JP5088241B2 - Continuously variable transmission - Google Patents

Continuously variable transmission Download PDF

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JP5088241B2
JP5088241B2 JP2008146872A JP2008146872A JP5088241B2 JP 5088241 B2 JP5088241 B2 JP 5088241B2 JP 2008146872 A JP2008146872 A JP 2008146872A JP 2008146872 A JP2008146872 A JP 2008146872A JP 5088241 B2 JP5088241 B2 JP 5088241B2
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movable
pulley
driving force
chain
continuously variable
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JP2009293681A (en
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敦史 月崎
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Nissan Motor Co Ltd
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Description

この発明は、無段変速装置(Continuously Variable Transmission:CVT)に関し、特に、プーリに付属する歯と駆動力を伝達する駆動力伝達手段が噛み合って動作する無段変速装置に関する。   The present invention relates to a continuously variable transmission (CVT), and more particularly, to a continuously variable transmission in which a tooth attached to a pulley and a driving force transmitting means for transmitting a driving force mesh with each other.

従来、Vベルトにより回転駆動力の伝達を行なう無段変速装置として、例えば、「無段変速機構」(特許文献1参照)が知られている。
従来の「無段変速機構」は、Vベルトを用いて回転力の伝達を確実に行うために、駆動回転軸に付されたプーリと従動回転軸に付されたプーリとの間でVベルトにより回転駆動力の伝達を行い、且つ上記2つのプーリの内の少なくとも一方が可変ピッチプーリであるVベルト式無段変速機構において、Vベルトが歯付きVベルトであり、且つ少なくとも一方の可変ピッチプーリがV溝底に上記Vベルトの歯と噛み合う歯車を有することを特徴としている。
特開昭63−120950号公報
Conventionally, for example, a “continuously variable transmission mechanism” (see Patent Document 1) is known as a continuously variable transmission that transmits a rotational driving force using a V-belt.
The conventional “continuously variable transmission mechanism” uses a V-belt between a pulley attached to a drive rotary shaft and a pulley attached to a driven rotary shaft in order to reliably transmit the rotational force using the V-belt. In a V-belt continuously variable transmission mechanism that transmits rotational driving force and at least one of the two pulleys is a variable pitch pulley, the V belt is a toothed V belt, and at least one of the variable pitch pulleys is V It has a gear which meshes with the teeth of the V belt at the groove bottom.
JP-A-63-120950

しかしながら、従来の「無段変速機構」においては、可変ピッチプーリがV溝底に有する、Vベルトの歯と噛み合う歯車が、V溝底の軸に固定されていることから、このV溝底の軸に付属する歯とVベルトの歯が十分噛み合っていない場合、両方の歯のピッチが一致しないため、軸に付属する歯がVベルトを攻撃してしまうことが避けられなかった。
つまり、可変ピッチプーリのV溝底の軸に設置した歯(即ち、噛合手段)と、この歯に噛み合って駆動力を伝達する駆動力伝達手段(Vベルトやチェーン等)との協調した動きが阻害されてしまうことになり、駆動力の伝達ができなくなると共に駆動力伝達手段が傷付くことも起こり得る。
However, in the conventional “continuously variable transmission mechanism”, the gear that meshes with the teeth of the V belt, which the variable pitch pulley has on the V groove bottom, is fixed to the shaft of the V groove bottom. When the teeth attached to the shaft and the teeth of the V-belt are not sufficiently meshed with each other, the pitches of both teeth do not match, so that the teeth attached to the shaft inevitably attack the V-belt.
In other words, the coordinated movement between the teeth installed on the shaft of the bottom of the V groove of the variable pitch pulley (that is, the meshing means) and the driving force transmitting means (V belt, chain, etc.) meshing with the teeth and transmitting the driving force is obstructed. As a result, the driving force cannot be transmitted and the driving force transmitting means may be damaged.

この発明の目的は、プーリのV溝底の軸に設置した噛合手段が、この噛合手段と噛み合って駆動力を伝達する駆動力伝達手段を攻撃することがなく、噛合手段と駆動力伝達手段の協調した動きを阻害することがない無段変速装置を提供することである。   An object of the present invention is that the meshing means installed on the shaft of the bottom of the V groove of the pulley does not attack the driving force transmitting means that meshes with the meshing means and transmits the driving force. To provide a continuously variable transmission that does not hinder coordinated movement.

この発明に係る無段変速装置は、無段変速装置の変速領域が最Hi時及び最Lo時の少なくとも一方のとき、可動噛合部がプーリの軸部に対し進出状態になって、駆動力伝達手段の被噛合部に噛合し、可動噛合部の駆動力伝達手段と接触する部位は、駆動力伝達手段が可動噛合部から受けるトルク反力を一定にする形状に形成されている。   In the continuously variable transmission according to the present invention, when the speed change region of the continuously variable transmission is at least one of the highest level and the lowest level, the movable meshing portion is in the advanced state with respect to the shaft portion of the pulley, so that the driving force is transmitted. The portion that meshes with the meshed portion of the means and contacts the driving force transmission means of the movable meshing portion is formed in a shape that makes constant the torque reaction force that the driving force transmission means receives from the movable meshing portion.

この発明によれば、無段変速装置の変速領域が最Hi時及び最Lo時の少なくとも一方のとき、可動噛合部がプーリの軸部に対し進出状態になって、駆動力伝達手段の被噛合部に噛合し、可動噛合部の駆動力伝達手段と接触する部位は、駆動力伝達手段が可動噛合部から受けるトルク反力を一定にする形状に形成されているので、プーリのV溝底の軸に設置した噛合手段が、この噛合手段と噛み合って駆動力を伝達する駆動力伝達手段を攻撃することがなく、噛合手段と駆動力伝達手段の協調した動きを阻害することがない。   According to the present invention, when the speed change region of the continuously variable transmission is at least one of the highest time and the lowest time, the movable meshing portion is advanced with respect to the shaft portion of the pulley, and the meshing force of the driving force transmitting means The portion of the movable meshing portion that contacts the driving force transmission means of the movable meshing portion is formed in a shape that makes the torque reaction force that the driving force transmission means receives from the movable meshing portion constant. The meshing means installed on the shaft does not attack the driving force transmitting means that meshes with the meshing means and transmits the driving force, and does not hinder the coordinated movement of the meshing means and the driving force transmitting means.

以下、この発明を実施するための最良の形態について図面を参照して説明する。
図1は、この発明の一実施の形態に係る無段変速装置の概略説明図である。図1に示すように、無段変速装置(CVT)10は、ドライブプーリ(プライマリプーリ)11とドリブンプーリ(セカンダリプーリ)12と共に、ドライブプーリ11とドリブンプーリ12の間に掛け回された駆動力伝達手段13を有しており、ドリブンプーリ12の軸部(プーリ軸部)14には、可動歯固定部品15を介して可動歯(可動噛合部)16が装着されている。
The best mode for carrying out the present invention will be described below with reference to the drawings.
FIG. 1 is a schematic explanatory diagram of a continuously variable transmission according to an embodiment of the present invention. As shown in FIG. 1, the continuously variable transmission (CVT) 10 includes a drive pulley (primary pulley) 11 and a driven pulley (secondary pulley) 12, and a driving force hung between the drive pulley 11 and the driven pulley 12. A movable tooth (movable meshing portion) 16 is attached to a shaft portion (pulley shaft portion) 14 of the driven pulley 12 via a movable tooth fixing component 15.

このCVT10は、例えば、車両に備えられて、車両の走行速度を無段階に変化させることができる。なお、駆動力伝達手段13としては、ベルトやチェーン等が用いられるが、ここでは、駆動力伝達手段13としてチェーンを用いた例について説明する。
ドライブプーリ11には、エンジン(図示しない)からの駆動力が入力し、ドリブンプーリ12から出力された駆動力は、駆動軸(図示しない)に伝達される。ドライブプーリ11とドリブンプーリ12は、共に、固定プーリに対し可動プーリを移動させて、固定プーリと可動プーリの間にV字状断面溝(V溝)を形成すると共にV溝幅を変更することができる。そして、駆動する側であるドライブプーリ11と駆動される側であるドリブンプーリ12のV溝幅を連続的に変えることで、駆動する側と駆動される側のチェーン13の伝達ピッチを変化させ、これにより滑らかな無段階変速を行なうことができる。
The CVT 10 is provided in a vehicle, for example, and can change the traveling speed of the vehicle steplessly. In addition, although a belt, a chain, etc. are used as the driving force transmission means 13, the example using a chain as the driving force transmission means 13 is demonstrated here.
A driving force from an engine (not shown) is input to the drive pulley 11, and the driving force output from the driven pulley 12 is transmitted to a driving shaft (not shown). Both the drive pulley 11 and the driven pulley 12 move the movable pulley relative to the fixed pulley to form a V-shaped cross-sectional groove (V groove) between the fixed pulley and the movable pulley and change the V groove width. Can do. Then, by continuously changing the V groove width of the drive pulley 11 which is the driving side and the driven pulley 12 which is the driving side, the transmission pitch of the chain 13 on the driving side and the driving side is changed, Thereby, a smooth stepless speed change can be performed.

図2は、図1のプーリ軸部にチェーンが巻き付いていない状態を示す説明図である。図3は、図1のプーリ軸部にチェーンが巻き付いている状態を示す説明図である。
図2及び図3に示すように、プーリ軸部14の外周面に装着された可動歯固定部品15には、可動歯固定部品15の外表面に対し退避自在に突出して、つまり、円筒状に形成された可動歯固定部品15の半径方向に移動自在に、可動歯固定部品15の全周に渡って可動歯16が組み込まれている。
FIG. 2 is an explanatory view showing a state where no chain is wound around the pulley shaft portion of FIG. 1. FIG. 3 is an explanatory view showing a state where the chain is wound around the pulley shaft portion of FIG. 1.
As shown in FIGS. 2 and 3, the movable tooth fixing component 15 mounted on the outer peripheral surface of the pulley shaft portion 14 protrudes retreatably from the outer surface of the movable tooth fixing component 15, that is, in a cylindrical shape. A movable tooth 16 is incorporated over the entire circumference of the movable tooth fixing component 15 so as to be movable in the radial direction of the formed movable tooth fixing component 15.

可動歯16は、プーリ軸部14の外表面との間に、例えば、コイルスプリング等のばね部材を介して、可動歯固定部品15に組み込まれており、このとき、ばね部材は圧縮状態にある。従って、可動歯固定部品15に組み込まれた可動歯16は、可動歯16の上端側部分である、傾斜面16aに囲まれた上端面16bを、可動歯固定部品15の外表面から突出させると共に、その状態に保持されている。
なお、コイルスプリングに代えて、リング状のスプリングをばね部材として用いても良く、リング状スプリングをプーリ軸部14外表面に縮径状態で装着することで、拡径時のばね力が可動歯16に作用し、可動歯16をプーリ軸部14の半径方向外側に突出させることができる。
The movable tooth 16 is incorporated in the movable tooth fixing part 15 between the outer surface of the pulley shaft part 14 via a spring member such as a coil spring, for example. At this time, the spring member is in a compressed state. . Therefore, the movable tooth 16 incorporated in the movable tooth fixing component 15 projects the upper end surface 16b surrounded by the inclined surface 16a, which is the upper end side portion of the movable tooth 16, from the outer surface of the movable tooth fixing component 15. Is held in that state.
In place of the coil spring, a ring-shaped spring may be used as a spring member. By mounting the ring-shaped spring on the outer surface of the pulley shaft portion 14 in a reduced diameter state, the spring force at the time of diameter expansion is movable. 16, the movable teeth 16 can protrude outward in the radial direction of the pulley shaft portion 14.

この可動歯16は、CVT10の最Hi(例えば、オーバドライブ:OD)時、可動歯固定部品15の外表面から突出し、チェーン13と噛み合った状態になる(図2参照)。なお、可動歯16は、ドリブンプーリ12のプーリ軸部14に設けられている場合に限らず、ドライブプーリ11のプーリ軸部14に設けられていても良く、この場合、CVT10の最Lo時、可動歯固定部品15の外表面から突出し、チェーン13と噛み合った状態になる。
このように、プーリ軸部14に設けられている可動歯16は、CVT10の最Hi時及び最Lo時の少なくとも一方のとき、即ち、駆動力伝達手段であるチェーン13がプーリのV溝底に存在するとき、可動歯固定部品15の外表面から突出した傾斜面16aに囲まれた上端面16bが、チェーン13に噛み合った状態になる。
The movable tooth 16 protrudes from the outer surface of the movable tooth fixing part 15 and engages with the chain 13 when the CVT 10 has the highest Hi (for example, overdrive: OD) (see FIG. 2). The movable teeth 16 are not limited to being provided on the pulley shaft portion 14 of the driven pulley 12, but may be provided on the pulley shaft portion 14 of the drive pulley 11. In this case, when the CVT 10 is at the lowest Lo, It protrudes from the outer surface of the movable tooth fixing part 15 and is engaged with the chain 13.
Thus, the movable tooth 16 provided on the pulley shaft portion 14 is at least one of the CVT 10 at the highest time and at the lowest time, that is, the chain 13 as the driving force transmission means is attached to the bottom of the V groove of the pulley. When present, the upper end surface 16 b surrounded by the inclined surface 16 a protruding from the outer surface of the movable tooth fixing component 15 is engaged with the chain 13.

チェーン13は、例えば、薄板リング状のチェーンリンク17を、2個一組のピン18を用いて、重ね合わせた状態で円環状に連結することにより形成されており、ピン18を連結軸として連結された各チェーンリンク17は、ピン18を軸としてピン18周りに自在に回動(揺動)する。各チェーンリンク17は、可動歯16に巻き付く側の可動歯16当接部分に、可動歯16のプーリ軸部14外表面からの突出形状に対応して切り欠かれた凹部(被噛合部)17aを有しており、凹部17aは、可動歯16のピッチと略一致したピッチで配置されている。   The chain 13 is formed by, for example, connecting thin chain ring-shaped chain links 17 in an annular shape using a set of two pins 18 and connecting the pins 18 as a connecting shaft. Each of the chain links 17 thus rotated freely (swings) around the pin 18 with the pin 18 as an axis. Each chain link 17 has a recess (engaged portion) cut out at a contact portion of the movable tooth 16 that wraps around the movable tooth 16 in accordance with the protruding shape of the movable tooth 16 from the outer surface of the pulley shaft portion 14. 17a, and the recesses 17a are arranged at a pitch substantially equal to the pitch of the movable teeth 16.

図4は、プーリ軸部にチェーンが巻き付いている状態を拡大して示す説明図である。図4に示すように、チェーン13がプーリのV溝底に位置するとき、プーリ軸部14に装着されて、例えば、コイルスプリング(或いはリング状スプリング)により軸部半径方向外側に押し上げられた(図中、矢印参照)可動歯16は、傾斜面16aに囲まれた上端面16bを、可動歯固定部品15の外表面から突出させている。
つまり、可動歯16は、突出する上端側が、駆動力伝達手段としてのチェーン(ロックアップチェーン)13のチェーンリンク17に形成された凹部17aに係止することで、チェーン13と噛み合った状態になる。
FIG. 4 is an explanatory view showing, in an enlarged manner, a state in which the chain is wound around the pulley shaft portion. As shown in FIG. 4, when the chain 13 is positioned at the bottom of the V groove of the pulley, the chain 13 is attached to the pulley shaft portion 14 and pushed up outward in the shaft portion radial direction by, for example, a coil spring (or ring-shaped spring) ( The movable tooth 16 has an upper end surface 16b surrounded by the inclined surface 16a protruding from the outer surface of the movable tooth fixing component 15.
That is, the movable tooth 16 is engaged with the chain 13 by engaging the protruding upper end side with the recess 17a formed in the chain link 17 of the chain (lock-up chain) 13 as the driving force transmitting means. .

このとき、チェーン13の凹部17aと噛み合い状態となった可動歯16は、傾斜面16aに囲まれた上端面16bをチェーンリンク17の凹部17aに位置させており、傾斜面16aを、凹部17aの開口縁部17bに接触させた状態になる。
図5は、図4におけるチェーンの凹部と可動歯の噛み合い状態を拡大して示す説明図である。図5に示すように、チェーンリンク17の凹部17aの、可動歯16に接触する開口縁部17bは、可動歯16に向かって側面視山形に膨出する凸曲面、即ち、鈍角度で交差する斜面の交差部を半円形状曲線で連結した曲面により形成されている。また、可動歯16の、上端面16bに向かう傾斜面16aは、開口縁部17bの形状に対応して側面視円弧状に穿かれた凹曲面により形成されている。
At this time, the movable tooth 16 meshed with the concave portion 17a of the chain 13 has the upper end surface 16b surrounded by the inclined surface 16a positioned at the concave portion 17a of the chain link 17, and the inclined surface 16a is moved to the concave portion 17a. It will be in the state made to contact the opening edge part 17b.
FIG. 5 is an explanatory view showing, in an enlarged manner, the meshing state of the recesses of the chain and the movable teeth in FIG. As shown in FIG. 5, the opening edge 17 b of the recess 17 a of the chain link 17 that contacts the movable tooth 16 intersects with a convex curved surface that bulges toward the movable tooth 16 in a side view, that is, at an obtuse angle. It is formed by a curved surface in which the intersections of the slopes are connected by a semicircular curve. Further, the inclined surface 16a of the movable tooth 16 toward the upper end surface 16b is formed by a concave curved surface that is bored in an arc shape in a side view corresponding to the shape of the opening edge portion 17b.

つまり、開口縁部17bの山形の頂部と傾斜面16aのなだらかな円弧が接触する接触部においては、可動歯16によるばね部材のばね反力F1(図中、白抜き矢印参照)と、チェーン13からの回転方向荷重F2が作用することになる。この回転方向荷重F2は、可動歯16からチェーン13へのトルク反力となる。
なお、開口縁部17bの凸曲面及び傾斜面16aの凹曲面は、可動歯16の回転方向一方に形成する場合(図5参照)に限らず、可動歯16の回転方向両方に形成されていてもよい。
In other words, at the contact portion where the top of the chevron of the opening edge portion 17b contacts the gentle arc of the inclined surface 16a, the spring reaction force F1 of the spring member by the movable teeth 16 (see the white arrow in the figure) and the chain 13 The rotation direction load F2 from is applied. This rotational load F2 becomes a torque reaction force from the movable tooth 16 to the chain 13.
The convex curved surface of the opening edge portion 17b and the concave curved surface of the inclined surface 16a are not limited to the case where the movable tooth 16 is formed in one rotational direction (see FIG. 5), but are formed in both the rotational directions of the movable tooth 16. Also good.

図6は、図5の接触部におけるばね反力と回転方向荷重について示す説明図である。図6に示すように、図5に示すような構成におけるチェーン(チェーン13)及びチェーンと噛合する噛合歯(可動歯16)の場合、チェーンが噛合歯から受けるトルク反力は、噛合歯のばね力(F1)と、チェーンと噛合歯の接触点の接線角度θによって決定される。従って、チェーンが受けるトルク反力(F2)を一定にするためには、噛合歯の軸部半径方向移動量によって接触点の接線角度θを変化させる(θ1,θ2)必要がある。   FIG. 6 is an explanatory diagram showing the spring reaction force and the rotational load at the contact portion of FIG. As shown in FIG. 6, in the case of the chain (chain 13) and the meshing teeth (movable teeth 16) meshing with the chain as shown in FIG. 5, the torque reaction force that the chain receives from the meshing teeth is the spring of the meshing teeth. It is determined by the force (F1) and the tangent angle θ of the contact point between the chain and the meshing teeth. Therefore, in order to make the torque reaction force (F2) that the chain receives constant, it is necessary to change the tangent angle θ of the contact point (θ1, θ2) according to the amount of movement of the meshing teeth in the axial direction.

このため、この発明に係るチェーン13と可動歯16の噛み合い構造では、可動歯16の、チェーン13と接触する部分が、可動歯16の回転方向荷重が一定(k×x×sinθ×cosθ=一定)となる形状を有している。ここで、k:可動歯に半径方向荷重を付与するばね部材のばね定数、x:可動歯の半径方向移動量、θ:可動歯のチェーンと接触する位置の接線角度、k×x×sinθ×cosθ:回転方向荷重である。   For this reason, in the meshing structure of the chain 13 and the movable teeth 16 according to the present invention, the portion of the movable teeth 16 that contacts the chain 13 has a constant rotational load of the movable teeth 16 (k × x × sin θ × cos θ = constant). ). Here, k: the spring constant of the spring member that applies a load in the radial direction to the movable tooth, x: the amount of movement of the movable tooth in the radial direction, θ: the tangential angle of the position that contacts the chain of the movable tooth, k × x × sin θ × cos θ: a rotational load.

図7は、この発明に係る可動歯の接触部形状の一例を示す説明図である。開口縁部17bの山形の頂部と接触する傾斜面16aのなだらかな円弧は、可動歯16の回転方向長さ(mm)と可動歯16の軸部半径方向長さ(mm)の間で、図7に示すような関係で変化する曲線から形成されている。これにより、チェーンが受けるトルク反力(F2)が一定になる。   FIG. 7 is an explanatory view showing an example of the shape of the contact portion of the movable tooth according to the present invention. The gentle arc of the inclined surface 16a that contacts the top of the chevron of the opening edge 17b is between the rotational direction length (mm) of the movable tooth 16 and the axial radial direction length (mm) of the movable tooth 16. 7 is formed from a curve that changes in the relationship shown in FIG. Thereby, the torque reaction force (F2) received by the chain becomes constant.

このように、図5に示すような、チェーン(チェーン13)及びチェーンと噛合する歯(可動歯16)を有する構成、即ち、チェーンのリンクの巻き付き側に凹部を設け、プーリ軸部(例えば、セカンダリプーリシャフト)の半径方向に可動する歯を配置し、軸部の歯にチェーンを噛み合わせる構成において、軸部半径方向に可動する歯(可動歯)の半径方向移動量が異なる場合、歯を突出状態に保持するばね反力が不均一になって、歯が受ける歯回転方向の荷重が不均一になってしまう。このため、歯に過大な荷重が加わることになり、歯の耐久性が低下してしまうことが避けられなかった。   Thus, as shown in FIG. 5, a structure having a chain (chain 13) and a tooth (movable tooth 16) meshing with the chain, that is, a recess is provided on the winding side of the link of the chain, and a pulley shaft portion (for example, (Secondary pulley shaft) in the configuration in which teeth that move in the radial direction are arranged and the chain is meshed with the teeth in the shaft portion, if the amount of movement in the radial direction of the shaft portion (movable teeth) differs, The spring reaction force held in the protruding state becomes nonuniform, and the load in the tooth rotation direction received by the teeth becomes nonuniform. For this reason, an excessive load is applied to the teeth, and the durability of the teeth is inevitably lowered.

そこで、軸部に配置された歯のチェーンと接触する部位が、歯の半径方向移動量に拘わらず歯からチェーンに伝わる回転方向のトルク反力が一定となるようにする。つまり、この発明に係る無段変速装置にあっては、可動歯16の軸部半径方向移動量によって可動歯16とチェーン13の接触点の接線角度を変更し、可動歯16の軸部半径方向移動量が異なる場合でも、チェーン13と噛み合っている可動歯16が受ける回転方向荷重を一定にするため、チェーン13と噛み合う可動歯16のチェーン13との接触部を、開口縁部17bの山形の頂部と傾斜面16aのなだらかな円弧が接触する構成にしている。   Therefore, the torque reaction force in the rotational direction transmitted from the tooth to the chain is constant regardless of the amount of radial movement of the tooth at the site in contact with the tooth chain disposed on the shaft. That is, in the continuously variable transmission according to the present invention, the tangent angle of the contact point between the movable tooth 16 and the chain 13 is changed according to the amount of movement of the movable tooth 16 in the axial portion radial direction. Even when the amount of movement is different, in order to make the rotational load received by the movable teeth 16 meshed with the chain 13 constant, the contact portion of the movable teeth 16 meshed with the chain 13 with the chain 13 is shaped like a chevron of the opening edge 17b. The top portion and the gentle arc of the inclined surface 16a are in contact with each other.

これにより、可動歯16と噛み合うチェーン13のピッチが異なっていても、チェーン13と噛み合っている可動歯16が受ける可動歯回転方向の荷重、即ち、チェーンが受けるトルク反力が一定となり、可動歯16及びチェーン13の耐久性が低下してしまうのを抑制することができる。
また、可動歯16のチェーン13と接触する部分が、可動歯16の回転方向荷重が一定(k×x×sinθ×cosθ=一定)となる形状を有する構成とすることで、任意のばね力や可動歯16の軸部半径移動量においても、可動歯16及びチェーン13の耐久性が低下してしまうのを抑制する効果を得ることができる。
As a result, even if the pitch of the chain 13 meshing with the movable tooth 16 is different, the load in the rotational direction of the movable tooth received by the movable tooth 16 meshing with the chain 13, that is, the torque reaction force received by the chain becomes constant. It can suppress that durability of 16 and the chain 13 falls.
Further, the portion of the movable tooth 16 that contacts the chain 13 has a configuration in which the rotational load of the movable tooth 16 is constant (k × x × sin θ × cos θ = constant), so that an arbitrary spring force or Even in the amount of movement of the shaft radius of the movable tooth 16, it is possible to obtain an effect of suppressing the deterioration of the durability of the movable tooth 16 and the chain 13.

このように、この発明に係る無段変速装置は、プーリのV溝底の軸に設置した噛合手段が、この噛合手段と噛み合って駆動力を伝達する駆動力伝達手段を攻撃することがなく、噛合手段と駆動力伝達手段の協調した動きを阻害することがない。その上に、可動歯16及びチェーン13の耐久性が低下してしまうのを抑制することができる。   Thus, in the continuously variable transmission according to the present invention, the meshing means installed on the shaft of the bottom of the V groove of the pulley does not attack the driving force transmitting means that meshes with the meshing means and transmits the driving force. The coordinated movement of the meshing means and the driving force transmitting means is not hindered. In addition, it is possible to prevent the durability of the movable teeth 16 and the chain 13 from decreasing.

この発明の一実施の形態に係る無段変速装置の概略説明図である。It is a schematic explanatory drawing of the continuously variable transmission which concerns on one embodiment of this invention. 図1のプーリ軸部にチェーンが巻き付いていない状態を示す説明図である。It is explanatory drawing which shows the state in which the chain is not wound around the pulley axial part of FIG. 図1のプーリ軸部にチェーンが巻き付いている状態を示す説明図である。It is explanatory drawing which shows the state in which the chain is wound around the pulley axial part of FIG. プーリ軸部にチェーンが巻き付いている状態を拡大して示す説明図である。It is explanatory drawing which expands and shows the state in which the chain is wound around the pulley shaft part. 図4におけるチェーンの凹部と可動歯の噛み合い状態を拡大して示す説明図である。It is explanatory drawing which expands and shows the meshing state of the recessed part of a chain in FIG. 4, and a movable tooth. 図5の接触部におけるばね反力と回転方向荷重について示す説明図である。It is explanatory drawing shown about the spring reaction force and rotation direction load in the contact part of FIG. この発明に係る可動歯の接触部形状の一例を示す説明図である。It is explanatory drawing which shows an example of the contact part shape of the movable tooth which concerns on this invention.

符号の説明Explanation of symbols

10 CVT
11 ドライブプーリ
12 ドリブンプーリ
13 チェーン(駆動力伝達手段)
14 軸部
15 可動歯固定部品
16 可動歯
16a 傾斜面
16b 上端面
17 チェーンリンク
17a 凹部
17b 開口縁部
18 ピン
F1 ばね反力
F2 回転方向荷重
θ 接線角度
10 CVT
11 Drive pulley 12 Driven pulley 13 Chain (drive force transmission means)
14 Shaft portion 15 Movable tooth fixed part 16 Movable tooth 16a Inclined surface 16b Upper end surface 17 Chain link 17a Recessed portion 17b Opening edge portion 18 Pin F1 Spring reaction force F2 Rotational load θ Tangential angle

Claims (3)

共にプーリ溝幅を変更可能な二つのプーリの間に掛け回された駆動力伝達手段により、一方のプーリの回転駆動力を他方のプーリに伝達する無段変速装置において、
前記駆動力伝達手段のプーリ巻き付き側に設けた被噛合部と、
前記プーリの軸部に、前記軸部に対し進出退避自在に軸部半径方向に移動可能に設置され、変速領域が最Hi時及び最Lo時の少なくとも一方のとき、進出状態になって前記被噛合部に噛合することができる可動噛合部とを有し、
前記可動噛合部の前記駆動力伝達手段と接触する部位を、前記可動噛合部の軸部半径方向移動量に拘わらず、前記駆動力伝達手段が前記可動噛合部から受けるトルク反力を一定にする形状に形成したことを特徴とする無段変速装置。
In the continuously variable transmission that transmits the rotational driving force of one pulley to the other pulley by the driving force transmitting means that is hung between two pulleys that can both change the pulley groove width.
A meshed portion provided on a pulley winding side of the driving force transmitting means;
It is installed on the shaft of the pulley so as to be movable in the shaft radial direction so that it can move forward and backward with respect to the shaft. When the speed change region is at least one of Hi and Lo, A movable meshing portion that can mesh with the meshing portion;
Regardless of the amount of movement of the movable mesh portion in the radial direction of the shaft, the torque reaction force that the drive force transmission device receives from the movable mesh portion is made constant at the portion of the movable mesh portion that contacts the drive force transmission device. A continuously variable transmission characterized by being formed into a shape.
前記可動噛合部の前記駆動力伝達手段と接触する部位は、前記可動噛合部の軸部半径方向移動量によって接触点の接線角度を変化させる山形の頂部となだらかな円弧により形成されていることを特徴とする請求項1に記載の無段変速装置。   The portion of the movable meshing portion that comes into contact with the driving force transmitting means is formed by a gentle arc that forms a top of a chevron that changes the tangential angle of the contact point according to the amount of radial movement of the movable meshing portion. The continuously variable transmission according to claim 1, wherein: 前記可動噛合部の前記駆動力伝達手段と接触する部位は、
前記可動噛合部を進出状態とするばねのばね定数をk、前記可動噛合部の半径方向移動量をx、前記可動噛合部の前記駆動力伝達手段と接触する位置の接線角度をθ、前記可動噛合部の回転方向荷重をk×x×sinθ×cosθとして、
k×x×sinθ×cosθ=一定
となる形状を有することを特徴とする請求項2に記載の無段変速装置。
The portion of the movable meshing portion that comes into contact with the driving force transmitting means is
The spring constant of the spring that sets the movable meshing portion in the advanced state is k, the radial movement amount of the movable meshing portion is x, the tangent angle of the position of the movable meshing portion in contact with the driving force transmitting means is θ, and the movable The rotation direction load of the meshing portion is k × x × sin θ × cos θ,
The continuously variable transmission according to claim 2, wherein the continuously variable transmission has a shape of k × x × sin θ × cos θ = constant.
JP2008146872A 2008-06-04 2008-06-04 Continuously variable transmission Expired - Fee Related JP5088241B2 (en)

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