JP3022112B2 - Friction wheel type continuously variable transmission - Google Patents
Friction wheel type continuously variable transmissionInfo
- Publication number
- JP3022112B2 JP3022112B2 JP5322206A JP32220693A JP3022112B2 JP 3022112 B2 JP3022112 B2 JP 3022112B2 JP 5322206 A JP5322206 A JP 5322206A JP 32220693 A JP32220693 A JP 32220693A JP 3022112 B2 JP3022112 B2 JP 3022112B2
- Authority
- JP
- Japan
- Prior art keywords
- friction wheel
- support member
- wheel support
- link
- spherical joint
- 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.)
- Expired - Lifetime
Links
Landscapes
- Friction Gearing (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、摩擦車式無段変速機
の、変速制御精度の向上を狙った改良提案に関するもの
である。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement proposal for a continuously variable transmission of a friction wheel type, which aims at improving the speed control accuracy.
【０００２】[0002]
【従来の技術】摩擦車式無段変速機は通常、例えば実開
平１−１７３５５２号公報に記載の如く、同軸に対向配
置した入出力ディスクと、これら入出力ディスク間で摩
擦係合により動力の受渡しを行うよう、該入出力ディス
クの回転軸線周りに配置された複数の摩擦車と、各摩擦
車を回転自在に支持した摩擦車支持部材と、これら摩擦
車支持部材の隣合う端部同士を相互に、摩擦車支持部材
が摩擦車の回転軸線と直交する首振り軸線方向へ同期し
てストロークされるよう、球面継手を介して連結するリ
ンクとを具え、摩擦車支持部材のストロークにより摩擦
車の首振り軸線周りの傾転を生起させて変速を行うよう
構成するのが普通である。2. Description of the Related Art As described in Japanese Utility Model Laid-Open Publication No. 1-173552, for example, a friction wheel type continuously variable transmission is usually provided with input / output disks coaxially opposed to each other and frictional engagement between these input / output disks to generate power. A plurality of friction wheels arranged around the rotation axis of the input / output disk, a friction wheel support member rotatably supporting each friction wheel, and adjacent ends of the friction wheel support members to perform delivery. And a link connected via a spherical joint so that the friction wheel support member is stroked synchronously in a swing axis direction orthogonal to the rotation axis of the friction wheel. In general, a shift is performed by causing a tilt around the axis of the swinging motion.
【０００３】[0003]
【発明が解決しようとする課題】しかし、上記に代表さ
れる従来の摩擦車式無段変速機では、摩擦車支持部材と
リンクとを図８に示すように相関させていたため、以下
の問題を生じていた。この図において、ａは摩擦車支持
部材、ｂはリンクを示し、摩擦車支持部材ａはこれに嵌
合した軸受ｃによりリンクｂに対して回転自在に支持
し、更に、軸受ｃ上に嵌合した球面継手ｄによりリンク
ｂに対し傾動可能に連結する。なお、ｅはリンクｂを中
央において変速機ケースに傾動自在に支持するためのリ
ンクサポートである。However, in the conventional friction wheel type continuously variable transmission represented by the above, the friction wheel support member and the link are correlated as shown in FIG. Had occurred. In this figure, a denotes a friction wheel support member, b denotes a link, and the friction wheel support member a is rotatably supported on the link b by a bearing c fitted to the friction wheel support member. The link b is tiltably connected to the link b by the spherical joint d. Reference numeral e denotes a link support for supporting the link b at the center so as to be tiltable to the transmission case.
【０００４】ところで、図８（ａ）にｆで示すように摩
擦車支持部材ａとリンクｂとが、変速を行わない中立位
置で平面接触しているため、同図（ｂ），（ｃ）に示す
ように摩擦車支持部材ａをストロークさせてアップシフ
ト変速またはダウンシフト変速を行う時に、摩擦車支持
部材ａがリンクｂに対し交角をもって、リンクサポート
（ｅ）寄りの内側点ｇまたは逆寄りの外側点ｈでリンク
ｂにエッジ当たりする。Since the friction wheel support member a and the link b are in flat contact with each other at a neutral position where no gear shifting is performed, as shown by f in FIG. 8A, FIGS. When the upshift or downshift is performed by moving the friction wheel support member a as shown in FIG. 7, the friction wheel support member a has an intersection angle with the link b, and the inner point g or the reverse point closer to the link support (e). At the outside point h of the link b.
【０００５】従って変速時には、当該内側のエッジ当た
り点ｇまたは外側のエッジ当たり点ｈを支点にして摩擦
車支持部材ａとリンクｂとの間の上記した交角が発生す
ることとなり、このため変速時に球面継手ｄは、リンク
ｂに設けた球面継手嵌合孔ｉの内周面を摺動しつつ摩擦
車支持部材ａの軸線方向へリンクｂに対し相対変位す
る。Therefore, at the time of gear shifting, the above-mentioned intersection angle occurs between the friction wheel support member a and the link b with the inner edge contact point g or the outer edge contact point h as a fulcrum, and therefore, at the time of gear shifting, The spherical joint d is displaced relative to the link b in the axial direction of the friction wheel support member a while sliding on the inner peripheral surface of the spherical joint fitting hole i provided in the link b.
【０００６】ここで当該相対変位の量について考察する
に、図８（ｂ），（ｃ）に示すようにエッジ当たり点
ｇ，ｈから球面継手嵌合孔ｉのリンクサポート（ｅ）寄
りにおける内側内周面部位（球面継手ｄの内側外周面部
位）までの内側アーム長をＬinとし、エッジ当たり点
ｇ，ｈから球面継手嵌合孔ｉの直径方向逆側における外
側内周面部位（球面継手ｄの外側外周面部位）までの外
側アーム長をＬout とすると、図８（ｂ）に示す内側の
エッジ当たり点ｇを発生する変速時、図示の摩擦車支持
部材ａについてはＬout ＞Ｌinであるため、球面継手ｄ
は球面継手嵌合孔ｉの外側内周面部位との接触部におい
て内側内周面部位との接触部におけるよりも大きく摺動
し、図８（ｃ）に示す外側のエッジ当たり点ｈを発生す
る変速時、図示の摩擦車支持部材ａについてはＬin＞Ｌ
out であるため、球面継手ｄは球面継手嵌合孔ｉの内側
内周面部位との接触部において外側内周面部位との接触
部におけるよりも大きく摺動する。Considering the amount of the relative displacement, as shown in FIGS. 8B and 8C, the inner side of the spherical joint fitting hole i near the link support (e) from the edge contact points g and h as shown in FIGS. The length of the inner arm up to the inner circumferential surface portion (the inner outer circumferential surface portion of the spherical joint d) is L in, and the outer inner circumferential surface portion (spherical surface) on the diametrically opposite side of the spherical joint fitting hole i from the points g and h per edge. Assuming that the outer arm length up to the outer peripheral surface portion of the joint d) is L out , at the time of shifting in which an inner edge contact point g shown in FIG. 8B is generated, L out > L in , the spherical joint d
Slides more at the contact portion of the spherical joint fitting hole i with the outer inner peripheral surface portion than at the contact portion with the inner inner peripheral surface portion, and generates the outer edge contact point h shown in FIG. 8C. In the illustrated speed change, L in > L for the friction wheel support member a shown in the drawing.
Therefore , the spherical joint d slides more at the contact portion with the inner inner peripheral surface portion of the spherical joint fitting hole i than at the contact portion with the outer inner peripheral surface portion.
【０００７】ところで摩擦車支持部材ａは、摩擦車が入
出力ディスク間で動力伝達を行い得るよう伝達トルク対
応の力で当該入出力ディスク間に挟圧されているため、
常時リンクサポートｅから遠ざかる外側方向の力を受け
ており、球面継手ｄは球面継手嵌合孔ｉの外側内周面部
位に対し強力に押圧されている。従って、図８（ｂ）に
示すように球面継手ｄが球面継手嵌合孔ｉの外側内周面
部位との接触部において大きく摺動する変速時において
は、対応する摩擦車支持部材ａの矢で示すストロークに
大きな抵抗が作用する。一方で、図８（ｃ）に示すよう
に球面継手ｄが球面継手嵌合孔ｉの内側内周面部位との
接触部において大きく摺動する変速時においては、図示
する摩擦車支持部材ａの場合、球面継手ｄが球面継手嵌
合孔ｉの外側内周面部位との接触部において僅かしか摺
動しないために上記の問題を生じない。しかして図８
（ｃ）に示す変速時においても、図示する摩擦車支持部
材ａとは反対側における摩擦車支持部材が当該図示する
摩擦車支持部材ａとは非対称に内側のエッジ当たり点を
支点にしてリンクｂとの間に上記した交角を発生し、当
該反対側の摩擦車支持部材に係わる球面継手が球面継手
嵌合孔の外側内周面部位との接触部において大きく摺動
するため、当該反対側の摩擦車支持部材のストロークに
大きな抵抗が作用するという上記の問題を生ずる。The friction wheel support member a is sandwiched between the input and output disks by a force corresponding to the transmission torque so that the friction wheel can transmit power between the input and output disks.
The spherical joint d is constantly pressed in the outward direction away from the link support e, and is strongly pressed against the outer inner peripheral surface of the spherical joint fitting hole i. Therefore, as shown in FIG. 8 (b), at the time of shifting in which the spherical joint d slides largely at the contact portion with the outer inner peripheral surface of the spherical joint fitting hole i, the gear of the corresponding friction wheel support member a is shifted. A large resistance acts on the stroke indicated by. On the other hand, as shown in FIG. 8 (c), at the time of shifting in which the spherical joint d slides largely at the contact portion with the inner peripheral surface of the spherical joint fitting hole i, at the time of gear shifting, the friction wheel support member a shown in FIG. In this case, the above-described problem does not occur because the spherical joint d slides only slightly at the contact portion with the outer inner peripheral surface of the spherical joint fitting hole i. FIG. 8
Also at the time of the gear shift shown in (c), the friction wheel support member on the opposite side to the illustrated friction wheel support member a has the link b with the inner edge contact point as a fulcrum asymmetrically with respect to the illustrated friction wheel support member a. The above-mentioned intersection angle is generated between the spherical joint and the spherical joint relating to the friction wheel support member on the opposite side slides largely at the contact portion with the outer inner peripheral surface portion of the spherical joint fitting hole. The above problem occurs in that a large resistance acts on the stroke of the friction wheel support member.
【０００８】以上のことから明らかなように何れのリン
クｂにおいても、その両端における摩擦車支持部材のう
ち一方の摩擦車支持部材は必ず、変速時に上記した内側
のエッジ当たり点を生じ、これを支点にしてリンクとの
間に交角を発生し、球面継手を球面継手嵌合孔の外側内
周面部位との接触部において大きく摺動させる結果、無
段変速機全体としては、摩擦車支持部材のストロークに
より行う変速操作に大きな抵抗が作用するのを免れなか
った。従って、従来の摩擦車式無段変速機にあっては当
該大きな抵抗が、変速指令に対する変速比の変化状況を
示す図７（ａ）から明らかなように、変速制御特性のヒ
ステリシスを大きくし、変速制御精度を低下させるとい
う問題を発生していた。As is apparent from the above description, in any link b, one of the friction wheel support members at both ends of the link b always generates the above-mentioned inner edge contact point at the time of gear shifting. As a fulcrum, an intersecting angle is generated between the link and the link, and the spherical joint slides largely at the contact portion with the outer inner peripheral surface of the spherical joint fitting hole. As a result, the continuously variable transmission as a whole is a friction wheel support member. It was inevitable that a large resistance would act on the speed change operation performed by the stroke. Therefore, in the conventional friction wheel type continuously variable transmission, the large resistance increases the hysteresis of the shift control characteristic, as is clear from FIG. There has been a problem that the shift control accuracy is reduced.
【０００９】請求項１に記載の第１発明は、摩擦車支持
部材の何れ方向のストローク時も、これとリンクとの接
触位置が不変に保たれるようにすれば、この接触位置の
選択次第で各リンクごとに全ての摩擦車支持部材に係わ
る球面継手がともに、リンクに設けた球面継手嵌合孔の
外側内周面部位との接触部における前記の摺動量を小さ
くされ得るとの事実認識に基づき、この着想を具体化し
て当該摺動量を総体的に小さくし得るような構成にする
ことで、上述の問題を解消可能にした摩擦車式無段変速
機を提案することを目的とする。According to the first aspect of the present invention, if the contact position between the friction wheel support member and the link is kept constant during any stroke of the friction wheel support member, the contact position can be determined by selecting the contact position. The fact that both the spherical joints associated with all friction wheel support members for each link can reduce the sliding amount at the contact portion with the outer inner peripheral surface of the spherical joint fitting hole provided in the link. It is an object of the present invention to propose a friction wheel type continuously variable transmission that can solve the above-described problem by realizing this idea and making the sliding amount generally small based on the concept. .
【００１０】また請求項２に記載の第２発明は、リンク
に設けた球面継手嵌合孔の外側内周面部位との接触部に
おける球面継手の上記摺動量を確実に小さくし得る摩擦
車支持部材とリンクとの上記接触位置を提案することを
目的とする。According to a second aspect of the present invention, there is provided a friction wheel support capable of reliably reducing the sliding amount of the spherical joint at a contact portion of the spherical joint fitting hole provided on the link with the outer inner peripheral surface. It is an object of the invention to propose the contact position between the member and the link.
【００１１】更に請求項３に記載の第３発明は、リンク
に設けた球面継手嵌合孔の外側内周面部位との接触部に
おける球面継手の上記摺動量がほとんど０になる摩擦車
支持部材とリンクとの上記接触位置を提案することを目
的とする。According to a third aspect of the present invention, there is provided a friction wheel support member in which the sliding amount of the spherical joint at the contact portion of the spherical joint fitting hole provided on the link with the outer inner peripheral surface portion is almost zero. It is intended to propose the above-mentioned contact position between the link and the link.
【００１２】[0012]
【課題を解決するための手段】これらの目的のため先ず
第１発明は、同軸に対向配置した入出力ディスクと、こ
れら入出力ディスク間で摩擦係合により動力の受渡しを
行うよう、該入出力ディスクの回転軸線周りに配置され
た複数の摩擦車と、各摩擦車を回転自在に支持した摩擦
車支持部材と、該摩擦車支持部材の隣合う端部同士を相
互に、摩擦車支持部材が摩擦車の回転軸線と直交する首
振り軸線方向へ同期してストロークされるよう、球面継
手を介して連結するリンクとを具え、該摩擦車支持部材
のストロークにより前記摩擦車の首振り軸線周りの傾転
を生起させて変速を行うようにした摩擦車式無段変速機
において、前記摩擦車支持部材の何れ方向のストローク
時も、該摩擦車支持部材と前記リンクとの間の交角に係
わらず、これら摩擦車支持部材およびリンク間の接触位
置を不変に保つための突起をリンクに設けたことを特徴
とするものである。SUMMARY OF THE INVENTION For these purposes, a first aspect of the present invention is to provide an input / output disk arranged coaxially opposed to the input / output disk so that power can be transferred between the input / output disks by frictional engagement. A plurality of friction wheels arranged around the rotation axis of the disk, a friction wheel support member rotatably supporting each friction wheel, and mutually adjacent ends of the friction wheel support members, A link connected via a spherical joint so as to be stroked synchronously in a swing axis direction orthogonal to the rotational axis of the friction wheel, and a stroke of the friction wheel support member around the swing axis of the friction wheel. In a friction wheel type continuously variable transmission configured to shift by causing tilting, regardless of the angle of intersection between the friction wheel support member and the link, regardless of the stroke of the friction wheel support member in any direction. , These In which characterized in that a projection for keeping a contact position between the vehicle support member and links unchanged link.
【００１３】また第２発明は、上記第１発明において、
上記の突起を、上記首振り軸線方向に見たとき前記球面
継手の外周縁上で隣の摩擦車支持部材から最も遠い側に
配置したことを特徴とするものである。[0013] The second invention is the above-mentioned first invention, wherein:
The projection is arranged on the outer peripheral edge of the spherical joint on the farthest side from an adjacent friction wheel support member when viewed in the direction of the swing axis.
【００１４】更に第３発明は、上記第１発明において、
上記摩擦車支持部材のストロークに伴う該摩擦車支持部
材および前記リンク間の交角変化中に生ずる前記球面継
手の回動中心上に前記突起を配置したことを特徴とする
ものである。[0014] In a third aspect based on the first aspect,
The projection is arranged on the center of rotation of the spherical joint generated during a change in the angle of intersection between the friction wheel support member and the link with the stroke of the friction wheel support member.
【００１５】[0015]
【作用】第１発明において、複数の摩擦車は入出力ディ
スク間で摩擦係合により動力の受渡しを行う。また、各
摩擦車を回転自在に支持した摩擦車支持部材を個々に、
摩擦車の回転軸線と直交する首振り軸線方向へストロー
クさせると、摩擦車は首振りを生起されて入出力ディス
ク間の伝動比を無段階に変化させることができる。な
お、この変速中にリンクは、摩擦車支持部材の上記スト
ロークを同期させるよう機能し、変速制御を正確になし
得る。In the first invention, a plurality of friction wheels transfer power between the input and output disks by frictional engagement. Also, the friction wheel support members that rotatably support each friction wheel are individually
When the friction wheel is stroked in the direction of the swing axis orthogonal to the rotation axis of the friction wheel, the friction wheel is swung, and the transmission ratio between the input and output disks can be changed steplessly. During the shift, the link functions to synchronize the strokes of the friction wheel support member, so that the shift control can be accurately performed.
【００１６】ところで、上記摩擦車支持部材のストロー
ク中、該摩擦車支持部材と上記リンクとの間の交角に係
わらず、これら摩擦車支持部材およびリンク間の接触位
置を不変に保つための突起をリンクに設けたから、摩擦
車支持部材のストローク中、これとリンクとが常時上記
の突起で接触して接触位置が不変に保たれることとな
り、当該接触位置の選択次第で、全ての摩擦車支持部材
に係わる球面継手について、隣接する球面継手から遠い
側の外側外周面部位とリンクとの間における摩擦車支持
部材の軸線方向への摺動量を小さくすることが可能で、
結果として、前記した根拠から摩擦力が大きくなる当該
球面継手の外側外周面部位における摩擦車支持部材の軸
線方向への摺動量を総体的に小さくし得る。従って、当
該球面継手の外側外周面部位の大きな摺動に伴い発生す
る抵抗力に起因して、従来の摩擦車式無段変速機で生じ
ていた変速制御特性の大きなヒステリシスを小さくする
ことができる。By the way, during the stroke of the friction wheel support member, a projection for keeping the contact position between the friction wheel support member and the link unchanged regardless of the intersection angle between the friction wheel support member and the link. Because the link is provided on the link, during the stroke of the friction wheel support member, the link and the link are always in contact with the above-mentioned protrusions, and the contact position is kept unchanged. Depending on the selection of the contact position, all the friction wheel support members are supported. Regarding the spherical joint relating to the member, it is possible to reduce the sliding amount in the axial direction of the friction wheel support member between the outer peripheral surface portion on the side far from the adjacent spherical joint and the link,
As a result, the amount of sliding of the friction wheel support member in the axial direction at the outer peripheral surface portion of the spherical joint at which the frictional force increases from the basis described above can be reduced as a whole. Therefore, the large hysteresis of the shift control characteristic that occurs in the conventional friction wheel type continuously variable transmission due to the resistance generated by the large sliding of the outer peripheral surface portion of the spherical joint can be reduced. .
【００１７】また第２発明では、上記第１発明における
突起を特に、首振り軸線方向に見たとき上記球面継手の
外周縁上で隣の摩擦車支持部材から最も遠い側に配置し
たから、突起が上記球面継手外側外周面部位の摺動量を
確実に小さくする摩擦車支持部材とリンクとの上記接触
位置を提供して第１発明の作用効果を更に確実なものに
すると共に、突起が、リンクに形成すべき球面継手嵌合
孔に掛からず、該球面継手嵌合孔の加工時に、突起の存
在故に孔の加工性が低下するといった弊害をなくすこと
ができる。In the second invention, the projection in the first invention is arranged on the outermost edge of the spherical joint on the farthest side from the adjacent friction wheel support member when viewed in the direction of the swinging axis. Provides the above-mentioned contact position between the friction wheel support member and the link, which reliably reduces the sliding amount of the outer peripheral surface portion of the spherical joint, so that the operation and effect of the first invention can be further ensured. Therefore, it is possible to eliminate the problem that the workability of the hole is reduced due to the presence of the projection when the spherical joint is formed.
【００１８】更に第３発明は、上記摩擦車支持部材のス
トロークに伴う該摩擦車支持部材および前記リンク間の
交角変化中に生ずる前記球面継手の回動中心上に、上記
第１発明における突起を配置したから、当該突起により
提供される摩擦車支持部材とリンクとの間の不変の接触
位置が上記の回動中心上に存在することとなり、結果と
して理論上、球面継手とリンクとの間で首振り軸線方向
への摺動を惹起するようなことがほとんどなくなり、従
って、上記球面継手外側外周面部位の首振り軸線方向へ
の摺動量をほとんど０にし得て第１発明の作用効果を第
２発明よりも更に確実なものにすることができる。Further, a third aspect of the present invention provides the projection according to the first aspect of the present invention, wherein the projection of the first aspect of the present invention is provided on the center of rotation of the spherical joint which occurs during a change in the angle of intersection between the friction wheel support member and the link accompanying the stroke of the friction wheel support member. Because of the arrangement, a constant contact position between the friction wheel support member and the link provided by the projection is present on the rotation center, and as a result, theoretically, between the spherical joint and the link. Sliding in the direction of the oscillating axis is hardly caused. Therefore, the sliding amount of the outer peripheral surface portion of the spherical joint in the direction of the oscillating axis can be reduced to almost zero, and the operation and effect of the first invention can be reduced. It can be made more reliable than the two inventions.
【００１９】[0019]
【実施例】以下、本発明の実施例を図面に基づき詳細に
説明する。図１乃至図３は、本発明による摩擦車式無段
変速機の一実施例を示し、図１において１は変速機ケー
ス、２は主軸、３は、主軸２を挟んでその両側に対向さ
せて配置した一対のパワーローラ（摩擦車）である。Embodiments of the present invention will be described below in detail with reference to the drawings. 1 to 3 show an embodiment of a friction wheel type continuously variable transmission according to the present invention. In FIG. 1, reference numeral 1 denotes a transmission case, 2 denotes a main shaft, and 3 And a pair of power rollers (friction wheels).
【００２０】図示しなかったが、主軸２上に入出力コー
ンディスク（ディスク）を対向させて回転自在に支持
し、入力コーンディスクを動力源に駆動結合し、出力コ
ーンディスクを出力軸に駆動結合する。パワーローラ３
は、これら入出力コーンディスク間で摩擦係合により動
力伝達を行うもので、これがため各パワーローラ３を個
々のトラニオン（摩擦車支持部材）４に回転自在に支持
する。Although not shown, an input / output cone disk (disk) is rotatably supported on the main shaft 2 so as to face each other, the input cone disk is drive-coupled to a power source, and the output cone disk is drive-coupled to the output shaft. I do. Power roller 3
The power transmission is performed by frictional engagement between the input and output cone disks, and thus each power roller 3 is rotatably supported by an individual trunnion (friction wheel support member) 4.
【００２１】各トラニオン４はアッパリンク５およびロ
アリンク６により変速機ケース１に支持する。これがた
めアッパリンク５の中央に図２（ａ），（ｂ）に示す如
く透孔５ａを穿ち、これに球面嵌合するリンクサポート
７によりアッパリンク５を変速機ケース１に揺動可能に
支持し、ロアリンク６の中央に図３（ａ），（ｂ）に示
す如く透孔６ａを穿ち、これに球面嵌合するリンクサポ
ート８によりロアリンク６を変速機ケース１に揺動可能
に支持する。Each trunnion 4 is supported on the transmission case 1 by an upper link 5 and a lower link 6. For this reason, a through hole 5a is formed in the center of the upper link 5 as shown in FIGS. 2 (a) and 2 (b), and the upper link 5 is swingably supported on the transmission case 1 by a link support 7 which is fitted into the through hole 5a. As shown in FIGS. 3A and 3B, a through hole 6a is formed in the center of the lower link 6, and the lower link 6 is swingably supported on the transmission case 1 by a link support 8 fitted into the through hole 6a. I do.
【００２２】そして、アッパリンク５の両端にそれぞれ
図２（ａ），（ｂ）に示す如く透孔５ｂを穿ち、これら
に球面嵌合する球面継手９および該球面継手内に嵌合す
る軸受１０を介して両トラニオン４の上端をアッパリン
ク５の両端に夫々揺動可能および回転自在に支持する。As shown in FIGS. 2A and 2B, through-holes 5b are formed at both ends of the upper link 5, and a spherical joint 9 and a bearing 10 are fitted into the spherical joint 9 and the spherical joint, respectively. The upper ends of both trunnions 4 are supported at both ends of the upper link 5 so as to be swingable and rotatable, respectively.
【００２３】また、ロアリンク６の両端にそれぞれ図３
（ａ），（ｂ）に示す如く透孔６ｂを穿ち、これらに球
面嵌合する球面継手１１および該球面継手内に嵌合する
軸受１２を介して両トラニオン４の下端をロアリンク６
の両端に夫々揺動可能および回転自在に支持する。FIG. 3 shows two ends of the lower link 6 respectively.
As shown in (a) and (b), through holes 6b are drilled, and the lower ends of the two trunnions 4 are connected to the lower link 6 via a spherical joint 11 fitted into the spherical joints and a bearing 12 fitted in the spherical joints.
At both ends thereof so as to be swingable and rotatable, respectively.
【００２４】なお、軸受１０，１２で規定される各トラ
ニオン４の回転軸線は、パワーローラ３の回転軸線に直
交させる。The rotation axis of each trunnion 4 defined by the bearings 10 and 12 is orthogonal to the rotation axis of the power roller 3.
【００２５】各トラニオン４の下端には更にピストン１
３を同軸に結合して設け、これらピストンをコントロー
ルバルブ１４により、同時に逆向きにストロークさせて
周知の変速制御を行うものとし、かかる両トラニオンの
ストロークの同期を、リンク５，６により補償するもの
とする。At the lower end of each trunnion 4, a piston 1 is further provided.
3 are coaxially connected, and these pistons are simultaneously moved in opposite directions by the control valve 14 to perform a well-known shift control. The synchronization of the strokes of the two trunnions is compensated by the links 5 and 6. And
【００２６】本例においては、図１にも示すが、特に図
２および図３に明示するように、アッパリンク５および
ロアリンク６の球面継手嵌合孔５ｂ，６ｂの周縁上で、
隣の球面継手嵌合孔とは反対の側に配して突起５ｃ，６
ｃを形成し、これら突起は夫々、図２（ｂ）および図３
（ｂ）に示すようにリンク５，６の幅方向に延在させ
る。In this embodiment, as also shown in FIG. 1, as specifically shown in FIGS. 2 and 3, on the peripheral edges of the spherical joint fitting holes 5b, 6b of the upper link 5 and the lower link 6,
The protrusions 5c, 6 are arranged on the side opposite to the adjacent spherical joint fitting hole.
c, and these protrusions are respectively shown in FIG. 2 (b) and FIG.
The links 5 and 6 extend in the width direction as shown in FIG.
【００２７】ここで、突起５ｃ，６ｃをかかる位置に決
定した理由は、以下の理由によるものである。即ち、摩
擦車式無段変速機においてパワーローラ３は、入出力コ
ーンディスク間での動力伝達を可能にするためこれら入
出力コーンディスク間に挟圧されており、このため図４
にαで示すような力がトラニオン４を経てリンク５，６
の球面継手嵌合孔５ｂ，６ｂに作用している。その結果
として、球面継手９，１１から球面継手嵌合孔５ｂ，６
ｂへの応力分布はβで示すようなものになり、この応力
分布に応じた摩擦力が球面継手９，１１と球面継手嵌合
孔５ｂ，６ｂとの間における楕円状の接触部に作用す
る。ところで応力分布がβで示すようなものであること
から、球面継手嵌合孔５ｂ，６ｂのリンク中央部に近い
半円周部においては球面継手９，１１からの押し付け力
が作用しないため当該球面継手９，１１との間に摩擦力
が発生することがなく、これを無視することができる。Here, the reason why the projections 5c and 6c are determined at such positions is as follows. That is, in the friction wheel type continuously variable transmission, the power roller 3 is pinched between the input and output cone disks in order to enable power transmission between the input and output cone disks.
The force indicated by α at the links 5 and 6 via the trunnion 4
Act on the spherical joint fitting holes 5b and 6b. As a result, spherical joint fitting holes 5b, 6
The stress distribution on b becomes as shown by β, and the frictional force corresponding to this stress distribution acts on the elliptical contact portion between the spherical joints 9, 11 and the spherical joint fitting holes 5b, 6b. . By the way, since the stress distribution is represented by β, the pressing force from the spherical joints 9 and 11 does not act on the semicircular portion near the link center of the spherical joint fitting holes 5b and 6b, so that the spherical surface is not applied. No frictional force is generated between the joints 9 and 11, which can be ignored.
【００２８】一方で、トラニオン４のストロークに伴い
これとリンク５，６との間に交角変化を生ずる時は、上
記楕円状の接触部において球面継手９，１１が球面継手
嵌合孔５ｂ，６ｂの内周面上を滑りながら上記の交角変
化を吸収する。この時上記楕円状の接触部における各点
の摩擦力は、当該各点における法線方向の押し付け力
（応力分布βで決まる）が強いほど大きくなって、球面
継手９，１１を球面継手嵌合孔５ｂ，６ｂの内周面上で
滑りにくくし、逆に上記の法線方向押し付け力が弱いほ
ど小さくなって、球面継手９，１１を球面継手嵌合孔５
ｂ，６ｂの内周面上で滑り易くする。On the other hand, when the angle of intersection between the trunnion 4 and the links 5 and 6 is changed with the stroke of the trunnion 4, the spherical joints 9 and 11 are fitted into the spherical joint fitting holes 5b and 6b at the elliptical contact portions. Absorbs the above-mentioned change in the angle of intersection while sliding on the inner peripheral surface of the. At this time, the frictional force at each point in the elliptical contact portion increases as the pressing force in the normal direction (determined by the stress distribution β) at each point increases, and the spherical joints 9 and 11 are fitted with the spherical joints. Slip on the inner peripheral surfaces of the holes 5b and 6b, and conversely, the weaker the pressing force in the normal direction, the smaller the force.
b, 6b to make it easy to slide on the inner peripheral surface.
【００２９】ここで、上記摩擦力が最も大きくなる両球
面継手嵌合孔５ｂ，６ｂの相互に最も遠い側の周縁部に
おける接線と、これに平行でトラニオン回転軸線と直交
する線との間に挟まれ、これらに平行な例えば図４にδ
で示す線から、上記摩擦力が作用する上記楕円状接触部
の各点までの距離（アーム長）に当該各点の上記摩擦力
を掛けて算出した回転モーメントの総和を求め、この総
和が最低になるような線δの、図４に例示する位置が、
トラニオン４のストロークに伴って生ずる球面継手嵌合
孔５ｂ，６ｂ内での（上記楕円状接触部上での）球面継
手９，１１の回動中心である。なお当該球面継手９，１
１の回動中心δは、上記の事実から応力分布β（摩擦力
分布）の形状によって決まり、この分布の中高傾向が強
くなるほど球面継手９，１１の回動中心δはリンク中央
部から遠ざかること勿論である。Here, between the tangent line at the peripheral portion of the two spherical joint fitting holes 5b and 6b at which the frictional force becomes the largest, and the line parallel to this and orthogonal to the trunnion rotation axis. For example, FIG.
From the line shown by, the sum of the rotational moments calculated by multiplying the distance (arm length) to each point of the elliptical contact portion on which the frictional force acts by the frictional force at each point is obtained. The position illustrated in FIG. 4 of the line δ such that
The center of rotation of the spherical joints 9 and 11 (on the elliptical contact portions) in the spherical joint fitting holes 5b and 6b generated with the stroke of the trunnion 4. The spherical joints 9, 1
The rotation center δ of 1 is determined by the shape of the stress distribution β (frictional force distribution) from the above fact, and the rotation center δ of the spherical joints 9 and 11 moves away from the center of the link as the tendency of the distribution becomes stronger. Of course.
【００３０】上記球面継手９，１１の回動中心δは、ト
ラニオン４およびリンク５，６間の交角変化中もリンク
５，６および球面継手９，１１間の首振り軸線方向にお
ける相対変位を生じない球面継手９，１１の回動中心で
ある。従って上記の突起５ｃ，６ｃは前記本発明の目的
に照らして、回動中心δの近くに位置させるのが良く、
本実施例においては突起５ｃ，６ｃを回動中心δに近い
上記の位置、つまり図２および図３に明示するように、
アッパリンク５およびロアリンク６の球面継手嵌合孔５
ｂ，６ｂの周縁上で、隣の球面継手嵌合孔とは反対の側
に決定した。The center of rotation δ of the spherical joints 9 and 11 causes a relative displacement in the direction of the swing axis between the links 5 and 6 and the spherical joints 9 and 11 even during the change of the intersection angle between the trunnion 4 and the links 5 and 6. This is the center of rotation of the spherical joints 9 and 11. Therefore, the projections 5c and 6c are preferably located near the center of rotation δ in light of the object of the present invention.
In the present embodiment, the protrusions 5c and 6c are positioned at the above-mentioned position close to the rotation center δ, that is, as clearly shown in FIGS.
Spherical joint fitting hole 5 for upper link 5 and lower link 6
On the periphery of b, 6b, it was determined on the side opposite to the adjacent spherical joint fitting hole.
【００３１】なお本実施例における突起５ｃ，６ｃの位
置によれば、これら突起が球面継手嵌合孔５ｂ，６ｂに
掛からず、球面継手嵌合孔５ｂ，６ｂの切削加工に際
し、その加工性が低下するのを回避することができて好
適である。According to the positions of the projections 5c and 6c in the present embodiment, these projections do not engage with the spherical joint fitting holes 5b and 6b, and the workability of the spherical joint fitting holes 5b and 6b is reduced. This is preferable because it can be prevented from lowering.
【００３２】ところで、かかる球面継手嵌合孔５ｂ，６
ｂの切削加工性についての低下が許容される場合、図５
および図６に示すように突起５ｃ，６ｃは、図４の回動
中心δ上に位置させるのが機能上最適である。The spherical joint fitting holes 5b, 6
FIG. 5 shows a case where a decrease in the machinability of b is allowable.
As shown in FIG. 6 and FIG. 6, the projections 5c and 6c are optimally functionally located on the rotation center δ in FIG.
【００３３】上記実施例の作用を次に説明する。図１に
おいて、パワーローラ３は主軸２上の図示せざる入出力
コーンディスク間で動力の受渡しを行うよう回転され、
この伝動中ピストン１３によりトラニオン４を、パワー
ローラ回転軸線と直交する首振り軸線の方向に、同期し
て同位相でストロークさせると、パワーローラ３が主軸
２からオフセットされて首振り軸線周りの分力を受け、
当該軸線周りに首振り回動される。これによりパワーロ
ーラ３は入出力コーンディスクに対する摩擦係合円径を
連続的に変化され、入出力コーンディスク間の伝動比、
つまり変速比を無段階に変化させることができる。そし
て、変速比が所定比になったところで、周知のフィード
バック制御によりピストン１３は、トラニオン４を介し
パワーローラ３を、コーンディスク回転軸線からのオフ
セットが０となるようなストローク位置に復帰せしめ、
当該所定変速比を保つ。The operation of the above embodiment will now be described. In FIG. 1, a power roller 3 is rotated to transfer power between an input / output cone disk (not shown) on a main shaft 2,
During this transmission, when the trunnion 4 is stroked by the piston 13 in the direction of the oscillating axis orthogonal to the power roller rotation axis and synchronously and in the same phase, the power roller 3 is offset from the main shaft 2, and the force around the oscillating axis is reduced. Receiving power
The head is swung around the axis. Thus, the diameter of the friction engagement circle of the power roller 3 with respect to the input / output cone disk is continuously changed, and the transmission ratio between the input / output cone disk and
That is, the gear ratio can be changed steplessly. Then, when the gear ratio reaches the predetermined ratio, the piston 13 returns the power roller 3 to a stroke position where the offset from the cone disk rotation axis becomes 0 through the trunnion 4 by well-known feedback control,
The predetermined gear ratio is maintained.
【００３４】ところで、かかる変速に際して行うトラニ
オン４の上記ストローク中、トラニオン４と、アッパリ
ンク５およびロアリンク６との間の交角に係わらず、こ
れらは突起５ｃ，６ｃにおいて接触し続け、これら突起
５ｃ，６ｃを支点として相対的に傾動する。よって、ト
ラニオン４の上記ストローク中、トラニオン４とアッパ
リンク５およびロアリンク６との接触位置がそれぞれ、
アッパリンク５およびロアリンク６との間の交角に係わ
らず、不変に保たれることとなる。By the way, during the above-described stroke of the trunnion 4 performed at the time of shifting, regardless of the angle of intersection between the trunnion 4, the upper link 5 and the lower link 6, they continue to contact at the projections 5c, 6c. , 6c as a fulcrum. Accordingly, during the above-described stroke of the trunnion 4, the contact positions of the trunnion 4, the upper link 5 and the lower link 6 are respectively
Irrespective of the angle of intersection between the upper link 5 and the lower link 6, it is kept unchanged.
【００３５】そして当該接触位置（突起５ｃ，６ｃの位
置）を、図１乃至図３に示す如くアッパリンク５および
ロアリンク６の球面継手嵌合孔５ｂ，６ｂの周縁上で、
隣の球面継手嵌合孔とは反対の側の位置にして、図４に
おける回動中心δの近辺に決定する場合、トラニオン４
とアッパリンク５およびロアリンク６との間の交角に係
わらず、全ての球面継手９，１１について、隣接する球
面継手から遠い側の外側外周面部位とリンク５，６との
間におけるトラニオン軸線方向への摺動量を小さくする
ことが可能で、結果として、前記した根拠から摩擦力が
大きくなる当該球面継手９，１１の外側外周面部位にお
ける摺動量を総体的に小さくし得る。従って、当該球面
継手９，１１の外側外周面部位の大きな摺動に伴い発生
する抵抗力に起因して、従来の摩擦車式無段変速機で図
７（ａ）に示すごとくに生じていた変速制御特性の大き
なヒステリシスを、同図（ｂ）に示すように大幅に小さ
くすることができる。The contact positions (positions of the projections 5c, 6c) are set on the peripheral edges of the spherical joint fitting holes 5b, 6b of the upper link 5 and the lower link 6 as shown in FIGS.
When the position is on the side opposite to the adjacent spherical joint fitting hole and is determined near the rotation center δ in FIG.
Irrespective of the angle of intersection between the upper link 5 and the lower link 6, the trunnion axial direction between all the spherical joints 9 and 11 and the link 5 and 6 between the outer peripheral surface portion remote from the adjacent spherical joint and the links 5 and 6 Can be reduced, and as a result, the sliding amount at the outer peripheral surface of the spherical joints 9, 11 at which the frictional force increases due to the above grounds can be reduced as a whole. Therefore, as shown in FIG. 7A, the friction force is generated by the conventional friction wheel type continuously variable transmission due to the resistance generated by the large sliding of the outer peripheral surface portions of the spherical joints 9 and 11. The large hysteresis of the shift control characteristic can be significantly reduced as shown in FIG.
【００３６】また突起５ｃ，６ｃを図１乃至図３に示す
如くアッパリンク５およびロアリンク６の球面継手嵌合
孔５ｂ，６ｂの周縁上で、隣の球面継手嵌合孔とは反対
の側に配置し、換言すれば突起５ｃ，６ｃを、首振り軸
線方向に見たとき球面継手９，１１の外周縁上で隣のト
ラニオン４から最も遠い側に配置する場合、突起５ｃ，
６ｃは上記の作用効果を奏する他に、リンク５，６に形
成すべき球面継手嵌合孔５ｂ，６ｂに掛からず、該球面
継手嵌合孔５ｂ，６ｂの加工時に、突起５ｃ，６ｃの存
在故に孔５ｂ，６ｂの加工性が低下するといった弊害を
なくすことができる。As shown in FIGS. 1 to 3, the projections 5c and 6c are formed on the peripheral edges of the spherical joint fitting holes 5b and 6b of the upper link 5 and the lower link 6 on the side opposite to the adjacent spherical joint fitting hole. In other words, when the projections 5c, 6c are disposed on the outermost edge of the spherical joints 9, 11 on the outermost edge from the adjacent trunnion 4 when viewed in the direction of the swinging axis, the projections 5c, 6c
In addition to the above-mentioned effects, the spherical joint fitting holes 6b, 6b to be formed in the links 5, 6 do not extend over the spherical joint fitting holes 5b, 6b. Therefore, it is possible to eliminate the adverse effect that the workability of the holes 5b and 6b is reduced.
【００３７】なお、突起５ｃ，６ｃの位置を図５および
図６に示す如く、図４に示す球面継手９，１１の回動中
心δ上に決定する場合、図１乃至図３に示す例において
得られた上記加工上の有利性がなくなる反面、理論上、
変速中における球面継手９，１１とリンク５，６との間
のトラニオン軸線方向における摺動をほとんど生じなく
することができ、従って、球面継手９，１１の上記外側
外周面部位の首振り軸線方向への摺動量をほとんど０に
し得て、上記の作用効果を更に顕著なものにして変速制
御特性のヒステリシスを図７（ｂ）よりも更に一層低下
させることができる点で有利である。When the positions of the projections 5c and 6c are determined on the rotation center δ of the spherical joints 9 and 11 shown in FIG. 4 as shown in FIGS. 5 and 6, in the example shown in FIGS. While the obtained processing advantage is lost, theoretically,
Sliding between the spherical joints 9, 11 and the links 5, 6 in the axial direction of the trunnion during gear shifting can be substantially eliminated. This is advantageous in that the sliding amount can be reduced to almost zero, and the above-described operation and effect can be further remarkable, and the hysteresis of the shift control characteristic can be further reduced as compared with FIG. 7B.
【００３８】[0038]
【発明の効果】かくして第１発明の摩擦車式無段変速機
は、請求項１に記載の如く、変速に際して行う摩擦車支
持部材４のストローク中、該摩擦車支持部材と、これら
摩擦車支持部材の隣接端部同士を連結するリンク５，６
との間の交角に係わらず、これら摩擦車支持部材４およ
びリンク５，６間の接触位置を不変に保つための突起５
ｃ，６ｃを、リンク５，６に設けたから、摩擦車支持部
材４の上記ストローク中、これとリンク５，６とが常時
上記の突起５ｃ，６ｃで接触して接触位置が不変に保た
れることとなり、当該接触位置（突起５ｃ，６ｃの位
置）の選択次第で、全ての摩擦車支持部材４に係わる球
面継手９，１１について、隣接する球面継手から遠い側
の外側外周面部位とリンク５，６との間における摩擦車
支持部材４の軸線方向への摺動量を小さくすることが可
能で、結果として、前記した根拠で摩擦力が大きくなる
当該球面継手９，１１の外側外周面部位における上記摺
動量を総体的に小さくすることができる。従って、球面
継手９，１１の外側外周面部位の大きな摺動に伴い発生
する抵抗力に起因して、従来の摩擦車式無段変速機で生
じていた変速制御特性の大きなヒステリシスを小さくす
ることができる。Thus, in the friction wheel type continuously variable transmission according to the first aspect of the present invention, during the stroke of the friction wheel support member 4 performed at the time of shifting, the friction wheel support member and the friction wheel support member are supported. Links 5, 6 for connecting adjacent ends of members
Projection 5 for keeping the contact position between the friction wheel support member 4 and the links 5 and 6 unchanged regardless of the angle of intersection between
Since the links c and 6c are provided on the links 5 and 6, during the stroke of the friction wheel support member 4, the links 5 and 6 are always in contact with the projections 5c and 6c, and the contact position is kept unchanged. In other words, depending on the selection of the contact position (the position of the protrusions 5c and 6c), the spherical joints 9 and 11 related to all the friction wheel support members 4 are connected to the outer peripheral surface portion on the side farther from the adjacent spherical joint and the link 5 , 6 in the axial direction of the friction wheel support member 4 can be reduced, and as a result, the frictional force increases on the basis of the above-mentioned reason at the outer peripheral surface portions of the spherical joints 9 and 11. The sliding amount can be reduced as a whole. Therefore, the large hysteresis of the shift control characteristic that occurs in the conventional friction wheel type continuously variable transmission due to the resistance generated by the large sliding of the outer peripheral surface portions of the spherical joints 9 and 11 is reduced. Can be.
【００３９】また第２発明の摩擦車式無段変速機は、請
求項２に記載の如く、上記第１発明における突起５ｃ，
６ｃを特に、摩擦車支持部材４の軸線方向に見たとき球
面継手９，１１の外周縁上で隣の摩擦車支持部材から最
も遠い側に配置したから、突起５ｃ，６ｃが上記の摺動
量を確実に小さくする摩擦車支持部材４とリンク５，６
との上記接触位置を提供して上記第１発明の作用効果を
更に確実なものにすると共に、突起５ｃ，６ｃが、リン
ク５，６に形成すべき球面継手嵌合孔５ｂ，６ｂに掛か
らず、該球面継手嵌合孔の加工時に、突起５ｃ，６ｃが
その加工性が低下させるといった弊害をなくすことがで
きる。Further, according to a second aspect of the present invention, there is provided a friction wheel type continuously variable transmission according to the first aspect of the present invention.
6c is arranged on the outer peripheral edge of the spherical joints 9, 11 farthest from the adjacent friction wheel support member when viewed in the axial direction of the friction wheel support member 4, so that the protrusions 5c, 6c have the above-mentioned sliding amount. Wheel support member 4 and links 5 and 6 for reliably reducing
In addition to providing the above-mentioned contact position, the operation and effect of the first invention are further ensured, and the projections 5c, 6c are not hung on the spherical joint fitting holes 5b, 6b to be formed in the links 5, 6. Further, at the time of processing the fitting hole of the spherical joint, it is possible to eliminate the adverse effect that the processability of the projections 5c and 6c is reduced.
【００４０】更に第３発明の摩擦車式無段変速機は、請
求項３に記載の如く、摩擦車支持部材４のストロークに
伴う該摩擦車支持部材および前記リンク５，６間の交角
変化中に生ずる球面継手９，１１の回動中心δ上に、上
記第１発明における突起５ｃ，６ｃを配置したから、当
該突起により提供される摩擦車支持部材４とリンク５，
６との間の不変の接触位置が、上記の回動中心δ上に存
在することとなり、結果として理論上、球面継手９，１
１とリンク５，６との間で首振り軸線方向への摺動を惹
起するようなことがほとんどなくなり、従って、上記球
面継手外側外周面部位の首振り軸線方向への摺動量をほ
とんど０にし得て第１発明の作用効果を第２発明よりも
更に確実なものにすることができる。Further, in the friction wheel type continuously variable transmission according to the third aspect of the present invention, during the change of the angle of intersection between the friction wheel support member and the links 5 and 6 accompanying the stroke of the friction wheel support member 4, Since the projections 5c and 6c according to the first aspect of the present invention are arranged on the center of rotation δ of the spherical joints 9 and 11 generated in the above, the friction wheel support member 4 provided by the projections and the link 5,
6 is present on the above-mentioned center of rotation δ, and as a result, theoretically, the spherical joints 9, 1
There is almost no sliding in the direction of the oscillating axis between 1 and the links 5 and 6. Therefore, the sliding amount of the outer peripheral surface portion of the spherical joint in the direction of the oscillating axis is almost zero. As a result, the operation and effect of the first invention can be made more reliable than the second invention.
【図１】本発明による摩擦車式無段変速機の一実施例を
示す横断正面図である。FIG. 1 is a cross-sectional front view showing an embodiment of a friction wheel type continuously variable transmission according to the present invention.
【図２】（ａ）は同例におけるアッパリンクの縦断側面
図、 （ｂ）は同じくその底面図である。2A is a vertical side view of an upper link in the same example, and FIG. 2B is a bottom view of the same.
【図３】（ａ）は同例におけるロアリンクの縦断側面
図、 （ｂ）は同じくその平面図である。3A is a longitudinal side view of a lower link in the same example, and FIG. 3B is a plan view of the same.
【図４】摩擦車式無段変速機におけるトラニオンからリ
ンクへの応力分布を示すリンクの平面図である。FIG. 4 is a plan view of the link showing a stress distribution from the trunnion to the link in the friction wheel type continuously variable transmission.
【図５】（ａ）は本発明の他の例を示すアッパリンクの
縦断側面図、 （ｂ）は同じくその底面図である。FIG. 5A is a longitudinal side view of an upper link showing another example of the present invention, and FIG. 5B is a bottom view of the same.
【図６】（ａ）は同例におけるロアリンクの縦断側面
図、 （ｂ）は同じくその平面図である。FIG. 6A is a longitudinal side view of a lower link in the same example, and FIG. 6B is a plan view of the same.
【図７】（ａ）は従来の摩擦車式無段変速機における変
速制御特性を示す線図、 （ｂ）は図１乃至図３に示す摩擦車式無段変速機の変速
制御特性を示す線図である。FIG. 7A is a diagram showing shift control characteristics of a conventional friction wheel type continuously variable transmission, and FIG. 7B is a diagram showing shift control characteristics of the friction wheel type continuously variable transmission shown in FIGS. 1 to 3; FIG.
【図８】従来型摩擦車式無段変速機の動作説明図であ
る。FIG. 8 is an operation explanatory view of a conventional friction wheel type continuously variable transmission.
１ 変速機ケース ２ 主軸 ３ パワーローラ（摩擦車） ４ トラニオン（摩擦車支持部材） ５ アッパリンク ５C 突起 ６ ロアリンク ６C 突起 ７ リンクサポート ８ リンクサポート ９ 球面継手 δ 同球面継手の回動中心 10 軸受 11 球面継手 12 軸受 13 ピストンDESCRIPTION OF SYMBOLS 1 Transmission case 2 Main shaft 3 Power roller (friction wheel) 4 Trunnion (friction wheel support member) 5 Upper link 5 C protrusion 6 Lower link 6 C protrusion 7 Link support 8 Link support 9 Spherical joint δ Rotation center of the same spherical joint 10 Bearing 11 Spherical joint 12 Bearing 13 Piston
Claims (3)
を行うよう、該入出力ディスクの回転軸線周りに配置さ
れた複数の摩擦車と、 各摩擦車を回転自在に支持した摩擦車支持部材と、 該摩擦車支持部材の隣合う端部同士を相互に、摩擦車支
持部材が摩擦車の回転軸線と直交する首振り軸線方向へ
同期してストロークされるよう、球面継手を介して連結
するリンクとを具え、 該摩擦車支持部材のストロークにより前記摩擦車の首振
り軸線周りの傾転を生起させて変速を行うようにした摩
擦車式無段変速機において、 前記摩擦車支持部材のストローク中、該摩擦車支持部材
と前記リンクとの間の交角に係わらず、これら摩擦車支
持部材およびリンク間の接触位置を不変に保つための突
起をリンクに設けたことを特徴とする摩擦車式無段変速
機。An input / output disk arranged coaxially and opposed, and a plurality of friction wheels arranged around a rotation axis of the input / output disk so as to transfer power by frictional engagement between the input / output disks, A friction wheel support member rotatably supporting each friction wheel, and adjacent ends of the friction wheel support members are synchronized with each other in such a manner that the friction wheel support member is oscillated in the direction of a swing axis orthogonal to the rotation axis of the friction wheel. And a link connected via a spherical joint so as to be stroked. A friction wheel type in which the stroke of the friction wheel is caused to tilt about the oscillating axis of the friction wheel by the stroke of the friction wheel support member to perform a gear shift. In the continuously variable transmission, a projection for keeping a contact position between the friction wheel support member and the link unchanged regardless of an intersection angle between the friction wheel support member and the link during a stroke of the friction wheel support member. Friction wheel continuously variable transmission, characterized in that provided in the link.
振り軸線方向に見たとき前記球面継手の外周縁上で隣の
摩擦車支持部材から最も遠い側に配置したことを特徴と
する摩擦車式無段変速機。2. The friction member according to claim 1, wherein the projection is disposed on the outer peripheral edge of the spherical joint and farthest from an adjacent friction wheel support member when viewed in the direction of the oscillating axis. Vehicle type continuously variable transmission.
のストロークに伴う該摩擦車支持部材および前記リンク
間の交角変化中に生ずる前記球面継手の回動中心上に前
記突起を配置したことを特徴とする摩擦車式無段変速
機。3. The method according to claim 1, wherein the protrusion is arranged on a center of rotation of the spherical joint generated during a change in an angle of intersection between the friction wheel support member and the link with a stroke of the friction wheel support member. Features a friction wheel type continuously variable transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5322206A JP3022112B2 (en) | 1993-12-21 | 1993-12-21 | Friction wheel type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5322206A JP3022112B2 (en) | 1993-12-21 | 1993-12-21 | Friction wheel type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07174201A JPH07174201A (en) | 1995-07-11 |
| JP3022112B2 true JP3022112B2 (en) | 2000-03-15 |
Family
ID=18141145
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5322206A Expired - Lifetime JP3022112B2 (en) | 1993-12-21 | 1993-12-21 | Friction wheel type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3022112B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3463624B2 (en) * | 1999-09-27 | 2003-11-05 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
| JP3463625B2 (en) * | 1999-09-27 | 2003-11-05 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
| JP4941712B2 (en) * | 2006-08-22 | 2012-05-30 | 日本精工株式会社 | Toroidal continuously variable transmission |
| US8876654B2 (en) | 2009-11-25 | 2014-11-04 | Nsk Ltd. | Toroidal continuously variable transmission |
-
1993
- 1993-12-21 JP JP5322206A patent/JP3022112B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07174201A (en) | 1995-07-11 |
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