止め輪１９を組み付けた構造をユ
ニット化した点にある。その他の部分の構造及び作用に
就いては、前述した従来構造と同様である為、重複する
図示及び説明を省略若しくは簡略にし、以下、本発明の
特徴部分を中心に説明する。1 to 3 show a first embodiment of the present invention. The feature of the present invention is that the inside of the output side disk 4 constituting the toroidal type continuously variable transmission is
The point is that the structure in which the needle bearing 16 and the retaining ring 19 are assembled is unitized. Since the structure and operation of the other parts are the same as those of the above-described conventional structure, overlapping illustration and description will be omitted or simplified, and the following description will focus on features of the present invention.
【００２２】上記出力側ディスク４は、軸受鋼等の硬質
金属に鍛造加工を施す事により一体形成したもので、内
側面４ａを断面円弧状の凹面とし、中心部に断面形状が
円形である貫通孔１７を、軸方向（図１〜３の左右方
向）に貫通する状態で設けている。この様な出力側ディ
スク４は、図３に示す様に、回転軸である入力軸１５ａ
の中間部周囲に、この入力軸１５ａに対する回転を自在
に支持する。この為に、上記貫通孔１７の内周面には、
ラジアル転がり軸受であるニードル軸受１６を配置して
いる。上記貫通孔１７の内周面は、内側面側大径部４４
と、円筒面部４５と、雌スプライン部４６と、外側面側
大径部４７とを、内側面側から外側面側に向け（図１の
左から右に）、軸方向に関して互いに直列に配置して成
る。The output side disk 4 is formed integrally by forging a hard metal such as a bearing steel. The inner side surface 4a has an arc-shaped concave surface, and the central portion has a circular cross-section at the center. The hole 17 is provided so as to penetrate in the axial direction (the left-right direction in FIGS. 1 to 3). As shown in FIG. 3, the output side disk 4 has an input shaft 15a which is a rotating shaft.
Around the input shaft 15a. For this reason, on the inner peripheral surface of the through hole 17,
A needle bearing 16 which is a radial rolling bearing is arranged. The inner peripheral surface of the through-hole 17 has an inner surface side large diameter portion 44.
And the cylindrical surface portion 45, the female spline portion 46, and the outer surface side large diameter portion 47 are arranged in series with each other in the axial direction from the inner surface side to the outer surface side (from left to right in FIG. 1). Consisting of
【００２３】このうちの円筒面部４５は、軸方向中間部
の内側面寄り（図１の左寄り）部分に設けられたもの
で、上記ニードル軸受１６の外輪軌道として機能する。
又、上記雌スプライン部４６は、上記入力軸１５ａの中
間部周囲に、この入力軸１５ａに対する回転自在に配置
したスリーブ４８（図３）の端部に形成した雄スプライ
ン部に係合して、上記出力側ディスク４を上記スリーブ
４８に、同期した回転を自在に結合する。更に、上記外
側面側大径部４７は、上記雌スプライン部４６と雄スプ
ライン部とを係合させた状態で、上記スリーブ４８の中
間部でこの雄スプライン部よりも中央寄り部分に密に外
嵌し、このスリーブ４８の中心軸と上記出力側ディスク
４の中心軸とを一致させる。尚、上記出力側ディスク４
の回転を取り出す為の出力歯車２１ａは、上記スリーブ
４８の中間部外周面に、このスリーブ４８と一体に形成
している。又、このスリーブ４８はハウジング４３内に
設けた仕切壁４１の内側に、それぞれがアンギュラ型で
ある１対の玉軸受４２、４２により、回転自在に支持し
ている。The cylindrical surface portion 45 is provided near the inner side surface (leftward in FIG. 1) of the intermediate portion in the axial direction, and functions as an outer ring track of the needle bearing 16.
Further, the female spline portion 46 engages with a male spline portion formed around an intermediate portion of the input shaft 15a at an end of a sleeve 48 (FIG. 3) rotatably disposed with respect to the input shaft 15a. The output side disk 4 is freely coupled to the sleeve 48 by synchronous rotation. Further, the outer-surface-side large-diameter portion 47 closes the center portion of the male spline portion closer to the center than the male spline portion at an intermediate portion of the sleeve 48 in a state where the female spline portion 46 and the male spline portion are engaged. The center axis of the sleeve 48 and the center axis of the output side disk 4 are aligned. The output side disk 4
The output gear 21a for taking out the rotation of is formed integrally with the sleeve 48 on the outer peripheral surface of the intermediate portion of the sleeve 48. The sleeve 48 is rotatably supported inside a partition wall 41 provided in the housing 43 by a pair of angular ball bearings 42, 42, respectively.
【００２４】又、上記円筒面部４５の内側には、保持器
４９により複数本のニードル５０、５０を転動自在に保
持して成る、上記ニードル軸受１６を配置している。ト
ロイダル型無段変速機への組み付け状態で、このニード
ル軸受１６を構成する上記各ニードル５０、５０の転動
面は、内輪軌道として機能する、上記入力軸１５ａの中
間部外周面に当接する。又、上記内側面側大径部４４と
円筒面部４５との間には係止溝１８を形成し、この係止
溝１８に止め輪１９を係止して、上記ニードル軸受１６
が上記円筒面部４５の内側から、上記内側面側大径部４
４側（図１〜２の左側）に抜け出る事を防止している。
尚、上記ニードル軸受１６が上記円筒面部４５の内側か
ら上記外側面側大径部４７側に抜け出る事は、上記保持
器４９と上記雌スプライン部４６の端縁との係合により
防止する。The needle bearing 16, which is rotatably held by the retainer 49, is disposed inside the cylindrical surface portion 45. In a state of being assembled to the toroidal type continuously variable transmission, the rolling surfaces of the needles 50, 50 constituting the needle bearing 16 abut on the outer peripheral surface of the intermediate portion of the input shaft 15a functioning as an inner raceway. A locking groove 18 is formed between the inner surface side large diameter portion 44 and the cylindrical surface portion 45, and a retaining ring 19 is locked in the locking groove 18 so that the needle bearing 16
From the inside of the cylindrical surface portion 45 to the inner surface side large diameter portion 4.
4 (left side in FIGS. 1 and 2).
The needle bearing 16 is prevented from coming out of the inside of the cylindrical surface portion 45 toward the outer surface side large diameter portion 47 by engagement of the retainer 49 with the edge of the female spline portion 46.
【００２５】上記円筒面部４５の内径Ｒ45及び上記外側
面側大径部４７の内径Ｒ47は、上記雌スプライン部４６
の溝底の外接円の直径Ｄ46よりも大きく（Ｒ45＞Ｄ46、
Ｒ47＞Ｄ46）している。従って、上記雌スプライン部４
６を構成する為の凹溝を前記貫通孔１７の内周面に形成
する作業を、ブローチ加工により能率良く行なう事がで
き、上記雌スプライン部４６を有する前記出力側ディス
ク４の製作費低減を図れる。尚、上記雌スプライン部４
６のスプラインモジュールは、前記スリーブ４８の端部
に形成した雄スプライン部の肉厚を確保して、これら両
スプライン部同士の係合部でのトルク容量を確保する面
から、１〜２程度にするのが好ましい。尚、スプライン
係合部の許容トルクは、モジュール、歯数、スプライン
長さにより決まる。更に、上記内側面側大径部４４の内
径Ｒ44は、上記円筒面部４５の内径Ｒ45よりも更に大き
く（Ｒ44＞Ｒ45）する事が望ましい。この様に内側面側
大径部４４の内径Ｒ44を大きくする事により、上記係止
溝１８に止め輪１９を係止する作業を容易に行なえる。The inner diameter R 47 of the inner diameter R 45 and the outer side surface side large diameter portion 47 of the cylindrical surface portion 45, the female spline portion 46
Larger than the diameter D 46 of the circumscribed circle at the bottom of the groove (R 45 > D 46 ,
R 47 > D 46 ). Therefore, the female spline portion 4
6 can be efficiently formed by broaching to form a concave groove on the inner peripheral surface of the through hole 17, and the production cost of the output side disk 4 having the female spline portion 46 can be reduced. I can do it. The female spline section 4
The spline module No. 6 has a thickness of about 1 to 2 from the viewpoint of securing the thickness of the male spline portion formed at the end of the sleeve 48 and securing the torque capacity at the engaging portion between the two spline portions. Is preferred. Note that the allowable torque of the spline engagement portion is determined by the module, the number of teeth, and the spline length. Further, it is desirable that the inner diameter R 44 of the inner-surface-side large-diameter portion 44 be larger than the inner diameter R 45 of the cylindrical surface portion 45 (R 44 > R 45 ). By increasing the inner diameter R 44 of the inner surface side large diameter portion 44 in this manner, it facilitates the task of engaging the retaining ring 19 into the engaging groove 18.
【００２６】上述の様な形状の貫通孔１７を中心部に形
成した前記出力側ディスク４と、前記保持器４９とニー
ドル５０、５０とから成るニードル軸受１６と、上記止
め輪１９とは、図３に示す様にトロイダル型無段変速機
に組み付ける以前に、図１に示す様に、このトロイダル
型無段変速機の組立完了後の位置関係に予め組み立てて
おく。そして、これら各部材４、４９、５０、１９を図
１に示す様に組み立てた状態で、これら構成各部材４、
４９、５０、１９が正しく機能するか否かを、これら構
成各部材４、４９、５０、１９を、図３に示す様にハウ
ジング４３内に組み付ける以前に確認しておく。そし
て、正しく機能する事を確認した出力側ディスクユニッ
トを、他の構成部材と共に、図３に示す様にハウジング
４３内に組み付けてトロイダル型無段変速機を構成す
る。従って、トロイダル型無段変速機全体を分解、再組
立する等の面倒な作業を要する事なく、トロイダル型無
段変速機の効率並びに耐久性を確保すべく、構成各部材
同士の位置関係を高精度に維持できる。尚、上記構成各
部材４、４９、５０、１９を組み立てて図１に示す様な
出力側ディスクユニットを構成した状態で、これら構成
各部材４、４９、５０、１９の表面には防錆油を塗布し
ておく。この防錆油としては、上記ハウジング４３内に
注入するトラクション油と混ざった場合にもこのトラク
ション油を劣化させる事のない、指定防錆油を使用する
事が好ましい。The output side disk 4 having a through hole 17 having the above-described shape at the center, the needle bearing 16 comprising the retainer 49 and the needles 50 and 50, and the retaining ring 19 are shown in FIG. Before assembling to the toroidal type continuously variable transmission as shown in FIG. 3, as shown in FIG. 1, the toroidal type continuously variable transmission is preliminarily assembled in a positional relationship after assembly is completed. Then, in a state where these members 4, 49, 50 and 19 are assembled as shown in FIG.
Whether the components 49, 50, and 19 function properly is checked before assembling these components 4, 49, 50, and 19 into the housing 43 as shown in FIG. Then, the output side disk unit, which has been confirmed to function properly, is assembled together with other components in the housing 43 as shown in FIG. 3 to constitute a toroidal type continuously variable transmission. Accordingly, the positional relationship between the constituent members is increased to secure the efficiency and durability of the toroidal-type continuously variable transmission without requiring troublesome work such as disassembling and reassembling the entire toroidal-type continuously variable transmission. Accuracy can be maintained. In a state where the above-mentioned constituent members 4, 49, 50, and 19 are assembled to form an output-side disk unit as shown in FIG. Is applied. As the rust preventive oil, it is preferable to use a designated rust preventive oil which does not deteriorate the traction oil even when mixed with the traction oil injected into the housing 43.
【００２７】尚、図３に示す様に、ハウジング４３内に
構成各部材を組み付けてトロイダル型無段変速機を構成
した状態で、各出力側ディスク４、４の内側面４ａ、４
ａと各入力側ディスク２Ａ、２Ｂの内側面２ａ、２ａと
の間には、それぞれ２個又は３個ずつのパワーローラ
８、８（図６〜１１参照）を挟持する。これら各内側面
４ａ、２ａ同士の間に挟持するパワーローラ８、８の数
が２個ずつである場合には、上記各入力側ディスク２
Ａ、２Ｂから上記各出力側ディスク４、４への動力伝達
時に、これら各出力側ディスク４、４の中心部に形成し
た前記貫通孔１７、１７の内周面形状が、楕円形に弾性
変形する。この様な変形に拘らず、前記ニードル軸受１
６を構成する各ニードル５０、５０の転動面の端部に過
大な荷重（エッヂロード）が加わる事を防止する為、上
記各ニードル５０、５０として、転動面に大きなクラウ
ニングを施したものを使用する事が好ましい。As shown in FIG. 3, in a state where the constituent members are assembled in a housing 43 to form a toroidal type continuously variable transmission, the inner surfaces 4a, 4a,
a and two or three power rollers 8, 8 (see FIGS. 6 to 11), respectively, between the input side disks 2A, 2B and the inner side surfaces 2a, 2a of the input side disks 2A, 2B. When the number of the power rollers 8, 8 sandwiched between the inner side surfaces 4a, 2a is two, each of the input side disks 2
When the power is transmitted from A, 2B to the output side disks 4, 4, the inner peripheral surfaces of the through holes 17, 17 formed in the center of the output side disks 4, 4 are elastically deformed into elliptical shapes. I do. Despite such deformation, the needle bearing 1
In order to prevent an excessive load (edge load) from being applied to the end of the rolling surface of each of the needles 50, 50 constituting 6, each of the needles 50, 50 is provided with a large crowning on the rolling surface. It is preferred to use
【００２８】次に、図４は、本発明の実施の形態の第２
例を示している。本例の構造は、各入力側ディスク２
Ａ、２Ｂから各出力側ディスク４、４への動力伝達時に
これら各出力側ディスク４、４の弾性変形を抑え、これ
ら各出力側ディスク４、４の耐久性を確保できる構造を
実現すべく考えたものである。即ち、上記動力伝達時に
上記各出力側ディスク４、４には、それぞれ２〜３個ず
つのパワーローラ８、８（図６〜１１参照）から大きな
スラスト荷重が加わる。上記各出力側ディスク４、４
は、このスラスト荷重に基づいて繰り返し弾性変形する
が、この弾性変形量が大きくなると、上記各出力側ディ
スク４、４の耐久性を確保する事が難しくなる。特に、
トロイダル型無段変速機が減速状態で運転される際に
は、上記各パワーローラ８、８の周面８ａ、８ａが上記
各出力側ディスク４、４の内側面４ａ、４ａの外周寄り
部分に当接する。これら各出力側ディスク４、４の軸方
向に関する肉厚は、上記外周寄り部分が最も小さく、上
記減速状態での運転時の弾性変形量が大きくなりがちで
ある。Next, FIG. 4 shows a second embodiment of the present invention.
An example is shown. The structure of this example is such that each input side disk 2
In order to realize a structure capable of suppressing the elastic deformation of each of the output disks 4 and 4 during power transmission from A and 2B to each of the output disks 4 and 4 and ensuring the durability of each of the output disks 4 and 4. It is a thing. That is, a large thrust load is applied to each of the output-side disks 4 and 4 from the power rollers 8 and 8 (see FIGS. 6 to 11) at the time of the power transmission. Each of the output side disks 4, 4
Are repeatedly elastically deformed on the basis of the thrust load, but when the amount of elastic deformation is large, it becomes difficult to ensure the durability of the output side disks 4, 4. Especially,
When the toroidal type continuously variable transmission is operated in a decelerating state, the peripheral surfaces 8a of the power rollers 8, 8 are located on the inner surfaces 4a, 4a of the output disks 4, 4 near the outer periphery. Abut The thickness of each of the output side disks 4 and 4 in the axial direction is the smallest at the portion near the outer periphery, and the amount of elastic deformation during operation in the deceleration state tends to increase.
【００２９】そこで、本例の場合には、前述した図１１
の構造と同様に、トロイダル型無段変速機の構造を、１
対の出力側ディスク４、４同士の間に仕切壁４１（図
３、１０）を設けない構造とすると共に、スリーブ４８
の中間部外周面に設けた出力歯車２１ｂの両側面外周寄
り部分を、上記各出力側ディスク４、４の外側面外周寄
り部分に当接させて、上記減速状態での運転時に上記各
出力側ディスク４、４の外周寄り部分の弾性変形を抑え
る様にしている。即ち、上記各出力側ディスク４、４の
外側面の内周寄り部分と外周寄り部分とを、上記出力歯
車２１ｂの側面の内周寄り部分と外周寄り部分とを、そ
れぞれ入力軸１５ａに対し直角方向に存在する単一平面
上に位置させて、これら各部分同士を互いに当接させて
いる。従って、上記各出力側ディスク４、４の外側面は
上記出力歯車２１ｂにより、それぞれの内径寄り部分を
支持（バックアップ）されるだけでなく、これら各出力
側ディスク４、４の軸方向に関する厚さが最も薄くなっ
ている（断面円弧状の内側面４ａの底部に対応する）部
分が、上記出力歯車２１ｂにより支持されている。従っ
て、特に上記各出力側ディスク４、４の肉厚を大きくし
なくても、トロイダル型無段変速機の運転時に於ける、
上記各出力側ディスク４、４の弾性変形を抑えて、これ
ら各出力側ディスク４、４の耐久性を確保する事が容易
になる。従って、トロイダル型無段変速機の軽量化と耐
久性確保との両立を図れる。Therefore, in the case of this example, FIG.
The structure of the toroidal type continuously variable transmission is
A partition wall 41 (FIGS. 3 and 10) is not provided between the pair of output side disks 4 and 4 and a sleeve 48 is provided.
The outer peripheral portions of both sides of the output gear 21b provided on the outer peripheral surface of the intermediate portion are brought into contact with the outer peripheral portions of the outer surfaces of the output disks 4 and 4 so that the output gears 21b are driven during the deceleration state. The elastic deformation of the portions of the disks 4, 4 near the outer periphery is suppressed. That is, a portion of the outer surface of each of the output-side disks 4 and 4 closer to the inner periphery and a portion of the outer periphery thereof are closer to the input shaft 15a at right angles to the inner and outer portions of the side surface of the output gear 21b. These parts are brought into contact with each other on a single plane existing in the direction. Therefore, the outer surface of each of the output side disks 4, 4 is not only supported (backed up) by the output gear 21b, but also has a thickness in the axial direction of each of the output side disks 4, 4. Is thinnest (corresponding to the bottom of the inner side surface 4a having an arc-shaped cross section) is supported by the output gear 21b. Therefore, even when the thickness of each of the output side disks 4 and 4 is not particularly increased, when the toroidal type continuously variable transmission is operated,
It is easy to suppress the elastic deformation of each of the output-side disks 4, 4 and ensure the durability of each of the output-side disks 4, 4. Accordingly, it is possible to achieve both reduction in weight and securing durability of the toroidal-type continuously variable transmission.
【００３０】次に、図５は、本発明の実施の形態の第３
例を示している。本例の場合も、上述した第２例の場合
と同様に、入力側ディスク２から出力側ディスク４への
動力伝達時に出力側ディスク４の弾性変形を抑え、この
出力側ディスク４の耐久性を確保できる構造を実現する
ものである。上述した第２例の場合、この様な構造を、
前述の図１１に示した様な、入力側ディスク２Ａ、２Ｂ
と出力側ディスク４、４とを２個ずつ設けた、所謂ダブ
ルキャビティ型のトロイダル型無段変速機に適用してい
るのに対して、本例の場合には、前述の図８に示した様
な、入力側ディスク２と出力側ディスク４とを１個ずつ
設けた、所謂シングルキャビティ型のトロイダル型無段
変速機に適用したものである。この為に本例の場合に
は、出力歯車２１ｃの外周寄り部分を幅広に形成し、こ
の外周寄り部分の片側面（図５の左側面）と、上記出力
側ディスク４の外側面で断面円弧状の内側面４ａの底部
に対応する部分とを当接させている。FIG. 5 shows a third embodiment of the present invention.
An example is shown. Also in the case of this example, similarly to the case of the above-described second example, elastic deformation of the output side disk 4 is suppressed when power is transmitted from the input side disk 2 to the output side disk 4, and the durability of the output side disk 4 is reduced. This realizes a structure that can be secured. In the case of the second example described above, such a structure is
Input side disks 2A, 2B as shown in FIG.
8 is applied to a so-called double-cavity toroidal-type continuously variable transmission in which two output disks 4 and 4 are provided. In the case of this example, however, this is shown in FIG. The present invention is applied to a so-called single cavity type toroidal type continuously variable transmission in which one input side disk 2 and one output side disk 4 are provided. For this reason, in the case of the present example, a portion near the outer periphery of the output gear 21c is formed wide, and one side surface (the left side surface in FIG. 5) of the portion near the outer periphery and the outer surface of the output side disk 4 have a circular cross section. The portion corresponding to the bottom of the arc-shaped inner side surface 4a is brought into contact.
【００３１】[0031]
【発明の効果】本発明のトロイダル型無段変速機用出力
側ディスクユニットは、以上に述べた通り構成され作用
する為、トロイダル型無段変速機の組立作業の能率化に
より、トロイダル型無段変速機の価格低減を図れる。The output disk unit for a toroidal-type continuously variable transmission according to the present invention is constructed and operates as described above. Therefore, the efficiency of the assembling work of the toroidal-type continuously variable transmission is improved. The cost of the transmission can be reduced.
【図１】本発明の実施の形態の第１例を、出力側ディス
クとニードル軸受と止め輪とを組み合わせた状態で示す
断面図。FIG. 1 is a sectional view showing a first example of an embodiment of the present invention in a state where an output side disk, a needle bearing, and a retaining ring are combined.
【図２】図１のＡ部拡大図。FIG. 2 is an enlarged view of a portion A in FIG.
【図３】出力側ディスクユニットをトロイダル型無段変
速機に組み込んだ状態で示す断面図。FIG. 3 is a sectional view showing a state in which the output side disk unit is incorporated in a toroidal type continuously variable transmission.
【図４】本発明の実施の形態の第２例を示す、図３と同
様の断面図。FIG. 4 is a sectional view similar to FIG. 3, showing a second example of the embodiment of the present invention;
【図５】同第３例を示す、図３と同様の断面図。FIG. 5 is a sectional view similar to FIG. 3, showing the third example;
【図６】従来から知られているトロイダル型無段変速機
の基本的構成を、最大減速時の状態で示す側面図。FIG. 6 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.
【図７】同じく最大増速時の状態で示す側面図。FIG. 7 is a side view showing a state at the time of maximum speed increase.
【図８】従来の具体的構造の第１例を示す断面図。FIG. 8 is a sectional view showing a first example of a conventional specific structure.
【図９】図８のＢ−Ｂ断面図。FIG. 9 is a sectional view taken along line BB of FIG. 8;
【図１０】従来の具体的構造の第２例を示す部分断面
図。FIG. 10 is a partial cross-sectional view showing a second example of a conventional specific structure.
【図１１】同第３例を示す部分断面図。FIG. 11 is a partial sectional view showing the third example.
１ 入力軸 ２ａ 内側面 ２、２Ａ、２Ｂ 入力側ディスク ３ 出力軸 ４ 出力側ディスク ４ａ 内側面 ５ 枢軸 ６ トラニオン ７ 変位軸 ８ パワーローラ ８ａ 周面 ９ 押圧装置 １０ カム板 １１ 保持器 １２ ローラ １３ 駆動側カム面 １４ 被駆動側カム面 １５、１５ａ 入力軸 １６ ニードル軸受 １７ 貫通孔 １８ 係止溝 １９ 止め輪 ２０ 鍔部 ２１、２１ａ、２１ｂ、２１ｃ 出力歯車 ２２ キー ２３ 支持板 ２４ 円孔 ２５ 支持軸部 ２６ 枢支軸部 ２７ ラジアルニードル軸受 ２８ ラジアルニードル軸受 ２９ スラスト玉軸受 ３０ スラストニードル軸受 ３１ 外輪 ３２ 駆動ロッド ３３ 駆動ピストン ３４ 駆動シリンダ ３５ 駆動軸 ３６ ラジアル軸受 ３７ ローディングナット ３８、３８ａ ボールスプライン ３９ 皿板ばね ４０ スラストニードル軸受 ４１ 仕切り壁 ４２ 玉軸受 ４３ ハウジング ４４ 内側面側大径部 ４５ 円筒面部 ４６ 雌スプライン部 ４７ 外側面側大径部 ４８ スリーブ ４９ 保持器 ５０ ニードル ５１ 皿板ばね Reference Signs List 1 input shaft 2a inner surface 2, 2A, 2B input disk 3 output shaft 4 output disk 4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 pressing device 10 cam plate 11 retainer 12 roller 13 drive Side cam surface 14 Driven cam surface 15, 15a Input shaft 16 Needle bearing 17 Through hole 18 Locking groove 19 Retaining ring 20 Flange 21, 21a, 21b, 21c Output gear 22 Key 23 Support plate 24 Circular hole 25 Support shaft Part 26 Pivot shaft part 27 Radial needle bearing 28 Radial needle bearing 29 Thrust ball bearing 30 Thrust needle bearing 31 Outer ring 32 Drive rod 33 Drive piston 34 Drive cylinder 35 Drive shaft 36 Radial bearing 37 Loading nut 38, 38a Ball spline 39 Plate Spring 40 Thrust Need Ball bearing 41 partition wall 42 ball bearing 43 housing 44 inner side large diameter part 45 cylindrical surface part 46 female spline part 47 outer side large diameter part 48 sleeve 49 retainer 50 needle 51 disc spring
───────────────────────────────────────────────────── フロントページの続き (72)発明者 藤波 誠 神奈川県藤沢市鵠沼神明一丁目５番50号 日本精工株式会社内 (72)発明者 加藤 寛 神奈川県藤沢市鵠沼神明一丁目５番50号 日本精工株式会社内 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Makoto Fujinami 1-5-150 Kugenuma Shinmei, Fujisawa-shi, Kanagawa Nippon Seiko Co., Ltd. (72) Inventor Hiroshi Kato 1-5-150 Kugenuma Shinmei, Fujisawa-shi, Kanagawa Nippon Seiko Co., Ltd.
Claims (3)
に軸方向に貫通する断面形状が円形である貫通孔を有
し、回転軸の中間部周囲にこの回転軸に対する回転を自
在に支持する出力側ディスクと、上記貫通孔の内側に配
置したラジアル転がり軸受と、この貫通孔の内周面に形
成した係止溝に係止し、このラジアル転がり軸受がこの
貫通孔から抜け出る事を防止する止め輪とを、トロイダ
ル型無段変速機への組み付け以前に、このトロイダル型
無段変速機の組立完了後の位置関係に予め組み立てたト
ロイダル型無段変速機用出力側ディスクユニット。1. An inner surface having a concave surface having an arcuate cross section, a central portion having a through hole having a circular cross section penetrating in the axial direction, and being rotatable around the intermediate portion of the rotary shaft with respect to the rotary shaft. An output side disk to be supported, a radial rolling bearing disposed inside the through hole, and a locking groove formed on an inner peripheral surface of the through hole to prevent the radial rolling bearing from coming out of the through hole. An output-side disk unit for a toroidal-type continuously variable transmission in which a retaining ring to be prevented is assembled in a positional relationship after assembly of the toroidal-type continuously variable transmission before assembling the toroidal-type continuously variable transmission.
面寄り部分に設けられ、ラジアル転がり軸受の外輪軌道
として機能する円筒面部と、軸方向中間部の外側面寄り
部分に設けられた雌スプライン部と、内側面側の軸方向
端部に設けられた内側面側大径部と、外側面側の軸方向
端部に設けられた外側面側大径部とを備え、上記円筒面
部及び外側面側大径部の内径は、上記雌スプライン部の
溝底の外接円の直径よりも大きい、請求項１に記載した
トロイダル型無段変速機用出力側ディスクユニット。2. An inner peripheral surface of the through hole is provided at a portion closer to an inner surface of an intermediate portion in the axial direction, and is provided at a cylindrical surface portion functioning as an outer ring raceway of the radial rolling bearing, and at a portion closer to an outer surface of the intermediate portion in the axial direction. A female spline portion, an inner surface-side large-diameter portion provided at an inner surface-side axial direction end, and an outer surface-side large-diameter portion provided at an outer surface-side axial end portion; 2. The output side disk unit for a toroidal-type continuously variable transmission according to claim 1, wherein the inner diameter of the cylindrical surface portion and the outer surface side large diameter portion is larger than the diameter of a circumscribed circle at the groove bottom of the female spline portion.
機への組み付け状態に於いて出力側ディスクの外側面に
対向する部分には、この出力側ディスクと同期して回転
する出力歯車を回転自在に支持し、この出力歯車の一部
で上記出力側ディスクの肉厚が最も薄くなっている部分
に対向する部分は、この出力側ディスクの外側面に当接
させる、請求項１〜２の何れかに記載したトロイダル型
無段変速機用出力側ディスクユニット。3. An output gear that rotates in synchronization with the output-side disk is provided at a portion opposite to the outer surface of the output-side disk in a state where the intermediate portion of the rotation shaft is mounted on the toroidal-type continuously variable transmission. 3. A part of the output gear, which is rotatably supported, and a part of the output gear facing a part where the thickness of the output disk is the thinnest is brought into contact with an outer surface of the output disk. The output side disk unit for a toroidal type continuously variable transmission according to any one of the above.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33554097A JP3740812B2 (en) | 1997-12-05 | 1997-12-05 | Output side disk unit for toroidal type continuously variable transmission |
| US09/277,959 US6238318B1 (en) | 1997-11-21 | 1999-03-29 | Power roller unit and output disc unit for torodial type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33554097A JP3740812B2 (en) | 1997-12-05 | 1997-12-05 | Output side disk unit for toroidal type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11166605A true JPH11166605A (en) | 1999-06-22 |
| JP3740812B2 JP3740812B2 (en) | 2006-02-01 |
Family
ID=18289726
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33554097A Expired - Fee Related JP3740812B2 (en) | 1997-11-21 | 1997-12-05 | Output side disk unit for toroidal type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3740812B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6473248B1 (en) | 1999-09-21 | 2002-10-29 | Matsushita Electronics Industrial Co. Ltd. | Method for manufacturing an optical pickup |
| JP2007292145A (en) * | 2006-04-21 | 2007-11-08 | Nsk Ltd | Toroidal continuously variable transmission |
| DE10232966B4 (en) * | 2001-07-19 | 2010-06-02 | Nsk Ltd. | Stepless toroidal transmission |
| JP2015090208A (en) * | 2013-11-07 | 2015-05-11 | 日本精工株式会社 | Toroidal type non-stage transmission |
| JP2015094456A (en) * | 2013-11-14 | 2015-05-18 | 日本精工株式会社 | Toroidal type non-stage transmission |
| US9765862B2 (en) | 2015-08-07 | 2017-09-19 | Kabushiki Kaisha F.C.C. | Continuously variable transmission |
-
1997
- 1997-12-05 JP JP33554097A patent/JP3740812B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6473248B1 (en) | 1999-09-21 | 2002-10-29 | Matsushita Electronics Industrial Co. Ltd. | Method for manufacturing an optical pickup |
| DE10232966B4 (en) * | 2001-07-19 | 2010-06-02 | Nsk Ltd. | Stepless toroidal transmission |
| JP2007292145A (en) * | 2006-04-21 | 2007-11-08 | Nsk Ltd | Toroidal continuously variable transmission |
| JP2015090208A (en) * | 2013-11-07 | 2015-05-11 | 日本精工株式会社 | Toroidal type non-stage transmission |
| JP2015094456A (en) * | 2013-11-14 | 2015-05-18 | 日本精工株式会社 | Toroidal type non-stage transmission |
| US9765862B2 (en) | 2015-08-07 | 2017-09-19 | Kabushiki Kaisha F.C.C. | Continuously variable transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3740812B2 (en) | 2006-02-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7195576B2 (en) | Continuously variable transmission apparatus | |
| JP3885650B2 (en) | Continuously variable transmission | |
| JP2000205359A (en) | Half troidal type continuously variable transmission | |
| US6375595B1 (en) | Toroidal type continuously variable transmission | |
| JP3740812B2 (en) | Output side disk unit for toroidal type continuously variable transmission | |
| JPH08135747A (en) | Toroidal type continuously variable transmission | |
| JP3783626B2 (en) | Toroidal continuously variable transmission | |
| JP3870594B2 (en) | Toroidal continuously variable transmission | |
| JP3899745B2 (en) | Toroidal continuously variable transmission | |
| JPH1151135A (en) | Toroidal type continuously variable transmission | |
| JP3674264B2 (en) | Continuously variable transmission | |
| JP3829512B2 (en) | Input side disk unit for toroidal type continuously variable transmission | |
| JP3424560B2 (en) | Input disk unit for toroidal type continuously variable transmission | |
| JP3627459B2 (en) | Toroidal continuously variable transmission | |
| JP3603544B2 (en) | Toroidal continuously variable transmission | |
| JP3503393B2 (en) | Toroidal type continuously variable transmission | |
| JP3458495B2 (en) | Toroidal type continuously variable transmission | |
| JP3743147B2 (en) | Toroidal continuously variable transmission | |
| JP3617265B2 (en) | Toroidal continuously variable transmission | |
| JP4032549B2 (en) | Toroidal continuously variable transmission | |
| JP4362858B2 (en) | Ball spline of toroidal type continuously variable transmission | |
| JP4110645B2 (en) | Toroidal continuously variable transmission | |
| JP4144166B2 (en) | Continuously variable transmission for pumping pump or generator | |
| JPH08135746A (en) | Toroidal type continuously variable transmission | |
| JP4026237B2 (en) | Toroidal continuously variable transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20040921 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20050802 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20050922 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20051018 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20051031 |
|
| R150 | Certificate of patent (=grant) or registration of utility model |
Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20081118 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20091118 Year of fee payment: 4 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20101118 Year of fee payment: 5 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20111118 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20111118 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20121118 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20121118 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20131118 Year of fee payment: 8 |
|
| LAPS | Cancellation because of no payment of annual fees |