JPH07229549A - Thrust ball bearing for power roller - Google Patents
Thrust ball bearing for power rollerInfo
- Publication number
- JPH07229549A JPH07229549A JP2141594A JP2141594A JPH07229549A JP H07229549 A JPH07229549 A JP H07229549A JP 2141594 A JP2141594 A JP 2141594A JP 2141594 A JP2141594 A JP 2141594A JP H07229549 A JPH07229549 A JP H07229549A
- Authority
- JP
- Japan
- Prior art keywords
- power roller
- balls
- outer ring
- degrees
- inner ring
- 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
Landscapes
- Friction Gearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明に係るパワーローラ用ス
ラスト玉軸受は、例えばトロイダル型無段変速機を構成
するパワーローラに加わるスラスト荷重を支承するのに
利用する。BACKGROUND OF THE INVENTION The thrust ball bearing for a power roller according to the present invention is used for bearing a thrust load applied to a power roller constituting a toroidal type continuously variable transmission, for example.
【０００２】[0002]
【従来の技術】自動車用変速機、或は各種産業機械用の
変速機として、図３〜４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、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
ングの内面、或はこのケーシング内に設けられた支持ブ
ラケットには、前記入力軸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が設けられている。2. Description of the Related Art The use of a toroidal type continuously variable transmission as schematically shown in FIGS. 3 and 4 has been studied as a transmission for an automobile or a transmission for various industrial machines. This toroidal type continuously variable transmission supports an input side disk 2 concentrically with an input shaft 1 and an output side disk at an end of an output shaft 3 as disclosed in Japanese Utility Model Laid-Open No. 62-71465. 4 is fixed. An inner surface of a casing accommodating the toroidal type continuously variable transmission, or a support bracket provided in the casing, has pivots 5 and 5 in a twisted position with respect to the input shaft 1 and the output shaft 3 as a center. Swing trunnions 6, 6 are provided.
【０００３】各トラニオン６、６は、両端部外側面に前
記枢軸５、５を設けている。又、各トラニオン６、６の
中心部には変位軸７、７の基端部を支持し、上記枢軸
５、５を中心として各トラニオン６、６を揺動させる事
により、各変位軸７、７の傾斜角度の調節を自在として
いる。各トラニオン６、６に支持された変位軸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、各パワーローラ８、８を、前記入
力側、出力側両ディスク２、４の間に挟持している。The trunnions 6, 6 are provided with the pivots 5, 5 on the outer surfaces of both ends. Further, the base ends of the displacement shafts 7, 7 are supported on the central portions of the trunnions 6, 6, and the trunnions 6, 6 are swung about the pivot shafts 5, 5, so that the displacement shafts 7, The inclination angle of 7 can be freely adjusted. Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by the trunnions 6, 6, respectively. The power rollers 8, 8 are sandwiched between the input side and output side disks 2, 4.
【０００４】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は、それぞれ断面が、ほぼ上
記枢軸５を中心とする円弧形の凹面をなしている。そし
て、球面状の凸面に形成された各パワーローラ８、８の
周面８ａ、８ａは、前記内側面２ａ、４ａに当接させて
いる。The inner surfaces 2a, 4a of the input-side and output-side disks 2, 4 facing each other have arcuate concave surfaces whose cross sections are substantially centered on the pivot shaft 5, respectively. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed on the spherical convex surface are in contact with the inner side surfaces 2a, 4a.
【０００５】前記入力軸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、前記入力側ディスク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
により保持された複数個（例えば４個）のローラ１２、
１２とから構成されている。前記カム板１０の片側面
（図３〜４の左側面）には、円周方向に亙る凹凸面であ
るカム面１３を形成し、又、前記入力側ディスク２の外
側面（図３〜４の右側面）にも、同様のカム面１４を形
成している。そして、前記入力軸１の中心に対して放射
方向の軸を中心とする複数個のローラ１２、１２を、回
転自在に支持している。A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the pressing device 9 causes the input side disk 2 to face the output side disk 4 and elastically moves. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1, and a retainer 11.
A plurality of (for example, four) rollers 12 held by
It is composed of 12 and. On one side surface (left side surface of FIGS. 3 to 4) of the cam plate 10, a cam surface 13 which is a concavo-convex surface extending in the circumferential direction is formed, and an outer side surface of the input side disk 2 (FIGS. 3 to 4). A similar cam surface 14 is also formed on the right side surface of the. Then, a plurality of rollers 12, 12 having a radial axis as a center with respect to the center of the input shaft 1 are rotatably supported.
【０００６】上述の様に構成され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、カム面１３によって複数個のローラ１２、１
２が、入力側ディスク２の外側面に形成したカム面１４
に押圧される。この結果、前記入力側ディスク２が前記
複数のパワーローラ８、８に押圧されると同時に、前記
１対のカム面１３、１４と複数個のローラ１２、１２と
の噛合に基づいて、前記入力側ディスク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 toroidal type continuously variable transmission constructed as described above is used, when the cam plate 10 rotates as the input shaft 1 rotates, the cam surface 13 causes the plurality of rollers 12, 1 to rotate.
2 is a cam surface 14 formed on the outer surface of the input side disk 2.
Is pressed by. As a result, the input side disk 2 is pressed by the plurality of power rollers 8 and at the same time, the input side disk 2 is input based on the engagement between the pair of cam surfaces 13 and 14 and the plurality of rollers 12 and 12. The side disc 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 and the output shaft 3 fixed to the output side disk 4 rotates.
【０００７】入力軸１と出力軸３との回転速度を変える
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、枢軸５、５を中心として各トラニオン６、６
を揺動させ、各パワーローラ８、８の周面８ａ、８ａが
図３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、各変位軸７、７を傾斜さ
せる。When the rotational speeds of the input shaft 1 and the output shaft 3 are changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions 6, 6 centering on the pivot shafts 5, 5 are used.
3, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are located near the center of the inner side surface 2a of the input side disk 2 and near the outer peripheral side of the inner side surface 4a of the output side disk 4, as shown in FIG. The displacement shafts 7, 7 are tilted so as to abut with and respectively.
【０００８】反対に、増速を行なう場合には、各パワー
ローラ８、８の周面８ａ、８ａが図４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、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３と図４との中間にすれば、入力軸
１と出力軸３との間で、中間の変速比を得る事ができ
る。On the other hand, when increasing the speed, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are, as shown in FIG. 4, a portion near the outer periphery of the inner surface 2a of the input side disk 2 and the output side disk. The displacement shafts 7, 7 are tilted so as to abut the center portion of the inner side surface 4a of the shaft 4. Each displacement axis 7,
If the inclination angle of 7 is set to an intermediate value between FIG. 3 and FIG. 4, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.
【０００９】図３〜４には、トロイダル型無段変速機の
基本構造のみを示しているが、自動車用変速機等として
より具体化した構造も、例えば実願昭６１−８７５２３
号（実開昭６２−１９９５５７号）のマイクロフィルム
に記載されている様に、従来から種々知られている。3 to 4 show only the basic structure of the toroidal type continuously variable transmission, a structure more concretely embodied as a transmission for automobiles is also disclosed in, for example, Japanese Utility Model Application No. 61-87523.
As described in the microfilm of Japanese Utility Model Publication No. Sho 62-199557, various types are conventionally known.
【００１０】ところで、上述の様なトロイダル型無段変
速機の運転時に上記各パワーローラ８、８は、入力側デ
ィスク２及び出力側ディスク４からのスラスト荷重を受
けつつ、高速で回転する。この為、これら各パワーロー
ラ８、８と前記各トラニオン６、６との間には、図５に
示す様にスラスト玉軸受１５を設けている。By the way, during operation of the toroidal type continuously variable transmission as described above, the power rollers 8, 8 rotate at a high speed while receiving the thrust load from the input side disk 2 and the output side disk 4. Therefore, thrust ball bearings 15 are provided between the power rollers 8, 8 and the trunnions 6, 6 as shown in FIG.
【００１１】上記スラスト玉軸受１５は、内輪として機
能する上記パワーローラ８と、複数の玉１６、１６と、
これら複数の玉１６、１６を転動自在に保持する為の保
持器２０と、外輪１７とから構成されている。尚、上記
パワーローラ８、玉１６、１６、外輪１７は、それぞれ
軸受用鋼、或はセラミックにより形成されている。又、
上記パワーローラ８の軸方向片面（図５の上面）には内
輪軌道１８を、上記外輪１７の軸方向片面（図５の下
面）で上記内輪軌道１８と対向する部分には外輪軌道１
９を、それぞれ形成している。これら各軌道１８、１９
は、それぞれ断面が円弧形で全体が円環状とされてい
る。上記各玉１６、１６の転動面は、これら内輪軌道１
８と外輪軌道１９とに転接する。The thrust ball bearing 15 includes the power roller 8 functioning as an inner ring, a plurality of balls 16 and 16,
It is composed of a retainer 20 for holding the plurality of balls 16 and 16 in a rollable manner, and an outer ring 17. The power roller 8, balls 16, 16 and outer ring 17 are each made of bearing steel or ceramic. or,
An inner ring raceway 18 is provided on one axial surface of the power roller 8 (upper surface in FIG. 5), and an outer ring raceway 1 is provided on a portion of the outer ring 17 on one axial surface (lower surface of FIG. 5) facing the inner ring raceway 18.
9 are formed respectively. Each of these trajectories 18, 19
Has an arc-shaped cross section and has an annular shape as a whole. The rolling surfaces of the balls 16, 16 are the inner ring raceways 1
8 and the outer ring raceway 19 are brought into contact with each other.
【００１２】又、前記保持器２０は、金属或は合成樹脂
により円輪状に造られた主体２１を有する。この主体２
１の直径方向中間部で円周方向等間隔位置には、円形の
ポケット２２、２２を形成し、これら各ポケット２２、
２２に上記玉１６、１６を、１個ずつ、転動自在に保持
している。更に、外輪１７は、ニードル軸受、滑り軸受
等のスラスト軸受２３を介して、前記各トラニオン６の
内側面に突き当てられている。このスラスト軸受２３
は、上記外輪１７が前記トラニオン６に対し変位する事
を許容する。即ち、前記入力側、出力側両ディスク２、
４の振れ等に対して前記パワーローラ８を追従させるべ
く、前記変位軸７は基端部を上記トラニオン６に回転自
在に支持すると共に、その先端部をこの基端部に対し偏
心させ、この先端部に上記パワーローラ８を回転自在に
支持している。そして、上記追従の際には上記外輪１７
がトラニオン６に対し変位するので、この変位に要する
力を低減し、パワーローラ８の相手部材に対する追従性
を向上させるべく、上記スラスト軸受２３を設けてい
る。Further, the cage 20 has a main body 21 made of metal or synthetic resin in the shape of a circular ring. This subject 2
Circular pockets 22 and 22 are formed at equal intervals in the circumferential direction at the diametrical intermediate portion of 1, and these pockets 22 and 22 are formed.
22 holds the balls 16, 16 one by one so that they can roll. Further, the outer ring 17 is abutted against the inner surface of each trunnion 6 via a thrust bearing 23 such as a needle bearing or a slide bearing. This thrust bearing 23
Allows the outer ring 17 to be displaced with respect to the trunnion 6. That is, both the input side and output side disks 2,
4, the displacement shaft 7 rotatably supports the base end portion of the trunnion 6 in order to make the power roller 8 follow the runout and the like, and the tip end portion of the displacement shaft 7 is eccentric with respect to the base end portion. The power roller 8 is rotatably supported at the tip. Then, when following the above, the outer ring 17
Is displaced with respect to the trunnion 6, so that the thrust bearing 23 is provided in order to reduce the force required for this displacement and improve the followability of the power roller 8 to the mating member.
【００１３】トロイダル型無段変速機の運転時に、前記
スラスト玉軸受１５は、前記各パワーローラ８、８に加
わるスラスト荷重を支承しつつ、高速で回転する。この
為、従来から考えられていたトロイダル型無段変速機用
のスラスト玉軸受１５の接触角（玉１６、１６から各軌
道に加わる荷重の方向とスラスト軸受１５の中心軸に垂
直な平面とのなす角度）は、図６に示す様に、９０度と
していた。尚、２４は、スラスト玉軸受１５に潤滑油を
供給する給油孔である。During operation of the toroidal type continuously variable transmission, the thrust ball bearing 15 rotates at high speed while bearing the thrust load applied to the power rollers 8, 8. Therefore, the contact angle of the thrust ball bearing 15 for the toroidal type continuously variable transmission that has been conventionally considered (the direction of the load applied from the balls 16, 16 to each track and the plane perpendicular to the central axis of the thrust bearing 15) The angle formed was 90 degrees as shown in FIG. Reference numeral 24 is an oil supply hole for supplying lubricating oil to the thrust ball bearing 15.
【００１４】[0014]
【発明が解決しようとする課題】ところが、実際にトロ
イダル型無段変速機に組み込まれてパワーローラ８を支
承するスラスト玉軸受の場合には、次のの様な解決
すべき点がある。However, in the case of the thrust ball bearing which is actually incorporated in the toroidal type continuously variable transmission to support the power roller 8, there are the following points to be solved.
【００１５】 入力側ディスク２及び出力側ディスク
４からパワーローラ８に加わる荷重の作用点と、各玉１
６、１６の転動面と内輪軌道１８との接触点とのラジア
ル方向に亙る距離が必ずしも短くない。この為、上記作
用点からパワーローラ８に加わる荷重によって、このパ
ワーローラ８に大きな曲げ応力が加わり易い。即ち、ト
ロイダル型無段変速機の運転時には、パワーローラ８の
周面８ａの一部で上記各ディスク２、４の内側面２ａ、
４ａとの当接部に荷重Ｆ0 が、この周面８ａに対し垂直
方向に加わる。そして、この荷重Ｆ0 のうちのスラスト
方向の分力Ｆ1 に基づき上記パワーローラ８に、上記接
触点を中心とする曲げ応力が加わる。The point of action of the load applied from the input side disc 2 and the output side disc 4 to the power roller 8 and each ball 1
The distance between the rolling surfaces of 6, 16 and the contact point between the inner ring raceway 18 and the radial direction is not necessarily short. Therefore, a large bending stress is likely to be applied to the power roller 8 due to the load applied to the power roller 8 from the above action point. That is, when the toroidal type continuously variable transmission is in operation, a part of the peripheral surface 8a of the power roller 8 causes the inner surface 2a of each of the disks 2 and 4,
A load F 0 is applied to the contact portion with 4a in a direction perpendicular to the peripheral surface 8a. A bending stress centered on the contact point is applied to the power roller 8 based on the thrust component F 1 of the load F 0 .
【００１６】この曲げ応力の大きさは、上記作用点と接
触点とのラジアル方向に亙る距離Ｌ0 に比例する。従来
のパワーローラ用玉軸受の場合には、この距離Ｌ0 が必
ずしも小さくなかった。この為、上記曲げ応力が比較的
大きくなり、長期間に亙る使用に伴って上記パワーロー
ラ８に、亀裂等の損傷を発生する可能性がある。The magnitude of the bending stress is proportional to the distance L 0 between the point of action and the contact point in the radial direction. In the case of the conventional ball bearing for power rollers, this distance L 0 was not necessarily small. For this reason, the bending stress becomes relatively large, and there is a possibility that the power roller 8 may be damaged such as a crack with use for a long period of time.
【００１７】 トロイダル型無段変速機の運転時に上
記パワーローラ８にラジアル方向の荷重が加わると、こ
のパワーローラ８がラジアル方向に変位し易い。即ち、
パワーローラ８の周面８ａには、変速に伴う変位軸７の
変位、或は組立精度や自重に基づいて、スラスト方向の
荷重だけでなくラジアル方向の荷重が加わる。そして、
このラジアル荷重に基づいて上記パワーローラ８が、ラ
ジアル方向に変位する。特に、従来の様に玉１６、１６
の接触角が９０度であると、上記ラジアル荷重に基づく
パワーローラ８の変位を阻止する力が弱く、図７に示す
様にこのパワーローラ８が、外輪１７に対してラジアル
方向に変位してしまう。When a load is applied to the power roller 8 in the radial direction during operation of the toroidal type continuously variable transmission, the power roller 8 is easily displaced in the radial direction. That is,
On the peripheral surface 8a of the power roller 8, not only the load in the thrust direction but also the load in the radial direction is applied on the basis of the displacement of the displacement shaft 7 due to the shift, or the assembly accuracy and the self-weight. And
The power roller 8 is displaced in the radial direction based on this radial load. In particular, balls 16 and 16 as in the past
If the contact angle is 90 degrees, the force for preventing the displacement of the power roller 8 due to the radial load is weak, and the power roller 8 is displaced in the radial direction with respect to the outer ring 17 as shown in FIG. I will end up.
【００１８】この結果、上記玉１６、１６の接触角θ
が、円周方向の或る位置（図７の右側位置）では９０度
を越え、別の位置（同左側位置）では９０度未満となっ
てしまう。この様に、玉の接触角θが９０度を境に変化
すると、玉が自転しつつ公転する通常の運動だけでな
く、接触角θを連続的に変化させる為に非常に複雑な運
動をする。そして、この様な複雑な運動に、玉のジャイ
ロモーメントやスピンによる影響が加わり、玉１６、１
６や内輪軌道１８及び外輪軌道１９の摩耗や疲れ寿命に
悪影響を及ぼし、スラスト玉軸受の耐久性が損なわれて
しまう。本発明のパワーローラ用スラスト玉軸受は、こ
の様な事情に鑑みて発明したものである。As a result, the contact angle θ of the balls 16, 16
However, it exceeds 90 degrees at a certain position in the circumferential direction (the right side position in FIG. 7), and is less than 90 degrees at another position (the same left side position). In this way, when the contact angle θ of the ball changes at 90 degrees, not only the normal motion of the ball revolving around its axis but also a very complicated motion for continuously changing the contact angle θ. . Then, due to the influence of the gyro moment and spin of the ball, the ball 16, 1
6 and the inner ring raceway 18 and the outer ring raceway 19 are adversely affected by wear and fatigue life, and the durability of the thrust ball bearing is impaired. The thrust ball bearing for a power roller of the present invention was invented in view of such circumstances.
【００１９】[0019]
【課題を解決する為の手段】本発明のパワーローラ用ス
ラスト玉軸受は、トロイダル型無段変速機に組み込まれ
たパワーローラの軸方向片面に形成された、断面が円弧
状で全体が円環状の内輪軌道と、上記パワーローラと同
心に配置された外輪と、この外輪の軸方向片面で上記内
輪軌道と対向する部分に形成された、断面が円弧状で全
体が円環状の外輪軌道と、それぞれの転動面を上記内輪
軌道及び外輪軌道に当接させた複数の玉とを備え、次の
の条件を満たす。 上記複数の玉の接触角が９０度から外れている。 上記接触角が９０度から外れる方向は、パワーロー
ラの周面に加わる荷重の作用点と、上記玉の転動面と上
記内輪軌道との接触点との距離が、上記接触角が９０度
である場合に比べて短くなる方向である。A thrust ball bearing for a power roller according to the present invention is formed on one side in the axial direction of a power roller incorporated in a toroidal type continuously variable transmission, and has an arcuate cross section and an annular shape as a whole. Inner ring raceway, an outer ring arranged concentrically with the power roller, an outer ring raceway formed in a portion facing the inner ring raceway on one axial surface of the outer ring, the outer ring raceway having a circular arc shape in cross section, Each of the rolling surfaces is provided with a plurality of balls abutting on the inner ring raceway and the outer ring raceway, and the following conditions are satisfied. The contact angles of the plurality of balls deviate from 90 degrees. In the direction in which the contact angle deviates from 90 degrees, the distance between the point of action of the load applied to the peripheral surface of the power roller and the contact point between the rolling surface of the ball and the inner ring raceway is 90 degrees. It tends to be shorter than in some cases.
【００２０】[0020]
【作用】上述の様に構成される本発明のパワーローラ用
スラスト玉軸受の場合には、パワーローラがラジアル荷
重に基づいてラジアル方向に変位しにくくなる。従っ
て、玉の運動が複雑になりにくく、玉や外輪、内輪両軌
道の摩耗や疲れ寿命に悪影響を及ぼしにくい。In the thrust ball bearing for a power roller of the present invention constructed as described above, the power roller is less likely to be displaced in the radial direction based on the radial load. Therefore, the movement of the ball is not complicated, and the wear of the ball, the outer ring, and the inner ring raceways and the fatigue life are unlikely to be adversely affected.
【００２１】又、パワーローラに加わる荷重の作用点
と、各玉の転動面と内輪軌道との接触点との距離が短く
なる為、パワーローラとディスクとの当接部に加わる荷
重に基づく上記パワーローラに加わる曲げ応力が小さく
なる。この結果、上記パワーローラの耐久性向上を図れ
る。Further, since the distance between the point of action of the load applied to the power roller and the point of contact between the rolling surface of each ball and the inner ring raceway becomes short, it is based on the load applied to the contact portion between the power roller and the disk. The bending stress applied to the power roller is reduced. As a result, the durability of the power roller can be improved.
【００２２】[0022]
【実施例】図１は、本発明の第一実施例を示している。
尚、本発明のパワーローラ用スラスト玉軸受の特徴は、
玉の接触角を９０度からずらせる事で、耐久性を向上さ
せる点にあり、その他の構成及び作用は、前述したトロ
イダル型無段変速機に組み込まれている、従来から知ら
れたパワーローラ用スラスト玉軸受と同様である。よっ
て、重複する説明を省略し、本発明の特徴部分を中心に
説明する。FIG. 1 shows a first embodiment of the present invention.
The features of the thrust ball bearing for a power roller of the present invention are as follows:
By shifting the contact angle of the balls from 90 degrees, the durability is improved, and other configurations and functions are the conventionally known power roller incorporated in the toroidal type continuously variable transmission described above. It is the same as the thrust ball bearing. Therefore, overlapping description will be omitted and the description will focus on the characteristic part of the present invention.
【００２３】パワーローラ８の片面（図１の上面）に形
成した内輪軌道１８の直径は、外輪１７の片面（図１の
下面）に形成した外輪軌道１９の直径よりも少し小さく
している。従って、これら内輪軌道１８と外輪軌道１９
との間に転動自在に設けた複数の玉１６、１６の接触角
θは、９０度よりも大きくなっている。この結果、接触
角θが９０度（図６参照）である場合と比較した場合、
各玉１６、１６の転動面と上記内輪軌道１８との当接位
置Ｔ18、Ｔ18は直径方向外側に、転動面と上記外輪軌道
１９との当接位置Ｔ19、Ｔ19は直径方向内側に、それぞ
れ位置する。The diameter of the inner ring raceway 18 formed on one surface of the power roller 8 (upper surface in FIG. 1) is made slightly smaller than the diameter of the outer ring raceway 19 formed on one surface of the outer ring 17 (lower surface in FIG. 1). Therefore, these inner ring raceway 18 and outer ring raceway 19
The contact angle θ of the plurality of balls 16, 16 rotatably provided between and is greater than 90 degrees. As a result, when compared with the case where the contact angle θ is 90 degrees (see FIG. 6),
The contact positions T 18 , T 18 between the rolling surfaces of the balls 16, 16 and the inner ring raceway 18 are diametrically outward, and the contact positions T 19 , T 19 between the rolling surfaces and the outer ring raceway 19 are the diameter. Located inside the direction, respectively.
【００２４】尚、本実施例の場合には、入力側、出力
側、両ディスク２、４の内側面２ａ、４ａ（図３〜４）
とパワーローラ８の周面８ａとの当接位置ＴF は、上記
各玉１６、１６の転動面と上記内輪軌道１８との当接位
置Ｔ18よりも直径方向外方に存在する。従って、この当
接位置ＴF と一致する荷重の作用点と、上記当接位置Ｔ
18とのラジアル方向に亙る距離Ｌ1 は、上記接触角θが
９０度である場合の距離Ｌ0 よりも小さい（Ｌ1 ＜Ｌ
0 ）。又、上記転動面と上記外輪軌道１９との複数の当
接位置Ｔ19、Ｔ19同士を結ぶ円弧の半径ｒ19は、上記接
触角θが９０度である場合の半径Ｒ19よりも小さい（ｒ
19＜Ｒ19）。In the case of the present embodiment, the input side, the output side, the inner side surfaces 2a, 4a of both disks 2, 4 (FIGS. 3 to 4).
And a contact position T F between the power roller 8 and the peripheral surface 8 a of the power roller 8 are located diametrically outward from a contact position T 18 between the rolling surfaces of the balls 16 and the inner ring raceway 18. Therefore, the point of action of the load that matches the contact position T F and the contact position T F
The distance L 1 with respect to 18 in the radial direction is smaller than the distance L 0 when the contact angle θ is 90 degrees (L 1 <L
0 ). The radius r 19 of the arc connecting the plurality of contact positions T 19 , T 19 between the rolling surface and the outer ring raceway 19 is smaller than the radius R 19 when the contact angle θ is 90 degrees. (R
19 <R 19 ).
【００２５】上述の様に構成される本発明のパワーロー
ラ用スラスト玉軸受の場合には、パワーローラ８がラジ
アル荷重に基づいてラジアル方向に変位しにくくなる。
即ち、上記接触角θが９０度を越えている為、何れの方
向のラジアル荷重を受けた場合でも、一部の玉１６がこ
のラジアル荷重を支承し、上記パワーローラ８がラジア
ル方向に変位する事を阻止する。例えば、図１で左から
右に向いたラジアル荷重が作用した場合には、同図で左
側の玉１６がこのラジアル荷重を支承する。この結果、
各玉１６、１６の運動が複雑になりにくく、玉１６や外
輪、内輪両軌道１９、１８の摩耗や疲れ寿命に悪影響を
及ぼしにくい。In the case of the thrust ball bearing for a power roller of the present invention constructed as described above, the power roller 8 is less likely to be displaced in the radial direction based on the radial load.
That is, since the contact angle θ exceeds 90 degrees, no matter which direction the radial load is applied to, some balls 16 support the radial load and the power roller 8 is displaced in the radial direction. Prevent things. For example, when a radial load directed from left to right in FIG. 1 is applied, the ball 16 on the left side in FIG. 1 bears this radial load. As a result,
The movements of the balls 16 and 16 are unlikely to be complicated, and the wear and fatigue life of the balls 16 and outer and inner ring raceways 19 and 18 are less likely to be adversely affected.
【００２６】又、パワーローラ８に加わる荷重の作用点
（ＴF ）と、各玉１６、１６の転動面と内輪軌道１８と
の接触点（Ｔ18）とのラジアル方向に亙る距離Ｌ1 が上
記接触角θが９０度である場合のラジアル方向に亙る距
離Ｌ0 よりも短くなる為、上記パワーローラ８の周面８
ａと前記各ディスク２、４の内側面２ａ、４ａとの当接
部に加わる荷重Ｆ0 に基づき上記パワーローラ８に加わ
る曲げ応力が小さくなる。この結果、上記パワーローラ
８の耐久性向上を図れる。Further, the distance L 1 across the radial direction between the point of action of the load applied to the power roller 8 (T F ) and the point of contact between the rolling surfaces of the balls 16 and 16 and the inner ring raceway 18 (T 18 ). Is shorter than the distance L 0 over the radial direction when the contact angle θ is 90 degrees, the peripheral surface 8 of the power roller 8 is
The bending stress applied to the power roller 8 is reduced on the basis of the load F 0 applied to the abutting portions between the a and the inner side surfaces 2a, 4a of the disks 2, 4. As a result, the durability of the power roller 8 can be improved.
【００２７】更に、図示の実施例の場合には、上記各玉
１６、１６の転動面と上記外輪軌道１９との複数の当接
位置Ｔ19、Ｔ19同士を結ぶ円弧の半径ｒ19が、上記接触
角θが９０度である場合の半径Ｒ19よりも小さい（ｒ19
＜Ｒ19）為、上記各玉１６、１６から外輪１７に加わっ
たスラスト荷重に拘らず、この外輪１７に加わる曲げ応
力を小さくできる。即ち、トロイダル型無段変速機のパ
ワーローラ８を支承する為の玉軸受の場合、外輪１７の
中央寄り部分を支承して外周寄り部分を支承しない場合
がある。この場合でも、上記当接位置Ｔ19、Ｔ19が直径
方向内側によっているので、上記曲げ応力を小さくし
て、外輪１７の耐久性向上を図れる。Furthermore, in the case of the illustrated embodiment, the radius of the arc r 19 connecting a plurality of contact positions T 19, T 19 between the rolling surface and the outer raceway 19 of the balls 16, 16 , Smaller than the radius R 19 when the contact angle θ is 90 degrees (r 19
<R 19) Therefore, regardless of the thrust load applied to the outer ring 17 from the balls 16, 16, the bending stress exerted on the outer ring 17 can be reduced. That is, in the case of a ball bearing for supporting the power roller 8 of the toroidal type continuously variable transmission, there are cases in which the central portion of the outer ring 17 is supported but the outer peripheral portion is not supported. Even in this case, since the abutting positions T 19 and T 19 are located inside in the diametrical direction, the bending stress can be reduced and the durability of the outer race 17 can be improved.
【００２８】次に、図２は本発明の第二実施例を示して
いる。本実施例の場合には、入力側、出力側、両ディス
ク２、４の内側面２ａ、４ａ（図３〜４）とパワーロー
ラ８の周面８ａとの当接位置ＴF ´は、上記各玉１６、
１６の転動面と上記内輪軌道１８との当接位置Ｔ18´よ
りも直径方向内方に存在する。これに合わせて本実施例
の場合には、パワーローラ８の片面（図２の上面）に形
成した内輪軌道１８の直径は、外輪１７の片面（図２の
下面）に形成した外輪軌道１９の直径よりも少し大きく
している。従って、これら内輪軌道１８と外輪軌道１９
との間に転動自在に設けた複数の玉１６、１６の接触角
θは、９０度よりも小さくなっている。Next, FIG. 2 shows a second embodiment of the present invention. In the case of the present embodiment, the contact position T F ′ between the input side, the output side, the inner side surfaces 2a, 4a (FIGS. 3 to 4) of both disks 2, 4 and the peripheral surface 8a of the power roller 8 is the above-mentioned value. Each ball 16,
It exists diametrically inward from the contact position T 18 ′ between the rolling surface 16 and the inner ring raceway 18. Accordingly, in the case of the present embodiment, the diameter of the inner ring raceway 18 formed on one surface (upper surface in FIG. 2) of the power roller 8 is the same as that of the outer ring raceway 19 formed on one surface (lower surface in FIG. 2) of the outer ring 17. It is slightly larger than the diameter. Therefore, these inner ring raceway 18 and outer ring raceway 19
The contact angle θ of the plurality of balls 16, 16 provided rotatably between and is smaller than 90 degrees.
【００２９】本実施例の場合も、上述した第一実施例と
同様に、パワーローラ８がラジアル荷重に基づいてラジ
アル方向に変位しにくくなって、玉１６、１６の運動が
複雑になりにくく、玉１６や外輪、内輪両軌道１９、１
８の摩耗や疲れ寿命に悪影響を及ぼしにくくなる。又、
パワーローラ８に加わる荷重の作用点と、各玉１６、１
６の転動面と内輪軌道１８との接触点とのラジアル方向
に亙る距離が短くなる。この為、パワーローラ８と入力
側、出力側各ディスク２、４の内側面２ａ、４ａとの当
接部に加わる荷重Ｆ0 に基づき上記パワーローラ８に加
わる曲げ応力が小さくなり、上記パワーローラ８の耐久
性向上を図れる。Also in the case of this embodiment, similarly to the above-mentioned first embodiment, the power roller 8 is less likely to be displaced in the radial direction based on the radial load, and the movement of the balls 16, 16 is less likely to be complicated. Ball 16, outer ring, inner ring both tracks 19, 1
The wear and fatigue life of No. 8 are less likely to be adversely affected. or,
Point of action of load applied to power roller 8 and balls 16, 1
The distance between the rolling surface of No. 6 and the contact point of the inner ring raceway 18 in the radial direction becomes short. Therefore, the bending stress applied to the power roller 8 based on the load F 0 applied to the contact portion between the power roller 8 and the inner side surfaces 2a, 4a of the input side and output side disks 2, 4 is reduced, and the power roller is reduced. The durability of No. 8 can be improved.
【００３０】[0030]
【発明の効果】本発明のパワーローラ用スラスト玉軸受
は、以上に述べた通り構成され作用する為、構成各部品
の摩耗低減、疲れ寿命の延長、並びに曲げモーメントの
低減を図り、スラスト玉軸受全体としての信頼性、耐久
性向上を図れる。Since the thrust ball bearing for a power roller of the present invention is constructed and operates as described above, the thrust ball bearing is designed to reduce wear of each component, extend fatigue life, and reduce bending moment. The reliability and durability as a whole can be improved.
【図１】本発明の第一実施例を示す断面図。FIG. 1 is a sectional view showing a first embodiment of the present invention.
【図２】同第二実施例を示す断面図。FIG. 2 is a sectional view showing the second embodiment.
【図３】スラスト玉軸受を組み込んだトロイダル型無段
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. 3 is a side view showing a basic configuration of a toroidal type continuously variable transmission incorporating a thrust ball bearing in a state at maximum deceleration.
【図４】同じく最大増速時の状態で示す側面図。FIG. 4 is a side view showing the same state at the time of maximum acceleration.
【図５】スラスト玉軸受並びにその潤滑装置部分の断面
図。FIG. 5 is a sectional view of a thrust ball bearing and a lubrication device portion thereof.
【図６】スラスト玉軸受のみを取り出して示す断面図。FIG. 6 is a sectional view showing only a thrust ball bearing.
【図７】ラジアル荷重を受けた状態で示す、図６と同様
の図。FIG. 7 is a view similar to FIG. 6, showing a state in which a radial load is applied.
１ 入力軸 ２ 入力側ディスク ２ａ 内側面 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、１４ カム面 １５ スラスト玉軸受 １６ 玉 １７ 外輪 １８ 内輪軌道 １９ 外輪軌道 ２０ 保持器 ２１ 主体 ２２ ポケット ２３ スぺーサ ２４ 給油孔 1 Input Shaft 2 Input Side Disk 2a Inner Side Surface 3 Output Shaft 4 Output Side Disk 4a Inner Side Surface 5 Axis 6 Trunnion 7 Displacement Axis 8 Power Roller 8a Circumferential Surface 9 Pressing Device 10 Cam Plate 11 Cage 12 Roller 13, 14 Cam Surface 15 Thrust ball bearing 16 Ball 17 Outer ring 18 Inner ring raceway 19 Outer ring raceway 20 Cage 21 Main body 22 Pocket 23 Spacer 24 Oil supply hole
Claims (1)
パワーローラの軸方向片面に形成された、断面が円弧状
で全体が円環状の内輪軌道と、上記パワーローラと同心
に配置された外輪と、この外輪の軸方向片面で上記内輪
軌道と対向する部分に形成された、断面が円弧状で全体
が円環状の外輪軌道と、それぞれの転動面を上記内輪軌
道及び外輪軌道に当接させた複数の玉とを備え、次の
の条件を満たすスラスト玉軸受。 上記複数の玉の接触角が９０度から外れている。 上記接触角が９０度から外れる方向は、パワーロー
ラの周面に加わる荷重の作用点と、上記玉の転動面と上
記内輪軌道との接触点との距離が、上記接触角が９０度
である場合に比べて短くなる方向である。1. An inner ring orbit having an arcuate cross section and an annular shape as a whole, which is formed on one axial surface of a power roller incorporated in a toroidal type continuously variable transmission, and an outer ring concentrically arranged with the power roller. And an outer ring raceway formed in a portion of the outer ring facing the inner ring raceway on one side in the axial direction and having an annular cross section and an annular shape as a whole, and the respective rolling surfaces contacting the inner raceway and the outer raceway. A thrust ball bearing that has the following multiple balls and satisfies the following conditions. The contact angles of the plurality of balls deviate from 90 degrees. In the direction in which the contact angle deviates from 90 degrees, the distance between the point of action of the load applied to the peripheral surface of the power roller and the contact point between the rolling surface of the ball and the inner ring raceway is 90 degrees. It tends to be shorter than in some cases.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP02141594A JP3303503B2 (en) | 1994-02-18 | 1994-02-18 | Thrust ball bearings for power rollers |
| US08/387,087 US5536091A (en) | 1994-02-18 | 1995-02-13 | Thrust ball bearing for use with power rollers |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP02141594A JP3303503B2 (en) | 1994-02-18 | 1994-02-18 | Thrust ball bearings for power rollers |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07229549A true JPH07229549A (en) | 1995-08-29 |
| JP3303503B2 JP3303503B2 (en) | 2002-07-22 |
Family
ID=12054389
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP02141594A Expired - Lifetime JP3303503B2 (en) | 1994-02-18 | 1994-02-18 | Thrust ball bearings for power rollers |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3303503B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19644958A1 (en) * | 1995-10-30 | 1997-05-07 | Nissan Motor | Infinitely variable ratio power transmission |
| US5976053A (en) * | 1995-10-30 | 1999-11-02 | Nissan Motor Co., Ltd. | Method of manufacturing traction rollers for continuously variable transmissions and traction rollers resulting therefrom |
| EP1143167A2 (en) | 2000-04-03 | 2001-10-10 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission |
| CN100392266C (en) * | 2006-06-06 | 2008-06-04 | 加西贝拉压缩机有限公司 | Diameter-variable plane thrust ball bearing |
-
1994
- 1994-02-18 JP JP02141594A patent/JP3303503B2/en not_active Expired - Lifetime
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19644958A1 (en) * | 1995-10-30 | 1997-05-07 | Nissan Motor | Infinitely variable ratio power transmission |
| US5823911A (en) * | 1995-10-30 | 1998-10-20 | Nissan Motor Co., Ltd. | Supports for power rollers for use in toroidal-type continuously variable transmissions |
| US5976053A (en) * | 1995-10-30 | 1999-11-02 | Nissan Motor Co., Ltd. | Method of manufacturing traction rollers for continuously variable transmissions and traction rollers resulting therefrom |
| US6282789B1 (en) | 1995-10-30 | 2001-09-04 | Nissan Motor Co., Ltd. | Method of manufacturing traction rollers for continuously variable transmissions and traction rollers resulting therefrom |
| DE19644958C2 (en) * | 1995-10-30 | 2003-04-10 | Nissan Motor | Gearbox with continuously adjustable transmission ratio |
| EP1143167A2 (en) | 2000-04-03 | 2001-10-10 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission |
| EP1143167A3 (en) * | 2000-04-03 | 2002-04-03 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission |
| US6524213B2 (en) | 2000-04-03 | 2003-02-25 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission |
| CN100392266C (en) * | 2006-06-06 | 2008-06-04 | 加西贝拉压缩机有限公司 | Diameter-variable plane thrust ball bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3303503B2 (en) | 2002-07-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5536091A (en) | Thrust ball bearing for use with power rollers | |
| US5575733A (en) | Toroidal type continuously variable transmission having retainer ring with lubricating oil paths | |
| JP4239307B2 (en) | Thrust tapered roller bearing | |
| JP4135249B2 (en) | Half toroidal continuously variable transmission | |
| JP3303503B2 (en) | Thrust ball bearings for power rollers | |
| JP3638303B2 (en) | Thrust ball bearing for half toroidal type continuously variable transmission | |
| JP2001004003A (en) | Toroidal type continuously variable transmission | |
| JP3326950B2 (en) | Thrust ball bearing for half toroidal type continuously variable transmission | |
| JPH07174146A (en) | Thrust roller bearing | |
| JP3899745B2 (en) | Toroidal continuously variable transmission | |
| JP3716571B2 (en) | Toroidal continuously variable transmission | |
| JPH07243492A (en) | Toroidal type continuously variable transmission | |
| JPH07239003A (en) | Thrust ball bearing for power roller | |
| JP4207330B2 (en) | Toroidal continuously variable transmission | |
| JP2001050360A (en) | Toroidal continuously variable transmission | |
| JPH08240251A (en) | Toroidal type continuously variable transmission | |
| JP4114396B2 (en) | Toroidal continuously variable transmission | |
| JPH0616753U (en) | Toroidal type continuously variable transmission | |
| JPH07174142A (en) | Thrust roller bearing | |
| JP4721040B2 (en) | Toroidal continuously variable transmission | |
| JP2598886Y2 (en) | Toroidal type continuously variable transmission | |
| JP3293306B2 (en) | Toroidal type continuously variable transmission | |
| JP4415709B2 (en) | Toroidal continuously variable transmission | |
| JP2001099253A (en) | Toroidal type continuously variable transmission | |
| US6896414B2 (en) | Ball roller |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Year of fee payment: 6 Free format text: PAYMENT UNTIL: 20080510 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090510 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100510 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100510 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110510 Year of fee payment: 9 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120510 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Year of fee payment: 11 Free format text: PAYMENT UNTIL: 20130510 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Year of fee payment: 11 Free format text: PAYMENT UNTIL: 20130510 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20140510 Year of fee payment: 12 |
|
| EXPY | Cancellation because of completion of term |