JP5834525B2

JP5834525B2 - Toroidal continuously variable transmission

Info

Publication number: JP5834525B2
Application number: JP2011137178A
Authority: JP
Inventors: 豊田　俊郎; 俊郎豊田; 優也大黒
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2011-06-21
Filing date: 2011-06-21
Publication date: 2015-12-24
Anticipated expiration: 2031-06-21
Also published as: JP2013002609A

Description

この発明は、例えば車両（自動車）用の自動変速機、建設機械（建機）用の自動変速機、航空機（固定翼機、回転翼機、飛行船等）等で使用されるジェネレータ（発電機）用の自動変速機、ポンプ等の各種産業機械の運転速度を調節する為の自動変速機として利用する、ハーフトロイダル型のトロイダル型無段変速機の改良に関する。 The present invention relates to a generator (generator) used in, for example, an automatic transmission for a vehicle (automobile), an automatic transmission for a construction machine (construction machine), an aircraft (a fixed wing aircraft, a rotary wing aircraft, an airship, etc.), etc. The present invention relates to improvement of a half toroidal toroidal continuously variable transmission that is used as an automatic transmission for adjusting the operating speed of various industrial machines such as automatic transmissions and pumps.

自動車用変速装置としてハーフトロイダル型のトロイダル型無段変速機を使用する事が、特許文献１〜４等の多くの刊行物に記載されると共に一部で実施されていて周知である。又、トロイダル型無段変速機と遊星歯車機構とを組み合わせて変速比の調整幅を広くする構造も、特許文献５等、やはり多くの刊行物に記載されて、従来から広く知られている。図１１〜１２は、これら各特許文献に記載されて従来から広く知られているトロイダル型無段変速機の第１例を示している。この従来構造の第１例の場合、入力回転軸１の両端寄り部分の周囲に１対の入力ディスク２、２を、それぞれがトロイド曲面である内側面同士を互いに対向させた状態で、前記入力回転軸１と同期した回転を自在に支持している。又、この入力回転軸１の中間部周囲に出力筒３を、この入力回転軸１に対する回転を自在に支持している。又、この出力筒３の外周面には、軸方向中央部に出力歯車４を固設すると共に、軸方向両端部に１対の出力ディスク５、５を、スプライン係合により、前記出力筒３と同期した回転を自在に支持している。又、この状態で、それぞれがトロイド曲面である、前記両出力ディスク５、５の内側面を、前記両入力ディスク２、２の内側面に対向させている。 The use of a half-toroidal toroidal continuously variable transmission as a transmission for an automobile is described in many publications such as Patent Documents 1 to 4 and partially implemented, and is well known. Further, a structure in which a toroidal type continuously variable transmission and a planetary gear mechanism are combined to widen the adjustment range of the gear ratio is also described in many publications such as Patent Document 5 and has been widely known. FIGS. 11 to 12 show a first example of a toroidal type continuously variable transmission that is described in each of these patent documents and has been widely known. In the case of the first example of this conventional structure, a pair of input disks 2 and 2 are disposed around the portions near both ends of the input rotation shaft 1 in a state where the inner surfaces, each of which is a toroidal curved surface, face each other. The rotation synchronized with the rotating shaft 1 is freely supported. An output tube 3 is supported around the intermediate portion of the input rotary shaft 1 so as to freely rotate with respect to the input rotary shaft 1. Further, on the outer peripheral surface of the output cylinder 3, an output gear 4 is fixed at the center in the axial direction, and a pair of output disks 5 and 5 are connected to both ends in the axial direction by spline engagement. Supports rotation synchronized with the motor. In this state, the inner surfaces of the output disks 5 and 5, each of which is a toroidal curved surface, are opposed to the inner surfaces of the input disks 2 and 2.

又、前記両入力ディスク２、２と前記両出力ディスク５、５との間に、それぞれの周面を球状凸面とした複数個のパワーローラ６、６を挟持している。これら各パワーローラ６、６は、それぞれトラニオン７、７に回転自在に支持されており、これら各トラニオン７、７は、それぞれ前記各ディスク２、５の中心軸に対し捩れの位置にある傾転軸８、８を中心とする揺動変位自在に支持されている。即ち、これら各トラニオン７、７は、それぞれの軸方向両端部に互いに同心に設けられた１対の傾転軸８、８と、これら各傾転軸８、８同士の間に存在する支持梁部９、９とを備えており、これら各傾転軸８、８が、支持板１０、１０に対し、ラジアルニードル軸受１１、１１を介して枢支されている。 Further, a plurality of power rollers 6, 6 each having a spherical convex surface are sandwiched between the input disks 2, 2 and the output disks 5, 5. The power rollers 6 and 6 are rotatably supported by trunnions 7 and 7, respectively. The trunnions 7 and 7 are tilted with respect to the central axes of the disks 2 and 5, respectively. The shafts 8 and 8 are supported so as to be swingable and displaceable. That is, each of the trunnions 7 and 7 includes a pair of tilting shafts 8 and 8 provided concentrically with each other at both axial ends, and a supporting beam existing between the tilting shafts 8 and 8. These tilting shafts 8 and 8 are pivotally supported with respect to the support plates 10 and 10 via radial needle bearings 11 and 11, respectively.

又、前記各パワーローラ６、６は、前記各トラニオン７、７を構成する支持梁部９、９の内側面に、基半部と先半部とが互いに偏心した支持軸１２、１２と、複数の転がり軸受とを介して、これら各支持軸１２、１２の先半部回りの回転、及び、これら各支持軸１２、１２の基半部を中心とする若干の揺動変位を自在に支持されている。この様な各パワーローラ６、６の外側面と、前記各トラニオン７、７を構成する支持梁部９、９の内側面との間には、それぞれが前記複数の転がり軸受の一部であり、スラスト転がり軸受である、スラスト玉軸受１３、１３と、同じくスラスト転がり軸受であるスラストニードル軸受１４、１４とを、前記各パワーローラ６、６の側から順番に設けている。このうちのスラスト玉軸受１３、１３は、前記各パワーローラ６、６に加わるスラスト方向の荷重を支承しつつ、これら各パワーローラ６、６の回転を許容するものである。これら各スラスト玉軸受１３、１３は、前記各パワーローラ６、６の外側面に形成された内輪軌道１５と、外輪１６の内側面に形成された外輪軌道１７との間に、それぞれがスラスト転動体である複数個の玉１８、１８を、転動自在に設けて成る。又、前記各スラストニードル軸受１４、１４は、前記各パワーローラ６、６から前記各スラスト玉軸受１３、１３を構成する外輪１６、１６に加わるスラスト荷重を支承しつつ、これら各外輪１６、１６及び前記各支持軸１２、１２の先半部が、これら各支持軸１２、１２の基半部を中心に揺動する事を許容するものである。 Each of the power rollers 6 and 6 includes support shafts 12 and 12 in which the base half portion and the tip half portion are eccentric to each other on the inner surface of the support beam portions 9 and 9 constituting the trunnions 7 and 7, respectively. Via a plurality of rolling bearings, it is possible to freely support rotation around the front half of each of the support shafts 12 and 12 and slight swing displacement around the base half of each of the support shafts 12 and 12. Has been. Between the outer side surfaces of the power rollers 6 and 6 and the inner side surfaces of the support beam portions 9 and 9 constituting the trunnions 7 and 7, each of them is a part of the plurality of rolling bearings. Thrust ball bearings 13 and 13 which are thrust rolling bearings, and thrust needle bearings 14 and 14 which are also thrust rolling bearings are provided in order from the power rollers 6 and 6 side. Of these, the thrust ball bearings 13, 13 allow the power rollers 6, 6 to rotate while supporting a load in the thrust direction applied to the power rollers 6, 6. Each of the thrust ball bearings 13 and 13 has a thrust rotation between an inner ring raceway 15 formed on the outer side surface of each of the power rollers 6 and 6 and an outer ring raceway 17 formed on the inner side surface of the outer ring 16. A plurality of balls 18 and 18 which are moving bodies are provided so as to roll freely. The thrust needle roller bearings 14, 14 support thrust loads applied to the outer rings 16, 16 constituting the thrust ball bearings 13, 13 from the power rollers 6, 6. The front half of each of the support shafts 12 and 12 is allowed to swing around the base half of each of the support shafts 12 and 12.

上述の様なトロイダル型無段変速機の運転時には、駆動軸１９により一方（図１１の左方）の入力ディスク２を、押圧装置２０を介して回転駆動する。この結果、前記入力回転軸１の両端部に支持された１対の入力ディスク２、２が、互いに近づく方向に押圧されつつ同期して回転する。そして、この回転が、前記各パワーローラ６、６を介して前記両出力ディスク５、５に伝わり、前記出力歯車４から取り出される。前記入力回転軸１と前記出力歯車４との間の変速比を変える場合は、油圧式のアクチュエータ２１、２１により前記各トラニオン７、７を前記各傾転軸８、８の軸方向に変位させる。この結果、前記各パワーローラ６、６の周面と前記各ディスク２、５の内側面との転がり接触部（トラクション部）に作用する、接線方向の力の向きが変化する（転がり接触部にサイドスリップが発生する）。そして、この力の向きの変化に伴って前記各トラニオン７、７が、自身の傾転軸８、８を中心に揺動し、前記各パワーローラ６、６の周面と前記各ディスク２、５の内側面との接触位置が変化する。これら各パワーローラ６、６の周面を、前記両入力ディスク２、２の内側面の径方向外寄り部分と、前記両出力ディスク５、５の内側面の径方向内寄り部分とに転がり接触させれば、前記入力回転軸１と前記出力歯車４との間の変速比が増速側になる。これに対して、前記各パワーローラ６、６の周面を、前記両入力ディスク２、２の内側面の径方向内寄り部分と、前記両出力ディスク５、５の内側面の径方向外寄り部分とに転がり接触させれば、前記入力回転軸１と前記出力歯車４との間の変速比が減速側になる。 During operation of the toroidal-type continuously variable transmission as described above, one input disk 2 (left side in FIG. 11) is rotationally driven by the drive shaft 19 via the pressing device 20. As a result, the pair of input disks 2 and 2 supported at both ends of the input rotating shaft 1 rotate synchronously while being pressed in a direction approaching each other. The rotation is transmitted to the output disks 5 and 5 through the power rollers 6 and 6 and is taken out from the output gear 4. When changing the gear ratio between the input rotary shaft 1 and the output gear 4, the trunnions 7, 7 are displaced in the axial direction of the tilt shafts 8, 8 by hydraulic actuators 21, 21. . As a result, the direction of the tangential force acting on the rolling contact portion (traction portion) between the peripheral surface of each of the power rollers 6 and 6 and the inner surface of each of the disks 2 and 5 changes (in the rolling contact portion). Side slip occurs). As the direction of the force changes, the trunnions 7 and 7 swing around their tilting shafts 8 and 8, and the peripheral surfaces of the power rollers 6 and 6 and the disks 2 and 8. The contact position with the inner surface of 5 changes. The circumferential surfaces of the power rollers 6 and 6 are in rolling contact with the radially outer portions of the inner surfaces of the input disks 2 and 2 and the radially inner portions of the inner surfaces of the output disks 5 and 5. By doing so, the gear ratio between the input rotary shaft 1 and the output gear 4 is increased. On the other hand, the peripheral surfaces of the power rollers 6 and 6 are arranged radially inwardly on the inner side surfaces of the input disks 2 and 2 and radially outwardly on the inner side surfaces of the output disks 5 and 5. If it is brought into rolling contact with the portion, the gear ratio between the input rotary shaft 1 and the output gear 4 becomes the deceleration side.

上述の様なトロイダル型無段変速機の運転時には、動力の伝達に供される各部材、即ち、前記入力、出力各ディスク２、５と前記各パワーローラ６、６とが、前記押圧装置２０が発生する押圧力に基づいて弾性変形する。そして、この弾性変形に伴って、前記入力、出力各ディスク２、５が軸方向に変位する。又、前記押圧装置２０が発生する押圧力は、前記トロイダル型無段変速機により伝達するトルクが大きくなる程大きくなり、それに伴って前記各部材２、５、６の弾性変形量も多くなる。従って、前記トルクの変動に拘らず、前記入力、出力各ディスク２、５の内側面と前記各パワーローラ６、６の周面との接触状態を適正に維持する為に、前記各トラニオン７、７に対して前記各パワーローラ６、６を、前記各ディスク２、５の軸方向に変位させる機構が必要になる。上述した従来構造の第１例の場合には、前記各パワーローラ６、６を支持した前記各支持軸１２、１２の先半部を、同じく基半部を中心として揺動変位させる事により、前記各パワーローラ６、６を前記軸方向に変位させる様にしている。 When the toroidal type continuously variable transmission as described above is operated, the members used for power transmission, that is, the input and output disks 2 and 5 and the power rollers 6 and 6 are connected to the pressing device 20. It is elastically deformed based on the pressing force generated. In accordance with this elastic deformation, the input and output disks 2 and 5 are displaced in the axial direction. The pressing force generated by the pressing device 20 increases as the torque transmitted by the toroidal continuously variable transmission increases, and the amount of elastic deformation of the members 2, 5, 6 increases accordingly. Accordingly, in order to properly maintain the contact state between the inner surface of each of the input and output disks 2 and 5 and the peripheral surface of each of the power rollers 6 and 6 regardless of the fluctuation of the torque, the trunnions 7 and 7 7, a mechanism for displacing the power rollers 6 and 6 in the axial direction of the disks 2 and 5 is required. In the case of the above-described first example of the conventional structure, the tip half of each of the support shafts 12 and 12 that support the power rollers 6 and 6 is also oscillated and displaced about the base half as well. The power rollers 6 and 6 are displaced in the axial direction.

上述の様な従来構造の第１例の場合、前記各パワーローラ６、６を前記軸方向に変位させる為の構造が複雑で、部品製作、部品管理、組立作業が何れも面倒になり、コストが嵩む事が避けられない。この様な問題を解決する為の技術として前記特許文献３には、図１３〜１８に示す様な構造が記載されている。本発明は、この図１３〜１８に示した従来構造の第２例を改良するものであるから、次に、この従来構造の第２例に就いて説明する。この従来構造の第２例の特徴は、トラニオン７ａに対してパワーローラ６ａを、入力、出力各ディスク２、５（図１１参照）の軸方向の変位を可能に支持する部分の構造にあり、トロイダル型無段変速機全体としての構造及び作用は、前述の図１１〜１２に示した従来構造の第１例と同様である。 In the case of the first example of the conventional structure as described above, the structure for displacing each of the power rollers 6 and 6 in the axial direction is complicated, and parts manufacturing, parts management, and assembly work are all troublesome and costly. It is inevitable that the volume increases. As a technique for solving such a problem, Patent Document 3 describes a structure as shown in FIGS. Since the present invention improves the second example of the conventional structure shown in FIGS. 13 to 18, the second example of the conventional structure will be described next. The feature of the second example of this conventional structure is the structure of the portion that supports the trunnion 7a so that the power roller 6a can be displaced in the axial direction of the input and output disks 2, 5 (see FIG. 11). The overall structure and operation of the toroidal type continuously variable transmission are the same as those of the first example of the conventional structure shown in FIGS.

前記従来構造の第２例を構成するトラニオン７ａは、両端部に互いに同心に設けられた１対の傾転軸８ａ、８ｂと、これら両傾転軸８ａ、８ｂ同士の間に存在し、少なくとも入力、出力各ディスク２、５（図１１参照）の径方向（図１４、１７〜１８の上下方向）に関する内側（図１４、１７〜１８の上側）の側面を円筒状凸面２２とした、支持梁部２３とを備える。前記両傾転軸８ａ、８ｂは、それぞれラジアルニードル軸受１１ａ、１１ａを介して、支持板１０、１０（図１２参照）に、揺動を可能に支持する。 The trunnion 7a constituting the second example of the conventional structure exists between a pair of tilting shafts 8a and 8b concentrically provided at both ends, and between these tilting shafts 8a and 8b, and at least A support having a cylindrical convex surface 22 on the inner side (upper side in FIGS. 14 and 17 to 18) in the radial direction (up and down direction in FIGS. 14 and 17 to 18) of the input and output disks 2 and 5 (see FIG. 11). And a beam portion 23. The two tilting shafts 8a and 8b are supported on the support plates 10 and 10 (see FIG. 12) via the radial needle bearings 11a and 11a, respectively, so as to be swingable.

又、前記円筒状凸面２２の中心軸イは、図１４、１７に示す様に、前記両傾転軸８ａ、８ｂの中心軸ロと平行で、これら両傾転軸８ａ、８ｂの中心軸ロよりも、前記各ディスク２、５の径方向に関して外側（図１４、１７〜１８の下側）に存在する。又、前記支持梁部２３とパワーローラ６ａの外側面との間に設けるスラスト玉軸受１３ａを構成する外輪１６ａの外側面に、部分円筒面状の凹部２４を、この外側面を径方向に横切る状態で設けている。そして、この凹部２４と、前記支持梁部２３の円筒状凸面２２とを係合させ、前記トラニオン７ａに対して前記外輪１６ａを、前記各ディスク２、５の軸方向に関する揺動変位を可能に支持している。 Further, as shown in FIGS. 14 and 17, the center axis A of the cylindrical convex surface 22 is parallel to the center axis B of the both tilt axes 8a and 8b, and the center axis B of the both tilt axes 8a and 8b. Rather than the outer side (the lower side of FIGS. 14 and 17 to 18) in the radial direction of the disks 2 and 5. Further, a concave portion 24 having a partially cylindrical surface is radially crossed on the outer surface of the outer ring 16a constituting the thrust ball bearing 13a provided between the support beam portion 23 and the outer surface of the power roller 6a. It is provided in the state. And this recessed part 24 and the cylindrical convex surface 22 of the said support beam part 23 are engaged, and the said outer ring 16a is rockable displacement about the axial direction of each said disks 2 and 5 with respect to the said trunnion 7a. I support it.

又、前記外輪１６ａの内側面中央部に支持軸１２ａを、この外輪１６ａと一体に固設して、前記パワーローラ６ａをこの支持軸１２ａの周囲に、ラジアル転がり軸受であるラジアルニードル軸受２５を介して、回転自在に支持している。このラジアルニードル軸受２５は、前記パワーローラ６ａの中心孔の内周面に形成した、円筒状のラジアル外輪軌道と、前記支持軸１２ａの外周面に形成した、円筒状のラジアル内輪軌道との間に、それぞれがラジアル転動体である、複数本のニードルを転動自在に配置して成る。更に、前記トラニオン７ａの内側面のうち、前記支持梁部２３の両端部と１対の傾転軸８ａ、８ｂとの連続部に、互いに対向する１対の段差面２６、２６を設けている。そして、これら両段差面２６、２６と、前記スラスト玉軸受１３ａを構成する外輪１６ａの外周面とを、当接若しくは近接対向させて、前記パワーローラ６ａからこの外輪１６ａに加わるトラクション力を、何れかの段差面２６、２６で支承可能としている。 A support shaft 12a is fixed to the central portion of the inner surface of the outer ring 16a, and the outer ring 16a is fixed integrally therewith, and the power roller 6a is provided around the support shaft 12a with a radial needle bearing 25 as a radial rolling bearing. Via the support. The radial needle bearing 25 is formed between a cylindrical radial outer ring raceway formed on the inner peripheral surface of the center hole of the power roller 6a and a cylindrical radial inner ring raceway formed on the outer peripheral surface of the support shaft 12a. In addition, a plurality of needles, each of which is a radial rolling element, are arranged so as to freely roll. Furthermore, a pair of stepped surfaces 26 and 26 facing each other are provided on the inner surface of the trunnion 7a at a continuous portion between both end portions of the support beam portion 23 and the pair of tilting shafts 8a and 8b. . Then, these stepped surfaces 26, 26 and the outer peripheral surface of the outer ring 16a constituting the thrust ball bearing 13a are brought into contact with or in close proximity to each other, and any traction force applied from the power roller 6a to the outer ring 16a is selected. These step surfaces 26 and 26 can be supported.

上述の様に構成する従来構造の第２例のトロイダル型無段変速機によれば、前記パワーローラ６ａを前記各ディスク２、５の軸方向に変位させて、構成各部材の弾性変形量の変化に拘らず、このパワーローラ６ａの周面と前記各ディスク２、５との接触状態を適正に維持できる構造を、簡単で低コストに構成できる。
即ち、トロイダル型無段変速機の運転時に、入力、出力各ディスク２、５、各パワーローラ６ａ等の弾性変形に基づき、これら各パワーローラ６ａをこれら各ディスク２、５の軸方向に変位させる必要が生じると、これら各パワーローラ６ａを回転自在に支持している前記スラスト玉軸受１３ａの外輪１６ａが、外側面に設けた部分円筒面状の凹部２４と支持梁部２３の円筒状凸面２２との当接面を滑らせつつ、この円筒状凸面２２の中心軸イを中心として揺動変位する。この揺動変位に基づき、前記各パワーローラ６ａの周面のうちで、前記各ディスク２、５の軸方向片側面と転がり接触する部分が、これら各ディスク２、５の軸方向に変位し、前記接触状態を適正に維持する。 According to the toroidal type continuously variable transmission of the second example of the conventional structure configured as described above, the power roller 6a is displaced in the axial direction of each of the disks 2 and 5, and the amount of elastic deformation of each constituent member is increased. Regardless of the change, a structure capable of appropriately maintaining the contact state between the peripheral surface of the power roller 6a and the disks 2 and 5 can be configured simply and at low cost.
That is, during operation of the toroidal continuously variable transmission, the power rollers 6a are displaced in the axial direction of the disks 2 and 5 based on elastic deformation of the input and output disks 2 and 5 and the power rollers 6a. When necessary, the outer ring 16a of the thrust ball bearing 13a that rotatably supports each of the power rollers 6a is provided with a concave portion 24 having a partial cylindrical surface provided on the outer surface and a cylindrical convex surface 22 of the support beam portion 23. The sliding surface of the cylindrical convex surface 22 is oscillated and displaced about the central axis a. Based on this oscillating displacement, a portion of the peripheral surface of each power roller 6a that is in rolling contact with one axial side surface of each disk 2, 5 is displaced in the axial direction of each disk 2, 5; The contact state is properly maintained.

前述した通り、前記円筒状凸面２２の中心軸イは、変速動作の際に各トラニオン７ａの揺動中心となる傾転軸８ａ、８ｂの中心軸ロよりも、前記各ディスク２、５の径方向に関して外側に存在する。従って、前記円筒状凸面２２の中心軸イを中心とする揺動変位の半径は、前記変速動作の際の揺動半径よりも大きく、前記両入力ディスク２、２と前記両出力ディスク５、５との間の変速比の変動に及ぼす影響は少ない（無視できるか、容易に修正できる範囲に留まる）。 As described above, the central axis A of the cylindrical convex surface 22 is larger in diameter than the central axes B of the tilting shafts 8a and 8b, which are the oscillation centers of the trunnions 7a during the shifting operation. Exists with respect to the direction. Therefore, the radius of the rocking displacement about the central axis A of the cylindrical convex surface 22 is larger than the rocking radius at the time of the speed change operation, and both the input disks 2 and 2 and the both output disks 5, 5 Has little effect on the change in the transmission ratio between (and can be neglected or remain within an easily modifiable range).

図１３〜１８に示した従来構造の第２例の場合、図１１〜１２に示した同第１例に比べて、部品製作、部品管理、組立作業が何れも容易になり、コスト低廉化を図り易いが、変速動作を安定させる面からは、改良の余地がある。この理由は、前記各支持梁部２３を中心とする前記各外輪１６ａの揺動変位を円滑に行わせる為、これら各支持梁部２３の両端部分に、前記各トラニオン７ａ毎に１対ずつ設けた、前記各段差面２６、２６同士の間隔Ｄを、前記各外輪１６ａの外径ｄよりも少し大きく（Ｄ＞ｄ）する為である。これら各外輪１６ａ、及び、この外輪１６ａと同心に支持された前記各パワーローラ６ａは、前記間隔Ｄと前記外径ｄとの差（Ｄ−ｄ）分だけ、前記各支持梁部２３の軸方向に変位可能になる。 Compared to the first example shown in FIGS. 11 to 12, the second example of the conventional structure shown in FIGS. 13 to 18 makes it easier to manufacture parts, manage parts, and assemble, thereby reducing costs. Although easy to achieve, there is room for improvement in terms of stabilizing the shifting operation. The reason for this is that each outer ring 16a is centered on each support beam portion 23 so that the outer ring 16a can be smoothly moved and displaced, and one pair of each trunnion 7a is provided at each end of each support beam portion 23. This is because the distance D between the stepped surfaces 26, 26 is made slightly larger (D> d) than the outer diameter d of each outer ring 16a. The outer rollers 16a and the power rollers 6a supported concentrically with the outer ring 16a have shafts of the support beam portions 23 corresponding to a difference (D−d) between the distance D and the outer diameter d. Displaceable in the direction.

一方、トロイダル型無段変速機を搭載した車両の運転時、前記各パワーローラ６ａには前記各ディスク２、５から、加速時と減速時（エンジンブレーキの作動時）とで逆方向の力（トロイダル型無段変速機の技術分野で周知の「２Ｆｔ」）が加わる。そして、この力２Ｆｔにより、前記各パワーローラ６ａが、前記各外輪１６ａと共に、前記各支持梁部２３の軸方向に変位する。この変位の方向は、前述した各アクチュエータ２１、２１による各トラニオン７、７（図１２参照）の変位方向と同じであり、変位量が０．１mm程度であっても、変速動作が開始される可能性を生じる。そして、この様な原因で変速動作が開始された場合には、運転動作とは直接関連しない変速動作となり、何れ修正されるにしても、運転者に違和感を与える。特に、トロイダル型無段変速機が伝達するトルクが低い状態で、上述の様な、運転者が意図しない変速が行われると、運転者に与える違和感が大きくなり易い。 On the other hand, during operation of a vehicle equipped with a toroidal-type continuously variable transmission, each power roller 6a receives a force in the opposite direction from the respective disks 2 and 5 during acceleration and deceleration (when the engine brake is activated) ( "2Ft", which is well known in the technical field of toroidal-type continuously variable transmissions, is added. Then, the force 2Ft causes the power rollers 6a to be displaced in the axial direction of the support beam portions 23 together with the outer rings 16a. The direction of this displacement is the same as the displacement direction of each trunnion 7 and 7 (see FIG. 12) by each actuator 21 and 21 described above, and the shifting operation is started even if the displacement is about 0.1 mm. Create a possibility. When the shifting operation is started for such a reason, the shifting operation is not directly related to the driving operation, and the driver feels uncomfortable regardless of any correction. In particular, when a shift that is not intended by the driver as described above is performed in a state where the torque transmitted by the toroidal-type continuously variable transmission is low, a sense of discomfort given to the driver tends to increase.

上述の様にして生じる、運転動作とは直接関連しない変速動作の発生を抑える為には、前記間隔Ｄと前記外径ｄとの差（Ｄ−ｄ）を僅少に（例えば数十μｍ程度に）抑える事が考えられる。但し、ハーフトロイダル型のトロイダル型無段変速機の運転時には、トラクション部から前記各パワーローラ６ａ、前記各外輪１６ａを介して前記各支持梁部２３に加わるスラスト荷重により、前記各トラニオン７ａが、図１９に誇張して示す様に、前記各外輪１６ａを設置した側が凹となる方向に弾性変形する。そして、この弾性変形の結果、前記各トラニオン７ａ毎に１対ずつ設けた段差面２６、２６同士の間隔が縮まる。この様な状態でも、これら両段差面２６、２６同士の間隔Ｄが前記各外輪１６ａの外径ｄ以下にならない様にする為には、通常状態（前記各トラニオン７ａが弾性変形していない状態）での、前記間隔Ｄと前記外径ｄとの差を或る程度確保する必要がある。この結果、特に違和感が大きくなり易い、低トルクでの運転時に、上述の様な、運転動作とは直接関連しない変速動作が発生し易くなる。 In order to suppress the occurrence of the speed change operation that is not directly related to the driving operation as described above, the difference (D−d) between the distance D and the outer diameter d is made small (for example, about several tens of μm). ) Can be suppressed. However, during operation of the half-toroidal toroidal continuously variable transmission, each trunnion 7a is caused by a thrust load applied from the traction portion to each support beam portion 23 via each power roller 6a and each outer ring 16a. As exaggeratedly shown in FIG. 19, the side where the outer rings 16a are installed is elastically deformed in the direction of being recessed. As a result of this elastic deformation, the distance between the step surfaces 26, 26 provided in pairs for each trunnion 7a is reduced. Even in such a state, in order to prevent the distance D between the two step surfaces 26 and 26 from becoming smaller than the outer diameter d of each outer ring 16a, the normal state (the state where each trunnion 7a is not elastically deformed). It is necessary to ensure a certain difference between the distance D and the outer diameter d. As a result, a shift operation that is not directly related to the driving operation as described above is likely to occur particularly during driving at a low torque, which tends to increase the sense of discomfort.

一方、前記特許文献３には、支持梁部側に設けた円筒状凸面の一部に係止したアンカ駒と、外輪側の凹部の内面に形成したアンカ溝とを係合させる事により、前記力２Ｆｔを支承する構造が記載されている。即ち、図２０に示す様に、支持梁部２３の一部に、係止部材であるキー２７を、この支持梁部２３の外周面から突出する状態で固設すると共に、外輪１６ｂに形成した凹部２４の内周面に、係止溝であるアンカ溝２８を、この凹部２４の周方向に形成する。そして、前記キー２７をこのアンカ溝２８に係合させる事により、前記外輪１６ｂを前記支持梁部２３に、この支持梁部２３を中心とする揺動変位を可能に、且つ、前記力２Ｆｔを支承可能に支持する。 On the other hand, in Patent Document 3, the anchor piece locked to a part of the cylindrical convex surface provided on the support beam part side and the anchor groove formed on the inner surface of the concave part on the outer ring side are engaged with each other. A structure for supporting a force 2Ft is described. That is, as shown in FIG. 20, a key 27 as a locking member is fixed to a part of the support beam portion 23 so as to protrude from the outer peripheral surface of the support beam portion 23 and is formed on the outer ring 16b. Anchor grooves 28 as locking grooves are formed in the circumferential direction of the recess 24 on the inner peripheral surface of the recess 24. Then, by engaging the key 27 with the anchor groove 28, the outer ring 16b can be oscillated and displaced about the support beam 23, and the force 2Ft can be applied. Support to support.

又、トラニオン７ｂに対しパワーローラ６ａを回転自在に支持する為のスラスト玉軸受１３ａ及びラジアルニードル軸受２５に潤滑油を送り込む為に、前記トラニオン７ｂの内部に上流側潤滑油流路２９を、前記外輪１６ｂと一体に設けた支持軸１２ａの内部に下流側潤滑油流路３０を、それぞれ設けている。そして、これら両潤滑油流路２９、３０同士を、前記キー２７の中央部に形成した通孔３１を介して連通させて、前記上流側潤滑油流路２９の下流端開口と前記下流側潤滑油流路３０の上流端開口との間で潤滑油の受け渡しを可能としている。前記上流側潤滑油流路２９から前記通孔３１を通じて前記下流側潤滑油流路３０に送り込まれた潤滑油は、前記支持軸１２ａの外周面に存在する、この下流側潤滑油流路３０の下流側開口からこの支持軸１２ａの周囲に吐出し、前記スラスト玉軸受１３ａ及び前記ラジアルニードル軸受２５を潤滑する。又、図示は省略するが、円筒状凸面と凹部との互いに整合する部分に形成された、それぞれが断面円弧形である転動溝同士の間に複数個の玉を掛け渡して、前記力２Ｆｔを支承する構造も記載されている。 Further, in order to send the lubricating oil to the thrust ball bearing 13a and the radial needle bearing 25 for rotatably supporting the power roller 6a with respect to the trunnion 7b, an upstream lubricating oil passage 29 is provided inside the trunnion 7b. Downstream lubricating oil passages 30 are respectively provided in the support shafts 12a provided integrally with the outer ring 16b. The two lubricating oil passages 29 and 30 are communicated with each other through a through hole 31 formed in the central portion of the key 27 so that the downstream end opening of the upstream lubricating oil passage 29 and the downstream lubricating portion are connected. Lubricating oil can be transferred to and from the upstream end opening of the oil flow path 30. The lubricating oil sent from the upstream lubricating oil flow passage 29 to the downstream lubricating oil flow passage 30 through the through hole 31 is present on the outer peripheral surface of the support shaft 12a. It discharges to the circumference | surroundings of this support shaft 12a from a downstream opening, and the said thrust ball bearing 13a and the said radial needle bearing 25 are lubricated. Although not shown in the drawings, a plurality of balls are formed between the rolling grooves formed on the cylindrical convex surface and the concavely aligned portion, each having an arcuate cross section, and the force A structure for supporting 2Ft is also described.

上述の様な構造によれば、前記パワーローラ６ａは前記トラニオン７ｂに対し、前記支持梁部２３の軸方向に変位する事を抑えて、しかも、このトラニオン７ｂの弾性変形に拘らず、このトラニオン７ｂに対する前記パワーローラ６ａの揺動変位が円滑に行われる様にできる。この為、低トルクでの運転時にも、運転動作とは直接関連しない変速動作が発生する事を防止できて、運転者に違和感を与える事を防止できる。 According to the structure as described above, the power roller 6a is prevented from being displaced in the axial direction of the support beam portion 23 with respect to the trunnion 7b, and the trunnion 7b is not affected by the elastic deformation of the trunnion 7b. The swinging displacement of the power roller 6a with respect to 7b can be performed smoothly. For this reason, even when driving at a low torque, it is possible to prevent a shift operation not directly related to the driving operation from occurring, and to prevent the driver from feeling uncomfortable.

但し、前記上流側潤滑油流路２９の下流端開口と前記下流側潤滑油流路３０の上流端開口との間に前記キー２７が存在するので、前記上流側潤滑油流路２９の下流端開口から吐出された潤滑油のうちの多くの部分が、前記下流側潤滑油流路３０内に取り込まれずに周囲に流失したり、或いは、これら両潤滑油流路２９、３０を含む潤滑油供給経路の抵抗が大きくなる。前記転動溝同士の間に複数個の玉を掛け渡した従来構造の場合も、同様の問題がある。何れにしても、前記スラスト玉軸受１３ａ及び前記ラジアルニードル軸受２５に十分量の潤滑油を送り込む面からは不利になる。 However, since the key 27 exists between the downstream end opening of the upstream lubricating oil passage 29 and the upstream end opening of the downstream lubricating oil passage 30, the downstream end of the upstream lubricating oil passage 29 is provided. Many parts of the lubricating oil discharged from the openings are not taken into the downstream lubricating oil flow path 30 and flow away to the surroundings, or a lubricating oil supply including both the lubricating oil flow paths 29 and 30 is provided. The resistance of the path increases. The same problem occurs in the case of a conventional structure in which a plurality of balls are spanned between the rolling grooves. In any case, the thrust ball bearing 13a and the radial needle bearing 25 are disadvantageous from the surface for feeding a sufficient amount of lubricating oil.

特開２００３−２１４５１６号公報JP 2003-214516 A 特開２００７−３１５５９５号公報JP 2007-315595 A 特開２００８−２５８２１号公報JP 2008-25821 A 特開２００８−２７５０８８号公報JP 2008-275088 A 特開２００４−１６９７１９号公報JP 2004-169719 A

本発明は、上述の様な事情に鑑み、部品製作、部品管理、組立作業が何れも容易で、コスト低減を図り易く、しかも変速動作を安定させる事ができ、且つ、トラニオンに対してパワーローラを回転自在に支持する為のスラスト、ラジアル両転がり軸受に、十分量の潤滑油を送り込み易い構造を実現すべく発明したものである。 In view of the circumstances as described above, the present invention makes it easy to manufacture parts, manage parts, and assemble, easily reduce costs, stabilize the speed change operation, and provide a power roller for the trunnion. Invented in order to realize a structure in which a sufficient amount of lubricating oil can be easily fed into a thrust and radial double rolling bearing for rotatably supporting the shaft.

本発明のトロイダル型無段変速機は、前述の従来から知られているトロイダル型無段変速機と同様に、少なくとも１対のディスクと、複数のトラニオンと、これら各トラニオンと同数のパワーローラと、これら各トラニオン毎に設けられたスラスト転がり軸受及びラジアル転がり軸受とを備える。そして、これら各トラニオン側又は前記スラスト転がり軸受を構成する前記スラスト外輪側に支持した係止部材と、このスラスト外輪側又は前記各トラニオン側に設けた係止溝との係合により、前記各パワーローラに加わる力を支承し、前記各スラスト外輪が前記各トラニオンに対し、この力の作用方向に変位する事を阻止する様にしている。又、前記各スラスト転がり軸受及び前記各ラジアル転がり軸受に潤滑油を供給する為に、前記各トラニオン内に上流側潤滑油流路を、前記スラスト外輪の中心部に設けた支持軸内に下流側潤滑油流路を、それぞれ設けている。 The toroidal type continuously variable transmission of the present invention includes at least one pair of disks, a plurality of trunnions, and the same number of power rollers as each of the trunnions, as in the above-described conventionally known toroidal type continuously variable transmissions. And a thrust rolling bearing and a radial rolling bearing provided for each trunnion. And, by engaging each of the trunnion side or the locking member supported on the thrust outer ring side constituting the thrust rolling bearing with the locking groove provided on the thrust outer ring side or each trunnion side, A force applied to the roller is supported, and the thrust outer rings are prevented from being displaced in the direction in which the force is applied to the trunnions. Further, in order to supply lubricating oil to each thrust rolling bearing and each radial rolling bearing, an upstream lubricating oil passage is provided in each trunnion, and a downstream side is provided in a support shaft provided in a central portion of the thrust outer ring. Lubricating oil flow paths are respectively provided.

特に、本発明のトロイダル型無段変速機に於いては、前記各係止部材及び前記各係止溝を、前記各スラスト外輪の内側面の中心部にこれら各スラスト外輪と同心に設けられた支持軸の中心から前記各支持梁部の軸方向に外れた部分に設けている。そして、前記各上流側潤滑油流路の下流端開口と前記各下流側潤滑油流路の上流端開口との間に前記各係止部材を配置する事なく、これら各下流端開口とこれら各上流端開口とを直接対向させている。 In particular, in the toroidal-type continuously variable transmission according to the present invention, the locking members and the locking grooves are provided concentrically with the thrust outer rings at the center of the inner side surface of the thrust outer rings. It is provided in a portion deviated from the center of the support shaft in the axial direction of each of the support beam portions. And, without arranging each locking member between the downstream end opening of each upstream lubricating oil flow path and the upstream end opening of each downstream lubricating oil flow path, each of these downstream end openings and each of these The upstream end opening is directly opposed.

上述の様に構成する本発明のトロイダル型無段変速機によれば、部品製作、部品管理、組立作業が何れも容易になり、コスト低廉化を図り易く、しかも変速動作を安定させる事ができ、且つ、各トラニオンに対して各パワーローラを回転自在に支持する為のスラスト、ラジアル各転がり軸受に、十分量の潤滑油を送り込み易い構造を実現できる。
このうちのコスト低廉化は、前述の図１３〜１８に示した従来構造の第２例と同様の理由により、図り易い。
又、変速動作の安定化は、前記各トラニオン側又は前記スラスト転がり軸受を構成するスラスト外輪側に支持した係止部材と、これら各スラスト外輪側又は前記各トラニオン側に設けた係止溝との係合により、これら各スラスト外輪がこれら各トラニオンに対し、前記各パワーローラに作用する力の方向に変位する事を阻止する事により図れる。
更に、各転がり軸受に十分量の潤滑油を送り込み易くする事は、各上流側潤滑油流路の下流端開口と各下流側潤滑油流路の上流端開口との間に前記各係止部材を配置する事なく、これら各下流端開口とこれら各上流端開口とを直接対向させる事により図れる。 According to the toroidal-type continuously variable transmission of the present invention configured as described above, it is easy to manufacture parts, manage parts, and assemble work, facilitate cost reduction, and stabilize the speed change operation. In addition, it is possible to realize a structure in which a sufficient amount of lubricating oil can be easily fed to the thrust and radial rolling bearings for rotatably supporting each power roller with respect to each trunnion.
Of these, cost reduction is easy to achieve for the same reason as in the second example of the conventional structure shown in FIGS.
Further, the stabilization of the speed change operation is performed by a locking member supported on each trunnion side or the thrust outer ring side constituting the thrust rolling bearing, and a locking groove provided on each thrust outer ring side or each trunnion side. By engaging, the thrust outer rings can be prevented from being displaced in the direction of the force acting on the power rollers with respect to the trunnions.
Furthermore, it is easy to feed a sufficient amount of lubricating oil to each rolling bearing, because each locking member is provided between the downstream end opening of each upstream lubricating oil flow path and the upstream end opening of each downstream lubricating oil flow path. These downstream end openings and the respective upstream end openings can be directly opposed to each other without arranging them.

本発明の実施の形態の第１例を、トラニオンと外輪とを取り出した状態で示す断面図。Sectional drawing which shows the 1st example of embodiment of this invention in the state which took out the trunnion and the outer ring | wheel. トラニオンのみを取り出して、各ディスクの径方向に関して内側から見た状態で示す斜視図。The perspective view shown in the state which took out only the trunnion and was seen from the inner side regarding the radial direction of each disk. 支持軸を設けた外輪のみを取り出して、各ディスクの径方向に関して外側から見た状態で示す斜視図（Ａ）と、正投影図（Ｂ）と、アンカ溝の形状を異ならせた別例を示す正投影図（Ｃ）。Only the outer ring provided with the support shaft is taken out, and the perspective view (A) shown in the state viewed from the outside in the radial direction of each disk and the orthographic view (B), and another example in which the shape of the anchor groove is different. An orthographic projection (C) shown. 図１のａ部拡大図（Ａ）と、ｂ部拡大図（Ｂ）と、ｃ部拡大図（Ｃ）。The a section enlarged view (A), b section enlarged view (B), and c section enlarged view (C) of FIG. 本発明の実施の形態の第２例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. 同じく、図２と同様の図。Similarly, the same figure as FIG. 本発明の実施の形態の第３例を示す、図２と同様の図。The figure similar to FIG. 2 which shows the 3rd example of embodiment of this invention. 同第４例を示す、図２と同様の図。The figure similar to FIG. 2 which shows the 4th example. 同第５例を示す、図２と同様の図。The figure similar to FIG. 2 which shows the 5th example. 同第６例を示す、図２と同様の図。The figure similar to FIG. 2 which shows the said 6th example. 従来構造の第１例を示す断面図。Sectional drawing which shows the 1st example of a conventional structure. 図１１のｄ−ｄ断面図。Dd sectional drawing of FIG. 従来構造の第２例を示す、スラスト玉軸受を介してパワーローラを支持したトラニオンを、各ディスクの径方向外側から見た斜視図。The perspective view which looked at the trunnion which supported the power roller via the thrust ball bearing which shows the 2nd example of the conventional structure from the radial direction outer side of each disk. 同じく、ディスクの周方向から見た状態で示す正面図。Similarly, the front view shown in the state seen from the circumferential direction of the disk. 図１４の上方から見た平面図。The top view seen from the upper part of FIG. 図１４の右方から見た側面図。The side view seen from the right side of FIG. 図１５のｅ−ｅ断面図。Ee sectional drawing of FIG. 図１４のｆ−ｆ断面図。Ff sectional drawing of FIG. パワーローラから加わるスラスト荷重に基づいてトラニオンが弾性変形した状態を誇張して示す、図１７と同方向から見た断面図。FIG. 18 is a cross-sectional view seen from the same direction as FIG. 17, exaggeratingly showing a state where the trunnion is elastically deformed based on a thrust load applied from a power roller. 従来構造の第３例を示す、図１８と同様の図。The figure similar to FIG. 18 which shows the 3rd example of conventional structure.

［実施の形態の第１例］
図１〜４は、本発明の実施の形態の第１例を示している。尚、本例の特徴は、変速動作を安定させるべく、各トラニオン７ｂの支持梁部２３に対し、スラスト玉軸受１３ａ（図１３〜１８参照）を構成する外輪１６ｂを、これら各支持梁部２３に対する揺動変位を可能に支持しつつ、これら各支持梁部２３の軸方向に変位しない様にし、且つ、前記各トラニオン７ｂ側に設けた上流側潤滑油流路２９ａから前記外輪１６ｂと一体に設けた支持軸１２ａ側に設けた下流側潤滑油流路３０ａに、効率良く潤滑油を送り込み自在とする為の構造にある。その他の部分の構造及び作用は、前述の図１３〜１９に示した従来構造の第２例と同様であるから、同等部分に関する図示並びに説明は、省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。 [First example of embodiment]
1 to 4 show a first example of an embodiment of the present invention. The feature of this example is that the outer ring 16b constituting the thrust ball bearing 13a (see FIGS. 13 to 18) is provided to the support beam portion 23 of each trunnion 7b to stabilize the speed change operation. The supporting beam portions 23 are supported so as to be able to swing and displace in the axial direction, and are integrated with the outer ring 16b from the upstream lubricating oil flow passage 29a provided on the trunnion 7b side. The lubricating oil can be efficiently fed into the downstream lubricating oil passage 30a provided on the provided support shaft 12a side. Since the structure and operation of the other parts are the same as those of the second example of the conventional structure shown in FIGS. 13 to 19 described above, the illustration and description of the equivalent parts are omitted or simplified. The explanation will be focused on.

本例の構造の場合、前記外輪１６ｂを前記支持梁部２３に対し、揺動変位を可能に、且つ、この支持梁部２３の軸方向への変位を阻止した状態で支持する為の係止部材であるキー２７ａと、係止溝であるアンカ溝２８ａとを、前記外輪１６ｂの中心から前記各支持梁部２３の軸方向に外れた部分に設けている。即ち、この外輪１６ｂの外側面に凹部２４を、この外輪１６ｂの径方向に形成しているが、前記アンカ溝２８ａを、この凹部２４の長さ方向中央部ではなく、この凹部２４の長さ方向一端寄り（図１の左寄り）部分に形成している。又、前記キー２７ａの片半部を、前記支持梁部２３の一部外周面で、前記トラニオン７ｂと前記外輪１６ｂとを組み合わせた状態で、前記アンカ溝２８ａに整合する部分に形成した嵌合凹部３２に、締り嵌めにより内嵌固定している。この状態で、前記キー２７ａの他半部が、前記支持梁部２３の外周面から突出している。尚、前記アンカ溝２８ａは、図３の（Ａ）（Ｂ）に示す様に、前記凹部２８の全幅に亙って形成しても良いし、同図の（Ｃ）に示す様に、前記トラニオン７ｂに対する前記外輪１６ｂの、必要とする揺動変位を可能にする範囲にのみ設けても良い。 In the case of the structure of this example, the outer ring 16b is locked to support the support beam portion 23 in a state in which the displacement can be oscillated and the support beam portion 23 is prevented from being displaced in the axial direction. A key 27a, which is a member, and an anchor groove 28a, which is a locking groove, are provided in a portion that deviates in the axial direction of each support beam portion 23 from the center of the outer ring 16b. That is, the recess 24 is formed on the outer surface of the outer ring 16b in the radial direction of the outer ring 16b. However, the anchor groove 28a is not the central portion in the length direction of the recess 24 but the length of the recess 24. It is formed in a portion closer to one end in the direction (leftward in FIG. 1). Further, one half of the key 27a is a part of the outer peripheral surface of the support beam 23 and is formed in a portion that is aligned with the anchor groove 28a in a state where the trunnion 7b and the outer ring 16b are combined. The recess 32 is internally fitted and fixed by an interference fit. In this state, the other half of the key 27 a protrudes from the outer peripheral surface of the support beam 23. The anchor groove 28a may be formed over the entire width of the recess 28 as shown in FIGS. 3A and 3B, or as shown in FIG. You may provide only in the range which enables the rocking | swiveling displacement which the said outer ring | wheel 16b with respect to the trunnion 7b requires.

何れにしても、前記トラニオン７ｂと前記外輪１６ｂとを組み合わせ、前記アンカ溝２８ａに前記キー２７ａの他半部を係合させた状態で、この外輪１６ｂの外周面と前記トラニオン７ｂの段差面２６、２６との間には、それぞれ隙間が存在する様に、各部の寸法及び位置関係を規制している。前記支持梁部２３の軸方向に関する前記両隙間の厚さ寸法は、前記キー２７ａの他半部両側面と前記アンカ溝２８の両内側面との間に存在する微小隙間よりも大きくして、前記外輪１６ｂの外周面と前記トラニオン７ｂの段差面２６、２６とが当接しない様にしている。又、前記両隙間の厚さ寸法は、前記トラニオン７ｂが、前述の図１９に示す様に弾性変形した場合にも消失しないだけの大きさを有する。 In any case, in the state where the trunnion 7b and the outer ring 16b are combined and the other half of the key 27a is engaged with the anchor groove 28a, the outer peripheral surface of the outer ring 16b and the step surface 26 of the trunnion 7b. , 26, the size and positional relationship of each part are regulated so that there is a gap between them. The thickness dimension of the both gaps in the axial direction of the support beam portion 23 is set to be larger than a minute gap existing between both side surfaces of the other half of the key 27a and both inner side surfaces of the anchor groove 28, The outer peripheral surface of the outer ring 16b and the step surfaces 26, 26 of the trunnion 7b are prevented from coming into contact with each other. Further, the thickness dimension of both the gaps is large enough not to disappear even when the trunnion 7b is elastically deformed as shown in FIG.

更に、前記トラニオン７ｂの内部に設けた上流側潤滑油流路２９ａの下流端開口が、前記支持梁部２３の外周面の長さ方向中央部に開口している。又、前記外輪１６ｂと一体に設けた支持軸１２ａの中心部に設けた下流側潤滑油流路３０ａの上流端が、前記外輪１６ｂの外側面に形成した凹部２４の底部の長さ方向中央部に開口している。前記上流側潤滑油流路２９ａの下流端開口と前記下流側潤滑油流路３０ａの上流端開口との間には、前記キー２７ａ等の部材が存在する事はなく、これら下流端開口と上流端開口とは、直接対向している。このうちの上流端開口部分は、部分円すい凹面状の傾斜面として、開口部の面積を十分に確保し、前記トラニオン７ｂに対する前記外輪１６ｂの、若干の揺動変位に拘らず、前記上流側潤滑油流路２９ａの下流端開口と前記下流側潤滑油流路３０ａの上流端開口との対向部の面積が十分に確保される様にしている。この為、本例のトロイダル型無段変速機によれば、前記トラニオン２７ｂに対しパワーローラ６ａを回転自在に支持する為のスラスト玉軸受１３ａ及びラジアルニードル軸受２５（図１７〜１８参照）に、十分量の潤滑油を送り込み易くできる。 Further, the downstream end opening of the upstream side lubricating oil passage 29 a provided inside the trunnion 7 b opens at the center in the length direction of the outer peripheral surface of the support beam portion 23. In addition, the upstream end of the downstream-side lubricating oil passage 30a provided at the center of the support shaft 12a provided integrally with the outer ring 16b is the central portion in the length direction of the bottom of the recess 24 formed on the outer surface of the outer ring 16b. Is open. There is no member such as the key 27a between the downstream end opening of the upstream lubricating oil passage 29a and the upstream end opening of the downstream lubricating oil passage 30a. It directly faces the end opening. Of these, the upstream end opening portion is a partial conical concave inclined surface that ensures a sufficient area of the opening portion, and the upstream side lubrication regardless of the slight displacement of the outer ring 16b relative to the trunnion 7b. The area of the facing portion between the downstream end opening of the oil passage 29a and the upstream end opening of the downstream lubricating oil passage 30a is sufficiently secured. For this reason, according to the toroidal type continuously variable transmission of this example, the thrust ball bearing 13a and the radial needle bearing 25 (see FIGS. 17 to 18) for rotatably supporting the power roller 6a with respect to the trunnion 27b, It is easy to feed a sufficient amount of lubricating oil.

［実施の形態の第２例］
図５〜６は、本発明の実施の形態の第２例を示している。本例の場合には、トラニオン７ｂの支持梁部２３の一部に形成した嵌合凹部３２ａに、係止部材である円柱状のピン３３の片半部を、締り嵌めにより内嵌固定している。そして、前記支持梁部２３の外周面から突出した、前記支持梁部２３の他半部を、外輪１６ｂの外側面に形成した凹部２４の内周面に形成した、係止溝であるアンカ溝２８ｂに係合させている。尚、このアンカ溝２８ｂの断面形状は、図示の様な矩形に限らず、前記ピン３３の他半部とがたつきなく係合する、半円形であっても良い。
その他の部分の構成及び作用は、上述した実施の形態の第１例と同様であるから、重複する説明は省略する。 [Second Example of Embodiment]
5 to 6 show a second example of the embodiment of the present invention. In the case of this example, one half of a cylindrical pin 33, which is a locking member, is internally fitted and fixed to the fitting recess 32a formed in a part of the support beam 23 of the trunnion 7b by an interference fit. Yes. An anchor groove, which is a locking groove, is formed on the inner peripheral surface of the concave portion 24 formed on the outer surface of the outer ring 16b with the other half portion of the support beam portion 23 protruding from the outer peripheral surface of the support beam portion 23. 28b is engaged. The cross-sectional shape of the anchor groove 28b is not limited to the rectangular shape shown in the figure, and may be a semicircular shape that engages with the other half of the pin 33 without rattling.
Since the configuration and operation of the other parts are the same as those in the first example of the above-described embodiment, redundant description is omitted.

［実施の形態の第３〜６例］
図７〜１０は、本発明の実施の形態の第３〜６例を示している。前述した実施の形態の第１例はキー２７ａ（図１、２、４参照）を、上述した実施の形態の第２例はピン３３（図５〜６参照）を、それぞれ上流側潤滑油流路２９ａの下流端開口が向いている側で、支持梁部２３に設けた円筒状凸面２２の周方向中央部に設置している。但し、前記キー２７ａ及びピン３３は、必ずしもこの様な位置に設置する必要はない。例えば、キー２７ａに関しては、図７に示した実施の形態の第３例の様に、上流側潤滑油流路２９ａの下流端開口が向いている側で円筒状凸面２２の周方向中央部から外れた位置に設置する事もできる。或いは、図８に示した実施の形態の第４例の様に、上流側潤滑油流路２９ａの下流端開口が向いているのと反対側に設置する事もできる。前記ピン３３に関しても、図９〜１０に示した実施の形態の第５〜６例の様に、前記キー２７ａと同様の位置に設置する事もできる。要は、前記キー２７ａ、前記ピン３３の何れの部材に関しても、他の部材との干渉防止、トラニオン７ｂの強度確保等を勘案して、適切な位置に設置する。 [Third to Sixth Embodiments]
7 to 10 show third to sixth examples of the embodiment of the present invention. In the first example of the embodiment described above, the key 27a (see FIGS. 1, 2, and 4) is used, and in the second example of the embodiment described above, the pin 33 (see FIGS. 5 to 6) is used as the upstream lubricant flow. On the side where the downstream end opening of the passage 29a faces, it is installed at the center in the circumferential direction of the cylindrical convex surface 22 provided on the support beam portion 23. However, the key 27a and the pin 33 are not necessarily installed at such positions. For example, with respect to the key 27a, as in the third example of the embodiment shown in FIG. 7, on the side where the downstream end opening of the upstream lubricating oil passage 29a faces, It can also be installed in an off position. Alternatively, as in the fourth example of the embodiment shown in FIG. 8, it can be installed on the side opposite to the downstream end opening of the upstream lubricating oil passage 29a. The pin 33 can also be installed at the same position as the key 27a as in the fifth to sixth examples of the embodiment shown in FIGS. In short, any member of the key 27a and the pin 33 is installed at an appropriate position in consideration of preventing interference with other members and ensuring the strength of the trunnion 7b.

本発明は、トロイダル型無段変速機単独で実施できる他、特許文献５に記載されている様な、遊星歯車機構と組み合わせた無段変速装置として実施する事もできる。
又、図示の例とは逆に、各スラスト外輪に形成した凹部の内周面に係止部材を設け、各トラニオンの支持梁部の外周面に係止溝を形成する事もできる。 The present invention can be implemented by a toroidal continuously variable transmission alone, or can be implemented as a continuously variable transmission in combination with a planetary gear mechanism as described in Patent Document 5.
Also, contrary to the illustrated example, a locking member can be provided on the inner peripheral surface of the recess formed in each thrust outer ring, and a locking groove can be formed on the outer peripheral surface of the support beam portion of each trunnion.

１入力回転軸
２入力ディスク
３出力筒
４出力歯車
５出力ディスク
６、６ａパワーローラ
７、７ａ、７ｂトラニオン
８、８ａ、８ｂ傾転軸
９支持梁部
１０支持板
１１、１１ａラジアルニードル軸受
１２、１２ａ支持軸
１３、１３ａスラスト玉軸受
１４スラストニードル軸受
１５内輪軌道
１６、１６ａ、１６ｂ外輪
１７外輪軌道
１８玉
１９駆動軸
２０押圧装置
２１アクチュエータ
２２円筒状凸面
２３支持梁部
２４凹部
２５ラジアルニードル軸受
２６段差面
２７、２７ａキー
２８、２８ａ、２８ｂアンカ溝
２９、２９ａ上流側潤滑油流路
３０、３０ａ下流側潤滑油流路
３１通孔
３２、３２ａ嵌合凹部
３３ピン DESCRIPTION OF SYMBOLS 1 Input rotating shaft 2 Input disk 3 Output cylinder 4 Output gear 5 Output disk 6, 6a Power roller 7, 7a, 7b Trunnion 8, 8a, 8b Tilt shaft 9 Support beam part 10 Support plate 11, 11a Radial needle bearing 12, 12a support shaft 13, 13a thrust ball bearing 14 thrust needle bearing 15 inner ring raceway 16, 16a, 16b outer ring 17 outer ring raceway 18 ball 19 drive shaft 20 pressing device 21 actuator 22 cylindrical convex surface 23 support beam portion 24 concave portion 25 radial needle bearing 26 Step surface 27, 27a Key 28, 28a, 28b Anchor groove 29, 29a Upstream lubricating oil flow path 30, 30a Downstream lubricating oil flow path 31 Through hole 32, 32a Fitting recess 33 Pin

Claims

At least one pair of disks, a plurality of trunnions, the same number of power rollers as each trunnion, and the same number of thrust rolling bearings and radial rolling bearings provided for each trunnion,
Each of these discs is a toroidal curved surface having a circular arc cross section, with the axial one side surfaces facing each other, concentrically supported and freely supported by relative rotation,
Each trunnion exists between a pair of tilting shafts provided concentrically with each other at both ends, and between the two tilting shafts, and at least the inner side surface in the radial direction of each of the disks, A support beam portion having a partially cylindrical convex surface having a central axis that is parallel to the central axis of both tilting axes and that is present outside the central axis of the tilting axis with respect to the radial direction of each disk. Oscillating displacement about the tilting shaft that is twisted with respect to the central axis of each disk is freely provided at a plurality of locations in the circumferential direction between the axial side surfaces of each disk with respect to the axial direction. And
Each power roller is rotatably supported by each trunnion via each thrust rolling bearing and each radial rolling bearing, and each circumferential surface formed as a partially spherical convex surface is an axial piece of each disk. It is in contact with each side,
Each thrust rolling bearing is provided between the support beam portion of each trunnion and the outer surface of each power roller. A thrust outer ring provided on each support beam portion side, and each thrust outer ring. A plurality of thrust rolling elements provided between the thrust outer ring raceway provided on the inner side surface of the power roller and the thrust inner ring raceway provided on the outer side surface of each of the power rollers. Yes,
Each thrust outer ring engages a concave portion provided on each outer surface with a cylindrical convex surface of each of the support beam portions, thereby causing a swing displacement in the axial direction of each disk with respect to each trunnion. Supported as possible,
The distance between the pair of stepped surfaces for each trunnion provided at a position sandwiching each supporting beam portion from both ends in the axial direction by a part of each trunnion is the each supporting beam of each thrust outer ring. Larger than the diameter of the part in the axial direction,
A part of one peripheral surface of the outer peripheral surface of each support beam portion and the inner peripheral surface of the concave portion of each thrust outer ring protrudes from the one peripheral surface to the same portion facing the other peripheral surface. And a locking member supported in a state where axial displacement of each of the support beam portions is prevented, and the other peripheral surface is formed in the circumferential direction of each of the other peripheral surfaces. By engaging the locking groove, axial displacement of each thrust outer ring with respect to each support beam portion is prevented,
Each of the radial rolling bearings includes a radial inner ring raceway provided on an outer peripheral surface of a support shaft provided concentrically with each thrust outer ring at a central portion of an inner side surface of each thrust outer ring, and an inner hole of a center hole of each power roller. A plurality of radial rolling elements are provided so as to freely roll between each of the radial outer ring raceways provided on the peripheral surface,
In order to supply lubricating oil to each thrust rolling bearing and each radial rolling bearing, an upstream lubricating oil passage is provided on each trunnion side, and each downstream end is an axially central portion of each supporting beam portion. In the state facing the inner peripheral surface of the concave portion of each thrust outer ring, a downstream lubricating oil flow path is provided at the center of each of the support shafts, and the respective upstream ends thereof are located within the concave portions of the respective thrust outer rings. Each downstream end is provided on the peripheral surface in a state of opening to the outer peripheral surface of each support shaft, and the downstream end opening of each upstream lubricating oil flow channel and the upstream end of each downstream lubricating oil flow channel In the toroidal type continuously variable transmission that enables the transfer of lubricating oil to and from the opening,
By providing each locking member and each locking groove in a portion that is axially disengaged from the center of each support shaft in the axial direction of each support beam portion, Toroidal characterized in that the respective downstream end openings and the respective upstream end openings are directly opposed to each other without disposing the respective engaging members between the upstream end openings of the respective downstream lubricating oil flow paths. Type continuously variable transmission.

2. The toroidal continuously variable transmission according to claim 1, wherein each one of the peripheral surfaces is an outer peripheral surface of each of the support beam portions, and each of the other peripheral surfaces is an inner peripheral surface of each of the recesses.