JPH0684027U - Torque limiter - Google Patents
Torque limiterInfo
- Publication number
- JPH0684027U JPH0684027U JP3111993U JP3111993U JPH0684027U JP H0684027 U JPH0684027 U JP H0684027U JP 3111993 U JP3111993 U JP 3111993U JP 3111993 U JP3111993 U JP 3111993U JP H0684027 U JPH0684027 U JP H0684027U
- Authority
- JP
- Japan
- Prior art keywords
- drive shaft
- driven member
- cam
- clutch
- clutch disc
- 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
Landscapes
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
(57)【要約】
【目的】 安価でかつ高い加工精度を必要としないクラ
ッチディスクを使用でき、しかも長期にわたってトルク
リミッタの高い信頼性を確保する。
【構成】 駆動軸と被駆動部材との間に設けるカム機構
を、第１、第２の凹状カム面間にカムボールを遊嵌して
構成し、駆動軸と被駆動部材との間の所定以上の過剰の
回転力又は回転抵抗力をカム機構で軸線方向の変位に変
換し、ばね部材のクラッチディスクに対する付勢を遮断
し又は減少させる一方、少なくとも一方のクラッチディ
スクの摩擦面にはＭｏＳ2 及びグラファイトを主成分と
しエポキシ系バインダーを使用してなる表面安定化層を
１０〜２０μｍの厚みで形成した。
(57) [Summary] [Purpose] An inexpensive clutch disk that does not require high processing accuracy can be used, and high reliability of the torque limiter is ensured for a long period of time. A cam mechanism provided between the drive shaft and the driven member is configured by loosely fitting a cam ball between the first and second concave cam surfaces, and a predetermined or more distance between the drive shaft and the driven member is provided. Excessive rotational force or rotational resistance force of the cam mechanism is converted into an axial displacement to block or reduce the bias of the spring member to the clutch disc, while at least one clutch disc friction surface has MoS 2 and A surface stabilizing layer containing graphite as a main component and an epoxy binder was formed to a thickness of 10 to 20 μm.
Description
【０００１】[0001]
この考案は、トルクリミッタに関し、特に駆動軸から被駆動部材に長期にわた って応答性よく高精度に所定のトルクを伝達できるようにしたトルクリミッタに 関する。 The present invention relates to a torque limiter, and more particularly to a torque limiter capable of accurately transmitting a predetermined torque from a drive shaft to a driven member over a long period of time with high responsiveness.
【０００２】[0002]
各種駆動系においては、クラッチディスクをばね部材で付勢してなるトルクリ ミッタを採用し、駆動側又は被駆動側の負荷が増大した時に過大負荷の伝達を制 限することがよく行われている。 In various drive systems, a torque limiter in which a clutch disk is biased by a spring member is used to often limit the transmission of excessive load when the load on the drive side or the driven side increases. .
【０００３】 例えば、負荷増大時にクラッチディスク面をばね部材の付勢力に抗して相互 に滑らせる方式、駆動側と被駆動側との間に、相互に係合しうるカム凹部とカ ム凸部とからなるカム機構を設け、過大な負荷の作用時に、カム凹部とカム凸部 とを接触面で相互にスライドさせてクラッチディスクを切断するようにした方式 （特開平２−１５０５１７号公報等参照）、が知られている。For example, when the load increases, the clutch disk surface slides against each other against the biasing force of the spring member, and the cam concave portion and the cam convex portion that can be engaged with each other are provided between the driving side and the driven side. And a cam mechanism configured to disengage the clutch disc by sliding the cam concave portion and the cam convex portion on the contact surface with each other when an excessive load is applied (Japanese Patent Laid-Open No. 2-150517, etc.). (See), is known.
【０００４】[0004]
しかし、前者の方式では、クラッチ機構の滑り始めの負荷の大きさがばね部 材の付勢力とクラッチディスクの摩擦面の固有物的特性や加工状態とによって決 まるために、組付精度等に起因してクラッチディスクの滑り開始にバラツキが生 じ、又長時間使用すれば設定値が大幅に変化するばかりでなく、静摩擦特性と動 摩擦特性とに大きくバラツキが生じ、経時変化が顕著で、信頼性が低いという問 題があった。 However, in the former method, the magnitude of the load at the beginning of slippage of the clutch mechanism is determined by the biasing force of the spring material and the inherent physical properties and working conditions of the friction surface of the clutch disc, so that the assembling accuracy, etc. As a result, there is variation in the start of slippage of the clutch disc, and not only the set value changes significantly when used for a long time, but also the static friction characteristics and dynamic friction characteristics greatly vary, and changes over time are significant. There was a problem of low reliability.
【０００５】 また、後者の方式では、クラッチディスクの切断開始トルクがカム凹部とカ ム凸部の接触面の表面性状や傾斜角度のバラツキによって大きく変動し、これを 精度よく制御するためには極めて高精度な加工を必要としていた。Further, in the latter method, the disengagement start torque of the clutch disc fluctuates greatly due to the surface texture of the contact surface between the cam concave portion and the cam convex portion and the variation in the inclination angle, and it is extremely necessary to control this with high accuracy. It required high-precision processing.
【０００６】 この考案は、かかる問題点に鑑み、高い加工精度を必要としない安価なクラッ チディスクを使用でき、しかも長期にわたって高い信頼性を有するトルクリミッ タを提供することを課題とする。In view of such problems, it is an object of the present invention to provide a torque limiter that can use an inexpensive clutch disk that does not require high processing accuracy and that has high reliability for a long period of time.
【０００７】[0007]
そこで本考案に係るトルクリミッタは、少なくとも一対のクラッチディスクが ばね部材によって軸線方向に付勢されて駆動軸と被駆動部材とが切断可能に接続 されており、上記駆動軸と被駆動部材との間には第１、第２の凹状カム面間にカ ムボールを遊嵌して構成されたカム機構が設けられ、上記駆動軸と被駆動部材と の間の所定以上の過剰の回転力又は回転抵抗力が上記カム機構で軸線方向の変位 に変換され、該変位によって上記ばね部材のクラッチディスクに対する付勢が遮 断又は減少可能である一方、少なくとも一方の上記クラッチディスクの摩擦面に はＭｏＳ2 及びグラファイトを主成分としエポキシ系バインダーを使用してなる 表面安定化層が１０〜２０μｍの厚みで形成されていることを特徴とする。Therefore, in the torque limiter according to the present invention, at least a pair of clutch discs are axially urged by spring members to disconnectably connect the drive shaft and the driven member, and the drive shaft and the driven member are connected to each other. A cam mechanism formed by loosely fitting a cam ball between the first and second concave cam surfaces is provided therebetween, and an excessive rotational force or rotation more than a predetermined value between the drive shaft and the driven member is provided. The resistance force is converted into an axial displacement by the cam mechanism, and the displacement can block or reduce the bias of the spring member against the clutch disc, while at least one of the friction faces of the clutch disc has MoS 2 And a surface stabilizing layer containing graphite as a main component and using an epoxy binder with a thickness of 10 to 20 μm.
【０００８】[0008]
駆動軸と被駆動部材との間の回転力又は回転抵抗値が所定値を越えると、その 回転力又は回転抵抗力がカム機構によって軸線方向の変位に変換され、クラッチ ディスクの接続力が減少され、あるいはクラッチディスクが切断される。他方、 カム機構に伝達される回転力又は回転抵抗力も低下し、軸線方向の変位が減少し 、ばね部材の付勢力が元に戻ってクラッチディスクが再び接続され、かかる動作 が連続的に繰り返して自動的に行われ、駆動軸と被駆動部材との間には一定のト ルクが伝達される。 When the rotational force or rotational resistance value between the drive shaft and driven member exceeds a predetermined value, the rotational force or rotational resistance force is converted into axial displacement by the cam mechanism, and the clutch disc connection force is reduced. , Or the clutch disc is disconnected. On the other hand, the rotational force or rotational resistance force transmitted to the cam mechanism is also reduced, the axial displacement is reduced, the biasing force of the spring member is restored, the clutch disc is reconnected, and this operation is repeated continuously. This is done automatically and a constant torque is transmitted between the drive shaft and the driven member.
【０００９】 その際、カム機構において、カムボールが第１、第２の凹状カム面と線接触し 、かつ第１、第２の凹状カム面が相対変位する際に第１、第２の凹状カム面間で 回転するので、従来のカム凹部とカム凸部とが面接触する場合に比して表面性状 の影響は少ない。また、第１の凹状カム面及び第２の凹状カム面がカムボールの 表面に対してそれぞれ一定の角度で接触しつつ相対変位するので、従来のカム凹 部とカム凸部が面接触してスライドする場合に比し、第１、第２の凹状カム面の 傾斜角度のバラツキがクラッチ機構の切断開始トルクに与える影響も少ない。そ の結果、切断開始時のトルクが部品の寸法精度や組付精度、クラッチディスクの 物的特性に影響されるのを低減できる。At that time, in the cam mechanism, when the cam ball is in line contact with the first and second concave cam surfaces and the first and second concave cam surfaces are relatively displaced, the first and second concave cam surfaces are moved. Since it rotates between the surfaces, the surface texture has less influence than the conventional case where the cam concave portion and the cam convex portion are in surface contact. Further, since the first concave cam surface and the second concave cam surface are displaced relative to the surface of the cam ball while being in contact with each other at a constant angle, the conventional cam concave portion and the cam convex portion are in surface contact and slide. Compared with the case of the above, the influence of the variation in the inclination angle of the first and second concave cam surfaces on the disengagement start torque of the clutch mechanism is less. As a result, it is possible to reduce the influence of the torque at the start of cutting on the dimensional accuracy and assembly accuracy of parts and the physical properties of the clutch disc.
【００１０】 しかも、クラッチディスクの摩擦面にはＭｏＳ2 及びグラファイトを主成分と しエポキシ系バインダーを使用してなる表面安定化層が形成されていることから 、摩擦面の固有物的特性が加工状態の影響を受けず、表面安定化層の自己潤滑性 とも相まって長期にわたって安定し、加工精度の悪い安価なクラッチディスクを 使用しても信頼性を大幅に向上できる。Moreover, since the friction stabilizing surface of the clutch disc is formed with the surface stabilizing layer containing MoS 2 and graphite as the main components and using the epoxy binder, the inherent characteristics of the friction surface are processed. It is not affected by the condition and is stable for a long period of time in combination with the self-lubricating property of the surface stabilization layer. Even if an inexpensive clutch disc with poor processing accuracy is used, the reliability can be greatly improved.
【００１１】 ここに、表面安定化層を１０〜２０μｍとしたのは、１０μｍ未満では実作業 上、摩擦面の全面に表面安定化層を均一に形成することが難しくなる一方、２０ μｍを越えると厚みの割に性能をアップできないばかりでなく、クラッチディス クの厚みや材質等の特性を変更する必要が生じる、等の不具合が招来されるから である。The reason why the surface stabilizing layer is set to 10 to 20 μm is that when it is less than 10 μm, it is difficult to form the surface stabilizing layer uniformly on the entire surface of the friction surface, but it exceeds 20 μm. This is because not only the performance cannot be improved for the thickness, but also the characteristics such as the thickness and material of the clutch disk need to be changed, which causes problems.
【００１２】[0012]
以下、本考案を図面に示す具体例に基づいて詳細に説明する。図１及び図２は 本考案の実施例によるトルクリミッタを示す。図において、１は動力源モータの 回転軸（図示せず）が取付けられる駆動軸で、該駆動軸１の先端部には小径軸部 １０が一体に形成され、該小径軸部１０の基部側には円周上の１２０°毎に扇状 係止部１１が一体に形成され、該扇状係止部１１の先端面には円錐凹状のボール 穴１６が形成され、又小径軸部１０の先端側にはねじ１２が設けられている。 Hereinafter, the present invention will be described in detail based on specific examples shown in the drawings. 1 and 2 show a torque limiter according to an embodiment of the present invention. In the figure, reference numeral 1 denotes a drive shaft to which a rotary shaft (not shown) of a power source motor is attached, and a small diameter shaft portion 10 is integrally formed at a tip end portion of the drive shaft 1, and a base side of the small diameter shaft portion 10 A fan-shaped engaging portion 11 is integrally formed at every 120 ° on the circumference, and a conical concave ball hole 16 is formed in the tip surface of the fan-shaped engaging portion 11, and the tip side of the small diameter shaft portion 10 is formed. Is provided with a screw 12.
【００１３】 上記駆動軸１の小径軸部１０の外周にはスリーブ２が設けられ、該スリーブ２ の中央には小径軸部１０がスライド自在に挿通しうる貫通孔２０が軸方向に穿設 され、スリーブ２は駆動軸１の小径軸部１０に対して軸線方向にスライド自在に かつ回転自在となっている。このスリーブ２の外周面には円周上の１２０°毎に 扇状係止部２１が形成され、又スリーブ２の先端面には円錐台状の凹部２２が駆 動軸小径軸部１０のボール穴１６に対向して同位置に形成され、該各凹部２２と ボール穴１６とで構成される空間にはカムボール３０が介在され、こうしてカム 機構３が構成されている。A sleeve 2 is provided on the outer periphery of the small-diameter shaft portion 10 of the drive shaft 1, and a through hole 20 is formed in the center of the sleeve 2 so that the small-diameter shaft portion 10 can be slidably inserted in the axial direction. The sleeve 2 is slidable and rotatable in the axial direction with respect to the small diameter shaft portion 10 of the drive shaft 1. A fan-shaped engaging portion 21 is formed on the outer peripheral surface of the sleeve 2 at intervals of 120 ° on the circumference, and a conical recess 22 is formed on the tip end surface of the sleeve 2 in a ball hole of the driving shaft small diameter shaft portion 10. A cam ball 30 is interposed in the space formed by the recesses 22 and the ball hole 16 facing each other at the same position as the cam mechanism 3, thus constituting the cam mechanism 3.
【００１４】 上記スリーブ２の外周面には複数のインナーディスク４０が設けられ、該イン ナーディスク４０の中央には上記スリーブ２及び扇状係止部２１がスライド自在 に貫通しうる形状の貫通孔が形成され、これによってインナーディスク４０はス リーブ２に対して軸線方向にスライド自在でかつ回転不能となっている。A plurality of inner discs 40 are provided on the outer peripheral surface of the sleeve 2, and a through hole having a shape through which the sleeve 2 and the fan-shaped engaging portion 21 can slidably pass is provided at the center of the inner disc 40. As a result, the inner disc 40 is slidable in the axial direction with respect to the sleeve 2 and is not rotatable.
【００１５】 また、上記駆動軸小径軸部１０の外側には円筒状の被駆動部材５が外装されて 駆動軸１の段部と当接することによって位置決めされ、該被駆動部材５の内面に は複数のアウターディスク４２がインナーディスク４０と対面しかつ交互に配設 され、該アウターディスク４２は被駆動部材５の内面にスプライン係合されて回 転不能になっており、インナー及びアウターの両ディスク４０、４２によって駆 動軸１と被駆動部材５とを軸線方向に接続し切断するクラッチ機構４が構成され ている。A cylindrical driven member 5 is externally mounted on the outer side of the drive shaft small-diameter shaft portion 10 and positioned by abutting against the step portion of the drive shaft 1, and the inner surface of the driven member 5 is positioned. A plurality of outer discs 42 face the inner discs 40 and are alternately arranged. The outer discs 42 are spline-engaged with the inner surface of the driven member 5 so that they cannot rotate. A clutch mechanism 4 for connecting and disconnecting the drive shaft 1 and the driven member 5 in the axial direction is constituted by 40 and 42.
【００１６】 このクラッチ機構４において、各アウターディスク４２の摩擦面にはＭｏＳ2 及びグラファイトを主成分としエポキシ系バインダーを使用してなる表面安定化 層８が１０〜２０μｍの厚みで均一に塗布され形成されている。表面安定化層８ の配合は例えばＭｏＳ2 及びグラファイトの両組成で４０〜６０ｗｔ％とし、残 部をエポキシ系バインダーとするのがよい。In the clutch mechanism 4, a surface stabilizing layer 8 containing MoS 2 and graphite as a main component and using an epoxy binder is uniformly applied to the friction surface of each outer disk 42 in a thickness of 10 to 20 μm. Has been formed. The composition of the surface stabilizing layer 8 is preferably, for example, 40 to 60 wt% for both compositions of MoS 2 and graphite, and the balance is an epoxy binder.
【００１７】 また、上記駆動軸小径軸部１０の外周面には座板６がスライド自在に外装され 、該座板６の背後には座金７１が配設され、該座金７１と座板６との間には円周 上の１２０°毎にばね部材７が３つ介設され、又座板６とスリーブ２との間には 所定の間隙６０が設定されている。また、上記駆動軸１のねじ部１２にはナット ７２が螺合され、該ナット７２を回転させることによってばね部材７の付勢力を 調整できるようになっている。A seat plate 6 is slidably mounted on the outer peripheral surface of the drive shaft small-diameter shaft portion 10, and a washer 71 is disposed behind the seat plate 6, and the washer 71 and the seat plate 6 are provided. Three spring members 7 are provided at intervals of 120 ° on the circumference between them, and a predetermined gap 60 is set between the seat plate 6 and the sleeve 2. A nut 72 is screwed into the threaded portion 12 of the drive shaft 1, and the biasing force of the spring member 7 can be adjusted by rotating the nut 72.
【００１８】 次に動作について説明する。被駆動部材５側の負荷、即ち回転抵抗の小さい通 常時においては、カム機構３のボール穴１６と凹部２２との間には大きな位置ず れは発生せず、ボール３０がスリーブ２の凹部２２内周面に大きく乗り上げず、 スリーブ２は座板６との間隙６０をスライドする程度であって座板６は後退しな い。ばね部材７は座板６を介してクラッチディスク４０、４２を軸線方向に付勢 し、その摩擦面は相互に接続状態に保持され、かかる状態では駆動軸１の回転は カム機構３、スリーブ２、クラッチ板４０、４２を経て被駆動部材５に伝達され る。Next, the operation will be described. When the load on the driven member 5 side is small, that is, when the rotational resistance is small, a large displacement does not occur between the ball hole 16 of the cam mechanism 3 and the recess 22. The sleeve 2 does not ride on the inner peripheral surface largely, and the sleeve 2 slides in the gap 60 between the seat plate 6 and the seat plate 6 does not retreat. The spring member 7 urges the clutch discs 40, 42 in the axial direction via the seat plate 6, and the friction surfaces thereof are held in a mutually connected state. In such a state, the rotation of the drive shaft 1 is caused by the cam mechanism 3 and the sleeve 2. Is transmitted to the driven member 5 via the clutch plates 40 and 42.
【００１９】 被駆動部材５の抵抗が増大し、又は被駆動部材５がロックされて負荷が増大し 、駆動軸１の回転抵抗力が増大すると、カム機構３においてはスリーブ２の凹部 ２２と駆動軸１のボール穴１６との間に大きな位置ずれが発生し、ボール３０が スリーブ２の凹部２２内周面に大きく乗り上げてスリーブ２が座板６の間隙６０ 以上にスライドされ、座板６がばね部材７の付勢力に抗して後退されてばね部材 ７の付勢が減少又は遮断され、これによってクラッチディスク４０、４２、従っ て駆動軸１と被駆動部材５の接続が切断される。When the resistance of the driven member 5 increases or the driven member 5 is locked to increase the load and the rotational resistance force of the drive shaft 1 increases, the cam mechanism 3 drives the concave portion 22 of the sleeve 2 and the driving force. A large misalignment occurs between the shaft 1 and the ball hole 16, the ball 30 largely rides on the inner peripheral surface of the recess 22 of the sleeve 2, and the sleeve 2 is slid over the gap 60 of the seat plate 6, so that the seat plate 6 moves. The spring member 7 is retracted against the biasing force of the spring member 7 so that the biasing force of the spring member 7 is reduced or cut off, whereby the clutch discs 40, 42, and thus the drive shaft 1 and the driven member 5 are disconnected.
【００２０】 駆動軸１と被駆動部材５とが切断されると、駆動軸１の回転抵抗力が減少し、 カム機構３の凹部２２とボール穴１６との位置ずれが小さくなってボール３０が スリーブ２の凹部２２内に復帰し、座板６はばね部材７の付勢力によって前進し てクラッチ板４０、４２を接続し、駆動軸１と被駆動部材５とが接続される。こ うしてクラッチ機構３が切断・接続を繰り返し、駆動軸１から被駆動部材５に一 定のトルクが円滑に伝達され、又ばね部材７の設定値に追随した伝達トルクが高 精度に得られ、しかも可変設定可能である。When the drive shaft 1 and the driven member 5 are disconnected, the rotational resistance force of the drive shaft 1 is reduced, the positional deviation between the recess 22 of the cam mechanism 3 and the ball hole 16 is reduced, and the ball 30 is removed. After returning to the inside of the recess 22 of the sleeve 2, the seat plate 6 is advanced by the urging force of the spring member 7 to connect the clutch plates 40 and 42, and the drive shaft 1 and the driven member 5 are connected. Thus, the clutch mechanism 3 repeats disconnection and connection, a certain torque is smoothly transmitted from the drive shaft 1 to the driven member 5, and a transmission torque that follows the set value of the spring member 7 is obtained with high accuracy. Moreover, it can be variably set.
【００２１】 また、何らかの原因で駆動モータ側の回転トルクが異常に増大した場合にも上 記と同様に、ボール３０がスリーブ２の凹部２２内周面に大きく乗り上げてスリ ーブ２が座板６の間隙６０以上にスライドされてクラッチディスク４０、４２が 切り離され、駆動軸１と被駆動部材５との接続が切断される。Also, when the rotational torque on the drive motor side abnormally increases for some reason, the ball 30 rides greatly on the inner peripheral surface of the recess 22 of the sleeve 2 and the sleeve 2 is seated in the same manner as described above. The clutch discs 40 and 42 are disengaged by sliding over the gap 60 of 6 to disconnect the connection between the drive shaft 1 and the driven member 5.
【００２２】 また、本トルクリミッタは駆動側と被駆動側の方向が反対になっても全く支障 なく作動する。Further, the torque limiter operates without any problem even if the directions of the driving side and the driven side are reversed.
【００２３】 本件考案者は本考案に係るトルクリミッタを試作し、クラッチディスクの摩擦 面に他の表面安定化層を形成した比較装置と性能の比較試験を行った。本考案装 置では、インナーディスクには厚み１．６ｍｍの電気亜鉛メッキ鋼板を使用し、 アウターディスクには厚み１．２ｍｍの冷間圧延鋼板の摩擦面に、ＭｏＳ2 、グ ラファイト及びエポキシ系バインダーからなるモリコート１０６（大東化学社製 商品名）を１０〜２０μｍの厚みで均一に塗布して表面安定化層を形成したもの を使用した。他方、比較装置については、１．２ｍｍ厚の冷間圧延鋼板製アウタ ーディスクの摩擦面にＭｏＳ2 、グラファイト及び無機系バインダー（又は無機 系基油）からなるモリコート３２１Ｒ（大東化学社製商品名）を１０〜２０μｍ の厚みで均一に塗布して表面安定化層を形成したもの（比較装置１）、同じく１ ．２ｍｍ厚の冷間圧延鋼板製アウターディスクの摩擦面に、亜鉛メッキを１０〜 ２０μｍの厚みで形成したもの（比較装置２）を使用した。試験は１秒ＯＮ、１ 秒ＯＦＦのクラッチディスクの接断を繰り返し、その時の動トルク及び静トルク を測定した。試験結果を表１に示す。The present inventor prototyped the torque limiter according to the present invention and conducted a performance comparison test with a comparative device in which another surface stabilizing layer was formed on the friction surface of the clutch disc. In the device of the present invention, an electro-galvanized steel plate with a thickness of 1.6 mm is used for the inner disc, and a friction surface of a cold-rolled steel plate with a thickness of 1.2 mm is used for the outer disc, MoS 2 , grafite and an epoxy binder. Molycoat 106 (trade name, manufactured by Daito Kagaku Co., Ltd.) was uniformly coated in a thickness of 10 to 20 μm to form a surface stabilizing layer. On the other hand, for the comparative device, Molycoat 321R (trade name, manufactured by Daito Chemical Co., Ltd.), which is made of MoS 2 , graphite and an inorganic binder (or an inorganic base oil) on the friction surface of a 1.2 mm thick cold rolled steel plate outer disk Of 10 to 20 μm uniformly applied to form a surface stabilizing layer (Comparative Device 1). A 2 mm thick outer disk made of cold-rolled steel plate was galvanized on the friction surface to a thickness of 10 to 20 μm (Comparative device 2). In the test, the clutch disc was turned on for 1 second and turned off for 1 second repeatedly, and the dynamic torque and static torque at that time were measured. The test results are shown in Table 1.
【００２４】[0024]
【表１】 [Table 1]
【００２５】 表１から、本考案装置及び比較装置１、２とも４万回程度の慣らし動作で設計 上の動トルク及び静トルクに達するが、比較装置１では切断回数が８５万回以上 、比較装置２では切断回数が６０万回以上になると、動トルク及び静トルクとも 設計上のトルクから低下が見られた。これに対し、本考案装置については１２５ 万回で漸く動トルク及び静トルクに低下が見られた。このことから、本考案の装 置は性能の経年変化が非常に少なく、通常の使用年数内においてはほとんど性能 低下がないことが分かる。It can be seen from Table 1 that both the device of the present invention and the comparison devices 1 and 2 reach the designed dynamic torque and static torque by a break-in operation of about 40,000 times, but the comparison device 1 cuts 850,000 times or more. In the device 2, when the number of cuts was 600,000 or more, both the dynamic torque and the static torque decreased from the designed torque. On the other hand, in the device of the present invention, the dynamic torque and the static torque gradually decreased after 1.25 million times. From this, it can be seen that the device of the present invention has very little change in performance over time, and there is almost no deterioration in performance within the normal number of years of use.
【００２６】 なお、本件考案者らは、クラッチディスクをばね部材の付勢力に抗して相互に 滑らせる方式の従来の多板式トルクリミッタについて、そのクラッチディスクの 摩擦面に同様の表面安定化層を１０〜２０μｍ形成したところ、本考案装置に比 して劣るものの、設定した伝達トルクの経年変化が表面安定化層を形成しない場 合に比して少なく、信頼性を向上できることが確認された。The inventors of the present invention have proposed a conventional multi-plate torque limiter of the type in which the clutch discs slide against each other against the biasing force of the spring member, and a similar surface stabilizing layer is provided on the friction face of the clutch discs. It was confirmed that, although 10 to 20 μm was formed, it was inferior to the device of the present invention, but the secular change of the set transmission torque was smaller than that when the surface stabilizing layer was not formed, and the reliability could be improved. .
【図面の簡単な説明】[Brief description of drawings]
【図１】 本考案の一実施例によるトルクリミッタを示
す断面側面構成図である。FIG. 1 is a sectional side view showing a torque limiter according to an embodiment of the present invention.
【図２】 上記トルクリミッタにおいて被駆動部材を除
いた状態を示す分解組立斜視図である。FIG. 2 is an exploded perspective view showing a state in which a driven member is removed from the torque limiter.
１ 駆動軸 １６ ボール穴（凹部） ２２ 凹部 ３ カム機構 ３０ カムボール ４０ インナーディスク ４２ アウターディスク ５ 被駆動部材 ７ ばね部材 ８ 表面安定化層 1 Drive Shaft 16 Ball Hole (Recess) 22 Recess 3 Cam Mechanism 30 Cam Ball 40 Inner Disc 42 Outer Disc 5 Driven Member 7 Spring Member 8 Surface Stabilizing Layer
Claims (1)
ね部材によって軸線方向に付勢されて駆動軸と被駆動部
材とが切断可能に接続されている一方、 上記駆動軸と被駆動部材との間には第１、第２の凹状カ
ム面間にカムボールを遊嵌して構成されたカム機構が設
けられ、上記駆動軸と被駆動部材との間の所定以上の過
剰の回転力又は回転抵抗力が上記カム機構で軸線方向の
変位に変換され、該変位によって上記ばね部材のクラッ
チディスクに対する付勢が遮断又は減少可能となってお
り、 少なくとも一方の上記クラッチディスクの摩擦面にはＭ
ｏＳ2 及びグラファイトを主成分としエポキシ系バイン
ダーを使用してなる表面安定化層が１０〜２０μｍの厚
みで形成されていることを特徴とするトルクリミッタ。1. A drive shaft and a driven member are detachably connected to each other by at least a pair of clutch discs being axially urged by a spring member, and a drive shaft and a driven member are connected between the drive shaft and the driven member. A cam mechanism configured by loosely fitting a cam ball between the first and second concave cam surfaces is provided, and an excessive rotational force or rotational resistance force between the drive shaft and the driven member which is equal to or larger than a predetermined value is set as described above. The cam mechanism converts the displacement into an axial direction displacement, and the displacement can block or reduce the bias of the spring member against the clutch disc. At least one friction surface of the clutch disc has M
A torque limiter characterized in that a surface stabilizing layer containing oS 2 and graphite as a main component and using an epoxy binder is formed with a thickness of 10 to 20 μm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3111993U JPH0684027U (en) | 1993-05-17 | 1993-05-17 | Torque limiter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3111993U JPH0684027U (en) | 1993-05-17 | 1993-05-17 | Torque limiter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0684027U true JPH0684027U (en) | 1994-12-02 |
Family
ID=12322529
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3111993U Pending JPH0684027U (en) | 1993-05-17 | 1993-05-17 | Torque limiter |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0684027U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0989103A (en) * | 1995-09-20 | 1997-03-31 | Seirei Ind Co Ltd | Shock preventing structure of geared speed changer |
| JP2010270869A (en) * | 2009-05-22 | 2010-12-02 | Kubota Corp | Power transmission mechanism and crushing device |
| JP2012522951A (en) * | 2009-04-06 | 2012-09-27 | メシエ−ブガッティ−ドウティ | Mechanical device for transmitting force with threshold |
| JP2013200027A (en) * | 2012-02-22 | 2013-10-03 | Takimoto Yoshie | Torque control device |
| JP2015068374A (en) * | 2013-09-27 | 2015-04-13 | 多摩川精機株式会社 | Torque limiter |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5027873A (en) * | 1973-07-11 | 1975-03-22 | ||
| JPH01316558A (en) * | 1988-06-17 | 1989-12-21 | Mitsubishi Electric Corp | Device for limiting transmission of torque |
| JPH0319606A (en) * | 1989-06-14 | 1991-01-28 | Yanmar Agricult Equip Co Ltd | Method for image processing in steering control of harvester |
| JPH04165125A (en) * | 1990-10-26 | 1992-06-10 | Matsushita Electric Ind Co Ltd | Electromagnetic clutch |
| JPH04191526A (en) * | 1990-11-26 | 1992-07-09 | Tsubakimoto Emason:Kk | Overload clutch |
-
1993
- 1993-05-17 JP JP3111993U patent/JPH0684027U/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5027873A (en) * | 1973-07-11 | 1975-03-22 | ||
| JPH01316558A (en) * | 1988-06-17 | 1989-12-21 | Mitsubishi Electric Corp | Device for limiting transmission of torque |
| JPH0319606A (en) * | 1989-06-14 | 1991-01-28 | Yanmar Agricult Equip Co Ltd | Method for image processing in steering control of harvester |
| JPH04165125A (en) * | 1990-10-26 | 1992-06-10 | Matsushita Electric Ind Co Ltd | Electromagnetic clutch |
| JPH04191526A (en) * | 1990-11-26 | 1992-07-09 | Tsubakimoto Emason:Kk | Overload clutch |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0989103A (en) * | 1995-09-20 | 1997-03-31 | Seirei Ind Co Ltd | Shock preventing structure of geared speed changer |
| JP2012522951A (en) * | 2009-04-06 | 2012-09-27 | メシエ−ブガッティ−ドウティ | Mechanical device for transmitting force with threshold |
| JP2010270869A (en) * | 2009-05-22 | 2010-12-02 | Kubota Corp | Power transmission mechanism and crushing device |
| JP2013200027A (en) * | 2012-02-22 | 2013-10-03 | Takimoto Yoshie | Torque control device |
| JP2015068374A (en) * | 2013-09-27 | 2015-04-13 | 多摩川精機株式会社 | Torque limiter |
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