JPS63219953A - Disc type continuously variable transmission - Google Patents
Disc type continuously variable transmissionInfo
- Publication number
- JPS63219953A JPS63219953A JP5441287A JP5441287A JPS63219953A JP S63219953 A JPS63219953 A JP S63219953A JP 5441287 A JP5441287 A JP 5441287A JP 5441287 A JP5441287 A JP 5441287A JP S63219953 A JPS63219953 A JP S63219953A
- Authority
- JP
- Japan
- Prior art keywords
- transmission
- disk
- disc
- ball
- continuously variable
- 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.)
- Granted
Links
Landscapes
- Friction Gearing (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、駆動軸に駆動部材を固定し、前記駆動部材側
のボスに伝動ディスクを軸芯方向に沿ってシフト可能に
遊嵌し、前記駆動部材と伝動ディスクとの間に自動調圧
用のボールカム機構と予備圧用のコイルスプリングを介
在させると共に、外周部に弾性材を有する従動ディスク
を伝動デイクの伝動面に圧接しながら伝動ディスクの径
方向に移動可能に構成してあるディスク式無段変速装置
に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention provides a method for fixing a drive member to a drive shaft, and loosely fitting a transmission disk to a boss on the drive member side so as to be shiftable along the axial direction. A ball cam mechanism for automatic pressure adjustment and a coil spring for pre-pressure are interposed between the driving member and the transmission disc, and a driven disc having an elastic material on the outer periphery is pressed against the transmission surface of the transmission disc while adjusting the diameter of the transmission disc. The present invention relates to a disc-type continuously variable transmission configured to be movable in a direction.
かかるディスク式無段変速装置に使われる自動調圧用の
ボールカム機構は、第５図に示すように、駆動部材（５
）の伝動ディスク側の面部に同心円上に形成した複数の
係合凹部（７）と、伝動ディスク（６）の駆動部材側の
面部に同心円上に形成した複数の係合凹部（８）を夫々
向い合わせとすると共に、それら両係合凹部（７） 、
（８）によって形成された空間にボール（９）を介在
させたものが一般的である。このボールカム機構（Ａ）
では、駆動軸（４）とトルクを駆動部材（５）の係合凹
部（７）からボール（９）、そして伝動ディスク（６）
の係合四部（８）へと伝動していく。従って、従動ディ
スク（２）を介して伝動ディスク（６）に大負荷が加わ
ると、駆動部材（５）と伝動ディスク（６）が相対回転
しようとしてトルク伝動を担っていたボール（９）を両
係合凹部（７） 、 （８）から押し出そうとする。そ
して、この押し出そうとする力をボール（９）によって
駆動部材（５）と伝動ディスククロ）とを離間させよう
とする力に変換し、伝動ディスク（６）を従動ディスク
（２）に強く圧接する。The ball cam mechanism for automatic pressure adjustment used in such a disc-type continuously variable transmission has a drive member (5) as shown in FIG.
), and a plurality of engaging recesses (8) formed concentrically on the surface of the transmission disk (6) on the drive member side. facing each other, and both engaging recesses (7),
Generally, a ball (9) is interposed in the space formed by (8). This ball cam mechanism (A)
Now, the drive shaft (4) and the torque are transferred from the engagement recess (7) of the drive member (5) to the ball (9) and then to the transmission disc (6).
The power is transmitted to the four engaging parts (8). Therefore, when a large load is applied to the transmission disk (6) via the driven disk (2), the driving member (5) and the transmission disk (6) try to rotate relative to each other, causing the ball (9) that is responsible for torque transmission to be rotated. It tries to push out from the engagement recesses (7) and (8). Then, the ball (9) converts this pushing force into a force that tries to separate the driving member (5) and the transmission disc (2), causing the transmission disc (6) to strongly push against the driven disc (2). Pressure contact.
又、ボールカム機構（Ａ） と共に備えられるコイル
スプリング（１０）は、ボールカム機構（Ａ）が作動し
ない程の小負荷しか従動ディスク（２）に加わっていな
い場合に、伝動ディスク（６）と従動ディスク（２）と
の圧接が不十分になってスリップを生じるのを抑えるた
め、最低限の圧接力を伝動ディスク（６）に与えておく
ためのものである。In addition, the coil spring (10) provided together with the ball cam mechanism (A) is designed to prevent the transmission disc (6) and the driven disc from operating when only a small load is applied to the driven disc (2), such that the ball cam mechanism (A) does not operate. This is to apply a minimum pressure contact force to the transmission disk (6) in order to prevent slippage due to insufficient pressure contact with the transmission disk (6).
ところで、上述したようなボールカム機構を備えたディ
スク式無段変速装置には、次のような問題点があった。By the way, the disc-type continuously variable transmission equipped with the ball cam mechanism as described above has the following problems.
即ち、従動ディスクに高い負荷が加わることによって駆
動部材と伝動ディスクとの離間が促進され、ボールが係
合凹部から限界近く押し出されると、従動ディスク側か
らの反力も高まり、ボールと係合凹部の傾斜面との圧接
力も著しく高まる。そして、ボールが微小に変形するこ
とも手伝ってボールと係合凹部の摩擦力が増大し、ボー
ル及び伝動ディスクがその位置に固定されて、小負荷に
なっても元に戻らなくなってしまうことがある。傾斜面
が緩いときには特にその傾向が強い。In other words, when a high load is applied to the driven disk, the separation between the driving member and the transmission disk is promoted, and when the ball is pushed out of the engagement recess to near its limit, the reaction force from the driven disk side also increases, causing the separation between the ball and the engagement recess. The contact force with the inclined surface also increases significantly. In addition, the slight deformation of the ball increases the frictional force between the ball and the engagement recess, and the ball and transmission disk are fixed in that position, preventing them from returning to their original positions even under a small load. be. This tendency is particularly strong when the slope is gentle.
本発明は、このような実情に着目し、大負荷から小負荷
になる際に発生する伝動ディスクの戻り不良を解消し、
自動調圧用のボールカム機構が良好に作動できるように
することを目的としている。The present invention focuses on this situation and solves the failure of the transmission disk to return, which occurs when the load changes from a large load to a small load.
The purpose is to enable the ball cam mechanism for automatic pressure regulation to operate well.
本発明の特徴構成は、コイルスプリングの一端を駆動部
材に係止すると共に、他端を伝動ディスクに係止してあ
る点にあり、その作用・効果は次の通りである。A characteristic feature of the present invention is that one end of the coil spring is locked to a driving member, and the other end is locked to a transmission disk, and the functions and effects thereof are as follows.
つまり、駆動部材の係合凹部と従動ディスクの係合凹部
とか完全に向き合うボールカム機構の初期状態において
、予備圧用のコイルスプリングの一端を駆動部材に係止
し、他端を伝動ディスクに係止してお（ことによって、
大負荷時に駆動部材と伝動ディスクが相対回転するとそ
の回転量に応じてコイルスプリングの弾性復元力が増大
する。そして、大負荷が小負荷になる場合、例えば高速
から低速に変速操作した場合にコイルスプリングの弾性
復元力は、駆動部材と伝動ディスクを逆向きに相対回転
させてボールカム機構を初期状態に戻す力の一部として
、或いは固定されてしまったボール及び伝動ディスクが
動き出すきっかけを与えてやる力として放出されるので
ある。In other words, in the initial state of the ball cam mechanism where the engagement recess of the drive member and the engagement recess of the driven disk completely face each other, one end of the pre-pressure coil spring is engaged with the drive member and the other end is engaged with the transmission disc. (possibly)
When the drive member and the transmission disk rotate relative to each other under heavy load, the elastic restoring force of the coil spring increases in accordance with the amount of rotation. When a large load becomes a small load, for example when changing speed from high speed to low speed, the elastic restoring force of the coil spring is the force that causes the drive member and the transmission disk to rotate relative to each other in opposite directions, returning the ball cam mechanism to its initial state. It is released as part of the force, or as a force that triggers the fixed ball and transmission disk to start moving.
その結果、大負荷から小負荷になる際に発生する伝動デ
ィスクの戻り不良を極力少なくしてボールカム機構を良
好に作動させ、ディスク式無段変速装置の性能を高める
ことが、可能になった。As a result, it has become possible to minimize the return failure of the transmission disk that occurs when the load changes from a large load to a small load, to allow the ball cam mechanism to operate well, and to improve the performance of the disk type continuously variable transmission.
以下、本発明の実施例を図面に基づいて説明する。 Embodiments of the present invention will be described below based on the drawings.
第１図に歩行型芝刈機に装備されるディスク式無段変速
装置が示されている。FIG. 1 shows a disc-type continuously variable transmission device that is installed on a walk-behind lawn mower.
この無段変速装置は、外周部に弾性体（１）を付設した
従動ディスク（２）と弾性体（１）に伝動面（３ａ）を
圧接させである駆動用の原動ディスク（３）とからなり
、前記従動ディスク（２）を圧接状態のまま原動ディス
ク（３）を半径方向に移動させることで原動ディスク（
３）の回転動力を無段階変速して従動ディスク（２）に
伝達できるようになっている。This continuously variable transmission consists of a driven disk (2) with an elastic body (1) attached to its outer periphery and a drive disk (3) with a transmission surface (3a) pressed against the elastic body (1). By moving the driving disk (3) in the radial direction while keeping the driven disk (2) in pressure contact, the driving disk (
3) can be transmitted to the driven disk (2) in a stepless manner.
前記原動ディスク（３）は、駆動軸（４）に位置固定さ
れた駆動ディスク（５）とこれに相対回動及び軸芯（Ｐ
）方向へ摺動自在に外嵌された伝動ディスク（６）とか
らなり、それら両ディスク（５）。The driving disk (3) includes a driving disk (5) which is fixed in position to a driving shaft (4), and a driving disk (5) that rotates relative to this and an axis (P).
), and a transmission disk (6) fitted on the outside so as to be slidable in the direction ), and both disks (5).
（６）の間には、伝動ディスク（６）に負荷が加わると
伝動ディスク（６）を自動的に従動ディスク（２）側へ
摺動させる自動調圧用のボールカム機構（Ａ）を介在さ
せである。(6) is interposed with a ball cam mechanism (A) for automatic pressure adjustment that automatically slides the transmission disc (6) toward the driven disc (2) when a load is applied to the transmission disc (6). be.
前記ボールカム機構（Ａ）は、第２図に示すように駆動
ディスク（５）の伝動ディスク（６）側の対向面に同心
円上に形成された複数の係合凹部（７）と、伝動ディス
ク（６）の駆動ディスク（５）側の対向面に同心円上に
形成された複数の係合凹部（８）との間にトルク伝動用
のボール（９）を介在させてなるものであり、駆動ディ
スク（５）が駆動された状態において従動ディスク（２
）に負荷が加わると、伝動ディスク（６）を摺動させて
その伝動面（３ａ）を従動ディスク（２）の弾性体（１
）に圧接する作用をする。即ち、従動ディスク（２）に
負荷が加わると駆動ディスク（５）と伝動ディスク（６
）とが相対回転しようとし、夫々の対向面に形成した保
合凹部（７） 、 （８）が周方向にずれてくる（第３
図参照）。その時、ボール（９）を転勤させて係合凹部
（７）−、（８）から押し出そうとし、その力が伝動デ
ィスク（６）を従動ディスク（２）側へ軸芯方向に摺動
させる力として作用するのである。それ故、負荷の増大
に比例して弾性体（１）への圧接力も強まることになる
。As shown in FIG. 2, the ball cam mechanism (A) includes a plurality of engagement recesses (7) concentrically formed on the opposing surface of the drive disk (5) on the transmission disk (6) side, and a transmission disk (6). A ball (9) for torque transmission is interposed between a plurality of engaging recesses (8) formed concentrically on the opposing surface of the drive disk (5) of the drive disk (6). (5) is driven, the driven disk (2
), the transmission disk (6) slides and its transmission surface (3a) is pressed against the elastic body (1) of the driven disk (2).
). That is, when a load is applied to the driven disk (2), the driving disk (5) and the transmission disk (6)
) tend to rotate relative to each other, and the retaining recesses (7) and (8) formed on the respective opposing surfaces become displaced in the circumferential direction (the third
(see figure). At that time, the ball (9) is transferred and tries to be pushed out from the engagement recesses (7)-, (8), and the force causes the transmission disc (6) to slide in the axial direction toward the driven disc (2). It acts as a force. Therefore, the pressure applied to the elastic body (1) increases in proportion to the increase in load.
前記駆動ディスク（５）と伝動ディスク（６）との間に
は、伝動ディスク（６）のボス（６ａ）に巻き付く格好
で第４図に示すようなコイルスプリング（１０）を介装
して伝動ディスク（６）に予備圧を付与してある。それ
により、ボールカム機構（八）の作動しない駆動開始時
及び小負荷時に伝動ディスク（６）の伝動面（３ａ）を
弾性体（１）に圧接して伝動に必要な摩擦力を得る。A coil spring (10) as shown in FIG. 4 is interposed between the drive disk (5) and the transmission disk (6) so as to wrap around the boss (6a) of the transmission disk (6). Pre-pressure is applied to the transmission disc (6). As a result, the transmission surface (3a) of the transmission disk (6) is brought into pressure contact with the elastic body (1) at the start of driving when the ball cam mechanism (8) does not operate, and when the load is small, thereby obtaining the frictional force necessary for transmission.
前記コイルスプリング（１０）の一端は、駆動ディスク
（５）に穿設した孔（５ｂ）に差込み固定してあり、他
端は伝動ディスク（６）に穿設した孔（６ｂ）に差込み
固定してある。そのため、従動ディスク（２）に負荷が
加わって駆動ディスク（５）と伝動ディスク（６）とが
相対回転し、コイルスプリング（１０）が１戻られて弾
性エネルギーが蓄積される。One end of the coil spring (10) is inserted and fixed into a hole (5b) drilled in the drive disk (5), and the other end is inserted and fixed into a hole (6b) drilled in the transmission disk (6). There is. Therefore, a load is applied to the driven disk (2), the driving disk (5) and the transmission disk (6) rotate relative to each other, the coil spring (10) is returned by 1, and elastic energy is accumulated.
そして、この蓄積された弾性エネルギーは、駆動ディス
ク（５）と従動ディスク（２）とを反対方向に相対回転
させてボールカム機構（Ａ）を初期状態に復元する力と
なる。又、第３図に示したように、大負荷が加わること
によってボール（９）と係合凹部（７） 、 （８）の
傾斜面との圧接力も著しく高まり、そして、ボール（９
）が微小に変形することも手伝ってボール（９）と係合
凹部（７） 、 （８）の摩擦力が増大した場合、ボー
ル（９）と駆動ディスク（５）及び伝動ディスク（６）
が固定されて小負荷になっても戻らなくなることが従来
から多かったが、当該ディスク式無段変速装置ではコイ
ルスプリング（１０）による弾性復元力が作用するため
にそのような伝動ディスク（６）の戻り不良が極めて少
なく、ボールカム機構（Ａ）を良好に作動させることが
できるのである。This accumulated elastic energy becomes a force that causes the driving disk (5) and the driven disk (2) to rotate relative to each other in opposite directions, thereby restoring the ball cam mechanism (A) to its initial state. Further, as shown in Fig. 3, when a large load is applied, the pressure contact force between the ball (9) and the inclined surfaces of the engaging recesses (7) and (8) increases significantly, and the ball (9)
) when the frictional force between the ball (9) and the engaging recesses (7) and (8) increases due to the slight deformation of the ball (9), the drive disk (5), and the transmission disk (6).
Conventionally, it has often been the case that the transmission disc (6) is fixed and does not return even under a small load, but in the disc type continuously variable transmission, the elastic restoring force of the coil spring (10) acts, so the transmission disc (6) There are extremely few return failures, and the ball cam mechanism (A) can be operated satisfactorily.
尚、特許請求の範囲の項に図面との対照を便利にする為
に符号を記すが、該記入により本発明は添付図面の構造
に限定されるものではない。Incidentally, although reference numerals are written in the claims section for convenient comparison with the drawings, the present invention is not limited to the structure shown in the accompanying drawings.
図面は本発明に係るディスク式無段変速装置の実施例を
示し、第１図は縦断面図、第２図はボールカム機構の初
期状態における周方向の断面図、第３図はボールカム機
構の大負荷状態における周方向の断面図、第４図はコイ
ルスプリングの斜視図であり、第５図は従来の縦断面図
である。
（１）・・・・・・弾性材、（２）・・・・・・従動デ
ィスク、（３ａ）・・・・・・伝動面、（４）・・・・
・・駆動軸、（５）・・・・・・駆動部材、（６）・・
・・・・伝動ディスク、（ｆＯ）・・・・・・コイルス
プリング、（八）・・・・・・ボールカム機構、（Ｐ）
・・・・・・軸芯。The drawings show an embodiment of the disc-type continuously variable transmission according to the present invention, in which Fig. 1 is a longitudinal sectional view, Fig. 2 is a circumferential sectional view of the ball cam mechanism in its initial state, and Fig. 3 is a general view of the ball cam mechanism. 4 is a perspective view of a coil spring in a loaded state, and FIG. 5 is a longitudinal sectional view of a conventional coil spring. (1)...Elastic material, (2)...Driver disk, (3a)...Transmission surface, (4)...
... Drive shaft, (5) ... Drive member, (6) ...
...Transmission disk, (fO) ...Coil spring, (8) ...Ball cam mechanism, (P)
・・・・・・Axis core.
Claims (1)
（５）側のボスに伝動ディスク（６）を軸芯（Ｐ）方向
に沿ってシフト可能に遊嵌し、前記駆動部材（５）と伝
動ディスク（６）との間に自動調圧用のボールカム機構
（Ａ）と予備圧用のコイルスプリング（１０）を介在さ
せると共に、外周部に弾性材（１）を有する従動ディス
ク（２）を伝動デイク（６）の伝動面（３ａ）に圧接し
ながら伝動ディスク（６）の径方向に移動可能に構成し
てあるディスク式無段変速装置であって、前記コイルス
プリング（１０）の一端を駆動部材（５）に係止すると
共に、他端を伝動ディスク（６）に係止してあるディス
ク式無段変速装置。A drive member (5) is fixed to the drive shaft (4), a transmission disk (6) is loosely fitted into the boss on the drive member (5) side so as to be shiftable along the axis (P) direction, and the drive member (5) is fixed to the drive shaft (4). A ball cam mechanism (A) for automatic pressure adjustment and a coil spring (10) for preliminary pressure are interposed between the drive disk (5) and the transmission disk (6), and the driven disk (2) has an elastic material (1) on the outer periphery. ) is configured to be movable in the radial direction of the transmission disc (6) while being in pressure contact with the transmission surface (3a) of the transmission disc (6), the coil spring (10) A disc-type continuously variable transmission device whose one end is locked to a drive member (5) and the other end is locked to a transmission disk (6).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5441287A JPS63219953A (en) | 1987-03-10 | 1987-03-10 | Disc type continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5441287A JPS63219953A (en) | 1987-03-10 | 1987-03-10 | Disc type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63219953A true JPS63219953A (en) | 1988-09-13 |
| JPH0527770B2 JPH0527770B2 (en) | 1993-04-22 |
Family
ID=12969986
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5441287A Granted JPS63219953A (en) | 1987-03-10 | 1987-03-10 | Disc type continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63219953A (en) |
Cited By (41)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008516165A (en) * | 2004-10-05 | 2008-05-15 | フォールブルック テクノロジーズ インコーポレイテッド | Continuously variable transmission |
| WO2008057507A1 (en) * | 2006-11-08 | 2008-05-15 | Fallbrook Technologies Inc. | Clamping force generator |
| US7419451B2 (en) | 1997-09-02 | 2008-09-02 | Fallbrook Technologies Inc. | Continuously variable transmission |
| US7422546B2 (en) | 2003-08-11 | 2008-09-09 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
| US7455617B2 (en) | 2004-07-21 | 2008-11-25 | Fallbrook Technologies Inc. | Rolling traction planetary drive |
| US7462127B2 (en) | 2001-04-26 | 2008-12-09 | Fallbrook Technologies Inc. | Continuously variable transmission |
| US7600771B2 (en) | 2006-05-11 | 2009-10-13 | Catadon Systems Llc | Continuously variable drivetrain |
| US7632203B2 (en) | 2005-10-28 | 2009-12-15 | Fallbrook Technologies Inc. | Electromotive drives |
| USRE41892E1 (en) | 1997-09-02 | 2010-10-26 | Fallbrook Technologies Inc. | Continuously variable transmission |
| EP1963713A4 (en) * | 2005-12-09 | 2012-01-04 | Fallbrook Technologies Inc | VARIATION TRANSMISSION CONTINUES |
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| US8845485B2 (en) | 2011-04-04 | 2014-09-30 | Fallbrook Intellectual Property Company Llc | Auxiliary power unit having a continuously variable transmission |
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-
1987
- 1987-03-10 JP JP5441287A patent/JPS63219953A/en active Granted
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| Publication number | Publication date |
|---|---|
| JPH0527770B2 (en) | 1993-04-22 |
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