JPH0640501U - Toroidal type continuously variable transmission - Google Patents
Toroidal type continuously variable transmissionInfo
- Publication number
- JPH0640501U JPH0640501U JP8026192U JP8026192U JPH0640501U JP H0640501 U JPH0640501 U JP H0640501U JP 8026192 U JP8026192 U JP 8026192U JP 8026192 U JP8026192 U JP 8026192U JP H0640501 U JPH0640501 U JP H0640501U
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- JP
- Japan
- Prior art keywords
- surface portion
- input
- concave surface
- continuously variable
- type continuously
- Prior art date
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Abstract
(57)【要約】
【目的】パワーローラ７の球面部２３の母線長さＬを確
保して、この球面部２３から外れた部分が相手部材と接
触するのを防止し、この相手部材の耐久性向上を図る。
【構成】パワーローラ７の片側面内周縁部に円筒面部２
４を形成する。この円筒面部２４は、スラスト軸受を構
成する玉２１、２１の内側に位置させる。球面部２３を
加工する際には、この円筒面部２４をシュータイプのホ
ルダに保持する。
(57) [Abstract] [Purpose] To secure a generatrix length L of the spherical surface portion 23 of the power roller 7 to prevent a portion deviated from the spherical surface portion 23 from coming into contact with a mating member, and durability of the mating member. To improve the sex. [Structure] The cylindrical surface portion 2 is provided on the inner peripheral edge of one side surface of the power roller 7.
4 is formed. The cylindrical surface portion 24 is located inside the balls 21, 21 that form the thrust bearing. When processing the spherical surface portion 23, the cylindrical surface portion 24 is held by a shoe type holder.
Description
【０００１】[0001]
この考案に係るトロイダル型無段変速機は、自動車用変速機等として利用出来 る。 The toroidal type continuously variable transmission according to this invention can be used as a transmission for automobiles.
【０００２】[0002]
自動車用変速機として、図３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に対し捻れの位置にある枢軸１６、１ ６を中心として揺動する、トラニオン５、５が設けられている。 The use of a toroidal type continuously variable transmission as schematically shown in Fig. 3 has been studied as a vehicle transmission. 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. On the inner surface of the casing accommodating the toroidal type continuously variable transmission, or on the support bracket provided in this casing, the pivots 16, 16 in the twisted position with respect to the input shaft 1 and the output shaft 3 are centered. Trunnions 5 and 5 that swing as are provided.
【０００３】 各トラニオン５、５は、十分な剛性を有する金属材により形成されたもので、 両端部外側面に前記枢軸１６、１６を設けている。又、各トラニオン５の中心部 に設けた変位軸６、６の周囲には、それぞれパワーローラ７、７を回転自在に支 持している。そして、各パワーローラ７、７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。Each trunnion 5, 5 is made of a metal material having sufficient rigidity, and the pivots 16, 16 are provided on the outer surfaces of both ends. Further, power rollers 7, 7 are rotatably supported around displacement shafts 6, 6 provided at the center of each trunnion 5, respectively. The power rollers 7, 7 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の軸方向片側面で、互いに対向する面には、 それぞれ断面が前記枢軸１６、１６を中心とする円弧形の入力側凹面２ａ、出力 側凹面４ａを形成している。そして、球状凸面に形成された各パワーローラ７、 ７の外周面７ａ、７ａを、前記入力側凹面２ａ及び出力側凹面４ａに当接させて いる。On the axially opposite side surfaces of both the input side and output side disks 2 and 4, the surfaces facing each other have an arcuate input side concave surface 2 a having a cross section centered on the pivots 16 and 16 and an output side. The concave surface 4a is formed. The outer peripheral surfaces 7a, 7a of the power rollers 7, 7 formed in the spherical convex surface are brought into contact with the input side concave surface 2a and the output side concave surface 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加圧装置 ８を設け、この加圧装置８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。この加圧装置８は、入力軸１と共に回転するカム 板９と、保持器１０により保持された複数個（例えば４個）のローラ１１、１１ とから構成されている。前記カム板９の片側面（図３の右側面）には、円周方向 に亙る凹凸面であるカム面１２を形成し、又、前記入力側ディスク２の外側面（ 図３の左側面）にも、同様のカム面１３を形成している。そして、前記複数個の ローラ１１、１１を、前記入力軸１の中心に対して放射方向の軸を中心に、回転 自在としている。A loading cam type pressurizing device 8 is provided between the input shaft 1 and the input side disc 2, and the pressurizing device 8 elastically directs the input side disc 2 toward the output side disc 4. Is pressed against. The pressurizing device 8 is composed of a cam plate 9 that rotates together with the input shaft 1, and a plurality of (for example, four) rollers 11 and 11 held by a holder 10. On one side surface (right side surface in FIG. 3) of the cam plate 9, there is formed a cam surface 12 which is an uneven surface extending in the circumferential direction, and the outer side surface of the input side disk 2 (left side surface in FIG. 3). Also, a similar cam surface 13 is formed. The plurality of rollers 11, 11 are rotatable about an axis in the radial direction with respect to the center of the input shaft 1.
【０００６】 入力軸１の回転に伴なってカム板９が回転すると、カム面１２によって複数個 のローラ１１、１１が、入力側ディスク２外側面のカム面１３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７、７に押圧される と同時に、前記１対のカム面１２、１３と複数個のローラ１１、１１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７、７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 9 rotates in accordance with the rotation of the input shaft 1, the cam surface 12 presses the plurality of rollers 11, 11 against the cam surface 13 on the outer surface of the input side disk 2. As a result, the input side disk 2 is pressed by the plurality of power rollers 7, 7 and at the same time, based on the meshing between the pair of cam surfaces 12, 13 and the plurality of rollers 11, 11. The input side disk 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 7, 7, and the output shaft 3 fixed to the output side disk 4 rotates.
【０００７】 尚、前記各変位軸６、６の基端部には外輪１４、１４を設け、各外輪１４、１ ４とパワーローラ７、７との間に設けた円環状の保持器１５、１５に、複数の転 動体（通常は玉２１、２１。後述する図２参照）を転動自在に保持して、各外輪 １４、１４に対するパワーローラ７、７の回転を自在としている。又、図示は省 略したが、前記各変位軸６、６の外周面と各パワーローラ７、７の内周面との間 にも複数の転動体（通常はニードル）を設けて、各変位軸６、６に対するパワー ローラ７、７の回転を自在としている。Outer rings 14, 14 are provided at the base ends of the displacement shafts 6, 6, and an annular cage 15, provided between the outer rings 14, 14 and the power rollers 7, 7, A plurality of rolling elements (usually balls 21, 21; see FIG. 2 to be described later) are rotatably held by 15, and the power rollers 7, 7 can freely rotate with respect to the outer rings 14, 14. Although not shown, a plurality of rolling elements (usually needles) are provided between the outer peripheral surface of each of the displacement shafts 6, 6 and the inner peripheral surface of each of the power rollers 7, 7 to provide each displacement. The power rollers 7, 7 can freely rotate about the shafts 6, 6.
【０００８】 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、図３（Ａ）に示す様に、枢軸１６、１６を中心と して各トラニオン５、５を揺動させ、各パワーローラ７、７の外周面７ａ、７ａ が、入力側凹面２ａの中心寄り部分と、出力側凹面４ａの外周寄り部分とに、そ れぞれ当接する様に、各変位軸６、６を傾斜させる。反対に、増速を行なう場合 には、前記トラニオン５、５を同図（Ｂ）に示す様に揺動させ、各パワーローラ ７、７の外周面７ａ、７ａが、入力側凹面２ａの外周寄り部分と、出力側凹面４ ａの中心寄り部分とに、それぞれ当接する様に、各変位軸６、６を傾斜させる。 各変位軸６、６の傾斜角度を、図３（Ａ）と同図（Ｂ）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 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, as shown in FIG. , 16 are oscillated around the trunnions 5 and 5, and the outer peripheral surfaces 7a and 7a of the power rollers 7 and 7 are divided into a central portion of the input side concave surface 2a and an outer peripheral portion of the output side concave surface 4a. Then, the displacement shafts 6, 6 are tilted so that they are brought into contact with each other. On the other hand, when increasing the speed, the trunnions 5 and 5 are swung as shown in FIG. 7B, and the outer peripheral surfaces 7a and 7a of the power rollers 7 and 7 are aligned with the outer peripheral surface of the input side concave surface 2a. The displacement shafts 6, 6 are tilted so that the displacement shafts 6 and 6 come into contact with the displacement portion and the center portion of the output side concave surface 4a, respectively. If the inclination angles of the displacement shafts 6, 6 are set in the middle of FIG. 3 (A) and FIG. 3 (B), an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.
【０００９】 前記パワーローラ７、７の外周面７ａ、７ａは、前記各凹面２ａ、４ａと接触 自在な球状凸面とされているが、研磨機等の加工機を使用してこの球状凸面を形 成する為には、前記パワーローラ７、７をシュータイプのホルダに保持する必要 がある。この為に従来は、パワーローラ７の外周面７ａを、図２に示す様に球面 部１７と円筒面部１８とから構成していた。この内の球面部１７の中心は、前記 枢軸１６の中心線上に位置させ、円筒面部１８の中心は、前記変位軸６の中心に 一致させている。前記球面部１７の加工を行なう際には、加工機のホルダ部分に 前記円筒面部１８を保持した状態で、加工作業を行なう。The outer peripheral surfaces 7a, 7a of the power rollers 7, 7 are spherical convex surfaces that can come into contact with the concave surfaces 2a, 4a, and the spherical convex surfaces are formed using a processing machine such as a polishing machine. In order to achieve this, it is necessary to hold the power rollers 7, 7 in a shoe type holder. For this reason, conventionally, the outer peripheral surface 7a of the power roller 7 is composed of a spherical surface portion 17 and a cylindrical surface portion 18 as shown in FIG. The center of the spherical surface portion 17 is located on the center line of the pivot shaft 16, and the center of the cylindrical surface portion 18 is aligned with the center of the displacement shaft 6. When processing the spherical surface portion 17, the processing operation is performed with the cylindrical surface portion 18 held in the holder portion of the processing machine.
【００１０】[0010]
本考案のトロイダル型無段変速機は、パワーローラ７、７の角部が入力側凹面 ２ａ或は出力側凹面４ａに当たる危険性を低くする事で、耐久性の向上を図るも のである。 The toroidal type continuously variable transmission of the present invention improves durability by reducing the risk of the corners of the power rollers 7, 7 hitting the input side concave surface 2a or the output side concave surface 4a.
【００１１】 図２に示した従来構造の様に、パワーローラ７の外周面７ａに、球面部１７と この球面部１７の端部から連続する円筒面部１８とを形成した場合、パワーロー ラ７の大きさを同じとすると、前記球面部１７の母線の長さｌが、前記円筒面部 １８を設けない場合に比べて短くなる事が避けられない。When the spherical surface portion 17 and the cylindrical surface portion 18 continuous from the end of the spherical surface portion 17 are formed on the outer peripheral surface 7 a of the power roller 7 as in the conventional structure shown in FIG. If the same size is used, it is inevitable that the length l of the generatrix of the spherical surface portion 17 becomes shorter than that in the case where the cylindrical surface portion 18 is not provided.
【００１２】 一方、前記球面部１７と、入力側凹面２ａ及び出力側凹面４ａとは、トロイダ ル型無段変速機の使用時に於いて、各面の母線方向をその長径とする楕円形部分 （接触楕円）で接触する。通常の使用状態に於いては、この接触楕円の長径は小 さく、この接触楕円が前記球面部１７からはみ出す事はないが、何らかの原因で トロイダル型無段変速機により伝達されるトルクが過大になると、前記接触楕円 の長径方向片端部が、前記球面部１７からはみ出す事が考えられる。On the other hand, the spherical surface portion 17 and the input-side concave surface 2a and the output-side concave surface 4a are elliptical portions whose major axis is the generatrix direction of each surface when the toroidal type continuously variable transmission is used. Contact with a contact ellipse). In a normal use condition, the major axis of this contact ellipse is small and this contact ellipse does not protrude from the spherical portion 17, but for some reason, the torque transmitted by the toroidal type continuously variable transmission becomes excessive. Then, it is conceivable that one end of the contact ellipse in the major axis direction extends from the spherical surface portion 17.
【００１３】 前記接触楕円が前記球面部１７からはみ出すと、この球面部１７と前記円筒面 部１８との境界部分に存在するエッジ１９が、前記入力側凹面２ａ及び出力側凹 面４ａに接触する。この様にして、尖ったエッジ１９が各凹面２ａ、４ａに接触 すると、各凹面２ａ、４ａの一部に過大な応力が加わり、各凹面２ａ、４ａの表 面が剥離する恐れがある。When the contact ellipse protrudes from the spherical surface portion 17, the edge 19 existing at the boundary between the spherical surface portion 17 and the cylindrical surface portion 18 contacts the input side concave surface 2a and the output side concave surface 4a. . When the sharp edge 19 contacts the concave surfaces 2a, 4a in this manner, excessive stress is applied to a part of the concave surfaces 2a, 4a, and the surface of each concave surface 2a, 4a may be peeled off.
【００１４】 本考案のトロイダル型無段変速機は、上述の様な事情に鑑みて考案されたもの である。The toroidal type continuously variable transmission of the present invention was devised in view of the above circumstances.
【００１５】[0015]
本考案の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 と同様に、入力軸と、軸方向片面を断面が円弧形の入力側凹面とし、この入力軸 の回転に伴なって回転する入力側ディスクと、軸方向片面を断面が円弧形の出力 側凹面とし、この出力側凹面と前記入力側凹面とを対向させた状態で、且つ、前 記入力軸に対する回転を自在として、前記入力軸と同心に支持された出力側ディ スクと、前記入力軸に対し捻れの位置にある枢軸を中心として揺動する複数のト ラニオンと、各トラニオンに基端部を支持固定された変位軸と、各変位軸の基端 部周囲に設けられた外輪と、前記各変位軸の先端部に回転自在に支持された円環 状のパワーローラと、各パワーローラと前記各外輪との間に転動自在に設けられ た複数の転動体とを備え、前記各パワーローラは、前記入力側凹面及び出力側凹 面に当接する球面部及びこの球面部を加工する為の円筒面部をその外周面に、前 記複数の転動体を当接させる軌道をその片側面に、それぞれ有する。 The toroidal type continuously variable transmission according to the present invention, like the conventional toroidal type continuously variable transmission described above, has an input shaft and one side in the axial direction which is a concave surface on the input side with an arcuate cross section. With the input side disk rotating with it, the output side concave surface of which one side in the axial direction has an arcuate cross section is formed, and the output side concave surface and the input side concave surface are opposed to each other, and rotation with respect to the input shaft is performed. Freely, the output side disc is supported concentrically with the input shaft, a plurality of trunnions swinging around a pivot shaft in a twisted position with respect to the input shaft, and a base end part is supported by each trunnion. A fixed displacement shaft, an outer ring provided around the base end of each displacement shaft, an annular power roller rotatably supported at the distal end of each displacement shaft, each power roller and each A plurality of rolling elements that can be rolled between the outer ring Each of the power rollers has a spherical surface portion that abuts on the concave surface on the input side and a concave surface on the output side, and a cylindrical surface portion for processing the spherical surface portion, the outer peripheral surface of which abuts the plurality of rolling elements. Each has a track on one side.
【００１６】 特に、本考案のトロイダル型無段変速機に於いては、前記円筒面部の外径は、 前記複数の転動体の内接円の直径よりも小さく、且つ、この円筒面部は、前記片 側面の一部で前記軌道の内側部分に存在する事を特徴としている。In particular, in the toroidal type continuously variable transmission of the present invention, the outer diameter of the cylindrical surface portion is smaller than the diameter of the inscribed circle of the plurality of rolling elements, and the cylindrical surface portion is It is characterized in that it exists in the inner part of the track on a part of one side surface.
【００１７】[0017]
上述の様に構成される本考案のトロイダル型無段変速機により、入力軸と出力 軸との間で変速比を自在に変える際の作用自体は、前述した従来のトロイダル型 無段変速機の場合と同様である。 With the toroidal type continuously variable transmission of the present invention configured as described above, the action itself at the time of freely changing the speed ratio between the input shaft and the output shaft is the same as that of the conventional toroidal type continuously variable transmission described above. It is similar to the case.
【００１８】 特に、本考案のトロイダル型無段変速機の場合、パワーローラの球面部の母線 の長さを十分に確保しつつ、工業的手法によりこの球面部を研磨する事が可能と なる。この為、前記パワーローラの外周面で、前記球面部から外れた部分と、入 力側凹面及び出力側凹面とが接触する事がなくなり、各凹面に過大な応力が加わ る事で、各凹面が損傷を受ける事がなくなる。Particularly, in the case of the toroidal type continuously variable transmission of the present invention, it is possible to polish the spherical portion by an industrial method while sufficiently securing the length of the generatrix of the spherical portion of the power roller. Therefore, on the outer peripheral surface of the power roller, the part deviated from the spherical portion and the concave surface on the input side and the concave surface on the output side do not come into contact with each other, and excessive stress is applied to each concave surface. Will not be damaged.
【００１９】[0019]
図１は本考案の実施例を示している。尚、本考案のトロイダル型無段変速機は 、パワーローラの形状に特徴があり、基本的構成は、前記図３に示した従来構造 と同様である為、重複する説明を省略する。 FIG. 1 shows an embodiment of the present invention. The toroidal type continuously variable transmission according to the present invention is characterized by the shape of the power roller, and the basic structure is the same as the conventional structure shown in FIG.
【００２０】 組み立てた状態で互いに対向する、変位軸６（図３）の基端部周囲に設けられ た円輪状の外輪１４の片面（図１の下面）と、前記変位軸６の先端部に回転自在 に支持された円環状のパワーローラ７の片側面（図１の上面）とには、それぞれ 軌道２０ａ、２０ｂを形成している。そして、両軌道２０ａ、２０ｂの間に複数 の玉２１、２１を転動自在に設け、前記パワーローラ７に加わるスラスト荷重を 支承する為の、スラスト軸受を構成している。前記各玉２１、２１は、合成樹脂 製の保持器２２により、転動自在に保持されている。In the assembled state, one surface (a lower surface in FIG. 1) of a circular ring-shaped outer ring 14 provided around the base end portion of the displacement shaft 6 (FIG. 3) and the tip end portion of the displacement shaft 6 that face each other. Tracks 20a and 20b are respectively formed on one side surface (the upper surface in FIG. 1) of the annular power roller 7 rotatably supported. A plurality of balls 21, 21 are rotatably provided between the two orbits 20a, 20b to form a thrust bearing for bearing a thrust load applied to the power roller 7. The balls 21, 21 are rotatably held by a cage 22 made of synthetic resin.
【００２１】 前記パワーローラ７の外周面７ａには、入力側ディスク２の入力側凹面２ａ及 び出力側ディスク４の出力側凹面４ａ（図３）に当接する球面部２３と、この球 面部２３を加工する為の円筒面部２４とを形成している。On the outer peripheral surface 7 a of the power roller 7, a spherical surface portion 23 that comes into contact with the input concave surface 2 a of the input disk 2 and the output concave surface 4 a of the output disk 4 (FIG. 3), and the spherical surface portion 23 And a cylindrical surface portion 24 for processing the.
【００２２】 本考案のトロイダル型無段変速機に於いて、前記円筒面部２４の外径Ｄは、前 記複数の玉２１、２１の内接円の直径Ｒよりも小さく（Ｄ＜Ｒ）している。そし て、この円筒面部２４は、前記パワーローラ７の片側面の内周縁部で、前記軌道 ２０ｂの内側部分に存在する。In the toroidal type continuously variable transmission of the present invention, the outer diameter D of the cylindrical surface portion 24 is smaller than the diameter R of the inscribed circle of the plurality of balls 21, 21 (D <R). ing. Then, the cylindrical surface portion 24 exists on the inner peripheral portion of one side surface of the power roller 7 and inside the track 20b.
【００２３】 この様な円筒面部２４を、前記パワーローラ７の片側面に形成するのに伴なっ て、前記保持器２２の内周寄り部分は薄肉部２５とし、この保持器２２と前記円 筒面部２４とが干渉する事を防止している。Along with the formation of such a cylindrical surface portion 24 on one side surface of the power roller 7, the inner peripheral portion of the retainer 22 is formed as a thin portion 25, and the retainer 22 and the circular cylinder are formed. The interference with the surface portion 24 is prevented.
【００２４】 上述の様に構成される本考案のトロイダル型無段変速機の場合、パワーローラ ７の球面部２３の母線の長さＬを十分に確保しつつ、工業的手法によりこの球面 部２３を研磨する事が可能となる。In the case of the toroidal type continuously variable transmission of the present invention configured as described above, the spherical length 23 of the power roller 7 is secured by the industrial method while ensuring a sufficient length L of the busbar of the spherical portion 23. It is possible to polish.
【００２５】 即ち、研磨機等の加工機を使用して前記球面部２３を加工する場合、前記円筒 面部２４をシュータイプのホルダ部分に保持した状態で、加工作業を行なう。本 考案のトロイダル型無段変速機に組み込むパワーローラ７の場合、前記円筒面部 ２４を、玉２１、２１の内側部分に設けた為、前記図２に示した従来構造の如く 、球面部１７の大径側端部から連続する円筒面部１８を設けた場合に比べて、球 面部２３の母線長さＬを大きく出来る。That is, when processing the spherical surface portion 23 using a processing machine such as a polishing machine, the processing operation is performed with the cylindrical surface portion 24 being held by the shoe type holder portion. In the case of the power roller 7 incorporated in the toroidal type continuously variable transmission of the present invention, since the cylindrical surface portion 24 is provided inside the balls 21 and 21, the spherical surface portion 17 of the spherical portion 17 is provided as in the conventional structure shown in FIG. The generatrix length L of the spherical surface portion 23 can be made larger than in the case where the cylindrical surface portion 18 continuous from the large diameter side end portion is provided.
【００２６】 この為、伝達トルクが大きくなり、前記球面部２３と、入力側凹面２ａ及び出 力側凹面４ａとの接触楕円が大きくなった場合でも、前記パワーローラ７の外周 面で、前記球面部２３から外れた部分と、入力側凹面２ａ及び出力側凹面４ａと が接触する事がなくなる。この結果、各凹面２ａ、４ａに過大な応力が加わる事 で、各凹面２ａ、４ａが損傷を受ける事がなくなる。しかも、加工時に保持する 為の円筒面部２４を玉２１、２１の内側に配置している為、パワーローラ７とス ラスト軸受とを合わせた部分の厚さ寸法が大きくなる事もない。Therefore, even when the transmission torque becomes large and the contact ellipse between the spherical surface portion 23 and the input-side concave surface 2a and the output-side concave surface 4a becomes large, the spherical surface is formed on the outer peripheral surface of the power roller 7. It is possible to prevent the portion separated from the portion 23 from coming into contact with the input side concave surface 2a and the output side concave surface 4a. As a result, excessive stress is applied to the concave surfaces 2a and 4a, so that the concave surfaces 2a and 4a are not damaged. Moreover, since the cylindrical surface portion 24 for holding at the time of processing is arranged inside the balls 21, 21, the thickness dimension of the combined portion of the power roller 7 and the thrust bearing does not become large.
【００２７】 又、図２に示す円筒面部１８をなくす事により、球面部２３の母線の長さをｌ からＬに大きく出来るので、パワーローラ７の端面により構成される内輪の最大 外径をｄS からｄL へと大きく出来る。この結果、玉２１、２１のピッチ円直径 （P.C.D ）も大きく出来るので、玉２１、２１の直径を大きくするか、或は玉２ １、２１の数を増やす事が可能となり、スラスト軸受の負荷容量を大きく出来る 。従って本考案により、同じ大きさのパワーローラ７でもより大きなトルクを伝 達出来る。Further, by eliminating the cylindrical surface portion 18 shown in FIG. 2, the length of the generatrix of the spherical surface portion 23 can be increased from 1 to L, so that the maximum outer diameter of the inner ring formed by the end surface of the power roller 7 is d. It can be increased from S to d L. As a result, the pitch circle diameter (PCD) of the balls 21, 21 can be increased, so that the diameter of the balls 21, 21 can be increased or the number of balls 21, 21 can be increased, and the load of the thrust bearing can be increased. The capacity can be increased. Therefore, according to the present invention, even a power roller 7 having the same size can transmit a larger torque.
【００２８】[0028]
本考案のトロイダル型無段変速機は、以上に述べた通り構成され作用する為、 小型で耐久性が優れたトロイダル型無段変速機を、工業的手法により造る事が可 能となる。 Since the toroidal type continuously variable transmission of the present invention is configured and operates as described above, it becomes possible to manufacture a toroidal type continuously variable transmission that is small and has excellent durability by an industrial method.
【図１】本考案のトロイダル型無段変速機に組み込まれ
るパワーローラをスラスト軸受と共に示す断面図。FIG. 1 is a sectional view showing a power roller incorporated in a toroidal type continuously variable transmission according to the present invention together with a thrust bearing.
【図２】従来のトロイダル型無段変速機に組み込まれる
パワーローラをスラスト軸受と共に示す断面図。FIG. 2 is a sectional view showing a power roller incorporated in a conventional toroidal type continuously variable transmission together with a thrust bearing.
【図３】トロイダル型無段変速機の基本構造を、最大減
速時と最大増速時との状態で示す側面図。FIG. 3 is a side view showing the basic structure of the toroidal type continuously variable transmission in a state of maximum deceleration and a state of maximum acceleration.
【符号の説明】 １ 入力軸 ２ 入力側ディスク ２ａ 入力側凹面 ３ 出力軸 ４ 出力側ディスク ４ａ 出力側凹面 ５ トラニオン ６ 変位軸 ７ パワーローラ ７ａ 外周面 ８ 加圧装置 ９ カム板 １０ 保持器 １１ ローラ １２ カム面 １３ カム面 １４ 外輪 １５ 保持器 １６ 枢軸 １７ 球面部 １８ 円筒面部 １９ エッジ ２０ａ 軌道 ２０ｂ 軌道 ２１ 玉 ２２ 保持器 ２３ 球面部 ２４ 円筒面部 ２５ 薄肉部[Explanation of reference symbols] 1 input shaft 2 input side disc 2a input side concave surface 3 output shaft 4 output side disk 4a output side concave surface 5 trunnion 6 displacement shaft 7 power roller 7a outer peripheral surface 8 pressurizing device 9 cam plate 10 cage 11 roller 12 cam surface 13 cam surface 14 outer ring 15 retainer 16 pivot 17 spherical surface portion 18 cylindrical surface portion 19 edge 20a track 20b track 21 ball 22 retainer 23 spherical surface portion 24 cylindrical surface portion 25 thin portion
Claims (1)
入力側凹面とし、この入力軸の回転に伴なって回転する
入力側ディスクと、軸方向片面を断面が円弧形の出力側
凹面とし、この出力側凹面と前記入力側凹面とを対向さ
せた状態で、且つ、前記入力軸に対する回転を自在とし
て、前記入力軸と同心に支持された出力側ディスクと、
前記入力軸に対し捻れの位置にある枢軸を中心として揺
動する複数のトラニオンと、各トラニオンに基端部を支
持固定された変位軸と、各変位軸の基端部周囲に設けら
れた外輪と、前記各変位軸の先端部に回転自在に支持さ
れた円環状のパワーローラと、各パワーローラと前記各
外輪との間に転動自在に設けられた複数の転動体とを備
え、前記各パワーローラは、前記入力側凹面及び出力側
凹面に当接する球面部及びこの球面部を加工する為の円
筒面部をその外周面に、前記複数の転動体を当接させる
軌道をその片側面に、それぞれ有するトロイダル型無段
変速機に於いて、前記円筒面部の外径は、前記複数の転
動体の内接円の直径よりも小さく、且つ、この円筒面部
は、前記片側面の一部で前記軌道の内側部分に存在する
事を特徴とするトロイダル型無段変速機。1. An input shaft and an input side concave surface of which one side in the axial direction has an arcuate section, and an input side disk which rotates with the rotation of the input shaft and one side in the axial direction have an arcuate section. An output side concave surface, an output side disk supported concentrically with the input shaft in a state in which the output side concave surface and the input side concave surface are opposed to each other and freely rotatable with respect to the input shaft,
A plurality of trunnions swinging around a pivot in a twisted position with respect to the input shaft, a displacement shaft having a base end supported and fixed to each trunnion, and an outer ring provided around the base end of each displacement shaft. And an annular power roller rotatably supported at the tip of each displacement shaft, and a plurality of rolling elements rotatably provided between each power roller and each outer ring, Each power roller has a spherical surface portion that abuts on the input-side concave surface and the output-side concave surface and a cylindrical surface portion for processing the spherical surface portion on its outer peripheral surface, and an orbit for abutting the plurality of rolling elements on one side surface thereof. In each of the toroidal type continuously variable transmissions, the outer diameter of the cylindrical surface portion is smaller than the diameter of the inscribed circle of the plurality of rolling elements, and the cylindrical surface portion is a part of the one side surface. To be characterized by being present in the inner part of the orbit. Idar-type continuously variable transmission.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992080261U JP2598886Y2 (en) | 1992-10-28 | 1992-10-28 | Toroidal type continuously variable transmission |
| US08/095,014 US5391126A (en) | 1992-08-05 | 1993-07-22 | Toroidal type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992080261U JP2598886Y2 (en) | 1992-10-28 | 1992-10-28 | Toroidal type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0640501U true JPH0640501U (en) | 1994-05-31 |
| JP2598886Y2 JP2598886Y2 (en) | 1999-08-23 |
Family
ID=13713378
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1992080261U Expired - Fee Related JP2598886Y2 (en) | 1992-08-05 | 1992-10-28 | Toroidal type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2598886Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6945904B2 (en) | 2002-01-17 | 2005-09-20 | Nsk Ltd. | Toroidal-type continuously variable transmission |
-
1992
- 1992-10-28 JP JP1992080261U patent/JP2598886Y2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6945904B2 (en) | 2002-01-17 | 2005-09-20 | Nsk Ltd. | Toroidal-type continuously variable transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2598886Y2 (en) | 1999-08-23 |
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