JPH05296270A - Coned disc spring device - Google Patents
Coned disc spring deviceInfo
- Publication number
- JPH05296270A JPH05296270A JP9326092A JP9326092A JPH05296270A JP H05296270 A JPH05296270 A JP H05296270A JP 9326092 A JP9326092 A JP 9326092A JP 9326092 A JP9326092 A JP 9326092A JP H05296270 A JPH05296270 A JP H05296270A
- Authority
- JP
- Japan
- Prior art keywords
- disc spring
- coned disc
- pulley
- deformation
- elements
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000000903 blocking effect Effects 0.000 claims description 3
- 230000007423 decrease Effects 0.000 abstract description 10
- 238000004804 winding Methods 0.000 abstract description 6
- 230000002093 peripheral effect Effects 0.000 abstract description 4
- 230000005540 biological transmission Effects 0.000 description 24
- 238000006073 displacement reaction Methods 0.000 description 14
- 230000002265 prevention Effects 0.000 description 6
- 230000002441 reversible effect Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000002829 reductive effect Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
Landscapes
- Transmissions By Endless Flexible Members (AREA)
- Springs (AREA)
- Pulleys (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は可動式変速プーリ等の装
置に用いられる皿バネ装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disc spring device used in a device such as a movable transmission pulley.
【0002】[0002]
【従来の技術】従来皿バネ装置としては図4に示す可動
変速プーリに用いられたものがある。図4はVベルトを
介して駆動軸から従動軸のプーリに回転駆動が伝達され
る無段変速機を示したものである。同図に示すように従
動軸10はフレーム11にベアリング12を介して回動
自在に軸支されている。さらに従動軸にはベアリング1
3、14を介してドリブンフェース15にはV型プーリ
16が取着されている。当該V型プーリ16は固定プー
リ17と可動プーリ18からなり、Vベルト19が可動
プーリ18の外側に複数の皿バネ20が重ね合わされて
いる。かかる可動変速プーリを有する無段変速機は前記
対を成すプーリの可動プーリを開閉することにより当該
間隔に巻き掛けられているVベルト19の巻き付き径を
増減させて変速を行うものである。この場合に低速回転
から高速回転に至るまでのプーリ開閉のストロークを満
たすために可動プーリの外側に複数の皿バネ素子を並立
した皿バネ装置が配設される。2. Description of the Related Art As a conventional disc spring device, there is one used for a movable transmission pulley shown in FIG. FIG. 4 shows a continuously variable transmission in which rotary drive is transmitted from a drive shaft to a pulley of a driven shaft via a V belt. As shown in the figure, the driven shaft 10 is rotatably supported by a frame 11 via a bearing 12. Furthermore, the driven shaft has a bearing 1
A V-shaped pulley 16 is attached to the driven face 15 via the rollers 3 and 14. The V-shaped pulley 16 includes a fixed pulley 17 and a movable pulley 18, and a V-belt 19 has a plurality of disc springs 20 superposed on the outside of the movable pulley 18. In the continuously variable transmission having such a movable speed change pulley, the movable pulleys of the paired pulleys are opened and closed to increase or decrease the winding diameter of the V-belt 19 wound around the gap to perform the speed change. In this case, a disc spring device having a plurality of disc spring elements arranged side by side is arranged outside the movable pulley in order to satisfy the opening / closing stroke of the pulley from low speed rotation to high speed rotation.
【0003】ところで、当該皿バネ素子の一般的特性の
うち、皿バネの変形変位と押圧荷重との関係は変形変位
の増加とともに押圧荷重が増加するか、所定変位後は漸
次増加するものがある。一方、皿バネの変形変位の増加
とともに押圧荷重がピークに達し、その後は皿バネの直
立時(密着点)に向かうに従い押圧荷重が減少する特性
を有するものである。Among the general characteristics of the Belleville spring element, there is a relationship between the deformation displacement of the Belleville spring and the pressing load, in which the pressing load increases with the increasing deformation displacement, or gradually increases after a predetermined displacement. .. On the other hand, the pressing load reaches a peak with an increase in the deformation displacement of the disc spring, and thereafter, the pressing load decreases as the disc spring goes upright (the contact point).
【0004】前記無段変速機は、前述したように可動プ
ーリとV型ベルトにより駆動軸の回転を従動軸に伝達す
るもので、可動プーリの押圧荷重が小さいと、プーリと
ベルトの伝達面においてすべりを生じ、一方、皿バネ素
子の押圧荷重が大きい程、プーリとベルトの間に所定の
押圧荷重以上の圧着力が働き、いずれにしてもベルト式
の無段変速機の動力伝達機構では、伝達効率が悪い。As described above, the continuously variable transmission transmits the rotation of the drive shaft to the driven shaft by the movable pulley and the V-shaped belt. If the pressing load of the movable pulley is small, the transmission surface between the pulley and the belt is reduced. On the other hand, slippage occurs, and on the other hand, the larger the pressing load of the disc spring element, the more pressing force acts between the pulley and the belt than the predetermined pressing load. Transmission efficiency is poor.
【0005】押圧荷重が小さく、プーリとベルトの伝達
面において、すべりを生じる場合には、皿バネ素子を並
列の積み重ね配置することにより、このすべりを防止す
ることができるが、前記の変形変位の増加とともに押圧
荷重が増加する特性を有する皿バネ素子を採用すると図
4下半部に示される状態の時には必要以上の圧着力でベ
ルトが押圧されるので伝達効率を低下させることにな
る。そこで伝達効率を低下させないものとして前記変形
変位の増加とともに押圧荷重がピークに達し、その後密
着点に向うに従い押圧荷重が減少する特性を有する皿バ
ネを採用することが考えられる。When the pressing load is small and slippage occurs on the transmission surfaces of the pulley and the belt, the slippage can be prevented by arranging the Belleville spring elements in parallel. If a disc spring element having a characteristic that the pressing load increases with an increase is adopted, in the state shown in the lower half of FIG. 4, the belt is pressed with an excessive pressing force, so that the transmission efficiency is reduced. Therefore, it is conceivable to employ a disc spring that has a characteristic that the pressing load reaches a peak with the increase of the deformation displacement and then the pressing load decreases toward the close contact point, without decreasing the transmission efficiency.
【0006】かかる皿バネ素子は可動プーリの移動範囲
に対して、変形変位と押圧荷重特性のうち、押圧荷重の
ピーク時を含む両側を作動範囲とすることによりベルト
による駆動力の伝達効率をより高くすることができる。[0006] Such a disc spring element further improves the transmission efficiency of the driving force by the belt by setting both sides of the deformation displacement and the pressing load characteristics, including the peak time of the pressing load, as the operating range with respect to the moving range of the movable pulley. Can be higher.
【0007】[0007]
【発明が解決しようとする課題】ベルト式無段変速機に
皿バネ装置を用いた場合には、伝達効率の向上の点から
鑑みると、前記特性を有する皿バネ素子を選択すること
により目的を達することができるが、可動プーリの移動
距離を大きくするには複数枚の皿バネ素子を対向配置さ
せる必要がある。しかし、かかる複数枚の皿バネ素子
は、各皿バネの荷重のばらつきにより、押圧荷重の高い
素子は低い素子を押しつけ、前述した押圧荷重のピーク
時以降の押圧荷重−変形変位の減衰曲線からの騒音を発
するとともに、反転して皿バネ素子自体も反転した変形
曲線を描くこととなる。つまり、反転した皿バネ素子に
より可動プーリは正規の移動ができなくなり伝達効率を
悪化させるばかりか無段変速機の変速特性にまで悪影響
を及ぼすことになる。そこで、本発明は、皿バネ素子に
押圧力が加えられた場合に各皿バネの荷重のばらつきが
あった場合でも、作動範囲中に反転することがなく、押
圧荷重を初期設定状態の性能に保つことができる皿バネ
装置の提供を目的とするものである。When a disc spring device is used in a belt type continuously variable transmission, in view of improving transmission efficiency, the purpose is to select a disc spring element having the above-mentioned characteristics. However, in order to increase the moving distance of the movable pulley, it is necessary to dispose a plurality of disc spring elements facing each other. However, in such a plurality of Belleville spring elements, due to the variation in the load of each Belleville spring, the element with a high pressure load pushes the element with a low pressure, and from the above-described pressure load-deformation displacement attenuation curve Along with the generation of noise, the disk spring element itself is inverted to draw a deformation curve. That is, the reversing disc spring element prevents the movable pulley from moving properly, which not only deteriorates the transmission efficiency but also adversely affects the transmission characteristics of the continuously variable transmission. Therefore, the present invention does not reverse within the operating range even if the load of each disc spring varies when a pressing force is applied to the disc spring element, and the pressing load is set to the performance in the initial setting state. An object is to provide a disc spring device that can be kept.
【0008】[0008]
【課題を解決するための手段】本発明は上記に鑑みてな
されたものであり、各皿バネ素子の荷重がばらついても
各素子が反転することがなく、従って、反転時の騒音を
発することがなく、皿バネの各素子の変形変位の作動範
囲中において皿バネ荷重がピークを有する皿バネ素子を
採用することができ、かかる素子を使用した場合に高速
回転での伝達効率の低下を回避することができるもので
ある。SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and even if the load of each disc spring element varies, each element does not invert, so that noise is generated at the time of inversion. It is possible to adopt a Belleville spring element that has a peak in the Belleville spring load within the operating range of deformation and displacement of each element of the Belleville spring, and avoids a reduction in transmission efficiency at high speed rotation when using such an element. Is what you can do.
【0009】かかる目的を達成するために、複数の皿バ
ネ素子を組み合わせて弾性源とする皿バネ装置におい
て、互いに向かい合って配置された皿バネ素子間に、反
転阻止部材を介在させたものである。In order to achieve such an object, in a disc spring device in which a plurality of disc spring elements are combined and used as an elastic source, a reversal prevention member is interposed between the disc spring elements arranged so as to face each other. ..
【0010】[0010]
【実施例】以下、本発明の一実施例を詳細に説明する。
前記した図4で説明した記載と重複する説明は省略する
が、図1において駆動源1からの動力はV型ベルト2に
よって無段変速機のV型プーリ3に伝達される。このV
型プーリ3は一対の固定プーリ4と、可動プーリ支持部
材に滑動的に支持された可動プーリ5が対面する傾斜面
を有するように立設され、この傾斜面によって形成され
たV溝間に前記駆動源1の駆動軸に軸支されたプーリか
らの駆動力を伝達するようにV型ベルト2が無端状に巻
架されている。かかる駆動源1からの動力は、V型ベル
ト2の端面と無段変速機のプーリのV溝の傾斜面の摩擦
力によって伝達される。この摩擦力は可動プーリ5の外
側に当接する複数の皿状の皿バネ装置6の圧縮変形力に
よって押圧されることにより発生し、かかる摩擦力とV
型ベルトの回転数との関係によってV溝傾斜面でのV型
ベルトの位置が変動する。即ち、V型ベルト2の回転ス
タート時はその巻付き径が大きい位置に巻架されるが、
回転数が増大するとともに巻付き径が減少する。この巻
付き径が減少する場合には、プーリ間のV溝間隙が拡張
し、可動プーリ5が可動プーリ支持部材上を後退する。
一般的な弾性体においては荷重−変形特性によって変形
量に応じてその荷重(押圧荷重)は増大するが、本発明
においては前述した荷重−変形変位特性にピークを有す
る皿バネ素子を採用するために、V型ベルトの巻付き径
とこれに関与するプーリの摩擦力が最適な状態で回転駆
動を付与し、伝達効率を向上するものである。EXAMPLES An example of the present invention will be described in detail below.
Although the description that overlaps with the description described with reference to FIG. 4 is omitted, in FIG. 1, the power from the drive source 1 is transmitted to the V-shaped pulley 3 of the continuously variable transmission by the V-shaped belt 2. This V
The mold pulley 3 is erected so as to have a pair of fixed pulleys 4 and a sloped surface facing a movable pulley 5 slidably supported by a movable pulley support member, and between the V grooves formed by the sloped surfaces. A V-shaped belt 2 is endlessly wound so as to transmit a driving force from a pulley axially supported by a drive shaft of a drive source 1. The power from the drive source 1 is transmitted by the frictional force between the end surface of the V-shaped belt 2 and the inclined surface of the V groove of the pulley of the continuously variable transmission. This frictional force is generated by being pressed by the compressive deformation force of the plurality of disc-shaped disc spring devices 6 contacting the outside of the movable pulley 5, and the frictional force and V
The position of the V-shaped belt on the V-groove inclined surface varies depending on the relationship with the rotation speed of the mold belt. That is, when the V-shaped belt 2 starts rotating, the V-shaped belt 2 is wound around a position where the winding diameter is large.
The winding diameter decreases as the rotation speed increases. When this winding diameter decreases, the V-groove gap between the pulleys expands, and the movable pulley 5 retracts on the movable pulley support member.
In a general elastic body, its load (pressing load) increases according to the amount of deformation due to the load-deformation characteristic, but in the present invention, since the above-mentioned disc spring element having a peak in the load-deformation displacement characteristic is adopted. In addition, the wrapping diameter of the V-shaped belt and the frictional force of the pulleys related to the V-shaped belt are applied to the rotational drive in an optimal state to improve the transmission efficiency.
【0011】図2は本発明で採用される各皿バネ素子が
有する荷重−変位特性を示すものである。各皿バネ素子
はその中心が凹状に変形した皿状の形態を有し、当該皿
の外周縁が平板になる方向に漸次応力を掛けたときに、
皿の変形量に応じて応力が増大し、一端ピークを迎えた
後は減少する。この場合に、減少曲線の変曲点付近で皿
バネ素子は中心部と外周縁が平板となり(密着点)、そ
の後皿バネ素子は一転して凹凸が反転する。この反転後
の皿バネ素子は当初の変位量に応じた応力の増減がみら
れる。前述した通り、本発明で採用される皿バネ素子は
その作動範囲が図2における荷重がピーク時を含み増減
する範囲を採用するものであり、密着点以降の変形押圧
力は必要としない。しかし、複数の皿バネ素子を直列に
配列し、その各素子間に一律に応力が働くと、各素子の
質量、板厚あるいはその素材が有する組成のバラツキに
よって、各皿バネ素子間で変形量が相違することがあ
る。このことは、各素子における図2の荷重−変形特性
曲線が一律に描かれないことを意味し、各素子の中には
早く密着点に達するものと、隣接する素子が密着点に達
しないものが存在することとなる。従って、各素子の荷
重−変形特性のばらつきにより各素子を直列に配置した
場合には、各素子間の変形により、荷重が大きい(密着
点に達しない)素子が荷重が小さい(早く密着点に達し
ようとする)素子を押圧し、荷重が小さい素子は荷重の
ピーク点に達すると騒音を発するとともに反転すること
になる。このような各素子の変形特性のばらつきはプー
リとベルト間の摩擦力の変動を招来し、回転駆動力の伝
達効率の低下を来す。かかる観点から本発明においては
各々の皿バネ素子のばらつきを容認した上で、その密着
点に到達した場合でも素子は一律に反転させない変位制
限部材を配したものである。FIG. 2 shows the load-displacement characteristics of each disc spring element used in the present invention. Each disc spring element has a dish shape in which its center is deformed into a concave shape, and when a gradual stress is applied in a direction in which the outer peripheral edge of the dish becomes a flat plate,
The stress increases with the amount of dish deformation, and then decreases after reaching a peak. In this case, in the vicinity of the inflection point of the decreasing curve, the central portion and the outer peripheral edge of the Belleville spring element become flat (contact point), and then the Belleville spring element reverses and the irregularities are reversed. After the reversal, the disc spring element shows an increase or decrease in stress according to the initial displacement amount. As described above, the Belleville spring element used in the present invention adopts a range in which the operating range thereof increases and decreases including the peak load in FIG. 2, and does not require the deformation pressing force after the contact point. However, if multiple disc spring elements are arranged in series and a uniform stress is applied between the elements, the amount of deformation between the disc spring elements may vary due to variations in the mass of each element, the plate thickness, or the composition of the material. May be different. This means that the load-deformation characteristic curve of each element in FIG. 2 is not drawn uniformly, and some elements reach the contact point early and those adjacent elements do not reach the contact point. Will exist. Therefore, when each element is arranged in series due to the variation in load-deformation characteristics of each element, the element with a large load (not reaching the contact point) has a small load due to the deformation between the elements (it quickly reaches the contact point). An element with a small load will generate noise and will flip when it reaches the peak point of the load. Such variations in the deformation characteristics of the respective elements cause fluctuations in the frictional force between the pulley and the belt, resulting in a reduction in the transmission efficiency of the rotational driving force. From this point of view, in the present invention, the variation of each disc spring element is allowed, and the element is provided with a displacement limiting member that does not uniformly reverse even when the contact point is reached.
【0012】図3は本発明による皿バネ装置6の構成の
一実施例を示すものであり、プーリ軸7に取り付けられ
た一対の固定プーリ4と可動プーリ5と、当該可動プー
リ5はプーリ軸7に可動的であり、このプーリ間に形成
されたV溝の外側に、可動プーリの背面に当接するよう
に複数枚の皿バネ素子が直列に立設され、各皿バネ素子
8の凹凸面が表裏背中合わせになるように交互に所定枚
数が配されている。この各二枚の隣接した素子間で形成
される空間には、皿バネの外周縁を縦断するような円形
状の反転阻止板9(反転阻止部材)が内包されている。
かかる反転阻止板9は、剛性の高い素材で略皿バネ径と
同径のものであり、各皿バネ阻止が有する荷重−変位特
性をそれぞれ分断するものである。即ち、相対面する一
対の皿ばねの一方が、所定応力値(荷重)によって他方
の皿バネ素子より早く密着点に達した場合にこれ以上の
変形を阻止し、他方の変形を継続するようにしたもので
ある。これによって、Vベルトの巻付け径が小さくなる
と、皿バネ素子は変形して平板に近づくが、当該反転阻
止板により密着点以降の変形を阻止して、反転すること
がない。以上の説明から明かなように、本発明の皿バネ
装置を無断変速機に用いた場合、低速回転から高速回転
に至るまで連続的に変速させるのに適応した複数の各皿
バネ素子が各々有する変形−応力特性を作動範囲中に拘
束し、これ以上の変形によって生ずる騒音を回避し、さ
らに作動範囲中に荷重のピークを有する皿ばねを無断変
速機に導入することができる。従って、従来の高速回転
時に顕著な伝達効率の低下を回避することができる。FIG. 3 shows an embodiment of the structure of a disc spring device 6 according to the present invention. A pair of fixed pulley 4 and movable pulley 5 mounted on a pulley shaft 7, and the movable pulley 5 is a pulley shaft. 7, a plurality of disc spring elements are erected in series outside the V groove formed between the pulleys so as to come into contact with the back surface of the movable pulley. A predetermined number of sheets are arranged alternately so that the front and back sides of the sheets are back to back. A circular reversal prevention plate 9 (reversal prevention member) that vertically cuts the outer peripheral edge of the disc spring is included in the space formed between the two adjacent elements.
The reversal prevention plate 9 is made of a highly rigid material and has a diameter substantially equal to the diameter of the disc spring, and separates the load-displacement characteristic of each disc spring prevention. That is, when one of the pair of disc springs facing each other reaches the contact point earlier than the other disc spring element by a predetermined stress value (load), further deformation is prevented and the other deformation is continued. It was done. As a result, when the winding diameter of the V-belt becomes smaller, the disc spring element deforms and approaches the flat plate, but the reversal prevention plate prevents deformation after the contact point and does not reverse. As is apparent from the above description, when the disc spring device of the present invention is used in an continuously variable transmission, each disc spring element adapted to continuously shift from low speed rotation to high speed rotation has a plurality of disc spring elements. It is possible to constrain the deformation-stress characteristics in the operating range, to avoid noise caused by further deformation, and to introduce a disc spring with a peak load in the operating range into the continuously variable transmission. Therefore, it is possible to avoid a significant decrease in transmission efficiency during conventional high-speed rotation.
【0013】[0013]
【発明の効果】本発明の皿バネ装置によれば、複数枚の
各皿バネ素子が各々有する荷重−変形特性を作動範囲中
に拘束し、これ以上の変形によって生ずる騒音を回避
し、さらに作動範囲中に応力(荷重)のピークを有する
皿バネを導入することができる。従って、作動範囲を広
く取ることができると共に作動範囲中に多様な荷重状態
を得ることができる。According to the Belleville spring device of the present invention, the load-deformation characteristics of a plurality of Belleville spring elements are constrained within the operating range to avoid noise caused by further deformation and to operate further. A Belleville spring having a peak of stress (load) in the range can be introduced. Therefore, the operating range can be widened and various load states can be obtained in the operating range.
【図1】本発明の皿バネ装置を用いた変速プーリ装置の
断面図である。FIG. 1 is a sectional view of a speed change pulley device using a disc spring device of the present invention.
【図2】皿バネ素子が有する荷重−変位曲線の説明図で
ある。FIG. 2 is an explanatory diagram of a load-displacement curve of a disc spring element.
【図3】本発明の皿バネ装置の説明図である。FIG. 3 is an explanatory view of a disc spring device of the present invention.
【図4】従来例の皿バネ装置を用いた変速プーリ装置の
概略説明図である。FIG. 4 is a schematic explanatory view of a speed change pulley device using a conventional disc spring device.
1 駆動源 2 V型ベルト 3 V型プーリ 4 固定プーリ 5 可動プーリ 6 皿バネ 7 プーリ軸 8 皿バネ素子 9 反転阻止板(反転阻止部材) 1 Drive Source 2 V-Type Belt 3 V-Type Pulley 4 Fixed Pulley 5 Movable Pulley 6 Disc Spring 7 Pulley Shaft 8 Disc Spring Element 9 Reversal Blocking Plate (Reversal Blocking Member)
Claims (1)
る皿バネ装置において、互に向い合って配置された皿バ
ネ素子間に、反転阻止部材を介在して構成したことを特
徴とする皿バネ装置。1. A Belleville spring device in which a plurality of Belleville spring elements are combined and used as an elastic source is characterized in that a reversal blocking member is interposed between the Belleville spring elements arranged to face each other. Disc spring device.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9326092A JPH05296270A (en) | 1992-04-14 | 1992-04-14 | Coned disc spring device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9326092A JPH05296270A (en) | 1992-04-14 | 1992-04-14 | Coned disc spring device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH05296270A true JPH05296270A (en) | 1993-11-09 |
Family
ID=14077521
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP9326092A Pending JPH05296270A (en) | 1992-04-14 | 1992-04-14 | Coned disc spring device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH05296270A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001165257A (en) * | 1999-11-08 | 2001-06-19 | Luk Lamellen & Kupplungsbau Gmbh | Conical disk type wrapping connector |
-
1992
- 1992-04-14 JP JP9326092A patent/JPH05296270A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001165257A (en) * | 1999-11-08 | 2001-06-19 | Luk Lamellen & Kupplungsbau Gmbh | Conical disk type wrapping connector |
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