JP4873337B2 - Conical disk winding transmission that can be adjusted steplessly - Google Patents

Conical disk winding transmission that can be adjusted steplessly Download PDF

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Publication number
JP4873337B2
JP4873337B2 JP2001303119A JP2001303119A JP4873337B2 JP 4873337 B2 JP4873337 B2 JP 4873337B2 JP 2001303119 A JP2001303119 A JP 2001303119A JP 2001303119 A JP2001303119 A JP 2001303119A JP 4873337 B2 JP4873337 B2 JP 4873337B2
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Japan
Prior art keywords
transmission
winding
conical disk
adjusted
winding member
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JP2001303119A
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Japanese (ja)
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JP2002276791A (en
Inventor
トイベルト アンドレ
ドゥーア ウーヴェ
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/125—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members characterised by means for controlling the geometrical interrelationship of pulleys and the endless flexible member, e.g. belt alignment or position of the resulting axial pulley force in the plane perpendicular to the pulley axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable

Description

【０００１】
【発明の属する技術分野】
本発明は、請求項１の上位概念として記載した無段階に調節可能な円錐円板巻掛け伝動装置に関する。
【０００２】
【従来の技術】
前述の型式の円錐円板巻掛け伝動装置は例えばＤＥ１００１７００５Ａ１号明細書により公知であり、その全内容を本願明細書に援用することにする。巻掛け部材は例えば板リンクチェーンとして構成できる。この板リンクチェーンは結合部材もしくは板リンクを貫通するピンを有し、該ピンはその端面で円錐円板の円錐面に接触させられ、これによって摩擦接続で力もしくは回転モーメントを伝達する。このような円錐円板巻掛け伝動装置の特徴は、当該伝動装置の伝動比とその摩滅状態とに関連して、巻掛け部材の幅の中心が各円錐円板対にて異なって変化し、巻掛け部材が軌跡シフトを伴って循環することである。このような軌跡シフトは当該伝動装置の耐用年限を短縮する。何故ならば前記軌跡シフトは巻掛け部材に曲げ負荷を作用させ、円錐円板若しくは該円錐円板に接触するピン端面の不等な摩耗をもたらすからである。
【０００３】
【発明が解決しようとする課題】
本発明の課題は軌跡シフトによって発生する問題が軽減されている円錐円板巻掛け伝動装置を提供することである。
【０００４】
【課題を解決するための手段】
前記課題は請求項１に記載した特徴によって解決された。
【０００５】
本発明によれば円錐円板巻掛け伝動装置の軸方向で不動である円板の軸方向シフトは当該伝動装置の耐用年限の間存在する巻掛け伝動装置もしくは巻掛け部材の総負荷が減退させられるように調節される。これは、摩耗に基づく軌跡シフトが当該伝動装置の耐用年限の間、軌跡シフト零を中心として変動すること、つまり、当該伝動装置の新しい状態では零の片側にありかつ古い状態では零の反対側にあり、軌跡シフトが全体としては零からできるだけわずかにしか遠ざからないようにすることによって達成された。
【０００６】
従属請求項は本発明による円錐巻掛け伝動装置の有利な実施例に関するものである。
【０００７】
【実施例】
図１に示されているように円錐円板巻掛け伝動装置は２つの円錐円板対１０と１２とを有している。これらの円錐円板対１０と１２は、互いに平行でかつ互いに間隔をおいて配置された軸Ａ１とＡ２とを中心として回転可能である。各円錐円板対は軸１４もしくは１６に不動に結合された固定円板１８もしくは２０と、軸１４もしくは１６と相対回動不能に結合はされてはいるものの、軸方向に軸に対し移動可能な調節円板２２もしくは２４とを有している。調節円板２２もしくは２４は公知の形式で復矢印の方向に逆向きに調節可能である。したがって円錐円板対に巻掛け部材２６，例えば板リンクチェーンが位置する有効半径が変化し、相応して当該伝動装置によって伝達される伝動比が変化させられる。
【０００８】
円錐円板の実線で示された位置が当該伝動装置の伝動比１に相当すると仮定する。つまり巻掛け部材２６両方の円錐円板対１０，１２を巡って循環する有効半径が等しいと仮定する。固定円板１８と２０との間の軸方向で測った間隔が、当該伝動装置の伝動比１で、円板２２と２０並びに１８と２４が半径方向で整合するように調節されると、巻掛け部材は軌道シフト零で、つまり軸Ａ１とＡ２とに対し正確に直角に循環する。この位置での巻掛け部材２６の中心線は２点鎖線で示されている。
【０００９】
さらに上側の調節円板２２が軸方向で固定円板１８に向かって動かされると、巻掛け部材２６は、円錐円板対１０においては、外方へ圧迫される。つまり当該伝動装置はオーバドライブの方向へ調節される。上方の円錐円板対１０の円錐円板が互いに接近するのに相応して、下方の円錐円板対１２の調節円板２４が軸方向で右へ調節され、巻掛け部材２６が円錐円板対１２に巻掛けられる半径は小さくなる。下方の円錐円板対１２における半径変化は上方の円錐円板対１０における半径変化よりも大きい。何故ならば円錐円板対の両方の区分は伝動比１の以外では軸Ａ１とＡ２との間の結合線に対し傾斜して延びることになるからである。図１にて見ることのできる巻掛け部材２６の上側領域Ｂは図１によれば、巻掛け部材２６の下側領域Ｃよりもわずかにしか右へ移動しない。したがって巻掛け部材２６が破線で示された位置にある場合に領域ＢとＣの中心点を結合する線は、伝動比が１である場合に巻掛け部材の相応する領域の中心点を結合する、正確に垂直に延びる２点差線で示された線に対し傾斜して延びることになる。２点鎖線に対する３点鎖線の傾斜は巻掛け部材２６が循環するときのシフトの尺度である。
【００１０】
図２には前述の関係が一層明確に示されている。
【００１１】
位置Ｉは当該伝動装置の伝動比１に相当している。固定歯車１８と２０との間の軸方向の間隔ａは図示の例では、巻掛け部材２６がシフトなしで、つまり巻掛け部材の上方の領域Ｂの中心が下方の領域Ｃの中心と同一平面内に位置するように調節されている。
【００１２】
位置ＩＩはオーバドライブ位置に相応する。この位置では上方の領域Ｂは位置Ｉに較べ、下方の領域Ｃに対し、さらに左へ移動させられている。したがって両方の領域の中心の間にはシフトｓが生じる。このシフトｓは巻掛け部材を付加的に負荷し、付加的な摩擦をもたらし、左側と右側の負荷を不等ならしめる。
【００１３】
位置ＩＩＩはアンダドライブ位置に相応する。この位置ＩＩＩでは上方領域Ｂは位置Ｉに較べて、上記理由と同じ理由からわずかにしか右へ移動させられていないので、両方の領域の中心間には、位置ＩＩにおけるシフトとほぼ正確に同じ大きさのシフトが生じる。
【００１４】
１１°の円錐角と湾曲させられた円錐面とを持って構成された伝動装置においては、最大の軌跡シフトと最小の軌跡シフトとの間の差異は約０．９ｍｍである。円錐面の凸状の湾曲は軌跡シフトを傾向的に、湾曲させられていない円錐面に対して縮小させる。
【００１５】
耐用年限の経過に伴って巻掛け部材２６は摩滅に晒される。この結果、巻掛け部材２６の軸方向の幅は減少させられる。つまり、位置Ｉにおける領域Ｂの中心は右へかつ領域Ｃの中心は左へ移動させられる。これにより反対方向での軸方向のシフトが発生する。総じて前記幅摩滅は、図３に示したように軌跡シフトｓを当該伝動装置の伝動比Ｕに関連して、新しい状態の実線カーブから破線カーブへ変化させる。この場合、破線カーブは巻掛け部材２６の最大許容幅摩滅での伝動比に関連した軌跡シフトを示している。
【００１６】
第３図においては当該伝動装置の両方の極比での軌跡シフトｓの絶対値が、チェーンもしくは巻掛け部材の幅摩耗に基づく耐用年限の終わりにおける伝動比１での軌跡シフトとほぼ同じ大きさである特に有利なケースが示されてる。この関係が与えられていないと、この関係は、値ａ（図２）の変化、つまり調節可能である固定板の間の間隔の変化によって達成するか又はほぼ達成することができる。値ａの調節方向に応じて図３の曲線は持上げられるか又は下げられるので、新しい状態での当該伝動装置の極比での軌跡シフトが巻掛け部材の耐用年限の終わりでの軌跡シフトとほぼ同じである状態を作ることができる。もちろん、値ａの調節は有利には当該伝動装置の新しい状態で行われる。
【００１７】
図３に示された関係は、当該伝動装置がその耐用年限の間、すべての伝動比でほぼ同じ長さ運転される限り、当該伝動装置が平均してポジティブな軌跡シフトと同じ長さネガティブな軌跡シフトで運転されるので特に有利である。
【００１８】
当該伝動装置が種々の伝動比で不等な長さ運転されると、例えば当該伝動装置の耐用年限の間もっぱらオーバドライブ領域で運転される（これは消費理由から有利である）と、オーバドライブ領域（伝動比０．５よりも小）における軌跡シフトが新しい状態もしくは当該伝動装置が調節される状態で、摩耗した巻掛け部材の場合と絶対的に正確に同じ大きさに調節することが有利である。この場合には図３の両方の曲線は図示の状態に対し約ｓ＝０．２だけ上方へシフトされるので、オーバドライブ領域における軌跡シフトは当該伝動装置の耐用年限の間、ネガティブな値からポジティブな値へ変化させれる。
【００１９】
さらに有利であることは、固定円板の軸方向の間隔ａを調節する場合には巻掛け部材の幅の製作公差を考慮することである。この場合には当該伝動装置はその瞬間に存在する巻掛け部材の幅平均値に調節されることである。
【００２０】
又、当該伝動装置が運転温度に達すると該伝動装置が受ける寸法変化も考慮し、図３に示された関係が当該伝動装置の運転温度でも存在するようにすることも有利である。
【００２１】
さらに有利であることは当該伝動装置及び巻掛け部材が負荷のもとで場合によっては変形することを考慮し、図３の関係が所定の回転モーメントで運転される伝動装置及び／又は所定の回転数帯域内で運転される伝動装置にて与えられるようにすることが有利である。
【００２２】
本願で提出した請求項は記載形態例であって、他の形態での特許権の保護の断念を意味するものではない。出願人はこれまで明細書本文及び／又は図面に開示されている別の特徴の組合わせについて特許を申請する権利を留保する。
【００２３】
従属請求項で用いた請求項の引用は独立請求項の対象の、各従属請求項の特徴による構成の変更を示しており、引用した従属請求項の特徴の組合わせの独立した保護の達成の断念として解されるべきではない。
【００２４】
従属請求項の対象は優先権主張日の公知技術に関して、個有の独立した発明を形成することができるので、出願人は、従属請求項を独立した請求項とするか分割出願とする権利を留保する。さらに従属請求項は先行する従属請求項の対象とは無関係な構成を有する独立した発明をも含んでいる。
【００２５】
実施例は本発明を限定するものと解されるべきではない。むしろ本願明細書の開示の枠内で、例えば明細書本文及び実施例並びに請求項に記載されかつ図面に含まれている特徴もしくは部材又は方法段階と関連して当業者が発明の課題の解決に関連して推考し、組合わされた特徴により新しい対象又は方法段階もしくは方法段階順序をもたらす数多くの変化及び変更、特にヴァリエーション、部材、組合わせ及び／又は材料が、製造、検査及び作業方法に関しても可能である。
【図面の簡単な説明】
【図１】円錐円板巻掛け伝動装置の円錐円板対を異なる伝達比のもとで示した断面図。
【図２】調節例を説明するための概略図。
【図３】線図。
【符号の説明】
１０，１２ 円錐円板対、 １４，１６ 軸、 １８，２０ 固定円板、 ２２，２４ 調節円板、 ２６ 巻掛け部材[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a continuously variable conical disk winding transmission device described as a superordinate concept of claim 1.
[0002]
[Prior art]
A conical disk winding transmission of the aforementioned type is known, for example, from DE 10017005A1, the entire content of which is incorporated herein by reference. The winding member can be configured as a plate link chain, for example. The plate link chain has a pin that passes through the coupling member or plate link, the pin being brought into contact with the conical surface of the conical disk at its end face, thereby transmitting a force or a rotational moment in a frictional connection. The characteristics of such a conical disk winding transmission device are related to the transmission ratio of the transmission device and its worn state, and the center of the width of the winding member varies differently for each conical disk pair, The winding member circulates with a locus shift. Such a trajectory shift shortens the service life of the transmission. This is because the trajectory shift causes a bending load to be applied to the winding member, resulting in unequal wear of the conical disk or the pin end surface contacting the conical disk.
[0003]
[Problems to be solved by the invention]
SUMMARY OF THE INVENTION An object of the present invention is to provide a conical disk winding transmission device in which problems caused by locus shift are reduced.
[0004]
[Means for Solving the Problems]
The problem has been solved by the features of claim 1.
[0005]
According to the present invention, the axial shift of the disc, which is stationary in the axial direction of the conical disk winding transmission, reduces the total load of the winding transmission or the winding member that exists for the lifetime of the transmission. Adjusted to be. This is because the wear-induced trajectory shift fluctuates around the trajectory shift zero during the lifetime of the transmission, i.e., on one side of zero in the new state of the transmission and on the opposite side of zero in the old state. The trajectory shift as a whole was achieved by moving as little as possible away from zero.
[0006]
The dependent claims relate to advantageous embodiments of the conical winding transmission according to the invention.
[0007]
【Example】
As shown in FIG. 1, the conical disk winding transmission has two conical disk pairs 10 and 12. These conical disk pairs 10 and 12 are rotatable about axes A1 and A2 which are parallel to each other and spaced from each other. Each pair of conical discs is fixed to a fixed disc 18 or 20 that is immovably coupled to the shaft 14 or 16 and is non-rotatably coupled to the shaft 14 or 16, but is movable relative to the shaft in the axial direction. And an adjusting disk 22 or 24. The adjusting disk 22 or 24 can be adjusted in a known manner in the reverse direction in the direction of the reverse arrow. Accordingly, the effective radius at which the winding member 26, for example, the plate link chain is positioned on the conical disk pair is changed, and the transmission ratio transmitted by the transmission is changed accordingly.
[0008]
It is assumed that the position indicated by the solid line of the conical disk corresponds to the transmission ratio 1 of the transmission. That is, it is assumed that the effective radii circulating around the conical disk pairs 10 and 12 of both the winding members 26 are equal. When the axially measured spacing between the fixed discs 18 and 20 is adjusted so that the discs 22 and 20 and 18 and 24 are aligned in the radial direction with a transmission ratio 1 of the transmission, The hanging member circulates exactly at right angles to the axes A1 and A2 with zero orbital shift. The center line of the winding member 26 at this position is indicated by a two-dot chain line.
[0009]
When the upper adjustment disk 22 is moved toward the stationary disk 18 in the axial direction, the winding member 26 is pressed outward in the conical disk pair 10. That is, the transmission is adjusted in the direction of overdrive. Corresponding to the conical disks of the upper conical disk pair 10 approaching each other, the adjusting disk 24 of the lower conical disk pair 12 is adjusted to the right in the axial direction and the winding member 26 is conical. The radius wound around the pair 12 becomes smaller. The radius change in the lower conical disc pair 12 is larger than the radius change in the upper conical disc pair 10. This is because both sections of the conical disk pair extend at an angle with respect to the connecting line between the axes A1 and A2 except for a transmission ratio of 1. According to FIG. 1, the upper region B of the winding member 26 visible in FIG. 1 moves slightly to the right than the lower region C of the winding member 26. Therefore, the line connecting the center points of the regions B and C when the winding member 26 is in the position indicated by the broken line connects the center points of the corresponding regions of the winding member when the transmission ratio is 1. , It extends with an inclination with respect to a line indicated by a two-point difference line extending vertically. The slope of the three-dot chain line with respect to the two-dot chain line is a measure of the shift when the winding member 26 circulates.
[0010]
FIG. 2 shows the above relationship more clearly.
[0011]
The position I corresponds to a transmission ratio 1 of the transmission. In the illustrated example, the axial distance a between the fixed gears 18 and 20 is the same as the center of the lower region C when the winding member 26 is not shifted, that is, the center of the region B above the winding member. It is adjusted to be located inside.
[0012]
Position II corresponds to the overdrive position. At this position, the upper area B is moved further to the left than the position I with respect to the lower area C. Therefore, a shift s occurs between the centers of both regions. This shift s additionally loads the wrapping member, provides additional friction and makes the left and right loads unequal.
[0013]
Position III corresponds to the underdrive position. At this position III, the upper area B is moved slightly to the right compared to position I for the same reason as above, so between the centers of both areas is almost exactly the same as the shift at position II. A magnitude shift occurs.
[0014]
In a transmission constructed with a cone angle of 11 ° and a curved conical surface, the difference between the maximum and minimum trajectory shift is about 0.9 mm. The convex curvature of the conical surface tends to reduce the trajectory shift relative to the uncurved conical surface.
[0015]
As the service life expires, the winding member 26 is subject to wear. As a result, the axial width of the winding member 26 is reduced. That is, the center of the region B at the position I is moved to the right and the center of the region C is moved to the left. This causes an axial shift in the opposite direction. In general, the width wear changes the locus shift s from the solid curve in the new state to the broken curve in relation to the transmission ratio U of the transmission as shown in FIG. In this case, the dashed curve indicates the locus shift associated with the transmission ratio at the maximum allowable width wear of the winding member 26.
[0016]
In FIG. 3, the absolute value of the locus shift s at both pole ratios of the transmission is almost the same as the locus shift at the transmission ratio 1 at the end of the service life based on the width wear of the chain or the winding member. A particularly advantageous case is shown. If this relationship is not given, this relationship can be achieved or almost achieved by a change in the value a (FIG. 2), ie the change in the spacing between the fixed plates which is adjustable. Depending on the adjustment direction of the value a, the curve in FIG. 3 is lifted or lowered so that the trajectory shift at the pole ratio of the gearing in the new state is almost the same as the trajectory shift at the end of the service life of the winding member. You can make a state that is the same. Of course, the adjustment of the value a is preferably performed in the new state of the transmission.
[0017]
The relationship shown in FIG. 3 is that, as long as the transmission is operated for approximately the same length at all transmission ratios during its service life, the transmission is on average negative as long as a positive trajectory shift. It is particularly advantageous because it is operated with a trajectory shift.
[0018]
If the transmission is operated at unequal lengths with different transmission ratios, for example, it is operated exclusively in the overdrive region for the lifetime of the transmission (this is advantageous for reasons of consumption) and overdrive It is advantageous to adjust it to exactly the same magnitude as in the case of a worn winding member in a new state of the trajectory shift in the region (less than transmission ratio 0.5) or in a state where the transmission is adjusted. It is. In this case, both curves in FIG. 3 are shifted upward by about s = 0.2 with respect to the state shown, so that the trajectory shift in the overdrive region is negative from the negative value during the lifetime of the transmission. It can be changed to a positive value.
[0019]
It is further advantageous to take into account the manufacturing tolerances of the width of the winding member when adjusting the axial spacing a of the fixed disks. In this case, the transmission is adjusted to the average width value of the winding member existing at that moment.
[0020]
It is also advantageous that the relationship shown in FIG. 3 also exists at the operating temperature of the transmission, taking into account the dimensional changes experienced by the transmission when the transmission reaches the operating temperature.
[0021]
It is further advantageous that the transmission and / or winding member is operated with a predetermined rotational moment and / or a predetermined rotation, taking into account that the transmission and the winding member may be deformed in some cases under load. It is advantageous to be provided with a transmission that operates within several bands.
[0022]
The claims filed in this application are examples of description, and do not imply abandonment of protection of patent rights in other forms. Applicant reserves the right to apply for a patent for another combination of features previously disclosed in the specification and / or drawings.
[0023]
The citation of a claim used in a dependent claim indicates a change in structure of the subject of the independent claim due to the characteristics of each dependent claim, and achieves independent protection of the combination of features of the dependent claims cited. It should not be interpreted as an abandonment.
[0024]
Since the subject matter of the dependent claim can form an independent independent invention with respect to the prior art of the priority claim date, the applicant has the right to make the dependent claim an independent claim or a divisional application. Reserve. In addition, the dependent claims include independent inventions having configurations unrelated to the subject matter of the preceding dependent claims.
[0025]
The examples should not be construed as limiting the invention. Rather, within the scope of the disclosure herein, one of ordinary skill in the art, for example, in connection with the features or elements or method steps described in the specification and examples, and in the claims and included in the drawings, solves the problems of the invention. Numerous changes and modifications, particularly variations, components, combinations and / or materials, that can lead to new objects or method steps or method step sequences with associated inference and combined features are also possible with respect to manufacturing, inspection and working methods It is.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a conical disk pair of a conical disk winding transmission apparatus under different transmission ratios.
FIG. 2 is a schematic diagram for explaining an adjustment example.
FIG. 3 is a diagram.
[Explanation of symbols]
10,12 conical disk pairs, 14,16 shafts, 18,20 fixed disks, 22,24 adjusting disks, 26 winding members

Claims (7)

無段階に調節できる円錐円板巻掛け伝動装置であって、巻掛け部材の巻掛けられた、それぞれ１つの軸と相対回動不能に結合された２つの円錐円板対を有し、前記軸が互いに平行にかつ半径方向で間隔をおいて配置されており、各円錐円板対が、所属の軸と不動に結合された固定円板と所属の軸に対し相対的に軸方向に移動可能な調節円板とを有し、両方の円板対の固定円板と調節円板とが反対に向き合って配置され、伝動比を変化させるための円錐円板対の円板間の逆向きの間隔変化に際して巻掛け部材が軸方向で同じ方向へ移動するように前記固定円板と調節円板とが配置されている円錐円板巻掛け伝動装置において、巻掛け部材の軌跡シフトのための第１の関係として、少なくとも所定の伝動比で、伝動装置のさらなる耐用年限の間、巻掛け部材の軌跡シフトがその符号を巻掛け部材の幅摩滅に基づき変化させるように、当該巻掛け伝動装置の現時点での軸方向で測った固定円板間の間隔が調節されることを特徴とする、無段階に調節できる、円錐円板巻掛け伝動装置。A conical disk winding transmission that can be adjusted steplessly, comprising two conical disk pairs wound around a winding member, each of which is coupled to a single shaft so as not to rotate relative to each other. Are arranged parallel to each other and spaced in the radial direction, and each conical disc pair can move in the axial direction relative to the associated disc and the associated disc immovably coupled to the associated axis. And the fixed disk of both disk pairs and the adjusting disk are arranged opposite to each other, with the opposite direction between the disks of the conical disk pair for changing the transmission ratio. In the conical disk winding transmission device in which the fixed disk and the adjustment disk are arranged so that the winding member moves in the same direction in the axial direction when the interval is changed, a first for shifting the locus of the winding member is provided. as one relationship, even without least at a predetermined transmission ratio, during the further lifetime of the transmission, The locus shift its sign member to vary based on the width attrition wrapping member over a feature in that distance fixed donut plates, measured in the axial direction at the present time of the belt-driven is adjusted Conical disk winding transmission that can be adjusted steplessly. 軸方向で測った固定円板間の間隔が当該伝動装置の新しい状態で調節される、請求項１記載の円錐円板巻掛け伝動装置。  2. The conical disk winding transmission according to claim 1, wherein the distance between the fixed disks measured in the axial direction is adjusted in a new state of the transmission. 巻掛け部材の軌跡シフトのための第２の関係として、所定の伝動比における巻掛け部材の軌跡シフトが調節状態では巻掛け部材の幅摩滅に関して許容される耐用年限の終わりにおける巻掛け部材の摩滅状態にほぼ等しい絶対値を有するように、軸方向で測った固定円板の間隔が調節されている、請求項１又は２記載の円錐円板巻掛け伝動装置。 As a second relationship for the locus shift of the winding member, the wear of the winding member at the end of the service life permitted with respect to the width wear of the winding member when the locus shift of the winding member at a predetermined transmission ratio is adjusted. The conical disk-wound transmission device according to claim 1 or 2, wherein the distance between the fixed disks measured in the axial direction is adjusted so as to have an absolute value substantially equal to the state. 巻掛け部材の軌跡シフトのための第３の関係として、当該伝動装置の両方の限界伝動比における巻掛け部材の軌跡シフトの絶対値が巻掛け部材の最大許容幅摩滅での伝動比１で期待される軌跡シフトの絶対値とほぼ同じ大きさになるように、軸方向で測った固定円板の間隔が調節される、請求項１又は２記載の円錐円板巻掛け伝動装置。 A third relationship for the locus shift of wrapping member, in transmission ratio 1 at the maximum allowable width attrition absolute value wrapping member of both the locus shift winding member at the limit transmission ratio of the transmission The conical disk-wound transmission device according to claim 1 or 2, wherein the distance between the fixed disks measured in the axial direction is adjusted so as to be approximately the same as an expected absolute value of the locus shift. 新しい状態で許容される公差の限界にある幅を有する巻掛け部材の軌跡シフトに対して前記第１，２，３の関係が満たされるように、軸方向で測った固定円板の間隔が調節される、請求項１から４までのいずれか１項記載の円錐円板巻掛け伝動装置。The distance between the fixed disks measured in the axial direction is adjusted so that the first, second, and third relations are satisfied with respect to the locus shift of the winding member having a width that is within the limit of the allowable tolerance in the new state. The conical disk-wound transmission device according to any one of claims 1 to 4 , wherein the transmission device is wound. 巻掛け部材の軌跡シフトのための前記第１，２，３の関係が運転温度にある当該伝動装置でも充たされるように、軸方向で測った固定円板の間隔が調節される、請求項１から５までのいずれか１項記載の円錐円板巻掛け伝動装置。 The distance between the fixed disks measured in the axial direction is adjusted so that the first , second, and third relationships for trajectory shifting of the winding member are also satisfied in the transmission device at the operating temperature. The conical disk winding transmission device according to any one of claims 1 to 5. 巻掛け部材の軌跡シフトのための前記第１，２，３の関係が、負荷のもとで運転される当該伝動装置で充たされるように、軸方向で測った固定円板の間隔が調節される、請求項１から６までのいずれか１項記載の円錐円板巻掛け伝動装置。The distance between the fixed disks measured in the axial direction is adjusted so that the first, second, and third relations for shifting the locus of the winding member are satisfied by the transmission that is operated under a load. The conical disk winding transmission device according to any one of claims 1 to 6.
JP2001303119A 2001-03-12 2001-09-28 Conical disk winding transmission that can be adjusted steplessly Expired - Fee Related JP4873337B2 (en)

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